PVElite Manual

12777 Jones Rd. Ste. 480 Houston, TX 77070 Tel: 281 890-4566 FAX: 281 890-3301 Web: www.coade.com January 1, 2002 Dear PVElite User, Enclosed please find Version 4.3 of the PVElite Pressure Vessel Design and Analysis software program. This package includes a CD-ROM and update pages to the manual. The program installs using the Setup program on the CD. The CD contains an auto-run feature that should automatically start the installation process. If it does not start, execute the setup program contained on the CD. The installation serial number is located on the inside of the CD jacket. Do not discard the jacket. Some New Features of Version 4.3 are: • • • • • • • • •

Tailing lug analysis Leg Baseplate Analysis Updated 3-D Graphics Considerations for Rectangular Top head platforms and Caged Ladders PD 5500 Annex F Nozzle Calculations IBC 2000 Earthquake Code Added Modal Natural Frequency Solver Dynamic Response Spectrum Analysis added, including IBC 2000 and ASCE 7-98 parameters ASME 2001 Code 2001 addenda updates

Component Analysis Features: • • • • • • • • • • •

ASME 2001 Code 2001 Addenda update Div1 or Div2 database available when using WRC 107 Split Screen Graphics Tailing Lug Analysis Thick Shell band entry for ASME fixed tubesheets Pneumatic Hydrotest calks added Simplified input for non-radial Nozzles Static Head Input in the nozzle module Improved Summary Improved On-line registration Tailing Lug Calculations

Plus many others

This version of PVElite has been extensively tested according to the QA standards established at COADE. At least 115 different vessel jobs have been run to verify the results of the program.

Important Release Notes For the HTML Help system to work properly, you must install Internet Explorer 5 or later. IE5 updates critical Windows DLLs and also installs DCOM 95 on Windows 95 machines if it is not present. DCOM 95 allows the “CodeCalc” portion of PVElite to function properly. Otherwise the error “Failed to create empty document” may appear when that processor is invoked. IE5 can be installed from the PVElite CD. If version 4.2 is working fine, this step is not necessary. Please note that Microsoft has dropped support for Windows 95. Windows 9x will not be supported after this release. For network users, the file netuser.bat must be executed from each workstation. This will register some critical DLLs that allow the 3-D modeler to function properly. If this is not done, the 3-D graphics modeler will abort with an error. The error will state that some XML components are not available.

Sincerely, PVElite Development Staff

PVElite User's Guide Version 4.3 PVElite is a PC-based pressure vessel design and analysis software program developed, marketed, and sold by COADE Engineering Software.

Version 4.30 Revised 1/2002

This page is intentionally left blank.

PVElite - User Guide

Contents Preface PVElite LICENSE AGREEMENT P-2 ACCEPTANCE OF TERMS OF AGREEMENT BY THE USER P-2 LICENSE GRANT P-2 TERM P-2 LIMITED WARRANTY P-3 ENTIRE AGREEMENT P-3 LIMITATIONS OF REMEDIES P-3 GENERAL P-4 DISCLAIMER - PVElite P-4

HOOPS‘ License Grant P-6

Chapter: 1 Introduction What is PVElite? 1-1 What is the purpose and scope of the PVElite Program? 1-1What distinguishes PVElite from other commercial pressure vessel packages? 1-3 What Applications are Available? 1-4 General Vessels 1-4 Complete Vertical Vessels 1-4 Complete Horizontal Vessels 1-4 Individual Shells & Heads 1-4 Conical Sections 1-4 Vessel Nozzles 1-4 Flanges 1-4 Base Rings 1-5 Lifting Lug 1-5 Pipe & Pad 1-5 Local Stress Calculation Due To Attached Loads 1-5 Thin-Walled Expansion Joints 1-5 Thick-Walled Expansion Joints 1-5 TEMA Tubesheets 1-5 ASME Tubesheets 1-5 Floating Heads 1-5 Half-Pipe Jacket 1-6 Large Openings 1-6 Rectangular Vessels 1-6 Shells & Heads 1-6 Nozzles 1-6 Flanges 1-6 Horizontal Vessels 1-6 Legs & Lugs 1-7 WRC 107 1-7 Summary 1-7 WRC 297 1-7 Appendix Y Flanges 1-7

About the PVElite Documentation 1-8 Program Support / User Assistance 1-9 COADE Technical Support Phone Numbers 1-9

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Updates 1-10 Licenses 1-10 Full Run 1-10 Lease 1-10 Limited Run 1-10

Summary of Version 3.5 Improvements 1-11 Summary of Version 3.6 Improvements 1-11 PV Elite Component Analysis New Features 1-11 Summary of PVElite Version 4.00 Improvements 1-12 Summary of Version 4.1 Improvements 1-12 Summary of Version 4.2 Improvements 1-13 PV Elite Component Analysis New Features Version 4.2 1-14 Summary of Version 4.3 Improvements 1-14 PV Elite Component Analysis New Features Version 4.3 1-14

Chapter: 2 Overview of the Installation/Configuration Process System and Hardware Requirements 2-1 External Software Lock 2-1 Starting the Installation Procedure 2-2 Installing PVElite 2-4

Network Installation / Usage 2-7 Software Installation on a Network Drive 2-7

ESL Installation on a Network 2-7 Novell File Server ESL Installation 2-8 Novell Workstation ESL Installation 2-8 Windows Server Installation 2-8

Notes on Network ESLs 2-8

Chapter: 3 Tutorial / Master Menu Program Structure and Control 3-1 A Road Map for PVElite 3-2 The Input Processor 3-3 Other Input Processors 3-6 Error Checking 3-9 Analysis 3-10 Tools Menu 3-11 Output Review & Report Generation 3-12 Design and Analysis of Vessel Details 3-14 Main Menu 3-16 File Menu 3-17 Input Menu 3-20 Analyze Menu 3-22 Output Menu 3-23 Tools Menu 3-24 Print Water Volume in Gallons? 3-24 Use AD-540.2 sketch b and not sketch d for normal? 3-25 Round Thickness to Nearest Nominal Size? 3-25

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Compute Increased Nozzle Thickness? 3-25 Compute and Print Areas for Small Nozzles? 3-25 Print Equations and Substitutions? 3-25 Increase Blind Flange Thickness for Reinforcement? 3-25 Use OD as the Basis for the shell Radius in Zick? 3-26 Allowable Tower Deflection 3-26 Wind Shape Factor 3-26 Do not use the bolt correction factor. 3-26 Use Pre-99 Addenda Division 1 only. 3-26 Use Code Case 2260/2261. 3-26 Use EigenSolver 3-27

Diagnostics Menu 3-29 View Menu 3-30 Using the 3D Viewer 3-32

ESL Menu 3-38 Help Menu 3-39 Quick Start with PVElite 3-40 Entering PVElite 3-40 Defining the Basic Vessel 3-40

Adding Details 3-42 Recording the Model - Plotting the Vessel Image 3-43 Specifying Global Data - Loads and Design Constraints 3-45 Running the Analysis 3-48 Reviewing the Results 3-49 Analyzing Individual Vessel Components (Details) 3-50 DXF File Generation Option 3-53 Setting Up the Required Parameters 3-53 User Border Creation 3-54 Invoking the Drawing 3-55

Chapter: 4 Element Data Element Basic Data 4-2 Element’s From Node 4-2 Element’s To Node 4-3 Inside Diameter 4-3 Distance 4-3 Finished Thickness 4-3 Corrosion Allowance 4-4 Wind Load Diameter Multiplier 4-4 Material Name 4-4 Joint Efficiency for Longitudinal and Circumferential Seams 4-4 Design Internal Pressure 4-5 Design Temperature for Internal Pressure 4-5 Design External Pressure 4-5 Examples of external pressure 4-5 Design Temperature for External Pressure 4-5

Element Additional Data 4-6 Cylindrical Shell 4-6 Elliptical Head 4-6 Head Factor 4-6 Inside Head Depth 4-6

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Torispherical Head 4-7 Crown Radius 4-7 Knuckle Radius 4-7

Spherical Head 4-8 Conical Head or Shell Segment 4-8 To Node Diameter 4-8 Cone Length 4-8 Half Apex Angle 4-8 Toriconical 4-9 Toricone Dialog 4-9 Large End Knuckle Radius 4-9 Large End Knuckle Thickness 4-9 Small End Knuckle Radius 4-9 Small End Knuckle Thickness 4-9

Welded Flat Head 4-10 Attachment Factor 4-10 Non-Circ. Small Diameter 4-10

Flange Analysis 4-11 Body Flange 4-11

Flange Input Data 4-14 Flange Type 4-14 Weld Neck Flanges 4-14 Slip-on Flanges 4-14 Ring Flanges 4-14 Lap Joint Flanges 4-14 Reverse Geometry Flanges 4-14 Split Loose-type Flanges (mostly with lap joints) 4-14 Flat Face Flanges with Full Face Gaskets 4-15 Integral Ring (3) & Loose Ring (5) Additional Data 4-15 Lap Joint (6) Additional Data 4-15 Blind (7) Additional Data 4-15 Hub Thickness, Small End 4-17 Hub Thickness, Large End 4-17 Hub Length 4-17 Bolt Material Specification 4-17 Bolt Allowable Stress, Design Temperature 4-17 Bolt Allowable Stress, Ambient Temperature 4-18 Diameter of Bolt Circle 4-18 Nominal Bolt Diameter 4-18 Thread Series 4-18

User-Specified Root-Area Additional Data 4-18 Number of Bolts 4-18 Gasket Factor m 4-18 Gasket Design Seating Stress y 4-18 Flange Face Facing Sketch 4-19 Column for Gasket Seating (I, II) 4-19 Gasket Thickness 4-19 Nubbin Width (or width of Ring Joint) 4-19

Partition Gasket Additional Data 4-19

External Loads 4-20 External Loads Additional Data 4-20

Mating Flange Loads 4-21 Mating Loads Additional Data 4-21

Skirt Support with Basering 4-23 Inside Diameter at Base 4-23 Basering Dialog 4-23

Basering Analysis 4-24 Thickness of a Basering Under Compression 4-24

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Thickness of Basering Under Tension 4-26 Thickness of Top Ring Under Tension 4-26 Required Thickness of Gussets in Tension 4-26 Required Thickness of Gussets in Compression 4-26 Basering Design 4-27 Selection of Number of Bolts 4-27 Calculation of Required Area for each Bolt 4-27 Selection of the Bolt Size 4-27 Selection of Preliminary Basering Geometry 4-27 Analysis of Preliminary Basering Geometry 4-27 Selection of Final Basering Geometry 4-27 Analysis of Basering Thicknesses 4-28 Basic Skirt Thickness 4-28 Stress in Skirt due to Gussets or Top Ring 4-28 Brownell and Young Method 4-28

Basering Input Data 4-30 Basering Description 4-30 Analyze or Design Basering 4-30 Temperature of Basering (needed if not ambient) 4-30 Thickness of Basering 4-30 Basering Material Specification 4-30 Inside Diameter of Basering 4-30 Outside Diameter of Basering 4-30 Bolt Material Specification 4-31 Nominal Bolt Diameter 4-31 Number of Bolts 4-31 Diameter at Bolt Circle 4-31 Bolt Table (Fine Thread, TEMA ), (Coarse, UNC ) User 4-31 Bolt Table 3 Additional Data 4-32 User Specified Root Area of a Single Bolt 4-32

Nominal Compressive Stress of Concrete 4-32 Allowable Compressive Strength of Concrete 4-32 Bolt Corrosion Allowance 4-32 Gussets Additional Data 4-32 Thickness of Gusset Plates 4-32 Height of Gussets 4-32 Distance between Gussets 4-32 Average Width of Gusset Plates 4-32 Elastic Modulus for Plates 4-32 Yield Stress for Plates 4-32

Thickness of Top Ring 4-32 Width of Top Ring 4-33 External Corrosion Allowance 4-33

Tailing Lug Analysis 4-34 Tailing Lug Input Data 4-35 Perform Tailing Lug Analysis 4-35 Tail Lug Type 4-35 Centerline Offset 4-35 Lug Thickness 4-35 Pin Hole Diameter 4-35 Weld Size Thickness 4-35 Lug Height (only if no Top Ring) 4-35 Discussion of Results 4-36

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Chapter: 5 Vessel Detail Data Introduction 5-1 Assigning Details to Elements 5-3 Detail Definition Buttons 5-4 Defining the Details 5-6 From Node 5-6 Distance from “From” Node or Offset from Vessel Centerline 5-6 Detail ID 5-6

Rings 5-7 Inside Diameter of Ring 5-8 Outside Diameter of Ring 5-8 Thickness of Ring 5-8 Ring Material 5-8 Moment of Inertia 5-8 Cross Sectional Area 5-8 Distance to Ring Centroid 5-8 Name of Section Type 5-8

Nozzles 5-10 Overriding Nozzle Weight 5-10

Nozzle Analysis 5-11 Nozzle Input Data 5-13 Nozzle Description 5-13 Angle Between Nozzle and Shell 5-13 Offset Distance from Cylinder/Head Centerline (L1) 5-13 Class for Attached B16.5 Flange 5-13 Grade for Attached B16.5 Flange 5-13

Modification of Reinforcing Limits 5-14 Physical Maximum for Nozzle Diameter Limit 5-14 Physical Maximum for Nozzle Thickness Limit 5-14 Do you want to set Area1 or Area 2 to 0 5-14 Nozzle Material Specification 5-14 Nozzle Diameter Basis 5-14 Actual or Nominal Diameter of Nozzle 5-14 Nozzle Size and Thickness Basis 5-14 Actual Diameter and Thickness 5-15 Nominal Diameter and Thickness 5-15 Minimum Diameter and Thickness 5-15 Actual Thickness of Nozzle 5-15 Nominal Schedule of Nozzle 5-15 Nozzle Corrosion Allowance 5-15 Joint Efficiency of Shell Seam through which Nozzle Passes 5-15 Joint Efficiency of Nozzle Neck 5-15 Insert Nozzle or Abutting Nozzle 5-16 Nozzle Outside Projection 5-16 Weld Leg Size for Fillet Between Nozzle and Shell or Pad 5-16 Depth of Groove Weld Between Nozzle and Vessel 5-16 Nozzle Inside Projection 5-16 Weld Leg Size Between Inward Nozzle and Inside Shell 5-16 Local Shell Thickness 5-16 Shell Tr Value 5-16 Tapped Hole Area Loss 5-17 Additional Data for Reinforcing Pad 5-17

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Pad Outside Diameter along Vessel Surface 5-17 Pad Thickness 5-17 Pad Weld Leg Size as Outside Diameter 5-17 Depth of Groove Weld between Pad and Nozzle Neck 5-17 Pad Material 5-17 ASME Code Weld Type 5-17 ASME Code Weld Type 5-17 Flange Type 5-18 Flange Material 5-18

Lugs 5-19 Distance from Vessel OD to Lug Midpoint 5-19 Lug Bearing Width 5-19 Radial Width of Bottom Support Plate 5-19 Length of Bottom Lug Support Plate 5-19 Thickness of Bottom Plate 5-20 Distance between Gussets 5-20 Mean Width of Gussets 5-20 Height of Gussets 5-20 Thickness of Gussets 5-20 Radial Width of Top Plate/Ring 5-20 Thickness of Top Plate/Ring 5-20 Overall Height of Lug 5-20 Overall Width of Lug 5-20 Weight of One Lug 5-20 Number of Lugs 5-20 Perform WRC 107 Calc 5-20 Pad Width 5-20 Pad Thickness 5-21 Pad Length 5-21

Weight 5-22 Miscellaneous Weight 5-22 Offset from Centerline 5-22

Forces and Moments 5-23 Force in X, Y, or Z Direction 5-23 Moment about X, Y, or Z Axis 5-23 Acts During Wind or Seismic 5-23

Platforms 5-24 Platform Start Angle (degrees) 5-24 Platform End Angle (degrees) 5-24 Platform Wind Area 5-24 Platform Weight 5-24 Platform Railing Weight 5-24 Platform Grating Weight 5-24 Platform Width 5-25 Platform Height 5-25 Platform Clearance 5-25 Platform Force Coefficient 5-25 Platform Wind Area Calculation [Installation \ Misc. Options] 5-25 Platform Length (Non- Circular) 5-25

Saddles 5-26 Width of Saddle 5-26 Centerline Dimension (B) 5-26 Saddle Contact Angle (degrees) 5-26 Height of Composite Stiffener 5-26 Width of Wear Plate 5-26

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Thickness of Wear Plate 5-26 Wear Plate Contact Angle (degrees) 5-27 Saddle Dimension A 5-27 Perform Saddle Check (Y/N) 5-27 Material Yield Stress 5-27 E for Plates 5-27 Baseplate Length 5-27 Baseplate Thickness 5-27 Baseplate Width 5-27 Number of Ribs 5-27 Rib Thickness 5-27 Web Thickness 5-27 Web Location 5-27 Height of Center Web 5-27

Trays 5-28 Number of Trays 5-28 Tray Spacing 5-28 Tray Weight Per Unit Area 5-28 Height of Liquid on Tray 5-28 Density of Liquid on Tray 5-28

Legs 5-29 Distance from Outside Diameter: or Diameter at Leg Centerline 5-29 Leg Orientation 5-29 Number of Legs 5-30 Section Identifier 5-30 Length of Leg 5-30

Packing 5-31 Height of Packed Section 5-31 Density of Packing 5-31

Liquid 5-33 Height/Length of Liquid 5-33 Density of Liquid 5-33

Insulation 5-35 Height/Length of Insulation / Fireproofing 5-35 Thickness of Insulation or Fireproofing 5-35 Insulation Density 5-35

Lining 5-36 Height/Length of Lining 5-36 Thickness of Lining 5-36 Density of Lining 5-36

Chapter: 6 General Vessel Data Design Data 6-2 Design Internal Pressure 6-2 Design Internal Temperature 6-2 Datum Line Distance 6-2 Hydrotest Type 6-2 1 - ASME UG-99(b) 6-2 2 - ASME UG-99(c) 6-2 3 - ASME UG-99(b) footnote 34 6-3

Hydrotest Position 6-3 Projection from Top 6-3 Projection from Bottom 6-3

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Min. Metal Temperature 6-3 Flange Distance to Top 6-3 Construction Type 6-3 Special Service 6-4 Degree of Radiography 6-4 Miscellaneous Weight 6-4 Use Higher Long. Stresses? 6-4 Hydro. Allowable Unmodified (Y/N) 6-4 Consider Vortex Shedding? 6-5 User Defined MAWP/MAPnc 6-5 User Defined Hydrostatic Test Pressure 6-5 Corroded Hydrotest? 6-5 Is This a Heat Exchanger 6-5

Installation Options 6-6 Platform Area Calculation Method 6-6 Stiffener Type 6-6 For Angle Sections Rolled the Hard Way 6-7 Bar Thickness to use Designing 6-7 Rigging Data 6-7 Impact Factor 6-7 Lug Distances from Base 6-8 Select from Standard Bar Ring List 6-8

Design Modification 6-9 Select Wall Thickness for Internal Pressure 6-9 Select Wall Thickness for External Pressure 6-9 Select Stiffening Rings for External Pressure 6-9 Select Wall Thickness for Axial Stress 6-9

Load Case 6-10 Nozzle Design Modifications 6-12 Nozzle Design Modifications, Design Pressure, M.A.W.P. + Static Head 6-12 Nozzle Design Modifications, Design Pressure, Design Pressure + Static Head 6-12 Nozzle Design Modifications, Design Pressure, Overall MAWP + Static Head 6-12 Nozzle Design Modifications, Consider MAP nc in Analysis 6-12 Modify Tr based on the Maximum Stress Ratio 6-12 Consider Code Case 2168 for Nozzle Design 6-13 Redesign Pads to Reinforce Openings 6-13 6-13

Wind & Seismic Data 6-14 Wind Data 6-14 Wind Design Code 6-14

ASCE Wind Data 6-15 Design Wind Speed 6-15 Exposure Constant 6-15 Base Elevation 6-15 Percent Wind for Hydrotest 6-15 ASCE 7-93 Importance Factor 6-15 ASCE Roughness Factor 6-16

UBC Wind Data 6-17 Design Wind Speed 6-17 Exposure Constant 6-17 Base Elevation 6-17 Percent Wind for Hydrotest 6-17 UBC Wind Importance Factor 6-17

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NBC Wind Data 6-19 Design Wind Speed 6-19 Exposure Constant 6-19 Base Elevation 6-19 Percent Wind for Hydrotest 6-19 Critical Damping Ratio 6-19 Roughness Factor 6-20

ASCE 95 Wind Data 6-21 Percent Wind for Hydrotest 6-21 Design Wind Speed 6-21 Base Elevation 6-21 Exposure Constant 6-21 Importance Factor 6-22 Roughness Factor 6-22 Height of Hill (H) 6-22 Distance to Site (x) 6-22 Height above Ground 6-22 Crest Distance 6-22 Type of Hill 6-22 Damping Factor 6-22

IS 875 Wind Code 6-24 Percent Wind for Hydrotest 6-24 Base Elevation 6-24 Wind Zone Number 6-24 Risk Factor 6-24 Terrain Category 6-24 Category 1 6-24 Category 2 6-24 Category 3 6-24 Category 4 6-24

Equipment Class 6-25 Consider Gust Response Factor 6-25

User-Defined Wind Profile 6-26 Percent Wind for Hydrotest 6-26 Wind Profile Data 6-26

Seismic Data 6-27 Seismic Design Code 6-27

ASCE 7-88 Seismic Data 6-28 Importance Factor 6-28 Soil Type 6-28 Horizontal Force Factor 6-29 Percent Seismic for Hydrotest 6-29 Seismic Zone 6-29

ASCE 7-93 Seismic Data 6-30 Seismic Coefficient Av 6-30 Seismic Coefficient Cc 6-30 Performance Criteria Factor P 6-30 Percent Seismic for Hydrotest 6-30 Amplification Factor ac 6-30

UBC Seismic Data 6-31 Importance Factor 6-31 Soil Type 6-31 Horizontal Force Factor 6-31 Percent Seismic for Hydrotest 6-31

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Seismic Zone 6-32

NBC Seismic Data 6-33 Importance Factor 6-33 Soil Type 6-33 Force Modification Factor 6-33 Percent Seismic for Hydrotest 6-34 Acceleration Zone 6-34 Velocity Zone 6-35

India’s Earthquake Standard IS-1893 RSM and SCM 6-36 Percent Seismic for Hydrotest 6-36 Importance Factor 6-36 Soil Factor 6-36 Zone Number 6-36 Period of Vibration 6-36 Damping Factor 6-36

ASCE-95 Seismic Data 6-37 Percent Seismic for Hydrotest 6-37 Importance Factor 6-37 Force Factor ( R ) 6-37 Seismic Coefficient Ca 6-37 Seismic Coefficient Cv 6-37

UBC 1997 Earthquake Data 6-38 Percent Seismic for Hydrotest 6-38 UBC Earthquake Importance Factor 6-38 Category Value 6-38

UBC Seismic Coefficient CA 6-38 UBC Seismic Coefficient CV 6-38 UBC Near Source Factor 6-38 UBC Seismic Zone 6-38 UBC Horizontal Force Factor 6-39

Seismic Load Input in G's 6-40 IBC-2000 Earthquake Parameters 6-41 EarthQuake Parameters Ss and Sl 6-41 Response Modification Factor R 6-41 Importance Factor 6-41 Moment Reduction Factor Tau 6-41 Seismic Design Category 6-41 EarthQuake Parameters Fa and Fv 6-41

Response Spectrum 6-43 Seismic for Hydrotest 6-43 Response Spectrum Name 6-43 User Defined 6-44 El Centro 6-44 ASCE 6-44 IBC 6-44 1.60D.5 6-44 1.60D2 6-44 1.60D5 6-44 1.60D7 6-44 1.60D10 6-45 Importance Factor 6-45 Shock Scale X|Y dir 6-45 Zero Period Acceleration 6-45 Combination Method 6-45

Acc.Based Factor Fa: 6-46

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Acc Based Factor Fv: 6-46 Max. Mapped Res. Acc. Ss: 6-46 Max. Mapped Res. Acc. Sl: 6-46 Response Modification R: 6-46 Coefficient Cd: 6-47 Range Type: 6-47 Ordinate Type: 6-47 Include Missing Mass Components: 6-47

Chapter: 7 PVElite Analysis Steps for Calculating and Displaying Vessel-Analysis Results 7-3 Step 0: Error Checking 7-3 Step 1: Input Echo 7-3 Step 2: XY Coordinate Calculations 7-3 Step 3: Internal Pressure Calculations 7-3 Step 4: Hydrotest calculations 7-3 Step 5: External Pressure calculations 7-3 British Standard PD:5500 7-4 Step 6: Weight of Elements 7-4 Step 7: Weight of Details 7-4 Step 8: ANSI Flange MAWP 7-4 Steps 9 and 10: Total weight and detail moment 7-5 Step 11: Natural Frequency Calculation 7-6 Step 12: Wind Load Calculation 7-6 Step 13: Earthquake Load Calculation 7-6 Step 14: Shear and Bending Moments due to Wind and Earthquake 7-6 Step 15: Wind Deflection 7-6 Step 16: Longitudinal Stress Constants 7-6 Step 17: Longitudinal Allowable Stresses 7-6 Step 18: Longitudinal stresses due to . . . 7-6 Step 19: Stress due to Combined Loads 7-6

Optional Steps 7-8 Component Analysis 7-9

Chapter: 8 Output / Review Generating Output 8-1 The Review Screen 8-2 Using Review 8-3 Component Analysis 8-4 Purpose of This Chapter 9-1

Chapter: 9 Component Analysis Tutorial Starting the PVElite Component Analysis Module 9-1 Component Analysis Main Menu 9-2 File Menu 9-2

Edit Menu 9-5 Analysis Menu 9-6 Output Menu 9-8

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Tools Menu 9-9 Configuration 9-9 Computation Control Tab 9-9 Miscellaneous Tab 9-11

Diagnostics Menu 9-16 ESL Menu 9-17 View Menu 9-18 Help Menu 9-19 Performing an Analysis 9-20 Reviewing the Results - The Output Option 9-25 Printing or Saving Reports to a File 9-27 Printing the Reports 9-27

Summary - Seeing Results for a Whole Vessel 9-28 Tutorial Problem Printout 9-29

Chapter: 10 The Shell Module Introduction 10-1 Purpose, Scope, and Technical Basis 10-1Discussion of Input Data 10-5 Main Input Fields 10-5 Design Internal Pressure 10-5 Design Temperature for Internal Pressure 10-5 Design External Pressure 10-5 Design Temperature for External Pressure 10-5 Shell Section Material 10-5 Include Hydrostatic Head Component 10-5 Shell Allowable Stress at Design Temperature 10-5 Shell Allowable Stress at Ambient Temperature 10-6 Joint Efficiency for Longitudinal Seams 10-6 Is the Shell/Head Material Normalized? 10-6 Type of Shell or Head 10-6 Diameter Basis 10-7 Diameter of Shell/Head 10-7 Minimum Thickness of Pipe or Plate 10-7 Nominal of Average Thickness of Pipe or Plate (optional) 10-7 Corrosion Allowance 10-7 Type of Reinforcing Ring 10-7 Minimum Design Metal Temperature 10-7 Skip UG-16(B) Minimum Thickness Calculation 10-8

Pop-up Input Fields 10-9 Operating Liquid Density 10-9 Height of Liquid Column Operating 10-9 Height of Liquid Column Hydrotest 10-9 Design Length of Section 10-9 Design Length for Cylinder Volume Calculations 10-9 Aspect Ratio for Elliptical Heads 10-9 Crown Radius for Torispherical Heads 10-9 Length of Straight Flange 10-9 Knuckle Radius for Torispherical Heads 10-9 Half APEX Angle for Conical Sections 10-10 Large Diameter for Non-Circular Welded Flat Heads 10-10 Attachment Factor for Flat Head 10-10 Width of Reinforcing Ring 10-10 Thickness of Reinforcing Ring 10-10 Size of Fillet Weld Leg Connecting Ring to Shell 10-10 Ring Type to Satisfy Inertia and Area Requirements 10-11 Ring Weld Attachment Style (Intermittent, Continuous, Both) 10-11 Location of Ring (Internal or External) 10-11

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Moment of Reinforcing Ring 10-11 Cross-Sectional Area of Reinforcing Ring 10-11 Distance from Ring Centroid to Shell Surface 10-11 Is the Ring Angle Rolled the Hard Way? 10-12

Results 10-13 Status Bar 10-13 Thickness Due to Internal Pressure 10-13 Maximum Allowable Working Pressure at Given Thickness 10-13 Maximum Allowable Working Pressure, New & Cold 10-14 Actual Stress at Given Pressure and Thickness 10-14 Summary of Internal Pressure Results 10-14 Minimum Metal Temperatures 10-14 Weight & Volume Results, No Corrosion Allowance 10-14 Results for Maximum Allowable External Pressure 10-14 Results for Required Thickness for External Pressure 10-15 Summary of External Pressure Results 10-15

Example Problems 10-16

Chapter: 11 The Nozzle Module Introduction 11-1 Purpose, Scope, and Technical Basis 11-1 Discussion of Input Data 11-3 Main Input Fields 11-3 Pop-Up Input Fields 11-10 Discussion of Results 11-13


Chapter: 12 The Flange Module Introduction 12-1 Purpose, Scope, and Technical Basis 12-1Discussion of Input Data 12-4 Main Input Fields 12-4 Pop-Up Input Fields 12-11

Discussion of Results 12-14 Status Bar 12-14 Flanges with Different Bending Moments 12-14 Blind Flanges and Channel Covers 12-14 Allowable Flange Stresses 12-15


Chapter: 13 The Conical Sections Module 13-1 Introduction 13-1 Purpose, Scope, and Technical Basis 13-1 Cone Number 13-2 Cone Description 13-2 Internal Design Pressure 13-2 Internal Design Temperature 13-2 External Design Pressure 13-2 External Design Temperature 13-2 Cone\Cylinder\Ring\Knuckle Material Name 13-3 Material Allowable Stress, Design Temperature 13-3 Material Allowable Stress, Ambient Temperature 13-3 Cone Joint Efficiency 13-3 Cone Actual Thickness 13-3 Cone Corrosion Allowance 13-3 Cone Diameter Basis ( ID, OD ) 13-4

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Cone Diameter at Small End 13-4 Cone Diameter at Large End 13-4 Cone Half Apex Angle 13-4 Cone Axial Length 13-4 Are There Axial Forces on the Cone? 13-4 Small Cylinder Joint Efficiency 13-4 Small Cylinder Actual Thickness 13-4 Small Cylinder Corrosion Allowance 13-5 Small Cylinder Axial Strength 13-5 Small End Reinforcing (None, Bar, Section, Knuckle) 13-5 Large Cylinder Joint Efficiency 13-5 Large Cylinder Actual Thickness 13-5 Large Cylinder Corrosion Allowance 13-5 Large Cylinder Axial Length 13-5 Large End Reinforcing (None, Bar, Section, Knuckle) 13-5 Cone Circumferential Joint Efficiency 13-6

Pop-Up Input Fields 13-7 Take Cone as Lines of Support for External Pressure? 13-7 Total Axial Force on Large End for Internal Pressure Case 13-7 Total Axial Force on Large End for External Pressure Case 13-7 Total Axial Force on Small End for Internal Pressure Case 13-7 Total Axial Force on Small End for External Pressure Case 13-7 Location of Reinforcing Cone ( Shell, Cone ) 13-7 Radial Width of Reinforcing Ring 13-8 Axial Thickness of Reinforcing Ring 13-8 Moment of Inertia of Reinforcing Section 13-8 Cross-Sectional Area of Reinforcing Section 13-8 Distance to Centroid of Reinforcing Section 13-8 Knuckle Bend Radius, Large End 13-8 Knuckle Thickness, Large End 13-8 Knuckle Bend Radius, Small End 13-8 Knuckle Thickness, Small End 13-8

Discussion of the Results 13-9 Internal Pressure Results 13-9 External Pressure Results 13-9 Reinforcement Calculations Under Internal Pressure 13-9 Reinforcement Calculations Under External Pressure 13-10

Example Problems 13-11 Example Problem #1 13-11 Example Problem #2 13-14 Example Problem #3 13-18

Chapter: 14 The Floating Head Module Introduction 14-1 Purpose, Scope, and Technical Basis 14-1 Discussion of Input Data 14-3 Main Input Fields 14-3

Pop-Up Input Fields 14-8 Bolt Root Area 14-8 Inside Depth of Flange from Flange Face to Attached Head 14-8 Backing Ring Inside Diameter 14-8 Backing Ring Actual Thickness 14-8 Number of Splits in Backing Ring (0, 1, or 2) 14-8

Discussion of Results 14-9 Internal Pressure Results for the Head 14-9

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External Pressure Results for the Head 14-9 Intermediate Calculations for Flanged Portion of Head 14-9 Required Thickness Calculations 14-9 Soehren’s Calculations 14-9

Example Problems 14-11 Example Problem #1 14-11 Example Problem #2 14-14

Chapter: 15 The Horizontal Vessel Module Introduction 15-1 Discussion of Input 15-1 Main Input Fields 15-1Pop-Up Input Fields 15-5 Base Plate Length 15-5 Base Plate Thickness 15-5 Base Plate Width 15-5 Number of Ribs 15-5 Thickness of Ribs 15-5 Thickness of Web 15-5 Web Location Center or Side 15-5 Height of Center Web 15-5 Force Coefficient 15-5 Additional Area 15-5 Wind Pressure on Vessel 15-5 Importance Factor ( I ) 15-6 Basic Wind Speed 15-6 Wind Exposure 15-6 Height of Vessel Above Grade 15-6 Distance from Vessel Centerline to Saddle Base 15-6 Use ASCE 7-95 Code 15-6 Types of Hill 15-6 Height of Hill or Escarpment (H) 15-7 Distance to Site (x) 15-7 Height Above Ground (z) 15-7 Distance to Crest (Lh) 15-7 Natural Frequency for the Structure (Fn) — Optional (Hz) 15-7 Damping Ratio (beta) — Optional 15-7 Seismic Zone 15-7 Distance from Vessel Centerline to Saddle Base 15-7 User-Entered Seismic Zone Factor CS 15-7 Aspect Ratio (D/2H) for Elliptical Heads 15-8 Knuckle Ratio for Torispherical Heads 15-8 Crown Radius for Torispherical Heads 15-8 Stiffening Ring Location 15-8 Stiffening Ring Material Specification 15-8 Stiffening Ring Properties 15-8 Moment of Inertia of Stiffening Ring 15-8 Cross-Sectional Area of Stiffening Ring 15-8 Distance to Ring Centroid from Shell Surface 15-9 Height of Stiffener from Shell Surface 15-9

Discussion of Results 15-10 Saddle Wear Plate Design 15-11 Restrictions of this Method 15-11

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Conclusions 15-11

Example Problem 15-14

Chapter: 16 The TEMA Tubesheet Module Introduction 16-1 Purpose, Scope, and Technical Basis 16-1 Discussion of Input Data 16-5 Main Input Fields 16-5


Chapter: 17 The WRC 107/FEA Module Introduction 17-1 Discussion of Input 17-2 Main Input Fields 17-2

Pop-Up Input Fields 17-7 Additional Input for VRC107 17-16 Additional Input for FEA 17-17

Discussion of Results 17-19 WRC107 Stress Calculations 17-19

WRC107 Stress Summations 17-22 ASME Section VIII Division 2 - Elastic Analysis of Nozzle 17-23 Finite Element Analysis (FEA): 17-27 Examples 17-29

Chapter: 18 The Leg & Lug Module Introduction 18-1 Discussion of Input 18-2 Main Input Fields 18-2

Pop-Up Input Fields 18-6 Vessel Leg Input 18-8 Leg Results 18-10 Support Lug Input 18-11 Lifting Lug Input 18-13 Output 18-16 Examples 18-17 Baseplate Input 18-24 Baseplate Results 18-27 Trunnion Input 18-28 Trunnion Result 18-31

Chapter: 19 The Pipe & Pad Module Introduction 19-1 Discussion of Input 19-1 Main Input Fields 19-1Pop-Up Input Fields 19-5 Output 19-6 Example Problem 19-10

xvii


Chapter: 20 The Base Ring Module Introduction 20-1 Calculation Techniques 20-1 Thickness of a Base Ring Under Compression 20-1 Thickness of Base Ring Under Tension 20-3 Thickness of Top Ring Under Tension 20-3 Required Thickness of Gussets in Tension 20-3 Required Thickness of Gussets in Compression 20-4 Base Ring Design 20-4 Selection of Number of Bolts 20-4 Calculation of Load per Bolt 20-4 Calculation of Required Area for each Bolt 20-4 Selection of the Bolt Size 20-4 Selection of Preliminary Base Ring Geometry 20-4 Analysis of Preliminary Base Ring Geometry 20-4 Selection of Final Base Ring Geometry 20-5 Analysis of Base Ring Thicknesses 20-5 Basic Skirt Thickness 20-5 Stress in Skirt due to Gussets or Top Ring 20-5

Discussion of Input 20-6 Main Input Fields 20-6

Pop-up Input Fields 20-10 Example Problem 20-13

Chapter: 21 The Thin Joint Module Introduction 21-1 Purpose, Scope, and Technical Basis 21-1 Discussion of Input Data 21-2 Main Input Fields 21-2

Pop-Up Input Fields 21-4 Example Problems 21-6

Chapter: 22 The Thick Joint Module Introduction 22-1 Discussion of Input Data 22-3 Main Input Fields 22-3 Pop-Up Input Fields 22-7

Discussion of Results 22-9 Example Problem 22-11

Chapter: 23 The ASME Tubesheets Module Introduction 23-1 Purpose, Scope, and Technical Basis 23-1 Discussion of Input Data 23-4 Main Input Fields 23-4

xviii


Pop-Up Input Fields 23-10

Discussion of Results 23-19 Example Problem 23-21

Chapter: 24 The Half-Pipe Module Introduction 24-1 Purpose, Scope, and Technical Basis 24-1 Discussion of Input Data 24-3 Discussion of Results 24-6 Example Problem 24-8

Chapter: 25 The Large Opening Module Introduction 25-1 Purpose, Scope, and Technical Basis 25-1 Discussion of Input Data 25-3 Main Input Fields 25-3

Example Problem 25-5

Chapter: 26 The Rectangular Vessel Module Introduction 26-1 Purpose, Scope, and Technical Basis 26-1Discussion of Input Data 26-9 Main Input Fields 26-9 Pop-Up Input Fields 26-13 Type of Reinforcing Ring 26-15 None—No reinforcing ring 26-15 Simple Bar Geometry—Enter the width, thickness, and length (if necessary) of the bar. 26-15 General Beam Section—Enter the moment of inertia, cross-sectional area, and the distance from the centroid. 2616

Discussion of Results 26-17 Example Problems 26-20

Chapter: 27 The WRC 297/Annex G Module Introduction 27-1 Purpose, Scope, and Technical Basis 27-1 Discussion of Input Data 27-1 Item Number 27-1 Description 27-1 Diameter Basis for Vessel 27-1 Vessel Diameter 27-1 Vessel Wall Thickness 27-1Vessel Corrosion Allowance 27-2 Design Pressure 27-2 Design Temperature 27-2 Vessel Material 27-2 Vessel Stress Concentration Factor 27-2 Is there a Reinforcing Pad? 27-2 Diameter Basis for Nozzle 27-2 Diameter of Nozzle 27-2 Nozzle Wall Thickness 27-2

xix


Nozzle Corrosion Allowance 27-2 Axial Force "P" (IN WRC 107 ) or FR (IN PD 5500) 27-3 Shear Force VC (IN WRC 107 ) or FC (IN PD 5500) 27-3 Shear Force VL (IN WRC 107 ) or FL (IN PD 5500) 27-3 Torsional Moment MT 27-3 Circumferential Moment MC 27-3 Longitudinal Moment ML 27-4 Add Axial Pressure Thrust ? 27-5 Use Stress Indices (AD 560.7)? 27-5 Additional Input for PD 5500, Annex G 27-6 Allowable Stress Increase Factor (Membrane + Bending) 27-6 Allowable Stress Increase Factor (Membrane) 27-6 Nozzle Inside Projection 27-6 Stiffened Length of Vessel Section 27-6 Offset from Left Tangent Line 27-6 Is the Location of the Nozzle in the Vessel Spherical? 27-6

Sample Calculation 27-7 Discussion of Results 27-11 Appendix G Sample Problem 27-12

Chapter: 28 The Appendix Y Module Introduction 28-1 Purpose, Scope, and Technical Basis 28-1 Gasket and Gasket Factors 28-2 Sample Calculation 28-3 Discussion of Results 28-8

Chapter: 29 Miscellaneous Processors File Manager 29-1 Heading Edit 29-3 Material Definition 29-4 Material Name 29-6 Allowable Stress at Ambient Temperature 29-6 Allowable Stress at Operating Temperature 29-6 Allowable Stress at Hydrotest Temperature 29-6 Nominal Density of this Material 29-6 P Number Thickness 29-7 Yield Stress, Operating 29-7 UCS-66 Chart Number 29-7 External Pressure Chart Name 29-8 Carbon Steel Materials 29-9 Heat Treated Materials 29-9 Stainless Steel (High Alloy) Materials 29-9 Non Ferrous Materials 29-9

TEMA Number 29-10 Keyboard Commands 29-11 Mouse Operation 29-12

Chapter: 30 Vessel Example Problems Introduction 30-1 Vessel Example 30-1

xx

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PVElite LICENSE AGREEMENT


PVElite LICENSE AGREEMENT Licensor: COADE/Engineering Physics Software, Inc., 12777 Jones Rd., Ste. 480, Houston, Texas 77070

ACCEPTANCE OF TERMS OF AGREEMENT BY THE USER YOU SHOULD CAREFULLY READ THE FOLLOWING TERMS AND CONDITIONS BEFORE USING THIS PACKAGE. USING THIS PACKAGE INDICATES YOUR ACCEPTANCE OF THESE TERMS AND CONDITIONS. The enclosed proprietary encoded materials, hereinafter referred to as the Licensed Program(s), are the property of COADE and are provided to you under the terms and conditions of this License Agreement. You assume responsibility for the selection of the appropriate Licensed Program(s) to achieve the intended results, and for the installation, use and results obtained from the selected Licensed Program(s).

LICENSE GRANT In return for the payment of the license fee associated with the acquisition of the Licensed Program(s) from COADE, COADE hereby grants you the following non-exclusive rights with regard to the Licensed Programs(s): a. Use of the License Program(s) on one machine. Under no circumstance is the License Program to be executed without a COADE External Software Lock (ESL). b. To transfer the Licensed Program(s) and license it to a third party if the third party acknowledges in writing its agreement to accept the Licensed Program(s) under the terms and conditions of this License Agreement; if you transfer the Licensed Program(s), you must at the same time either transfer all copies whether printed or in machine-readable form to the same party or destroy any copies not so transferred; the requirement to transfer and/or destroy copies of the Licensed Program(s) also pertains to any and all modifications and portions of Licensed Program(s) contained or merged into other programs. You agree to reproduce and include the copyright notice as it appears on the Licensed Program(s) on any copy, modification or merged portion of the Licensed Program(s). THIS LICENSE DOES NOT GIVE YOU ANY RIGHT TO USE COPY, MODIFY, OR TRANSFER THE LICENSED PROGRAM(S) OR ANY COPY, MODIFICATION OR MERGED PORTION THEREOF, IN WHOLE OR IN PART, EXCEPT AS EXPRESSLY PROVIDED IN THIS LICENSE AGREEMENT. IF YOU TRANSFER POSSESSION OF ANY COPY, MODIFICATION OR MERGED PORTION OF THE LICENSED PROGRAM(S) TO ANOTHER PARTY, THE LICENSE GRANTED HEREUNDER TO YOU IS AUTOMATICALLY TERMINATED.

TERM This License Agreement is effective upon acceptance and use of the Licensed Program(s) until terminated in accordance with the terms of this License Agreement. You may terminate the License Agreement at any time by destroying the Licensed Program(s) together with all copies, modifications, and merged portions thereof in any form. This License

2

Preface



Agreement will also terminate upon conditions set forth elsewhere in this Agreement or automatically in the event you fail to comply with any term or condition of this License Agreement. You hereby agree upon such termination to destroy the Licensed Program(s) together with all copies, modifications, and merged portions thereof in any form.

LIMITED WARRANTY The Licensed Program(s), i.e. the tangible proprietary software, is provided “AS IS” WITHOUT WARRANTY OF ANY KIND, EITHER EXPRESSED OR IMPLIED, AND EXPLICITLY EXCLUDING ANY IMPLIED WARRANTIES OF MERCHANTABILITY OR FITNESS FOR A PARTICULAR PURPOSE. The entire risk as to the quality and performance of the Licensed Program(s) is with you. Some jurisdictions do not allow the exclusion of limited warranties, and, in those jurisdictions the above exclusions may not apply. This Limited Warranty gives you specific legal rights, and you may also have other rights which vary from one jurisdiction to another. COADE does not warrant that the functions contained in the Licensed Program(s) will meet your requirements or that the operation of the program will be uninterrupted or error free. COADE does warrant, however, that the CD(s), i.e. the tangible physical medium on which the Licensed Program(s) is furnished, to be free from defects in materials and workmanship under normal use for a period of ninety (90) days from the date of delivery to you as evidenced by a copy of your receipt. COADE warrants that any program errors will be fixed by COADE, at COADE’s expense, as soon as possible after the problem is reported and verified. However, only those customers current on their update/maintenance contracts are eligible to receive the corrected version of the program.

ENTIRE AGREEMENT This written Agreement constitutes the entire agreement between the parties concerning the Licensed Program(s). No agent, distributor, salesman or other person acting or representing themselves to act on behalf of COADE has the authority to modify or supplement the limited warranty contained herein, nor any of the other specific provisions of this Agreement, and no such modifications or supplements shall be effective unless agreed to in writing by an officer of COADE having authority to act on behalf of COADE in this regard.

LIMITATIONS OF REMEDIES COADE’s entire liability and your exclusive remedy shall be: a. the replacement of any CD not meeting COADE’s “Limited Warranty” as defined herein and which is returned to COADE or an authorized COADE dealer with a copy of your receipt, or b. if COADE or the dealer is unable to deliver a replacement CD which is free of defects in materials or workmanship you may terminate this License Agreement by returning the Licensed Program(s) and associated documentation and you will be refunded all monies paid to COADE to acquire the Licensed Program(s).

Preface

3



IN NO EVENT WILL COADE BE LIABLE TO YOU FOR ANY DAMAGES, INCLUDING ANY LOST PROFITS, LOST SAVINGS, AND OTHER INCIDENTAL OR CONSEQUENTIAL DAMAGES ARISING OUT OF THE USE OR INABILITY TO USE THE LICENSED PROGRAM(S) EVEN IF COADE OR AN AUTHORIZED COADE DEALER HAS BEEN ADVISED OF THE POSSIBILITY OF SUCH DAMAGES, OR FOR ANY CLAIM BY ANY OTHER PARTY. SOME JURISDICTIONS DO NOT PERMIT LIMITATION OR EXCLUSION OF LIABILITY FOR INCIDENTAL AND CONSEQUENTIAL DAMAGES SO THAT THE ABOVE LIMITATION AND EXCLUSION MAY NOT APPLY IN THOSE JURISDICTIONS. FURTHERMORE, COADE DOES NOT PURPORT TO DISCLAIM ANY LIABILITY FOR PERSONAL INJURY CAUSED BY DEFECTS IN THE CDS OR OTHER PRODUCTS PROVIDED BY COADE PURSUANT TO THIS LICENSE AGREEMENT.

GENERAL You may not sublicense, assign, or transfer your rights under this License Agreement or the Licensed Program(s) except as expressly provided in this License Agreement. Any attempt otherwise to sublicense, assign or transfer any of the rights, duties or obligations hereunder is void and constitutes a breach of this License Agreement giving COADE the right to terminate as specified herein. This Agreement is governed by the laws of the State of Texas, United States of America. The initial license fee includes 1 year of support, maintenance and enhancements to the program. After the first 1 year term, such updates and support are optional at the then current update fee. Questions concerning this License Agreement, and all notices required herein, shall be made by contacting COADE in writing at COADE, 12777 Jones RD., Ste. 480, Houston, Texas, 77070, or by telephone, 281-890-4566.

DISCLAIMER - PVElite Copyright(c) COADE/Engineering Physics Software, Inc., 2002, all rights reserved. This proprietary software is the property of COADE/Engineering Physics Software, Inc. and is provided to the user pursuant to a COADE/Engineering Physics Software, Inc. program license agreement containing restrictions on its use. It may not be copied or distributed in any form or medium, disclosed to third parties, or used in any manner except as expressly permitted by the COADE/Engineering Physics Software, Inc. program license agreement. THIS SOFTWARE IS PROVIDED “AS IS” WITHOUT WARRANTY OF ANY KIND, EITHER EXPRESSED OR IMPLIED. COADE/ENGINEERING PHYSICS SOFTWARE, INC. SHALL NOT HAVE ANY LIABILITY TO THE USER IN EXCESS OF THE TOTAL AMOUNT PAID TO COADE UNDER THE COADE/ENGINEERING PHYSICS SOFTWARE, INC. LICENSE AGREEMENT FOR THIS SOFTWARE. IN NO EVENT WILL COADE/ENGINEERING PHYSICS SOFTWARE, INC. BE LIABLE TO THE USER FOR ANY LOST PROFITS OR OTHER INCIDENTAL OR CONSEQUENTIAL DAMAGES ARISING OUT OF USE OR INABILITY TO USE THE SOFTWARE EVEN IF COADE/ENGINEERING PHYSICS, INC. HAS BEEN

Preface

4



ADVISED AS TO THE POSSIBILITY OF SUCH DAMAGES. IT IS THE USERS RESPONSIBILITY TO VERIFY THE RESULTS OF THE PROGRAM.

Preface

5

HOOPS‘ License Grant


HOOPS License Grant COADE grants to PVElite Users a non-exclusive license to use the Software Application under the terms stated in this Agreement. PVElite Users agree not to alter, reverse engineer, or disassemble the Software Application. PVElite Users will not copy the Software except: (i) as necessary to install the Software Application onto a computer(s)... or (ii) to create an archival copy. PVElite Users agree that any such copies of the Software Application shall contain the same proprietary notices which appear on and in the Software Application. Title to and ownership of the intellectual property rights associated with the Software Application and any copies remain with COADE and its suppliers. PVElite Users are hereby notified that Tech Soft America, L.L.C. 1301 Marina Village Parkway, Suite 300, Alameda, CA 94501 ("Tech Soft America") is a third-party beneficiary to this Agreement to the extent that this Agreement contains provisions which relate to PVElite Users’ use of the Software Application. Such provisions are made expressly for the benefit of Tech Soft America and are enforceable by Tech Soft America in addition to COADE. In no event shall COADE or its suppliers be liable in any way for indirect, special, or consequential damages of any nature, including without limitation, lost business profits, or liability or injury to third persons, whether foreseeable or not, regardless of whether COADE or its suppliers have been advised of the possibility of such damages.

6

Preface


&KDSWHU ,QWURGXFWLRQ

What is PVElite? PVElite is a PC-based pressure vessel design and analysis software program developed, marketed, and sold by COADE Engineering Software. The PVElite program is a package of nineteen applications for the design and analysis of pressure vessels and heat exchangers. The purpose of the program is to provide the vessel engineer, designer, or estimator with easy-to-use, technically sound, well documented calculations which will speed and simplify the task of vessel design or re-rating. The popularity of PVElite is a reflection of COADE’s expertise in programming and engineering, as well as COADE’s dedication to service and quality.

What is the purpose and scope of the PVElite Program? Calculations in the PVElite program are based on the latest editions of national codes such as the ASME Boiler and Pressure Vessel Code, or industry standards such as the Zick method of analysis for horizontal vessels on saddles. The PVElite program offers exceptional ease of use which results in dramatic improvement in efficiency and comprehension. PVElite features include • • • • • •

•

• • •

Introduction

Graphical User Interface, which lists model data and control with a vessel display. Both horizontal and vertical vessels may be composed of cylinders, conic sections, body flanges and elliptical, torispherical, hemispherical, conical and flat heads. Saddle supports for horizontal vessels. Leg and skirt supports at any location for vertical vessels. Extensive on-line help. Deadweight calculation from vessel details such as nozzles, lugs, rings, trays, insulation, packing and lining. Wall thickness calculations for internal and external pressure in accordance with the rules of ASME Section VIII Division 1 and Division 2, and also BS 5500. Stiffener ring evaluation for external pressure. Wind and seismic data using the American Society of Civil Engineers (ASCE) standard, the Uniform Building Code (UBC), and the National (Canadian) Building Code, and the India Standard. User defined unit system. A complete examination of the vessel’s structural loads combining the effects of pressure, deadweight and live loads in the empty, operating and hydrotest conditions. Logic to automatically increase wall thickness to satisfy requirements for pressure and structural loads and introduce stiffener rings to address external pressure rules.

1-1

What is the purpose and scope of the PVElite Program?

• • • • •

1-2


Structural load evaluation in terms of both tensile and compressive stress ratios (to the allowable limits). Detailed analysis of nozzles, flanges, and base rings. A complete material library for all three design standards. A component library containing pipe diameter and wall thickness, ANSI B16.5 flange pressure vs. temperature charts, and section properties for AISC beams. Printed output from the PVElite program is exceptionally clear and complete, with user definable headings on each page. User comments and additions may be inserted at any point in the output.

Introduction


What distinguishes PVElite from other commercial pres-

What distinguishes PVElite from other commercial pressure vessel packages? COADE treats PVElite more as a service than a product. Our staff of experienced pressure vessel engineers are involved in day-to-day software development, program support, and training. This approach has produced a program which most closely fits today’s requirements of the pressure vessel industry. Data entry is simple and straight forward through annotated input screens and/or spreadsheets. PVElite provides the widest range of modelling and analysis capabilities without becoming too complicated for simple system analysis. Users may tailor their PVElite installation through default setting and customized data bases. Comprehensive input graphics confirms the model construction before the analysis is made. The program’s interactive output processor presents results on the monitor for quick review or sends complete reports to a file or printer. PVElite is an up-to-date package that not only utilizes standard analysis guidelines but also provides the latest recognized opinions for these analyses. PVElite is a field-proven engineering analysis program. It is a widely recognized product with a large customer base and an excellent support and development record. COADE is a strong and stable company where service is a major commitment.

Introduction

1-3

What Applications are Available?


What Applications are Available? The following applications are available in the PVElite Program. General Vessels

Wall thickness design and analysis of any vessel for realistic combinations of pressure, deadweight, nozzle, wind and seismic loads in accordance with ASME Section VIII Division 1 rules, Division 2 rules, and the rules of BS 5500. These calculations address minimum wall thickness for pressure and allowable longitudinal stress (both tension and compression) in the vessel wall for the expected structural load combinations. Complete Vertical Vessels

Vessels supported by either skirts, legs or lugs can be defined for complete dead load and live load analysis. Stacked vessels with liquid are also addressed. Hydrotest conditions may be specified for either vertical or horizontal test positions. Vessel MAWP includes hydrostatic head and ANSI B16.5 flange pressure limitations. Complete Horizontal Vessels

Stress analysis of horizontal drums on saddle supports using the method of L. P. Zick. Results include stresses at the saddles, the midpoint of the vessel, and in the heads. Individual Shells & Heads

Internal and external pressure design of vessels using any of the three design standards. Components include cylinders; conical sections; and elliptical, torispherical, flat, and spherical heads. PVElite calculates required thickness and maximum allowable internal pressure for the given component. It also determines the minimum design metal temperature per UCS-66, and evaluates stiffening rings for external pressure design. Conical Sections

Internal and external pressure analysis of conical sections and stiffening rings. Complete area of reinforcement and moment of inertia calculations for the cone under both internal and external pressure are included. Vessel Nozzles

Required wall thickness and reinforcement per the applicable code (Div. 1 or Div. 2) under internal, and external pressures and under MAPNC conditions for nozzles in shells and heads. The program includes tables of outside diameter and wall thickness for all nominal pipe diameters and schedules. The program also calculates the strength of reinforcement and evaluates failure paths for the nozzle. Flanges

MAWP and MAP are listed for all nozzle flanges. For those flanges requiring stress analysis (e.g. body flanges), complete Appendix 2 stress analysis is provided. PVElite can also design flanges either by increasing the flange thickness or by changing several flange parameters.

1-4

Introduction



Base Rings

Stress and thickness evaluation for tailing lugs, skirts and base rings. Results from both the neutral axis shift and simplified method for basering required thickness are reported. The following pressure vessel components, while unincorporated in the general vessel model, may be modeled and analyzed on an individual basis in PVElite. Lifting Lug

The stresses on legs, supporting lugs, lifting lugs, and their allowable limits can be calculated. Stresses on cap type and continuous top support rings (girder rings) can also be calculated. Trunnion and shell stress as well as baseplate thickness is also computed. Pipe & Pad

Required wall thickness and maximum allowable working pressure for two pipes, and branch reinforcement requirements for the same two pipes considered as a branch and a header. Based on ANSI B31.3 rules, this program includes tables of outside diameter and wall thickness for all nominal pipe diameters and schedules. Local Stress Calculation Due To Attached Loads

Stresses in cylindrical or spherical shells due to loading on an attachment, using the method of P. P. Bijlaard as defined in Welding Research Council Bulletin 107. Thin-Walled Expansion Joints

Stress and life cycle evaluation for thin walled expansion joints in accordance with ASME VIII Div. 1 Appendix 26. Thick-Walled Expansion Joints

Stress, life cycle and spring rate calculations for flanged and flued expansion joints in accordance with ASME VIII Div. 1 Appendix CC. The spring rate computation is per TEMA 8th edition. TEMA Tubesheets

Analysis of all types of tubesheets using the Seventh Edition of the Standards of the Tubular Exchanger Manufacturers Association. The program takes full account of the effects of tubesheets extended as flanges, and for fixed tubesheets also includes the effects of differential thermal expansion and the presence of an expansion joint. ASME Tubesheets

This program determines required thickness of tubesheets for fixed or U-tube exchangers per the ASME Code Section VIII Division 1 Appendix AA. Floating Heads

Internal and external pressure analysis of bolted dished heads (floating heads) using the ASME Code, Section VIII, Division 1 rules. An additional calculations technique allowed by the Code (Soehren’s calculation) is also implemented by this program.

Introduction

1-5



Half-Pipe Jacket

This program determines required thickness and MAWP for half-pipe jacketed vessels per the ASME Code Section VIII Division 1 Appendix EE. Large Openings

This program analyzes large openings in integral flat heads per the ASME Code Section VIII Division 1 Appendix 2 and Appendix 14. Required thickness, MAWP and weights are computed for geometries that have no nozzle or an attached nozzle. Rectangular Vessels

This program analyzes non-circular pressure vessels using the rules of the ASME Code, Section VIII, Division 1, Appendix 13. Most of the vessel types in Appendix 13 are analyzed for internal pressure, including reinforced or stayed rectangular vessels with a diametral staying plate. All membrane and bending stresses are computed and compared to the appropriate allowables. Shells & Heads

Internal and external pressure design of vessels and exchangers using the ASME Code, Section VIII, Division 1 rules. Components include cylinders, conical sections, elliptical heads, torispherical heads, flat heads, and spherical shells and heads. This program calculates required thickness and maximum allowable internal pressure for the given component. It also calculates the minimum design metal temperature per UCS-66, and evaluates stiffening rings for external pressure design. Nozzles

Required wall thickness and reinforcement under internal pressure for nozzles in shells and heads, using the ASME Code, Section VIII, Division 1 rules and including tables of outside diameter and wall thickness for all nominal pipe diameters and schedules. The program also calculates the strength of reinforcement and evaluates failure paths for the nozzle. Flanges

Stress analysis and geometry selection for all types of flanges using the ASME Code, Section VIII, Division 1 rules. This program both designs and analyzes the following types of flanges: • • • • • • •

Weld neck flanges and all integral flange types Slip on flanges and all loose flange types with hubs Ring type flanges and all loose flange types without hubs Blind flanges, both circular and non-circular TEMA channel covers Reverse geometry weld neck flanges Flat faced flanges with full face gaskets

Horizontal Vessels

Stress analysis of horizontal drums on saddle supports using the method of L.P. Zick. Results include stresses at the saddles, the midpoint of the vessel, and in the heads. Stiffening rings used in the design of the vessel are also evaluated. Wind and seismic loadings are

1-6

Introduction



also considered. Additionally, the saddle, webs and baseplate are checked for external seismic and wind loads. Legs & Lugs

Analysis of vessel support legs, support lugs, and lifting lugs. This analysis is based on industry standard calculation techniques, and the resulting stresses are compared to the AISC Handbook of Steel Construction or the ASME Code. A full table of 929 AISC beams, channels and angles is included in the program. WRC 107

Stresses in cylindrical or spherical shells due to loading on an attachment, using the method of P.P. Bijlaard as defined in Welding Research Council Bulletin 107, including a stress comparison to VIII div. 2 allowables for 3 different loading conditions. An FEA interface to PRG’s NOZPRO is also included. Summary

Description and evaluation of all the components of a pressure vessel or heat exchanger. Design pressure, temperature, material, actual thickness, and Maximum Allowable Working Pressure are shown for each component. WRC 297

Stresses in cylindrical shells and nozzles due to external loading, per Welding Research Council Bulletin 297 and PD5500 Annex G. Appendix Y Flanges

Required thickness and MAWP for Class 1 flanges with metal to metal contact outside the bolt circle per Appendix Y.

Introduction

1-7

About the PVElite Documentation


About the PVElite Documentation Chapter 2 gives you information on the hardware and software required to run the PVElite program, instructions on how to install the program, and how to prepare your computer to run the program. Chapter 3 tells you how to get the PVElite program started on your computer. Use Chapter 3 to learn the structure of the program, and the keystrokes needed to make it work. Each of the applications operates the same way, so you will only need to learn these skills one time. Chapter 4 discusses the PVElite element input data for each basic element and the vessel details added to these elements is explained in Chapter 5. Chapter 6 describes the general vessel input data. Chapter 7 discusses the Anaylze options of PVElite while Chapter 8 contains information needed to review or generate output for the job. This chapter also focuses on the capabilities of the review processor. Chapter 9 contains a complete step-by-step tutorial which leads you through the use of one application of the PVElite Component Analysis Module. Chapter 10 gives a more detailed description of several features associated with the spreadsheet input program - merging shell data, selecting materials, editing materials properties, and inserting or deleting analyses. Chapters 10 through 28 contain the technical descriptions for each of the PVElite module applications. The information provided for each application includes: • • • •

The purpose and scope of the application and its technical basis Notes on the input to the program and results of the program A figure showing the relevant geometry One or more example problems

Chapter 29 describes the miscellaneous processors included in PVElite. Finally, Chapter 30 provides a listing for typical vertical and horizontal vessels along with complete example problems.

1-8

Introduction


Program Support / User Assistance

Program Support / User Assistance COADE’s staff understands that PVElite is not only a complex analysis tool but also, at times, an elaborate process—one that may not be obvious to the casual user. While our documentation is intended to address the questions raised regarding piping analysis, system modeling, and results interpretation, not all the answers can be quickly found in these volumes. COADE understands the engineer’s need to produce efficient, economical, and expeditious designs. To that end, COADE has a staff of helpful professionals ready to address any PVElite issues raised by all users. PVElite support is available by telephone, fax, the Internet, discussion board, and by mail; literally hundreds of support calls are answered every week. COADE provides this service at no additional charge to the user. It is expected, however, that questions focus on the current version of the program. Formal training in PVElite and pressure vessel analysis is also available from COADE. COADE conducts regular training classes in Houston and provides in-house and open attendance courses around the world. These courses focus on the expertise available at COADE—modeling, analysis, and design. COADE Technical Support Phone Numbers

Introduction

Phone: 281-890-4566

E-mail: [email protected]

Fax:

WEB: www.coade.com

281-890-3301

1-9

Updates


Updates PVElite update sets are identified by their version number. The current release of PVElite is Version 4.2.

Licenses There are 3 types of PVElite licenses: Full Run

Provides unlimited access to PVElite and one year of updates, maintenance, and support. Updates, maintenance, and support are available on an annual basis after the first year. Lease

Provides unlimited access to PVElite with updates, maintenance, and support provided as long as the lease is in effect. Limited Run

Provides 50 analyses over an unlimited period of time, but does not include program updates. The user is upgraded (if necessary) whenever a new set of 50 “runs” is purchased. A run is decremented when the “Analyze” Option is selected from the menu bar and the “Analyze” submenu item is selected.

1-10

Introduction


Summary of Version 3.5 Improvements

Summary of Version 3.5 Improvements • • • • • •

Code Case 2260 Code Case 2261 Thick-walled equations from App. 1 WRC 297 added Appendix Y calculations added Microsoft Word output report generation

Summary of Version 3.6 Improvements • • • • • • • • • • • • • • • •

A-99 addenda changes have been incorporated, including the higher allowable stresses for Div. 1 The pre 99 addenda is available as an option (uses the 98 addenda material database, etc.) Other FVC nozzles such as types F, V1, V2, and V3 are now included (with or with nut relief) Nozzle calculations in ANSI blind flanges can now be performed (full area replacement) An ANSI flange dimension lookup feature has been added Required flange thickness calculations based on Rigidity considerations are included A saddle copy feature has been incorporated The program’s documentation is now available on-line in PDF format Several enhancements to the user interface have been made Dimensional Solutions Foundation 3-D interface has been added MAWP and MAPnc can now be manually defined The 3/32 min. thickness requirement based on the Service type (Unfired Steam) is accounted for The Maximum hydrotest pressure is computed in the case of overstressed geometries The ESL will automatically be updated for current users (obviating the need for the phone call) An option for the pneumatic hydrotest type has been added The material database editor can select materials from the database for editing purposes

PV Elite Component Analysis New Features • • • • • • • •

Introduction

A-99 addenda changes have been incorporated, including the higher allowable stresses for Div. 1 The pre 99 addenda is available as an option (uses the 98 addenda material database, etc.) Required flange thickness calculations based on Rigidity considerations TEMA Eighth edition changes are included Code Case 2260 has been added The CodeCalc User interface has been re-written and now has lower memory requirements The material database editor can select materials from the database for editing purposes Thick Walled Cylinder and Sphere equations are implemented per Appendix 1

1-11

Summary of PVElite Version 4.00 Improvements


Summary of PVElite Version 4.00 Improvements • • • • • • • • • • •

An option for a user defined hydrotest pressure has been added A provision for a corroded hydrotest has been added An interactive 3D graphical viewer has been added Local Stress calculations per BS-5500 Appendix G for Nozzles on Spheres and Cylinders has been added PV Elite now creates a Data Interchange File (DXF), Nozzle Summary and Bill of Material An interface to Paulin Research Group’s Nozpro Finite Element Analysis program has been added The flange input now accepts different M and Y factors for the partition Gasket The nozzle input has been expanded to accept an alternate Angle and Manway specification as well as tapped hole area loss The UBC 97 Earthquake Code has an alternate provision to use higher allowables Some additional Basering Design Parameters have also been included UCS-79 Fiber Elongation Calculations are now reported

Summary of Version 4.1 Improvements • • • • • • • • • • • •

1-12

ASME 2000 addenda has been incorporated Provision to use the 99 year material database TEMA and ASME tubesheet programs updated to perform multiple load cases Separate entry of m and y factors for partition gaskets User bolt loads in the tubesheet programs Simultaneous Corroded and UnCorroded thick expansion joint calculations ASCE 98 wind code added Rigging analysis with graphical results processor added The input (thicknesses, rings, and repads) can now be updated by the analysis program The 3- D viewer now has a transparency option Ladder information is now collected User time history input for IS-893 RSM

Introduction


Summary of Version 4.2 Improvements

Summary of Version 4.2 Improvements • • • • • • • •

• • • • • • • • • • • • • • • • • • • • • • • • • • •

Introduction

Computation of Slen (allowable length between stiffeners) displays on the status bar Computation of Tr for external pressure displays on the Status bar Computation of EMAWP for heads displays on the Status bar Computation of Areas (Required and Available) in the Nozzle dialog Computation of Inertias (Required and Available) in the Stiffener Ring dialog Inputs for Type and Material of Construction for Nozzle flanges Nozzles on heads are now listed allowing the ability to copy and paste nozzles between heads (cut and paste) The program will automatically design a ring on entry in to the Ring dialog once the minimum parameters are entered in or if the ring OD is zeroed out and you tab around the data fields A standard Bar Ring Selection table is now available Minimum leg size is calculated if the leg selected fails the AISC Unity Check Minimum thickness of Gusset plates, bottom, and top lug plates are now shown Minimum size of Cone/Shell junction rings are computed if the selected ring fails on area or inertia The Liquid dialog was reworked to allow entry of Specific Gravity and Distance of Liquid from datum line A group of Stiffening Rings can be added at one time ANSI Flange MAWP displays on the Status bar FVC Studding Outlets added to the FVC database WRC 107 Calcs performed for Legs and Lugs automatically Percent Liquid Holdup and SP specification added to Packing dialog Y forces now add/subtract to axial stress for cases with FW or FS added to them Nozzle Flange Rating displays on the Status bar Pressing the F5 key in Nozzle, Ring, and Flange dialog acts as a Refresh (recalc) Key Added offset dimension in the Weight dialog Flange Calcs are now available from the Flange dialog Added 48 character element descriptions for each element From Nodes now display on the printout of the sketch input Diameter and length dimensions now display on the sketch Option to print a sketch in color Several default values can be set such as pressure, temperature, thickness, material, etc. Computed Cone Half Apex angle now displays on the Status bar Option to vary the temperature used to determine the compressive allowables for load cases involving internal and external pressure Overall MDMT now reported in the Vessel Summary report Required Blind Flange Thickness at the Gasket location now computed A search facility in the Material Database is now included The 3D graphics were updated to include showing elevations, element names and weights Added Flange MDMT calculations

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PV Elite Component Analysis New Features Version 4.2


PV Elite Component Analysis New Features Version 4.2 • • • • • • • • • •

Added Trunnion analysis and WRC analysis capability Added Baseplate design for vessel legs Added capability to display Nozzle results on the Status bar Added capability to display Shell and Flange results on the Status bar Added advanced search capabilities to the Material Database Improved the look up into the Yield Stress database Added Flange MDMT calculations Improved the Flange Summary Added the capability to print the allowable stress for spherical vessels Improved the file saving logic for modified and/or unmodified files

Summary of Version 4.3 Improvements • • • • • • • • • •

Added Tailing Lug analysis Added Leg Baseplate analysis Rectangular top head platform and ladder cases are addressed Added IBC 200 Earthquake Code Added PD:5500 Annex F nozzle calculations Added Dynamic Response Spectrum Earthquake analysis including guidelines per ASCE -98 and IBC 2000 Updated ASME 2001 Code Added new Natural Frequency Solver Updated 3D Graphics Improved 2D Graphics

PV Elite Component Analysis New Features Version 4.3 • • • • • • • • • •

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Updated ASME 2001 Code Added Div 1 and Div 2 to WRC107 Module Added Split screen Graphics Added Static Head to Nozzle calcs Added Pneumatic Hydrotest calculation Added Tailing Lug calculations Simplified nozzle input for non-radial nozzles Improved Summary capability Added Thick Shell band for ASME Tubesheets Improved Online Registration

Introduction


&KDSWHU Overview of the Installation/ Configuration Process The PVElite program is installed on the system hard disk using the program setup located on the CD. This installation program has been designed to allow total or partial installations, diagnostic checks of the installation, multi-language support, and ease of updating. This section will explain the process of running the PVElite setup application. For users upgrading to a new version of PVElite, the installation program can be instructed to place the new files in the same directory where the current version resides. The new version files will overwrite the old version files where appropriate. The PVElite program can be run from anywhere on the system hard disk. It is recommended that job files be kept in one or more data or project directories separate from the PVElite installation directory. The installation process consists of the following steps:

1. Copying files from the CD to the hard disk. 2. 3. 4. 5.

Extraction of the PVElite program from these compressed files. Verification of the extracted files. Installation of the External Software Lock drivers Configuring the PVElite program.

System and Hardware Requirements The specific system resources necessary to run PVElite are listed below: • • • • •

Intel Pentium processor (or equivalent) Microsoft Windows (95/98/2000, NT 4.0, XP, or higher) Operating System 32 Mbytes RAM (recommended) 70 Mbytes of disk space CD-ROM Drive

Note

PVElite is designed for 800x600 resolution (using small fonts) or 1024x768 resolution (using large fonts).

External Software Lock The External Software Lock (ESL) is the security protection method employed by COADE. The PVElite program cannot execute unless an appropriate ESL (green or white) is attached to the PC locally, or to another computer in the network (red ESL).

Overview of the Installation/Configuration Process

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Starting the Installation Procedure


The ESL can be easily attached to the parallel port of the computer in a matter of seconds. The printer cable should then be attached to the other side of the ESL. The essential requirement for the successful operation of the ESL is that the port must be a Centronics compatible DB-25 pin parallel port. This is the IBM PC standard read/write printer port. The ESL contains the PVElite licensing data, and other client-specific information. This information includes the client company name and user ID number. Additional data may be stored on the ESL depending on the specific program and the specific client.

Starting the Installation Procedure Insert the CD into the CD-ROM drive. The installation program should start up automatically. If so, the user is invited to skip to the section entitled “Installing PVElite”. If not, it may be started manually using the following procedure. Select the Windows Desktop Start button, select Settings, then Control Panel (see below).

Opening Control Panel

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From the Control Panel select Add/Remove Programs.

Control Panel

This brings up the Add/Remove Programs dialog box. Click on the Install button to start the installation process.

Add/Remove Programs Dialog

The next screen prompts the user for the folder in which PVElite is to be installed. This folder may be entered by selecting the Browse button. The folder may be the current location of an existing PVElite installation, or a new location.


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This starts the installation process by prompting you to place the CD in the CD-ROM drive and clicking on the Next button. The Add/Remove Programs application searches for the SETUP.EXE file located on the CD and prompts the user for verification of the file to be installed. Clicking the Finish button runs the PVElite setup program. Installing PVElite

The PVElite installation routine is easily navigable by responding to on-screen prompts and then clicking the Next button. After an opening screen, the user must enter the Serial Number provided with the CD. This serial number should be kept in a safe place for future installations.

Entering the PVElite Serial Number

Note

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The serial number is located on the sticker that is attached to the CD. Do not discard the jewel case!




The next screen prompts the user for the folder in which PVElite is to be installed. This folder may be entered by selecting the Browse button. The folder may be the current location of an existing PVElite installation or a new location.

PVElite Destination Folder

Next the install routine prompts for the type of installation, with a “Full Install” being the default choice and recommended for most users.

Type of PVElite Installation


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The program then prompts for the folder in which to add the program icons.

Icon Folder Selection

The user then specifies the color of the ESL being used. This ensures that the correct drivers get loaded during the installation.

ESL Selection

Note

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After loading the ESL drivers, the computer will have to be rebooted in order for them to become operative.



Network Installation / Usage

Network Installation / Usage COADE products can be run on network file servers as easily as on stand alone workstations. There are two different installation configurations which must be considered. COADE software supports three different ESLs from two different manufacturers. Two of these devices are intended for “local” usage, and are green or white in color. The third device is the “network” ESL, and is red in color. Do not attempt to put a “local” ESL on a network server - the system will usually crash. Software Installation on a Network Drive

The Setup program treats a network drive no different than a local hard drive. Simply specify the target installation drive and directory and the software will be copied and expanded accordingly. Some networks protect installation directories from subsequent modification by users. This involves setting the access rights in the installation directory to usually “read,” “share,” and “scan.” Since COADE software utilizes data files specific to the installation (i.e., accounting, files, material files, etc....) which a user may need to modify, these files cannot be located in the “protected” installation directory. These data files are located in a sub-directory named SYSTEM, underneath the installation directory. Users should be given all access rights to this SYSTEM directory. While the actual name of the program’s installation directory can be specified by the person installing the software, the SYSTEM sub-directory name is fixed, and is automatically created. Renaming this sub-directory will cause the software to fail and generate an error report.

Note

The SYSTEM subdirectory is not the primary top level SYSTEM directory containing the network operating system.

Once the software has been installed on the network drive, the installation program invokes the configuration program which generates a default configuration file. Once the installation directory is write protected this file cannot be modified. Leaving this file as read only would insure the configuration file can then only be used as a starting template to generate other configuration files located in the various user data directories.

ESL Installation on a Network COADE software programs support two different ESLs, “local” ESLs and “network” ESLs. Both types of ESLs are intended to be attached to the parallel ports of the applicable computers. The local ESLs provide the maximum flexibility in using the software, since these devices can be moved between computers (i.e., between desktops and laptops). If your computer uses a local ESL, the remainder of this section can be skipped. The network ESL must be attached to the parallel port of any machine on the network (this can be a workstation or the file server). The file server is a better location for this ESL, since it will usually be up and running. If the network ESL is attached to a workstation, the workstation must be running and/or logged onto the network before anyone can use the software. In order for the network to recognize the ESL, a utility program must be loaded on the machine controlling the ESL. The actual utility used depends on whether the ESL is on the file server or a workstation and the type of network. The drivers for network ESL usage


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Notes on Network ESLs


can be found in the subdirectory ASSIDRV beneath the PVElite program directory. The documentation files in this subdirectory contain instructions for a variety of networks and operating systems.

Note

Whenever a new version of PVElite is installed in a network environment the new ESL drivers must be installed on the machine where the red key resides.

Novell File Server ESL Installation

If the network ESL is to be located on a Novell file server, the driver HASPSERV.NLM is needed. This driver should be copied onto the file server, into the top level SYSTEM directory. Then, the system startup file (AUTOEXEC.NCF) should be modified to include the command:

LOAD HASPSERV This modification can be accomplished with SYSCON (or equivalent) assuming Supervisor rights. Novell Workstation ESL Installation

If the network ESL is to be located on a workstation, the driver HASPSERV.EXE is needed. This driver should be copied onto the workstation. The actual location (directory) on the workstation is not important, as long as the program can be located for startup. Place the command:

HASPSERV in the AUTOEXEC.BAT file of the workstation, after the commands which load the network drivers. The workstation does not need to be logged in. Note however, the workstation must always be up and running for users to access the software. Windows Server Installation

For a Windows server installation, please refer to the documentation files NETHASP.TXT and ESL_RED.TXT found in the ASSIDRV subdirectory for network specific instructions.

Notes on Network ESLs There are advantages and disadvantages in utilizing a network ESL. The prime advantage is that many users (up to the number of licenses) have access (from a variety of computers) to the software on a single server. The prime disadvantage is that users cannot transfer the ESL between machines in order to take PVElite home or to another remote location. Since both a network and several local ESLs may be initialized on the same system (there is no network specific version of the software), it is suggested that only 70 to 80 percent of the desired licenses be assigned to a network ESL. The remaining 20 to 30 percent of the licenses should be assigned to local ESLs. This enables the local ESLs to be moved between computers, to run the software at remote locations. Alternatively, if all of the

2-8




licenses are on the ESL, a user must then be logged into the network to access the software. A few local ESLs provide much greater operating flexibility.

Note

The number of licenses assigned to a network ESL is not a parameter that can be modified remotely by COADE software.

Local users running the software from a network drive should run the file "Netuser.bct" one time to update all locations.


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&KDSWHU Tutorial / Master Menu

Program Structure and Control The basic PVElite hard disk configuration would be structured as follows: •

PVELITE:

Directory holding PVElite program

•

Project #1:

Data files for Project #1

•

Project #2:

Data files for Project #2

•

SYSTEM:

Program database & control files

•

EXAMPLES:

Sample input files

Most files in the data subdirectories are identified by a user-defined filename with a given extension. The remaining files hold data controlling the program’s operation. These files and their description follow: •

jobname.PVI

PVElite input file

•

jobname.TAB

temporary results file

•

jobname.T80

results file used by the output review processor

•

jobname.CCI

input file for component analysis

•

units.FIL

User units file (relating user’s units and program units)

•

*.BIN

PVElite Material Database

•

UMAT1.BIN

Binary file holding the user-defined materials

Tutorial / Master Menu

3-1

A Road Map for PVElite


A Road Map for PVElite There are many PVElite functions that are not addressed here. This section focuses on the structure and control of the fundamental units of the program - input, analysis, and output. By understanding these basic concepts, a firm foundation for understanding PVElite is assured. Input, analysis, output; it is as simple as that. Input - collect information required to define the vessel, its service requirements and its design guidelines. Analysis - translate the user’s input into appropriate data for the design and analysis algorithms, correctly apply the rules of appropriate code or standard and generate results. Output - present those results with explanation in a way that the final report is comprehensive and meaningful.

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The Input Processor

The Input Processor To define the data necessary for the analysis, the vessel is broken down into its basic elements—heads, shells, cones, etc. A quick look at the default PVElite input screen (below) shows the data which defines the element. Except for the “From Node” and “To Node”, these data are common to all vessel wall thickness calculations. The From and To Nodes are necessary to assemble the individual elements into the complete vessel and are automatically assigned by PVElite. A complete vessel is required if all dead and live loads are to be included in the design or analysis. Yet PVElite will run wall thickness calculations on elements without constructing the entire vessel.

PVElite Completed Input Screen

PVElite is a Windows package and exploits the advantages of the Graphical User Interface or GUI. Looking at the input screen above, no direct path through the processor is evident; control can jump to many other points in the program. This style of control is called an event driven, graphic environment. This screen has a Main Menu across the top which controls the major routing through the processor. These items — File, Input, Analyze, Output, Tools, etc. — may be accessed directly from this menu at any point in the processor. In a row directly below the Main Menu appears a series of toolbars and buttons specific to the current screen. In the screen above, the buttons manipulate the elements (Insert, Delete, Update), specify unique data (Material, Share), or change the view or input method (Zoom, Layout view). The three toolbars control the data file, add elements and add details to the current element. These toolbars and buttons may be relocated on the screen. The body of the screen contains either two or three areas - a table of the Element Basic Data, a table of the Element Additional Data (when required), and the graphic area which contains an image of the current status of the entire vessel or the current element. A status bar runs across the bottom of the screen. The status bar displays an element count, the


3-3

The Input Processor


position and orientation of the current element, and quick internal pressure calculations for the current element. How are the menu selections made, how are the buttons pushed, how is the data entered? Most operations are obvious when using a mouse; simply point to the item and click the left mouse button1 to open drop down menus from the menu line, activate the button commands, pick a tool or move control to one of the screen areas. All buttons and toolbars have fly-out definitions which are activated when the mouse rests on the button. When a mouse click occurs in the data area(s), the Tab key moves the highlight (and control) through its input cells. In most element data areas, the Enter key has no function; it is the tab key which moves the cursor to the next input cell. The exception is at “combo boxes”2 where a click on the arrow will display the available choices and a down arrow will step through the choices. An example of the combo box is found on the Input screen shown above where the element is chosen from a list of available types. Throughout the program, the [F1] key shows the help screen for the highlighted data item. Once familiar with these screen controls, a combination of mouse and keystroke commands will provide the most efficient navigation through the program.

Note

The right mouse button is used to select vessel details on the vessel graphic.

Note

Combo boxes have the down arrow button at the right end of the input cell.

Main Menu Toolbars and Buttons (Default)

“Element Basic Data” Area

Graphic Display Area

“Element Additional Data” Area (If required)

Status Bar

Layout of the Input Screen

When the graphics area of the Input screen is active a few more keys are available. No special highlight will appear but the string “PgUp/PgDn/Home/End” will appear at the bottom graphics area. This indicates these keys are now active. The image in the graphics

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The Input Processor

area shows the current state of the input for the vessel model with its elements and the details on these elements. One element is highlighted. This is the current element and the element data (Element Basic Data and Element Additional Data) shown on the screen defines this element. By pressing PgUp or PgDn, the highlight changes from one element to the next through the vessel. Home and End keys are pressed to move the highlight to the first and last elements in the vessel. Clicking the left mouse button on the element will also highlight it. Once an element is highlighted the detail information for that element may be accessed. With the mouse, simply click the right mouse button for the existing detail image to be displayed. To add details to the current element, simply click on the appropriate detail on the toolbar and provide the necessary data.

Detail Pop-up Screen

Once the control of this screen is understood, all the remaining input processors will present no difficulties as they all have the same control structure with mouse and keyboard commands.


3-5

Other Input Processors


Other Input Processors The other menu items listed under input indicate the other types of data that may be necessary for the analysis.

Input Menu

Enter Vessel Data

Other than the Vessel Data there are four other categories of vessel input which must be addressed - component analysis data, report headings, the guidelines for the vessel design or analysis, and a definition of the live (wind and seismic) loads. These input processors are entered through Input on the Main Menu. The drop down menu here can be used to switch between the Build and Define mode and also enter the Heading definition and the Global processor. The Design/Analysis Constraints are important here as this is where the overall analysis for this vessel is defined and controlled. Finished thickness is required input for each vessel element but the user may allow the program to increase element thickness so that each element passes the requirements for internal pressure, external pressure, and the combined loads of pressure, dead and live loads. Remember that the status bar lists internal pressure information about the current element including the required thickness. A switch is also available to locate stiffener rings on the vessel to satisfy the external pressure requirements. The Component Analysis Data option allows the user to enter data and analyze without building a vessel. These are COADE’s remaining CodeCalc analysis modules some of which cannot be incorporated directly in PVElite. CodeCalc, COADE’s popular vessel component analysis package is included in PVElite.

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Component Analysis Data screen:

Component Analysis Processor

Report Headings

Report Headings screen:


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Design / Analysis Constraints screen:

Design/ Analysis Constraints

Live Load Data screen: Enter Live Load Data

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Error Checking

Error Checking The input processor makes many data consistency checks during the input session. For example, the processor will create an error message if the user tries to specify a nozzle 20 feet from the bottom of a 10 foot shell element. Not all pieces of data can be confirmed on input. For that reason, a general error processor is executed prior to the analysis. This error processor can be run in a stand-alone mode as well. The error checker may be accessed from the pull down menu under Analyze. In addition to the notes that are presented on the screen during error checking, these error messages also appear in the output report accessible through the output review processor.


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Analysis


Analysis PVElite can be used to confirm a safe design for a proposed or existing vessel. The program also provides direct design capabilities in which the wall thickness of individual elements are increased to meet the code requirements for internal and external pressure and longitudinal stress from a variety of dead and live loads. Whether or not the program changes wall thickness during the analysis is controlled through a Design/Analysis Constraint specification under Design Modification. (See Design/Analysis Constraints screen above). A simple analysis run (no design) occurs when the flags for “Select t for ...” are all unchecked. If any of these boxes are checked, the program will automatically step up the wall thickness until the constraint is satisfied. The user’s input in the resulting output report is automatically updated to reflect any changes made during the analysis. In addition to wall thickness, a fourth flag can be set - “Set Stiffener Rings?”. In this case, rather than increasing the wall thickness, stiffener rings are located along the vessel to satisfy the external pressure requirements. As with the wall thickness changes, these stiffener rings are added to the model input for this analysis. PVElite will analyze each element to determine the required wall thickness for internal and external pressure based on the Section VIII Division 1 rules, Division 2 rules or PD:5500 rules. The program then calculates the longitudinal stresses in the wall due to four categories of vessel loads: pressure, deadweight, deadweight moments from vessel attachments or applied loads, and moments due to the live loads - wind and earthquake. These four categories are set for three different load conditions: empty, operating, and hydrotest. The sensible combination of these various categories and conditions produce the default set of 12 load cases that are found in the Design/Analysis Contraints processor. For each load case, PVElite will calculate the maximum longitudinal stress around the circumference of the elements and compare these values to the allowable stress for the material, both tensile and compressive. If stresses in the vessel wall exceed the design limits, PVElite will proceed according to the design modification settings in the input. Once the program finishes a pass through the analysis, a check is made for any program design modifications. If any data was changed by the program, PVElite automatically reruns the complete analysis to review the impact of the changes. There are several additional analysis controls that should be reviewed here. These controls, however, are more general in nature and are not defined for the individual job. Instead, these seven computational control directives are set for all jobs executed in the Data subdirectory. These controls are viewed and modified through the Tools item on the Main Menu. Here, select Configuration to display the setup parameters dialogue.

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Tools Menu

Tools Menu

Setup Parameters and DXF Options screens:


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Output Review & Report Generation


Output Review & Report Generation Output is stored in a binary file having the same name as the input file but with the extension of “.T80”. Once the output file is created, it can be examined through the Review item under the Output option from the Main Menu. Each analysis module creates its own report in the output file. The reports of interest are selected with the mouse and can be sent to the screen, a printer or a file. Most of the reports take the form of tables with the rows related to the elements and the columns holding the values such as thickness, MAWP, and stress.

PVElite Output Review Screen

Following is a list of some reports available from PVElite: Step 0 Cover Title Step 1 Step 2 Step 3 Step 4 Step 5 Step 6 Step 7 Step 8 Step 9 Step 10 Step 11 Step 12 Step 13 Step 14 Step 15 Step 16 Step 17 Step 18 Cone 1-N Nozl 1-N Step 21 3-12

Vessel Element Error Checking Cover Sheet Title Page Vessel Input Echo XY Coordinate Calculations Internal Pressure Calculations External Pressure Calculations Weight of Elements & Details ANSI Flange MAWP Natural Frequency Calculations Forces & Moments Applied to Vessel Wind Load Calculation Earthquake Load Calculation Wind and Earthquake Shear, Bending Wind Deflection Longitudinal Stress Constants Longitudinal Allowable Stresses Longitudinal Stresses Due to Load Components Stress Due to Combined Loads Basering Calculations Center of Gravity Calculation Conical Sections Nozzle Calculations Nozzle Summary Tutorial / Master Menu


Output Review & Report Generation

Screen Display for the Internal Pressure Report:


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Design and Analysis of Vessel Details


Design and Analysis of Vessel Details At this point in the analysis the vessel details have been defined only so that their weights could be included in vessel calculations. With the structural analysis of the vessel complete and the wall thickness set, vessel details can be evaluated. To access the Input Processor for these vessel details, use the pulldown menu under Input and Select Component Analysis Data. This will bring up the processor from which the component is selected and defined. Component Selection Screen from the Component Pulldown menu:

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Design and Analysis of Vessel Details

WRC 107 Input Screen (by clicking on WRC 107 in Component Pulldown Menu):

WRC 107 On-screen Results:


3-15

Main Menu


Main Menu PVElite always starts with the Vessel Data Input Screen. Across the top of this screen is a line of items which is called the Main Menu. The Main Menu controls the major functions of the program. This chapter reviews the functions available in each of these menu items. The PVElite Vessel Data screen has the following structure: Main Menu Toolbars and Buttons (Default)

“Element Basic Data” Area

Graphic Display Area

“Element Additional Data” Area (If required)

Status Bar

The items in the Main Menu, File, Input, Analyze, Output, Tools, Diagnostics, View, ESL, and Help, may be selected with a mouse click or by pressing the underlined character while pressing the [Alt] key. For example, the Output processor may be selected by pressing [Alt]+ [O].

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File Menu

File Menu

File Menu

The File options control the general operations of PVElite files. Options that are displayed in the menu with an ellipsis (…) cause a file manage window to appear when selected. The file manager is described in the chapter titled Miscellaneous Processors. The following options are available from the Main Menu item - File: New

•

New - Starts a new file.

File New Dialog


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File Menu


•

Open—Opens a previously created file.

Open

File Open Dialog

Save

•

Save—Causes the current file to be saved in its present condition.

Save Dialog

Print

3-18

•

Save As—Allows the user to either save a file that has not been named or to save the current file under another name.

•

Print—Sends the current vessel graphic image directly to a printer.

•

Print Preview—Displays the page that will be sent to the printer (see above)

•

Print Setup—Brings up the standard Windows printer setup screen.

•

Exit—Allows the user to exit PVElite. A message window will appear to give the user a last opportunity to save any modification to the current job.

•

Export •

Dump Graphics to PCX...—Rather than sending the vessel image directly to the printer, the image may be stored in a standard PCX format file. This file can be printed at a later time or added to other documents. The name of the created PCX file will default to the name of the current job with the extension of PCX, e.g. JOBNAME.PCX.

•

Dump Screen to PCX...—As with “Dump Graphics to PCX File...,” this option will build a PCX file for later manipulation and printing. In this case, the entire contents of the screen are saved in the file. Tutorial / Master Menu


File Menu

•

Vessel Geometry to R12 DXF file

The File Menu will also list the last four vessel input files. Any of these files may be opened with a mouse click.


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Input Menu


Input Menu

Input Menu

The Input options controls the general operations of PVElite program input processes. The following options are available: Enter Vessel Data

Component Analysis Processor Report Headings

Design/ Analysis Constraints

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•

Vessel Data—This is the main input processor of the program, which allows the user to input and edit the element data (shell, heads, body flange, skirt and cone) and the detail data (saddle, platform, packing, liquid, insulation, lining, ring, nozzle, tray, leg, lug, weight, force and moment). Also in this option the user can add, delete, insert elements and details. The user can click on an element’s graphic field to bring this element’s data to the screen for further editing. The user can right click on an element for further editing. The ‘Individual Detail’ button on the Detail toolbar also allows the user to edit the detail data. This processor is discussed later in this section. See the Element Data and the Detail Data chapters for more information.

•

Component Analysis Data—This option includes those (CodeCalc) processors which are not integrated into the main vessel analysis. These processors are described in Chapters 9 thorough 28.

•

Report Headings—This option allows the user to input and edit a three line heading, which will be placed in the first three lines of each report page. It will also print on the title page, which will be the first page of the report.

•

Design/Analysis Constraints—This option allows the user to input and edit the global data, which includes the general vessel description, design control data, and the structural load analyses to be performed. This is where ASME Section VIII Division 1,



Input Menu

Division 2, or PD:5500 is specified as the design code. If the user does not select this option, the program will set the default data.

Enter Live Load Data

Design/Analysis Constraints Dialog

•

Live Load Data—This option switches to the wind and seismic data edit mode where the wind loads and seismic loads are defined through the specification of the appropriate load parameters.

Live Load Data Dialog


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Analyze Menu


Analyze Menu

Analyze Menu

The Analyze options cause program to quit the input process and enter the analysis process. PVElite will first save the current job to the input file with the same filename, then process the analysis. The following options are available:

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•

Analyze—This option quits the input process and begins the error checking process. After finishing the error checking, if no error is detected, the program will implement the analysis process. A description of the PVElite analysis is found in Chapter 7 of this user’s guide. The output from the analysis processor, whether error messages or results, may be examined by the Review function in Output. Once an analysis is completed, the program will automatically switch to the Review processor.

•

Error Check Only—This option will only process the error checking, and will not implement the analysis process. The error report may be examined in the Review option found in the Output item from this Main Menu.



Output Menu

Output Menu

Output Menu

The Output options allow the user to review the analysis results, and print the graphics of the vessel. The following options are available under Output: •

Review—This option allows the user to review the analysis results of the current job, if these results are already available.

•

Review the DXF file.


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Tools Menu


Tools Menu

Tools Menu

The Tools options control utility processors. Options that are displayed in the menu with ‘...’ cause a window to appear when selected. The configuration option allows the user to define a variety of system variables for the program:

Configuration Menu

The Configuration Option lets some specific program computation control parameters be set. These controls let you set some options in some programs that control the results of some computations. Following is a description of the options: Print Water Volume in Gallons?

Normally the volumes computed by the program are in diameter units. If you want to use US gallons instead of cubic diameter units check this directive. The program will use cubic units if the default value if it is not checked.

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Tools Menu

Use AD-540.2 sketch b and not sketch d for normal?

This setup parameter is used for the computation of the vertical thickness limit. The formulas for computing these limits are found in paragraph AD-540.2 of the ASME Code Section VIII Division 2. Sketch (b) of Fig. Ad-540.1 shows an integral connection with a smooth radius. Figure (d) shows a similar geometry with an alternative pad plate and fillet. By default PVElite uses sketch (d) to compute the vertical thickness limit. However if you would like to use sketch (b) then check this directive. Round Thickness to Nearest Nominal Size?

If you would like to have your thicknesses rounded to the nearest 1/16 of an inch (if you are in English units) or the nearest 1mm if you are in MM units, then check this directive. The program will increase the thickness of an element if you specify for it to do so in the Design/Analysis Constraints and the element thickness is inadequate. If this directive is not checked then no thickness rounding will be performed. Compute Increased Nozzle Thickness?

In many cases pressure vessels are designed and built long before the piping system is attached to them. This means that the nozzle loadings are unknown. If this field is checked, then your minimum nozzle thickness (trn) will be the maximum of: trn = max (.134, trn for internal pressure ) <=Nps 18 trn = max (OD/150, trn for internal pressure) > Nps 18 By using such a requirement in addition to UG-45, the piping designers will have some additional metal to work with to satisfy thermal bending stresses in systems these vessels are designed for. Note carefully, that these formulae are not in the ASME Code. They are used in industry. You can also specify the minimum wall thickness of the nozzle (Trn) in the Nozzle input. If you do so, that will override this calculation. Compute and Print Areas for Small Nozzles?

The Code paragraph UG-36 discusses the requirement of performing area replacement calculations when small nozzles are involved. The Code states: Openings in vessels not subject to rapid fluctuations in pressure do not require reinforcement other than that inherent in the construction under the following conditions: 3.5" finished opening in a shell or head .375 inches thick or less 2.375" finished opening in a shell or head greater than .375 inches If your geometry meets this criteria and this parameter is not checked, then the nozzle reinforcement areas and MAWP’s will not be computed. Print Equations and Substitutions?

By default PVElite will provide you with formulas and substitutions for internal and external pressure calculations. If you do not want these formulas and substitutions, do not check this box. Increase Blind Flange Thickness for Reinforcement?

For Section VIII Division 1, paragraph UG-39(d)(2) provides a consideration for bypassing reinforcement of a single opening of a flat end connection. This effectively increases


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Tools Menu


the required thickness of the blind flange cover. Please note that this can only be used if there is only 1 nozzle located in the blind flange. Use OD as the Basis for the shell Radius in Zick?

By default PVElite uses the ID basis on which to perform Zick analysis calculations. In general, this is more conservative than using the OD. However if you wish to use the OD as the basis, then check this box. Checking this box will change the “r” value used in the stress calculation equations. Allowable Tower Deflection

This setup directive applies to vertical tower geometries. By default PVElite uses a criteria of 6 inches per 100 feet for the allowable tower deflection. If your design specification requires a different value of allowable deflection then enter it here. Wind Shape Factor

Based on the wind design specification, PVElite will compute the wind shape factor. If your design requirement calls for a specific value for the shape factor that does not correspond to the calculated value, then enter that number here. For cylindrical structures it is typically 0.7. Do not use the bolt correction factor.

For the design of heat exchanger flanges and tubesheets, TEMA (like Taylor-Forge) provide a correction factor when the actual bolt spacing exceeds the allowable bolt spacing. The correction factor is then multiplied by the moment to design a thicker flange. The use of this term is very standard in industry and is used in other pressure vessel design Codes such as PD:5500. However, ASME Section VIII does not specifically address this subject. Thus, for a pure flange design per Appendix 2, there is no bolt-spacing correction factor. If you do not wish to use the factor, then check this box. The default is to use the bolt space correction factor. Use Pre-99 Addenda Division 1 only.

As of January 2000, the 1999 addenda of the ASME Code is mandatory. This mandatory revision includes changes to the material properties of many materials used for Division 1 vessel construction found in Section 2 Part D. Namely, the allowable stresses were increased in certain ranges. PV Elite contains 2 databases of material properties. The default behavior is to use the current higher allowable stress database. If you are re-rating an older vessel to the pre 99 addenda and would like to use the older material allowables, then you should check this box. Since the program uses this directive to connect to the database, it should be checked before any vessel modelling occurs. Other design codes will not be affected by this directive. Use Code Case 2260/2261.

Use of this code case calculates required thickness of elliptical and torispherical heads. The required thickness is less than that of the equations in UG-32 or Appendix 1 for these heads.

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Tools Menu

Use EigenSolver

The natural frequency of a structure can be calculated using more than 1 method. The traditional method is to use the analysis technique of Freese or Rayleigh-Ritz. For the skirt supported freestanding structure, this method provides acceptable results. When the support configuration is not the skirt/base type such as legs, lugs, or intermediate skirt, this analysis may not provide accurate results. To solve this problem generically, PVElite has a natural frequency solver that uses numerical methods to solve the general equations motion. Namely, the program must solve the following: [ [K] - Z 2[M]] {a}={0}. Which for the general case is a set of n homogenous (right hand side equal to zero, in this case abs[ [K] - Z 2[M]] {a}=0. This requires an iterative solution. After building a stiffness [K] and mass [M] matrix of the model with appropriate boundary conditions (anchors at skirts, bottom of legs, at support lugs etc.) the program can extract a number of modes that is meaningful in the solution of the dynamics problem, particularly the modal response spectrum analysis. Using this generic frequency Eigensolution method, PVElite can accurately extract modes of vibration for models that do not fit neatly into the cantilever beam model required for the Freese integration codes. The natural frequency of the vessel is used in several of the wind and seismic method. For PVElite files earlier than 4.3, the default is to use the Freese method. The default version for 4.3 and later is to use the EigenSolver. Check or uncheck this box as necessary. •

Create/Review Units—Creates a custom set of user units.

Create/Review Units Dialog

Edit/Add Materials—This option allows the user to create and edit a user defined material in the program’s material database. The screen appears as follows: Tutorial / Master Menu

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Tools Menu


Edit/Add Materials Dialog

To use this processor, fill in all of the values in all cells. If more than one material is to be entered, use the Next button to enter the new material. After all materials have been entered, save the file with the Save button. Finally, press the Merge key to join the user defined material database with the supplied material database. •

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Calculator—This option allows the user to perform simple calculations and paste the results in the input field in which the cursor resides.



Diagnostics Menu

Diagnostics Menu

Diagnostics Menu

•

Crc Check—This option performs a cyclic redundancy check on each of the supplied PVElite files.

•

Build Version Check—This option checks the revision level of the PVElite executable files.


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View Menu


View Menu

View Menu

The View Option allows the user to specify the toolbars to be displayed. The following options are available:

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•

Standard Bar—

•

Element Bar—PVElite allows the user to create a vessel with the default data by simply clicking an icon on the Element Toolbar. The following options are available:

•

Cylinder—Causes a cylindrical shell to be added to the end of the vessel under construction.

•

Ellipse—Adds an elliptical head to the end of the vessel.

•

Torisphere—Adds a torispherical head to the end of the vessel.

•

Sphere—Adds a spherical head to the end of the vessel.

•

Cone—Adds a conical head or shell element to the end of the vessel.

•

Welded Flat—Adds a flat head to the end of the vessel.

•

Body Flange—Adds a body flange to the end of the vessel.

•

Skirt—Skirt element with optional Basering.

•

Detail Bar—By clicking an icon on the Detail toolbar, certain details such as stiffeners, nozzles, forces, moments, platforms, liquid, lining, etc. can be added to the current element when applicable.



•

•

View Menu

Utility Bar—

•

Insert—inserts a new element after the current element.

•

Delete—deletes the current element.

•

Update—updates the vessel graphic.

•

Share—allows data to be shared between several vessel elements.

•

Flip—flips the current element’s orientation.

•

Mat—accesses the material database.

•

Zoom—allows the user to switch the vessel graphics display schemes. Pressing this button causes the current element (plus details) plus the partial of the previous element, if it exists, and the partial of the next element, if it exists, to be drawn to the graphic area.

•

Plan / Layout View—draws the head or cylinder from the top showing the orientation of the nozzles and their diameter limits.

Auxiliary Bar—

•

Pipe Properties—This option will access the database of pipe dimensions. By clicking OK, the current diameter and thickness will be replaced with the current selection.

•

List Dialog—

The list dialog allows the editing of some types of vessel details. One feature of the list is that the location of the detail can be specified from the datum position. To use the list dialog, select the type of detail to edit by


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View Menu


pressing its tab. Then simply enter the data as necessary for each cell. If the list is empty, then press the plus button (+) to add a row. The entry of the “From Node” is optional. The program will assign that value automatically. The description is a required mandatory input. If it is not entered, the program will treat that row as if it did not exist and that data will be lost. All of the other data must be entered as required. Rows of data can be duplicated from on row to the next. Click on the listing number of the item to copy. That row should turn black (selected). Next copy the data to the clipboard by pressing [ctrl-c]. Next paste it to a blank line by using [ctrl-v]. Next change any data that might be different for that detail.

•

PVElite 3D Viewer—Pressing this button starts the PVElite 3D viewer.

•

Status Bar—

•

Split—Allows the user to split the screen by moving the line left or right.

•

Input Bar—Allows selection of the various options as described earlier in this chapter.

•

Analyze Bar—Allows the user to analyze the current model, review previous results, error-check the model, or review the previously created DXF file.

Using the 3D Viewer

The viewer is started by pressing the blue sphere icon on the PVElite Auxilliary toolbar. A vessel model should be open and ready for viewing. The PVElite 3D viewer is a stand alone application that can render any PVElite input file showing the actual vessel geometry in 3 dimensions. In addition to showing the outer surfaces, the model can also be viewed in wire frame and hidden line mode. Different shading modes such as flat shaded, Gourard and Phong are all supported. This program is capable of viewing more that one file at a time making this a multi-document application. Other operations such as panning, zooming and model rotation are also supported. Help is also available in the application by pressing the F1 key or by selecting Help under the Help Menu Option.

Listed below is an explanation of the buttons (icons) on the toolbar.

Open

Open—Open a new file

Copy

Copy—Copies the contents of the current window to the clipboard. This image can

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View Menu

then be pasted into an application such as Microsoft Word. If this option is used, we suggest changing the background color to white instead of the default background color of black. Print

Print—Print the graphic image

Reset View

Reset View—Put the model back into its original location when the program started

Front Zoom Extents Zoom Window Rotate Pan

Predefined Views—Clicking one of these buttons changes the current view to front, back, top, bottom, left, or right view. Zoom Extents—Resizes the model so that it fits in the current window. Zoom Window—When this operator is selected, use the mouse to draw a window around the portion of the model that you want to zoom in on. This is a rubber band zoom. Alternately, spin the mouse wheel to zoom in and out. Rotate—This operator allows the model to be rotated using the mouse. Click the right mouse button and move the mouse to rotate the model.

Zoom Camera

Pan—The pan operator allows the model to be translated in the direction the mouse is being dragged. Pressing the mouse wheel and holding it down while moving the mouse will also pan the model.

Select by Window

Zoom Camera—This operator zooms in or out. Press this button then press the left mouse button and move the mouse diagonally across the screen to zoom in or out. Alternately, spin the mouse wheel to zoom in and out.

Select by Click Insert Cutting Plane

Translate Selection Rotate Selection Insert Text

Edit Properties

Select by Window—This is a rubber band selection of objects. Once objects are selected they can be translated and rotated. Select by Click—Allows the selection of objects by group for further manipulation. This is the cursor icon. Use ctrl + click to select more than one object. Insert Cutting Plane—Click on this button and then click anywhere in the window. A cutting plane will then appear. The plane can then be rotated after it has been selected with the selection tool (cursor icon). The rotating grid will then expose the various layers of the vessel. The visibility of the cutting plane can then be turned off once the view is set. Translate Selection—Moves the items in the current selection away from the main model. Rotate Selection—Rotates the current selection in its own 3D space. Insert Text—Add comments to the model. These comments are for the session only and will not be saved. However, if the graphic is printed, the comments will be printed out as well. Edit Properties—This option allows visibility of vessel details to be turned on or off. Additionally, the model colors can also be set here. After being set, the pro-


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View Menu


gram will remember them in between sessions. This option is also available by right clicking on the model window and selecting properties. The properties dialog is shown below:

You can also add an elements transparency attribute by clicking the Change This Item’s Color button and checking the transparency option on the color dialog.

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View Menu

The floating toolbar show in the window above is produced by right clicking in the window. These menus allow the model to be manipulated. Here it is seen that the grid used to slice the model has been turned off. Within this menu structure it is possible to change the shading algorithm, alter the appearance of surfaces and to change the selection level of various entities. The Options command brings up the Options (Properties) dialog.


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View Menu


Here some of the internals have been selected and translated out of the model. The viewer is a very powerful and useful processor. One of the greatest benefits is its ability to show interference between vessel details like rings, nozzles, platforms, and others.

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View Menu

This is a wire frame view of the 3D model. This option is available under the Render Mode option. After viewing the model close the 3D viewer to return to PVElite.


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ESL Menu


ESL Menu

ESL Menu

The ESL Menu gives access to utilities which interact with the External Software Lock. The options are as follows:

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•

Show Data—This option will display the data stored on the ESL.

•

Phone Update—This option will allow the user to obtain phone update authorization information or other ESL changes, to be made over the phone.

•

Generate Fax Codes—This option will provide the user with access codes for remote ESL updating. These access codes should be sent to COADE for authorization codes.

•

Enter Fax Authorization Codes—Choose this option to enter the remote authorization codes you received from COADE. Each set of four codes will make one change to the data stored on your ESL



Help Menu

Help Menu

Help Menu

The Help Menu displays on-line help and information on how to obtain technical support for PVElite. The options available are as follows: •

Tip of the Day—Provides tips for running PVElite.

•

Help Topics—Starts the help facility.

•

About PVElite—Provides information on the best ways to contact COADE personnel for technical support, and provides a link to COADE’s Web Site.

•

Online Registration—Register this product electronically with COADE.

•

Online Documentation—View this manual online.

•

Foundation 3D Help—Review the foundation 3D interface specification.


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Quick Start with PVElite


Quick Start with PVElite Entering PVElite

Before starting PVElite, most users will collect the necessary data for the vessel design or analysis. PVElite breaks the vessel into an assemblage of individual elements—heads, shells, cones, body flanges, and/or a skirt—and the components on these elements. Vessels are defined one element to the next - from bottom to top for vertical vessels and from left to right for horizontal vessels. Collecting data to define these elements before starting the program is not required but it will make the most efficient use of the designer’s time. Typical input items include actual or proposed values for vessel material, inside diameter, operating temperatures and pressures, wind and seismic site data, nozzle and ring location to name a few. If necessary, the input processor can be terminated at any time and restarted later if any missing data need be collected. With the program’s graphic display of the vessel input, it is easy to recall the current state of an unfinished model or identify where data is missing or incomplete. Start PVElite by clicking on the icon on the desktop or selecting the item from Programs. PVElite will start with a Vessel Input Screen for the job currently called “Untitled.”

Defining the Basic Vessel

PVElite displays the Element Basic Data, an empty graphic area, three tool bars (File Handling, Elements, and Details) and a button bar. Items which cannot be used are grayed out. Vertical vessels are built bottom to top and horizontal vessels are built left to right. It is not necessary to build an entire vessel if only thickness for pressure is desired. Before the first element can be placed on the screen, the Element Basic Data must be set. Start with Inside Diameter as both the node numbers and the Element Type will be set by using the element tool bar. Once the Basic Data is entered, elements are quickly assembled one after another by simply clicking on the Element tool bar and making any changes to the Basic Data. The complete vessel is created from the following elements (in their tool bar order):

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•

Shell

•

Elliptical head



Quick Start with PVElite

•

Torispherical head

•

Spherical head

•

Cone

•

Welded Flat head

•

Body flange

•

Skirt

If the vessel begins with a skirt element it will be a vertical vessel. Both vertical vessels on legs and horizontal vessels would start with a head element. If that first head element is improperly oriented for the vessel in mind (horizontal or vertical), simple click on the FLIP button to correct the orientation. Once the second element is added, the vessel can no longer be flipped between horizontal and vertical. Later, if heads, body flanges or cone elements show incorrect orientation, use the FLIP button to fix them. From Nodes and To Nodes are automatically assigned by the program; they start with node 10 and are incremented by 10’s throughout the model. The element data set at the beginning of the session carries forward from one element to the next. Any data changes on the last element will carry forward onto any new elements to be added. The element data displayed belongs to the highlighted element in the vessel image. Use the mouse to change the highlighted and displayed element by clicking on the element of interest. The Page Up and Page Down keys can also be used to scroll through the vessel elements. Data may be updated one element at a time but there are more efficient ways to change an item through several elements. Say, for example, the circumferential weld joint efficiency for the skirt (from node 10 to 20) is set at 0.7. If this value was not changed to 1.0 on the bottom head as it was created, this (incorrect) value is carried from one element to the next in the Build Mode to the top of the vessel element (say, From Node 50 To Node 60). In this situation, it is easiest to change the data on the bottom head element (20 to 30) and then use the SHARE button to “share” this item through the elements in the list with “From Node” 30 through “From Node” 50. Certain data is automatically “shared”. Inside diameter, for example is automatically changed for all elements (stopping at cones) attached to the element where the change occurs. Some changes to the element data do not immediately appear on the vessel image. To refresh the image click on the Update button.


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Adding Details


Adding Details With the elements defined, enough information exists to run through the pressure calculations but the total vessel weight is not yet set. Much of this information is specified as element details. Nozzles, insulation, operating fluid, platforms and the like are all entered as details on the various elements. PVElite will calculate the weight of each of these items and account for them in the various analyses. Details such as saddles, lugs and legs are also used to locate support points on the vessel—important data for load calculations. Details can only be specified on the current element. To enter the first detail, highlight (make current) the element which will hold the detail and click on the appropriate DETAIL button. Allowing the cursor to rest on the Tool Bar Button will produce a fly out definition of the button. Select the detail and enter the data in the screen that follows. Use the Help button on the detail screen or press [F1] to learn more about the requested data. Define all details necessary to develop the proper total vessel load. Help Screen ([F1]) for a Nozzle Detail:

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Recording the Model - Plotting the Vessel Image

Recording the Model - Plotting the Vessel Image At any point during the input process a standard PCX file with the vessel image is available through the Output item on the Menu Bar. This file can then be incorporated into reports or printed directly (on all printers) through most Microsoft Windows™ packages with graphics capabilities (such as Microsoft’s Word for Windows™ or Paintbrush™). Examples of the graphic dump and screen dump appear below following the illustration of the pull-down menu under File. The vessel graphic may also be sent directly to the printer using the Print command under the File Menu. File Menu:

Graphics dumped to a PCX file, inserted into this document, and scaled:


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Recording the Model - Plotting the Vessel Image


Screen dumped to a PCX file, inserted into this document, and scaled:

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Specifying Global Data - Loads and Design Constraints

Specifying Global Data - Loads and Design Constraints Although default values allow the analysis to proceed, other data should be set before the analysis continues. These data are the required live loads & design constraints and the optional vessel identification and report headings. These data are accessed and entered through the Input item on the Menu Bar. The pull down menu under Input shows the Report Headings, Design/Analysis Constraints, and Live Load Data along with the vessel and component analysis data. The heading input allows the specification of three lines of data which will appear at the top of each page in the printed output. The heading data also includes title page entry which will appear at the beginning of the input echo report. Clicking on Design/Analysis Contraints on the Input pull-down menu will present a screen that shows four data areas - Design Data, Design Modification, Load Case and Nozzle Design Modification. Design Data includes vessel identification along with items which will affect the design and analysis of the vessel; items such as type of hydrostatic testing and degree of radiographic examination appear here. It is important to note that this is where the design code is set - Division 1, Division 2, or PD:5500. The Design Modification area holds four flags which control the redesign of the vessel should the user-entered wall thickness be insufficient for the analyzed loads. If a box is checked, the program will increase the element’s wall thickness so that it meets or exceeds the requirements for that load category. There are four boxes for three load types - one box for internal pressure, two boxes for external pressure (either increase the wall thickness or locate stiffener rings along the vessel to satisfy the buckling requirements), and one box for the variety of structural loads which develop longitudinal stresses in the vessel wall. The program provides the option of rounding up a required thickness to a nominal value (such as the next 1/16 inch or 1 mm). (Use the Configuration item from the Utility menu on the Menu Bar. The third area, Load Case, shows twelve default structural load cases for the analysis. These twelve cases cover the extent of structural loads on the vessel wall. Each case contains a pressure component (axial)1, a weight component (both axial and bending), and a live load component (bending). The axial stresses are combined with the bending stresses to produce a total stress in the vessel wall. Both tensile and compressive stresses are compared to their allowable limits. Refer to the table and screen image below for a definition of terms used in the Load Case input.

Note

These pressure calculations should not be confused with those used for the wall thickness requirements defined in ASME Section VIII and PD:5500. Here, internal and hydrostatic pressures are used to calculate a longitudinal, tensile stress in the vessel wall and the external pressure a similar compressive stress in the wall.

The fourth area, Nozzle Design Modification, is used to set the overall pressure requirements for the nozzles on this vessel and also to include the maximum allowable pressure new and cold (MAP nc) case in the nozzle checks. There is also a button on this screen Install Option. Clicking on this button will produce a screen which allows the user to spec-


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ify where certain vessel details will be added - either at the fabrication shop or in the field. This data is used to properly set the detail weights for the empty and operating conditions. Pressure

Weight

Live Load

NP - No Pressure

EW - Empty Weight

WI -

IP - Internal Pressure

OW - Operating Weight

EQ - Earthquake

EP - External Pressure

HW - Hydrostatic Weight

HI -

Wind at Hydrostatic Weight conditions

HP - Hydrostatic Pressure

CW – Empty Weight NO CA

HE -

Earthquake at Hydrostatic Weight conditions

VF -

Vortex Shedding Filled

Wind

VO - Vortex Shedding Operating VE -

Vortex Shedding Empty

WE - Wind Bending Empty New and Cold WF - Wind Bend Filled New and Cold CW - Axial Weight Stress New and Cold

Design/Analysis Contraints Screen:

Wind and earthquake information is supplied through the Live Load Data Screen. PVElite generates the live loads based on the criteria established by one of four standards - the American Society of Civil Engineers (ASC), the Uniform Building Code (UBC), the (Canadian) National Building Code (NBC), and the Indian National Standard. Wind loads may also be specified directly by the user as a wind pressure profile. PVElite references

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these codes for live loads only. The ASME Section VIII or PD 5500 rules apply for all other calculations. The screen below shows the data required for the default codes. PVElite will use these criteria to set the magnitude of the live load and bending moment on each element of the vessel. Live Load Data Screen:

Once the element, detail, and global data is entered and checked, the model is ready for error processing and analysis.


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Running the Analysis


Running the Analysis The pull down menu under Analyze on the Menu Bar shows two options - Error Check Only and Analyze. Use Error Check Only immediately after any questionable data is entered. Analyze will automatically perform the Error Check before the analysis starts. Comments from the Error Check may be examined through the Review function under the Output item on the Menu Bar (discussed below). Of course errors must be corrected before the analysis can proceed. At each step through the analysis, PVElite will display intermediate calculations of interest to the user. For example, during the internal pressure calculations, the program will pause after displaying the entered wall thickness and required wall thickness for each element. At this point the user may move to the next step, continue non-stop through the rest of the analysis, or terminate the analysis. If any Design Modifications were set (e.g. Select Wall Thickness for Internal Pressure), PVElite will reset the thickness to the necessary value and perfect these increased thicknesses in all output reports and in all other calculations. For example, if the user-entered wall thickness of 1/2 inch is insufficient for the load and the design flag is turned on, the program will calculate the required thickness (say, 5/8 inch) and replace the user-entered input value (1/2) in the output report with the calculated required thickness (here, 5/8). The original model data is not changed by the program. PVElite will check the element wall thicknesses for the various pressure cases (internal, external, and hydrostatic) and then assemble the axial and bending loads to construct each load case defined in the Global Design data. PVElite will calculate the longitudinal stress on both sides of the vessel (e.g. both “windward” and “leeward” for loads with wind) and compare the calculated stresses with the allowable stresses, both tensile and compressive. PVElite will display the (“windward” or “leeward” side) stress which is closest by ratio to the allowable limit, again either tension or compression. Once the analysis is complete, the Review processor is displayed on the screen. The Vessel Analysis Screen:

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Reviewing the Results

Reviewing the Results The PVElite output is stored in a binary data file which requires interpretation by a processor. In PVElite this processor is called Output. Output is invoked at the end of the analysis and may also be accessed directly from the Output item on the Menu Bar. Review lists every report contained in the output from input echo through stress reports. One or more reports are selected by highlighting their titles though mouse clicks. Reports can be reviewed on the screen or sent to a printer or file by using the appropriate tool bar button. Review Output Screen:

Internal Pressure Calculation Report as it appears on the screen:


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Analyzing Individual Vessel Components (Details)


Analyzing Individual Vessel Components (Details) PVElite provides for the analysis of a variety of vessel components that are not included in the overall vessel analysis: Appendix Y Flange, Floating Heads, Lifting Lug, Pipe & Pad, WRC 107 and 297, Thin Joints, Thick Joints, ASME Tubesheets, TEMA Tubesheets, Halfpipe Jackets, Large Openings, and Rectangular Vessels. To enter the component data select Component Analysis Data from the Input Menu. On the Component Screen select a component type from the Component Menu and build the input for the analysis. Each component, once entered, may be analyzed and reviewed by selecting Analyze from the Tools Menu. Component Analysis Menu:

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Shell / Head:


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Shell / Head on screen results:

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DXF File Generation Option

DXF File Generation Option As of Version 4.00 PVElite provides an option to write out Data Interchange Files (3 all together). This type of file is termed a DXF file. The DXF file is a text file that contains commands for generating a 2D CAD drawing of the vessel. This drawing is on a one to one scale and the border and text are scaled by the diameter conversion constant and the scale factor generated by the program or typed in be the user. Many popular drawing programs such as AutoCad ® and MicroStation ® read and process these files. The DXF files produced by PVElite are release 12 compatible. Any version of AutoCad including release 12 and after, should be able to read the DXF file. Three files will be produced: the vessel drawing, the nozzle schedule, and the Bill of Material. The files will be written in the directory where the input file for the vessel file is located. These files are written at the end of the program’s execution. Please note that nearly every individual has his/her own way of drafting. A conscious effort was made not to be too specific. This approach allows the drafter to take the vessel drawing file and edit it as necessary.

Setting Up the Required Parameters In order for PVElite to generate these files, you must instruct it to do so. This is accomplished by pressing the red CAD Icon on the auxiliary toolbar, its look like a red letter A. Optionally, you can use the menu option File->Export->Generate DXF File to set this option. If the scale factor is not set the DXF options dialog will appear prompting for the scale factor and any other necessary options. These options should be entered after the vessel has been completely modeled. This is due to the fact that the scaling factor is based on the overall height/length of the vessel. It is best to check the scaling factor at the conclusion of the data input and before the model is analyzed. The DXF options are available under the Tools->Configuration menu. This is a tabbed dialog. Click the second tab and set the options as necessary. The following options are in the dialog. Create a Default Border—Checking this box instructs the program to put a border around the drawing. The border style differs based on the border size. You can create your own border styles. The borders are located in the PVElite\System subdirectory. They are named ANSI_A.txt and so fourth. These text files are essentially the core of ACAD Release 12 Dxf files. See user border creation instructions below. Create a Nozzle Schedule—Check this to create a Nozzle Schedule. The nozzle schedule contains information pertaining to the size and thickness of nozzles, their mark number and the necessity of reinforcing. Create a Bill of Material—Causes the program to generate a Bill of Material for the major components of the vessel including shells, heads, conical sections etc. OD Lines Shown Only—Normally the DXF file will contain ID as well as OD lines for the major shell sections. If you do not want to see the ID lines, then check this box. Show Dimensions—If you would like tail dimensions for the major shell courses, then check this box. The element diameters and thicknesses are shown in the BOM. Drawing Size—Select A, B, C or D. Each size has a different style. Scale Factor—It is best to let the program select this value. We then recommend rounding up to the nearest typical scale factor.


3-53

User Border Creation


User Border Creation In order to do the following, you must be able to use your Windows Explorer, AutoCad and Notepad. If you cannot, seek help from a seasoned support person. Start AutoCad and open your border. The border should be ANSI standard dimensions 8 ½ by 11 and so fourth scaled for the non-printable area of the paper. After the border drawing is open, save it as a release 12 Dxf file. After the file has been saved it will be necessary to edit it with a text editor such as Notepad. Since the main drawing will have a Dxf header, it will be necessary to delete the one in the border drawing. The Dxf header ends on about line 960 with the word Entities. Delete through this line. Next delete the last 4 lines in the file. This is the end of file marker. Save the file with a txt extension. Next rename the file in the PVElite\system directory that you will be replacing. We suggest putting a new extension on it. Save/Copy your border in the PVElite\system directory and then rename it replacing our default border. You should now have new ANSI_?.txt file in the PVElite\System subdirectory. It may be wise to review our border drawing text files before you start. Also please note that the border drawings must not contain any block attributes. These are not supported in our current implementation. A typical drawing is shown below:

3-54



Invoking the Drawing

Invoking the Drawing If you have a drawing tool on your computer that supports Dxf files, PVElite can invoke it directly. On the Analyze toolbar, there is a blue “A” button. If the button is lit up, the Dxf file for this job was created during the last run. Pressing the button will submit the file to Windows which will invoke your drawing tool. If the input is altered, the analysis must be run in order to generate a new Dxf file.


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Invoking the Drawing

3-56




&KDSWHU Element Data

PVElite has eight basic element types from which all vessels are constructed. PVElite terms for these elements are as follows: •

Cylindrical

Cylindrical Shell

•

Elliptical

Elliptical Head

•

Torispherical

Torispherical Head

•

Spherical

Spherical Head or Shell

•

Conical

Conical Head or Shell Segment

•

Welded Flat

Welded Flat Head

•

Flange

Body Flange

•

Skirt

Skirt Support with Basering

PVElite does not require the complete construction of a vessel for the analysis. Individual elements or groups of elements may be defined and at least partially analyzed. Only complete vessels, that is, vessels with proper supports, can be analyzed for deadweight and live loads. Except for the skirt element, all elements can be used to create either horizontal or vertical vessels. Models for vertical vessels are built from bottom to top and models for horizontal vessels are built from left to right. The vessel orientation is established with the first element. If starting with a skirt, it’s a vertical vessel. If starting with a head, the head may be “flipped” between a bottom head (vertical model) and a left head (horizontal model) by clicking on the FLIP button. Once the second element is added to the model, the orientation is fixed. Skirts are the only vessel support that are modelled as elements. Other supports such as legs and lugs for vertical vessels and saddles for horizontal vessels are modelled as “details” on the elements. These vessel details are in the next chapter.

Element Data

4-1

Element Basic Data


Element Basic Data

All elements share a common set of parameters: Element’s From Node

Enter a number associated with the starting point and ending point of this element. For Heads, the From and To Nodes mark the straight flange attachment to the head, not the overall extent of the head. (The straight flange length cannot equal zero.)

The ‘From’ node number for this element will also be used to define details such as nozzles, insulation, and packing which are associated with this element. The location of the ‘To’ node will be calculated by the program by adding the length of this element to the location of the ‘From’ node. The From and To nodes establish the overall organization of the vessel. When creating a vessel model in the BUILD mode, node numbers are automatically assigned to each element. The BUILD mode starts with node 10 and increments by 10 throughout the vessel. When DELETEing elements, the program will “reconnect” the ves-

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Element Data


Element Basic Data

sel elements by changing the From node of the following element to the To node of the previous element. When INSERTing elements, PVElite will ask for the new (added) To node number and again “reconnect” the elements so that the From and To nodes match with the previous and next elements in the model. The program defines a vertical vessel from the bottom to the top. If the vertical vessel is on a skirt, the first element would be the skirt. If it is on legs or lugs, the first element would be a head and the legs or lugs are defined as details on the appropriate shell element. The program defines a horizontal vessel from the left end to the right end. The first element in a horizontal vessel is usually a head, and the support saddles are defined as details on the appropriate shell element. Element’s To Node

Enter the number associated with the starting point of this element, the ‘From’ node. Inside Diameter

Enter the inside diameter of the element. •

For elliptical, torispherical and spherical heads, this should be the inside diameter of the straight flange.

•

For cones, this is the inside diameter at the From node end.

•

For flanges, this is the inside diameter of the body flange.

•

For skirts, this is the inside diameter at the top of the skirt.

Distance

Enter the distance between the ‘From’ Node and ‘To’ Node. •

For a cylindrical shell, enter the length of the shell from seam to seam.

•

For an elliptical, torispherical, or spherical head, enter the length of the straight flange. The straight flange length cannot equal zero.

•

For a conical head or shell segment, enter the length of the cone (including toriconical sections, if any) from seam to seam.

•

For a welded flat head, enter the thickness of the head.

•

For a body flange, enter the through thickness of the flange including the weld neck, if any.

•

For a skirt support, enter the distance from the bottom of the basering to the skirt/head/ shell seam.

Finished Thickness

Enter the finished thickness of the element. This is typically the nominal thickness minus any mill undertolerance, and taking into account any thinning due to forming. Note that the corrosion allowance is automatically subtracted from this thickness by the program and should not be subtracted by the user. •

Element Data

For elliptical, torispherical and spherical heads, you may have to reduce the nominal thickness of the plate used in order to take into account the thinning of the head due to forming.

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Element Basic Data


•

For cylindrical shells made from pipe, you will have to subtract the maximum possible mill undertolerance from nominal pipe wall thickness.

•

For welded flat heads, enter the through thickness of the flange portion, but do not include the hub and weld neck.

•

For a skirt, this is typically the nominal thickness minus any mill undertolerance, and taking into account any thinning due to forming. For cylindrical skirts made from pipe, you will have to subtract the maximum possible mill undertolerance from the nominal pipe wall thickness.

Corrosion Allowance

Enter the corrosion allowance. The analysis program will subtract this value from the entered thickness and add this value to inside diameter. Wind Load Diameter Multiplier

Enter the wind load diameter multiplier. The value entered here will be multiplied by the element outside diameter in order to determine the overall element diameter to be used in wind load calculations. The element outside diameter will include the insulation. When a number greater than 1 is used, it should be carefully chosen to account for the tributary area of external attachments such as nozzles, piping, or ladders. The typical multiplier used to determine wind load diameter is 1.2. Thus if the actual element OD was 50 inches, the overall wind load diameter for this element would be 50 * 1.2 = 60. The range of this value is normally greater than 1 and less than 2. However in some cases it can be used to turn the wind loads off of certain elements. You can turn the wind load off on the current element by setting this value to 0. A vessel that is supported by an intermediate skirt whose lower elements are protected from the wind would see no wind load on those elements. Material Name

Enter the material specification as it appears in the material allowable tables. Alternatively, the material can be selected from the material database by selecting the [Mat] button from the toolbar. Selecting one of the material names from the list will display the significant material parameters for the analysis. If the current element temperature is outside the valid temperature range for the material, the material may not be specified or selected. (Likewise, a temperature may not be entered if it exceeds the limits for the material.) Pressing Enter while on this field will display the material properties of the current element or detail. Note that if the material is newly selected, the data displayed here are directly from the program’s material database, otherwise the data are from the data structure of the current element or detail. If a newly selected material can not be found in the program’s material database, the program will assume that it is a “User-defined material”, in this case the user must define all material properties in this window. Joint Efficiency for Longitudinal and Circumferential Seams

Enter the efficiency of the welded joint for shell section with welded longitudinal seams. This will be the efficiency of the longitudinal seam in a cylindrical shell or any seam in spherical shell. Elliptical and torispherical heads are typically seamless but may require a

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Element Data


Element Basic Data

stress reduction which my be entered as a joint efficiency. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. The Joint Efficiency in this (and all other) ASME Code formulas is a measure of the inspection quality on the weld seam. In general, weld seams that receive full radiography have a joint efficiency of 1.0. Weld seams that receive spot radiography have a joint efficiency of 0.85. Weld seams that receive no radiography have a joint efficiency of 0.7. Seamless components have a joint efficiency of 1.0. In addition to the basic rules described above, the Code requires that no two seams in the same vessel differ in joint efficiency by more than one category of radiography. For example, if circumferential seams receive no radiography (E=0.7) then longitudinal seams have a maximum E of 0.85, even if they receive full radiography. The practical effect of this rule is circumferential seams, which are usually less highly stressed may be spot radiographed (E=0.85) while longitudinal seams are fully radiographed. This results in the same metal thickness at some savings in inspection costs. Except for the skirt, these values should be set to 1.0 for PD:5500 and Division II. Design Internal Pressure

Enter the design internal pressure for the component. This pressure need not include any pressure due to liquid head, as that value is calculated automatically by the program through the liquid Detail definition. For skirts, this value is preset to zero and cannot be modified. Design Temperature for Internal Pressure

Enter the metal design temperature for the internal pressure condition. This value will be used to collect the material allowable stress in the operating condition. PVElite will check the entered value against the valid temperature range for the current element material. The program will not allow the entry of a temperature outside the material’s range. This value will be used to determine the material allowable stress. Design External Pressure

Enter the design pressure for external pressure analysis. This should be a positive value, i.e. 14.7 psia. If you enter a zero in this field the program will not perform external pressure calculations. For skirts, this value is preset to zero and cannot be modified. Examples of external pressure

0—No external pressure calculation for the element 14.7—External pressure of one atmosphere (full vacuum) Design Temperature for External Pressure

Enter the design temperature for external pressure. This value will be used as the metal design temperature for external pressure calculations. When performing these calculations, the program will use the external design temperature along with the external chart name (found on the material edit window) to access the material tables and thus determine the allowable external pressure. The maximum design temperature will be used for the allowable compressive stress on each element.

Element Data

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Element Additional Data


Element Additional Data Several elements require more information for complete definition. Once the element is set, the Element Additional Data window appears below the Element Basic Data.

Cylindrical Shell There is no additional data for cylinders.

Elliptical Head

Head Factor

Enter the aspect ratio for the elliptical head. A value of 2 is typical, that is, the major axis (vessel diameter) is twice the minor axis (two times the head height). For example, a 60 inch diameter elliptical head would extend 15 inches beyond the straight flange. Inside Head Depth

Enter the inside depth of the elliptical in this field. This value is in the new condition and does not include the corrosion allowance. PVElite will compute the outer depth H and uses this item in the calculation of the parameters needed to compute the required thickness of the ellipse. This depth value is only required for PD:5500.

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Element Data


Torispherical Head

Torispherical Head

Crown Radius

Enter the crown radius of the torispherical head. For a standard ASME Flanged and Dished head, this is equal to the outside diameter of the shell. See the ASME Code, Section VIII, Division 1, Appendix 1-4, figure 1-4(b). The crown radius is ‘L’ in this figure. For PD:5500, this is equal to the outside diameter of crown section of torispherical end measured to tangent between crown and knuckle, as shown in Figure 3.5.2.1. Knuckle Radius

Enter the knuckle radius for the toroidal portion of the torispherical head. For a standard ASME Flanged and Dished head, this is equal to 6 percent of the crown radius. Allowable values range from 6 percent of the crown radius to 100 percent of the crown radius (hemispherical head). See the ASME Code, Section VIII, Division 1, Appendix 1-4, figure 14(b). The knuckle radius is r’ in this figure.

Element Data

4-7

Spherical Head


Spherical Head There is no additional data for spherical heads. Conical Head or Shell Segment

To Node Diameter

The diameter entered in the Element Basic Data for a cone is the inside diameter of the cone at the ‘From’ end of the cone. Enter the inside diameter of the cone at the ‘To’ end here. For a conical head, either the ‘From’ node or ‘To’ node will have a diameter equal to zero or two times the small end knuckle radius. Note that this should not be the diameter at the point where a knuckle or flare intersects the conical section, but at the point where the knuckle or flare intersects the cylindrical section. Cone Length

Enter the design length of the cone along the axis of the vessel. The program will calculate the effective length of the cone for internal and external pressure calculations. Note that for cones without a knuckle or flared section, you can enter either the half apex angle, or the design length of the cone. If you enter both, the program will check the given angle against the calculated angle. For cases where there is a knuckle or a flare, you must enter both the length and the angle. Half Apex Angle

Enter the half apex angle of the cone. Refer to the ASME Code, Section VIII, Division 1, paragraph UG-33, figure UG-33.1 for a sketch of the half apex angle for some typical geometries.

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Element Data


Spherical Head

For internal pressure calculations the half apex angle should not be greater than 30 degrees, though the program will give results for up to 60 degrees. For external pressure calculations it must not be greater than 60 degrees. Note that for cones without a knuckle or flared section, you can enter either the half apex angle, or the design length of the cone. If you enter both, the program will check the given angle against the calculated angle. Toriconical

Check this field if this cone has either a flare (at the small end) or a knuckle (at the large end). See ASME Code, Section VIII, Division 1, Paragraph UG-33, Figure UG-33.1 for an illustration of a toriconical section. By checking the field, the Cone Knuckle Data Edit window will appear. Toricone Dialog

The Toricone Dialog lets the user input and edit the data of the knuckles which are parts of a cone component. The following options are available: •

DELETE - Resets the input fields to values of 0.

•

OK - Saves the data then closes the window.

•

CANCEL - Exits the window without saving the data.

•

HELP - Displays the button definitions.

Large End Knuckle Radius

Enter the bend radius of the toroidal knuckle at the large end. Note that the Code requires this radius to be no less than 6 percent of the outside diameter of the head, nor less than three time the knuckle thickness (ASME Code, Section VIII, Division 1, Paragraph UG31(h)). Large End Knuckle Thickness

Enter the minimum thickness after forming the toroidal knuckle at the large end. Small End Knuckle Radius

Enter the bend radius of the toroidal knuckle at the small end. Note that the Code requires this radius to be no less than 6 percent of the outside diameter of the head, nor less than three times the knuckle thickness (ASME Code, Section VIII, Division 1, Paragraph UG31(h)). Small End Knuckle Thickness

Enter the minimum thickness after forming of the toroidal knuckle at the small end.

Element Data

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Welded Flat Head


Welded Flat Head

Attachment Factor

Enter the flat head attachment factor, calculated or selected from either the ASME Code, Section VIII, Division 1, or the British Standard PD:5500. For PD:5500, enter the factor C computed per figures 3.5.5(1-2). Typical values are 0.35 or 0.41. For ASME Code, refer to Paragraph UG-34, Figure UG-34. Some typical attachment factors are as follows: 0.17

(b-1)

Head welded to vessel with generous radius

0.20

(b-2)

Head welded to vessel with small radius

0.20

(c)

Lap welded or brazed construction

0.13

(d)

Integral flat circular heads

0.20

(e f g)

Plate welded inside vessel (check 0.33*m)

0.33

(h)

Plate welded to end of shell

0.20

(i)

Plate welded to end of shell (check 0.33*m)

0.30

(j k)

Bolted flat heads (include bending moment)

0.30

(m n o)

Plate held in place by screwed ring

0.25

(p)

Bolted flat head with full face gasket

0.75

(q)

Plate screwed into small diameter vessel

0.33

(r s)

Plate held in place by beveled edge

Non-Circ. Small Diameter

If the flat head is circular, you can leave this field at zero. However, if the flat head is noncircular, the program can still calculate the required thickness, etc., using the formulas in the ASME Code, Section VIII, Division 1, Paragraph UG-34. In this case the program assumes that you entered the larger dimension of the flat head in the ‘Diameter’ field, and that you will enter the smaller dimension of the head here. 4-10

Element Data


Flange Analysis

Flange Analysis Body Flange

PVElite calculates actual and allowable stresses for all types of flanges designed and fabricated to the ASME Code, Section VIII, Division 1. The program uses the Code rules found in Appendix 2 of the ASME Code, latest addenda. The flange design rules incorporated in the Code were based on a paper written in 1937 by Waters, Westrom, Rossheim, and Williams. These rules were subsequently published by Taylor Forge in 1937, and were incorporated into the Code in 1942. For all practical purposes they have been unchanged since that time. The Taylor Forge bulletin, frequently republished, is also still available, and is one of the most useful tools for flange analysis. The input and results for the PVElite flange program are roughly modeled on the Taylor Forge flange design sheets. The flange analysis model assumes that the flange can be modeled as stiff elements (the flange and hub) and springs (the bolts and gaskets). The initial bolt loads compress the gasket. This load needs to be high enough to seat (deform) the gasket, and needs to be high enough to seal even when pressure is applied. The pressure load adds to the bolt load and unloads the gasket. Analysis of a typical flange includes the following steps: 1. Identify operating conditions and materials: determine allowable stresses for the flange material and the bolting at both ambient and operating temperatures, from the Code tables of allowable stress. 2. Identify the gasket material and flange facing type. Determine the effective width and effective diameter of the gasket and the gasket factors from the Code charts. 3. From the design pressure and the gasket information, calculate the required area of the bolts. Calculate the actual area of the bolts, and make sure it is greater than the

Element Data

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Flange Analysis


required area. Based on the bolt areas and allowable stresses, calculate the flange design bolt loads. 4. Calculate the bending moments on the flange. In each case the bending moment is the product of a load (pressure, gasket load, etc.) and the distance from the bolt circle to the point of application of the load. The final result is one bending moment for operating conditions and a second for gasket seating conditions. The stresses on a given flange are determined entirely by the bending moment on the flange. All the loads on the flange produce bending in the same direction (i.e., counterclockwise) and this bending is resisted by the ring behavior of the flange, and in integral flanges by the reaction of the pipe. 5. Based on the flange type (Code Figure 2-4) calculate hub factors and other geometry factors for the flange. These are found in Code figures 2-7.1, 2-7.2, 2-7.3, 2-7.4, 2-7.5, and 2-7.6. Formulae are also given in the Code so that computer programs can consistently arrive at the answers that are normally selected from charts in the appendix. These formulae are implemented in this flange program. 6. Calculate stress formula factors based on the geometry factors and flange thickness. 7. Finally, calculate flange stresses using the stress formula factors and the bending moments. Compare these stresses to the allowable stresses for the flange material. The form of the stress equations is: S = k(geometry)*M/t2 That is, a constant dependant on the flange geometry times the bending moment, divided by some thickness squared, either the thickness of the flange or the thickness of the hub. The calculation procedures and format of results in this program are similar to those given in “Modern Flange Design”, Bulletin 503, Edition VII, published by Taylor Forge. This program includes the capability to analyze a given flange under the bolting loads imposed by a mating flange. The program also takes full account of corrosion allowance. The user enters uncorroded thicknesses and diameters which the program adjusts before performing the calculations. The program can treat corrosion in a special manner based on the input of a Yes/No question in the input.

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Element Data


Flange Analysis

The figure below shows geometry for the Flange analysis program:

Element Data

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Flange Input Data


Flange Input Data Flange Type

Click the button for the type of flange that is being analyzed. TYPE Integral Weld Neck Integral Slip On Integral Ring Loose Slip On Loose Ring Lap Joint Blind Reverse There are essentially only two categories of flanges for purposes of analysis. These are integral type flanges, where the flange and the vessel to which it is attached behave as a unit, and loose types, where the flange and the vessel do not behave as a unit. Within these categories, however, there are several additional subdivisions. Weld Neck Flanges

These have a hub which is butt welded to the vessel. Slip-on Flanges

These have hubs, and are normally analyzed as loose type flanges. To qualify as integral type flanges they require a full penetration weld between the flange and the vessel. Ring Flanges

These do not have a hub, though they frequently have a weld at the back of the flange. They are normally analyzed as loose, but may be analyzed as integral if a full penetration weld is used between the flange and the vessel. Lap Joint Flanges

These flanges may or may not have a hub, but they are completely disconnected from the vessel, bearing only on a vessel ‘lap’. They are always analyzed as loose. Reverse Geometry Flanges

Here the gasket seat is on the inside of the shell diameter. These use integral flange rules, which are suitably modified for the reversal of the bending moments. See Appendix 2-13. Split Loose-type Flanges (mostly with lap joints)

A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange (without splits) using 0.75 times the design moment.

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Element Data


Flange Input Data

The pair of rings shall be assembled so that the splits in one ring shall be 90 degrees from the splits in the other. Flat Face Flanges with Full Face Gaskets

A special type of gasket geometry, which is not included in the Code sketches, nor even in the Code design rules, is the flange with a flat face and a gasket that extend from the ID of the flange to the OD, beyond the bolt circle. The gaskets used with this type of flange are usually quite soft. These flanges can be analyzed using the Taylor Forge calculation sheets. Integral Ring (3) & Loose Ring (5) Additional Data

Number of Splits in the Ring Enter the number of splits in the ring, if any, for loose type flanges. This value must be either 0, 1, or 2. Typically split flanges are ring-type flanges. A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange - without splits) using 0.75 times the design moment. The pair of rings shall be assembled so that the splits in one ring shall be 90 deg. from the splits in the other. Weld Leg at Back of Ring Enter the length of the weld leg at the back of the ring. This value is added to the inside diameter during the design of ring type flanges to determine the minimum bolt circle when the design option is turned on. If you are performing a partial or regular analysis, PVElite will check to see if there is interference between the wrench and the weld. PVElite will print a brief message letting you know there is a potential problem. Lap Joint (6) Additional Data

Lap Joint Contact Point Inside Diameter Enter the inner diameter of the flange/joint contact surface. Lap Joint Contact Point Outside Diameter Enter the outer diameter of the flange/joint contact surface. Number of Splits in the Ring Enter the number of splits in the ring, if any, for loose type flanges. This value must be either 0, 1, or 2. Typically split flanges are ring-type flanges. A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange - without splits) using 0.75 times the design moment. The pair of rings shall be assembled so that the splits in one ring shall be 90 deg. from the splits in the other. Blind (7) Additional Data

Is this a TEMA Channel Cover (Y/N)

Element Data

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Flange Input Data


This cell indicates whether or not the current flange is a TEMA channel cover. A separate thickness and MAWP are computed for channel covers, as well as the deflection. Diameter of the Load Reaction (LONG SPAN) Enter the distance to the center of the gasket on the long side of the flange. This diameter is used to calculate the non- circular flange correction factor for ASME blind flanges. This factor is discussed in paragraph UG-34 of the ASME code. Diameter of the Load Reaction (SHORT SPAN) (d) Enter the distance to the center of the gasket on the short side of the flange. This diameter is used to calculate the non-circular flange correction factor for ASME blind flanges. This factor is discussed in paragraph UG-34 of the ASME code. Allowed Channel Cover Deflection For TEMA Channel Covers, enter the magnitude of the allowed deflection at the center of the cover. This value will be used in computing the channel cover thickness and MAWP, even if it is larger than the allowed deflection. However, a warning message will be printed stating this problem exists. Perimeter along the Center of the Bolt Holes (L) Enter the perimeter of the bolted head measured along the centerline of the bolts. This value (L) is needed for both non-circular and circular geometries. For a circular head, enter the value of (3.14159 * bolt circle diameter). For non-circular heads this value will have to be computed and entered. Include Corrosion in Flange Thickness Calculations? The flange thickness is used in several places throughout Appendix 2. The Code states that every dimension used should be corroded. In the flange stress calculations the flange thickness is used. However, some feel that the corrosion should not be taken off of the thickness for the stress calculations. Answering yes or no to this question will inform the program what it is you wish to do. Flange ID ( B’ for Reverse Types) Enter the inner diameter of the flange. For integral type flanges, this value will also be the inner pipe diameter. This value is referred to as “B” in the ASME code. The corrosion allowance will be used to adjust this value - two times the corrosion allowance will be added to the uncorroded ID given by the user. For a blind flange this entry should be 0 (in flange dialog only). Flange OD Enter the outer diameter of the flange. This value is referred to as “A” in the ASME code. Flange Face Outer Diameter Enter the outer diameter of the flange face. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. Flange Face Inner Diameter Enter the inner diameter of the flange face. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket.

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Element Data


Flange Input Data

Gasket Outer Diameter Enter the outer diameter of the gasket. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. Gasket Inner Diameter Enter the inner diameter of the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Hub Thickness, Small End

Enter the thickness of the small end of the hub. This value is referred to as “g0” in the ASME code. The corrosion allowance will be subtracted from this value. For weld neck flange types, this is the thickness of the shell at the end of the flange. For slip-on flange geometries, this is the thickness of the hub at the small end. For flange geometries without hubs, such as a blind flange, this thickness may be entered as zero. Hub Thickness, Large End

Enter the thickness of the large end of the hub. This value is referred to as “g1” in the ASME code. The corrosion allowance will be subtracted from this value. It is permissible for the hub thickness at the large end to equal the hub thickness at the small end. For flange geometries without hubs, such as a blind flange, this thickness may be entered as zero. Hub Length

Enter the hub length. This value is referred to as “h” in the ASME code. When analyzing an optional type flange that is welded at the hub end, the hub length should be the leg of the weld, and the thickness at the large end should include the thickness of the weld. When you analyze a flange with no hub, i.e. a ring flange, a lap joint flange, etc., you should enter zero for the hub length, the small end of the hub, and the large end of the hub. However, when you design as a loose flange or a ring flange which has a fillet weld at the back, enter the size of a leg of the fillet weld as the large end of the hub. This will insure that the program designs the bolt circle far enough away from the back of the flange to get a wrench around the nuts. Bolt Material Specification

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by using [D] command. If a material is not contained in the data base, its specification and properties can be entered manually. Bolt Allowable Stress, Design Temperature

This entry is automatically filled in by the program by entering a material specification.

Element Data

4-17

Flange Input Data


Caution

You should double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D.

Bolt Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification.

Caution


Diameter of Bolt Circle

Enter the diameter of the bolt circle of the flange. Nominal Bolt Diameter

Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the “Thread Series” cell. Thread Series

There are three options for this entry: 1 - TEMA Bolt Table, 2 - UNC Bolt Table, 3 - User specified root area of a single bolt. User-Specified Root-Area Additional Data

Bolt Root Area For nonstandard bolts, enter the root cross sectional area of the bolt. Number of Bolts

Enter the number of bolts to be used in the flange analysis. Gasket Factor m

The gasket factor m is one of two parameters defined by the ASME Code to characterize the behavior of the gasket material. The gasket factor is the multiple of the line pressure required as a stress on the gasket to ensure no leakage. For example, a gasket material with a factor of 4 requires a gasket stress of 200 psi if the line pressure is 50 psi. The gasket factor m is listed in ASME Section VIII Division 1 Appendix 2 Table 2-5.1. This table is reproduced at the end of this Flange Analysis section. Gasket Design Seating Stress y

The gasket design seating stress is the second of two parameters defined by the ASME Code to characterize the behavior of the gasket material. The gasket seating stress is the minimum stress required to seat the gasket in the flange. The gasket design seating stress y is listed in ASME Section VIII Division 1 Appendix 2 Table 2-5.1. This table is reproduced at the end of this Flange Analysis section.

4-18

Element Data


Flange Input Data

Flange Face Facing Sketch

The facing sketch characterizes the shape of the gasket and therefore its ability to seal the flanged joint. Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlation: FACING SKETCH

DESCRIPTION

1a 1b 1c 1d 2 3 4 5

flat finish faces serrated finish faces raised nubbin-flat finish raised nubbin-serrated finish 1/64 inch nubbin 1/64 inch nubbin both sides large serrations, one side large serrations, both sides

6

metallic O-ring type gasket

Column for Gasket Seating (I, II)

Enter 1 for Column I and 2 for Column II. This value is used with the facing sketch (above) to calculate the basic gasket seating width b0. Most gaskets are Column II gaskets; solid flat metal and ring joint gaskets are Column I gaskets. Gasket Thickness

Enter the gasket thickness. This value is only required for facing sketches 1c and 1d. Nubbin Width (or width of Ring Joint)

If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6 (PVElite equivalents 3, 4, 5, and 9). Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Partition Gasket Additional Data

Length of Partition Gasket This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. If the pass partition gaskets are a different width than the main gasket, scale the length you enter so that the area of the gasket is correct. Width of the Pass Partition Gasket Enter the width of the pass partition gasket. The gasket properties such as the facing sketch, column, M and Y will be taken from the main gasket. Using these properties and the known width, PVElite will compute the effective seating width and compute the gasket loads contributed by the partition gasket.

Element Data

4-19

External Loads


External Loads Flanges are frequently subject to external forces and moments, in addition to internal pressure. The program calculates a roughly approximate equivalent pressure for flanges loaded axially and/or in bending using the following formula:

Peq = Pdes + 4F/πG2+16*Μ/πG3 Where: Peq Pdes F M G

= = = = =

Equivalent pressure, psi Design pressure, psi Axial force, lbs Bending moment, in-lbs Diameter of gasket load reaction, in.

The program then uses the equivalent pressure as the design pressure. External Loads Additional Data

Axial Force Enter the magnitude of the external axial force which acts on this flange. Bending Moment Enter the magnitude of the external bending moment which acts on this flange.

4-20

Element Data


Mating Flange Loads

Mating Flange Loads Mating Loads Additional Data

Mating Flange Bolt Load, Operating Enter the bolt load from the mating flange in the operating case. Mating Flange Bolt Load, Seating Enter the bolt load from the mating flange for seating conditions. Mating Flange Design Bolt Load Enter the design bolt load for the mating flange.

Gasket Factor and Seating Stress Gasket Material Self Energizing Types, including metallic and elastomer O ring

Element Data

Gasket Factor m

Seating Stress y

0.00

0

Flat Elastomers: Below 75A Shore Durometer 75A Shore Durometer or higher

0.50 1.00

0 200

Flat asbestos with suitable binder: 1/8 inch thick 1/16 inch thick 1/32 inch thick

2.00 2.75 3.50

1600 3700 6500

Elastomer with cotton fabric insert

1.25

400

Elastomer with asbestos fabric insert: 3 ply 2.25 2 ply 2.50 1 ply 2.75

2200 2900 3700

Vegetable Fiber

1.75

1100

Spiral-wound metal, asbestos filled: Carbon Steel Stainless Steel or Monel

2.50 3.00

10000 10000

Corrugated metal, asbestos filled or Corrugated metal jacketed, asbestos filled: Soft aluminum 2.50 Soft copper or brass 2.75 Iron or soft steel 3.00 Monel or 4-6% Chrome 3.25 Stainless Steel 3.50

2900 3700 4500 5500 6500

4-21

Mating Flange Loads

Gasket Material Corrugated metal, not filled: Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel

4-22


Gasket Factor m

Seating Stress y

2.75 3.00 3.25 3.50 3.75

3700 4500 5500 6500 7600

Flat metal jacketed, asbestos filled: Soft aluminum Soft copper or brass Iron or soft steel Monel 4-6% Chrome Stainless Steel Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel

3.25 3.50 3.75 3.50 3.75 3.75 3.25 3.50 3.75 3.75 4.25

5500 6500 7600 8000 9000 9000 5500 6500 7600 9000 10100

Solid flat metal: Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel

4.00 4.75 5.50 6.00 6.50

8800 13000 18000 21800 26000

Ring Joint: Iron or soft steel Monel or 4-6% Chrome Stainless Steel

5.50 6.00 6.50

18000 21800 26000

Element Data




Inside Diameter at Base

Enter the inside diameter at the bottom of the skirt. This value must be larger than or equal to the inside diameter at the top of the skirt. Basering Dialog

The Basering Dialog lets the user input the basering data.

Note

Element Data

Use the Plot key to get a detailed sketch of the geometry you typed in.

4-23

Basering Analysis


Basering Analysis The PVElite basering module performs thickness calculations and design for annular plate baserings, top rings, bolting, and gussets found on skirts for vertical vessels. These calculations are performed using industry standard calculation techniques as described below. Thickness of a Basering Under Compression

The equation for the thickness of the basering is the equation for a simple cantilever beam. The beam is assumed to be supported at the skirt, and loaded with a uniform load caused by the compression of the concrete due to the combined weight of the vessel and bending moment on the down-wind / down-earthquake side of the vessel. The equation for the cantilever thickness is found in most of the common vessel design textbooks, including Jawad & Farr, Structural Analysis and Design of Process Equipment, page 434, formula 12.12: t

=

SQRT ( 3 * fc * l ** 2 / s )

fc

=

bearing stress on the concrete

l

=

cantilever length of basering

s

=

allowable bending stress of basering (typically 1.5 times Code allowable).

Where:

There are two commonly accepted methods of determining the bearing stress on the concrete. The approximate method simply calculates the compressive load on the concrete assuming that the neutral axis for the vessel is at the centerline. Thus the load per unit area of the concrete is, from Jawad & Farr equation 12.1, equal to: fc

=

-W / A - M * c / I

W

=

Weight of vessel (worst case).

M

=

Bending moment on vessel (worst case).

A

=

Cross sectional area of basering on foundation

c

=

Distance from the center of the basering to the edge

I

=

Moment of inertia of the basering on the foundation

Where:

However, when a steel skirt and basering are supported on a concrete foundation, the behavior of the foundation is similar to that of a reinforced concrete beam. If there is a net bending moment on the foundation, then the force upward on the bolts must be balanced by the force downward on the concrete. But because these two materials have different elastic modulii, and because the strain in the concrete cross section must be equal to the strain in the basering at any specific location, then the neutral axis of the combined bolt/ concrete cross section will be shifted in the direction of the concrete. Several authors, including Jawad & Farr (pages 428 to 433) and Megyesy (pages 70 to 73) have analyzed this phenomenon. The program uses the formulation of Singh and Soler, Mechanical Design of Heat Exchangers and Pressure Vessel Components, pages 957 to 959. This formulation seems to be the most readily adaptable to computerization, as there are no tabulated constants. Singh and Soler provide the following description of their method: In this case a neutral axis parallel to the y axis exists. The location of the neutral axis is identified by the angle alpha. The object is to determine the peak concrete pressure p and the angle alpha.

4-24

Element Data


Basering Analysis

For narrow base plate rings an approximate solution may be constructed using numerical iteration. It is assumed that the concrete annulus under the base plate may be treated as a thin ring of mean diameter c. Assuming the foundation to be linearly elastic, and the base plate to be relatively rigid, Brownnell and Young have developed an approximate solution which, can be cast in a form suitable for numerical solution. Let the total tensile stress area of all foundation bolts be A. Within the limits of accuracy sought, it is permissible to replace the bolts with a thin shell of thickness t and mean diameter equal to the bolt circle diameter c, such that t = A / PI * c. We assume that the discrete tensile bolt loads, acting around the ring, are replaced by a line load, varying in intensity with the distance from the neutral plane. Let n be the ratio of Young’s moduli of the bolt material to that of the concrete; n normally varies between 10 and 15. Assuming that the concrete can take only compression (nonadhesive surface) and that the bolts are effective only in tension (untapped holes in base plate), an analysis [similar to that given above] yields the following results: p

=

(2 * W + r2 * t * c * s) / [(t3 - t) * r1 * c]

s

=

(2 * (M - W * r4 * c) / (r2 * r3 * t * c ** 2)

alpha

=

acos[ (s - n * p) / ( s + n * p )]

t3

=

width of basering (similar to l in Jawad & Farr’s equations above)

c

=

bolt circle diameter

r1-r4

=

four constants based on the neutral axis angle, and defined in Singh & Soler equations 20.3.12 through 20.3.17, not reproduced here.

Where:

These equations give the required 7 non-linear equations to solve for 7 unknowns, namely p, c, alpha, and the ri (i = 1, 4) parameters. The simple iteration scheme described below converges rapidly. The iterative solution is started with assumed values of s and p; say so and po [the program takes these from the approximate analysis it has just performed]. Then alpha is determined via the above equation. Knowing alpha the dimensionless parameters r1, r2, r3, and r4 are computed. This enables computation of corrected values of p and s (say po’ and so’). The next iteration is started with s1 and p1 where we choose: s1

=

.5 * (so + so ’)

p1

=

.5 * (po + po ’)

This process is continue until the errors ei and Ei at the ith iteration stage are within specified tolerances, (ei = Ei = 0.005 is a practical value), where: e

i

E

i

=

(si’ - si) / si

=

(pi’ - pi) / pi

Actual numerical tests show that the convergence is uniform and rapid regardless of the starting values of so and po. Once the new values of bolt stress and bearing pressure are calculated, the thickness of the basering is calculated again using the same formula given above for the approximate method.

Element Data

4-25

Basering Analysis


Thickness of Basering Under Tension

On the tensile side, if there is no top ring but there are gussets, there is disagreement on how to do the analysis. For example, Megyesy uses a ‘Table F’ to calculate an equivalent bending moment. Dennis R. Moss uses the same approach but provides a table of coefficients in his book (pp 126-129 1st ed.), and Jawad & Farr use a ‘yield-line’ theory (page 435-436). Since Jawad & Farr is both accepted and explicit, the program uses their equation 12.13: t

=

SQRT{ (3.91 * F) / [Sy * ( x + y + z)]}

x

=

2*b/a

y

=

a / (2 * l)

z

=

d * ( 2 / a + 1 / [2 * l])

F

=

Bolt Load = Allowable Stress * Area

a

=

Distance between gussets

b

=

Width of base plate that is outside of the skirt

l

=

Distance from skirt to bolt circle

d

=

Diameter of bolt hole

Where:

Thickness of Top Ring Under Tension

If there is a top ring or plate, its thickness is calculated using a simple beam formula. Taking the plate to be a beam supported between two gussets with a point load in the middle equal to the maximum bolt load, we derive the following equation: t

=

SQRT(6 * M / s)

M

=

2 * Ft * Cg / 8.0, bending moment from Megyesy, beam formulas, case 11, fixed beam.

Ft

=

Bolt Load = Allowable Stress * Area

s

=

Allowable stress, 1.5 * plate allowable

Z

=

Section Modulus, from Megyesy, Properties of Sections

=

Wt * t2 / 6.0

=

(Do/2.- Ds/2. - db) = Width of Section

Where:

Wt

Required Thickness of Gussets in Tension

If there are gussets, they must be analyzed for both tension and compression. The stress formula in tension is just the force over the area, where the force is taken to be the allowable bolt stress times the bolt area, and the area of the gusset is the thickness of the gusset times one half the width of the gusset (because gussets normally taper). Required Thickness of Gussets in Compression

In compression (as a column) we must iteratively calculate the required thickness. Taking the actual thickness as the starting point, we perform the calculation in AISC 1.5.1.3. The radius of gyration for the gusset is taken as 0.289 t per Megyesy, Fifth edition, page 404.

4-26

Element Data


Basering Analysis

The actual compression is calculated as described above, then compared to the allowed compression per AISC. The thickness is then modified and another calculation performed until the actual and allowed compressions are within one half of one percent of one another. Basering Design

When the user requests a basering design, the program performs the following additional calculations to determine the design geometry. Selection of Number of Bolts

This selection is made on the basis of Megyesy’s table in Pressure Vessel Handbook (Table C, page 67 in the fifth edition). Above the diameter shown, the selection is made to keep the anchor bolt spacing at about 24 inches. Calculation of Load per Bolt: This calculation is made per Jawad & Farr, equation 12.3: P

=

-W / N + W * M / (N * R)

W

=

Weight of vessel

N

=

Number of bolts

R

=

Radius of bolt circle

M

=

Bending moment

Where:

Calculation of Required Area for each Bolt

This is just the load per bolt divided by the allowable stress. Selection of the Bolt Size

The program has a table of bolt areas, and selects smallest bolt with area greater than the area calculated above. Selection of Preliminary Basering Geometry

The table of bolt areas also contains the required clearances in order to successfully tighten the selected bolt (wrench clearances and edge clearances). The program selects a preliminary basering geometry based on these clearances. Values selected at this point are the bolt circle, basering outside diameter, and basering inside diameter. Analysis of Preliminary Basering Geometry

Using the methods described above for the analysis section, the program determines the approximate compressive stress in the concrete for the preliminary geometry. Selection of Final Basering Geometry

If the compressive stress calculated above is acceptable, then the preliminary geometry becomes the final geometry. If not, then the bolt circle and basering diameters are scaled up to the point where the compressive stress will be acceptable. These become the final basering geometry values.

Element Data

4-27

Basering Analysis


Analysis of Basering Thicknesses

The analysis then continues through the thickness calculation described above, determining required thicknesses for the basering, top ring, and gussets. Basic Skirt Thickness

The required thickness of the skirt under tension and compression loads is determined using the same formula used for the compressive stress in the concrete, except using the thickness of the skirt rather than the width of the basering: s

=

-W / A - M * c / I

Where W

=

Weight of vessel (worst case).

M

=

Bending moment on vessel (worst case).

A

=

Cross sectional area of skirt.

c

=

Distance from the center of the basering to the skirt (radius of skirt).

I

=

Moment of inertia of the skirt cross section.

In tension this actual stress is simply compared to the allowable stress, and the required thickness can be calculated directly by solving the formula for t. In compression, the allowable stress must be calculated from the ASME Code, per paragraph UG-23, where the geometry factor is calculated from the skirt thickness and radius, and the materials factor is found in the Code external pressure charts. As with all external pressure chart calculations, this is an iterative procedure. A thickness is selected, the actual stress is calculated, the allowable stress is determined, and the original thickness is adjusted so that the allowable stress approaches the actual stress. Stress in Skirt due to Gussets or Top Ring

If there are gussets or gussets and a top ring included in the base plate geometry, there is an additional load in the skirt. Jawad & Farr have analyzed this load and determined that the stress in the skirt due to the bolt load on the base plate is calculated as follows: s

=

(1.5 * F * b) / (π * h * t ** 2)

Where F

=

Total load in one bolt = load on one gusset

b

=

Width of the gusset at the base

t

=

thickness of the skirt

h

=

height of the gusset

Jawad & Farr note that this stress should be combined with the axial stress due to weight and bending moment, and should then be less than three times the allowable stress. They thus categorize this stress as secondary bending. The program performs the calculation of this stress, and then repeats the iterative procedure described above to determine the required thickness of the skirt at the top of the basering. Brownell and Young Method

The Brownell and Young Method computes the required thickness of the baseplate, the gussets and the top plate or top ring (if there is one). This method is discussed in the book,

4-28

Element Data


Basering Analysis

Process Equipment Design, by Brownell and Young. It is also discussed in the book, Pressure Vessel Design Manual, by Dennis R. Moss. This baseplate design method is based on the neutral axis shift method and will in general design a thinner basering than the method discussed in the previous paragraphs.

Element Data

4-29

Basering Input Data


Basering Input Data Basering Description

Enter a 15 character or less description of this basering. Analyze or Design Basering

The basering processor can either analyze existing baserings or design new ones. The valid entries are 1. Analyze an existing basering 2. Design a new basering 3. Brownell and Young analyze 4. Brownell and Young design The design mode may change the following items: •

Number of Bolts

•

Size of Bolts

•

Bolt Circle Diameter

•

Outside Diameter of the Basering

•

Inside Diameter of the Basering

Temperature of Basering (needed if not ambient)

Normally baserings operate at temperatures which are near ambient. If the basering is at a higher temperature, enter it here, otherwise leave the default temperature. Thickness of Basering

Enter the actual thickness of basering. Any allowances for corrosion or mill tolerance etc. should be subtracted from this entered thickness. PVElite will compute the required basering thickness using the simplified method and the neutral axis shift method. The user entered thickness value will be used only for comparison. Basering Material Specification

Enter the basering material. Plate materials such as SA-516 70 and SA-36 are commonly used. Use the material button to look at materials contained in the database. If your material is not present, enter the allowable stresses at the basering design metal temperature. Inside Diameter of Basering

Enter the inside diameter of the basering. This entry must be greater than 0 and less than the bolt circle diameter and the basering OD. If the you have specified the program to design the basering, the program may change this value. A good approximation for the basering ID should be entered when using either the analyze or design option. Outside Diameter of Basering

Enter the outside diameter of the basering. This entry must be greater than the basering ID and the bolt circle diameter. When in design mode, the program may change this value.

4-30

Element Data


Basering Input Data

Bolt Material Specification

Enter the bolt material. Use the material button to look at materials contained in the database. If your material is not present, enter the allowable stresses at the bolt design metal temperature. Nominal Bolt Diameter

The nominal bolt diameters accepted by PVElite range between 1/2 and 4 inches (1.27 and 10.16) centimeters. Values outside of this range will not be accepted. When in design mode the program may change the nominal bolt diameter. The bolt diameters are Bolt Size (inches)

Root Area (sq. in.)

1/2 5/8 3/4 7/8 1 1 1/8 1 1/4 1 3/8 1 1/2 1 5/8 1 3/4

0.12 0.202 0.302 0.419 0.551 0.728 0.929 1.155 1.405 1.680 1.980

Bolt Size (inches) 1 7/8 2 2 1/4 2 1/2 2 3/4 3 3 1/4 3 1/2 3 3/4 4

Root Area (sq. in.) 2.304 2.652 3.423 4.292 5.259 6.324 7.487 8.749 10.108 11.566

This bolt information was adapted from Jawad & Farr, Structural Analysis and Design of Process Equipment, (c) 1984, p 425. Number of Bolts

Enter the bolts that the basering design calls for. If in design mode, the program may change the number of bolts being used. The bolts are sized based on the maximum load per bolt in the operating case. The computation of the load per bolt is referenced in Jawad and Farr, equation 12.3. The number of bolts can be between 4 and 12ty0. Diameter at Bolt Circle

Enter the diameter of the bolt circle. This value must be greater than the basering ID and less than the basering OD. When in design mode, the program may change the bolt circle diameter. Whenever this happens, it will be reported in the output. The word DESIGN will appear followed by the value and description of the input the program has changed. Bolt Table (Fine Thread, TEMA ), (Coarse, UNC ) User

Enter the thread series identifier. If table 3 is selected, you will be prompted to enter the root area of a single bolt. This information can be obtained from a standard engineering handbook.

Element Data

4-31

Basering Input Data


Bolt Table 3 Additional Data User Specified Root Area of a Single Bolt

If your basering design calls for special bolts, enter the root area of a single bolt in this file. Note, however, this option is mutually exclusive from the design option. If this condition is detected, the numbers from Table 2 (UNC) will be used. Nominal Compressive Stress of Concrete

Enter the nominal compressive stress of the concrete to which the basering is bolted. This value is f’c in Jawad and Farr or FPC in Meygesy. A typical entry is 3000 psi. Allowable Compressive Strength of Concrete

Enter the allowable compressive stress of the concrete to which the basering is bolted. This value is fc in Brownell and Young. A typical entry is 1200 psi. Bolt Corrosion Allowance

Enter the value of the corrosion allowance the bolts will be subjected to. Gussets Additional Data Thickness of Gusset Plates

Enter the thickness of the gusset plates to be used for this basering. Any allowances for corrosion should be considered when making this entry. Height of Gussets

Enter the gusset dimension from the basering to the top of the gusset plate. The forces in the skirt are transmitted to the anchor bolts through the gussets. Distance between Gussets

Enter the distance between the inside edges of the gusset plates. Average Width of Gusset Plates

Enter the average width of the gusset plates. Elastic Modulus for Plates

The elastic modulus is used to determine the allowable stress for plates in compression according to AISC. This is a required value. For most common steels, this value is 29E6 psi. Yield Stress for Plates

Enter the yield stress for the gusset plates. This value is typically 36,000 psi. Thickness of Top Ring

If your basering design incorporates a top ring, enter its thickness here. If a thickness greater than 0.0 is entered, the program will compute the required thickness of the top plate. If no top ring thickness is entered, no top ring thickness calculations will be made.

4-32

Element Data


Basering Input Data

Width of Top Ring

If your basering design has a continuous top ring, enter its radial width here. This value will normally be close to the (skirt OD - basering OD) /2. If this were an inside chair cap type design, that would probably not be a good approximation. External Corrosion Allowance

Enter the corrosion allowance that would be applied to the skirt, baseplate, gussets and top ring. The external corrosion allowance will simply be added to the required thickness of these components.

Element Data

4-33

Tailing Lug Analysis


Tailing Lug Analysis

Tailing Lug Edit Window

The tailing lug calculation is included in the basering analysis for a single or dual type design as depicted in the figure on the following page. The design is based on a lift position where no bending occurs on the tailing lug. The main considerations for the design are the section modulus, shear and bearing stress at the pinhole and the weld strength. The location of the center of the pin hole will be assumed radially at the edge of the outer most of the top ring or the basering, which ever is larger. In the absence of the top ring/ plate the height of the tailing lug is required. The tailing lug material is assumed to be the same material as the gusset or basering. Note that all input fields pertain to one tail lug.

4-34

Element Data


Tailing Lug Input Data

Tailing Lug Input Data Perform Tailing Lug Analysis

Select this checkbox to perform the Tailing Lug analysis. Tail Lug Type

Select the type of tailing lug (single or dual) used as illustrated on the Centerline Offset

Enter the offset dimension (OS) for the dual tailing lug design only. Lug Thickness

Enter the thickness of the tailing lug. Pin Hole Diameter

Enter the pin hole diameter. The center of the pin hole will be placed radially in line with the larger of the outer most edge of the top ring or the basering (OD). Weld Size Thickness

Enter the leg weld size. Lug Height (only if no Top Ring)

Enter the tailing lug height measured from the top of basering.

Element Data

4-35

Tailing Lug Input Data


Discussion of Results

The tailing lug design consists of a three part analysis: •

the basering assembly (basering, skirt and top ring),

•

the strength of the weld

•

the tailing lug itself

It is assumed that there is no bending in the tailing lug. In the absence of the top ring only the basering and the decay length (e) are considered for the section modulus calculation. The table below lists the allowable stresses used to check the design strength.

4-36

Stress Type

Allowable Value

Shear at Pin Hole

0.4 Sy

Bearing Stress

0.75 Sy

Weld Stress

0.49 Sallow

Element Data


&KDSWHU Vessel Detail Data

Introduction PVElite vessel models are composed of the basic elements (heads, shells, cones, etc.) with details added to these elements. Vessel details are included for two reasons—to develop the total vessel deadweight loads, and to collect information for the analysis of vessel components. Not all of these details are sensible additions to every element. The following table defines the application of these vessel details to the different elements.

Cylinder

Elliptical Head

Torispherical Head

Spherical Head

Flat Head

Cone

Body Flange

Skirt

Ring

#1

Nozzle

#

#

#

#

#

#

Lugs

#

#

#

#

#

#

#

#

Weight

#

#

#

#

#

#

#

#

Forces / Moments

#

#

#

#

#

#

#

#

Platform 2

#

#

#

#

#

Saddle 3

#

Tray

2

#

#

Y/N 4

Legs5

Y/N

Y/N

Y/N

Y/N

Y/N

Packing

Y/N

Y/N

Y/N

Y/N

Y/N

Liquid

Y/N

Y/N

Y/N

Y/N

Y/N

Insulation

Y/N

Y/N

Y/N

Y/N

Y/N

Y/N

Y/N

Y/N

Lining

Y/N

Y/N

Y/N

Y/N

Y/N

Y/N

Y/N

Y/N

Relationship of Elements and Details 1

# indicates that this element type may have several of these details defined Vertical vessels only 3 Horizontal vessels only 4 Y/N (Yes or No) indicates that this element may have this detail turned on or turned off 5 Vertical vessels only and only if no skirt is defined 2

Vessel Detail Data

5-1

Introduction


It is also useful to note here the positioning of certain vessel “details” are applied at a point, such as over a length of the element. A good example is insulation. For a bottom (or left) head, the insulation (element detail) actually starts before the “From” node and covers the head to the “To” node. For a 60 inch diameter elliptical bottom head, the start point of the insulation is 15 inches below the “From” node (enter -15 for the “Distance from From Node”). If the head has the standard 3 inch straight flange, then the insulation covers 18 inches of the element (enter 18 for the “Height/Length of the Insulation”). See the chapter on Details for more information.

Locating “Continuous” Details

5-2

Vessel Detail Data


Assigning Details to Elements

Assigning Details to Elements Details may be assigned to elements by selecting them from the Detail toolbar located at the top of the vessel input screen. The first step in this simple process is to make the element of interest the current element by clicking on it. Next, click the appropriate detail icon for the detail which you need to add. You will then be presented with a dialog box. Fill in all of the information then press the OK button and PVElite will update the graphic image showing your new detail. Since the image is scaled you can see if you have placed your detail in the correct location.

Locating “Continuous” Details

Vessel Detail Data

5-3

Detail Definition Buttons


Detail Definition Buttons A detail is selected for definition by clicking on the detail name. An example of the resulting pop-up screen (here, a ring detail) is shown below.

The individual detail windows generally have the following buttons available: •

PREV. - Saves the current detail data to memory and displays the previous detail of the same type for the element. If there is no previous detail, an error message will be displayed.

•

NEXT - Saves the current detail data to memory and displays the next detail of the same type for the element. If no additional detail of this type exists, the program will create a default detail for the user’s modification. PVElite registers details by the Detail ID. If the current detail does not have a Detail ID defined, the program will display an error message if this button is used.

•

DELETE - Deletes the current detail and displays the data of the next detail of this type, if it exists. If there is not a next detail, the data of the previous detail, if it exists, will be displayed on the window. If no previous detail exists for the element, a new detail listing will be created.

•

OK - Allows the user to save the data of the current detail and close the window. Note that the program will generate an error and not save the data if no Detail ID is specified.

•

CANCEL - Closes the window without saving the current data.

•

MATERIAL - Brings up the material selection window. Clicking on a material name from the program’s database will close the material selection window and bring that material name into the detail data. As not all details require a material definition, not all detail edit windows contain this button.

•

HELP - Displays general help for the detail window.

Other buttons not shown in the illustration above: •

5-4

SECTIONID - This option is available for leg details. Clicking here will bring up the database names for the wide variety of cross section data stored in PVElite. As with

Vessel Detail Data


Detail Definition Buttons

MATERIAL..., clicking on a name in the database will close the database and copy the selected name into the Section ID field. •

FULL - This option appears with those details which involve some length such as insulation, packing and liquid. These details require a start position and end position (entered as a distance from From node and height/length of detail). If the detail extends throughout the element, clicking on this button will automatically calculate and enter these values so that the detail “covers" ’the entire element. This feature is very useful for heads where these two terms (distance and height/length) may not be obvious. Remember that the From node and To node mark the ends of the straight flange portion of the head element and the head itself starts before or extends beyond this node pair. This leads to negative distances from the From node or a larger height/ length of the detail.

•

ALL - This option allows some detail types such as insulation to be applied over the entire vessel at one time. Of course the detail type can be edited on an individual basis on any element if the ALL feature has been used.

Note that only the details of the current element are accessible. To review or define details on other elements, the element of interest must be made current by clicking on it first.

Note

Vessel Detail Data

The Detail Edit window may also be accessed directly from the graphic image found in the Build and Define modes. Simply click the left mouse button on the element to make it current and then click the right mouse button on the detail of interest. For details that cannot be “right button” clicked such as liquid, simply click the detail on the detail toolbar and its associated edit dialog will appear.

5-5

Defining the Details


Defining the Details Three items appear with every element detail. The From Node of the current element, the distance from the element’s From Node (or Offset from Vessel Centerline for heads), and the label given to the detail or Detail ID. From Node

The From Node is an element identifier that cannot be entered or modified. The From Node (and the highlighted element on the graphic) indicates the element which contains the detail. Distance from “From” Node or Offset from Vessel Centerline

Enter the axial or longitudinal distance from the “From” Node to the start of the item to be defined. Be aware that for heads this may be a negative value; for example, insulation on a bottom head starts before the “From” node since the “From” node marks the beginning of the straight flange. For nozzles on heads, enter the radial distance between the vessel centerline and the centerline of the nozzle. For the Detail

Enter the axial distance between the “From” node and the following location:

Ring

Centerline of the ring

Nozzle

Centerline of the nozzle

Lug

Centroid of the lug attachment weld

Weight

Point at which the weight acts

Force/Moment

Point at which the force or moment acts

Platform

Axial distance from the node to the bottom of the platform

Saddle

Vertical centerline of the saddle

Trays

Bottom of the lowest tray

Legs

Centroid of the leg attachment weld

Packing

Start of the packed section

Liquid

Start of the liquid section

Insulation

Start of the insulated section

Lining

Start of the lined section

Detail ID

Enter any alpha-numeric string to identify the detail. While not required, it is suggested to assign unique names for unique items for clear reporting. For example, nozzles should be unique as their individual identification is important while insulation on all elements, if consistent throughout, may be named INSUL on each element. Some consistency will help your naming process. You may wish to use the From node number with an alphabetical extension showing the detail type and the number of such details if needed. For example, for a nozzle, insulation and ring defined on the element From node 20 To node 30 you may have Detail IDs of “NOZL A”, “INSUL”, and “20 RING 1 of 2”, respectively. 5-6

Vessel Detail Data


Rings

Rings The Stiffening Ring Dialog lets the user input and edit the data of the rings which are attached to the current element. These data are used in the calculation of the weight of the ring and, for external pressure checks, in the calculation of the ring area and inertia. When using the ASME Code, the following data screen is displayed.

As the stiffening ring data is entered, PVElite will automatically compute the inertias required and available provided it is not a cone to cylinder junction ring. For bar rings, the program will size a new ring based on a default thickness of 0.375 inches or the value given in the Miscellaneous Options dialog located on the Design/Analysis window. The Check Standards Bars button helps you to select a suitable ring. As you cursor through the rings, the program will compute the results and place them in a display area at the bottom of the dialog. A ring that meets the Code requirements is shown in blue and a failed ring is displayed in red along with a failed message. Ensure the entire vessel is modeled prior to placing and sizing the rings. The Bar Selection dialog is shown below. Use the mouse, space bar, and arrow keys to navigate this tree.

Vessel Detail Data

5-7

Rings


Inside Diameter of Ring

Enter the inside diameter of the stiffening ring. This value is usually equal to the outside diameter of the shell, except for the relatively rare case of a stiffening ring inside of the vessel. Outside Diameter of Ring

Enter the outside diameter of the stiffening ring. This value is usually greater than the outside diameter of the shell. Thickness of Ring

Enter the axial thickness of the stiffening ring. Ring Material

Enter a name of the ring material from the program’s material database or select the material name by first clicking on the Ring Material button. Individual material parameters may be viewed and modified by pressing Enter when the cursor is in this field. PVElite allows entry of the generic entry of any type of stiffener. To do this you must know the cross sectional area of the stiffener as well as the moment of inertia and the distance from the shell surface to the ring centroid. If you are using an American type structural shape simply click on the section type button and then click on the type of geometry being used. If a non-American type section ring is being used, enter in the properties for your section type. Moment of Inertia

A property of the stiffener typically taken from a structural handbook. Units of inertia are length to the 4th power. Cross Sectional Area

This is the area of the ring. Distance to Ring Centroid

This is the distance from the surface of the shell to the center of the rings area. Again this property is typically taken from a structural handbook. Name of Section Type

This value is used for documentation purposes and it is used to look up the total height of the stiffener for the horizontal vessel analysis (if a section type ring is used).

5-8

Vessel Detail Data


Rings

When using British Standard PD:5500 for a cylindrical section, the following screen is shown:

Vessel Detail Data

5-9

Nozzles


Nozzles Nozzle Dialog lets the user input and edit the data of the nozzles which are attached to the current element. These nozzles will add to the total deadweight of the vessel. Even if the deadweight is not significant, entering the nozzles may be very important as the data entered here will be used to evaluate the flange’s and vessel’s maximum allowable pressure (MAP). The nozzle flange MAP will be set according to the element temperature, the nozzle class and the flange grade according to ANSI B16.5. If one of the nozzles controls the vessel’s MAP and a vertical hydrotest is carried out in accordance with ASME UG 99(c), be sure to enter the correct “Flange Distance to Top” in the Global Design Data. Flange distance to top will be the distance from the controlling flange to the top of the vessel. See the Global Data chapter for more information.

Overriding Nozzle Weight

Normally the program calculates the weight of the nozzle from the information the user has already entered and from internal tables of typical weights. If your nozzle is significantly different from a standard weight nozzle, you can enter the weight here, and it will override the program calculated weight.

Note

5-10

This value must be entered in for type HB nozzles.

Vessel Detail Data


Nozzle Analysis

Nozzle Analysis PVElite calculates required wall thickness and area of reinforcement for a nozzle in a pressure vessel shell or head, and compares this area to the area available in the shell, nozzle and optional reinforcing pad. The program also calculates the strength of failure paths for the nozzles. This calculation is based on the ASME Code, Section VIII, Division 1, Paragraph UG-37 through UG-45, 1995. The calculation procedure is based on figure UG37.1. The program calculates the required thickness (for reinforcement conditions) based on inside diameter for the following vessel components: Component

Paragraph

Limitations

Cylinder

G-27 (c) (1)

None

2:1 Elliptical Head

UG-32 (d) (1)

None

Torispherical Head

UG-32 (e) (1)

None


UG-27 (d) (3)

None

The program evaluates nozzles at any angle (less than 90 degrees) away from the perpendicular, allowing evaluation of off angle or hillside nozzles. The NOZZLE program takes full account of corrosion allowance. You enter actual thickness and corrosion allowance, and the program adjusts thicknesses and diameters when making calculations for the corroded condition. The NOZZLE program also performs UCS-66 Minimum Design Metal Temperature (MDMT) calculations for nozzles. As the nozzle data is entered, PVElite will automatically perform the ASME area of replacement or PD:5500 nozzle compensation calculations. A calculation is performed every time the cursor is moved in between input cells. If there is any error in the input that will not allow the analysis to be performed, a status of failed will appear at the bottom of the Nozzle Dialog. The calculation is initiated once the pipe size is specified. If you are changing data, such as the pad thickness and are not moving between cells, press F5 to force PVElite to recalculate and display the results. If the calculation has failed, the result will appear in red. A nozzle that has passed will have blue results. The result is typically the area and minimum nozzle overstress per 1-7. The program will display the text failed in brackets, even though the area of replacement may be sufficient. To effectively use this feature, we suggest that the entire vessel be modeled first, along with the liquid and nozzle pressure design options set. Also for vessels that have ANSI flanges note that the ANSI flange rating will be shown on the main Status bar.

Vessel Detail Data

5-11

Nozzle Analysis


The figure below shows geometry for the Nozzle module.

5-12

Vessel Detail Data


Nozzle Input Data

Nozzle Input Data Nozzle Description

Enter a 15 character or less description of this nozzle. If you type in the description “MANWAY” the UG-45 check for minimum nozzle neck thickness will not be performed. Angle Between Nozzle and Shell

Enter the angle between the centerline of the nozzle and a tangent to the vessel at the point where the nozzle centerline intersects the vessel outside diameter. If left blank, and an offset is entered, the program will compute the angle. Offset Distance from Cylinder/Head Centerline (L1)

Enter the distance from the center of the head to the nozzle centerline. Class for Attached B16.5 Flange

Enter the letters “CL” followed by a space and the number corresponding to the flange class. The following flange classes are available: CL 150, CL 300, CL 400, CL 600, CL 900, CL 1500, CL 2500 Grade for Attached B16.5 Flange

Enter the letters “GR” followed by a space and the number corresponding to the flange material grade. The following flange grades are available: GR 1.1

Med Carbon Steel

GR 1.2

High Carbon Steel

GR 1.4

Low Carbon Steel

Austenitic Steels: GR 2.1

Type 304

GR 2.2

Type 316

GR 2.3

Type 304L,316L

GR 2.4

Type 321

GR 2.5

Type 347,348

GR 2.6

Type 309

GR 2.7

Type 310

Alloy Steels: GR 1.5

C-1/2Mo

GR 1.7

1/2Cr-1/2Mo, Ni-Cr-Mo

GR 1.9

1-1/4Cr-1/2Mo

GR 1.10

2-1/4Cr-1Mo

GR 1.13

5Cr-1/2Mo

GR 1.14

9Cr-1Mo

High Alloy Steels GR 3.1 GR 3.2 GR 3.4 GR 3.5 GR 3.6 GR 3.7 GR 3.8

Vessel Detail Data

NI-FE-MO-CB NI Alloy 200 NI CU 400, 500 NI-CR-FE 600 NI CR-FE 800 NI-MO B2 Nickel Alloys

5-13

Modification of Reinforcing Limits


Modification of Reinforcing Limits You may enter any physical limitation which exists on the thickness available for reinforcement or the diameter available for reinforcement. An example of a thickness limitation would be a studding pad or nozzle stub which would not extend normal to the vessel wall as far as the thickness limit of the nozzle calculation. An example of a diameter limitation would be two nozzles close together, or a vessel seam for which you did not want to take an available area reduction. Physical Maximum for Nozzle Diameter Limit

Enter the maximum diameter for material contributing to nozzle reinforcement. An example of a diameter limitation would be two nozzles close together, or a vessel seam for which you did not want to take an available area reduction. Physical Maximum for Nozzle Thickness Limit

Enter the maximum thickness for material contributing to nozzle reinforcement. An example of a thickness limitation would be a studding pad or nozzle stub which would not extend normal to the vessel wall as far as the thickness limit of the nozzle calculation. Do you want to set Area1 or Area 2 to 0

In some vessel design specifications it is mandated that no credit be taken for the area contributed by the shell or nozzle. You can enter the text “A1” or “A2” in this field. If you do so, that area will be set equal to 0. You can also enter “A1 A2”. This would give you no credit for Area1 - available area in the vessel wall or Area2 - available area in the nozzle wall. Nozzle Material Specification

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by pressing D when the cursor is in the material field. If a material is not contained in the data base, its specification and properties can be entered manually. Nozzle Diameter Basis

Enter 0 for nozzles where the diameter you give is inside diameter. Enter 1 for nozzles where the diameter you give is outside diameter. Actual or Nominal Diameter of Nozzle

Enter the diameter of the nozzle. If you specify nominal or minimum for the nozzle size and thickness basis, then you must enter the nominal diameter of the nozzle in this field. Valid nominal diameters are 0.125 2 10

0.25 2.5 12

0.375 3 14

0.5 3.5 16

0.75 4 18

1 5 20

1.25 6 24

1.5 8 30

Nozzle Size and Thickness Basis

Select the appropriate basis for nozzle diameter and thickness.

5-14

Vessel Detail Data



Actual Diameter and Thickness

The program will use the actual diameter entered in the field above and the actual thickness entered in the field below. Nominal Diameter and Thickness

The program will look up the actual diameter based on the nominal diameter entered in the nozzle size and thickness basis field, and will look up the nominal thickness based on the schedule entered in the nominal schedule of nozzle field. Minimum Diameter and Thickness

The program will look up the actual diameter based on the nominal diameter entered in the nozzle size and thickness basis field, and will look up the nominal thickness based on the schedule entered in the nominal schedule of nozzle field. It will then multiply the nominal thickness by a factor of 0.875. Actual Thickness of Nozzle

Enter the minimum actual thickness of the nozzle wall. Enter a value in this field only if you selected ACTUAL for the nozzle diameter and thickness basis. Otherwise enter a schedule in the field below. Nominal Schedule of Nozzle

Enter the schedule for the nozzle wall. Enter a value in this field only if you selected NOMINAL or MINIMUM for the nozzle diameter and thickness basis. Otherwise enter a thickness in the field above. Type in the schedule for the nozzle, i.e. SCH 40. Available nozzle schedules are SCH 10

SCH 20

SCH 30

SCH 40

SCH 60

SCH 80

SCH 100

SCH 120

SCH 140

SCH 160

SCH 10S

SCH 40S

SCH 80S

SCH STD

SCH X-STG

SCH XX-STG

Nozzle Corrosion Allowance

Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Joint Efficiency of Shell Seam through which Nozzle Passes

Enter the seam efficiency. The seam efficiency is used in the ‘area available’ calculations to reduce the area available in the shell. Note that for shell and nozzle wall thickness calculations, the seam efficiency is always 1.0. Joint Efficiency of Nozzle Neck

Enter the seam efficiency of the nozzle. The seam efficiency is used in the UG45 calculation to determine the minimum required thickness of the nozzle due to internal pressure. Note that for shell and nozzle wall thickness calculations, the seam efficiency is always 1.0.

Vessel Detail Data

5-15



Insert Nozzle or Abutting Nozzle

The nozzle type and depth of groove welds are used to determine the required weld thicknesses and failure paths for the nozzle. If the nozzle is welded to the outside of the vessel wall, it is abutting the vessel wall. If the hole in the vessel is bigger than the nozzle OD and the nozzle is welded into the hole, it is inserted. Figure UW-16.1 shows typical insert and abutting nozzles. Nozzle Outside Projection

Enter the distance the nozzle projects outward from the surface of the vessel. This will usually be to the attached flange or cover. This length will be used for weight calculations and for external pressure calculations. Weld Leg Size for Fillet Between Nozzle and Shell or Pad

Enter the size of one leg of the fillet weld between the nozzle and the pad or shell. Depth of Groove Weld Between Nozzle and Vessel

Enter the total depth of the groove weld. Most groove welds between the nozzle and the vessel are full penetration welds. Thus the depth of the weld would be the same as the depth of the component, that is the thickness of the nozzle. If the nozzle is attached with a partial penetration weld, or just a fillet weld, enter the depth of the partial penetration or a zero, respectively, in this field. Nozzle Inside Projection

Enter the projection of the nozzle into the vessel. The program uses the least of the inside projection and the thickness limit with no pad to calculate the area available in the inward nozzle. Therefore, you may safely enter a large number such as six or twelve inches if the nozzle continues into the vessel a long distance. Weld Leg Size Between Inward Nozzle and Inside Shell

Enter the size of one leg of the fillet weld between the inward nozzle and the inside shell. Local Shell Thickness

Some vessels have insert plates which are thicker than the surrounding shell. If your vessel uses insert plates, enter the thickness of the plate here. This value will be thicker than the shell course thickness this nozzle is located on. The maximum of this value and the element thickness will be used in the nozzle reinforcement calculations. A basic assumption here is that the diameter of the insert plate is greater than the diameter limit of reinforcement which is roughly twice the diameter of the finished opening. Shell Tr Value

For some vessel designs the nozzle reinforcement is governed by bending and normal stresses in the local shell area where the nozzle is located. Normally the value of Tr (shell required thickness) is based on internal pressure requirements. Some specifications call out for "Full Replacement." If this is the case, enter in the actual shell thickness less the corrosion allowance. For another option, review the Nozzle Design Modification Section in the Design/Analysis Constraints. The check box titled "Base Nozzle tr on Max. Stress ratio" can also satisfy external loading criteria by computing the exact requirement for tr. If you enter the Shell Tr, this is the value the program will use. If you do not wish to use this value, enter a 0.

5-16

Vessel Detail Data



This directive is for vertical vessels only. This option should not be checked if the vessel is a horizontal vessel. Tapped Hole Area Loss

This entry is for the exclusion of area needed when holes are tapped into studding outlets and other similar connection elements. The traditional industry standard is to increase the area required by the tapped area loss. Values for tapped area loss are shown in the table below adapted from the Pressure Vessel Design Manual. Please note that PVElite will not multiply the tapped area loss by 2. It will simply use the value that has been supplied. Additional Data for Reinforcing Pad Pad Outside Diameter along Vessel Surface

Enter the outside diameter of the pad. The diameter of the pad is entered as the length along the vessel shell - not the projected diameter around the nozzle, although these two values will be equal when the nozzle is at 90 degrees. Pad Thickness

Enter the thickness of the pad. Any allowances for external corrosion should be taken into account for the pad thickness. Pad Weld Leg Size as Outside Diameter

Enter the size of one leg of the fillet weld between the pad OD and the shell. Note that if any part of this weld falls outside the diameter limit, the weld will not be included in the available area. Depth of Groove Weld between Pad and Nozzle Neck

Enter the total depth of the groove weld. Most groove welds between the pad and the nozzle are full penetration welds. Thus the depth of the weld would be the same as the depth of the component, that is the thickness of the pad. If the pad is attached with a partial penetration weld, or just a fillet weld, enter the depth of the partial penetration or a zero, respectively, in this field. Pad Material

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material database by pressing the button "Pad Material" when the cursor is in the material field. If a material is not contained in the data base, its specification and properties can be entered manually. ASME Code Weld Type

In many cases the Code does not require weld strength/path calculations for full penetration groove welds for pressure loadings. If your weld detail is per UW-16.1 sketch (a), (b), (c), (d), (e), (f-1), (f-2), (f-3), (f-4), (g), (x-1), (y-1) or (z-1) and you do not wish the program to perform the weld strength calculation, enter in a designation such as A. If you wish PVElite to perform this calculation regardless of the type of weld, leave this field blank. ASME Code Weld Type

If it is a type I, J, K, L, X-2, Y-2, Z-2 weld, then PVElite will perform the additional weld size calculations per UW-16(d)(1).

Vessel Detail Data

5-17



Flange Type

This is the type of nozzle flange. This value is not used by the program, but is echoed out for documentation purposes. Flange Material

This is the material the flange is constructed of. This value is not used by the program, but is echoed out for documentation purposes. The flange material should correspond to the type listed for the flange grade.

5-18

Vessel Detail Data


Lugs

Lugs The Lugs Edit Window allows the user to input and edit the data of the sets of lugs which are attached to the current element. If no skirt or legs are defined for a vertical vessel, the lowest set of lugs will be used as the vessel support point for deadload and levelled calculations.

PVElite allows the entry of one of three types of support lug geometries: 1 - simple geometry with gussets 2 - gusseted geometry with top plate 3 - gusseted geometry with continuous top ring

Depending on the type of geometry selected, additional data will need to be entered. Distance from Vessel OD to Lug Midpoint

This is the radial distance from the wall of the vessel to the point where the lug attaches to the structural steel. Lug Bearing Width

This is the width of the structure that is in contact with the bottom lug support plate. Radial Width of Bottom Support Plate

This is the distance the bottom support plate extends from the OD of the vessel. This value must be greater than or equal to the average gusset width. Length of Bottom Lug Support Plate

This value is typically equal to the distance between gussets plus two times the gusset plate thickness.

Vessel Detail Data

5-19

Lugs


Thickness of Bottom Plate

This value is the thickness of the bottom support plate. Distance between Gussets

This is the distance between the insides of the gusset plates. Mean Width of Gussets

This value is equal to the gusset width at the top plus the gusset width at the bottom divided by two. PVElite uses the mean gusset width in order to compute the actual stresses in the gusset plates. Height of Gussets

Enter the height of one gusset. Thickness of Gussets

Enter the thickness of the gusset plate. Radial Width of Top Plate/Ring

This is the radial dimension from the OD of the shell to the edge of the top plate. This value should be less than or equal to the mean gusset width. Thickness of Top Plate/Ring

Enter the thickness of the top plate which sits above the gussets. Overall Height of Lug

Enter the distance from the bottom of the support lug to the top. Overall Width of Lug

Enter the width of the support lug. Weight of One Lug

The program does not gather enough information to be able to do the detailed calculation of the support lug weight. Therefore you must enter the actual weight of one support lug. Number of Lugs

Enter the number of support lugs around the periphery of the vessel at this location. Perform WRC 107 Calc

If the box is checked to perform the WRC 107 local stress and analysis, you will need to fill out the pad dimensions (if there is a pad) and the allowable stress increase factor. Pad Width

The reinforcing pad width is measured along the circumferential direction of the vessel. The pad width must be greater than the attachment width. The length of the attachment is measured along the axis of the vessel.If the box is checked to perform the analysis

5-20

Vessel Detail Data


Lugs

and the pad properties are filled in, the program will compute the stresses at the edge of the attachment and the edge of the pad. Pad Thickness

Enter the thickness o of the pad. Any allowances for the external corrosion should be taken in to account for the pad thickness. Pad Length

Enter the outside diameter of the pad. The diameter of the pad is entered as the length along the vessel shell - not the projected diameter around the nozzle, though these two values will be equal when the nozzle is at 90 degrees.

Vessel Detail Data

5-21

Weight


Weight The Weight Edit Window allows the user to input and edit the data of the weights which are added to the current element.

Miscellaneous Weight

Enter a weight value. This could be generated by an attached piece of equipment such as a motor, by internals such as piping, or by externals such as structural elements. Note that this value will affect the seismic analysis. Offset from Centerline

Enter the distance of this generic weight from the centerline of the vessel. The value will be multiplied by the weight to obtain a moment that will be a part of the stress calculations. For horizontal vessels, the weight will add to the saddle loads and the offset dimension will not be used, but will be echoed for documentation purposes.

5-22

Vessel Detail Data


Forces and Moments

Forces and Moments The Force and Moment Edit Window allows the user to input and edit the data of the sets of forces and moments which are added to the current element. In most cases these are operating loads imposed on the vessel; usually piping loads on nozzles.

Force in X, Y, or Z Direction

Enter the force in the selected direction. Note that the Y direction is always vertically up, the X direction is from left to right, and the Z direction is out of the page. Loads perpendicular to the vessel will be resolved into a single vector and applied to create the worst combination with the live load. Unlike miscellaneous weight, this force is not included in the seismic analysis. Moment about X, Y, or Z Axis

Enter the moment about the selected axis. The rules stated for the forces apply here as well. Acts During Wind or Seismic

If the force or moment acts during either the Wind or Seismic case, check the appropriate box. Please note you can check both boxes but you must at least check one.

Vessel Detail Data

5-23

Platforms


Platforms The Platform Edit Window allows the user to input and edit the data of the platforms which are attached to the current vertical vessel element.

Platform Start Angle (degrees)

Enter the angle between the designated zero degree line of the vessel, and the start angle of the platform. Platform End Angle (degrees)

Enter the angle between the designated zero degree line of the vessel, and the ending angle of the platform. Platform Wind Area

Enter the tributary wind area of the platform. Typically this value will be the greatest span of the platform perpendicular to the vessel multiplied by a nominal platform height, between 12 and 36 inches on the hand rails and other equipment on the platform. Platform Weight

Enter the weight of the platform. Platform Railing Weight

Enter the weight of the railing in units of force/length in this field. This input will be used to compute the weight of the platform when the “calculate weight” button is pressed. Platform Grating Weight

The grating is the plate that one stands on while standing on a platform. This input will be used to compute the weight of the platform when the “calculate weight” button is pressed.

5-24

Vessel Detail Data


Platforms

Platform Width

Enter the radial width of the platform. The platform width, grating weight and railing weight are used to compute the weight of the platform when the “Calculate Weight” button is pressed. Platform Height

The platform height is the distance from the floor plate to the top hand rail. This dimension is usually 42 inches. The program uses this value to compute the wind area when one of the Wind area calculation buttons is pressed. Platform Clearance

The platform clearance is distance between the outer shell surface and the inner diameter of the platform. The value is used to compute the floor area of the platform. Platform Force Coefficient

The force coefficient is a term used to compute the wind area and consequently the wind force acting on a platform. This value is taken from ASCE7-95 from Table 6-9 and is referred to as Cf. A typical value for Cf is 1.2. This value should always be greater than or equal to 1.0. Platform Wind Area Calculation [Installation \ Misc. Options]

PVElite can perform platform area wind calculations in one of four ways. The methods are •

The height times the width times the force coefficient (conservative).

•

One half of the floor plate area times the force coefficient.

•

The height times the width times the force coefficient divided by 3.

•

The projected area of the platform times the force coefficient divided by 3. Note that this option will yield the same results as option 3 for platforms that have a sweep angle of greater than 180 degrees.

To have the program compute the area, simply fill in the required data such as the platform height , width, start and end angles and the force coefficient. As you enter the data the program will compute the result and insert it into the wind area cell. If you want to use your own value, type it in and do not press one of the area options. Platform Length (Non- Circular)

If the platform is the non-circular top head type, enter the long dimension of the platform.

Vessel Detail Data

5-25

Saddles


Saddles The Saddle Edit Window lets the user input and edit the data of the saddles which are attached to the current horizontal cylinder. The size and location of the saddles are important for the Zick calculations of local stresses on horizontal vessels with saddle supports. For proper Zick analysis, only two saddles may be defined and they do not have to be symmetrically placed about the center of the vessel axis. If no saddles are defined for a horizontal vessel, the deadload and live load calculations will not be performed.

Width of Saddle

Enter the width of the saddle support. This width does not include any wear pad on the vessel side. Centerline Dimension (B)

Enter the distance from the base of the saddle to the centerline of the vessel. This is referred to as dimension "B" in some pressure vessel texts. This value is used in determining additional saddle loads due to wind or seismic events. Saddle Contact Angle (degrees)

Enter the angle contained between the two ‘horns’ (contact points) of the saddle, measured from the axial center of the vessel. Typically this value ranges from 120 to 150 degrees. Height of Composite Stiffener

Enter the overall height of the composite stiffener over the saddle (if there is one). Width of Wear Plate

Enter the width of the wear plate between the vessel and the saddle support. Thickness of Wear Plate

Enter the thickness of the wear plate between the vessel and the saddle support.

5-26

Vessel Detail Data


Saddles

Wear Plate Contact Angle (degrees)

Enter the angle contained from one edge of the wear plate to the other edge, measured from the axial center of the vessel. Typically this value is approximately 130 degrees. Saddle Dimension A

This distance is the length between the centerline of the saddle support and the tangent line of the nearest head. This dimension is usually labeled A in most pressure vessel texts. Perform Saddle Check (Y/N)

By answering Y to this prompt and pressing and entering the following information PVElite will perform a structural design check on the saddle supports. Material Yield Stress

Enter the yield stress for the saddles at their design temperature. E for Plates

Enter the modulus of elasticity for the material used to make the saddles. Baseplate Length

This is the long dimension of the baseplate which is in contact with the supporting surface. This value is comparable with the vessel diameter. Baseplate Thickness

This is the thickness of the baseplate support. Baseplate Width

This is the short dimension (Width) of the baseplate. Number of Ribs

The ribs run parallel to the long axis of the vessel. Enter the number of ribs on one saddle support. Rib Thickness

Enter the thickness of the rib supports. Web Thickness

The web is the part of the support structure to which the ribs are attached. Enter the thickness of the web here. Web Location

There are 2 possible locations for the webs, Center or Side. Enter a 0 for center and a 1 for side. Height of Center Web

Enter the distance from the bottom of the center rib to top plus the thickness of the shell.

Vessel Detail Data

5-27

Trays


Trays The Tray Edit Window allows the user to enter and edit the one set of equally spaced trays with a set liquid height for the current element. The Distance from “From” Node will be to the bottom of the lowest tray. Trays may only be entered for vertical vessels.

Number of Trays

Enter the number of trays for the current element. Tray Spacing

Enter the vertical distance between trays. Tray Weight Per Unit Area

Enter the unit weight of each tray. Do not enter the total weight, since the program will multiply the unit weight by the cross sectional area of the element. Height of Liquid on Tray

Enter the height of the liquid on each tray. Density of Liquid on Tray

Enter the density of the liquid on each tray.

5-28

Vessel Detail Data


Legs

Legs The Legs Edit Window allows the user to input and edit the data of the legs which are attached to the current element. Legs may be entered for vertical vessels that have no skirt element.

Distance from Outside Diameter: or Diameter at Leg Centerline

For shell elements enter the distance between the centerline of the leg to the element outside diameter. Usually, this data is the half value of the leg’s width. For heads where the legs may not necessarily attach at the vessel OD but somewhere else along the head, enter the distance between the centerlines of two legs that are opposite to one another. If there are an odd number of legs (therefore no two are opposite), then enter the diameter of a circle drawn through the centerlines of the legs; this would be the outside diameter at the head attachment elevation plus the depth of the leg. Leg Orientation

Select the orientation of the leg to the centerline. Here each selection stands for P. Strong Axis - Strong axis perpendicular to vessel:

Vessel Detail Data

5-29

Legs


P. Weak Axis - Weak axis perpendicular to vessel:

D. Weak Axis - Strong axis diagonal to vessel:

Number of Legs

Enter the number of legs. Section Identifier

Enter the AISC section identifier for the vessel. The program holds data on 929 different AISC sections. The Section ID database may be displayed by pressing the “SectionID” button or press [Alt-S] keystroke combination. The section identifier can be selected directly from the database. Length of Leg

Enter the distance from the attachment point of the leg to the ground.

5-30

Vessel Detail Data


Packing

Packing The Packing Edit Window allows the user to input and edit the data of the packing which is attached to the current element.

Height of Packed Section

Enter the height of the packed section on this element. This value is used only to calculate the weight of the packed section. For seismic calculations the weight center of the packed section will be taken at half this height. Note that if you have a packed horizontal vessel (rare) the value entered in this cell will be the length of the packed section. Density of Packing

Enter the density of the packing. The following table lists some typical densities, shown in lbs/ft3. Note that the densities should be converted if you are using another units system.

Size (in.)

Density (lb/ft3)

Ceramic Raschig Ring

Vessel Detail Data

Size (in.)

Density (lb/ft3)

Carbon Raschig Ring

1/4

60.0

1/4

46.0

3/8

61.0

1/2

27.0

1/2

55.0

3/4

34.0

5/8

56.0

1

27.0

3/4

50.0

1 1/4

31.0

5-31

Packing


1

42.0

1 1/2

34.0

1 1/4

46.0

2

27.0

1 1/2

46.0

3

23.0

2

41.0

Carbon Steel Pall Ring

3

37.0

5/8

37.0

4

36.0

1

30.0

1 1/2

26.0

2

24.0

Carbon Steel Raschig Ring

5-32

1/4

133.0

3/8

94.0

1/2

75.0

5/8

7.25

5/8

62.0

1

5.50

3/4

52.0

1 1/2

4.75

1

39.0

2

4.50

1 1/2

42.0

3

4.50

2

37.0

3

25.0

Plastic Pall Ring

Vessel Detail Data


Liquid

Liquid The Liquid Edit Window allows the user to input and edit the data of the liquid which exists in the current element.

Height/Length of Liquid

Enter the height or length of the liquid on this element. This value is used only to calculate the weight of the liquid section. For seismic calculations the weight center of the liquid section will be taken at half this height. This value is also used to calculate the operating pressure at all points below the liquid. Density of Liquid

Enter the density of the liquid. Some typical specific gravities and densities are shown below in lbs/ft3. Note that the densities should be converted if you use another units system.

Name

Vessel Detail Data

Gravity

Density (lb/ft3)

Ethane

0.3564

22.23

Propane

0.5077

31.66

N-butane

0.5844

36.44

Iso-butane

0.5631

35.11

N-Pentane

0.6247

38.96

Iso-Pentane

0.6247

38.96

N-hexane

0.6640

41.41

2-methypentane

0.6579

41.03

5-33

Liquid

5-34


3-methylpentane

0.6689

41.71

2,2-dimethylbutane

0.6540

40.78

2,3-dimethylbutane

0.6664

41.56

N-heptane

0.6882

42.92

2-methylheptane

0.6830

42.59

3-methylheptane

0.6917

43.13

2,2-dimethylpentane

0.6782

42.29

2,4-dimethylpentane

0.6773

42.24

1,1-dimethylcyclopentane

0.7592

47.34

N-octane

0.7068

44.08

Cyclopentane

0.7504

46.79

Methylcyclopentane

0.7536

46.99

Cyclohexane

0.7834

48.85

Methylcyclohexane

0.7740

48.27

Benzene

0.8844

55.15

Toluene

0.8718

54.37

Alcohol

0.7900

49.26

Ammonia

0.8900

55.50

Benzine

0.6900

43.03

Gasoline

0.7000

43.65

Kerosene

0.8000

49.89

Mineral oil

0.9200

57.37

Petroleum oil

0.8200

51.14

Vessel Detail Data


Insulation

Insulation The Insulation Edit Window allows the user to input and edit the data of the insulation which is attached to the current element.

Height/Length of Insulation / Fireproofing

Enter the height or length of the insulation on this element. This value is used only to calculate the weight of the insulation. For seismic calculations the weight center of the insulated section will be taken at half this height. Note that if you have insulation on a horizontal vessel the value entered in this cell will be the length of the insulated section. Note also that the only distinction between insulation and lining, from the program’s point of view, is that insulation is on the OD of the element, while lining is on the ID of the element. Therefore, use the insulation field to enter OD fireproofing, and the lining field to enter ID fireproofing. Thickness of Insulation or Fireproofing

Enter the thickness of the insulation or fireproofing. Insulation Density

Enter the density of the insulation. The following table lists some typical densities, shown in lbs/ft3. Note that the densities should be converted if you are using another units system.

Name

Vessel Detail Data

Density (lbs/ft3)

Calcium Silicate

22.5

Foam Glass

16.0

Mineral Wool

14.0

Glass Fiber

11.0

Asbestos

30.0

Careytemp

18.0

Kaylo 10

22.0

Perlite/Celo-temp 1500

23.0

Polyurethane

4.0

Styrofoam

3.0 5-35

Lining


Lining The Lining Edit Window allows the user to input and edit the data of the lining which is attached to the current element.

Height/Length of Lining

Enter the height or length of the lining on this element. This value is used only to calculate the weight of the lined section. For seismic calculations the weight center of the lined section will be taken at half this height. Note that if you have lining in a horizontal vessel the value entered in this cell will be the length of the lined section. Thickness of Lining

Enter the thickness of the lining or fireproofing. Note that the only distinction between insulation and lining, from the program’s point of view, is that insulation is on the OD of the element, while lining is on the ID of the element. Therefore, use the insulation field to enter OD fireproofing, and the lining field to enter ID fireproofing. Density of Lining

Enter the density of the insulation, lining, or packing. The following table lists some typical densities, shown in lbs/ft3. Note that the densities should be converted if you are using another units system.

Name

5-36

Density (lbs/ft3)

Alumina Brick

170.0

Fire Clay

130.0

High Alumina

130.0

Kaolin

135.0

Magnesite

180.0

Silica

110.0

Concrete

140.0

Cement

100.0

Vessel Detail Data


&KDSWHU General Vessel Data

Global data edit mode allows the user to input and edit the data used by the whole vessel for analysis and design purposes. Global data includes hydrotest information, structural load cases, and program re-design instructions.

Rev. A

General Data Window

General Vessel Data

6-1

Design Data


Design Data Following is a discussion of the design data parameters that are used for overall vessel analysis: Design Internal Pressure

Enter the specified design internal pressure for the vessel. This value is used as general design data and also to set the UG-99(b) footnote 34 hydrotest pressure. Design Internal Temperature

This value is simply used by the input echo to help insure the correct design data was entered. This value is not used by the analysis portion of the program. Datum Line Distance

Enter the location of the datum line from the first elements from node. After this is done you can use the list command to enter the locations of nozzles, platforms, etc. from the datum line. Hydrotest Type

The Internal Pressure Calculations report from PVElite will list hydrotest pressures for all three test types described below. It is important to properly identify the information requested throughout this input group. That is, even though “Hydrotest Test Position,” “Projection from Top,” “Projection from Bottom,” and “Flange Distance to Top” are not used for ASME UG-99(b) or for ASME UG-99(b) footnote 34, these data are necessary to report the proper hydrostatic test pressure for ASME UG-99(c). Select the hydrotest type. The analysis program provides three different ways to determine hydrotest pressure: 1 - ASME UG-99(b)

The hydrotest pressure will be 1.3 times the maximum allowable working pressure for the vessel multiplied by the lowest ratio of the stress value Sa for the test temperature to the stress value S for the design temperature. This type of hydrotest is normally used for noncarbon steel vessels where the allowable stress changes with temperature starting even at a somewhat low temperature. 2 - ASME UG-99(c)

The hydrotest pressure will be determined by multiplying the minimum MAP by 1.3 and reducing this value by the hydrostatic head on that element or flange. If the vessel is tested in the horizontal position, the hydrostatic head will be based on the maximum shell diameter plus the “Projection from Top” plus the “Projection from Bottom” specified later in this input group. If the vessel is tested in the vertical position and a vessel element sets the minimum MAP, then the hydrostatic head is set by the distance of that element from the top of the vessel plus the “Projection from Top.” If the vessel is tested in the vertical position and a flange has the minimum MAP, the hydrostatic head is composed of the “Flange Distance to Top” plus the “Projection from Top.”

6-2

General Vessel Data


Design Data

3 - ASME UG-99(b) footnote 34

The hydrotest pressure will be 1.3 times the “Design Internal Pressure” specified at the beginning of this input group, multiplied by the lowest ratio of the stress value Sa for the test temperature to the stress value S for the design temperature. Hydrotest Position

This input is required so that the total static head can be determined and subtracted in accordance with UG-99(c). This field is used in conjunction with the “Projection from Top,” “Projection from Bottom,” and “Flange Distance to Top” fields to determine the total static head. Select one of the following Hydrotest Positions. •

Vertical—the vessel would be tested in the upright or vertical position. Note that not very many vessels are tested in the vertical position.

•

Horizontal—this is the position for the majority of vessels tested. The vessel would normally be on its side (in the case of a vertical vessel) or in its normal position (for a horizontal vessel).

Projection from Top

Enter the distance from the outer surface of the vessel in its test position to the face of the highest flange in the test position. This distance is added to the height (for vertical test positions) or to the maximum diameter of the vessel (for horizontal test positions) to determine the static head for the UG-99(c) hydrostatic test. Projection from Bottom

Enter this distance from the outer surface of the vessel in its test position to the face of the lowest flange in the test position. This distance is added to the height (for vertical test positions) or to the maximum vessel diameter (for horizontal test positions) to determine the static head for the UG-99(c) hydrostatic test. Min. Metal Temperature

Enter the specified minimum design metal temperature for the vessel. This value is listed in the Internal Pressure Calculations report for comparison with the calculated UCS-66 minimum temperature. Flange Distance to Top

If a flange controls the MAP of the vessel, the hydrostatic head associated with that flange may be important in determining the overall MAP of the vessel. The value entered here will be used by PVElite to calculate the hydrostatic head at this point and adjust the UG99(c) MAP for vertically tested vessels. Once the controlling flange is identified (usually through a previous analysis) the distance from that flange to the top of the vessel is entered in this field. If the vessel is to be tested in the vertical position in accordance with UG99(c), this value and the “Projection from Top” will be used to adjust hydrostatic test pressure should a (the) flange govern. Construction Type

Select the type of construction to be included on the name plate. This data is for information only; it is reported in the input echo. Available types of construction are:

General Vessel Data

6-3

Design Data


•

Welded—Welded

•

Press. Welded—Pressure Welded

•

Brazed—Brazed

•

Resist. Welded—Resistance Welded

Special Service

Select a type of special service in which the vessel will be used. This data is for information only; it is reported in the input echo. Available types of special service are: •

None—None

•

Lethal—Lethal Service

•

Unfired Steam—Unfired Steam Boiler

•

Direct Firing—Direct Firing

•

Nonstationary—Nonstationary Pressure Vessel

Degree of Radiography

Select the symbolic representation of the degree of radiography. This data is for information only; it is reported in the input echo. Options include: •

RT 1—When the complete vessel satisfies the full radiography requirements of UW11(a) and when the spot radiography provisions of UW-11(a)(5)(b) have not been applied.

•

RT 2—When the complete vessel satisfies the full radiography requirements of UW11(a)(5) and when the spot radiography provisions of UW-11(a)(5)(b) have been applied.

•

RT 3—When the complete vessel satisfies the spot radiography requirements of UW11(b).

•

RT 4—When only part of the vessel has met the other category requirements, or when none of the other requirements are applied.

Miscellaneous Weight

Many designers like to include extra weight to account for vessel attachments and internals not otherwise included in the models. The total weight of the vessel is multiplied by 1.0 plus this percent (i, e. 1.03, 1.05). The two most common choices are 3.0 or 5.0. Use Higher Long. Stresses?

Entering Y (yes) will increase the allowable stresses for vessel loads which include wind or earthquake by twenty percent. The ASME Code (Section VIII, Division 1, Paragraph UG-23(d)) allows the allowable stress for the combination of earthquake loading, or wind loading with other loadings to be increased by a factor of 1.2. Hydro. Allowable Unmodified (Y/N)

By default PVElite uses the hydrotest stress times the stress increase factor for occasional loads ( times the joint eff. on the tensile side ). However, for stainless steel vessels this value is often limited to 0.9 times the yield stress. In that instance you must enter in the

6-4

General Vessel Data


Design Data

hydrotest allowable stress for the hydrotest. Then this field should be set to Y so that PVElite will use the defined value without any modification. Consider Vortex Shedding?

For vertical vessels which are susceptible to wind induced oscillations, check this field. This will cause the program to compute fatigue stresses based on loads generated by wind flutter. The program will then go on to compute the number of hours of safe operation remaining under the wind vibration conditions. User Defined MAWP/MAPnc

Normally PV Elite computes the MAWP and the MAPnc based on pressure ratings for the elements and ANSI flanges. In some cases it may be necessary to override the program’s generated results with a pre-defined value. If this value is zero it will be ignored by the program. This is the default behavior. User Defined Hydrostatic Test Pressure

Normally the hydrostatic test pressure is computed by the program. It is then used to determine the stresses on the elements when subjected to this pressure. If this value is greater than 0, PVElite will use this pressure plus the applicable hydrostatic head which will be computed based on the hydrotest position. If this value is 0, the program will use the computed value based on the hydrotest type and position. Corroded Hydrotest?

By default PVElite uses the uncorroded wall thickness when the stresses on the elements during the hydrotest are computed. In some cases it is necessary to hydrotest the vessel after it has corroded. If you wish to use a corroded thickness in the calculations, check this box. Please note that longitudinal stresses due to Hydrostatic test pressure will also be computed in a similar manner. Is This a Heat Exchanger

If the Dimensional Solutions 3D file interface button is checked, PV Elite will Rev. A write out an ASCII text file that contains the geometry and loading information for this particular vessel design. If this box is checked, the program will simply write this data out to the Jobname.ini file created in the current working directory.

General Vessel Data

6-5

Installation Options


Installation Options The installation options shown below allow the specification of where the equipment such as platforms, insulation, lining, etc. will be installed. This information is used to calculate the center of gravity of the vessel in both the shop and the field (operating ) positions. Additionally, when computing such items as the fabricated weight, operating weight, empty weight, etc., PVElite will consider these detail weights as appropriate for the various weight cases.

Installation and Miscellaneous Options

Platform Area Calculation Method

PVElite uses the area of the platforms in the computation of forces that are applied to the vessel during the wind loading analysis. Unfortunately, there is no standard method for computing the amount of area that a platform provides for wind load calculations. Select one of the 4 options in the pull down box: This selection will be used to compute the wind area for all platforms specified in this job. Stiffener Type

For ASME VIII 1 and VIII 2 the program has the ability to determine the maximum stiffener spacing and add rings to the model. If you have selected this position to model, it can select an appropriate stiffener from the AISC database. The stiffener types are:

6-6

•

Equal Angle

•

Unequal Angle (hard way shown)

•

Double Angles with large or small sides back to back

•

Channels

•

Wide Flanges General Vessel Data



•

Structural Tees

•

Bar

For the bar ring design, the program will design a ring with an aspect ratio of 10 to 1.00. The height of the ring is 10 times its thickness. The minimum ring width the program will start out with is 0.5 inches or 12mm. For Angle Sections Rolled the Hard Way

If the stiffener above is an angle type, they are frequently rolled to have the strong axis of the ring perpendicular to the vessel wall. If they are rolled the hardway check this box. Bar Thickness to use Designing

When the bar ring option is selected the program must have a thickness to use when computing a suitable ring. For the ring design, the program will generate a ring with a 10 to 1 aspect ratio. In other words, the width of the ring will be 10 times bigger. This value can be left blank. If it is blank, the program will use a default thickness of 0.375 inches or 9 mm. When computing the ring width to meet the moment of inertia requirements. Rigging Data

The rigging analysis calculates and locates the bending and shear stresses created during erection process. Where the vessel is lifted from the horizontal position at two lifting points up to the vertical position where the vessel is set onto the foundation. The safety of the maximum combined stresses is also analyzed using the unity check method. This analysis however, does not evaluate the design of any rigging attachment such as, lugs, shackles, cables etc Rigging analysis is performed when the vessel is in the horizontal position where the combinations of stresses are at its maximum. The torsional effect is not considered in this analysis. The vessel is erected using two lifting points where the tail and lifting lugs are located. The design weight of the vessel is calculated by multiplying the erected empty weight, including internals and externals, with an impact factor to simulate the initial lift. The rigging analysis reports the field and design weight of the vessel, the center of gravity, the reaction forces at the lifting points, the location for the maximum bending and shear stresses, and the unity check. As a comparison, the allowable bending (per UG-23) and shear (0.4 Sy @ ambient) stresses are also reported, and can be plotted with the fore-mentioned parameters. The stresses are calculated in 1 foot increments along the vessel taking into account the varying diameter and thickness of the shell. A circular cross sectional shape is assumed throughout the vessel sections with no corrosion allowance included for the thicknesses. Node numbering starts at the base of the vessel and ends at the top section of the vessel where the straight line ended. For elliptical heads, the end node is the end of the straightline portion. Thus the total height of the vessel is the elevation of the last node. Impact Factor

PVElite can perform a rigging (combined shear plus bending stress) analysis granted that Rev. A the vessel has a support such as a skirt and the impact factor and lug elevations defined.

General Vessel Data

6-7



When the vessel is lifted from the ground, it may be yanked suddenly. The impact factor Rev. A takes this into account. This value typically ranges from 1.5 to 2.0, although values as high as 3.0 may be entered in. The impact factor effectively increases the overall weight of the vessel by the impact factor. If you do not wish to perform the rigging analysis, set the impact factor to 0. Lug Distances from Base

You will have to enter two distances (one in each field) to perform the rigging analysis. These distances are measured from the bottom of the vertical vessel or from the left end of the horizontal vessel. It does not matter which dimension goes in which box. The lesser distance will be the minimum of the two values. Select from Standard Bar Ring List

If this box is checked and the program is set to add reinforcing rings during runtime, PVElite will check all rings from smallest to largest and determine the minimum ring that will satisfy the moment of inertia requirements per UG-29(a) or Appendix 1-5 or 1-8 in the case of cone cylinder junction ring design. A list of sizes is shown in the table below:

6-8

General Vessel Data


Design Modification

Design Modification Select Wall Thickness for Internal Pressure

If the user toggles on this button and the required element thickness for internal pressure exceeds the user’s finished thickness for the element, the program will increase the user’s finished thickness to meet or exceed the thickness required for internal pressure. PVElite will exceed the required thickness only if the round off switch is activated in the program configuration (the round off will bump the thickness up to the next 1/8 inch in English units or to the next millimeter in metric units). The program will perform this calculation automatically as the model data is being typed in. Check this box before any part of the vessel has been modelled. If the given thickness is greater than the required thickness, then the program will not alter the given value. Note that during the input phase, the program cannot check the required thickness for flanges. That check will be performed during the analysis phase. Select Wall Thickness for External Pressure

If this check box is checked the program will calculate the required thickness of each element (or group of elements) and increase the given thickness appropriately for the external pressure. Note that if the user selects this button, the program will not calculate stiffening rings for the external pressure. After the analysis the program may prompt stating that the input file has been modified. If any of the elements have been thickened, simply select "yes" to the prompt and your model will be updated with the current changes. Select Stiffening Rings for External Pressure

If the user toggles on this button, the program will calculate the location and size stiffening rings needed for the external pressure. Note that if the user selects this button, the program will not modify thickness for the external pressure. After the analysis the program may prompt stating that the input file has been modified. If any rings have been added, simply select "yes" to the prompt and your model will be updated with the current changes. Please note that in order to do this the program computes the allowable length between stiffeners. This result must come out to be some reasonable value. If the maximum stiffened is too small, the program will not be able to add rings. In that case, you must increase the thickness of the shell and try the design again. Also note that the heads must also be properly designed for external pressure. Please verify that the thickness for external pressure is adequate. Select Wall Thickness for Axial Stress

If the user toggles on this button he program will calculate the required thickness of

each element (or group of elements) for longitudinal loadings (wind, earthquake, weight of vertical vessels) and increase the given thickness appropriately for the axial stress. PVElite will exceed the required thickness only if the round off switch is activated in the program configuration (the round off will bump the thickness up to the next 1/8 inch in English units or to the next millimeter in metric units).

General Vessel Data

6-9

Load Case


Load Case The program performs calculations for various combinations of internal pressure, external pressure, hydrotest pressure, wind load, and seismic load. You can define up to twelve combinations of these loadings for the program to evaluate. Load cases are defined by a string that shows the loads to be added, i.e. “IP+OW+WI”, which would be the sum of internal pressure plus operating weight plus wind. Typical definitions for the load cases are shown below, followed by the definition of the load case abbreviations: •

Load Case 1:

NP+EW+WI+FW

•

Load Case 2:

NP+EW+EQ+FS

•

Load Case 3:

NP+OW+WI+FW

•

Load Case 4:

NP+OW+EQ+FS

•

Load Case 5:

NP+HW+HI

•

Load Case 6:

NP+HW+HE

•

Load Case 7:

IP+OW+WI+FW

•

Load Case 8:

IP+OW+EQ+FS

•

Load Case 9:

EP+OW+WI+FW

•

Load Case 10: EP+OW+EQ+FS

•

Load Case 11: HP+HW+HI

•

Load Case 12: HP+HW+HE

•

Load Case 13: IP+WE+EW

•

Load Case 14: IP+WF+CW

•

Load Case 15: IP+VO+OW

•

Load Case 16: IP+VE+OW

•

Load Case 17: IP+VF+CW

Where: NP IP EP HP EW OW HW WI EQ HE HI WE WF CW FS FW

6-10

= = = = = = = = = = = = = = = =

No Pressure Internal Pressure External Pressure Hydrotest Pressure Empty Weight Operating Weight Hydrotest Weight Wind Load Earthquake Load Hydrotest Earthquake Hydrotest Wind Wind Bending Empty New and Cold Wind Bending Filled New and Cold Axial Weight Stress New and Cold Axial Stress due to Axial Forces (Seismic) Axial Stress due to Axial Forces (Wind)

General Vessel Data


Load Case

If you checked the box to perform vortex shedding calculations, the following load case descriptors may be used: VO VE VF

= = =

Bending Stress due to Vortex Shedding Loads (Ope) Bending Stress due to Vortex Shedding Loads (Emp) Bending Stress due to Vortex Shedding Loads (Test No CA.)

The live loads (wind and earthquake) are calculated for two conditions - operating and hydrotest. In both cases, the basic loads calculated are identical but the hydrotest live loads are usually a fraction of the operating live load. These hydrostatic fractions (percents) are entered in the live load definitions.

General Vessel Data

6-11

Nozzle Design Modifications


Nozzle Design Modifications PVElite has three mutually exclusive options for determination of the pressure where the nozzle is located. The fourth design option allows reinforcing calculations for the geometry to be made in the new and cold condition helping to satisfy hydrotest requirements. The last option deals with compliance with nozzle design for wind and seismic considerations. Check the option(s) you wish the program to use. Nozzle Design Modifications, Design Pressure, M.A.W.P. + Static Head

This option computes the internal pressure on the nozzle on the bottom of the element where the nozzle is located. This pressure is the MAWP of the vessel plus the static head to the bottom of that element. Thus, the design pressure can vary for nozzles located on different elements. This option is OK to use if you know for certain that your nozzle locations will not vary during the design process. If you use this option and a nozzle is lowered in the vessel and under additional pressure due to liquid head, you need to rerun the analysis in order to determine if your nozzle geometry is satisfactory. Nozzle Design Modifications, Design Pressure, Design Pressure + Static Head

This option computes the exact internal pressure at the nozzle location. Normally, this option would be used for re-rating vessels. This would allow one to get the exact results for each nozzle, because the static head on each nozzle is computed on an individual basis. Nozzle Design Modifications, Design Pressure, Overall MAWP + Static Head

This option computes one single design internal pressure for all of the nozzles located on the vessel. If the nozzle location on a vessel changes due to a client request, there would be no need to rerun nozzle calculations since the pressure used in the calculations would not change. This design option is ideal for designing new vessels. Nozzle Design Modifications, Consider MAP nc in Analysis

Some design specifications require that nozzle reinforcement calculations are performed for the MAP new and cold condition. PVElite will check to see if the nozzle is reinforced adequately using the MAPnc generated during the internal pressure calculations. When the area of replacement calculations are made for this case, cold allowable stresses are used and the corrosion allowance is set to 0. Designing nozzles for this case helps the vessel to comply with UG99 or appropriate (hydrotest) requirements. Check your design requirements to see if this case is required by your client. Modify Tr based on the Maximum Stress Ratio

Some Nozzle designs need to comply with ASME Section VIII Division 1 paragraph UG22 which deals with supplemental loadings. One factor in ASME nozzle design is the required thickness of the shell (tr). Usually internal pressure (hoop stress) governs. In some cases, such as when a nozzle is located on a shell course at the bottom of a tall tower, longitudinal stresses will govern. In this case the shell required thickness must be based on longitudinal stresses and not the hoop stress. If you check this option, PVElite will look at all of the defined load cases and select the highest stress ratio. It will then use this number as a multiplier on the shell thickness. Thus the nozzle design is based on the precise loading at the bottom of that shell course.

6-12

General Vessel Data


Note

Nozzle Design Modifications

Optionally, for full replacement options, you can type in your own value of tr for each nozzle. That value will override this directive.

Consider Code Case 2168 for Nozzle Design

For Div. 1 nozzles of integral construction, the Code in Code Case 2168 allows a different set of rules to be used from those in UG-37. It if is within the project specifications to use these rules check this box. Redesign Pads to Reinforce Openings

If this box is checked and pad defined geometries are inadequately reinforced, PVElite will determine the diameter and thickness of the pad required to reinforce the opening. If the program has changed the pad data during the analysis, it will prompt you to reload the file so that you can view the new changes. Note that this functionality is restricted to ASME VIII analysis at this time.

General Vessel Data

6-13

Wind & Seismic Data


Wind & Seismic Data Wind & Seismic Data Edit mode allows the user to input and edit the wind code data and the seismic code data for the current job. The wind code data and the seismic code data will be used for the wind load and the earthquake analysis.

Wind & Seismic Data Edit Mode Window

Wind Data Wind Design Code

Select one wind of the design codes: •

ASCE — American Society of Civil Engineers Standard 7 (formerly ANSI A58.1) The program implements ASCE 7-93.

•

UBC — Uniform Building Code. The program implements the 1991 edition.

•

NBC — National Building Code of Canada. The program implements the 1990 edition.

•

User Defined Wind Profile. — Instead of supplying the wind parameters required by the above codes, the user may specify the elevation vs. wind pressure directly.

•

ASCE-1995/98 — The American Society of Civil Engineers Standard 7 1995/1998. This revision includes a new calculation for the gust factor as well as the wind pressure at height Z. These calculations are based on a 3 second gust.

•

IS-875 — This is India’s National Standard Wind design code. The year of this code is 1987.

The remaining wind load data required by PVElite changes based on which Wind Design Code is selected. These data requirements are reviewed here according to the design code specification.

6-14

General Vessel Data


ASCE Wind Data

ASCE Wind Data Design Wind Speed

Enter the design value of the wind speed. These will vary according to geographical location and according to company or vendor standards. Typical wind speeds range from 85 to 120 miles per hour. Enter the lowest value reasonably allowed by the standards you are following, since the wind design pressure (and thus force) increases as the square of the speed. Exposure Constant

Enter an integer indicating the ASCE-7 Exposure Factor:

Entry Definition 1 2 3 4

Exposure A, Large city centers Exposure B, Urban and suburban areas Exposure C, Open terrain Exposure D, Flat unobstructed coastal areas

Note that most petrochemical sites use a value of 3, exposure C. Base Elevation

Enter the elevation at the base of the vessel. This value will be used to calculate the height of each point in the vessel above grade. Thus, for example, if the vessel is mounted on a pedestal foundation, or on top of another vessel, it will be exposed to higher wind pressures than if it were mounted at grade. Percent Wind for Hydrotest

Enter the fraction of the wind load (not wind speed) that will be applied during the hydrotest. This is typically as low as one third the design wind load, since it can be assumed that the vessel will not be hydrotested during a hurricane or severe storm. ASCE 7-93 Importance Factor

Enter the value of the importance factor that you wish the program to use. Please note the program will use this value directly without modification. In general this value ranges from .95 to 1.11. It is taken from Table 5 of the ASCE standard.

Category

General Vessel Data

100 mi or more from Hurricane Oceanline

Less than 100 miles from Hurricane Oceanline

I

1.00

1.05

II

1.07

1.11

III

1.07

1.11

IV

0.95

1.00

6-15

ASCE Wind Data


Category Classification I

Buildings and structures not listed below

II

Buildings and structures where more than 300 people congregate in one area.

III

Buildings designed as essential facilities, hospitals etc.

IV

Buildings and structures that represent a low hazard in the event of a failure.

Note that most petrochemical structures are Importance Category I. ASCE Roughness Factor

Enter an integer indicating the ASCE-7 Roughness Factor (from ASCE 7-93, Table 12 Force Coefficients for Chimneys, Tanks, and Similar Structures, Cf) Entry

Definition

1

Round, moderately smooth

2

Round, rough (D’/D = 0.02)

3

Round, very rough (D’/D = 0.08)

Where: D’ is the depth of protruding elements such as ribs and spoilers and D is the diameter or least horizontal dimension. Note that most petrochemical sites use a value of 1, moderately smooth, except that some designers use a value of 3, very rough, to account for platforms, piping, ladders, etc. instead of either entering them explicitly as a tributary wind area or implicitly as an increased wind diameter. The value Cf will vary between 0.5 and 1.2 depending on the type of surface and height to diameter ratio.

6-16

General Vessel Data


UBC Wind Data

UBC Wind Data Design Wind Speed


Enter an integer indicating the UBC Exposure Factor as defined in Section 2312: Entry

Definition

2

Exposure B, Terrain with buildings, forest or surface irregularities 20 feet or more in height covering at least 20 percent or the area extending one mile or more from the site.

3

Exposure C, Terrain which is flat and generally open, extending one-half mile or more from the site in any full quadrant.

4

Exposure D, The most severe exposure with basic wind speeds of 80 m.p.h. or more. Terrain which is flat and unobstructed facing large bodies of water over one mile or more in width relative to any quadrant of the building site. This exposure extends inland from the shoreline 1/4 mile or 10 times the building (vessel) height, whichever is greater.

Note that most petrochemical sites use a value of 3, exposure C. This value is used to set the Gust Factor Coefficient (Ce) found in Table 23-G. Base Elevation


Enter the fraction of the wind load (not wind speed) that will be applied during the hydrotest. This is typically as low as one third the design wind load, since it can be assumed that the vessel will not be hydrotested during a hurricane or severe storm. UBC Wind Importance Factor

Enter the value of the UBC Importance Factor. Please note the program will use this value directly without modification. This value is taken from Table 23-L of the UBC standard:

General Vessel Data

6-17

UBC Wind Data


Entry

Definition

1.15

Category I: Essential facilities

1.15

Category II: Hazardous facilities

1.0

Category III: Special occupancy structures

1.0

Category IV: Standard occupancy structures

Most petrochemical structures have an Importance Factor of 1.0. The four Occupancy Categories (I-IV) are defined in Table 23-K of the code.

6-18

General Vessel Data


NBC Wind Data

NBC Wind Data Design Wind Speed


Enter an integer indicating the NBC Exposure Factor: Entry

Definition

1

Exposure A, open or standard exposure

2

Exposure B, urban and suburban areas

3

Exposure C, centers of large cities

Note that most petrochemical site use a value 1, Exposure A. Note also that these exposure factors are reversed from those of ASCE-7 or UBC. Base Elevation


Enter the fraction of the wind load (not wind speed) that will be applied during the hydrotest. This is typically as low as one third the design wind load, since it can be assumed that the vessel will not be hydrotested during a hurricane or severe storm. Critical Damping Ratio

The dynamic gust evaluation in NBC requires that the user assign a critical damping ratio for the tower. NBC recommends the use of the value 0.0016 (dimensionless) for tall metal unlined stacks, but says that these values will go up for shorter towers. We recommend the following: Entry

General Vessel Data

Definition

0.0016

for tall towers ( L/D > 7 )

0.0032

for moderately tall towers

0.0064

for short towers ( L/D < 1) or horizontal

6-19

NBC Wind Data


Roughness Factor

Enter an integer indicating the NBC Roughness Factor as found in Figure B-15: Entry

Definition

1

Round, moderately smooth surface

2

Round, rough surface (rounded ribs, h = 2%d)

3

Round, very rough surface (sharp ribs, h = 8%d)

Note that most petrochemical sites use a value of 1, moderately smooth, except that some designers use a value of 3, very rough, to account for platforms, piping, ladders, etc. instead of either entering them explicitly as a tributary wind area or implicitly as an increased wind diameter.

6-20

General Vessel Data


ASCE 95 Wind Data

ASCE 95 Wind Data Percent Wind for Hydrotest

Enter the fraction of the wind load (not wind speed) that will be applied during the hydrotest. This is typically as low as one third the design wind load, since it can be assumed that the vessel will not be hydrotested during a hurricane or severe storm. Design Wind Speed

Enter the design value of the wind speed. These will vary according to geographical location and according to company or vendor standards. Typical wind speeds range from 85 to 120 miles per hour. Enter the lowest value reasonably allowed by the standards you are following, since the wind design pressure (and thus force) increases as the square of the speed. Base Elevation

Enter the elevation at the base of the vessel. This value will be used to calculate the height of each point in the vessel above grade. Thus, for example, if the vessel is mounted on a pedestal foundation, or on top of another vessel, it will be exposed to higher wind pressures than if it were mounted at grade. Exposure Constant

Enter an integer indicating the ASCE Exposure Factor: Entry

Definition

1

Exposure A, large city centers

2

Exposure B, urban and suburban areas

3

Exposure C, open terrain

4

Exposure D, flat unobstructed costal areas

Note that most petrochemical site use a value 1, Exposure A. Note also that these exposure factors are reversed from those of ASCE-7 or UBC.

General Vessel Data

6-21

ASCE 95 Wind Data


Importance Factor

This value varies between .087 and 1.15 and is found in Table 6-2 of ASCE 95. Roughness Factor

Enter an integer indicating the Roughness Factor as found in Table 6-7: Entry

Definition

1

Round, moderately smooth surface

2

Round, rough surface

3

Round, very rough surface

Note that most petrochemical sites use a value of 1, moderately smooth, except that some designers use a value of 3, very rough, to account for platforms, piping, ladders, etc. instead of either entering them explicitly as a tributary wind area or implicitly as an increased wind diameter. Height of Hill (H)

Height of Hill or Escarpment relative to the upwind terrain. Distance to Site (x)

Enter the distance ( upwind or downwind ) from the crest to the building site Height above Ground

ASCE defines this value as height above local ground level. Crest Distance

This is the distance upwind of the crest where the difference in ground elevation is half the hill or escarpment height. Type of Hill

•

0 - none

•

1 - 2-D ridge

•

2 - 2-D escarpment

•

3 - 3-D axisymmetric hill

Damping Factor

Enter the structural damping coefficient (percentage of critical damping). The damping factor is used in the calculation of the gust response factor. Additionally, if you wish to run another case empty or filled (or both), specify the values of the damping factor (beta) for these cases. By entering these values PVElite will compute the gust response factor for each case and the subsequent wind loads. The results will be displayed in the Wind Load Calculation and Wind Shear and Bending reports.

6-22

General Vessel Data


Technical Note

ASCE 95 Wind Data

Computation of h/d from table 6-7

For vessels that have a constant diameter the value of h/d is straightforward. The ratio is merely the total height of the vessel divided by the insulated outside diameter. This computation is more difficult for vessels of more than 1 diameter (i.e.: vessels that have cones). The first step is to compute the total height h. Next the total cross sectional area of the vessel is computed. To get a properly weighted value for h/d we square the maximum height and divide by the total area. Finally to get Cf we index into the table as needed and interpolate for the final value. If you have a shape factor specified and do not wish to use the computed value, specify your own shape factor in the Tools, Configuration option from the Main Menu.

General Vessel Data

6-23

IS 875 Wind Code


IS 875 Wind Code Percent Wind for Hydrotest

Enter the fraction of the wind load (not wind speed) that will be applied during the hydrotest. This is typically as low as one third the design wind load, since it can be assumed that the vessel will not be hydrotested during a hurricane or severe storm. Enter the design value of the wind speed. These will vary according to geographical location and according to company or vendor standards. Typical wind speeds range from 85 to 120 miles per hour. Enter the lowest value reasonably allowed by the standards you are following, since the wind design pressure (and thus force) increases as the square of the speed. Base Elevation

Enter the elevation at the base of the vessel. This value will be used to calculate the height of each point in the vessel above grade. Thus, for example, if the vessel is mounted on a pedestal foundation, or on top of another vessel, it will be exposed to higher wind pressures than if it were mounted at grade. Wind Zone Number

India is divided into 6 wind zones. Refer to figure 1 in the IS-875 code to determine which wind zone the vessel will operate in. The program will gather the basic wind speed based on the zone. However, this value can be overridden by typing in a basic wind speed in the Design Wind Speed field. Risk Factor

This is the value of K1 and it varies between 1.05 and 1.08 depending on which zone has been entered above. Terrain Category

The terrain category varies between 1 and 4. Category 1

Exposed open terrain with few or no obstructions including open sea coasts and treeless plains. Category 2

Open terrain with scattered obstructions having heights between 1.5 to 10 meters. This category is generally used for design purposes. Category 3

This is terrain with numerous closely spaced obstructions which have buildings up to 10 M in height. This includes well wooded areas, towns and industrial areas fully or partially developed. Category 4

Terrain consisting of large closely spaced obstructions. This category includes large urban centers and well developed industrial centers.

6-24

General Vessel Data


IS 875 Wind Code

Equipment Class

This field accepts a value of 1, 2, or 3. Class A - 1 Class B - 2 Class C - 3 Consider Gust Response Factor

If you wish to include the gust response factor per IS-875, check this box. However, since this factor increases the wind load 3 to 6 times, it may lead to a very conservative wind design.

General Vessel Data

6-25

User-Defined Wind Profile


User-Defined Wind Profile Percent Wind for Hydrotest

Enter the fraction of the wind load (not wind speed) that will be applied during the hydrotest. This is typically as low as one third the design wind load, since it can be assumed that the vessel will not be hydrotested during a hurricane or severe storm. Wind Profile Data

With this selection, PVElite will forego all code calculations and simply use the user’s profile of height versus wind pressure. Enter the profile in the area below the standard wind design code data. Enter the height above grade (in length units) in the left cell, and the wind pressure at that height in the right cell. If you have more cells available than you need to describe the profile, simply enter zeros in all the remaining cells. Zero elevation corresponds to the bottom of the skirt or leg supports for a vertical vessel and to the bottom of the saddle which supports a horizontal vessel.

Note

When entering this data, you need to multiply the wind pressure at each elevation by the shape factor you wish to use. If you do not do this, your wind loads will be higher (conservative) than they really are.

The first Elevation field should not be zero. If it is zero the program will not compute the wind loads on the following elements. The input should follow the convention below.

6-26

General Vessel Data


Seismic Data

Seismic Data Seismic Design Code

Select the design code to use for seismic calculations: •

ASCE-88 — American Society of Civil Engineers Standard 7 (formerly ANSI A58.1) released in 1988.

•

ASCE-93 — American Society of Civil Engineers Standard 7 (formerly ANSI A58.1) released in 1993. The new ASCE 7 earthquake standards released in 1993 are significantly more involved than the previous standards, and are also more strictly limited to buildings, and thus not as easily applied to vessels. Temporarily the program does not implement the complete dynamic analysis according to this standard. However the program does address the computation of the element mass multiplier as outlined on page 62 of the standard. In effect, the factors Av, Cc, P, and ac are multiplied together and then by the weight of the element to obtain the lateral force on the element. The program then computes the moments on the tower based on these results. One should have a good understanding of this code before using it.

•

UBC — Uniform Building Code. The program implements the 1991 edition.

•

NBC — National Building Code of Canada. The program implements the 1990 edition.

•

IS-1893 RSM — India's seismic design code based on the response spectrum method.

•

IS-1893 SCM — India's seismic design code based on the seismic coefficient method.

•

ASCE-95 — American Society of Civil Engineers 1995 edition. The methodology of this calculation is very similar to other earthquake codes. Essentially the base shear is computed based on paragraph 9.2.3.4 and the paragraphs which proceed it. The base shear is then distributed to the elements according to the equation 9.2.3.4-2 on page 70 of the standard.

•

UBC97 — Uniform Building Code. The 1997 version of this code is implemented.

•

G Loading — Acceleration of the vessel based on a fraction of gravity.

•

ASCE 7-98 — American Society of Civil Engineers Standard 7 (formerly ANSI A58.1) released in 1998.

•

IBC-2000 — International Building Code released in 2000.

•

Response Spectrum —The response spectrum analysis allows the use of modal time history analysis. The general design guidelines for this analysis are taken from the ASCE 7-98 or IBC 2000 Codes. Other predefined spectra are built into the program, such as the 1940 Earthquake El Centro and various spectra from the United States National Regulatory Commission Guide 1.60. If the spectrum analysis type is userdefined, the table of points that define the response spectra must be entered in the table, in the appropriate units. For tall structures, this analysis gives a much more accurate calculation than the typical static equivalent method. Usually the computed loads are lower in magnitude than those computed using the conventional Building Code techniques.

General Vessel Data

Rev. A Rev. A

6-27

Rev. A

ASCE 7-88 Seismic Data


ASCE 7-88 Seismic Data Importance Factor

Enter the value of ASCE 7-88 Importance Factor. Please note the program will use this value directly without modification. This value is taken from Table 22, Occupancy Importance Factor, I (Earthquake Loads) of the ASCE standard. Building categories are defined in Table1 of the standard. Entry

Definition

1.00

Category I: Buildings not listed below

1.25

Category II: High occupancy buildings

1.50

Category III: Essential facilities

0.00

Category IV: Low hazard buildings

Note that most petrochemical structures are Importance I. Soil Type

Enter an integer indicating the Soil Profile Coefficient, S found in Table 24 of the standard. Soil Profiles are identified in Section 9.4.2 of the standard. Note that where soil properties are not known, soil profiles S2 or S3 shall be used, whichever produces the larger value of CS. (C is defined in Eq. 8 of the standard.) Entry

6-28

Definition

1

Soil Profile S1: Rock or stiff soil conditions (S Factor = 1.0)

2

Soil Profile S2: Deep cohesion less deposits or stiff clay conditions (S Factor = 1.2)

3

Soil Profile S3: Soft- to medium-stiff clays and sands (S Factor = 1.5)

General Vessel Data



Horizontal Force Factor

Enter the seismic force factor per ANSI A58.1 Table 24. Typical values for this factor are as follows: Entry

Definition

1.33

Buildings with bearing walls

1.00

Buildings with frame systems

2.50

Elevated tanks

2.00

Other structures

Note that the value most often used is 2.0, though 2.5 is sometimes chosen for tanks supported by structural steel or legs. Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. Seismic Zone

Select the zone for seismic calculations. See ASCE 7-88 Figures 14 & 15 to select the appropriate zone. Values for Seismic Coefficient, Z are found in Table 21 of the standard. Zone

Definition

0

Zone 0: Gulf coast and prairies. (Z = 1/8)

1

Zone 1: Rockies and Appalachian areas. (Z = 3/16)

2

Zone 2: New England, Carolinas, Ozarks, valley area west of the Rockies and the Pacific Northwest. (Z = 3/8)

3

Zone 3: Sierras. (Z = 3/4)

4

Zone 4:California fault areas. (Z = 1)

Note that 0 indicates the least chance of a major earthquake, while 4 indicates the greatest chance of an earthquake.

General Vessel Data

6-29



ASCE 7-93 Seismic Data Seismic Coefficient Av

Enter Av, the seismic coefficient representing the effective peak velocity-related acceleration from Section 9.1.4.1 of the code. This value may be obtained from the map on pages 36 and 37 of the standard. In general this value ranges from 0.05 (low incidence of earthquake) to 0.4 (high incidence of earthquake). Seismic Coefficient Cc

Enter Cc, the system seismic coefficient for mechanical and electrical components from Table 9.8-2 on page 63 of the code. For tanks, vessels and heat exchangers this value is normally taken as 2.0. Performance Criteria Factor P

Enter P, the performance criteria factor from Table 9.8-2 on page 63 of the code. This factor depends on the Seismic Hazard Exposure Group which is defined in Section 9.1.4.2 of the standard. Entry

Definition

1.5

Seismic Hazard Exposure Group III: Essential facilities required for post-earthquake recovery

1.0

Seismic Hazard Exposure Group II: Buildings that have a substantial public hazard due to occupancy or use

0.5

Seismic Hazard Exposure Group I: All other buildings

Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. Amplification Factor ac

Enter ac, the attachment amplification factor determined in accordance with ASCE 7-93 Table 9.8-3. Values for this entry may be 1.0 or 2.0 depending on the relationship between the fundamental period of the vessel and the fundamental period of its supporting structure.

6-30

General Vessel Data


UBC Seismic Data

UBC Seismic Data Importance Factor

Enter the value of the UBC Importance Factor. Please note the program will use this value directly without modification. This value is taken from Table 23-L of the UBC standard: Entry

Definition

1.25

Category I: Essential facilities

1.25

Category II: Hazardous facilities

1.00

Category III: Special occupancy structures

1.00

Category IV: Standard occupancy structures

Note that most petrochemical structures have an Importance Factor of 1.0. Soil Type

Select the soil type (S1 to S4) defined in Table 23-J of the code. Note that where soil properties are not known, soil profile S3 shall be used. Soil

Definition

1

Soil Profile S1:Rock (S Factor = 1.0)

2

Soil Profile S2:Dense or stiff soil (S Factor = 1.2)

3

Soil Profile S3:Not more than 40 ft. of soft clay (S Factor = 1.5)

4

Soil Profile S4:More than 40 ft. of soft clay (S Factor = 12.0)

Horizontal Force Factor

Enter an integer corresponding to the factor RW found in UBC Table 23-Q. RW is used in determining the seismic force factor for nonbuilding structures. As per UBC: tanks, vessels or pressurized spheres on braced or unbraced legs have RW = 3 and distributed mass cantilever structures such as stacks, chimneys, silos, and skirt-supported vertical vessels have RW = 4. Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small.

General Vessel Data

6-31

UBC Seismic Data


Seismic Zone

Select the zone for seismic calculations. See UBC-91 Figure No. 23-2 to select the appropriate zone. The zone establishes the Seismic Zone Factor, Z, found in Table No. 23-I. Zone

Definition

0

Zone 0:Gulf coast and prairies. (Z = 0.00)

1

Zone 1:Rockies and Appalachian areas. (Z = 0.075)

2

Zone 2a:New England, Carolinas, and Ozarks. (Z = 0.15)

3

Zone 2b:Valley area west of the Rockies and the Pacific Northwest (Z = 0.20)

4

Zone 3:Sierras. (Z = 0.30)

5

Zone 4:California fault areas. (Z = 0.40)


6-32

General Vessel Data


NBC Seismic Data

NBC Seismic Data Importance Factor

Enter the value of the NBC Importance Factor found in Sentence 4.1.9.1 (10). Please note the program will use this value directly without modification. Entry

Definition

1.5

Post-disaster buildings

1.3

Schools

1.0

All other buildings

Note that most petrochemical structures have an Importance Factor of 1.0. Soil Type

Select the soil factor (From Table 4.1.9C) for the site: Soil

Definition

1

Category 1:From rock to stiff fine-grained soils up to 15 m deep

2

Category 2:From compact coarse-grained soils to soft fine-grained soils up to 15 m deep

3

Category 3:Very loose and loose coarse-grained soils with depth greater than 15 m

4

Category 4:Very soft and soft fine-grained soils with depth greater than 15 m

Force Modification Factor

Enter an integer to indicate the type of lateral load resisting system. This value will be used to set the Force Modification Factor (R) per Table 4.1.9.B and sentences 4.1.9.1 (8) and 4.1.9.3 (3): Entry

1

Case 18 - Elevated tanks (such as equipment on legs). (R = 1.0)

2

Case 6 - Ductile structures (such as towers on skirts). (R = 1.5)

Note

General Vessel Data

Definition

Elevated tank analysis also includes the special provisions of sentence 4.1.9.3 (3).

6-33

NBC Seismic Data


Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. Acceleration Zone

Select the acceleration-related seismic zone. For locations in Canada, the velocity and acceleration seismic zones are found in the city list, Chapter 1 of the supplement to NBC. Here are some examples of each zone: Entry

Acceleration-Related Zone

0

Calgary, Alberta

1

Toronto, Ontario

2

Saint John, New Brunswick

3

Varennes, Quebec

4

Vancouver, British Columbia

5

Duncan, British Columbia

6

Port Hardy, British Columbia


6-34

General Vessel Data


NBC Seismic Data

Velocity Zone

Select the zone indicating the velocity-related seismic zone. For locations in Canada, the velocity and acceleration seismic zones are found in the city list, Chapter 1 of the supplement to NBC. Here are some examples of each zone: Zone

Velocity-Related Zone

0

Steinbach, Manitoba

1

Calgary, Alberta

2

Montreal, Quebec

3

Quebec City, Quebec

4

Dawson, Yukon

5

Victoria, British Columbia

6

Destruction Bay, Yukon


General Vessel Data

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India’s Earthquake Standard IS-1893 RSM and SCM


India’s Earthquake Standard IS-1893 RSM and SCM Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. Importance Factor

The importance factor is taken from table 4 in the IS-1893 standard. This value ranges from a maximum of 6.0 to 1.0. •

6.0—A value typically used in nuclear applications.

•

2.0—Dams of all types and lethal service applications

•

1.5—Used in the design of important structures such as hospitals, tanks, water towers, and large assembly structures.

•

1.0—All others

Soil Factor

The soil factor (Beta) is taken from Table 3 of the IS-1893 seismic design code. This value ranges between 1 and 1.5. •

Type I soils and hard rock should have a value of 1.

•

Type II soils should also use a value of 1 except for well foundations or isolated RCC footings without tiebeams or unreinforced strip foundations which receive a value of 2.0.

•

Type III soils can receive a value between 1.0 and 1.5.

Zone Number

The zone number ranges between 1 and 5 and depends on where the vessel will operate in India. You can determine the zone from a colored map of which is Figure 1 in IS 1893. Period of Vibration

This field is optional. PVElite computes the natural frequency of the vessel and can thus compute the period of vibration. If this field is not 0 the program will use the entered value. This value is used in conjunction with Beta in order to determine Sa/g. Damping Factor

This value which is used with the period of vibration to determine Sa/g. Values of damping in the IS 1893 standard are 2, 5, 10 and 20 percent. The program will interpolate for intermediate values in between 2, 5, 10 and 20 percent. Extreme values will be used if a damping factor is entered which is outside the range above.

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General Vessel Data


ASCE-95 Seismic Data

ASCE-95 Seismic Data Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. Importance Factor

ASCE-95 does not address an importance factor. However, this value is multiplied times the other values to compute the base shear. Thusly, this entry can be used as a scale factor for the base shear. If you do not wish to use this value simply enter a value of 1.0. Force Factor ( R )

This value is taken from table 9.2.7.5. For vertical vessels, towers, stacks etc. this value is 2.0. Seismic Coefficient Ca

This value is derived from table 9.1.4.2.4A on page 55 of ASCE7-95. This factor is a function of the soil profile type and the value of Aa. Typically this will be a given value. However, if given the soil type and the value Aa, you will need to pick Ca from the table. Seismic Coefficient Cv

This value is derived from table 9.1.4.2.4B on page 55 of ASCE7-95. This factor is a function of the soil profile type and the value of Aa. Typically, this will be a given value. However, if given the soil type and the value Aa, you will need to pick Ca from the table. The help facility in PVElite contains the above referenced tables.

General Vessel Data

6-37

UBC 1997 Earthquake Data


UBC 1997 Earthquake Data Percent Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you can not predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. UBC Earthquake Importance Factor

Enter the value of the UBC Importance Factor. Please note the program will use this value directly without modification. This value is taken from Table 16-K of the UBC 1997 standard. The following is the context of Table 16-K. Category Value

1 - Essential facilities 1.25 2 - Hazardous facilities 1.25 3 - Special occupancy structures 1.0 4 - Standard occupancy structures 1.0 UBC Seismic Coefficient CA

Enter the value of CA per the project specifications and table 16-Q of UBC 1997 edition. This value is a function of the seismic zone Z, and the soil profile type. This coefficient ranges from 0.44 to 0.06. In zone 4 this value is also a function of Na. UBC Seismic Coefficient CV

Enter the value of CV per the project specifications and table 16-R of UBC 1997 edition. This value is a function of the seismic zone Z, and the soil profile type. This coefficient ranges from 0.96 to 0.06. In zone 4 this value is also a function of Nv. UBC Near Source Factor

This factor is only used in UBC Seismic Zone 4. This value ranges from 1 to 2 and is a function of the distance relative to the seismic source. UBC Seismic Zone

See UBC-91 Figure No. 23-2 to select the appropriate zone. The zone establishes the Seismic Zone Factor, Z, found in Table No. 23-I.

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•

Zone 0 - Gulf and prairies (Z=0.00)

•

Zone 1 - Rockies and Appalachian areas (Z=0.075)

•

Zone 2a - New England, Carolinas, and Ozarks (Z=0.15)

•

Zone 2b - Valley area west of the Rockies and the Pacific Northwest (Z=0.20)

•

Zone 3 - Sierras (Z=0.30)

•

Zone 4 - California fault areas (Z=0.40)

General Vessel Data


UBC 1997 Earthquake Data

Note that Zone 0 indicates the least chance of a major earthquake, while Zone 4 indicates the greatest chance of an earthquake. UBC Horizontal Force Factor

Enter the seismic force factor R per UBC Table 16-P 1997 edition: •

2.2 - Tanks on braced or unbraced legs

•

2.9 - Distributed mass cantilever structures such as stacks, chimneys, silos, and skirt supported vertical vessels.

R is defined as the numerical coefficient representative of the inherent overstrength and global ductility of lateral force resisting systems.

General Vessel Data

6-39

Seismic Load Input in G’s


Seismic Load Input in G’s Enter the value of g’s that your vessel will be subjected to in the specified direction. For vertical vessels, the horizontal component used will be the maximum of the Gx and Gz values. The horizontal force computed will be equal to the element’s weight times this maximum G factor. This force times its distance to the support will be computed and summed with all of the others. The Y component is also considered. This value is usually 2/3 of the Gx or Gz value, but note however any of these values can be zero. For horizontal vessels, the lateral (Gz) and longitudinal (Gx) directions are considered independently. The vertical load component (Gy) acting on the saddle supports is also computed. Typical values of G loads are from 0 to 0.4.

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General Vessel Data


Rev. A

IBC-2000 Earthquake Parameters

IBC-2000 Earthquake Parameters Selection of this option performs a seismic analysis according to the requirements of the International Building Code 2000 (which happens to mirror those of ASCE 7). EarthQuake Parameters Ss and Sl

The values for Ss and Sl are taken from the ASCE 7-98 / IBC 2000 publication. These factors are for short and long periods (0.2 and 1.0). These tables are found on pgs. 100 - 117 (ASCE 98), page 351 (IBC) publication. Response Modification Factor R

Enter the value from table 9.5.2.2 (ASCE) 1617.6 (IBC) as required. R is usually equal to 2.5 for inverted pendulum systems and cantilevered column systems. For elevated tanks use a value of 4. For horizontal vessels, leg supported vessels and others use a value of 3.0. Importance Factor

This is the occupancy importance factor as given in 9.1.4 (ASCE) 1604.5 (IBC). The importance factor accounts for loss of life and property. This value typically ranges between 1.0 and 1.5. Moment Reduction Factor Tau

This value is used to reduce the moment at each level. A value greater than one will scale the moments up, while a value that is less than one will lower the moments. We suggest a value of 1.0. This value should not be less than 0.8. Seismic Design Category

Select an appropriate category from the pulldown. The choices are A through F. The program uses these values only to check the minimum value of Cs per equation 9.5.3.2.1-4 (ASCE), 1615.1.1 (IBC). This additional check is only performed if the Seismic Design Category is E or F. EarthQuake Parameters Fa and Fv

Enter the coefficient from table 9.4.1.2.4A or 9.4.1.2.4B (ASCE), 1615.1.2(1) or 1615.1.2(2) (IBC) as required

General Vessel Data

6-41

IBC-2000 Earthquake Parameters


Rev. A

Table—9.4.1.2.4.A Values of Fa as a Function of Site Class and Mapped Short-Period Maximum Considered Earthquake Spectral Acceleration Site Class

Ss<+0.25

Ss=0.5

Ss=0.75

Ss=1.0

Ss>1.25b

A

0.8

0.8

0.8

0.8

0.8

B

1.0

1.0

1.0

1.0

1.0

C

1.2

1.2

1.1

1.0

1.0

D

1.6

1.4

1.2

1.1

1.0

E

2.5

1.7

1.2

0.9

a

F

a

a

a

a

a

Table—9.4.1.2.B (ASCE) 1615.2(2) (IBC), Values of Fv as a function of Site Class and Mapped 1-Second Period Maximum Considered Earthquake Spectral Acceleration Site Class

Sl<+0.1

Sl=0.2

Sl=0.3

Sl=0.4

Sl>0.5b

A

0.8

0.8

0.8

0.8

0.8

B

1.0

1.0

1.0

1.0

1.0

C

1.7

1.6

1.5

1.4

1.3

D

2.4

2.0

1.8

1.6

1.5

E

3.5

3.2

2.8

2.4

a

F

a

a

a

a

a

Note

For intermediate values, the higher value of the straight line interpolation shall be used to determine the value of Ssor Sl.

a

Site specific geo-technical information and dynamic site response analyses shall be performed. b Site specific studies required per Section 9.4.1.2.4 may result in higher values of than included on hazard maps, as may the provisions of Section 9.13.

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General Vessel Data


Rev. A

Response Spectrum

Response Spectrum Selecting this method performs a dynamic analysis of the vessel, applying loading based upon the selected seismic Response Spectrum. Initially, the vessel is modeled as a 2- dimensional structure (note that for asymmetric leg arrangements, the horizontal direction of interest is taken as that corresponding to the weakest axis of the arrangement). Next an eigensolution is performed on the vessel, which determines system mode shapes and modal natural frequencies (all modes with natural frequencies up through 100 HZ are calculated). The seismic response of each mode is then extracted from the Response Spectrum according to the natural frequency of each mode, and then adjusted according to the mode’s "participation factor". The system response is then determined by combining all of the modal responses. For tall structures, this analysis gives a much more accurate calculation than the typical static equivalent method. Usually the computed loads are lower in magnitude than those computed using conventional building Code techniques.

Seismic for Hydrotest

Enter the percent of the total seismic horizontal force which is to be applied during hydrotest. Although you cannot predict an earthquake, as you can high winds, some designers use a reduced seismic load for hydrotest on the theory that the odds of an earthquake during the test are very low, and the hazards of a water release small. Response Spectrum Name

The following seismic response spectra are available:

General Vessel Data

6-43

Response Spectrum


User Defined

This option allows the user to enter a custom seismic response spectrum of type Frequency or Period vs. Displacement, Velocity, or Acceleration (see instructions below). The same spectrum will be applied in both the horizontal and vertical directions. El Centro

This response spectrum is based on the May 18, 1940 El Centro, California earthquake, North-South component, 5-10% damping as described in Introduction to Structural Dynamics by John Biggs. This spectrum will be applied in both the horizontal and vertical directions. ASCE

Selection of this option performs a seismic analysis according to the requirements of the modal analysis procedure of ASCE Standard 7-98. The horizontal spectrum is a built according to the ASCE-7 Section 9.4.1.2.6, while the vertical spectrum provides a flat acceleration of 0.2S IBC

Selection of this option performs a seismic analysis according to the requirements of the modal analysis procedure of the International Building Code 2000 (which happen to mirror those of ASCE-7). The horizontal spectrum is built according to IBC-2000 Section 1615.1, while the vertical spectrum provides a flat acceleration of 0.2 (as per IBC-2000 Section 1617. 1). 1.60D.5

Selection of this option applies (in the X- and Y-directions respectively) the horizontal and vertical spectra specified in the United States Nuclear Regulatory Commission’s Regulatory Guide 1.60, for systems with 0.5% of critical damping. Note that this spectrum is normalized, so it must be scaled the site’s Zero Period Acceleration (see below). 1.60D2

Selection of this option applies (in the X- and Y-directions respectively) the horizontal and vertical spectra specified in the United States Nuclear Regulatory Commission’s Regulatory Guide 1.60, for systems with 2 % of critical damping. Note that this spectrum is normalized, so it must be scaled the site’s Zero Period Acceleration (see below). 1.60D5

Selection of this option applies (in the X- and Y-directions respectively) the horizontal and vertical spectra specified in the United States Nuclear Regulatory Commission’s Regulatory Guide 1.60, for systems with 0.5% of critical damping. Note that this spectrum is normalized, so it must be scaled the site’s Zero Period Acceleration (see below). 1.60D7

Selection of this option applies (in the X- and Y-directions respectively) the horizontal and vertical spectra specified in the United States Nuclear Regulatory Commission’s Regulatory Guide 1.60, for systems with 7% of critical damping. Note that this spectrum is normalized, so it must be scaled the site’s Zero Period Acceleration (see below).

6-44

General Vessel Data


Response Spectrum

1.60D10

Selection of this option applies (in the X- and Y-directions respectively) the horizontal and vertical spectra specified in the United States Nuclear Regulatory Commission’s Regulatory Guide 1.60, for systems with 10% of critical damping. Note that this spectrum is normalized, so it must be scaled the site’s Zero Period Acceleration (see below). Importance Factor

This is used for the ASCE and IBC options. FOr ASCE, this is the I, the occupancy importance factor determined from ASCE-7 Section 9.14. For IBC, this is the Ie, the occupancy importance factor in accordance with IBC 1616.2. Shock Scale X|Y dir

This is used for User defined, El Centro, and the 1.60Dxx spectra; and is used to scale the horizontal and vertical spectra respectively. For example, many seismic specifications require that the vertical spectrum be identical to, but with 2/3 of the magnitude, of the horizontal spectrum. This corresponds to an X scale of 1.0 and a Y scale of 0.6667. Traditionally in the analysis of vertical vessels, the component in the vertical direction is typically ignored. If you wish to do so, enter a value of 0 in the Y direction field. Zero Period Acceleration

This is used to scale the normalized 1.60 Dxx spectra. The Zero Period Acceleration corresponds to the acceleration of the rigid (high frequency) portion of the spectrum, which usually corresponds to the maximum ground acceleration expected at the site. Combination Method

Modal responses must be combined in a way that most accurately captures the statistical correlation of the responses to each other. The available options are: •

SRSS: This method performs a Square Root of the Sum of the Squares combination of the modal results. This simulates a response where all modal results are assumed to be uncorrelated with, or totally unrelated to, each other. If the ASCE or IBC method has been chosen, modal combinations will automatically be performed using this method. This is usually non-conservative, especially if there are any modes with very close frequencies, since those modes will probably experience their maximum DLF at approximately the same time during the load profile.

•

General Vessel Data

Group: This method performs a group combination method as described in the United States National Regulatory Commission’s Regulatory Guide 1.92 - responses of modes with natural frequencies within 10% of each other are combined using the Absolute Value method, while those sums are combined with each other and with m0ore far-flung modes, using the SRSS method. This simulates a response where the

6-45

Response Spectrum


results of similar modes are assumed to be correlated, while those of all dissimilar modes are assumed to be uncorrelated. •

Absolute: This method performs an Absolute Value combination of the modal results. This simulates a response where all modal results are assumed to be correlated with each other. This method gives the most conservative result, since it assumes that the all maximum modal responses occur at exactly the same time during the course of the applied load. This is usually overly-conservative, since modes with different natural frequencies will probably experience their maximum DLF at different times during the load profile.

Acc.Based Factor Fa:

This factor is required for ASCE-7 and IBC, and is used to construct the horizontal response spectrum. For ASCE-7 it is determine from Table 9.4.1.2.4a, while for IBC2000 it is determined from Table 1615.1.2(1). Typical values are 0.8 through 2.5 and above. For more information on the values of Fa refer to IBC 2000 Earthquake Parameters in this chapter. Acc Based Factor Fv:

This factor is required for ASCE - 7 and IBC, and is used to construct the horizontal response spectrum. For ASCE-7 it is determine from Table 9.4.1.2.4a, while for IBC2000 it is determined from Table 1615.1.2(2). Typical value are 0.8 through 3.5 and above. For more information on the values of Fv refer to IBC 2000 Earthquake Parameters in this chapter. Max. Mapped Res. Acc. Ss:

This factor, the "mapped maximum considered earthquake spectral response acceleration at short periods" is required for ASCE-7 and IBC, is used to construct the horizontal response spectrum. For ASCE-7 it is determined in accordance with Section 9.4.1, while for IBC-2000 it is determined from Section 1615.1. Typical values are 0.0 through 2.0g. Max. Mapped Res. Acc. Sl:

This factor, the mapped maximum considered earthquake spectral response acceleration at a period of 1 second", is required for ASCE-7 and IBC, is used to construct the horizontal response spectrum. For ASCE-7 it is determined in accordance with Section 9.4.1, while for IBC-2000 it is determined from Section 1615.1. Typical values are 0.0 through 1.5g. Response Modification R:

This factor is required for ASDCE-7 and IBC, and is used to reduce the spectrum response. For ASCE-7 it is determined from Table 9.5.2.2, while for IBC-2000 it is determined from Table 1617.6 Typical values are 1.25 through 8.0. For elevated tanks use a value of 4. For horizontal vessels, leg supported vessels and others use a value of 3.0.

6-46

General Vessel Data


Response Spectrum

Coefficient Cd:

This factor, the "deflection amplification factor", is used to scale up the calculated seismic displacements. For ASCE-7 it is determined from Table 9.5.2.2, while for IBC-2000 it is determined from Table 1617.6. Typical values are 1.25 through 6.5. Range Type:

User Defined spectra may be enter with a range X axis representing either Frequency or Period. In either case, the data points should be entered with ascending range values.

Note

A zero entry for either Frequency or Period is invalid. Interpolation will be made linearly for intermediate range values. Data points defining the spectrum can be entered by clicking Edit/Review Spectrum Points.

Ordinate Type:

User Defined spectra may be entered with an ordinate Y axis representing Displacement, Velocity, or Acceleration entered in units of Diameter, Diameter /second, of G’s respectively. Interpolation will be made linearly for intermediate Ordinate values. Data points defining the spectrum can be entered by clicking Edit/Review Spectrum Points. Include Missing Mass Components:

Since only a limited number of modes of vibration i.e., only those with natural frequencies up to 100 HZ or so are used in the analysis, the entire mass of the structure doesn’t get considered in the seismic analysis. Clicking this box causes PVElite to estimate the contribution of the neglected modes of vibration and add that to the dynamically calculated response.

Note

General Vessel Data

Selecting this option should always lead to a more conservative result.

6-47

Response Spectrum

6-48


General Vessel Data


&KDSWHU PVElite Analysis

Once all the data for the vessel model and analysis have been entered and corrected, the model is ready for analysis. The pull-down menu under Analyze shows two options: •

Analyze

•

Error Check Only

Error Check Only will review all the data and produce an output report listing any errors that are found. These messages can be examined through the Output - Review option. If Analyze is selected, PVElite will also run through the error checker but then continue on (if no errors are found) through the complete analysis. The analysis program is the heart of the PVElite system. All the data entered into the model is used by the analysis program to evaluate or design the pressure vessel. In any given analysis there will be between 16 and 20 analysis steps. As the program completes each calculation, important information from the step is displayed on the screen. The screen display at the completion of the internal pressure calculations, for example, lists both the given element thickness and the required thickness for each element in the vessel. The program waits for a user response before clearing the screen and moving on to the next analysis step. The user may respond by continuing on to the next step, continue nonstop through the remainder of all analysis steps, or quit the analysis. The results of the analysis are stored in two separate files on the hard disk. The text results of the job are held in a file with the extension .TAB (e.g. the jobname VES01 will have an input file named VES01.PVI and a text results file of VES01.TAB) The output processor replaces this .TAB file with a .T80 file (VES01.T80). The .T80 file contains a complete report for each analysis step for inspection and printing through the Review processor. The analysis also creates a .PVR file (e.g.. VES01.PVR); this file is used by the output Review processor for component analysis. The program transfers to the Review processor at the completion of the analysis. PVElite not only analyzes vessels, it also designs vessel walls for pressures and loads. In addition to increasing the vessel wall thickness, the program can instead introduce stiffener rings to accommodate external pressures. The program directives for these design modifications are set in each job in the Design Data section of Global Data. In increasing the wall thickness to meet the required values, PVElite can either set the thickness to the

PVElite Analysis

7-1


exact requirement, or, round up to the next nominal value (1/16 inch in English units or 1 mm in metric units). This switch, too, is a setting in the Configuration option under Utility. If PVElite’s design process changes any of the original input, the program will automatically erase the current output report and return to the beginning of the analysis and restart the run. All results will reflect the design changes, from the input echo to the added deadweight. The user’s original input, however, will not be changed. If a design flag is turned on and the required thickness is less than the entered thickness, PVElite will increase the thickness as needed and continue.

7-2

PVElite Analysis


Steps for Calculating and Displaying Vessel-Analysis Re-

Steps for Calculating and Displaying Vessel-Analysis Results Each of these steps calculates and displays specific results of the vessel analysis. Here is a brief description of the key analysis steps: Step 0: Error Checking

Most of the errors that are easily made will have already been caught by the input program. However, there are some errors which can only be discovered after the analysis begins. There are also some warnings that may be of help to the user. This first routine check creates a report in the output. If any of the input errors would prevent the program from running, execution stops right here. Check the output to determine the exact error discovered by the program. Step 1: Input Echo

PVElite provides a very complete listing of your input. This includes the geometry and materials for each element (head, shell, cone, flange, skirt, etc.) and the information for any details attached to that element. Step 2: XY Coordinate Calculations

The program simply calculates the X and Y locations of the first end of every element. Step 3: Internal Pressure Calculations

The geometry, material, and loading data from your model are used to calculate the required thickness and maximum allowable working pressure for each element (except skirts and flanges). The calculations are done using the ASME Code, Section VIII, Division 1 rules, or the British Standard PD:5500 rules. The internal design pressure at any point is taken to be the given design pressure for that element, plus the pressure due to liquid head, if any. If you checked the design flag ‘increase thickness for internal pressure’ and any element is too thin for the given pressure, the program will automatically (or under interactive control) increase the thickness of the element. There is a computation control (under Utilities on the Main Menu) that allows you to increase the element thickness to exactly that required, or to round the thickness up to the next nominal size. If the program has increased the thickness, it will recalculate all the required thicknesses and maximum allowable working pressures for the vessel, and create a new table showing these results. After the internal pressure calculation is complete, PVElite prints the formulas and substitutions, as well minimum design metal temperatures for the elements. Step 4: Hydrotest calculations

The user specifies what kind of hydrotest (and/or the hydrotest pressure) on the global input screens. The program uses this information to calculate the maximum allowed hydrotest pressure and required thickness at the given pressure for each element. Step 5: External Pressure calculations

Two of the three key variables for external pressure calculations are explicitly defined by the user: diameter and thickness. The third variable, length of section, is calculated by the

PVElite Analysis

7-3

Steps for Calculating and Displaying Vessel-Analysis Results


program for the given geometry. Thus if the vessel has two heads and some number of cylindrical elements with no stiffening rings, the program will calculate the design length for each cylinder using the full length of the vessel plus 1/3 the depth of the heads. If there are stiffening rings, the program will calculate an appropriately shorter value. The program displays the formulas and substitutions for the external pressure calculations on each element. Then the same results are displayed in tabular form. If the element is not thick enough for the external pressure (and you checked the design boxes in the input) the program will allow you to increase the thickness and/or add stiffening rings (which are created automatically and added to your model). If the thickness is increased the program has to go all the way back to step 3. For rings it simply repeats this step with the new lengths. British Standard PD:5500

When performing the PD:5500 external pressure calculations, the program first computes the length of section for the given geometry. The length of section is either the distance between stiffeners, or, if there are no stiffeners, it is the full length of the vessel plus 0.4 times the depth of the heads. Using the length of section computed, the program first tests to see whether the thickness of the unsupported cylinder (or distance between supports) is satisfactory for the given pressure. A value of Pmax is determined. If there are stiffeners, then the program performs the calculations described in section 3.6.2.3. The program first performs the computations described in Method A, and then performs the more rigorous calculations described in Method B. For each of these methods (and each value of n), a value of Pn and Fn are obtained. Pn is the elastic instability pressure of the stiffened cylinder or cone. The value of Pn must not be less than 1.8*Pext in the case of fabricated or hot formed stiffeners and 2.0*Pext in the case of cold formed stiffeners. Fn is the maximum stress in the stiffener flange divided by the yield stress of the stiffener. A value for Fn is computed for both fabricated or hot formed stiffeners and cold formed stiffeners. These values must be between 0.0 and 1.0. Step 6: Weight of Elements

Element weights are calculated in both the corroded and uncorroded conditions. Note that for heads the distance given in the input program is taken as the length of the straight flange on the head. This step also calculates the volume of the element. Step 7: Weight of Details

Each detail has a separate weight calculation. Of note is the fact that partial volumes of liquid in both heads and cylinders and in both the horizontal and vertical directions are correctly calculated. Step 8: ANSI Flange MAWP

If you entered nozzles, you specified the material and class of the attached flanges. PVElite has the full ANSI flange tables built in, and tells you the rating of the flanges at the operating temperature.

7-4

PVElite Analysis



Steps 9 and 10: Total weight and detail moment

Several weight cases are calculated including: empty, operating, and hydrotest. The various detail weights/loads are included in the following cases: Detail:

Empty

Operating

Hydrotest

Saddle

9

9

9

Platform

9

9

9

Packing

9

Liquid

9

Insulation

9

9

9

Lining

9

9

9

Rings

9

9

9

Nozzles

9

9

9

9

Trays Legs

9

9

9

Lugs

9

9

9

Weight

9

9

9

Forces/Moments

9

This step also calculates the moment due to individual detail which may not be on the centerline of the vessel. These are usually small. Finally, this step calculates the forces at the support. The vertical force and bending moment (due to detail weights only) are calculated for the ‘one support’ cases (skirts, legs, lugs) and the vertical force at each support is calculated when there are two saddle supports. Note : In addition to computing the above weights PVElite also computes the fabricated weight, shop test weight, shipping weight, erected weight, empty weight and field test weight. The computed weights may or may not include removable or field installed items such as packing and other details. You can specify where these details are to be installed (either shop or field) in the Global Input. Simply switch to the global input screen and click the Installation Miscellaneous Options button located on the button bar at the top of the screen. By default the program assumes that all details will be installed in the shop and calculate these various weights based on that assumption. The cumulative weight on the vessel will look drastically different for horizontal vessels on saddle supports than for vertical vessels on skirts, legs, and lugs: Horizontal cases: Expect the highest weight forces near the saddles, with almost no weight force at the ends or in the middle. Vertical cases: Expect the weight forces to increase from zero at the top to a maximum at the support. If there are elements below the support, expect the weight force to be negative. The cumulative moment includes only the moment due to eccentric details, and is usually quite small (except in the case of a large applied moment).

PVElite Analysis

7-5

Steps for Calculating and Displaying Vessel-Analysis Results


Step 11: Natural Frequency Calculation

PVElite uses two classical solution methods to determine the first order natural frequencies of vessels. For vertical vessels, the program uses the Freese method, which is commonly used in industry. For horizontal vessels a similar method attributed to Rayliegh and Ritz is used. Each method works by calculating the static deflection of the vessel (for vertical, the vessel as a horizontal cantilever beam). The natural frequency is proportional to the square root of the deflection. Note that the screen display shows only the deflection you must look at the output to see the frequency. Step 12: Wind Load Calculation

PVElite uses the rules of ASCE-7, NBC, UBC, and IS-875 to calculate wind loads. Each of these codes uses a basic wind pressure, a function of the velocity squared, along with several surface and site factors to determine the final wind pressure. Step 13: Earthquake Load Calculation

The five codes used by PVElite - ASCE-7, UBC, NBC, IS-1893 RSM and IS-1893 SCM each use a static equivalent load to model the earthquake load. Simple site data and loading data are used to determine an expected static equivalent horizontal load on the vessel. Step 14: Shear and Bending Moments due to Wind and Earthquake

These loadings generate horizontal loads, which are usually fine on a horizontal vessel, but can cause high overturning moments on a vertical vessel. The program calculates the cumulative shear and bending moment on the vessel, for use in later stress calculations. Step 15: Wind Deflection

PVElite calculates the deflection at every point in either horizontal or vertical vessels. Step 16: Longitudinal Stress Constants

As the program prepares to do structural calculations on the vessel, it first calculates the cross sectional area and section modulus of each element in both the corroded and uncorroded condition. Step 17: Longitudinal Allowable Stresses

There are four allowable stresses in the longitudinal direction for each element: (1) Longitudinal tension based on the basic allowable stress, often multiplied times 1.2 (as specified on the global input), (2) Hydrotest longitudinal tension - 1.5 times the allowable stress new & cold. (3) Longitudinal compression - based on paragraph UG-23 of the Code, and the material’s external pressure chart. (4) Hydrotest allowable compression - the basic allowable compression new & cold, multiplied by 1.5. Step 18: Longitudinal stresses due to . . .

Each load (wind, earthquake, weight, pressure) generates a stress. These are calculated individually and displayed by this routine. Note that bending stresses, though only displayed once, are actually positive on one side of the vessel and negative on the other. Step 19: Stress due to Combined Loads

In this step the various load cases combinations defined by the user are evaluated.

7-6

PVElite Analysis



There can be as many as twelve cases, combining pressure loads, weight loads, and moments in various ways. A fairly complete set of load cases is included as a default:

Load Case

Definition

1

NP+EW+WI+FW

No pressure + empty weight + wind

2

NP+EW+EQ+FS

No pressure + empty weight + earthquake

3

NP+OW+WI+FW

No pressure + operating weight + wind

4

NP+OW+EQ+FS

No pressure + operating weight + earthquake

5

NP+HW+HI

No pressure + hydrotest weight + hydro wind

6

NP+HW+HE

No pressure + hydrotest weight + hydro earthquake

7

IP+OW+WI+FW

Internal pressure + operating weight + wind

8

IP+OW+EQ+FS

Internal pressure + operating weight + earthquake

9

EP+OW+WI+FW

External pressure + operating weight + wind

10

EP+OW+EQ+FS

External pressure + operating weight + earthquake

11

HP+HW+HI

Hydrotest pressure + hydrotest weight + hydro wind

12

HP+HW+HE

Hydrotest pressure + hydrotest wind + hydro earthquake

13

IP+WE+EW

Internal pressure + wind empty + empty weight

14

IP+WF+CW

Internal pressure + wind filled + empty weight NO CA

15

IP+VO+OW

Internal pressure + vortex shedding (OPE) + operating weight

16

IP+VE+OW

Internal pressure + vortex shedding (EMP) + operating weight

17

IP+VF+CW

Internal pressure+ vortex shedding (Filled) + empty weight no ca

The difference between wind loads and hydrotest wind loads is simply a ratio (percentage) defined by the user. This percentage is specified in the Wind Data definition of Global Data - usually about 33% (thus setting the hydrotest wind load at 33% of the operating wind load). Likewise, the hydrotest earthquake load is a percentage of the earthquake load; this percentage is defined in the Seismic Data definition of Global Data. Some steps that are not applicable for horizontal vessels, such as natural frequency, will not be printed. Also, if a vessel has no supports, steps greater than 10 will not be computed.

PVElite Analysis

7-7

Optional Steps


Optional Steps PVElite includes two analyses that are done under specific circumstances: 1. Cone evaluation - cones are evaluated for internal and external pressure at the large and small ends, and any stiffening rings near the cones are included and evaluated. 2. Zick stresses - stresses due to saddle supports are evaluated and compared to allowable stresses using the method of L.P. Zick. Note that the stresses are calculated for each saddle, since in PVElite each saddle can have different loading. Note also that the stresses are not evaluated at the mid span, since the program automatically does that for all the various load case combinations. 3. AISC Leg Check: After the program has computed all of the weights, forces and moments, it can then determine the overall state of stress by using the AISC unity check method. The program typically looks at the worst loads on the legs due to wind or seismic in the operating condition and then applies the AISC method of checking the legs. The unity check must be less than or equal to 1.0. Most typical designs fall in the 0.7 - 0.8 range, which is a good check both in terms of economy and safety. 4. Lug Support Check : In a similar manner to the leg check the program gathers the worst loads on the support lugs and then evaluates them according to a set of acceptable standards. In this case, gussets are checked by the AISC method and the lug plates are checked by common industry standard methods. These methods are outlined in common pressure design handbooks. 5. Baserings: With known forces and moments at the base and the geometry of the basering, PVElite will analyze or design the basering and gusset geometry. 6. Flanges: For main body flanges, the program will compute the required thickness of the flange, all relevant stresses, and MAWP for the given geometry. The results seen in the output are based on the input thickness. The program additionally computes the required thickness of the flange. Please note that the program does not include the forces and moments to determine an equivalent design pressure. There are separate fields in the input that can be entered in if these effects are to be considered. In order to do this two runs would have to made. After run 1 was made the forces and moments on the flange could be entered in as needed. 7. Nozzle Analysis : Complete nozzle evaluation is incorporated into the program based on the rules in the ASME code. Design cases are made for Internal Pressure, External Pressure and MAPnc. The internal pressure can be based on the MAWP of the entire vessel or the exact pressure at the nozzle location. These options are located in the Global Input section of the input. In addition to perpendicular nozzles, hillside geometries are also considered. Nozzles at any angle can be entered in by using the ANG=xx.x command in the nozzle description field. The nozzle analysis also computes MDMT, weld size and strength calculations along with provisions for large nozzles as outlined in appendix 1-7 of the ASME Code.

7-8

PVElite Analysis


Component Analysis

Component Analysis Once the program has completed the above calculations, the results may be reviewed in the output processor. These results (such as required wall thickness vs. finished wall thickness) may also be used for the evaluation of other components of the vessel. Rather than automatically analyzing all the possible vessel element details, the output processor provides component analysis for only those details selected by the user. Other details that are not part of the current vessel may also be analyzed here. This processor is described in the next chapter.

PVElite Analysis

7-9

Component Analysis

7-10


PVElite Analysis


&KDSWHU Output / Review

Generating Output Output may be reviewed or generated for any job that has some input. Results of any previous analysis, of course, are only available if the analysis has been run. To access the output, first bring up the proper job through the File item on the Main Menu bar. Then, clicking on Output on the Main Menu bar will produce a pull-down menu that controls the program’s output. The pull-down menu provides two options:

•

Review Report —Enters the Review processor where results of the analysis may be inspected on the screen, printed, or copied to a file.

•

Review the DXF File—Invokes a compatible DXF processor on the machine if one exists.

The remainder of this chapter will focus on the many capabilities of the Review processor.

Output / Review

8-1

The Review Screen


The Review Screen The body of the Review screen shows all the reports available for the current job or file. These reports follow the analysis steps described in the previous chapter. To select one or more reports, simply use the mouse and (CTRL) key to select one or more reports.

Once you have selected some reports, click on the Monitor icon to review them on the screen or press the Printer icon to print them.

Note

8-2

Once a report has been selected for screen viewing, it can be edited just as if it were in a word processor. Comments can be added for clarity and entire lines and parts of reports can be deleted or rearranged.

Output / Review


Using Review

Using Review The following screen shows a selected report:

Below is an on-screen display of the Internal Pressure Report.

Output / Review

8-3

Component Analysis


Component Analysis Analysis of vessel details is initiated from the Input Menu.

8-4

Output / Review


Component Analysis

The units for the component analysis are extracted from the current vessel input. In the example here, Half Pipes Jacket was selected. The initial screen is shown below.

To produce a report, click the Analyze Current Item icon.

Analyze Current Item icon

Output / Review

8-5

Component Analysis

8-6


Output / Review


&KDSWHU Component Analysis Tutorial

Purpose of This Chapter This purpose of this chapter is to explain the basics of the PVElite component analysis operation by guiding you through one application of it. Each of the main menu choices used to control the program is described and illustrated. In addition, certain comments on how things are made in this chapter and not elsewhere. Use of the PVElite program assumes that the software has been installed as per the instructions detailed in Chapter 2.

Starting the PVElite Component Analysis Module The PVElite Component Analysis program may be started by selecting Component Analysis Data... from the Input option on the main menu. At this point the Main Menu is loaded.

PVElite Component Analysis Main Menu

Component Analysis Tutorial

9-1

Component Analysis Main Menu


Component Analysis Main Menu PVElite always starts with the Vessel Data Input Screen. Across the top of this screen is a line of items which is called the Main Menu. The Main Menu controls the major functions of the program. This chapter will review the functions available in each of these menu items. The items in the Main Menu - File, Edit, Analyze, Output, Tools, Diagnostics, ESL, View and Help - may be selected with a mouse click or by pressing the underlined character while pressing the Alt key. For example, the Output processor may be selected by pressing the Alt and O keys simultaneously. First, we will begin by going over each of the Main Menu items.

File Menu

File Menu

9-2




The File Menu controls the general operations of PVElite files. Options that are displayed in the menu with an ellipsis (…) cause a file manage window to appear when selected. The File Menu may be used to New

•

New - Start a new file.

New Dialog

Open

•

Open - Open a previously created file.

Open Dialog


9-3



When the Open option is chosen, the user is prompted to select an existing job file. Files of type *.cci will be displayed for selection. Save

•

Save - Save the current file in its present condition.

Save As Dialog

Print

•

Save As - Save a file that has not been previously named or save the current file under another name.

•

Print - Send the current vessel graphic image directly to a postscript or laser jet printer.

•

Print Preview - Display the page that will be sent to the printer (see above).

•

Print Setup - Display the standard Windows printer setup screen.

•

Exit - Exit PVElite. A message window will appear to give the user a last opportunity to save any modifications to the current job.

The File Menu will also list the last four vessel input files. Any of these files may be opened with a mouse click.

9-4



Edit Menu

Edit Menu

Edit Menu

Once a file is selected, the Edit Menu indicates the options available for editing. The Edit Menu may be used to •

Title Page - Enter report title for a report.

•

Insert Default Title Page - Insert a

•

Project Data - Enter up to 3 title lines which appear at the top of each page of a printed report.

Add New New Item Insert Item

•

Add New Item - Add a new element.

•

Insert New Item - Insert a new element after the current element.

Insert New Item Delete Current Item

•

Delete Current Item - Delete the current element.

•

Select All - Select all of the items in the browse window.

Delete

•

Deselect All - Deselect all of the items in the browse window.

Current Item


9-5

Analysis Menu


Analysis Menu

Analysis Menu

The Analysis options enable the program to quit the input process and enter the analysis process. PVElite will first save the current job to the input file with the same filename, then process the analysis. The Analyze Menu may be used to

Analyze File Analyze Selected Item

9-6

•

Analyze Current Item- Perform calculations for the current analysis type. The analysis program looks for appropriate data in the current analysis file and performs calculations, saving the results in a text file. The results of the analysis will then be ready for display or printing.

•

Analyze File - Allows the analysis of the input file.

•

Analyze Selected Items - Perform calculations for selected analysis types. The calculations will be saved in a binary file and will be ready for display or printing.

•

Summary - Prepare a brief summary of data in the current analysis file.

•

Choose Analysis Type - Select the type of component you wish to work on.



Analysis Menu

Choose Analysis Type Menu

The analysis types chosen from this menu can also be selected from the Analysis Tool Bar by simply clicking on the icon.


9-7

Output Menu


Output Menu

Output Menu

The Output option allows the user to review the analysis results and print the graphics of the vessel. The Output Menu may be used to •

9-8

Review - Review the analysis results of the current job, if those results are available.



Tools Menu

Tools Menu

Tools Menu

The Tools Menu controls the utility processors as summarized here.

Configuration •

Configuration - This option allows the user to define a variety of system variables for the program. The first screen of the Configuration menu looks like this:

Computation Control Tab

The Computation Control Tab lets some specific program computation control parameters be set. Following is a description of the options:

Compute Increased Nozzle Thickness? In many cases pressure vessels are designed and built long before the piping system is attached to them. This means that the nozzle loadings are unknown. If this field is checked, then your minimum nozzle thickness (trn) will be the maximum of: trn = (.134, trn for internal pressure) less than or equal Nps 18 trn = (OD/150, trn for internal pressure) greater than Nps 18 By using such a requirement in addition to UG-45, the piping designers will have some additional metal to work with to satisfy thermal bending stresses in systems these vessels


9-9

Tools Menu


are designed for. Note carefully, that these formulae are not in the ASME Code. They are used in industry. You can also specify the minimum wall thickness of the nozzle (Trn) in the Nozzle input. If you do so, that will override this calculation.

Calculate F in Flohead if the Pressure is Zero? In the design of Floating heads, a factor F is computed. The factor F is a direct function of the internal pressure. If the internal pressure is 0, then F is equal to 0. However, some interpret the Code to mean that F should always be computed regardless of which case we are analyzing. Typically, the case in question is the flange bolt up case. When bolting up the unit there is no internal pressure. That is why the default is not checked. If you wish F to always be considered in the thickness calcs, then check this box. This is conservative.

Use P instead of MAWP for UG-99B? The Code paragraph UG-99(b) discusses the subject of Hydrostatic test pressure on vessels. The equation that would normally be used is as follows : Test Pressure = 1.5 * MAWP * Stest/Sdesign (for A-98 addenda) Or Test Pressure = 1.3 * MAWP * Stest/Sdesign (for A-99 addenda & later) The code in note 35 states that if the MAWP may be assumed to be the same as the design pressure when calculations are not made to determine the MAWP. This will allow for lower test pressures. This directive should be used with caution.

Perform Area Calculations for Small Nozzles? The Code paragraph UG-36 discusses the requirement of performing area placement calculations when small nozzles are involved. The Code States: Openings in vessels not subject to rapid fluctuations in pressure do not require reinforcement other than that inherent in the construction under the following conditions: 3.5" finished opening in a shell or head .375 inches thick or less 2.375" finished opening in a shell or head greater than .375 inches If your geometry meets this criteria and this box is not checked, then no area of reinforcement calculations will be performed.

Print Water Volume in Gallons/Liters? Normally the volumes computed by the program are in diameter units. If you want to use US gallons instead of cubic diameter units check this directive. The program will use cubic units if the default value if it is not checked. For non-English units, the volume will be printed in liters if this box is checked.

Use Calculated Value of M for Torispherical Heads in UG-45 b1? The Code in paragraph UG-45 requires a calculation of the required head thickness at the location of the nozzle. This may lead one to believe that the thickness may be computed per paragraph UG-37. However a recent code interpretation states that the thickness should be computed by the rules of paragraph UG-32 or by the rules in Appendix 1.Thus, this directive should always be checked.

9-10



Tools Menu

Use Pre-1999 Addenda? As of January 2000, the 1999 addenda of the ASME Code is mandatory. This mandatory revision includes changes to the material properties of many materials used for Division 1 vessel construction found in Section 2 Part D. Namely, the allowable stresses were increased in certain ranges. PV Elite contains 2 databases of material properties. The default behavior is to use the current higher allowable stress database. If you are re-rating an older vessel to the pre-1999 addenda and would like to use the older material allowables, then you should check this box. Since the program uses this directive to connect to the database, it should be checked before any vessel modeling occurs. In case of an existing file, you must access the material database for each material on each element defined so far, to update material properties per the selected database. Other design codes will not be affected by this directive.

Use Code Case 2260? Code Case 2260 Approval Date: May 20, 1998. This Code Case is entitled "Alternate Design Rules for Ellipsoidal and Torispherical Formed Heads". It applies for Section VIII Division 1. If this flag is checked then CodeCalc will use the modified equations in the Code Case to compute the required thickness of Elliptical/Torispherical heads. The typical net result is that by using these modified rules, a thinner head will designed.

Select the Addenda for the Material Database. For Div, 1 the user can select between post 1999 material databases, up to the current addenda. The default behavior is to use the current addenda database. Miscellaneous Tab

The second screen of the Configuration Menu looks like this:

The Miscellaneous Tab of the Configuration Menu enables the user to select directives that controls printout style, and default unit options. Following is a description of the options:


9-11

Tools Menu


Report Content. This directive allows the user to change the length of the printed reports. When the summary option is checked, the formulas and substitutions will not be printed out. Thus, this option will generate less paper and more compact reports. When the detailed option is checked, the reports will be the normal length.

External Printout in Rows? There are 2 choices for the style of printing external pressure results; rows and columns. Printing the values row wise tend to reduce the length of the printouts. This is the default. If you wish to use the column wise printout, do not check this directive.

Reload last file at startup? Check this box to automatically load the last file you were working with when this processor is started.

Default units file. Select the system of units you typically prefer to work in. •

Set Unit - This option allows the user to change the current job’s units system. Once this option is selected, a File Open dialog will appear and allow the user to select a new units file. These units files have the extension .fil. English, Metric, Newton, Bars, and SI units are available in the system subdirectory. After you select a units file, the following window will appear:

If the units selection is acceptable, then click the OK button; otherwise, click Cancel. After OK is clicked, the current units will be overlayed with the selected units. •

9-12

Make Unit - This option allows the creation of a custom units file. Simply pull down the appropriate conversion constant or label and the corresponding unit or label will change accordingly. If your conversion constant is not one of the choices, enter the



Tools Menu

label and constant for your particular unit. (The program will continue to use English units internally).

Create a New Units File Dialog

This window presents a table of items, the internal units used for each item, a conversion factor, and the user units. The conversion factor is used to obtain the user units from the internal units. The up and down arrow keys can be used to move the selection to the desired item. If a desired unit conversion is not available as a default program selection, it can be entered manually by typing it in. Insure that your conversion constants are correct and that your labels go with the constants. Once all units have been set, press OK to exit this screen and save the new units file. A safe place to save it would be in the system subdirectory where the supplied units files are stored. After you have saved the new units file, you will need to overlay the current units in your job file with the new units. This option is the Set Unit option. After you set your file with the new units, all of the entered data will be converted into the new set of units immediately.


9-13

Tools Menu


•

Calculator - This option allows the user to perform simple calculations and paste the results in the input field in which the cursor resides.

Calculator

You can use the calculator to compute a number and transfer that number into PVElite by using the Edit, Copy feature. From the desired field, right click and choose the Paste option. Before pasting, ensure that the fields current contents have been removed. •

Units Conversion Viewer -

COADE Units Conversion Utility

9-14



•

Tools Menu

Edit/Add Materials - Allows you to add materials to the COADE Material database. The screen appears as follows:

User-Defined Material Editor Dialog

To use this processor, fill in all of the values in all cells. If more than one material is to be entered, use the Next button to enter the new material. After all materials have been entered, save the file with the Save button. Finally, press the Merge key to join the user defined material database with the supplied material database. •

Drawing Options - Allows the user to set the options for the graphics. Such as drawing line thickness, font and the background color.


9-15

Diagnostics Menu


Diagnostics Menu

Diagnostics Menu

The Diagnostics Menu helps to troubleshoot problem installations. The following options are available:

9-16

•

CRC Check - This option performs a cyclic redundancy check on each of the supplied PVElite files.

•

Build Version - This option checks the revision level of the PVElite executable files.

•

Error Review

•

DLL Version Check - This option checks to make sure the PVElite .dll files are current. Please note that if the dll’s are not current the program may behave in an unusual manner or may not run at all.

•

Register Servers - Sometimes the icons for various modules (Shells, Nozzles, Cones, etc. ...) are grayed out, the user can enter the path to the PVElite installation directory and select to register the DLLs. Then close the program and restart.(Does the icon become active after this happens?



ESL Menu

ESL Menu

ESL Menu

The ESL Menu gives access to utilities that interact with the External Software Lock. The options are as follows: •

Show Data - This option will display the data stored on the ESL.

•

Phone Update - This option will allow the user to obtain phone update authorization information or other ESL changes, to be made over the phone.

•

Generate Fax Codes - This option will provide the user with access codes for remote ESL updating. These access codes should be sent to COADE for authorization codes.

•

Enter Fax Authorization Codes - Choose this option to enter the remote authorization codes you received from COADE. Each set of four codes will make one change to the data stored on your ESL.

•

Check HASP Driver Status - This option provides information about the ESL device drivers.

•

Install HASP Device Driver - This option installs the ESL device drivers.


9-17

View Menu


View Menu

View Menu

The View Menu allows the user to move between the Input, Drawing, Quick Analysis, and Browse views.

9-18



Help Menu

Help Menu

Help Menu

The Help Menu displays on-line help and information on how to obtain technical support for PVElite. The options available are as follows: •

Help Topics - Starts the help facility.

•

Online Documentation - Opens the Users Guide in Acrobat Reader.

•

Desktop (online) Help - Starts an interactive help session with COADE personnel.

•

Tip of the Day - Provides tips for running PVElite.

•

Info - Provides information on the best ways to contact COADE personnel for technical support, and provides a link to COADE’s Web Site.

•

About This Program

•

On-Line Registration - Allows you to electronically register this product with COADE.

On-Line Registration screen


9-19

Performing an Analysis


Performing an Analysis The remainder of this chapter will help you perform an actual analysis using the Shell program. Start PVElite by clicking on the icon on the desktop or selecting the item from Programs. From the Input menu click Component Analysis Data.

New Add New Item

From the Main Menu click on File, New or click the New icon. This will allow you to specify the current analysis type. From the Analysis Toolbar, select Shells and Heads, then click the Add New Item icon. The following screen will appear:

Shell analysis can be defined on the Design Tab of this screen. You can use the Tab or Enter keys to move the cursor up and down the column of data. Notice also that many of the fields have default values built in. The first field on the input screen is the Item Number. A value must be entered in this field or the analysis will not be performed. We suggest that you number the different calculations sequentially. Enter a 1 in this field (type 1 and press [Tab]). The next field is for a description of the shell to be analyzed. This can be the part number or a short description of the part. This field is optional. For this tutorial, type in Spherical Head. The next block of fields concern the pressure and temperature. Tab to the Design Internal Pressure field and type 100 (assuming you are in English units). Now tab to the Design Temperature for Internal Pressure field and type 700. When you press Tab, the program will pause momentarily to check whether the material specified has allowable stresses greater than zero at the temperature which you entered. Note that the allowable stress for

9-20




SA516-70 material is 18100 psi at this temperature. This is precisely the value that PVElite extracted from the material database. The Design External pressure for this problem is 15. The Design Temperature for External pressure should be 650. Now you are ready to enter the material. Let’s say this vessel is constructed of SA-516-70. As you might expect, one way to enter that material is just to type it in the field. When you do so, the program will check the database, and then update the allowable stresses. This material happens to be the program default, but type the name anyway just to see what the program does. Another way to select a material is from the list of materials in the database. To see this list, click the Material Database icon. The Material Database screen will appear showing the materials list, which will look like this:

Material Database Screen

You can move the scroll bar up and down the screen and see the relevant properties for all of the materials in the PVElite database or, from the Search String field type the material name. Note that each major material classification is divided into columns. You can also view the material parameters by clicking on the material name.

Material Database Record


9-21



By clicking the OK button, the material name and the appropriate material parameters are returned. These parameters may be reviewed and modified through the Material Edit window. To see this window, click the "A" button next to the material input. By clicking the >> button, PVElite will scan the yield stress database for an exact material match and fill in the appropriate yield stress at operating temperature. For many applications, this value is not needed.

Yield Stress Record

In the Joint Efficiency, Longitudinal Seams field, enter the value of E, the longitudinal joint efficiencies to be used in the calculator. For full radiography, choose a value of 1. The next question asks if you would like to include Hydrostatic Head Components to our vessel design. Click on the box to activate the dialog. The Hydrostatic Head dialog appears and prompts you for a few items. The first item is the operating liquid density. Enter a value of 38 lb/cu.ft. The next two fields request the height of the liquid column in the operating position and the hydrotest position of the vessel. This particular vessel is a horizontal drum that will be operating in a partially filled position. When the shop hydrotests the vessel it will be filled and in the horizontal position. Enter values of 54 and 72 in. for these two fields. Click OK to get back to the main data input screen.

Hydrostatic Heads Dialog

You can now click on the Geometry Tab of the input screen. The first field is the Type of Shell or Head. Six options are shown on the pull-down, but if you need more details on this field you can press [F1] for help. We will analyze a hemispherical head, a cylinder and an elliptical head. These are components of the particular horizontal vessel we are analyzing. First enter the Diameter Basis, OD, for an Outside Diameter measurement (and calculation). Next, tab to the Diameter of Shell/Head field and enter the diameter, 72 inches.

9-22




Now, enter the Minimum Thickness of Pipe or Plate, .5 inches, and the Nominal Thickness of Pipe or Plate, .5 inches. Enter 0.0625 inches for the Corrosion Allowance. Since the input fields have a calculator capability, you could also enter the .0625 inch Corrosion Allowance as ‘1/16’. For the Type of Reinforcing Ring, there is no reinforcing ring required for internal pressure, so you can choose None from the pulldown list. You have now completed the hemispherical head input. Your screen should look like this:

Completed Hemispherical Head Input Screen

Note

Add New Item

You may view the drawing of the current item at any time by clicking on the slider at the right of the window and dragging it to the left.

This horizontal tank has two more sections, the shell section and the elliptical head on the other end. To add the new section, click the Add New Item icon. This will take you back to the Design Tab of the input screen and prompt you to enter the second item. Type in the number 2 in the Item Number field. Enter Cylind. Shell in the Description Field. Click the Geometry Tab to enter the type of shell. Since this is a cylinder type, from the pull down, select Cylindrical . A window will appear prompting for the Design Length of Section and the Design Length for Cylinder Volume Calculations; enter 180 inches for both. Click OK to resume. Next, we will enter in the data for the elliptical head. Click on the Add New Item icon. Type in the number 3 in the Item Number field and Elliptical head in the Description field.


9-23



Since the data from the previous element is brought forward, you will only have to modify the shell/head type. Click on the Geometry Tab of the Input screen and from the Type of Shell pulldown, select Elliptical. You will then be prompted for the head ratio. Enter the number 2 for a 2:1 elliptical head. Click OK to continue.

Note

Save Analyze Current Item

When entering new components be sure to type in appropriate descriptions in the description field. This will help make your finished reports more clear and easier to follow.

You are now ready to analyze these three components for internal pressure and hydrostatic head considerations. First, save the file. Now, click on the Analyze Item Icon on the analysis toolbar. Your screen will now look like this:

Next click the Analyze File Icon and you will be ready to review the results. Analyze File

9-24



Reviewing the Results - The Output Option

Reviewing the Results - The Output Option You can quickly review the results of this analysis using the Output Option. From the Main Menu select the Output, Review. The Output program will load and display the following screen. If you have analyzed the components from the input, PVElite will automatically display the output for you. You will see the following screen:

Available Reports Menu


9-25

Reviewing the Results - The Output Option

View Reports


There are now three analyses in the output file. However, if you were to do additional runs of the Shell program, or analyze nozzles, flanges, tubesheets, or anything else, those analyses would also appear on this list. Thus you can review (and print) all of the calculations you have done for a given vessel or job at one time. Select the first analysis, then select View, Report from the menu, or click on the View Reports Icon. Your screen should look like this:

PVElite Output Screen

You can scroll up and down in the text to see all of the input and results. Note especially the Summary of Internal Pressure Results, where you can clearly see that the required thickness is less than the actual thickness for this job, while the Maximum allowable working pressure is greater than the design pressure. Therefore, the shell thickness you selected is acceptable. After you finish reviewing the results, click the Done button to return to the Available Reports Menu. You may also select more than one analysis at a time by holding down the [Ctrl] key while selecting the items to view. You can also select all reports by selecting Edit, Select All, from the menu. When viewing the reports, click the Next Report Button to move to the next component.

9-26



Printing or Saving Reports to a File

Printing or Saving Reports to a File Printing the Reports Select Font Page Number Print

The PVElite output results brought to the screen may be sent directly to a printer. To print a hard copy of the reports, first select the report font by clicking on the Select Font Icon from the Available Reports Menu Toolbar. You may then select a new font for your reports by clicking on the Select Font Icon. You can also enter a new starting page number by clicking on the Page Number Icon on the Toolbar. Now, simply click on the Printer Icon.


9-27

Summary - Seeing Results for a Whole Vessel


Summary - Seeing Results for a Whole Vessel This section of the tutorial discusses the summary program in PVElite. The summary program will pull selected information from within the input file and summarize it. Selected portions of the output generated by PVElite are stored in the input file. To use the summary program follow these simple steps. Analyze File

1. Perform the analysis on each type chosen. Click the Analyze File icon from the Analysis Toolbar. 2. From the Main Menu, choose Analyze, Summary. The vessel summary will be appended to the current output files as seen on the Available Reports Screen. You may view this file or print it just as you would the analysis files.

View Reports Using Word

The view below is the Microsoft Word view. If you want to return to the Home Screen, click the Output Processor menu option..

Home Screen

Rev.A

9-28



Tutorial Problem Printout

Tutorial Problem Printout CodeCalc 6.20

Licensee: COADE, Inc. (Network Lock on Novell Server)

FileName : Example

---------------------------------------

Shell Analysis : CYLINDER

Input Echo, Component

Item:

2,

2

8:47a

Page 1 Dec 1,1999

Description: CYLINDER

Design Internal Pressure

P

Temperature for Internal Pressure Design External Pressure

PEXT

100.00

psig

700.00

F

15.00

Temperature for External Pressure

650.00

External Pressure Chart Name

psig F

CS-2

Include Hydrostatic Head Components

NO

Material Specification (Not Normalized) Allowable Stress At Temperature

SA-516 70 S

18100.00

psi

SA

20000.00

psi

Joint efficiency for Head Joint

E

1.00

Inside

D

40.0000

in.

T

0.5000

in.

CA

0.0000

in.

Allowable Stress At Ambient Curve Name for Chart UCS 66

B

Diameter of Hemispherical Head

Minimum Thickness of Pipe or Plate Corrosion Allowance

Type of Element:


INTERNAL PRESSURE RESULTS, SHELL NUMBER

2, Desc.: CYLINDER

ASME Code, Section VIII, Division 1, 1998, A-99

Thickness Due to Internal Pressure (TR): = (P*(D/2+CA))/(2*S*E-0.2*P) per UG-27 (d) = (100.00*(40.0000/2+0.0000))/(2*18100.00*1.00-0.2*100.00) = 0.0625 in. ( >= 0.0625 in. Per Ug 16b )

Max. All. Working Pressure at Given Thickness (MAWP): = (2*S*E*(T-CA))/((D/2+CA)+0.2*(T-CA)) per UG-27 (d) = (2*18100.00*1.00*(0.5000))/((40.0000/2+0.0000)+0.2*(0.5000)) = 900.50 psig

Maximum Allowable Pressure, New and Cold (MAPNC): = (2*SA*E*T)/(D/2+0.2*T) per UG-27 (d) = (2*20000.00*1.00*0.5000)/(40.0000/2+0.2*0.5000) = 995.02 psig


9-29



Actual stress at given pressure and thickness (Sact): = (P*((D/2+CA)+0.2*(T-CA)))/(2*E*(T-CA)) = (100.00*((40.0000/2+0.0000)+0.2*(0.5000)))/(2*1.00*(0.5000)) = 2010.00 psi

SUMMARY OF INTERNAL PRESSURE RESULTS: Required Thickness plus Corrosion Allowance, Trca

0.0625

in.

Actual Thickness as Given in Input Maximum Allowable Working Pressure

0.5000

in.

MAWP

900.50

psig

P

100.00

psig

Design Pressure as Given in Input

CodeCalc 6.20


FileName : Example

---------------------------------------

Shell Analysis : CYLINDER

Item:

2

8:47a

Page 2 Dec 1,1999

HYDROSTATIC TEST PRESSURES ( Measured at High Point ): Hydro. per UG-99(b); 1.3 * MAWP * Sa/S

1293.53

psig

Hydro. per UG-99(c); 1.3 * MAPNC

1293.53

psig

Min. Metal Temp. w/o impact per Fig. UCS-66 Min. Metal Temp. at Req’d thk. (per UCS 66.1)

-6

F

-146

F

WEIGHT and VOLUME RESULTS, NO C.A. : Volume of Shell Component

VOLMET

Weight of Shell Component Inside Volume of Component

WMET

364.6

VOLID

16755.2

WWAT

605.0

Weight of Water in Component

EXTERNAL PRESSURE RESULTS, SHELL NUMBER

1288.3

in.^3 lb. in.**3 lb.

2, Desc.: CYLINDER


External Pressure Chart

CS-2

at

Elastic Modulus for Material

650.00 25125000.00

F psi

Results for Max. Allowable External Pressure (Emawp): Corroded Thickness of Shell Outside Diameter of Shell Diameter / Thickness Ratio

TCA

0.5000

in.

OD

41.0000

in.

(D/T)

82.0000

Geometry Factor, A f(DT,LD)

A

0.0030488

Materials Factor, B, f(A, Chart)

B

10675.6992

Maximum Allowable Working Pressure

260.38

psi psig

EMAWP = B/((D/T)/2) = 10675.6992/( 82.0000 / 2 ) = 260.3829

Results for Reqd Thickness for Ext. Pressure (Tca):

9-30




Corroded Thickness of Shell Outside Diameter of Shell Diameter / Thickness Ratio

TCA

0.0634

in.

OD

41.0000

in.

(D/T)

647.0875


A

0.0003863


B

4853.4785


15.00

psi psig

EMAWP = B/((D/T)/2) = 4853.4785/( 647.0875 / 2 ) = 15.0010

SUMMARY of EXTERNAL PRESSURE RESULTS: Allowable Pressure at Corroded thickness Required Pressure as entered by User

260.38

psig

15.00

psig

Required Thickness including Corrosion all.

0.0634

in.

Actual Thickness as entered by User

0.5000

in.

The CODECALC Program, (c) 1989-2000 by COADE Engineering Software

CodeCalc 6.20


FileName : Example

---------------------------------------

Shell Analysis : HEMI HEAD


Item:

1,

1

8:47a

Page 3 Dec 1,1999

Description: HEMI HEAD


P


PEXT


100.00

psig

700.00

F

15.00 650.00


psig F

CS-2


NO

Material Specification (Not Normalized) Allowable Stress At Temperature Allowable Stress At Ambient

SA-516 70 S

18100.00

psi

SA

20000.00

psi

Curve Name for Chart UCS 66

B


E

1.00

Inside

D

40.0000

in.

T

0.5000

in.

CA

0.0000

in.

Diameter of Hemispherical Head


Type of Element:



1, Desc.: HEMI HEAD



9-31



Thickness Due to Internal Pressure (TR): = (P*(D/2+CA))/(2*S*E-0.2*P) per UG-27 (d) = (100.00*(40.0000/2+0.0000))/(2*18100.00*1.00-0.2*100.00) = 0.0625 in. ( >= 0.0625 in. Per Ug 16b )

Max. All. Working Pressure at Given Thickness (MAWP): = (2*S*E*(T-CA))/((D/2+CA)+0.2*(T-CA)) per UG-27 (d) = (2*18100.00*1.00*(0.5000))/((40.0000/2+0.0000)+0.2*(0.5000)) = 900.50 psig

Maximum Allowable Pressure, New and Cold (MAPNC): = (2*SA*E*T)/(D/2+0.2*T) per UG-27 (d) = (2*20000.00*1.00*0.5000)/(40.0000/2+0.2*0.5000) = 995.02 psig

Actual stress at given pressure and thickness (Sact): = (P*((D/2+CA)+0.2*(T-CA)))/(2*E*(T-CA)) = (100.00*((40.0000/2+0.0000)+0.2*(0.5000)))/(2*1.00*(0.5000)) = 2010.00 psi


0.0625

in.

Actual Thickness as Given in Input

0.5000

in.

MAWP

900.50

psig

P

100.00

psig

Maximum Allowable Working Pressure Design Pressure as Given in Input

CodeCalc 6.20


FileName : Example

---------------------------------------

Shell Analysis : HEMI HEAD

Item:

1

8:47a

Page 4 Dec 1,1999

HYDROSTATIC TEST PRESSURES ( Measured at High Point ): Hydro. per UG-99(b); 1.3 * MAWP * Sa/S

1293.53

psig


1293.53

psig


-6

F

-146

F


VOLMET

1288.3

Weight of Shell Component

WMET

364.6

VOLID

16755.2

WWAT

605.0

Inside Volume of Component Weight of Water in Component


9-32


1, Desc.: HEMI HEAD






CS-2

at


650.00 25125000.00

F psi


TCA

0.5000

in.

OD

41.0000

in.

(D/T)

82.0000


A

0.0030488


B

10675.6992


260.38

psi psig

EMAWP = B/((D/T)/2) = 10675.6992/( 82.0000 / 2 ) = 260.3829

Results for Reqd Thickness for Ext. Pressure (Tca): Corroded Thickness of Shell

TCA

Outside Diameter of Shell

OD

Diameter / Thickness Ratio

(D/T)

0.0634

in.

41.0000

in.

647.0875


A

0.0003863


B

4853.4785


15.00

psi psig

EMAWP = B/((D/T)/2) = 4853.4785/( 647.0875 / 2 ) = 15.0010


260.38

psig

15.00

psig


0.0634

in.


0.5000

in.

The CODECALC Program, (c) 1989-2000 by COADE Engineering Software

CodeCalc 6.20


FileName : Example

---------------------------------------

Shell Analysis : ELLIPTICAL


Item:

2,


Temperature for External Pressure External Pressure Chart Name


Material Specification (Not Normalized)


8:47a

Page 5 Dec 1,1999

Description: ELLIPTICAL

P


2

PEXT

100.00

psig

700.00

F

15.00 650.00

psig F

CS-2

NO

SA-516 70

9-33



Allowable Stress At Temperature

S

18100.00

psi

SA

20000.00

psi


E

1.00

Inside

D

40.0000

in.

T

0.5000

in.

CA

0.0000

in.

AR

2.0000

STRTFLG

2.0000

Allowable Stress At Ambient Curve Name for Chart UCS 66

B

Diameter of Elliptical Head


Aspect Ratio Length of Straight Flange

Type of Element:

in.

Elliptical Head


2, Desc.: ELLIPTICAL


Thickness Due to Internal Pressure (TR): = (P*(D+2*CA)*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (100.00*(40.0000+2*0.0000)*1.00)/(2*18100.00*1.00-0.2*100.00) = 0.1106 in.

Max. All. Working Pressure at Given Thickness (MAWP): = (2*S*E*(T-CA))/(K*(D+2*CA)+0.2*(T-CA)) per Appendix 1-4 (c) = (2*18100.00*1.00*(0.5000))/(1.00*(40.0000+2*0.0000)+0.2*(0.5000)) = 451.37 psig

Maximum Allowable Pressure, New and Cold (MAPNC): = (2*SA*E*T)/(K*D+0.2*T) per Appendix 1-4 (c) = (2*20000.00*1.00*0.5000)/(1.00*40.0000+0.2*0.5000) = 498.75 psig

Actual stress at given pressure and thickness (Sact): = (P*(K*(D+2*CA)+0.2*(T-CA)))/(2*E*(T-CA)) = (100.00*(1.00*(40.0000+2*0.0000)+0.2*(0.5000)))/(2*1.00*(0.5000)) = 4010.00 psi


0.1106

in.


0.5000

in.

CodeCalc 6.20


FileName : Example

---------------------------------------

Shell Analysis : ELLIPTICAL

9-34

Item:

2

8:47a

Page 6 Dec 1,1999





MAWP

451.37

psig

P

100.00

psig

Hydro. per UG-99(b); 1.3 * MAWP * Sa/S

648.38

psig


648.38

psig


HYDROSTATIC TEST PRESSURES ( Measured at High Point ):


-6

F

-146

F


VOLMET

1108.8


WMET

313.8

VOLID

8377.6

WWAT

302.5

Inside Volume of Component Weight of Water in Component Inside Vol. of

2.00 in. Straight

Total Volume for Head + Straight


VOLSCA

2513.3

in.**3

VOLTOT

10890.9

in.**3


2, Desc.: ELLIPTICAL



CS-2

at


650.00 25125000.00

F psi


TCA

0.5000

in.

OD

41.0000

in.

(D/T)

82.0000


A

0.0016938


B

9539.9775


129.27

psi psig

EMAWP = B/(K0*(D/T)) = 9539.9775/( 0.9000 * 82.0000 ) = 129.2680

Results for Reqd Thickness for Ext. Pressure (Tca): Corroded Thickness of Shell Outside Diameter of Shell Diameter / Thickness Ratio

TCA OD (D/T)

0.1140

in.

41.0000

in.

359.4930


A

0.0003863


B

4853.4790


15.00

psi psig

EMAWP = B/(K0*(D/T)) = 4853.4790/( 0.9000 * 359.4930 ) = 15.0010



129.27

psig

15.00

psig

9-35


9-36



0.1140

in.


0.5000

in.



&KDSWHU The Shell Module

Introduction The Shell module performs internal and external pressure design of vessel and exchanger components using the rules in the ASME Code, Section VIII, Division 1, 2001, A-2001. This module also considers static liquid head in the pressure design, performs stiffening ring calculations, sizes stiffening rings, and computes weld shear flows on stiffening ring welds.

Purpose, Scope, and Technical Basis The Shell module calculates the required thickness and Maximum Allowable Working Pressure for cylindrical shells and heads under internal or external pressure. The module is based on the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, 2001 Edi- R tion, A-2001. Under internal pressure, the module analyzes six types of heads or shells, using applicable code formulae as follows: Shell or Head Type

ID Basis

OD Basis

Cylinder

UG-27 (c) (1)

App 1-1 (a) (1)

Elliptical

App 1-4 (c) (1)

App 1-4 (c) (2)

Torispherical

App 1-4 (d) (3)

App 1-4 (d) (4)


UG-27 (d) (3)

App 1-1 (a) (2)

Conical Head or Shell

UG-32 (g)

App 1-4 (e) (1)

Flat Head

UG-34 (1) and (3)

Elliptical heads with aspect ratios between 1.0 and 3.0 (typically 2.0) may be analyzed. Torispherical heads with knuckle radii between 6% and 100% of the crown radius may be analyzed. Conical heads and sections with half apex angles up to 30 degrees may be analyzed. Reinforcement at the large and small ends of the cone should be analyzed in the Conical Sections module. Welded flat heads, circular or non-circular, are analyzed in this module. Bolted flat heads are analyzed in the Flange module. Bolted dished heads under internal or external pressure are analyzed in the Floating Heads module.

The Shell Module

10-1

Purpose, Scope, and Technical Basis


Under external pressure, the module analyzes five types of heads or shells, using applicable code formulae as follows: Shell or Head Type

Code Paragraph

Cylinder

G-28 (c)

2:1 Elliptical

UG-33 (d)

Torispherical

UG-33 (e)


UG-33 (c) and UG-28 (d)

Conical Shell or Head

UG-33 (f)

All of these shell or head types are analyzed for diameter to thickness ratios greater than 10. Elliptical heads with aspect ratios between 1.0 and 3.0 may be analyzed. Torispherical heads with any crown radius may be analyzed. Reinforcement at the large and small end of conical heads or sections is analyzed in the Conical Sections module. The Shell module takes full account of corrosion allowance. You enter actual thickness and corrosion allowance, and the program adjusts thicknesses and diameters when making calculations for the corroded condition. Figure 10A shows geometry for the Shell module. In addition, the Shell module also accounts for static liquid head for shell components. For carbon steel vessels, normalized material can be used for UCS-66 calculations.

10-2

The Shell Module



Figure 10A - Geometry for The Shell Module

The Shell Module

10-3



Figure 10B - Head Geometry

10-4

The Shell Module


Discussion of Input Data

Discussion of Input Data Main Input Fields Design Internal Pressure

Enter the Internal Design Pressure. You must define either the design pressure or the minimum metal thickness, preferably both. Design pressure is used to determine the required thickness and minimum metal thickness is used to determine the Maximum Allowable Working Pressure. Design Temperature for Internal Pressure

Enter the temperature associated with the internal design pressure. The PVElite program will automatically update materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Design External Pressure

Enter the design pressure for external pressure analysis. This should be a positive value, i.e. 14.7 psia. If you enter a zero in this field the program will not perform external pressure calculations. Design Temperature for External Pressure

Enter the temperature associated with the external design pressure. The PVElite program will automatically update materials properties for external pressure calculations when you change the design temperature. The design external pressure at this temperature is a completely different design case than the internal pressure case. Therefore this temperature may be different than the temperature for internal pressure. Many external pressure charts have both lower and upper limits on temperature. If your design temperature is below the lower limit, use the lower limit as your entry to the program. If your temperature is above the upper limit the component may not be designed for vacuum conditions. Shell Section Material

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. Examples of material names are: SA-516-70, SA-285-C. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Press [F1] for details. Include Hydrostatic Head Component

If your shell or head design needs to account for hydrostatic liquid head, check this box. PVElite will add the hydrostatic pressure head to the internal design pressure for the required thickness calculation. Shell Allowable Stress at Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the module will automatically update this field, but only for BUILT-IN materials. If you enter the

The Shell Module

10-5



allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section VIII Division 1 at the design temperature. Shell Allowable Stress at Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section VIII Division 1 at the ambient temperature. Joint Efficiency for Longitudinal Seams

Enter the efficiency of the welded joint for shell sections with welded seams. This will be the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. The joint Efficiency in this (and all other) ASME Code formulas is a measure of the inspection quality on the weld seam. In general, weld seams that receive full radiography have a joint efficiency of 1.0. Weld seams that receive spot radiography have a joint efficiency of 0.85. Weld seams that receive no radiography have a joint efficiency of 0.7. Seamless components have a joint efficiency of 1.0. In addition to the basic rules described above, the Code requires that no two seams in the same vessel differ in joint efficiency by more than one category of radiography. For example, if circumferential seams receive no radiography (E=0.7) then longitudinal seams have a maximum E of 0.85, even if they receive full radiography. The practical outworking of this is that circumferential seams, which are usually less highly stressed, may be spot radiographed (E=0.85) while longitudinal seams are fully radiographed. This provides the same metal thickness at some savings in inspection costs. Is the Shell/Head Material Normalized?

If your vessel material has been produced to a fine grain structure, check this box. PVElite will use the normalized material curve for the UCS 66 calculations. Type of Shell or Head

Enter the type of shell for this shell section. Choose one of the following shell types:

10-6

•

Shell or Head Type

•

Cylindrical Shell

•

Elliptical Head

•

Torispherical Head

•

Hemispherical Head or Spherical Shell

•

Conical Shell

•

Welded Flat Head

The Shell Module



Diameter Basis

If the vessel dimensions are specified on inside basis, pull down the ID selection. If the dimensions are based on the vessels outside diameter select the OD selection. For flat heads, this value is ignored. Always enter the outside diameter of the flat head. Diameter of Shell/Head

Enter the diameter of the shell or head. For torispherical heads, enter the crown radius. For flat heads, enter the outside diameter of the head. For cones, enter the largest diameter of the cone. The program allows you to use either an inside diameter or an outside diameter. Minimum Thickness of Pipe or Plate

Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel. Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. You should enter the minimum thickness. Nominal of Average Thickness of Pipe or Plate (optional)

Enter the NOMINAL or AVERAGE thickness of the actual plate or pipe used to construct the vessel. This thickness is used to calculate the volume and weight of the metal only if it is between 1 and 1.5 times the minimum thickness. If this value is left blank or 0 the program will use the minimum thickness to compute the weight and volume of this shell element. Corrosion Allowance

Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Type of Reinforcing Ring

Enter the index for the type of reinforcing ring on the cylindrical or conical section. Three options are available: •

No Reinforcing Ring

•

Simple Bar Reinforcing Ring—You will be required to enter the width and thickness of the bar.

•

General Beam Section—You will be required to enter the moment of inertia, crosssectional area and the distance from the shell to the centroid of the beam. In all cases the program includes the shell in the calculation of the moment of inertia for the stiffening ring. This calculation will only be performed for external pressure calculations. Also, the detailed analysis for the required moment of inertia and cross-sectional area for cones is contained in the separate Conical Sections module.

Minimum Design Metal Temperature

Enter in the minimum design metal temperature for the component. This value will only be printed in the input echo and will not be used in the calculation. Note that if this entry is zero, the minimum design metal temperature will not be echoed in the input.

The Shell Module

10-7



Skip UG-16(B) Minimum Thickness Calculation

Check this box to skip UG-16(b) calculations. The section UG-16(b) states the minimum thickness for pressure retaining components as 0.0625 in. (1.6 mm). There are certain exemptions from this requirement such as in the case of heat exchanger tubes. Refer to the ASME Section VIII, Div-1, UG-16(b) for more details.

10-8

The Shell Module



Pop-up Input Fields Operating Liquid Density

Enter the density of the operating fluid here. This value will be multiplied by the height of the liquid column in order to compute the static head pressure. Height of Liquid Column Operating

Enter the distance from the bottom of this shell or head element to the surface of the liquid. The head pressure is determined by multiplying the liquid density by the height of the fluid to the point of interest. Height of Liquid Column Hydrotest

Enter the distance from the bottom of this shell or head element to the surface of the liquid when the vessel is being hydrotested. If this is shop hydrotest, and the vessel is laying on its side, then the height of the liquid column should be equal to the inside diameter of the vessel. In the case of a vertical or field hydrotest this liquid height can be greater than the vessel diameter. Design Length of Section

Enter the design length of the section, typically the length of the vessel plus one third the depth of the heads or, alternately, the distance between stiffening rings. For a vessel with 2 elliptical heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/6. For a vessel with 2 spherical heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/3. For a vessel with 2 flanged and dished heads and no intermediate stiffeners, the design length is the tangent length plus the diameter/9. When analyzing a head, enter zero for the length. Design Length for Cylinder Volume Calculations

Enter the distance that you want PVElite to use for the liquid volume computation. For a horizontal vessel this would be the tangent to tangent distance. Aspect Ratio for Elliptical Heads

Enter the aspect ratio for the elliptical head. The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head the aspect ratio is 2.0. Crown Radius for Torispherical Heads

Enter the crown radius for torispherical heads. The crown radius for a torispherical head is referred to as the dimension “L”, in the ASME VIII Div. 1 code book. Length of Straight Flange

Enter the length of the straight section of the elliptical or torispherical head. This is used in volume and weight calculations. Knuckle Radius for Torispherical Heads

Enter the knuckle radius for torispherical heads. This dimension is “r”, in the ASME VIII Div. 1 code book.

The Shell Module

10-9



Half APEX Angle for Conical Sections

Enter the half-apex angle for cones or conical sections. The maximum value of the half apex angle for cones under internal pressure and without toriconical transitions is 30 degrees. The largest angle for cones under internal pressure and with toriconical sections is 60 degrees. The largest angle for cones under external pressure is 60 degrees. If you exceed these values the program will run, but with a warning. Large Diameter for Non-Circular Welded Flat Heads

If you have a non-circular welded flat head, enter the large dimension in this field, and enter the small dimension as the component diameter above. Attachment Factor for Flat Head

Enter the flat head attachment factor, calculated or selected from ASME Code, Section VIII, Division 1, Paragraph UG-34, Figure UG-34. Some typical attachment factors are as follows, but please be careful to consult Paragraph UG-34 before using these values: •

0.17 (b-1)Head welded to vessel with generous radius

•

0.20 (b-2)Head welded to vessel with small radius

•

0.20 (c)Lap welded or brazed construction

•

0.13 (d)Integral flat circular heads

•

0.20 (e f g)Plate welded inside vessel (check 0.33*m)

•

0.33 (h)Plate welded to end of shell

•

0.20 (I)Plate welded to end of shell (check 0.33*m)

•

0.30 (j k)Bolted flat heads (include bending moment)

•

0.30 (m n o)Plate held in place by screwed ring

•

0.25 (p)Bolted flat head with full face gasket

•

0.75 (q)Plate screwed into small diameter vessel

•

0.33 (r s)Plate held in place by beveled edge

Width of Reinforcing Ring

Enter the width of the reinforcing ring. For a reinforcing ring that is a simple bar, this is the dimension that is perpendicular to the surface of the shell. Thickness of Reinforcing Ring

Enter the thickness of the reinforcing ring. For a reinforcing ring that is a simple bar, this is the dimension that is parallel to the surface of the shell. Size of Fillet Weld Leg Connecting Ring to Shell

Enter the dimension of the weld leg which connects the stiffening ring to the shell section. This value will be used in the weld shear flow calculations if a simple bar stiffener has been selected as the type of reinforcing ring.

10-10

The Shell Module



Ring Type to Satisfy Inertia and Area Requirements

Entering a structural ring type here will cause PVElite search the structural database for a suitable member that will meet the inertia requirements for the ring. The valid types of structural shapes to enter here are •

EQUAL ANGLE—Equal Leg Angles

•

UNEQUAL ANGLE—Unequal Angle

•

DBL LARGE ANGLE—Double Angles Large Legs back to back

•

DBL SMALL ANGLE—Double Angles Small Legs back to back

•

CHANNEL—Channel Sections

•

I-BEAM—Wide Flange Sections

•

WT SECTION—Wide Flange Sections (T type)

•

MT SECTION—Miscellaneous Tee

•

ST SECTION—Structural Tee

•

MC SECTION—Miscellaneous Channel

Ring Weld Attachment Style (Intermittent, Continuous, Both)

Enter the style of the weld that attaches the stiffening ring to the shell section. Per UG-29 of the Code there are 3 “styles”: •

INTERMITTENT

•

CONTINUOUS

•

BOTH

This input in conjunction with the shell thickness and corrosion allowance will allow for the computation of the maximum spacing between weld segments. Location of Ring (Internal or External)

There are two possibilities for the location of the stiffening ring. •

INTERNAL—Attached to the inside of the Shell

•

EXTERNAL—On the outer surface of the Shell

Moment of Reinforcing Ring

Enter the moment of inertia for the beam section which is being used as a reinforcing ring, in the direction parallel to the surface of the shell. Cross-Sectional Area of Reinforcing Ring

Enter the cross sectional area for the beam section which is being used as a reinforcing ring. Distance from Ring Centroid to Shell Surface

Enter the distance from the surface of the shell to the centroid of the reinforcing ring. This distance should be measured normal to the shell surface.

The Shell Module

10-11



Is the Ring Angle Rolled the Hard Way?

If you have selected an angle type ring to satisfy the inertia requirements above, this prompt is meaningful; otherwise it is ignored. When this option is used the program will compute the distance from the shell surface to the ring centroid based on information in the ASIC Steel handbook.

10-12

The Shell Module



Results Status Bar

In CodeCalc, the Status bar, which is located at the bottom of the application, is divided into several panes, which compute and display critical results as the vessel is being modeled. The information includes: •

Required Thickness Due to Internal Pressure

•

Required Thickness Due to External Pressure

•

Internal MAWP

•

MDMT

•

Warning Messages if the Stiffening Ring or the Welds Connecting It Fails

Note

Results that display red in color indicate a failure.

Thickness Due to Internal Pressure

The appropriate formula from ASME Section VIII is referenced, and the formula and substitution are shown. The diameter or crown radius are adjusted to take into account the corrosion allowance. If your shell design includes hydrostatic head components, the additional pressure due to the height of the liquid column and the operating liquid density will be included to the basic design pressure. The hydrostatic head will be subtracted in order to properly determine the MAWP for the vessel part that is being analyzed. Remember, when pressures are being read from the pressure gauge, the gauge is usually at the high point of the vessel. The pressure registered by the gauge would be different if were at the bottom of the liquid filled vessel. •

For elliptical heads, the K factor is (2 + Ar * Ar) / 6, per App. 1-4 (c).

•

For torispherical heads the factor M is (1/4) * (3 + SQRT (L / R)), where “L” (the crown radius) and “R” (the knuckle radius) were entered by the user.

Important

The PVElite program does not replace the given thickness with this calculated minimum. If you are choosing the thickness for a component, compare the values shown under “Summary of Internal Pressure Results” (required vs. actual) and adjust the actual thickness up or down accordingly.

Maximum Allowable Working Pressure at Given Thickness

This value is calculated as described above, using the given thickness minus corrosion allowance and the operating allowable stress. The hydrostatic head component is subtracted from this value. The pressure gauge is assumed to be at the top of the vessel.

The Shell Module

10-13



Maximum Allowable Working Pressure, New & Cold

This value is calculated as described above, using the uncorroded thickness and the ambient allowable stress. Actual Stress at Given Pressure and Thickness

Note that the joint efficiency is included in this value, so this can be considered the stress at the welded joint rather than in the base metal. Summary of Internal Pressure Results

Either of two conditions can indicate a problem in your design. First, if the required thickness plus corrosion allowance is greater than the given thickness, then you must increase the given thickness. Second, if the M.A.W.P. is less than the design pressure then you must either decrease the design pressure or increase the given thickness to achieve an acceptable design. The hydrotest pressure is calculated as the maximum allowable working pressure times 1.3 times the ratio of the allowable stress at ambient temperature to the allowable stress at design temperature. The hydrotest pressure may not be appropriate for the entire vessel for three reasons. First, some other component may have a lower maximum allowable working pressure, which may govern the hydrotest pressure. Second, you may choose to base hydrotest pressure on design pressure rather than maximum allowable working pressure. Third, if the vessel is tested in the vertical position you may have to adjust the hydrotest pressure for the head of water in the vessel. For the UG99-C hydrotest, the liquid head is subtracted from the basic result. Minimum Metal Temperatures

For carbon steels, these temperatures represent the minimum design metal temperature for the given thickness and, in the second case, the given pressure. The first temperature is interpolated directly from chart UCS-66. The second temperature is reduced if the actual stress is lower than the allowable stress, using figure UCS-66.1. The program also checks for materials which qualify for the -20 minimum design temperature per UG-20 and assigns that temperature if it is less than the value found on the charts. See the input notes above to enter normalized or non-normalized materials. Weight & Volume Results, No Corrosion Allowance

The PVElite program computes the volume and weight of the shell component. Additionally, the inside volume for a 2.00 inch straight flange is computed and used in the computation of the total volume for the head and the flange. The dimensions used in the volume and weight calculations are non-corroded dimensions. Results for Maximum Allowable External Pressure

For the given diameter, thickness, and length, the maximum allowable external pressure is computed per UG-28.

10-14

The Shell Module



Results for Required Thickness for External Pressure

The required thickness is computed using the rules of UG-28 iteratively. Such items as the length and outside diameter are held constant, and the program calculates the required thickness based on the user entered external pressure. Summary of External Pressure Results

Summary listing displaying external pressure results for both the user entered thickness and the computed required thickness.

The Shell Module

10-15

Example Problems


Example Problems Example problem 1 is an example cylinder design. This particular problem involves most of the inputs available in the shell module. Note the form of the printout regarding the external pressure calculations. This form of the output can be selected by first choosing Tools from the Main Menu, and then selecting Configuration, Miscellaneous. Turn on the flag to print the external calculations in rows. This form of the output report is preferred if trying to conserve paper. There are many more example problems. The PVElite input file CHECKS contain several shell and head design examples taken directly from the ASME Code Appendices 1 and L. PVElite Licensee: COADE ESL FileName : SHELL

------------------------------------------- Page 1

Shell Analysis : SHELL SECTION

INPUT VALUES, COMPONENT

ITEM:

1,

1,

10:49am,

Description: SHELL SECTION


P

Temperature for Internal Pressure

100.00 700.00

Design External Pressure

PEXT


psig

F

15.00 300.00


psig

F

CS-2


YES

Operating Liquid Density

38.000

lb./cu.ft.

Height of Liquid Column ( Operating )

54.00

in.

Height of Liquid Column ( Hydrotest )

72.00

in.

Material Specification (Not Normalized)

SA-516 70

Allowable Stress At Temperature Allowable Stress At Ambient

S

16600.00

psi

SA

17500.00

psi

Curve Name for Chart UCS 66

B

Joint efficiency for Shell Joint

Design Length of Section

E

1.00

L

100.0000

in.

CYLLEN

100.0000

in.

Outside Diameter of Cylindrical Shell

D

72.0000

in.

Minimum Thickness of Pipe or Plate

T

.5000

in.

Nominal Thickness of Pipe or Plate

T

.5000

in.

CA

.0625

in.

Length of Cylinder for Volume Calcs.

05/14/98

Corrosion Allowance

Stiffening Ring Material Specification

SA-516 70

External Pressure Chart Name for Ring

CS-2

Size of Fillet Weld Leg Ring to Shell

.375

in.

Width of Reinforcing Ring

WRING

4.0000

in.

Thickness of Reinforcing Ring

TRING

1.0000

in.

Ring Type to Satisfy Inertia and Area Req. Ring Weld Attachment Style

INTERMITTENT

Location of Reinforcing Ring INTERNAL PRESSURE RESULTS, SHELL NUMBER

NONE

EXTERNAL 1, Description: SHELL SECTION

Thickness Due to Internal Pressure (TR): = (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1)

10-16

The Shell Module


Example Problems

= (101.19*72.0000/2)/(16600.00*1.00+0.4*101.19) = .2189 in.

Max. All. Working Pressure at Given Thickness (MAWP): Less Operating Hydrostatic Head Pressure of

1.19 psig

= (S*E*(T-CA))/(D/2-0.4*(T-CA)) per Appendix 1-1 (a)(1) = (16600.00*1.00*(.4375))/(72.0000/2-0.4*.4375) = 202.72 - 1.19 = 201.53 psig

Maximum Allowable Pressure, New and Cold (MAPNC): = (SA*E*T)/(D/2-0.4*T) per Appendix 1-1 (a)(1) = (17500.00*1.00*.5000)/(72.0000/2-0.4*.5000) = 244.41 psig

Actual stress at given pressure and thickness (Sact): = (P*(D/2-0.4*(T-CA)))/(E*(T-CA)) = (101.19*((72.0000/2-0.4*(.4375)))/(1.00*(.4375)) = 8285.81 psi


.2814

in.


.5000

in.


MAWP

201.53

psig

P

100.00

psig

Hydro. per UG-99(b); 1.5 * P * SA / S

160.01

psig

Hydro. per UG-99(c); 1.5 * MAPNC - Head (Hydro)

364.02

psig


HYDROSTATIC TEST PRESSURES ( Measured at High Point ):

Minimum Metal Temp. w/o impact per Fig. UCS-66 Minimum Metal Temp. at Required thickness

-6

F

-50

F

WEIGHT and VOLUME RESULTS, ORIGINAL THICKNESS: Volume of Shell Component

VOLMET

11231.2


WMET

3178.4

lb.

VOLID

1713.9

Gals.

WWAT

14297.1

Inside Volume of Component Weight of Water in Component

in.**3

lb.

WEIGHT AND VOLUME RESULTS, CORRODED THICKNESS: Volume of Shell Component,

Corroded

VOLMETCA

9835.9

in.**3

Weight of Shell Component,

Corroded

WMETCA

2783.6

lb.

Inside Volume of Component,

Corroded

VOLIDCA

1720.0

Gals.

Weight of Water in Component, Corroded

WWATCA

14347.5



CS-2

lb.

1, Description: SHELL SECTION

at


300.00 29000000.00

F psi

Results for Max. Allowable External Pressure (Emawp): TCA

OD

SLEN

D/T

L/D

Factor A

B

.4375

72.0000

100.00

164.57

1.3889

.0004433

6428.54

EMAWP=(4*B)/(3*DT)=(4*6428.5380)/(3*164.5714)=52.0831 psig

The Shell Module

10-17

Example Problems


Results for Reqd Thickness for Ext. Pressure (Tca): TCA

OD

SLEN

D/T

L/D

Factor A

B

.2659

72.0000

100.00

270.76

1.3889

.0002101

3046.24

EMAWP=(4*B)/(3*DT)=(4*3046.2380)/(3*270.7614)=15.0009 psig

Results for Maximum Length Between Stiffeners (Slen): TCA

OD

SLEN

D/T

L/D

Factor A

B

.4375

72.0000

347.19

164.57

4.8221

.0001277

1851.57

EMAWP=(4*B)/(3*DT)=(4*1851.5680)/(3*164.5714)=15.0011 psig

Effective Length of Shell

6.17

Area (sq.in.)

Distance (in.)

in.

Area*Dist

Shell:

2.701

.2188

.591

Ring :

4.000

2.4375

9.750

Total:

6.701

10.341

Centroid of Ring plus Shell

=

Inertia

Distance

1.543

in.

A*Dist^2

Shell:

.043

1.3244

4.738

Ring :

5.333

-.8943

3.199

Total:

5.376

7.937

Available Moment of Inertia, Ring plus Shell

13.314

Required Stress in Ring plus Shell

BREQ

1696.34

Required Strain in Ring plus Shell

AREQ

.0001170

in**4

psi

Required Moment of Inertia, Ring plus Shell = ( OD^2 * SLEN * (TCA+ARING/SLEN) * AREQ )/ 10.9 = (72.0000^2*100.0000*(.4375+4.0000/100.0000)*.0001170)/10.9 = 2.6570 in**4

RESULTS for STIFFENING RING WELD CALCULATIONS Radial Pressure Load

PEXT*SLEN

1500.00

lb./in.

The Radial Shear Load

V

1080.00

lb.

The First Moment of the Area ( Ring + Shell )

Q

3.58

VQ/I

290.19

.55*S

9130.00

psi

WLDMIN

.25

in.

3.50

in.

Weld Shear Flow due to Rad. Shear Load The Weld Allowable Stress Minimum Weld Thickness Min(.25,TCA,TRING) Minimum Space between Welds

8*TCA

The Weld Allowable Load The Combined Weld Load

in.^3 lb./in

WLDMIN*.55*S

2282.50

lb./in

SRSS of VQ/I and PEXT*SLEN

1527.81

lb./in

SUMMARY of EXTERNAL PRESSURE RESULTS: Allowable Pressure at Corroded thickness

52.08

psig

Required Pressure as entered by User

15.00

psig


.3284

in.


.5000

in.

347.194

in.

100.00

in.

Maximum Length for Thickness and Pressure Actual Length as entered by User Required

Inertia, Ring + Shell

2.657

in**4

Available Inertia, Ring + Shell

13.314

in**4

The PVElite Program, (C) 1989-2001 by COADE Engineering Software

10-18

The Shell Module


&KDSWHU The Nozzle Module

Introduction This module calculates required reinforcement under internal pressure and performs failure path calculations for nozzles in shells and heads, using the ASME Code, Section VIII, Division 1 rules, 2001, A-2001.

Purpose, Scope, and Technical Basis The Nozzle module calculates required wall thickness and area of reinforcement for a nozzle in a pressure vessel shell or head, and compares this area to the area available in the shell, nozzle and optional reinforcing pad. The module also calculates the strength of failure paths for the nozzles. The Nozzle module is based on the ASME Code, Section VIII, Division 1, Paragraph UG-37 through UG-45, 2001, A-2001. The calculation procedure is based on Figure UG-37.1. The module calculates the required thickness (for reinforcement conditions) based on inside diameter for the following vessel components: Component

Paragraph

Limitations Per UW-37

Cylinder

UG-27 (c) (1)

None

2:1 Elliptical Head

UG-32 (d) (1)

Nozzle concentric within 0.8D

Torispherical Head

UG-32 (e) (1)

Nozzle in spherical portion


UG-27 (d) (3)

None

The module evaluates nozzles at any angle (less than 90 degrees) away from the perpendicular, allowing evaluation of off angle or hillside nozzles. The Nozzle module takes full account of corrosion allowance. You enter actual thickness and corrosion allowance, and the module adjusts thicknesses and diameters when making calculations for the corroded condition. The Nozzle module also performs UCS-66 MDMT calculations for nozzles. Figure 11A shows geometry for the Nozzle module.

The Nozzle Module

11-1



Figure 11A - Geometry for The Nozzle Module

11-2

The Nozzle Module



Discussion of Input Data Main Input Fields Nozzle Description Enter a 15 character or less description of this nozzle. If you type in the description “MANWAY” the UG-45 check for minimum nozzle neck thickness will not be performed. Design Internal Pressure Enter the Internal Design Pressure. This is a non-zero positive value and is usually obtained from the design drawings or vessel design specification. Required information such as the required thickness tr and trn are determined from the design internal pressure. Design Temperature Enter the temperature associated with the design pressure. The PVElite program will automatically update materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Design External Pressure Enter the external design pressure. PVElite will compute the required thickness of the given geometry for the external pressure entered. If you are designing for a full vacuum you would enter a value of 15.00 psig. If you are entering an external pressure there are some prompts such as shell design length which will appear. PVElite will compute the required thickness for both external and internal pressure. It will then choose the greatest tr and proceed with the calculations. Maximum Allowable Pressure, New & Cold The normal entry in this field will be the minimum new and cold pressure of the major vessel components. When the program computes the areas for this case it will use ambient allowable stresses and 0 corrosion allowance. If this is the case that governs the area analysis, the corrosion allowance used in the remainder of the calculations will be set to 0.0 Shell, Nozzle, or Pad Material Name Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Allowable Stress at Design Temperature This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature.

The Nozzle Module

11-3



Allowable Stress at Ambient Temperature This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the ambient temperature. Is the Shell/Head/Nozzle Material Normalized? If your nozzle material has been produced to fine grain practice, check this box. The appropriate minimum design metal temperatures will be computed based on the normalized curve for this material from the chart UCS-66. Include Hydrostatic Head Component If your nozzle design needs to account for hydrostatic liquid head, then select this option. PVElite will add the hydrostatic pressure head to the internal head pressure for the required thickness calculation. Shell or Head Type Enter the type of shell for this shell section. Choose one of the following shell types:

ID Number

Shell or Head Type

1

Cylindrical Shell

2

Elliptical Head

3

Torispherical Head

4

Hemispherical Head or Spherical Shell

5

Conical Head or Shell

6

Welded Flat Head

The thickness of an elliptical head is analyzed as an equivalent spherical head, as specified in the Code, paragraph UG-37 (a). Similarly, the thickness of the spherical portion of a torispherical head is analyzed using the same paragraph. If your nozzle is outside 80% of the diameter of an elliptical head, or in the toroidal portion of a torispherical head, you must enter the required thickness to accurately perform the analysis. You must enter the required thickness (below) under the following circumstances: Shell Diameter Basis

If the vessel dimensions are specified on inside basis, pull down the ID selection. If the dimensions are based on the vessels outside diameter select the OD selection. For torispherical heads, select ID if the section is specified by inside crown radius, select ID if the section is specified by outside crown radius. Normally, for a flanged & dished torispherical head, the inside crown radius is equal to the vessel outside diameter. For flat heads, this value is ignored. Always enter the diameter of the flat head that is exposed to the pressure.

11-4

The Nozzle Module



Shell Diameter or Crown Radius for Torispherical Head Enter the diameter of the shell or head. For torispherical heads, enter the crown radius. For flat heads, enter the outside diameter of the head. For cones, enter the diameter of the cone at the point where the nozzle intersects the shell. Actual Thickness of Shell Enter the minimum thickness of the actual plate or pipe used to build the shell, or the minimum thickness measured for an existing vessel. Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. You should enter the minimum thickness. Enter Required Thicknesses The only time the required thickness must be entered is if the component being analyzed is a bolted flat head. Otherwise, the required thickness of the shell/head will be computed by the program. For hillside nozzles, as of Version 5.40, several changes have been made relating to the use of the required thickness. They are as follows:

•

If the user wishes to enter an offset and allow PVElite to compute the nozzle angle, the required thickness must be left blank.

•

If an angle less than 90 has been entered, or computed via the entered offset values, and the user would like to take credit for the Code 0.5 F-correction factor, the required thickness times the F-correction factor should be entered.

•

If an angle less than 90 has been entered and the user does not which to take credit for the Code 0.5 F-correction factor, the required thickness should be entered.

Shell Corrosion Allowance Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Rating of Attached Flange If your check this prompt the program will ask you the class and grade of the attached flange. The program will use these two items along with the temperature to rate the flange using the tables in ANSI B16.5. Modification of Reinforcement Limit Enter Y or N. You may enter any physical limitation which exists on the thickness available for reinforcement or the diameter available for reinforcement. An example of a thickness limitation would be a studding pad or nozzle stub which would not extend normal to the vessel wall as far as the thickness limit of the nozzle calculation. An example of a diameter limitation would be two nozzles close together, or a vessel seam for which you did not want to take an available area reduction. Set AREA1 or AREA2 Equal to 0 In some vessel design specifications it is mandated that no credit be taken for the area contributed by the shell or nozzle. You can enter the text “A1” or “A2” in this field. If you do so, that area will be set equal to 0. You can also enter “A1 A2”. This would give you no credit for area1 or area2. The Nozzle Module

11-5



Is the Nozzle Outside the 80% Diameter Limit? If the nozzle is outside of the spherical portion of the elliptical or torispherical head, check this field. Doing so will cause PVElite to use the standard internal pressure equation from UG-27 instead of the equation from UG-37. Nozzle Diameter Basis Enter 0 for nozzles where the diameter you give is inside diameter. Enter 1 for nozzles where the diameter you give is outside diameter. Actual or Nominal Diameter of Nozzle Enter the diameter of the nozzle. If you specify nominal or minimum for the nozzle size and thickness basis, then you must enter the nominal diameter of the nozzle in this field. Valid nominal diameters are: 0.125

2.010.0

0.25

2.512.0

0.375

3.014.0

0.50

3.516.0

0.75

4.018.0

1.00

5.020.0

1.25

6.024.0

1.5

8.030.0

Nozzle Size and Thickness Basis From the pull-down menu, select the appropriate size and thickness basis for the nozzle. For actual diameter and thickness, the program will use the actual diameter entered in the field above and the actual thickness entered in the field below. For nominal diameter and thickness, the program will look up the actual diameter based on the nominal diameter entered in the field above, and will look up the nominal thickness based on the schedule entered in the second field below. For minimum diameter and thickness, the program will look up the actual diameter based on the nominal diameter entered in the field above, and will look up the nominal thickness based on the schedule entered in the second field below. It will then multiply the nominal thickness by a factor of 0.875. Actual Schedule of Nozzle Enter the minimum actual thickness of the nozzle wall. Enter a value in this field only if you selected ACTUAL for the nozzle diameter and thickness basis. Otherwise enter a schedule in the field below. Nominal Thickness of Nozzle Enter the schedule for the nozzle wall. Enter a value in this field only if you selected NOMINAL or MINIMUM for the nozzle diameter and thickness basis. Otherwise enter a thickness in the field above. Type in the schedule for the nozzle, i.e. SCH 40. Available nozzle schedules are

11-6

The Nozzle Module



SCH 10

SCH 80

SCH STD

SCH 10S

SCH 80S

SCH X-STG

SCH 20

SCH 100

SCH XX-STG

SCH 30

SCH 120

SCH 40

SCH 140

SCH 40S

SCH 160

SCH 60 Required Thickness of Nozzle The program normally calculates the required thickness of the nozzle but under the following circumstances you must enter the required thickness:

•

When your job specification requires that no area be included from the nozzle. Enter the actual thickness minus the corrosion allowance.

•

When the nozzle is non-circular.

Nozzle Corrosion Allowance Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Efficiency of Shell Seam Through Which Nozzle Passes Enter the seam efficiency. The seam efficiency is used in the ‘area available’ calculations to reduce the area available in the shell. Note that for shell and nozzle wall thickness calculations, the seam efficiency is always 1.0. Insert Nozzle or Abutting Nozzle Select the insert or abutting nozzle from the pull-down menu. The nozzle type and depth of groove welds are used to determine the required weld thicknesses and failure paths for the nozzle. If the nozzle is welded to the outside of the vessel wall, it is abutting the vessel wall. If the hole in the vessel is bigger than the nozzle OD and the nozzle is welded into the hole, it is inserted. Figure UW-16.1 shows typical insert and abutting nozzles. Reinforcing Pad If there is a reinforcing pad on the nozzle, or if you wish to specify the geometry for a reinforcing pad, check this field.

Note

Although PVElite will design and recommend a reinforcing pad if one is needed, the analysis of areas is based only on what you have entered. If PVElite recommends a pad or a larger pad than the one you enter, you must go back into input and enter a pad of the correct size in order for the final configuration to be reflected in the final analysis.

ASME Code Weld Type The type of weld can optionally be netered in this field. If it is a type A, B, C, D, E, F-1, F2, F-3, F-4, G, X-1, Y-1, or Z-1 weld then PVElte will not perform the weld calculations If it is a type I, J, K, L, X-2, Y-2, Z-2 weld, then PVElite will perform the additional weld

The Nozzle Module

11-7



size calculations per UW-16(d)(1). The Code exempts these calculations per paragraph UW-15 when one of the above weld classifications such as "A" is used. If you wish PVElite to perform the weld strength calculation regardless of the type of weld geometry, leave this field blank. Compressed Air, Water, or Steam Service Checking this box sets the minimum thickness for use in the UG-45 Calculations. If left unchecked, a value of 1/16-in. will be used. Otherwise, if checked, a value of 3/32-in. will be incorporated. See UG-16 for more details. Manway or Access /Inspection Opening The ASME code states that it is not required to perform UG-45 minimum nozzle neck thickness calculations on manways and inspection openings. If this box is checked, the program will not perform these calculations. Nozzle Angle Geometry Non-radial nozzles can be specified by entering the angle between the vessel and the nozzle centerlines, and the offset from vessel centerline. This vessel-nozzle centerline angle can vary from 0 to a limiting value depending upon the specific gravity. Figure 1 below illustrates these dimensions. To specify a radial nozzle on a head or shell just click the "Is Radial ..’ checkbox. In this case the input for the offset dimension and vessel -nozzle centerline angle are optional, only required for the graphic and not for the analysis.

Figure 11B - Radial Nozzle

Hillside nozzles and some angular nozzles are subject to calculations to meet area requirements in both planes of reinforcement. In these cases CodeCalc automatically checks the area requirements in both the planes using the corresponding lengths of the nozzle opening. For integral construction, the Code F correction factor of 0.5 will automatically be applied in the hillside direction. If the connection is pad reinforced, a value of 1.0 will be used. The F factor is used to account for the fact that the longitudinal stress is one half of the hoop stress. The use of the F factor is limited to nozzles located on cylindrical and con-

11-8

The Nozzle Module



ical sections. A hill-side nozzle example based on ASME VIII Div 1 Appendix L-7.7 is illustrated in the CHECKS file under the PVElite examples directory - Nozzle items 10 and 11. Some examples are shown below.

Figure 11C - Hillside and Angular Nozzle

Y angle or lateral nozzles can be specified in case of conical and cylindrical sections by clicking on the "Is Lateral..." checkbox. In this case only the vessel-nozzle centerline angle needs to be specified. The following figure shows an example.

Figure 11D - Y-Angle Nozzle on a Cylinder and on a Cone

The Nozzle Module

11-9



For users of version prior to 6.40 the input specification for non-radial and non-hillside nozzles has changed. The current requirement is the angle between the centerline of the nozzle and the centerline of the vessel. Pop-Up Input Fields Enter the Shell Design Length for External Pressure Enter the design length of the section, typically the length of the vessel plus one third the depth of the heads or, alternatively, the distance between stiffening rings. For a vessel with 2 elliptical heads and no intermediate stiffeners, the design length is the tangent to tangent length plus the shell diameter /6. For a vessel with 2 spherical heads and no intermediate stiffeners, the design length is the tangent length plus the diameter /3. For a vessel with 2 flanged and dished heads and no intermediate stiffeners, the design length is the tangent length plus the diameter /9. When analyzing a conical head enter the axial length of the cone. If any other head types are being analyzed, enter a 0 here and you must enter the required thickness of the component in the required field. Print Intermediate Calcs for External Pressure If checked, PVElite will print out the parameters used for external pressure design. If this field is not checked, PVElite will not print out these intermediate computations. Operating Liquid Density Enter the density of the operating fluid here. This value will be multiplied by the height of the liquid column in order to compute the static head pressure. You can enter a number of specific gravity units and CodeCalc will convert the number entered to the current set of units. To do this, enter a number followed by the letters "sg". Height of Liquid Column, Operating Enter the distance from the nozzle to the surface of the liquid. The head pressure is determined by multiplying the liquid density by the height of the fluid to the point of interest. Enter the Aspect Ratio for Elliptical Heads The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head the aspect ratio is 2.0. Inside Crown Radius (L) of the Torispherical Head Enter the inside crown radius of torispherical head. Inside Knuckle Radius of the Torispherical Head Enter the inside knuckle radius of the torispherical head. This value is typically 0.17 * the head inside diameter.

11-10

The Nozzle Module



Half Apex Angle for Conical Sections Enter the half-apex angle for cones or conical sections. The maximum value of the half apex angle for cones under the internal pressure and without toriconical transitions is 30 degrees. The largest angle for cones under internal pressure and with toriconical sections is 60 degrees. The largest angle for cones under external pressure is 60 degrees. If you exceed these values the program will run, but with a warning. Attachment Factor for Welded Flat Heads Enter the attachment factors for the welded flat head. These factors are found in Section VIII, Division 1, Figure UG-34. The typical value for an attachment factor is 0.3. Large Diameter for Non-Circular Flat Heads If you have a non-circular welded flat head, enter the large dimension in this field, and enter the small dimension as the component diameter. Class for Attached B16.5 Flange Select the applicable class of the attached ANSI flange. The following flange classes are available: CL CL CL CL CL CL CL

150 300 400 600 900 1500 2500

Grade for Attached B16.5 Flange Select the appropriate material grade for the attached ANSI flange. The following flange grades are available:

GR 1.1 GR 1.2 GR 1.4 GR 1.5 GR 1.7 GR 1.9 GR 1.10 GR 1.13 GR 1.14

Med C Steel High C Steel Low C Steel C-1/2Mo 1/2Cr-1/2Mo, Ni-Cr-Mo 1-1/4Cr-1/2Mo 2-1/4Cr-1Mo 5Cr-1/2Mo 9Cr-1Mo

GR 2.1 GR 2.2 GR 2.3 GR 2.4 GR 2.5 GR 2.6 GR 2.7

Type 304 Type 316 Type 304L,316L Type 321 Type 347,348 Type 309 Type 310

Physical Maximum for Nozzle Diameter Limit Enter the maximum diameter for material contributing to nozzle reinforcement. An example of a diameter limitation would be two nozzles close together, or a vessel seam for which you did not want to take an available area reduction.

The Nozzle Module

11-11



Physical Maximum for Nozzle Thickness Limit Enter the maximum thickness for material contributing to nozzle reinforcement. An example of a thickness limitation would be a studding pad or nozzle stub which would not extend normal to the vessel wall as far as the thickness limit of the nozzle calculation. Nozzle Outside Projection Enter the distance the nozzle projects outward from the surface of the vessel. This will usually be to the attached flange or cover. This length will be used for weight calculations and for external pressure calculations. Depth of Groove Weld Between Nozzle and Vessel Enter the total depth of the groove weld. Most groove welds between the nozzle and the vessel are full penetration welds. Thus the depth of the weld would be the same as the depth of the component, that is the thickness of the nozzle. If the nozzle is attached with a partial penetration weld, or just a fillet welds, enter the depth of the partial penetration or a zero, respectively, in this field. Weld Leg Size Between Inward Nozzle and Inside Shell Enter the size of one leg of the fillet weld between the inward nozzle and the inside shell. Nozzle Inside Projection Enter the projection of the nozzle into the vessel. The program uses the least of the inside projection and the thickness limit with no pad to calculate the area available in the inward nozzle. Therefore, you may safely enter a large number such as six or twelve inches if the nozzle continues into the vessel a long distance. Weld Leg Size for Fillet Between Nozzle and Shell or Pad Enter the size of one leg of the fillet weld between the nozzle and the pad or shell. Pad Outside Diameter Along Vessel Surface Enter the outside diameter of the pad. The diameter of the pad is entered as the length along the vessel shell - not the projected diameter around the nozzle, although these two values will be equal when the nozzle is at 90 degrees. Pad Thickness Enter the thickness of the pad. Any allowances for external corrosion should be taken into account for the pad thickness. Pad Weld Leg Size at Outside Diameter Enter the size of one leg of the fillet weld between the pad OD and the shell. Note that if any part of this weld falls outside the diameter limit, the weld will not be included in the available area. Depth of Groove Weld Between Pad and Nozzle Neck Enter the total depth of the groove weld. Most groove welds between the pad and the nozzle are full penetration welds. Thus the depth of the weld would be the same as the depth of the component, that is the thickness of the pad. If the pad is attached with a partial pen-

11-12

The Nozzle Module



etration weld, or just a fillet weld, enter the depth of the partial penetration or a zero, respectively, in this field. Discussion of Results

Status Bar In CodeCalc, the Status bar, which is located at the bottom of the application, is divided into several panes, which compute and display critical results as the vessel is being modeled. The information includes:

•

Reinforcement Area Contributions, Available Area, Required Area

•

MDMT

•

Warning Messages if UG-45 Fails

Note

Results that display red in color indicate a failure.

Actual Nozzle Diameter and Thickness If you specified an ‘actual’ basis for nozzle diameter and thickness, the diameter and thickness shown will be the same as those which you entered. If you specified ‘Nominal’, these values will be the nominal diameter and thickness found in the programs pipe size tables. If you entered minimum the program will have looked up the diameter and thickness in the pipe size tables and then multiplied the thickness by 0.875. Required Thickness of Shell and Nozzle The required thickness for the shell and nozzle will be calculated as follows: CYLI (and the nozzle wall) - Calculated per UG-27 or as given by the user. HEMI-

Calculated per UG-27 or as given by the user.

TORI-


ELLI-


CONE-


FLAT-


The joint efficiency used in this calculation is always 1.0. In 1989 we submitted a request for interpretation to the ASME Code in order to show that the use of 1.0 under all circumstances was justified. The reply was published in the A-90 addenda as Interpretation VIII1-89-171. The question and reply were as follows: Question: In reinforcement calculations, is the joint efficiency used in calculating the required thickness of the vessel wall tr and the required thickness of the wall trn 1.0 regardless of the joint efficiency determined for the vessel wall and nozzle wall from the rules in UW-12, provided the nozzle does not pass through a weld? Reply: Yes

The Nozzle Module

11-13


Note


The program takes into account the case where the nozzle passes through a weld by asking the joint efficiency of the weld, if any.

Effective Material Diameter and Thickness Limits The diameter limit is the maximum distance from the centerline of the nozzle along the vessel wall which can be taken credit for when calculating available areas in the shell or a pad. If your pad has a greater diameter than the diameter limit, only the area inside the limit will be credited. If you entered a DMAX value for the analysis, that value will be used only if it is the least of all the diameter limit candidates. The thickness limit is the distance from the vessel surface along the nozzle axis which can be taken credit for when calculating the areas available in the nozzle wall and the pad. If your inward nozzle projection or outward pad projection are greater than the diameter limit, only the area inside the limit will be credited. If you entered a TMAX value for the analysis, that value will be used only if it the least of all the thickness limit candidates. UG-45 Minimum Nozzle Neck Thickness The design rules from paragraph UG-45 for minimum nozzle neck thickness are used. If the thickness used by PVElite for your nozzle calculation is less than required by UG-45, your Code Vessel is in violation of this paragraph. Required and Available Areas The area required is calculated per UG-37(c). For external pressure and flat heads, this value is multiplied by 0.5. The required areas are calculated per Fig. UG-37.1.

Note

The program uses dl-d, (Diameter limit minus inside hole radius) in the calculate for area available in shell. This is because the Code wrongly assumes that the dl-d is always equal to d, which is only true when the natural diameter limit is used. Since we allow the user to enter a reduced diameter limit, we could not use the pure Code equation.

Selection of Reinforcing Pad The program gives up to three possible reinforcing pad selections. The first is a pad thickness based on the given pad diameter. The second is a pad diameter based on the given pad thickness. Finally, the program selects a thickness based on the thinner of the shell and nozzle walls, and calculates a required diameter. If this exceeds the diameter limit, it selects a thickness based on a pad at the diameter limit. All thickness results are rounded up to the nearest sixteenth, while all diameter results are rounded up to the nearest eighth. Large Diameter Nozzle Calculations For large diameter nozzles, the rules of Appendix 1-7 require that two-thirds of the reinforcement be within 0.75 of the natural diameter limit for the nozzle. If the calculated value of the percent within this limit is greater than 66%, the nozzle is adequately reinforced for the large diameter rules. For a large nozzle geometry to meet Code requirements both sets of area calculations must meet their respective area requirements.

11-14

The Nozzle Module



Maximum Allowable Working Pressure Calculation The MAWP for reinforcement is an estimate, usually accurate to within 1 or 2 psi. Enter the given MAWP as the design pressure to check its accuracy. The MAP for the flange is based on ANSI B16.5 tables for the given grade and class of flange. Minimum Design Metal Temperature The minimum design metal temperature is computed for the nozzle. The program considers UG-20(f), UCS-66 and UCS-66.1 when performing these calculations. Weld Size Calculations Nozzle weld thicknesses are based on Figure UW-16.1. The outward nozzle weld is compared to the cover weld required by the Code. Note that the minimum dimension of a weld is 0.7 times its leg dimension. Note also that for cover welds the maximum weld the Code requires is 0.25 inches. The pad weld requirement is typically at least one half of the element thickness. In addition to the cover welds, the total groove weld plus cover weld for inserted nozzles must be at least 1.25 times the minimum element thickness. Weld Strength Calculations The strength of connection elements is their cross sectional area times the allowable unit stress for the element. The last two terms in the equations shown give the stress factor and basic allowable stress for the element in the direction considered. Failure Path Calculations The failure paths differ based on whether there is a reinforcing pad, whether the nozzle is inserted or abutting, and whether there is an inward projection. Note that the strength of each path must exceed either the W value or the W#-# associated with that path. Note also that UW-15(b) indicates that no strength calculations for nozzle attachment welds are required for figure UW-16.1, sketches (a), (b), (c), (d), (e), (f-1), (f-2), (f-3), (f-4), (g), (x-1), (y-1), and (z-1). Iterative Results Per Pressure, Area, and UG-45 Assuming the same corrosion allowance for the shell and nozzle, the maximum (failure) corrosion allowance, the minimum (discard) nozzle thickness and the minimum (failure) shell thickness are computed. The user can project the nozzle service lifetime based on the rate of corrosion and the above results.

The Nozzle Module

11-15

Example Problems


Example Problems The \example directory contains the input for most of the other example problems for nozzles shown in Appendix L of the Code. The file these examples are contained in is CHECKS. Some large nozzle examples are included in LG_NOZZLE.CCI.

Pressure Vessel Component Analysis Large Nozzle Examples per ASME VIII Div 1 Appendix 1-7 PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON FileName : LG_NOZZL --------------------------------- Page 1 Nozzle Analysis : 24" Nozzle

INPUT VALUES, NOZZLE NUMBER


ITEM:

1,

( Case 1 )

11:00am,

Description: 24"

05/14/98

Nozzle

P

100.00

psig


TEMP

350.00

F

Design External Pressure

PEXT

100.00

psig

TEMPEX

350.00

F

( Case 2 )


Shell Material

(Not Normalized or NA)

Shell Allowable Stress at Temperature Shell Allowable Stress At Ambient

SA-516 70 S

17500.00

psi

SA

17500.00

psi

Outside Diameter of Cylindrical Shell

D

55.2500

in.


L

184.5000

in.

Actual Thickness of Shell or Head

T

.9900

in.

CAS

.3125

in.

ANGLE

90.00

Degrees

Corrosion Allowance for Shell or Head

Angle between Nozzle and Shell or Head

11-16

1,

The Nozzle Module


Example Problems

Nozzle Material (Not Normalized or NA)

SA-106 B

Nozzle Allowable Stress at Temperature Nozzle Allowable Stress At Ambient

Diameter Basis for Nozzle

SN

15000.00

psi

SNA

15000.00

psi

BASISN

OD

Diameter of Nozzle

DIA

Nozzle Size and Thickness Basis

DBN

Actual Thickness of Nozzle

THK

1.0660

in.

Corrosion Allowance for Nozzle

CAN

.3125

in.

Joint Efficiency of Shell Seam at Nozzle

ES

1.00

Joint Efficiency of Nozzle Neck

EN

1.00

Insert or Abutting Nozzle Type

24.0000

in.

Actual

NTYP

Insert

Outward Projection of Nozzle

HO

4.0000

in.

Weld leg size between Nozzle and Pad/Shell

WO

.5000

in.

Groove weld depth between Nozzle and Vessel WGNV

.6250

in.

Pad Material (Not Normalized or NA)

SA-516 70

Pad Allowable Stress at Temperature

SN

17500.00

psi

SNA

17500.00

psi

Diameter of Pad along vessel surface

DP

31.0000

in.

Thickness of Pad

TP

.6250

in.

Weld leg size between Pad and Shell

WP

.6250

in.

WGPN

.6250

in.

Pad Allowable Stress At Ambient

Groove weld depth between Pad and Nozzle ASME Code Weld Type per UW-16.1

NOZZLE CALCULATION, NOZZLE NUMBER

1,

Description: 24"

Actual Nozzle Diameter Used in Calculation Actual Nozzle Thickness Used in Calculation

Nozzle

24.000

in.

1.066

in.

Internal Pressure Results for SHELL/HEAD :

Required thickness per UG-37(a) of Cylindrical Shell, TR,

CASE 1

= (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (100.00*55.2500/2)/(17500*1.00+0.4*100.00) = .1575 in.

External Pressure Results for SHELL/HEAD :


1, Description: 24"

Nozzle

ASME Code, Section VIII, Division 1, 1995 & A-96


CS-2

at


350.00 28500000.00

F psi


OD

SLEN

D/T

L/D

Factor A

B

.6775

55.2500

184.50

81.55

3.3394

.0005286

7532.86

EMAWP=(4*B)/(3*DT)=(4*7532.8560)/(3*81.5498)=123.1616 psig


The Nozzle Module

OD

SLEN

D/T

L/D

Factor A

B

11-17

Example Problems


.6233

55.2500

184.50

88.64

3.3394

.0004665

6647.86

EMAWP=(4*B)/(3*DT)=(4*6647.8600)/(3*88.6356)=100.0029 psig

Results for Maximum Length Between Stiffeners (Slen): TCA

OD

SLEN

D/T

L/D

Factor A

B

.6775

55.2500

227.22

81.55

4.1126

.0004292

6116.58

EMAWP=(4*B)/(3*DT)=(4*6116.5810)/(3*81.5498)=100.0056 psig


123.16

psig


100.00

psig


.9358

in.


.9900

in.

227.220

in.

184.50

in.

Maximum Length for Thickness and Pressure Actual Length as entered by User

Internal Pressure Results for NOZZLE :

Required thickness per UG-37(a) of Nozzle Wall, TRN

CASE 1

= (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (100.00*24.0000/2.0)/(15000*1.00+0.4*100.00) = .0798 in.

External Pressure Results for NOZZLE :



1, Description: 24"

CS-2

at


350.00 28500000.00

Nozzle

F psi


OD

SLEN

D/T

L/D

.7535

24.0000

4.00

31.85

.1667

Factor A

B

.0474581 17600.00

EMAWP=(4*B)/(3*DT)=(4*17600.0000)/(3*31.8514)=736.7556 psig


OD

SLEN

D/T

L/D

.1183

24.0000

4.00

202.85

.1667

Factor A

B

.0029529 15215.24

EMAWP=(4*B)/(3*DT)=(4*15215.2400)/(3*202.8471)=100.0112 psig

Results for Maximum Length Calculation: No Closure TCA

OD

SLEN

.7535

24.0000

.17E+24

D/T

L/D

31.85 .6911E+22

Factor A

B

.0010843 12079.53

EMAWP=(4*B)/(3*DT)=(4*12079.5300)/(3*31.8514)=505.6627 psig


736.76

psig


100.00

psig


.4308

in.

1.0660

in.

.1659E+24

in.

4.00

in.

Actual Thickness as entered by User Maximum Length for Thickness and Pressure Actual Length as entered by User

UG-40, Thickness and Diameter Limit Results : CASE 1

11-18

The Nozzle Module


Example Problems

Effective material diameter limit,

DL

44.9860

in.

TLNP

1.6938

in.

Effective material thickness limit, pad side TLWP

1.6938

in.

Effective material thickness limit, no pad

RESULTS of NOZZLE REINFORCEMENT AREA CALCULATIONS: AREA AVAILABLE, A1 to A5

Design

External

Mapnc

Area Required

AR

3.576

7.077

NA

sq.in.

Area in Shell

A1

11.584

1.207

NA

sq.in.

Area in Nozzle Wall

A2

1.956

1.844

NA

sq.in.

Area in Inward Nozzle

A3

.000

.000

NA

sq.in.

Area in Welds

A4

.605

.605

NA

sq.in.

Area in Pad

A5

4.375

4.375

NA

sq.in.

ATOT

18.521

8.031

NA

sq.in.

TOTAL AREA AVAILABLE

Pressure Case 2 Governs the Analysis

Nozzle Angle Used in Area Calculations

90.00

Degs.

The area available without a pad is Insufficient. The area available with the given pad is Sufficient.

SELECTION OF POSSIBLE REINFORCING PADS:

Diameter

Based on given Pad Thickness:

29.5000

Thickness .6250

in.

Based on given Pad Diameter:

31.0000

.5000

in.

Based on Shell or Nozzle Thickness:

27.5000

1.0000

in.

Reinforcement Area Required for Nozzle: AR = 0.5*(DLR*TR+2*THK*TR*(1-FFR1)) per UG-37(d) or UG-39 AR = 0.5*(22.4930*.6233+2*(1.0660-.3125)*.6233*(1.00-.86)) AR =

7.077 sq.in.

Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell (A1): A1 = (DL-DLR)*(ES*(T-CAS)-TR)-2*(THK-CAN)*(ES*(T-CAS)-TR)*(1-FFR1) A1 = (44.986-22.493)*(1.00*(.9900-.313)-.623)-2*(1.066-.313) *(1.00*(.9900-.3125)-.6233)*(1.0-.86) A1 =

1.207 sq.in.

Area Available in Nozzle Wall, no Pad: A2NP = ( 2 * MIN(TLNP,HO) ) * ( THK - CAN - TRN ) * FFR2 A2NP = ( 2 * 1.6938 ) * ( 1.0660 - .3125 - .1183 ) * .86 ) A2NP = 1.844 sq.in.

Area Available in Nozzle Wall, with Pad: A2WP = (2*MIN(TLWP,HO))*(THK-CAN-TRN)*FFR2 A2WP = ( 2 * 1.6938 ) * ( 1.0660 - .3125 - .1183 ) * .86 ) A2WP = 1.844 sq.in.

Area Available in Welds, no Pad: A4NP = WO^2*FFR2 + (WI-CAN/0.707)^2*FFR2 A4NP = .5000^2 * .86 + ( .0000 )^2 * .86 A4NP = .214 sq.in.

Area Available in Welds, with Pad:

The Nozzle Module

11-19

Example Problems


A4WP = WO^2*FFR3+(WI-CAN/0.707)^2*FFR2+WP^2*FFR4 A4WP = .5000^2 * .86 + ( .0000 )^2 * .86 + .6250^2 * 1.00 A4WP = .605 sq.in.

Area Available in Pad: A5 = (MIN(DP,DL)-(DIA+2*THK))*(MIN(TP,TLWP,TE))*FFR4 A5 = ( 31.0000 - 24.0000 ) * .6250 * 1.00 A5 =

4.375 sq.in.

UG-45 Minimum Nozzle Neck Thickness Requirement: = Max(Min(Max(Max(UG45B1,UG16B),Max(UG45B2,UG16B)),UG45B4),UG45A) = Max(Min(Max(Max( .4700, .3750),Max( .4700, .3750)), .6406), .4308) =

.4700 < Minimum Nozzle Thickness 1.0660 in. OK

M.A.W.P. RESULTS FOR THIS NOZZLE GEOMETRY Approximate M.A.W.P. for given geometry Nozzle is O.K. for the External Pressure

AMAP

304.2

psig

AMAPEXT

100.0

psig

Weight of Nozzle, with Pad, Uncorroded

161.94

lb.

Weight of Nozzle, with Pad, Corroded

123.84

lb.

MINIMUM DESIGN METAL TEMPERATURE RESULTS: Nozzle Minimum Temp. w/o impact per Fig. UCS-66 Minimum Temp. at operating stress

Shell

Pad

34

31

6

F

-76

-79

-104

F

NA

-20

-20

F

Minimum Temp. w/o impact per UG-20(f)

Nozzle MDMT Thickness Calc. per UCS-66 1(b), MIN(tn,t,te) Minimum Metal Temp. w/o impact per Fig. UCS-66 Minimum Metal Temp. at Required thickness Minimum Metal Temp. w/o impact per UG-20(f)

6

F

-104

F

-20

F

SUMMARY of REINFORCEMENT AREAS for LARGE NOZZLE (Per Appendix 1-7):

AREA REQUIRED for reinforcement of nozzle

AREA AVAILABLE, A1 to A5

AR

4.719

No Pad

With Pad

sq.in.

Area Available in Shell

A1

.597

.597

sq.in.

Area Available in Nozzle Wall

A2

1.844

1.844

sq.in.

Area Available in Inward Nozzle

A3

.000

.000

sq.in.

Area Available in Welds

A4

.214

.605

sq.in.

Area Available in Pad

A5

.000

4.375

sq.in.

ATOT

2.656

7.422

sq.in.

TOTAL AREA AVAILABLE

The area available without a pad is Insufficient. The area available with the given pad is Sufficient.

WELD SIZE CALCULATIONS, NOZZLE NUMBER

1,

Description: 24"

Minimum thickness for nozzle/shell welds Minimum thickness for pad/shell welds

11-20

Nozzle

TMIN

.6250

in.

TMINPAD

.6250

in.

Results Per UW-16.1,

Required Thickness

Actual Thickness

Nozzle Weld

.2500 = Min per Code

.3500 = 0.7 * WO

, in.

The Nozzle Module


Example Problems

Pad Weld

.3125 = 0.5*TMINPAD

.4375 = 0.7 * WP

, in.

WELD STRENGTH AND WELD LOADS PER UG-41.1, SKETCH (a) OR (b) W

= (AR-A1+2*(THK-CAN)*FFR1*(E1(T-CAS)-TR))*S

W

= ( 7.0775 - 1.2066 + 2 * ( 1.0660 - .3125 ) * .8571 *

W

= 103965. lb.

( 1.00 * ( .9900 - .3125) - .6233 ) ) * 17500

W1 = (A2+A5+A4-(WII-CAN/.707)^2*FFR2)*S W1 = ( 1.8443 + 4.3750 + .6049 - .1953 * .86 ) * 17500 W1 = 116494. lb. W2 = (A2+A3+A4+(2*(THK-CAN)*(T-CAS)*Fr1))*S W2 = ( 1.8443 + .0000 + .2143 + .8751 ) * 17500 W2 = 51340. lb. W3 = (A2+A3+A4+A5+(2*(THK-CAN)*(T-CAS)*Fr1))*S W3 = ( 1.8443 + .0000 + 4.3750 + .6049 + .8751 ) * 17500 W3 = 134739. lb.

STRENGTH OF CONNECTION ELEMENTS FOR FAILURE PATH ANALYSIS

SHEAR, OUTWARD NOZZLE WELD: SONW = (PI/2)*DLO*WO*0.49*SNW SONW = ( 3.1416 / 2.0 ) * 24.0000 * .5000 * 0.49 * 15000 SONW = 138544. lb.

SHEAR, PAD ELEMENT WELD: SPEW = (PI/2)*DP*WP*0.49*SEW SPEW = ( 3.1416 / 2.0 ) * 31.0000 * .6250 * 0.49 * 17500 SPEW = 260973. lb.

SHEAR, NOZZLE WALL: SNW = (PI*(DLR+DLO)/4.0)*(THK-CAN)*0.7*SN SNW = ( 3.1416 * 11.6233) * ( 1.0660 - .3125 ) * 0.7 * 15000 SNW = 288902. lb.

TENSION, PAD GROOVE WELD:

TPGW = (PI/2.0)*DLO*WGPN*0.74*SEG TPGW = ( 3.1416 / 2.0 ) * 24.0000 * .6250 * 0.74 * 15000 TPGW = 261538. lb.

TENSION, NOZZLE GROOVE WELD: TNGW = (PI/2)*DLO*(WGNVI-CAS)*0.74*SNG TNGW = ( 3.1416 / 2.0 ) * 24.0000 * ( .6250 - .3125 ) * 0.74 * 15000 TNGW = 130769. lb.

STRENGTH OF FAILURE PATHS: PATH11 = ( SPEW + SNW ) = ( 260973 + 288901 ) = 549874 lb. PATH22 = ( SONW + TPGW + TNGW + SINW ) = ( 138544 + 261537 + 130768 + 0 ) = 530850 lb. PATH33 = ( SPEW + TNGW + SINW ) = ( 260973 + 130768 + 0 ) = 391741 lb.

SUMMARY OF FAILURE PATH CALCULATIONS: Path 1-1 = 549875. lb., must exceed W = 103965. lb. or W1 = 116494. lb.

The Nozzle Module

11-21

Example Problems


Path 2-2 = 530851. lb., must exceed W = 103965. lb. or W2 =

51340. lb.

Path 3-3 = 391742. lb., must exceed W = 103965. lb. or W3 = 134739. lb.

Iterative Results per Pressure, Area and UG-45: (Assuming same Corr. Allowance for shell and nozzle) Maximum (failure) Corrosion Allowance:

.347 in.

Minimum (failure) Nozzle Thickness:

.719 in.

Minimum (failure) Shell

.643 in.

Thickness:


11-22

The Nozzle Module


&KDSWHU The Flange Module

Introduction The PVElite Flange module calculates actual and allowable stresses for all types of flanges designed and fabricated to the ASME Code, Section VIII, Division 1. The module uses the Code rules found in Appendix 2 of the 2001 Code, A-2001.

Purpose, Scope, and Technical Basis The flange design rules incorporated in the Code were based on a paper written in 1937 by Waters, Westrom, Rossheim, and Williams. These rules were subsequently published by Taylor Forge in 1937, and were incorporated into the Code in 1942. For all practical purposes they have been unchanged since that time. The Taylor Forge bulletin, frequently republished, is also still available, and is one of the most useful tools for flange analysis. The input and results for the PVElite flange program are roughly modeled on the Taylor Forge flange design sheets. The flange analysis model assumes that the flange can be modeled as stiff elements (the flange and hub) and springs (the bolts and gaskets). The initial bolt loads compresses the gasket. This load needs to be high enough to seat (deform) the gasket, and needs to be enough higher to seal even when pressure is applied. The pressure load adds to the bolt load and unloads the gasket. Analysis of a typical flange includes the following steps: 1. Identify operating conditions and materials: determine allowable stresses for the flange material and the bolting at both ambient and operating temperatures, from the Code tables of allowable stress. 2. Identify the gasket material and flange facing type. Determine the effective width and effective diameter of the gasket and the gasket factors from the Code charts (Tables 25.1 and 2-5.2). 3. From the design pressure and the gasket information, calculate the required area of the bolts. Calculate the actual area of the bolts, and make sure it is greater than the required area. Based on the bolt areas and allowable stresses, calculate the flange design bolt loads. 4. Calculate the bending moments on the flange. In each case the bending moment is the product of a load (pressure, gasket load, etc.) and the distance from the bolt circle to the point of application of the load. The final result is one bending moment for operating conditions and a second for gasket seating conditions.

The Flange Module

12-1



The stresses on a given flange are determined entirely by the bending moment on the flange. All the loads on the flange produce bending in the same direction (i.e., counterclockwise) and this bending is resisted by the ring behavior of the flange, and in integral flanges by the reaction of the pipe. 5. Based on the flange type (Code Figure 2-4) calculate hub factors and other geometry factors for the flange. These are found in Code figures 2-7.1, 2-7.2, 2-7.3, 2-7.4, 2-7.5, and 2-7.6. Formulae are also given in the Code so that computer programs can consistently arrive at the answers that are normally selected from charts in the appendix. These formulae are implemented in the PVElite flange program. 6. Calculate stress formula factors based on the geometry factors and flange thickness. 7. Finally, calculate flange stresses using the stress formula factors and the bending moments. Compare these stresses to the allowable stresses for the flange material. S = k(geometry)*M/t^2 That is, a constant dependant on the flange geometry times the bending moment, divided by some thickness squared, either the thickness of the flange or the thickness of the hub. The calculation procedures and format of results in this program are similar to those given in “Modern Flange Design,” Bulletin 503, Edition VII, published by Taylor Forge. The Flange module includes the capability to analyze a given flange under the bolting loads imposed by a mating flange. The module also takes full account of corrosion allowance. You enter uncorroded thicknesses and diameters which the program adjusts before performing the calculations. The module can treat corrosion in a special manner based on the input of a Yes/No question in the input. The module can also be used for two levels of flange design. The PARTIAL option forces the program to calculate the minimum flange thickness for a given geometry. The DESIGN option forces the program to select all of the relevant flange geometry including bolt circle, number of bolts, outside diameter, thickness, and hub geometry.

12-2

The Flange Module

PVElite -User Guide


.

Figure 12A - Geometry for The Flange Module

The Flange Module

12-3



Discussion of Input Data Main Input Fields Flange Number Enter the flange ID number. It is recommended that the flange numbers start at 1 and increase sequentially. If this field is left blank PVElite will assume there is no data here to be analyzed. The only exception to this is the first element, if an analysis is attempted and the item number is blank, PVElite will assign a value of 1 to the item number. Flange Designation Enter an alpha-numeric tag for this flange. This entry is optional. When performing a partial analysis, PVElite iterates for the required thickness of the flange. The final set of results you see is made using the final required thickness. If you would like to see the results using the input thickness, then enter a colon “:” as the last character in the description. In both cases, PVElite will determine the required thickness. Flange Type Enter the flange type number for this flange. Flange types are

•

Integral Weld Neck

•

Integral Slip On

•

Integral Ring

•

Loose Slip On

•

Loose Ring

•

Lap Joint

•

Blind

•

Reverse

There are essentially only two categories of flanges for purposes of analysis. These are integral type flanges, where the flange and the vessel to which it is attached behave as a unit, and loose types, where the flange and the vessel do not behave as a unit. Within these categories, however, there are several additional subdivisions. Weld Neck Flanges These have a hub which is butt welded to the vessel. Slip-on Flanges These have hubs, and are normally analyzed as loose type flanges. To qualify as integral type flanges they required a penetration weld between the flange and the vessel. Ring Flanges These do no have a hub, though they frequently have a weld at the back of the flange. They are normally analyzed as loose, but may be analyzed as integral if a penetration weld is used between the flange and the vessel.

12-4

The Flange Module

PVElite -User Guide


Lap Joint Flanges These flanges may or may not have a hub, but they are completely disconnected from the vessel, bearing only on a vessel ‘lap’. They are always analyzed as loose. Reverse Geometry Flange Here the gasket seat is on the inside of the shell diameter. These use integral flange rules, which are suitably modified for the reversal of the bending moments. See Appendix 2-13. Loose-Type Flanges, especially lap joints, may be split A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange (without splits) using 0.75 times the design moment. The pair of rings shall be assembled so that the splits in one ring shall be 90 deg. from the splits in the other. Flat Face Flanges with Full Face Gaskets A special type of gasket geometry, which is not included in the Code sketches, nor even in the Code design rules, is the flange with a flat face and a gasket that extend from the ID of the flange to the OD, beyond the bolt circle. The gaskets used with this type of flange are usually quite soft. These flanges can be analyzed using the Taylor Forge calculation sheets. Analysis Type Enter the analysis type for the computations to be performed on this flange. Analyze For this analysis type, the complete flange definition must be given by the user. The program will compute the resulting stresses. Partial For this analysis type, all information except for the flange thickness must be specified. The program will select a flange thickness such that the resulting flange stress equals the allowable stress. Design For this analysis type, only the flange diameter and thickness, gasket and flange face geometry, and gasket properties are specified. The program computes all other flange dimensions and stresses. Design Pressure Enter the internal design pressure. If the value entered in this field is negative, it will be treated as external pressure. Design Temperature Enter the design temperature for the flange. This temperature will be used to interpolate the material allowable tables and external pressure curves.

The Flange Module

12-5



Flange/Bolt Material Specification Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Allowable Stress at Design Temperature This entry is automatically filled in by the program by entering a material specification.

Caution


Allowable Stress at Ambient Temperature This entry is automatically filled in by the program by entering a material specification.

Caution


Flange Thickness Enter the flange thickness. The corrosion allowance will be subtracted from this value. Corrosion Allowance Enter the corrosion allowance for this flange. The value entered here will be subtracted from the flange and hub thicknesses to obtain the thicknesses actually used in the computations. Include Corrosion in Flange Thickness Calculations The flange thickness is used in several places throughout Appendix 2. The Code states that every dimension used should be corroded. In the flange stress calculations the flange thickness is used. However, some feel that the corrosion should not be taken off of the thickness for the stress calculations. Flange ID Enter the inner diameter of the flange. For integral type flanges, this value will also be the inner pipe diameter. This value is refereed to as “B” in the ASME code. The corrosion allowance will be used to adjust this value - two times the corrosion allowance will be added to the uncorroded ID given by the user). For a blind flange this entry should be 0. Flange OD Enter the outer diameter of the flange. This value is referred to as “A” in the ASME code. Shell Material Select the shell material name. This is used for computing the longitudinal hub allowable stress for optional type flanges that are analyzed as integral.

12-6

The Flange Module

PVElite -User Guide


Flange Face Outer Diameter Enter the outer diameter of the flange face. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Flange Face Inner Diameter Enter the inner diameter of the flange face. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. Gasket Outer Diameter Enter the outer diameter of the gasket. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Gasket Inner Diameter Enter the inner diameter of the gasket. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. Hub Thickness, Small End Enter the thickness of the small end of the hub. This value is referred to as “g0” in the ASME code. The corrosion allowance will be subtracted from this value. For weld neck flange types, this is the thickness of the shell at the end of the flange. For slip on flange geometries, this is the thickness of the hub at the small end. For flange geometries without hubs, such as a blind flange, this thickness may be entered as zero. Hub Thickness, Large End Enter the thickness of the large end of the hub. This value is referred to as “g1” in the ASME code. The corrosion allowance will be subtracted from this value. It is permissible for the Hub thickness at the large end to equal the hub thickness at the small end. For flange geometries without hubs, such as a blind flange, this thickness may be entered as zero. Hub Length Enter the hub length. This value is refereed to as “h” in the ASME code. For flange geometries without hubs, this length may be entered as zero. When analyzing an optional type flange that is welded at the hub end, the hub length should be the leg of the weld, and the thickness at the large end should include the thickness of the weld. When you analyze a flange with no hub, i.e. a ring flange, a lap joint flange, etc., you should enter zero for the hub length, the small end of the hub, and the large end of the hub. However, when you design as a loose flange a ring flange which has a fillet weld at the back, enter the size of a leg of the fillet weld as the large end of the hub. This will insure that the program designs the bolt circle far enough away from the back of the flange to get a wrench around the nuts.

The Flange Module

12-7



Diameter of Bolt Circle Enter the diameter of the bolt circle of the flange. Nominal Bolt Diameter Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the “Thread Series” cell. Thread Series There are three options for this entry: 1 - TEMA Bolt Table, 2 - UNC Bolt Table, 3 - User specified root area of a single bolt. Number of Bolts Enter the number of bolts to be used in the flange analysis. Gasket Materials and Contact Facings, TABLE 2-5.1

Gasket Factor Gasket Material

Seating Stress (m)

Facing (y)

Column

Self Energizing Types, including metallic and elastomer O ring

0.00

0

II

Flat Elastomers Below 75A Shore Durometer

0.50

0

II

75A Shore Durometer or higher

1.00

200

II

Flat asbestos with suitable binder 1/8 inch thick 1/16 inch thick 1/32 inch thick

2.00 2.75 3.50

1600 3700 6500

II II II

Elastomer with cotton fabric insert

1.25

400

II

Elastomer with asbestos fabric insert 3 ply 2 ply 1 ply

2.25 2.50 2.75

2200 2900 3700

II II II

Vegetable Fiber

1.75

1100

II

Spiral-wound metal, asbestos filled Carbon Steel Stainless Steel or Monel

2.50 3.00

10000 10000

II II

Corrugated metal, asbestos filled or Corrugated metal jacketed, asbestos filled Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel

2.50 2.75 3.00 3.25 3.50

2900 3700 4500 5500 6500

II II II II II

Corrugated metal, not filled

12-8

The Flange Module

PVElite -User Guide


Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel Flat metal jacketed, asbestos filled Soft aluminum Soft copper or brass Iron or soft steel Monel 4-6% Chrome Stainless Steel

2.75 3.00 3.25 3.50 3.75

3700 4500 5500 6500 7600

II II II II II

3.25 3.50 3.75 3.50 3.75 3.75

5500 6500 7600 8000 9000 9000

II II II II II II

Grooved metal Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel

3.25 3.50 3.75 3.75 4.25

5500 6500 7600 9000 10100

II II II II II

Solid flat metal Soft aluminum Soft copper or brass Iron or soft steel Monel or 4-6% Chrome Stainless Steel

4.00 4.75 5.50 6.00 6.50

8800 13000 18000 21800 26000

I I I I I

Ring Joint Iron or soft steel Monel or 4-6% Chrome Stainless Steel

5.50 6.00 6.50

18000 21800 26000

I I I

Flange Face Facing Sketch Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: FACING SKETCH

1a 1b 1c 1d 2 3 4 5 6

PVELITE EQUIVALENT

1 2 3 4 5 6 7 8 9

DESCRIPTION

flat finish faces serrated finish faces raised nubbin-flat finish raised nubbin-serrated finish 1/64 inch nubbin 1/64 inch nubbin both sides large serrations, one side large serrations, both sides metallic O-ring type gasket

Gasket Thickness Enter the gasket thickness. This value is only required for facing sketches 1c and 1d (PVElite equivalents 3 and 4).

The Flange Module

12-9



Nubbin Width If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6 (PVElite equivalents 3, 4, 5, and 9). Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Is There a Partition Gasket? If your exchanger geometry has a pass partition gasket, check this entry. PVElite will then prompt for the overall length and width of the gasket. Specify External Loads In order for leakage computations to be performed, the external loads acting on the flange must be specified. By checking this field, a pop-up input form is displayed to allow the entry of this loading data. Loading data of this nature would typically come from a pipe stress analysis program, such as CAESAR II. Flanges are frequently subject to external forces and moments, in addition to internal pressure. The program calculates a roughly approximate equivalent pressure for flanges loaded axially and/or in bending using the following formula:

Peq

=

Pdes + 4*F/3.14G^2+16*M/3.14*G^3

Peq

=

Equivalent pressure, psi

Pdes

=

Design pressure, psi

F

=

Axial force, lbs

M

=

Bending moment, in-lbs

G

=

Diameter of gasket load reaction, in.

Where:

The program then uses the equivalent pressure as the design pressure. Mating Flange Loads If loads from the mating flange are to be considered, check this field. A pop-up spreadsheet will appear for additional data entry. This auxiliary bolt loading will only be used if it is greater then the standard bolt loads computed using the ASME formulas.

Caution

Note

12-10

The use of mating flange values for bolt design calculations will result in incorrect MAWP calculations.

You probably don’t want to calculate MAWP based on the mating flange values, but rather based on the values developed by this flange at a given pressure. Also you definitely don’t want to do “design” when you have a mating flange, since the program will certainly pick a different bolt circle, etc. than the one chosen for the other flange. You can however, do a partial (thickness) design.

The Flange Module

PVElite -User Guide


Compute Thickness Based on Flange Rigidity? Appendix S has some equations that attempt to determine whether or not a given flange geometry will leak. If the computed rigidity index is greater than 1.0 then the leakage is predicted. By checking this box users can instruct the program to compute the thickness such that the corresponding rigidity index is 1.0. Please note that Appendix S is non-mandatory appendix and that these calculations regardless of the type flanges, that are analyzed as integral.

Pop-Up Input Fields Number of Splits in the Ring Enter the number of splits in the ring, if any, for loose type flanges. This value must be either 0, 1, or 2. Typically split flanges are ring-type flanges. A split is used when it is required to have the flange completely removable from the vessel. If the flange is split into two pieces by a single split, the design moment for the flange is multiplied by 2.0. If the flange consists of two separate split rings, each ring shall be designed as if it were a solid flange - without splits) using 0.75 times the design moment. The pair of rings shall be assembled so that the splits in one ring shall be 90 deg. from the splits in the other. Weld Leg at Back of Ring Enter the length of the weld leg at the back of the ring. This value is added to the inside diameter during the design of ring type flanges to determine the minimum bolt circle when the design option is turned on. If you are performing a partial or regular analysis, PVElite will check to see if there is interference between the wrench and the weld. PVElite will print a brief message letting you know there is a potential problem. Lap Joint Contact Inside Diameter Enter the inner diameter of the flange/joint contact surface as shown in the figure below.

Lap Joint Contact Outside Diameter Enter the outer diameter of the flange/joint contact surface as shown in the figure above.

The Flange Module

12-11



TEMA Channel Cover This checkbox indicates whether or not the current flange is a TEMA channel cover. A separate thickness and MAWP are computed for channel covers, as well as the deflection. Diameter of the Load Reaction (Long Span) Enter the distance to the center of the gasket on the long side of the flange. This diameter is used to calculate the non- circular flange correction factor for ASME blind flanges. This factor is discussed in paragraph UG-34 of the ASME code. Diameter of the Load Reaction (Short Span) Enter the distance to the center of the gasket on the short side of the flange. This diameter is used to calculate the non- circular flange correction factor for ASME blind flanges. This factor is discussed in paragraph UG-34 of the ASME code. Allowed Channel Cover Deflection For TEMA Channel Covers, enter the magnitude of the allowed deflection at the center of the cover. This value will be used in computing the channel cover thickness and MAWP, even if it is larger than the allowed deflection. However, a warning message will be printed stating this problem exists. Perimeter Along the Center of the Bolt Holes (L) Enter the perimeter of the bolted head measured along the centerline of the bolts. This value (L) is needed for both non-circular and circular geometries. For a circular head, enter the value of (3.14159 * bolt circle diameter). For non-circular heads this value will have to be computed and entered in. Length of the Partition Gasket This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. If the pass partition gaskets are a different width than the main gasket, scale the length you enter so that the area of the gasket is correct. Width of the Pass Partition Gasket Enter the width of the pass partition gasket. The gasket properties such as the facing sketch, column, M and Y will be taken from the main gasket. Using these properties and the known width, PVElite will compute the effective seating width and compute the gasket loads contributed by the partition gasket. Node Number (Optional) Enter the node number of this flange. This entry represents the node point in a stress analysis model from which the loads are obtained. Axial Force Enter the magnitude of the external axial force which acts on this flange. Bending Moment Enter the magnitude of the external bending moment which acts on this flange.

12-12

The Flange Module

PVElite -User Guide


Mating Flange Bolt Load, Operating Enter the bolt load from the mating flange in the operating case. Mating Flange Bolt Load, Seating Enter the bolt load from the mating flange for seating conditions. Mating Flange Design Bolt Load Enter the design bolt load for the mating flange.

The Flange Module

12-13




Status Bar

In CodeCalc the Status bar, which is located at the bottom of the application, is divided into several panes, which compute and display critical results as the vessel is being modeled. The information includes: Required Thickness due to pressure MAWP (minimum of operating and seating conditions)

Note

Results displaying red in color indicate a failure.

Flanges with Different Bending Moments The flange design moments differ from the norm for external pressure, reverse flanges, and flat flanges. Under external pressure only the end load and flange pressure are included in the design, and their sense is reversed. For reverse flanges all the moments are present, but the moment arm hd is negative, making MD negative. The load HT is negative, and the moment arm ht may be either positive or negative. The absolute value of the moment is used in the calculations. For flat faced flanges an alternate value of hg (h’’g) is used to calculate a reverse moment at the bolt circle. No calculations for seating conditions for full faced flanges are required. Blind Flanges and Channel Covers The ASME Code formula for a circular blind flange is t = d * SQRT(C*P/S*E + 1.9*W*Hg/S*E*d^3) The first term in this formula is the bending of a flat plate under pressure. The second term is the bending of the plate due to an edge moment. The stress is limited to 1.5 times the allowable stress, but the 1.5 factor is already built into the equation. For bolt-up conditions the first term is zero - the thickness of the flange depends only on the edge bending. For non-circular blind flanges the term Z is added to the first term in the square root. Once again, Z is a simple function of the ratio of the large dimension to the small dimension of the flange. It is interesting to note that the Code covers non-circular blind flanges, but no other type of non-circular flange (not even in the rectangular vessel appendix). Channel Covers designed to TEMA must meet at least the minimum thickness requirements of the Code. In addition, if there is a pass partition groove, the cover deflection is limited. The formula for flange deflection limitation is found in paragraph 9.21 of TEMA. The deflection is, of course, a function of t^3 and G^3. Thus, a very small increase in flange thickness will decrease the deflection significantly. The Seventh Edition of TEMA also gives recommended deflections as a function of flange size. The previous editions hid the actual deflection you were working toward in a thickness equation.

12-14

The Flange Module

PVElite -User Guide


Allowable Flange Stresses Allowable flange stresses are based on the ASME Code Allowable Stress for the flange material at the Ambient and Operating design temperatures. In the case of bending stresses, these allowable are multiplied by 1.5. This takes into account the higher maximum strain required to yield a section in bending versus pure tension. The stresses calculated and the allowable stresses are as follows:

Operating

Ambient

Longitudinal Hub Stress (bending) Radial Flange Stress Tangential Flange Stress Maximum Average Stress Stress in Bolts Stress in Reverse Flanges Stress in Full Faced Gasket Flanges

1.5 x Sfo 1.0 x Sfo 1.0 x Sfo 1.0 x Sfo 1.0 x Sbo 1.0 x Sfo 1.0 x Sfo

1.5 x Sfa 1.0 x Sfa 1.0 x Sfa 1.0 x Sfa 1.0 x Sba 1.0 x Sfa 1.0 x Sfa

Where: Sfo

=

ASME Code Allowable Stress for flange material at operating temperature.

Sfa

=

ASME Code Allowable Stress for flange material at ambient temperature.

Sbo

=

ASME Code Allowable Stress for bolt material at operating temperature.

Sba

=

ASME Code Allowable Stress for bolt material at ambient temperature.

The Flange Module

12-15



Maximum Allowable Working Pressure The following graph shows conceptually how the program extrapolates for the Maximum Allowable Working Pressure:

1. For Operating Pressure MAWP: The program calculates the stresses at the pressure given by the user. The program calculates the slope between the stress at zero pressure and the stress at the given pressure The program extrapolates the slope out to the point where the stress is equal to the allowable stress. The pressure at this point is the maximum allowable working pressure. 2. For Gasket Seating MAWP:

Note

At low pressures the stress due to gasket seating is not a function of the design pressure. At higher pressures the stress is a function of pressure, and the MAWP can be calculated as described above, except that the extrapolation is from the point where pressure comes into the calculation of the seating stress.

The program calculates the Gasket Seating MAWP and Operating MAWP based on the input geometry and pressure. In theory both MAWPs should be independent of the input pressure. However, because of the extrapolation algorithm, the estimate of the MAWP may depend on the pressure slightly (when the pressure is very small). Please note that in Partial or Design mode, the program will calculate MAWP based on the required flange thickness.

12-16

The Flange Module

PVElite -User Guide


Flange Rigidity Calculations Appendix S has some equations that attempt to determine whether or not a given flange geometry will leak. Two cases are considered, ambient and operating. If the computed rigidity factor is greater than 1.0, then leakage is predicted. Please note that Appendix S is a non-mandatory appendix and that these calculations are also non-mandatory. Flange Design The geometry defined by the user is the basis for the design performed by the program. Specifically, the inside diameter, materials, pressure, gasket geometry and gasket properties remain fixed throughout the design. Beginning from this point, the program uses the following approach to design the rest of the flange:

1. For slip-on type flanges, calculate the small end of the hub equal to roughly the thickness required for the design pressure 2. For weld neck, slip-on, and reverse flanges, calculate the large end of the hub as the small end of the hub plus 1/16th (for small end thicknesses less than one inch) or 1/8th (for small end thicknesses greater than one inch). Then calculate a hub length equal to the small end thickness plus the minimum slope (3:1) for the hub. The effect of these choices is to design a small hub when compared with standardized flanges. This has the additional effect of keeping the moment arms and diameters (of the bolt circle and flange OD) small, and keeping the flange light. Finally, the selection of a small hub keeps the amount of machining required for the flange to a minimum. 3. Select a preliminary number of bolts. This is a multiple of four based on the diameter of the flange. The algorithm chosen tends to select more and smaller bolts than would be found on standard flanges. This also has the effect of minimizing the flange outside diameter and the weight of the flange. 4.

Select a bolt size that will give the required bolt area for this number of bolts.

5.

Using this bolt size, calculate a final number of bolts based on: •

The area required divided by the area available per bolt -OR-

•

The maximum allowed spacing between bolt of this size.

6. Using this number of bolts, calculate the bolt circle base on: •

The OD of the hub plus the minimum ID spacing of the bolt -OR-

•

The OD of the gasket face plus the actual size of the bolt -OR-

•

The minimum spacing distance between the bolts -OR-

•

For reverse flanges, the vessel OD plus the bolt ID spacing.

7. Calculate the outside diameter of the flange based on the bolt circle plus the minimum edge spacing for the bolt size chosen. 8. For flanges with full face gaskets, adjust the gasket and face outside diameter for the values chosen, and recalculate the moment arms for the flange. 9. Finally (and this step also applies to partial design of the flange), select a thickness for the flange and calculate the stresses. If the stress is not equal to the allowable, adjust the thickness based on the difference between the actual and allowable

The Flange Module

12-17



stresses, and then repeat the stress calculation. This process continues until the actual stress for one of the stress components is equal to the allowable stress.

12-18

The Flange Module

PVElite -User Guide

Example Problems

Example Problems The example problem presented below is taken from “Modern Flange Design,” Page 12. This problem is the calculation of stresses for a typical weld neck flange. The results from the example problem agree very well with the Taylor Forge results. The detailed calculations on the second and third pages of the printout show the formulas and substitutions for the loads, distances and stresses calculated by the program. There are several additional example problems included in the files CHECKS, FEXAMPLE & FEXAMPL2. COADE Verification Problem Set PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON FileName : CHECKS

-------------------------------- Page 1

Flange Analysis : TAYLOR FORGE

INPUT VALUES, FLANGE NUMBER

ITEM:

1,

Description of Flange Geometry (Type)

1,

03:31pm,

Description: TAYLOR FORGE

Integral Weld Neck

Description of Flange Analysis Design Pressure

Analysis Only P

Design Temperature Corrosion Allowance

400.00

psig

650.00

F

FCOR

.0000

in.

Flange Inside Diameter

B

32.0000

in.

Flange Outside Diameter

A

39.1250

in.

Flange Thickness

T

2.0000

in.

Thickness of Hub at Small End

G0

.5000

in.

Thickness of Hub at Large End

G1

1.1250

in.

Length of Hub

HL

2.7500

in.

Flange Material

SA-516 70

Flange Allowable Stress At Temperature

SFO

17500.00

psi

Flange Allowable Stress At Ambient

SFA

17500.00

psi

Bolt Material

SA-193 B7

Bolt Allowable Stress At Temperature

SBO

25000.00

psi

Bolt Allowable Stress At Ambient

SBA

25000.00

psi


C

37.0000

in.

Nominal Bolt Diameter

DB

1.0000

in.

Type of Threads

TEMA Thread Series

Number of Bolts

36

Flange Face Outside Diameter

FOD

34.5000

in.

Flange Face Inside Diameter

FID

33.0000

in.

Flange Facing Sketch

The Flange Module

05/18/98

1, Code Sketch 1a

Gasket Outside Diameter

GOD

36.0000

in.

Gasket Inside Diameter

GID

33.0000

in.

Gasket Factor, m,

M

2.7500

Gasket Design Seating Stress

Y

3700.00

psi

12-19

Example Problems


Column for Gasket Seating

1, Code Column I

FLANGE ANALYSIS, FLANGE NUMBER

Corroded Flange ID,

1,

Description: TAYLOR FORGE

32.000

in.

Corroded Large Hub,

G1COR = G1-FCOR

BCOR = B+2.0*FCOR

1.125

in.

Corroded Small Hub,

G0COR = G0-FCOR

.500

in.

1.375

in.

Code R Dimension,

R = ((C-BCOR)/2.0)-G1COR

Gasket Contact Width,

.750

in.

Basic Gasket Width,

B0 = N / 2.0

N = (GOD-GID) / 2.0

.375

in.

Effective Gasket Width,

BE = SQRT(B0) / 2.0

.306

in.

33.888

in.

Gasket Reaction Diameter,

G = GOD-2.0*BE

BASIC FLANGE AND BOLT LOADS: Hydrostatic End Load due to Pressure: H = PI/4 * G * G * PEQ H = ( .7854 * 33.8876 * 33.8876 * 400.0000 ) H = 360771. lb. Contact Load on Gasket Surfaces: HP = 2.0 * BE * PI * G * M * PEQ HP = 2.0 * .3062 * 3.1416 * 33.8876 * 2.7500 * 400.00 HP = 71713. lb. Hydrostatic End Load at Flange ID: HD = PI * BCOR * BCOR * PEQ

/ 4.0

HD = 3.1416 * 32.0000 * 32.0000 * 400.0000 / 4.0 HD = 321699. lb. Pressure Force on Flange Face: HT = H - HD HT = 360771 - 321699 HT = 39072. lb. Operating Bolt Load: WM1 = H + HP +

HPP

WM1 = ( 360771 + 71713 + 0 ) WM1 = 432485. lb. Gasket Seating Bolt Load: WM2 = Y * (( BE * PI * G ) + (BEPG * GLPG)) + HPGY WM2 = 3700.00*((.3062*3.141*33.888)+(.00*.0000))+.00 WM2 = 120609. lb. Required Bolt Area: AM = Maximum of WM1/ABSTR, WM2/ABASTR AM = Maximum of 432484 / 25000 , 120608 / 25000 AM = 17.2994 sq.in.

Bolting Information for TEMA Thread Series: Total Area of Bolts, AB

12-20

19.836

sq.in.

Minimum radial distance between hub and bolts

1.375

in.

Minimum radial distance between bolts and edge

1.063

in.

Minimum circumferential spacing between bolts

2.250

in.

Actual

circumferential spacing between bolts

3.225

in.

Maximum circumferential spacing between bolts

5.692

in.

Min. Gasket Contact Width (Brownell&Young)

1.437

in.

Nmin =

The Flange Module

PVElite -User Guide

Example Problems

Flange Design Bolt Load, Gasket Seating: W = ABASTR * ( AM + AB ) / 2.0 W = 25000.00 * ( 17.2994 + 19.8360 ) / 2.0 W = 464192.40 lb. Gasket Seating Force: HG = WM1 - H HG = 432484 - 360771 HG = 71713.25 lb.

MOMENT ARM CALCULATIONS: Distance to Gasket Load Reaction: DHG = (C - G ) / 2.0 DHG = ( 37.0000 - 33.8876 ) / 2.0 DHG = 1.5562 in. Distance to Face Pressure Reaction: DHT = ( R + G1COR + DHG ) / 2.0 DHT = ( 1.3750 + 1.1250 + 1.5562 ) / 2.0 DHT = 2.0281 in. Distance to End Pressure Reaction: DHD = R + ( G1COR / 2.0 ) DHD = 1.3750 + ( 1.1250 / 2.0 ) DHD = 1.9375 in.

SUMMARY OF MOMENTS FOR INTERNAL PRESSURE: LOADING

Force

Distance

Bolt Corr

Moment

End Pressure,

MD

321699.

1.9375

1.0000

51941. ft.lb.

Face Pressure,

MT

39072.

2.0281

1.0000

6604. ft.lb.

Gasket Load,

MG

71713.

1.5562

1.0000

9300. ft.lb.

Gasket Seating, MA

464192.

1.5562

1.0000

60198. ft.lb.

TOTAL MOMENT FOR OPERATION,

RMO

67844. ft.lb.

TOTAL MOMENT FOR GASKET SEATING, RMA

60198. ft.lb.

Effective Hub Length, H0 = SQRT(BCOR*G0COR)

4.000

Hub Ratio,

HRAT = HL / H0

Thickness Ratio,

GRAT = (G1COR/G0COR)

in.

.688 2.250

Flange Factors for Integral Flange: Factor F per 2-7.2

.777

Factor V per 2-7.3

.162

Factor f per 2-7.6

1.000

Factors from Figure 2-7.1 T = Y = d =

K =

1.223

1.830

U =

10.740

9.773

Z =

5.041

66.480 in.^3

Stress Factors

e =

.194 in.^-1

ALPHA =

1.388

BETA =

1.518

GAMMA =

.759

DELTA =

.120

LAMBDA =

.879

Longitudinal Hub Stress, Operating: SHO = ( f * RMO / BCOR ) / ( RLAMBDA * G1COR^2 ) SHO = ( 1.0000 * 814133 / 32.0000 ) / ( .8792 * 1.1250^2 ) SHO = 22865. psi Longitudinal Hub Stress, Seating:

The Flange Module

12-21

Example Problems


SHA = ( f * RMA / BCOR ) / ( RLAMBDA * G1COR^2 ) SHA = ( 1.0000 * 722370 / 32.0000 ) / ( .8792 * 1.1250^2 ) SHA = 20288. psi Radial Flange Stress, Operating: SRO = ( BETA * RMO / BCOR ) / ( RLAMBDA * TH^2 ) SRO = ( 1.5180 * 814133 / 32.0000 ) / ( .8792 * 2.0000^2 ) SRO = 10982. psi Radial Flange Stress, Seating: SRA = ( BETA*RMA/BCOR ) / ( RLAMBDA*TH^2 ) SRA = ( 1.5180 * 722370/ 32.0000 ) / ( .8792 * 2.0000^2 ) SRA = 9744. psi Tangential Flange Stress, Operating: STO = ( Y*RMO / (TH*TH*BCOR) ) - Z*SRO STO = ( 9.7733 * 814133 / ( 2.0000^2 * 32.0000) ) - 5.0413 * 10981 STO = 6800. psi Tangential Flange Stress, Seating: STA = ( Y*RMA / (TH^2*BCOR) ) - Z*SRA STA = ( 9.7733 * 722370 / ( 2.0000^2 * 32.0000) ) - 5.0413 * 9744 STA = 6033. psi Average Flange Stress, Operating: SAO = ( SHO + MAX( SRO, STO ) ) / 2 SAO = ( 22864 + MAX( 10981, 6799 ))/ 2 SAO = 16923. psi Average Flange Stress, Seating: SAA = ( SHA + MAX( SRA, STA ) ) / 2 SAA = ( 20287 + MAX( 9744, 6033 ))/ 2 SAA = 15016. psi Bolt Stress, Operating: SBO = ( WM1 / AB ) SBO = ( 432484 / 19.8360 ) SBO = 21803. psi Bolt Stress, Seating: SBA = ( WM2 / AB ) SBA = ( 120608 / 19.8360 ) SBA = 6080. psi

Stress Computation Results:

OPERATING

Actual

Allowed

GASKET SEATING Actual

Allowed

Longitudinal Hub

22865.

26250.

20288.

26250. psi

Radial Flange

10982.

17500.

9744.

17500. psi

6800.

17500.

6033.

17500. psi

Maximum Average

16923.

17500.

15016.

17500. psi

Bolting

21803.

25000.

6080.

25000. psi

Tangential Flange

Estimated M.A.W.P. ( Operating )

413.6

psig

Estimated M.A.W.P. ( Gasket Seating )

542.0

psig

Estimated Finished Weight of Flange

290.5

lb.

Estimated Unfinished Weight of Forging

535.0

lb.

APP. S Flange Rigidity Index for Seating Case APP. S Flange Rigidity Index for Operating Case

.796 1.035


12-22

The Flange Module


&KDSWHU The Conical Sections Module

Introduction The PVElite Conical Sections Module performs internal and external pressure design of conical sections and stiffening rings using the ASME Code, Section VIII, Division 1 rules, 2001, A-2001.

Purpose, Scope, and Technical Basis The PVElite Conical Sections Module calculates the required thickness and Maximum Allowable Working Pressure for conical shells and sections under either internal or external pressure. The module is based on the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, 2001, A-2001. Specifically, the module is based on the rules in paragraphs UG-32, UG-33, and Appendix 1, Sections 1-5, and 1-7. The module calculates required thickness for the cone under both internal and external pressure. Also calculated are the required thickness of the attached cylinders under either internal or external pressure. Calculations for the required thickness of a transition knuckle are included. The required area of reinforcement and actual reinforcement available are calculated for both internal and external pressures. Reinforcement is limited to the area available in the shell sections plus simple stiffening rings. The Conical Sections Module takes full account of corrosion allowance. You enter actual thickness and corrosion allowance, and the module adjusts thicknesses and diameters when making calculations for the corroded condition.

The Conical Sections Module

13-1



Figure 13A shows geometry for the Conical Sections Module.

Figure 13A - Geometry for the Conical Sections Module

Cone Number Enter an ID number for the Cone. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Cone Description Enter an alpha-numeric description for this item. This entry is optional. Internal Design Pressure You may analyze both internal and external pressure at the same time, since the two cases are analyzed and reported separately. Enter zero for internal pressure if you only wish to analyze the external pressure case. Internal Design Temperature Enter the temperature associated with the internal design pressure. The PVElite program will automatically update materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. External Design Pressure Enter the design pressure for external pressure analysis. This should be a positive value, i.e. 14.7 psia. If you enter a zero in this field the program will not perform external pressure calculations. External Design Temperature Enter the temperature associated with the external design pressure. The PVElite program will automatically update materials properties for external pressure calculations when you

13-2




change the design temperature. The design external pressure at this temperature is a completely different design case than the internal pressure case. Therefore this temperature may be different than the temperature for internal pressure. Many external pressure charts have both lower and upper limits on temperature. If your design temperature is below the lower limit, use the lower limit as your entry to the program. If your temperature is above the upper limit the component may not be designed for vacuum conditions. Cone\Cylinder\Ring\Knuckle Material Name Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Material Allowable Stress, Design Temperature This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Material Allowable Stress, Ambient Temperature This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the ambient temperature. Cone Joint Efficiency Enter the efficiency of the welded joint for shell sections with welded seams. This will be the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. Cone Actual Thickness Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. You should enter the minimum thickness. Cone Corrosion Allowance Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter.


13-3



Cone Diameter Basis ( ID, OD ) Enter ID for shell sections based on inside diameter. Enter OD for shell sections based on outside diameter. Note that this diameter basis is also used for the cylinder at the small end of the cone, and the cylinder at the large end of the cone. Cone Diameter at Small End Enter the diameter of the cone at the small end. This diameter is also used for the cylinder at the small end of the cone. Note that this should not be the diameter at the point where a knuckle or flare intersects the conical section, but at the point where the knuckle or flare intersects the cylindrical section. The program will calculate the other diameter. Cone Diameter at Large End Enter the diameter of the cone at the large end. This diameter is also used for the cylinder at the large end of the cone. Note that this should not be the diameter at the point where a knuckle or flare intersects the conical section, but at the point where the knuckle or flare intersects the cylindrical section. The program will calculate the other diameter. Cone Half Apex Angle For internal pressure calculations the half apex angle should not be greater than 30 degrees, though the program will give results for up to 60 degrees. For external pressure calculations it must not be greater than 60 degrees. If you enter a zero for the angle, the PVElite program will calculate an angle based on the cone diameters and length. Cone Axial Length Enter the length of the cone along the axis of the vessel. The program will calculate the effective length of the cone for internal and external pressure calculations. Are There Axial Forces on the Cone? If there are axial forces on the cone, check this field. Examples of axial forces would include weight loads, loads from external attachments, and possibly thermal loads. The axial force due to internal or external pressure are already taken into account by the program. Note that in general loads causing compression are significant for the external pressure case, while loads causing tension are significant for the internal pressure case. Small Cylinder Joint Efficiency Enter the efficiency of the welded joint for shell sections with welded seams. This will be the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. Small Cylinder Actual Thickness Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. You should enter the minimum thickness.

13-4




Small Cylinder Corrosion Allowance Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Small Cylinder Axial Strength Enter the length of the cylinder along the axis of the vessel. This value is not used in internal pressure calculations, but is required for external pressure calculations. Small End Reinforcing (None, Bar, Section, Knuckle) Enter the type of reinforcing bar for the small end:

•

NONE = no reinforcement at the small end and no knuckle.

•

BAR = reinforcing bar at small end (width and thickness).

•

SECTION = reinforcing beam section at small end (inertia, area, and depth of beam).

•

KNUCKLE = toroidal knuckle at small end ( radius and thickness )

Note

Whichever option is chosen you will be prompted to enter a reinforcing material. If there is no reinforcing material, enter the small end shell material. The values for the elasticity and allowable stress values will be needed for the area and inertia calculations depending on the value of Delta.

Large Cylinder Joint Efficiency Enter the efficiency of the welded joint for shell sections with welded seams. This will be the efficiency of the longitudinal seam in a cylindrical shell or any seam in a spherical shell. Elliptical and torispherical heads are typically seamless but may require a stress reduction which may be entered as a joint efficiency. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. Large Cylinder Actual Thickness Enter the minimum thickness of the actual plate or pipe used to build the vessel, or the minimum thickness measured for an existing vessel Many pipe materials have a minimum specified wall thickness which is 87.5% of the nominal wall thickness. You should enter the minimum thickness. Large Cylinder Corrosion Allowance Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Large Cylinder Axial Length Enter the length of the cylinder along the axis of the vessel. This value is not used in internal pressure calculations, but is required for external pressure calculations. Large End Reinforcing (None, Bar, Section, Knuckle) Enter the type of reinforcing bar for the large end:

•

NONE=no reinforcement at the large end and no knuckle.


13-5



•

BAR=reinforcing bar at large end (width and thickness).

•

SECTION=reinforcing beam section at large end (inertia, area, and depth of beam).

•

KNUCKLE=toroidal knuckle at large end (radius and thickness).

Note

Whichever option is chosen you will be prompted to enter a reinforcing material. If there is no reinforcing material, enter the large end shell material. The values for the elasticity and allowable stress values will be needed for the area and inertia calculations depending on the value of Delta.

Cone Circumferential Joint Efficiency This value is used in the computation of allowable stresses for discontinuity stresses. It should be in the range of 0.7 to 1.0.

13-6



Pop-Up Input Fields

Pop-Up Input Fields Take Cone as Lines of Support for External Pressure? The ASME Code allows you to take the intersections of the cone and the two cylinders as lines of support for external pressure, provided that the moment of inertia and area of reinforcement requirements of Appendix 1-8 are satisfied. Alternately, you may calculate external pressure using an equivalent design length which includes the cone and both the large and small cylinders. For details see Section VIII, Division 1, Paragraph UG-28 and Figure UG-28.1 (A-90 Addenda and following.) Normally it is preferable to take the cone as lines of support, since the equivalent length of the large cylinder / cone / small cylinder combination may easily result in low allowable external pressures. However, the moment of inertia is very easy to be less than the required for knuckle-to-cylinder junction — because the shell/knuckle/cone is usually so close to the resulting neutral axis. Starting from CC version 5.6, the moment of inertia with the knuckle is calculated, following the procedure of code example L-3.3.

Total Axial Force on Large End for Internal Pressure Case Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The program calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a positive (tensile) axial force adds to the tension due to internal pressure, while a negative (compressive) axial force subtracts from the tension due to internal pressure.

Total Axial Force on Large End for External Pressure Case Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The program calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a negative (compressive) axial force adds to the compression due to external pressure, while a positive (tensile) axial force subtracts from the compression due to external pressure.

Total Axial Force on Small End for Internal Pressure Case Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The program calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a positive (tensile) axial force adds to the tension due to internal pressure, while a negative (compressive) axial force subtracts from the tension due to internal pressure.

Total Axial Force on Small End for External Pressure Case Enter the axial force, not the force per unit circumferences as used by the Code (f1, f2). The program calculates the force per unit circumference before performing the calculation. Note that we have formulated the calculations so that a negative (compressive) axial force adds to the compression due to external pressure, while a positive (tensile) axial force subtracts from the compression due to external pressure.

Location of Reinforcing Cone ( Shell, Cone ) Enter the location of the reinforcing bar:


13-7

Pop-Up Input Fields


•

SHELL = welded to the shell (cylinder).

•

CONE = welded to the cone.

Radial Width of Reinforcing Ring Enter the width of the reinforcing bar. You can also think of this as the projection of the bar out from the vessel OD. For example, a donut shaped plate 10 inches by 1 inch has a radial width of 10.

Axial Thickness of Reinforcing Ring Enter the thickness of the reinforcing bar. For example, a donut shaped plate 10 inches by 1 inch has an axial thickness of 1.

Moment of Inertia of Reinforcing Section Enter the moment of inertia of the beam section (I, T, etc.) used to reinforce the cone/cylinder junction. This can usually be found in the ‘Manual of Steel Construction’ for common beam sections.

Cross-Sectional Area of Reinforcing Section Enter the cross sectional area of the beam section (I, T, etc.) used to reinforce the cone/cylinder junction. This can usually be found in the ‘Manual of Steel Construction’ for common beam sections.

Distance to Centroid of Reinforcing Section Enter the distance to the centroid of the beam section ( I, T, etc.) used to reinforce the cone/cylinder junction. This can usually be found in the ‘Manual of Steel Construction’ for common beam sections.

Knuckle Bend Radius, Large End Enter the bend radius of the toroidal knuckle at the large end. Note that the Code requires this radius to be no less than 6% of the outside diameter of the head, nor less than three times the knuckle thickness (UG-31, (h)).

Knuckle Thickness, Large End Enter the minimum thickness after forming of the toroidal knuckle at the large end.

Knuckle Bend Radius, Small End Enter the bend radius of the toroidal knuckle at the large end. Note that the Code requires this radius to be no less than 6% of the outside diameter of the head, nor less than three times the knuckle thickness (UG-31, (h)).

Knuckle Thickness, Small End Enter the minimum thickness after forming of the toroidal knuckle at the large end.

13-8



Discussion of the Results

Discussion of the Results Internal Pressure Results The first section of results shows the required thicknesses and Maximum Allowable Working Pressures for the cone and for the upper and lower cylinders under internal pressure.

Note

This section is shown even when the internal design pressure is zero: the required thicknesses will be zero, but the Maximum Allowable Working Pressures will be meaningful.

Next the program summarizes these internal pressure results, adding the corrosion allowances as necessary.

External Pressure Results The External pressure module calculates materials properties and required thicknesses under external pressure. Because the program uses Young’s modulus values in both the internal and external reinforcement calculation, this module is called even when the external design pressure is zero. However, in this case the required thickness and Maximum Allowable Working Pressure calculations for external pressure are skipped. The required thickness under external pressure is calculated using the interactive method outlined in Paragraph UG-33 of the ASME Code. The effective length for toriconical sections is adjusted to include a fraction of the knuckle in the design length.

Reinforcement Calculations Under Internal Pressure The program calculates required reinforcement for the cone/cylinder junctions at both the large and the small ends. This calculation is performed whenever the internal pressure is greater than zero, and the reinforcing material is defined. If a knuckle is specified instead of a reinforcing ring, the knuckle calculation will be performed and the required area calculation will not. When a knuckle calculation is performed, the program calculates both the required thickness and the maximum allowable working pressure for the toroidal portion of the knuckle, using the rules in Appendix 1-4(d). When there is no knuckle, the program calculates the required area of reinforcement at the intersection of the cylinder and the two cones. Cones are required to have reinforcement at the large and small ends under internal pressure (Appendix 1-5) because of the tendency of the cone/cylinder junction to buckle under the radial load developed in the cone. The Code calculates the maximum angle below which buckling will not occur as a function of the design pressure and allowable stress. This ratio is used because it is a pretty good indication of the diameter thickness ratio for the cylinder, and takes into account the strength of the material. This approach has the odd effect that when you increase the allowable stress you decrease the allowable cone angle. However, you will normally find that for a given thickness this effect is offset by the increase area available in the cone for reinforcement. Given that reinforcement is required, the area required is a function of the pressure and the square of the radius. Area available in the shell within one decay length may be included in the area available for stiffening.


13-9

Discussion of the Results


The PVElite program will set the area required in the reinforcing ring to zero if either the allowed apex angle is higher than the actual apex angle or the area available in the shell is greater than the area required.

Reinforcement Calculations Under External Pressure The program calculates required reinforcement and moment of inertia for the cone/cylinder junctions at both the large and the small ends. This calculation is performed whenever the external pressure is greater than zero, the cone is taken as lines of support and reinforcing material is defined. If a knuckle is specified instead of a reinforcing ring, the knuckle calculation will be performed and the area of reinforcement calculation will not. If the user specifies that the cone/cylinder junctions are not to be taken as a line of support, then the area of reinforcement and moment of inertia calculations will not be performed. Cones are required to have reinforcement at the large and small ends under external pressure (Appendix 1-7) because of the tendency to buckle under axial external loads. At both the large and small ends there are requirements for area of reinforcement and moment of inertia of the reinforcement. The area of reinforcement is based on considerations similar to those described for internal pressure. The required moment of inertia of the reinforcement is a function of the strain in the ring at the cone/shell junction, which is in turn calculated using the Code materials chart from the stress in the ring. See the comments on stiffening rings in the external pressure section for further insight. The maximum apex angle is taken from Tables 1-8.1 in Appendix 1 of the ASME Code. The ratio P/SE is calculated by the program. Note that this angle applies only to the large end of the cone - the small end always requires at least a little reinforcement. The area required in the reinforcing ring will be set to zero if either the cone angle is less than the maximum angle (large end only), or the area of reinforcement available in the shell is greater than the area required.

13-10



Example Problems

Example Problems Example Problem #1 Example problem 1 is taken from the ASME Code, Section VIII, Division 1, Appendix L, L-3, Example 3. The Code example problem requests determination of the required thickness for the knuckle and cone with a small end diameter of 200 inches and a half apex angle of 30 degrees. The cone is to be designed for 50 psi internal pressure. Agreement with the required thickness per the Code is exact. Page 2 of the printout is included to illustrate the detailed calculations for internal pressure. These examples are contained in the file CHECKS. Examples per ASME VIII Div.1 Appendix L FileName : CHECKS

----------------------------------- Page 1

Conical Analysis : APP L, L-2.3

INPUT ECHO, CONE NUMBER

ITEM:

2,

Design Internal Pressure Temperature for Internal Pressure Design External Pressure Temperature for External Pressure

2,

01:55pm,

06/05/97

Description: APP L, L-2.3

PINT

50.00

TEMPIN

650.00

PEXT

.00

psig

TEMPEX

.00

F

Cone Material

psig F

SA-516 70

Cone Allowable Stress at Temperature

SAC

17500.00

psi

Cone Allowable Stress At Ambient

SOC

17500.00

psi

EC

.8500

TC

.4380

in.

CAC

.0000

in.

Joint Efficiency of Cone Actual Thickness of Cone Corrosion Allowance for Cone

Diameter Basis for Cone and Cylinders

BASIS

ID

Diameter of Small End of Cone

DS

100.0000

in.

Diameter of Large End of Cone

DL

200.0000

in.

ANGLE

30.00

LC

86.6000

in.

Total Axial Force on Large End, Internal Pressure

157079.00

lb.

Total Axial Force on Small End, Internal Pressure

19635.00

lb.

Half Apex Angle for Cone Axial Length of Cone

Small End Cylinder Material

degrees

SA-516 70

Small Cylinder Allowable Stress at Operating SAS

17500.00

psi

Small Cylinder Allowable Stress At Ambient

SOS

17500.00

psi

ES

1.0000

Joint Efficiency of Small Cylinder Actual Thickness of Small Cylinder Corrosion Allowance for Small Cylinder Axial Length of Small Cylinder

TS

.1880

in.

CAS

.0000

in.

LS

75.0000

in.

Large End Cylinder Material

SA-516 70

Large Cylinder Allowable Stress at Operating SAL

17500.00

psi

Large Cylinder Allowable Stress At Ambient

SOL

17500.00

psi

Joint Efficiency of Large Cylinder

EL

1.0000

Actual Thickness of Large Cylinder

TL

.3130


in.

13-11

Example Problems


Corrosion Allowance for Large Cylinder

CAL

.0000

in.

LL

250.0000

in.

Axial Length of Large Cylinder

Type of Reinforcement at Large End of Cone:

Bar

Large End Reinforcing/Knuckle Material

SA-36

Large Reinforcing/Knuckle Allowable, Operating

14500.00

psi

Large Reinforcing/Knuckle Allowable, Ambient

14500.00

psi

Location of Reinforcement at Large End of Cone:

Shell

Radial Width of Reinforcing Bar(Large End)

RWLB

.0001

in.

Axial Thickness of Reinforcing Bar

RTLB

.0001

in.

Type of Reinforcement at Small End of Cone:

Bar

Small End Reinforcing/Knuckle Material

SA-36

Small Reinforcing/Knuckle Allowable, Operating

14500.00

psi

Small Reinforcing/Knuckle Allowable, Ambient

14500.00

psi

Location of Reinforcement at Small End of Cone:

Shell

Radial Width of Reinforcing Bar(Small End)

RWSB

.0001

in.


RTSB

.0001

in.

INTERNAL PRESSURE RESULTS, CONE NUMBER

2,


INTERNAL PRESSURE CALCULATIONS for CONE:

Thickness Due to Internal Pressure: TR = (P*(Di+2*CA))/(2*COSA*(S*E-0.6*P)) per App 1-4(e) TR = ( 50.00 * ( 200.0000 + 2 * .0000 )) / ( 2 * .8660 * ( 17500 * .85 - 0.6 * 50.00 )) TR = .3889 in.

Maximum Allowable Working Pressure at Given Thickness: MAWP = (2*S*E*(T-CA)*COSA)/((Di+2*CA)+1.2*(T-CA)*COSA) App 1-4(e) MAWP = ( 2 * 17500 * .85 * ( .4380 - .0000 ) * .8660 ) / (( 200.0000 + 2 * .0000 ) + 1.2 * ( .4380 - .0000 ) * .8660 ) MAWP = 56.30 psig

INTERNAL PRESSURE CALCULATIONS for SMALL CYLINDER:

Thickness Due to Internal Pressure: TR = (P*(D/2+CA))/(S*E-0.6*P) per UG-27 (c)(2) TR = ( 50.00 * ( 100.0000 / 2 + .0000 )) / ( 17500 * 1.00 - 0.6 * 50.00 ) TR = .1431 in.

Maximum Allowable Working Pressure at Given Thickness: MAWP = (S*E*(T-CA))/((D/2+CA)+0.6*(T-CA)) per UG-27 (c)(2) MAWP = ( 17500 * 1.00 * ( .1880 - .0000 )) / (( 100.0000 / 2 + .0000 ) + 0.6 * ( .1880 - .0000 )) MAWP = 65.65 psig

INTERNAL PRESSURE CALCULATIONS for LARGE CYLINDER:

Thickness Due to Internal Pressure:

13-12



Example Problems

TR = (P*(D/2+CA))/(S*E-0.6*P) per UG-27 (c)(2) TR = ( 50.00 * ( 200.0000 / 2 + .0000 )) / ( 17500 * 1.00 - 0.6 * 50.00 ) TR = .2862 in.

Maximum Allowable Working Pressure at Given Thickness: MAWP = (S*E*(T-CA))/((D/2+CA)+0.6*(T-CA)) per UG-27 (c)(2) MAWP = ( 17500 * 1.00 * ( .3130 - .0000 )) / (( 200.0000 / 2 + .0000 ) + 0.6 * ( .3130 - .0000 )) MAWP = 54.67 psig SUMMARY of INT. PRESSURE RESULTS: Small Cyl

Cone

Large Cyl

Required Thickness plus CA

.1431

.3889

.2862

in.

Actual Given Thickness

.1880

.4380

.3130

in.

Max. All. Working Pressure

65.65

56.30

54.67

psig

Design Pressure as Given

50.00

50.00

50.00

psig

REINFORCEMENT CALCULATIONS for CONE / LARGE CYLINDER:

REQUIRED AREA of REINFORCEMENT for LARGE END

UNDER INTERNAL PRESSURE

Large end ratio of pressure to allowable stress

.00286

Large end max. half apex angle w/o reinforcement

17.571

degrees

Large end actual half apex angle

30.000

degrees

REQUIRED AREA of REINFORCEMENT, LARGE END, INTERNAL: ARL = (RKL*QL*RCLI/(SAL*EL))*(1-DELTA/ANGLE)*TANA ARL = ( 1.21 * 2749 * 100.0000 / ( 17500 * 1.00 ) ) * ( 1.0 - 17.57 / 30.00 ) * .5774 ARL = 4.5363 sq.in.

AREA of REINFORCEMENT AVAILABLE in LARGE END SHELL: AeL = ( TLC - TREQL ) * SQRT( RCLO * TLC ) + ( TCC - TREQC ) * SQRT( RCLO * TCC / COSA ) AeL = ( .3130 - .2862 ) * SQRT( 100.0000 * .3130 ) + ( .4380 - .3889 ) * SQRT( 100.0000 * .4380 / .8660 ) AeL = .4990 sq.in.

SUMMARY of REINFORMENT AREA, LARGE END, INTERNAL PRESSURE: Area of reinforcement required per App. 1-5(1)

4.5363

sq.in.

Area of reinforcement in shell per App. 1-5(2)

.4990

sq.in.

Area of reinforcement in stiffening ring

.0000

sq.in.

4.0374

sq.in.

Additional Area needed to satisfy requirements

REINFORCEMENT CALCULATIONS for CONE / SMALL CYLINDER:

REQUIRED AREA of REINFORCEMENT for SMALL END

under INTERNAL PRESSURE

Small end ratio of pressure to allowable stress Small end max. half apex angle w/o reinforcement Small end actual half apex angle

.00286 4.571

degrees

30.000

degrees

REQUIRED AREA of REINFORCEMENT, SMALL END, INTERNAL: ARS = ( RKS * QS * RCSI / ( SAS * ES ) ) * ( 1 - DELTA/ANGLE )* TANA ARS = ( 1.21 * 1312 * 50.0000 / ( 17500 * 1.00 ) ) * ( 1.0 - 4.57 / 30.00 ) * .5774 ARS = 2.2148 sq.in.


13-13

Example Problems


AREA of REINFORCEMENT AVAILABLE in SMALL END SHELL: Aes = .78*(Rs*Ts)^«*((Ts-t)+(Tc-Tr)/Cosà )) Aes = .78*( 50.000* .188)^«*(( .188- .143 )+( .438- .194 )/ .87 )) Aes = .7799 sq.in.

SUMMARY of REINFORMENT AREA, SMALL END, INTERNAL PRESSURE: Area of reinforcement required per App. 1-5(3)

2.2148

sq.in.


.7799

sq.in.


.0000

sq.in.

1.4350

sq.in.


Results for Discontinuity Stresses per Bednar p. 236 2nd Edition ---------------------------------------------------------------Stress Type

Stress

Allowable

Location

---------------------------------------------------------------Tensile

Stress

66477.39

70000.00

Small Cyl. Long.

Compres. Stress

-53154.52

-70000.00

Small Cyl. Long.

Membrane Stress

35423.96

26250.00

Small End Tang.

Tensile

Stress

14500.67

70000.00 Cone Longitudinal

Compres. Stress

-7814.98

-70000.00 Cone Longitudinal

Tensile

Stress

28704.24

Tensile

26250.00

Cone Tangential

Stress

103483.40

70000.00

Large Cyl. Long.

Compres. Stress

-87483.91

-70000.00

Large Cyl. Long.

Membrane Stress

-25324.62

26250.00

Large End Tang.

Tensile

Stress

56745.75

70000.00 Cone Longitudinal

Compres. Stress

-43213.55

-70000.00 Cone Longitudinal

Tensile

-28121.92

Stress

26250.00

Cone Tangential


Example Problem #2 The second example problem illustrates the calculation of a cone under external pressure. This example is also taken from the ASME Code, Section VIII, Division 1, Appendix L, L-3.3. The cone is similar to the one used in Example 1, but under external pressure. Agreement with the example problem results for area of reinforcement required, area available in shell, area available in reinforcing ring and the moment of inertia of the reinforcement is good at both the large and small ends of the cone. The third page of the printout is included to show the detailed calculations for external pressure at the large and small ends. Note that beginning from A-95, the code’s computation has good agreement with PVElite for this example. Examples per ASME VIII Div.1 Appendix L FileName : CHECKS

------------------------------------

Conical Analysis : APP L, L-3.3


1,

Design Internal Pressure Temperature for Internal Pressure

13-14

ITEM:

1,

Page

02:09pm,

1 06/05/97


PINT

.00

psig

TEMPIN

.00

F



Example Problems

Design External Pressure Temperature for External Pressure

PEXT

50.00

TEMPEX

650.00

Take Cone as Line of Support for External Pressure:

psig F

Yes

Cone Material Cone Allowable Stress at Temperature

SAC

15000.00

psi


SOC

17500.00

psi

EC

.8500

TC

1.2500

in.

CAC

.0000

in.



BASIS

OD


DS

50.7500

in.


DL

202.5000

in.

ANGLE

30.00

LC

130.0000

in.

Total Axial Force on Large End, External Pressure -157079.00

lb.

Total Axial Force on Small End, External Pressure

lb.



-9964.00

degrees

SA-516 70


17500.00

psi


SOS

17500.00

psi

ES

1.0000

Joint Efficiency of Small Cylinder Actual Thickness of Small Cylinder Corrosion Allowance for Small Cylinder

TS

.3750

in.

CAS

.0000

in.

LS

75.0000

in.

Axial Length of Small Cylinder


SA-516 70


17500.00

psi


SOL

17500.00

psi

EL

.8500

Joint Efficiency of Large Cylinder Actual Thickness of Large Cylinder Corrosion Allowance for Large Cylinder

TL

1.2500

in.

CAL

.0000

in.

LL

250.0000

in.



Beam Type


SA-36


14500.00

psi


14500.00

psi

Location of Reinforcement at Large End of Cone:

Shell

Moment of Inertia of

Section at Large End

RILS

26.90

Area of Reinforcing

Section at Large End

RALS

5.28

sq.in.

Centroid Distance for Section at Large End

RDLS

6.05

in.


in**4

Bar


SA-36


14500.00

psi


14500.00

psi

Location of Reinforcement at Small End of Cone:

Shell

Radial Width of Reinforcing Bar(Small End)

RWSB

3.5000

in.


RTSB

.5000

in.


13-15

Example Problems


EXTERNAL PRESSURE RESULTS, CONE NUMBER

1,


EXTERNAL PRESSURE CALCULATIONS for CONE:


CS-2

at


650.00 25125000.00

F psi

Results for Maximum Allowable External Pressure: TCA

OD

SLEN

D/T

L/D

Factor A

B

1.2500

202.5000

130.00

187.06

.4014

.0013249

9059.26

EMAWP=(4*B)/(3*DT)=(4*9059.259)/(3*187.0615)=64.5724 psig

Results for Required Thickness for External Pressure: TCA

OD

SLEN

D/T

L/D

Factor A

B

1.0325

202.5000

130.00

226.47

.4014

.0009946

8493.51

EMAWP=(4*B)/(3*DT)=(4*8493.511)/(3*226.4709)=50.0050 psig

EXTERNAL PRESSURE CALCULATIONS for SMALL CYLINDER:


CS-2

at


650.00 25125000.00

F psi


OD

SLEN

D/T

L/D

Factor A

B

.3750

50.7500

75.00

135.33

1.4778

.0005587

7019.19

EMAWP=(4*B)/(3*DT)=(4*7019.191)/(3*135.3333)=69.1546 psig


OD

SLEN

D/T

L/D

Factor A

B

.3294

50.7500

75.00

154.08

1.4778

.0004600

5778.14

EMAWP=(4*B)/(3*DT)=(4*5778.136)/(3*154.0769)=50.0022 psig

EXTERNAL PRESSURE CALCULATIONS for LARGE CYLINDER:


CS-2

at


650.00 25125000.00

F psi


OD

SLEN

D/T

L/D

Factor A

B

1.2500

202.5000

250.00

162.00

1.2346

.0005107

6415.52

EMAWP=(4*B)/(3*DT)=(4*6415.521)/(3*162.0000)=52.8026 psig


OD

SLEN

D/T

L/D

Factor A

B

1.2231

202.5000

250.00

165.57

1.2346

.0004943

6209.19

EMAWP=(4*B)/(3*DT)=(4*6209.191)/(3*165.5692)=50.0028 psig


CS-2

at

Elastic Modulus for Large End Reinforcement


CS-2

Elastic Modulus for Small End Reinforcement

13-16

650.00 25125000.00

at

650.00 25125000.00

F psi

F psi



Example Problems

SUMMARY of EXT. PRESSURE RESULTS: Small Cyl

Cone

Large Cyl

Reqd. Thickness + CA

.3294

1.0325

1.2231

in.


.3750

1.2500

1.2500

in.

Max. All. Working Pressure

69.15

64.57

52.80

psig

Design Pressure as Given

50.00

50.00

50.00

psig

REQUIRED AREA of REINFORCEMENT for LARGE END

UNDER EXTERNAL PRESSURE

Large end ratio of pressure to allowable stress

.00336

Large end max. half apex angle w/o reinforcement Large end actual half apex angle

5.908

degrees

30.000

degrees

Area of Reinforcement Required in Large End Shell: ARLE = (RKLE*QL*RCLO*TANà*/(SOL*EL))* (1.0-0.25*((PEXT*RCLO-QL)/QL)*(DELTE/ANGLE) ARLE = ( 1.2069 * 2778.1630 * 101.2500 * .577/( 17500 * .85 )) * ( 1.0 - 0.25 * (( 50.00 * 101.2500 - 2778.1630 ) / 2778.1630 ) ( 5.9076 / 30.0000 ) ARLE = 12.6433 sq.in.

AREA of REINFORCEMENT AVAILABLE in LARGE END SHELL: AeL = .55*( Dl*ts )^« * ( ts + tc/Cosà ) AeL = .55 * ( 202.500 * 1.250 )^« * ( 1.250 + 1.250/ .866 ) AeL =

23.5682 sq.in.

SUMMARY of REINFORCEMENT AREA, LARGE END, EXTERNAL PRESSURE: Area of reinforcement required per App. 1-8(1)

12.6433

sq.in.


23.5682

sq.in.

5.2800

sq.in.

.0000

sq.in.

Area of reinforcement in stiffening ring Additional Area needed to satisfy requirements

REQUIRED MOMENT of INERTIA, LARGE END, EXTERNAL PRESSURE: Area Available in Cone, Shell, and Reinforcement

255.28

sq.in.

Force per Unit Length on Shell / Cone Junction

7670.39

lb./in.

Actual Buckling Stress associated with this Force

4563.38

psi

Material Strain associated with this stress

.000363

REQUIRED MOMENT of INERTIA, LARGE END, EXTERNAL PRESSURE: ISL = AL * DCLO * DCLO * ATL / 10.9 ISL = .000363 * 202.5000 * 202.5000 * 255.28 / 10.9 ISL = 348.86 in.**4

AVAILABLE MOMENT of INERTIA, LARGE END, EXTERNAL PRESSURE: Area

Centroid

Ar*Ce

Shl

10.938

.0000

.000

.1159

1.424

.1

Con

12.630

-2.5259

-31.902

2.6417

29.053

88.1

Sec

5.280

6.6750

35.244

-6.5591

26.900

227.2

TOT

28.848

57.377

315.4

Centroid of Section

Dist

3.342 .1159

I

Ar*Di^2

Moment of Inertia

372.82

SUMMARY of LARGE END INERTIA CALCULATIONS Available Moment of Inertia ( Large End )

372.823

in**4

Required

348.860

in**4


Moment of Inertia ( Large End )

13-17

Example Problems


REQUIRED AREA of REINFORCEMENT for SMALL END

under EXTERNAL PRESSURE

Area of Reinforcement Required in Small End Shell: ARSE = (RKSE * QS * RCSI * TANANG / (SOS*ES) ) ARSE = (1.2069*696.8704*25.3750*.5774/(17500*1.00)) ARSE = .7041 sq.in.

AREA of REINFORCEMENT AVAILABLE in SMALL END SHELL: Aes = .55*(Ds*ts)^«*[(ts-t)+(tc-tr)/cosà )] Aes = .55*( 50.750* .375)^«*[( .375- .329)+( 1.250- .393)/ .866 )] Aes = 2.4844 sq.in.

SUMMARY of REINFORCEMENT AREA, SMALL END, EXTERNAL PRESSURE: Area of reinforcement required per App. 1-8(1)

.7041

sq.in.


2.4844

sq.in.


1.7500

sq.in.

.0000

sq.in.


REQUIRED MOMENT of INERTIA , SMALL END, EXTERNAL PRESSURE: Area Available in Cone, Shell, and Reinforcement

109.56

sq.in.


7742.36

lb./in.


2689.73

psi


.000214

REQUIRED MOMENT of INERTIA , SMALL END, EXTERNAL PRESSURE: ISS = AS * DCSO * DCSO * ATS / 10.9 ISS = .000214 * 50.7500 * 50.7500 * 109.56 / 10.9 ISS = 5.54 in.**4

AVAILABLE MOMENT of INERTIA, SMALL END, EXTERNAL PRESSURE: Area

Centroid

Ar*Ce

Dist

Shl

.900

.0000

.000

.9470

.011

I

Con

3.463

.6926

2.399

.2544

1.155

.224

Sec

1.750

1.9375

3.391

-.9905

1.786

1.717

TOT

6.113

2.952

2.748

5.789

Centroid of Section

.9470

Ar*Di^2 .807

Moment of Inertia

5.70

SUMMARY of SMALL END INERTIA CALCULATIONS Available Moment of Inertia ( Small End )

5.700

in**4

Required

5.543

in**4

Moment of Inertia ( Small End )


Example Problem #3 The third example shows the calculation for moment of inertia with knuckles. The available I is less than the required because the resulting neutral axis is very close to the shell/ knuckle (cone) juncture. FileName : CHECKS

----------------------------------

Conical Analysis : KNUCKLE

13-18

ITEM:

4,

Page

02:09pm,

1 05/18/98



Example Problems


4,

Description: KNUCKLE

Design Internal Pressure Temperature for Internal Pressure

PINT

.00

psig

TEMPIN

.00

F

PEXT

15.00

TEMPEX

500.00

Design External Pressure Temperature for External Pressure

Take Cone as Line of Support for External Pressure:

Cone Material

psig F

Yes

SA-516 70

Cone Allowable Stress at Temperature

SAC

17500.00

psi


SOC

17500.00

psi

EC

1.0000

TC

1.0000

in.

CAC

.0000

in.



BASIS

ID


DS

50.0000

in.


DL

100.0000

in.

ANGLE

20.50

LC

70.0000



degrees in.

SA-516 70


17500.00

psi


SOS

17500.00

psi

ES

1.0000

Joint Efficiency of Small Cylinder Actual Thickness of Small Cylinder Corrosion Allowance for Small Cylinder

TS

.5000

in.

CAS

.0000

in.

LS

50.0000

in.

Axial Length of Small Cylinder


SA-516 70


17500.00

psi


SOL

17500.00

psi

EL

1.0000

Joint Efficiency of Large Cylinder Actual Thickness of Large Cylinder Corrosion Allowance for Large Cylinder

TL

1.0000

in.

CAL

.0000

in.

LL

100.0000

in.



Knuckle


SA-285 C


13800.00

psi


13800.00

psi

Bend Radius for Knuckle at Large End

RBLK

10.0000

in.

Thickness for Knuckle at Large End

RTLK

1.0000

in.


Knuckle


SA-285 C


13800.00

psi


13800.00

psi

Bend Radius for Knuckle at Small End

RBSK

7.0000

in.

Thickness for Knuckle at Small End

RTSK

.5000

in.


13-19

Example Problems


EXTERNAL PRESSURE RESULTS, CONE NUMBER

4,

Description: KNUCKLE

EXTERNAL PRESSURE CALCULATIONS for CONE:


CS-2

at


500.00 27000000.00

F psi


OD

SLEN

D/T

L/D

1.0000

100.6068

70.00

107.41

.5265

Factor A

B

.0022902 11752.49

EMAWP=(4*B)/(3*DT)=(4*11752.490)/(3*107.4087)=145.8911 psig


OD

SLEN

D/T

L/D

Factor A

B

.2734

100.6068

70.00

392.86

.5265

.0003274

4419.89

EMAWP=(4*B)/(3*DT)=(4*4419.892)/(3*392.8625)=15.0006 psig

EXTERNAL PRESSURE CALCULATIONS for SMALL CYLINDER:


CS-2

at


500.00 27000000.00

F psi


OD

SLEN

D/T

L/D

.5000

51.0000

50.00

102.00

.9804

Factor A

B

.0012885 10514.21

EMAWP=(4*B)/(3*DT)=(4*10514.210)/(3*102.0000)=137.4406 psig


OD

SLEN

D/T

L/D

Factor A

B

.1685

51.0000

50.00

302.59

.9804

.0002522

3404.33

EMAWP=(4*B)/(3*DT)=(4*3404.330)/(3*302.5871)=15.0010 psig

EXTERNAL PRESSURE CALCULATIONS for LARGE CYLINDER:


HA-2

at


500.00 25200000.00

F psi


OD

SLEN

D/T

L/D

Factor A

B

1.0000

102.0000

100.00

102.00

.9804

.0012885

9164.62

EMAWP=(4*B)/(3*DT)=(4*9164.623)/(3*102.0000)=119.7990 psig


OD

SLEN

D/T

L/D

Factor A

B

.3465

102.0000

100.00

294.35

.9804

.0002628

3311.67

EMAWP=(4*B)/(3*DT)=(4*3311.668)/(3*294.3505)=15.0010 psig

SUMMARY of EXT. PRESSURE RESULTS: Small Cyl

Cone

Large Cyl

Reqd. Thickness + CA

.1685

.2734

.3465

in.


.5000

1.0000

1.0000

in.

137.44

145.89

119.80

psig

15.00

15.00

15.00

psig

Max. All. Working Pressure Design Pressure as Given

REQUIRED MOMENT of INERTIA, LARGE END, EXTERNAL PRESSURE:

13-20



Example Problems

Area Available in Cone, Shell, and Reinforcement

87.00


sq.in.

1102.29


lb./in.

956.01


psi

.000076

REQUIRED MOMENT of INERTIA, LARGE END, EXTERNAL PRESSURE: ISL = AL * DCLO * DCLO * ATL / 10.9 ISL = .000076 * 100.6068 * 100.6068 * 87.00 / 10.9 ISL = 6.13 in.**4

AVAILABLE MOMENT of INERTIA, LARGE END, EXTERNAL PRESSURE: Area

Centroid

Ar*Ce

Dist

Shl

5.555

.0000

.000

-.2539

.463

.358

Con

2.004

1.0159

2.036

.7621

.273

1.164

Knu

3.757

.2226

.836

-.0313

TOT

11.316

2.873

Centroid of Section

.2539

I

Ar*Di^2

.475

.004

1.211

1.526

Moment of Inertia

2.737

SUMMARY of LARGE END INERTIA CALCULATIONS Available Moment of Inertia ( Large End ) * LOW *

2.737

in**4

Required

6.130

in**4

Moment of Inertia ( Large End )

REQUIRED MOMENT of INERTIA , SMALL END, EXTERNAL PRESSURE: Area Available in Cone, Shell, and Reinforcement

49.50

sq.in.


925.55

lb./in.


728.52

psi


.000054

REQUIRED MOMENT of INERTIA , SMALL END, EXTERNAL PRESSURE: ISS = AS * DCSO * DCSO * ATS / 10.9 ISS = .000054 * 51.9499 * 51.9499 * 49.50 / 10.9 ISS = .66 in.**4

AVAILABLE MOMENT of INERTIA, SMALL END, EXTERNAL PRESSURE: Area

Centroid

Ar*Ce

Dist

Shl

1.389

.0000

.000

.1114

.029

.017

con

.254

.5037

.128

-.3923

.024

.039

knu

1.297

.1537

.199

-.0423

.053

.002

TOT

2.940

.106

.059

Centroid of Section

.328 .1114

I

Ar*Di^2

Moment of Inertia

.16

SUMMARY of SMALL END INERTIA CALCULATIONS Available Moment of Inertia ( Small End ) * LOW *

.165

in**4

Required

.661

in**4

Moment of Inertia ( Small End )



13-21

Example Problems

13-22




&KDSWHU The Floating Head Module

Introduction The PVElite Floating Head Module performs internal and external pressure design of spherically dished covers (bolted heads) using the ASME Code, Section VIII, Division 1 rules, 2001, A-2001.

Purpose, Scope, and Technical Basis The PVElite Floating Head Module calculates the required thickness of spherically dished covers (bolted heads) according to the ASME Code, Section VIII, Division 1 analysis rules found in Appendix 1, Paragraph 1-6. A more detailed analysis of bolted dished heads is included, based on Soehren’s analysis, “The Design of Floating Heads for HeatExchangers,” ASME 57-A-7-47. The more detailed analysis may be used for design of floating heads, as specifically mentioned in the ASME Code, Paragraph 1-6 (h). The module calculates required thickness for the dished part of the head under both internal and external pressure. Also calculated are the required thickness of the flange and the backing ring. Three types of heads as defined in the Code are included. The Soehren’s analysis applies only to the most common type of head, type d.

The Floating Head Module

14-1



Figure 14A shows geometry for the Floating Heads Module.

Figure 14A - Geometry for the Floating Heads Module

14-2




Discussion of Input Data Main Input Fields Floating Head Identification Number Enter the floating head ID number. It is recommended that the floating head numbers start at 1 and increase sequentially, but you may also enter some other meaningful number. This field is required, since the program uses this field to determine if a floating head has been defined. Floating Head Description Enter an alpha-numeric tag for this floating head. This entry is optional. Floating Head Type (b, c, d) Enter the type of floating head or spherically dished cover which you are analyzing. b

=

solid thick head, spherically dished.

c

=

thin dished head, continuous across flange face.

d

=

spherical cap welded to flange ID.

Type d is the most common type of head used for heat exchanger floating heads. Tube Side (Internal) Design Pressure Enter the internal pressure, which is the pressure on the concave side of the head, and is also the tubeside pressure for heat exchanger floating heads. Normally you may enter both the shellside and the tubeside pressures and evaluate the entire head in a single analysis. However, when analyzing a type ‘d’ head, the interaction between shellside and tubeside pressure may result in a lower thickness than if each pressure is entered separately. Therefore you may want to run the program twice, with first internal and then external pressures set to zero. Shell Side (External) Design Pressure Enter the external pressure, which is the pressure on the convex side of the head, and is also the shellside pressure for heat exchanger floating heads. Normally you may enter both the shellside and the tubeside pressures and evaluate the entire head in a single analysis. However, when analyzing a type ‘d’ head, the interaction between shellside and tubeside pressure may result in a lower thickness than if each pressure is entered separately. Therefore you may want to run the program twice, with first internal and then external pressures set to zero. Design Temperature Enter the design temperature for each head. This temperature will be used to interpolate the material allowable tables and external pressure curves. Material Specification Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right


14-3



clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Allowable Stress, Design Temperature This entry is automatically filled in by the program by entering a material specification.

Caution

You should double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. When you change the design temperature, or the thickness of the head, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature.

Allowable Stress, Ambient Temperature This entry is automatically filled in by the program by entering a material specification.

Caution

You should double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. When you change the design temperature, or the thickness of the head, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature.

Inside Crown Radius of Head Enter the inside crown radius of the head. This value may be any dimension greater than the inside radius of the flange. However, values roughly equal to the flange ID are more typical. Actual Thickness of Head Enter the minimum thickness of the actual plate used to build the floating head or spherical cap, or the minimum thickness measured for an existing floating head or spherical cap. Tube Side (Internal) Corrosion Allowance Enter the corrosion allowance on the concave side of the head. The shellside and tubeside corrosion allowances are fully implemented in this version of FLOHEAD. Thicknesses and diameters are adjusted by the program for the evaluation of allowable pressure. They are also added to the required thicknesses.

14-4




Shell Side (External) Corrosion Allowance Enter the corrosion allowance on the convex side of the head. The shellside and tubeside corrosion allowances are fully implemented in this version of FLOHEAD. Thicknesses and diameters are adjusted by the program for the evaluation of allowable pressure. They are also added to the required thicknesses. Outside Diameter of Flange Enter the outer diameter of the flange. This value is referred to as “A” in the ASME code. Inside Diameter of Flange Enter the inner diameter of the flange. For integral type flanges, this value will also be the inner pipe diameter. This value is referred to as “B” in the ASME code. The corrosion allowance will be used to adjust this value (two times the corrosion allowance will be added to the uncorroded ID given by the user). Actual Thickness of Flange Enter the through thickness of the flange. For type c spherical caps this includes the thickness of the head. Diameter of Bolt Circle Enter the diameter of the bolt circle of the flange. Nominal Bolt Diameter Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the “Root Area” cell which will pop up when you specify “root area” as the thread series. Thread Series There are three options for this entry:

•

TEMA Bolt Table

•

UNC Bolt Table

•

User specified root area of a single bolt

Number of Bolts Enter the number of bolts to be used in the flange analysis. Note that the number of bolts is almost always a multiple of four. Full Face Gasket Check this field if there is a full face gasket on the floating head. A full face gasket extends from the ID of the flange to the OD, enclosing the bolt holes. These gaskets are usually soft materials such as rubber or an elastomer, so that the bolt stresses do not go too high during gasket seating. The program adjusts the flange analysis and the design formulas to account for the full face gasket.


14-5



Flange Face Outer Diameter Enter the outer diameter of the flange face. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Flange Face Inner Diameter Enter the inner diameter of the flange face. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. Gasket Outer Diameter Enter the outer diameter of the gasket. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Gasket Inner Diameter Enter the inner diameter of the gasket. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. For gasket properties, refer to the table in Chapter 12, The Flange Module. Flange Face Facing Sketch Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: FACING SKETCH

PVElite EQUIVALENT

1a

1

flat finish faces

1b

2

serrated finish faces

1c

3

raised nubbin-flat finish

1d

4

raised nubbin-serrated finish

2

5

1/64 inch nubbin

3

6

1/64 inch nubbin both sides

4

7

large serrations, one side

5

8

large serrations, both sides

6

9


DESCRIPTION

Gasket Thickness Enter the gasket thickness. This value is only required for facing sketches 1c and 1d (PVElite equivalents 3 and 4).

14-6




Nubbin Width If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6 (PVElite equivalents 3, 4, 5, and 9). Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Length of Partition Gasket This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. If the pass partition gaskets are a different width than the main gasket, scale the length you enter so that the area of the gasket is correct. Width of Partition Gasket Enter the width of the pass partition gasket. The gasket properties such as the facing sketch, column, M and Y will be taken from the main gasket. Using these properties and the know width, PVElite will compute the effective seating width and compute the gasket loads contributed by the partition gasket. Distance from Flange Centroid to Head Centerline HR is the distance from the flange centroid to the intersection of the head centerline and the flange. HR is positive if it is above the flange centroid, and negative if it is below the flange centroid. HR is used in the Code calculation, but not in the Soehren’s calculation. Is the Flange Slotted? Check this box if the flange has slotted bolt holes for quick opening. A slotted flange has bolt holes which extend radially to the outer edge of the flange. The program automatically adjusts for this condition - you do not have to change the flange outside diameter. Do You Need to Perform Soehren’s Calculation? Check this box if you wish to perform the Soehren’s Calculation. Soehren’s calculation is a more detailed analysis of the interaction between the spherical cap and the flange. Frequently the stresses calculated using this method will be acceptable for heads or flanges that are slightly less thick than required by the normal code rules. Note that this analysis can only be done for type d heads. Note also that the Code (Par. 1-6(h)) allows this type of analysis. Is There a Backing Ring? Check this box if there is a backing ring. A backing ring is a second flange used to sandwich the tubesheet of a floating head heat exchanger. The backing ring may be a split ring. If the ring has one split, then it has been split along a diameter, into two pieces. The bending moment on the ring is multiplied by 2.0 for this case. A ring with two splits has been sliced in half like a bagel, and then each half has been split along a diameter. The ring is assembled with the diametral splits offset by 90 degrees. For this case, enter the thickness of one half of the original ring, since each half is required to support 75 percent of the original design moment.


14-7

Pop-Up Input Fields


Pop-Up Input Fields Bolt Root Area For nonstandard bolts, enter the root cross sectional area of the bolt. Inside Depth of Flange from Flange Face to Attached Head Q is the distance from the bolting face of the flange to the intersection of the head inside diameter and the flange. Q is used in the Soehren’s calculation, while HR is used in the Code calculation. Backing Ring Inside Diameter Enter the inside diameter of the backing ring. This value is usually a little larger than the inside diameter of the flange. Backing Ring Actual Thickness Enter the actual through thickness of the backing ring. Note that for doubly split rings, this is the thickness of each piece. Number of Splits in Backing Ring (0, 1, or 2) The backing ring may be a split ring. If the ring has one split, then it has been split along a diameter, into two pieces. The bending moment on the ring is multiplied by 2.0 for this case. A ring with two splits has been sliced in half like a bagel, and then each half has been split along a diameter. The ring is assembled with the diametral splits offset by 90 degrees. For this case, enter the thickness of one half of the original ring, since each half is required to support 75 percent of the original design moment.

14-8




Discussion of Results Internal Pressure Results for the Head The ASME Code provides a simple formula for calculating the required thickness of the head under internal pressure. This formula is the same for type b, c, and d heads: t = 5PL/6S The program solves this formula for required thickness, maximum allowable working pressure, and actual stress, and displays the results. Note that these results are also displayed in the thickness summary at the end of the printout. External Pressure Results for the Head The required thickness and maximum allowable working pressure for each head type is based on the external pressure requirements for an equivalent sphere. Intermediate Calculations for Flanged Portion of Head Three separate bending moments are calculated for each head. These are the bolt up moment, the moment due to external pressure, and the moment due to internal pressure. In each case the moment is calculated per the ASME Code, Section VIII, Division 1, Appendix 2. However, in the case of the type d head the moment is further modified to take into account the force imposed on the flange by the pressure on the head. This force is shown in the printout as MH. The sign of this force will be negative if the head is attached above the centroid of the flange, and positive if the head is attached below the centroid. Required Thickness Calculations The required thickness formulae for each flange type and loading condition are printed by the program. These formulae are taken from Appendix 1-6, paragraphs (e)(2) and (3), (f)(2) through (5) and (g)(2). The required thickness calculations for the backing ring are also shown. The backing ring is taken as a ring flange and calculated per Appendix 2. The analysis is corrected for the number of splits in the backing ring, and shows the required thickness for each piece of the split ring. The thickness calculations for the main flange and backing ring involve the factor F which is directly proportional to the design pressure. Thus when the pressure is 0, for the bolt-up condition, the factor F is theoretically equal to 0. Some however interpret the Code to mean that F should be computed using the design pressure even for the bolt-up cases. There is a setup file directive that allows you to toggle this to work one way or the other. To keep the program results consistent with older versions, this setup file parameter is set to compute F with 0 pressure for the bolt-up conditions. After the required thicknesses are calculated, a summary table is printed. Soehren’s Calculations The ASME Code, Section VIII, Division 1, Appendix 1-6, paragraph (h) states: These formulas are approximate in that they do not take into account continuity between the flange ring and the dished head. A more exact method of analysis which takes this into account may be used if it meets the requirements of U-2.


14-9



The analysis referred to in this paragraph is the Soehren’s calculation, based on the paper “The Design of Floating Heads for Heat-Exchangers”, ASME 57-A-7-47. Intermediate results and calculated stresses are shown in the printout. Equation numbers are included from the original paper. Allowable stresses are not shown in the printout, but bending stresses should be limited to 1.5 times the basic Code allowable stress, while membrane stresses should be limited to 1.0 times the basic Code allowable.

14-10



Example Problems

Example Problems The following 2 examples show the same floating head subjected to internal and external pressure. Separate runs have been made to clarify the individual calculations. These examples are included in the CHECKS file. Example Problem #1 INPUT ECHO, Floating Head Analysis:

2,

Floating Head Type

Description: FLOHEAD-INT

Appendix 1-6 type (d)

Tube Side ( Internal ) Design Pressure

PTS

100.00

psig

Shell Side ( External ) Design Pressure

PSS

0.00

psig

TEMP

360.00

Design Temperature for Spherical Head

Head Material

F

SA-516 70

Head Allowable Stress at Temperature

SOH

17500.00

psi

Head Allowable Stress at Ambient

SAH

17500.00

psi

Crown Radius for Spherical Head

CR

43.8750

in.

Head Thickness

TH

0.6250

in.

CATS

0.0625

in.

Shell Side ( External ) Corrosion Allowance CASS

0.1250

in.

Tube Side ( Internal ) Corrosion Allowance

Flange Material

SA-516 70

Flange Allowable Stress at Temperature

SOC

17500.00

psi

Flange Allowable Stress at Ambient

SAC

17500.00

psi


FOD

47.6250

in.


FID

43.8750

in.

TC

3.1250

in.

Flange Thickness

Bolt Material

SA-193 B7M


SBO

20000.00

psi


SBA

20000.00

psi

DB

45.7500

in.

DBOLT

0.7500

in.

Diameter of Bolt Circle Nominal Bolt Diameter Type of Threads

TEMA Thread Series

Number of Bolts

44

Full Face Gasket ( Yes or No )

No


FOD

44.7500

in.


FID

43.8750

in.


GOD

44.6250

in.


GID

43.8750

in.

Gasket Factor, m,

M

3.7500


Y

7600.00


1, Code Sketch 1a


2, Code Column II

psi

Gasket Thickness

0.1250

in.

Flange Face Nubbin Width

0.0000

in.


14-11

Example Problems


Length of Partition Gasket

0.0000

in.

Width

0.0000

in.

0.6875

in.

of Partition Gasket

Distance from Head Centerline to Flange Centroid

The Flange is not Slotted.

This unit does not have a Backing Ring.

INTERNAL PRESSURE RESULTS FOR SPHERICAL HEADS

Thickness Due to Internal Pressure: t = 5PL / 6S per Appendix 1-6 t = ( 5 * 100.00 * 43.9375 ) / ( 6 * 17500 ) t = 0.2092 in.

Maximum Allowable Working Pressure at Given Thickness: Pa = 6S(T-Cass-Cats) / 5L per Appendix 1-6 Pa = ( 6 * 17500 * 0.4375 ) / ( 5 * 43.9375 ) Pa = 209.10 psig

Maximum Allowable Working Pressure, New and Cold: Pnc = 6ST / 5L per Appendix 1-6 Pnc = ( 6 * 17500 * 0.6250 ) / ( 5 * 43.8750 ) Pnc = 299.15 psig

Actual stress at given pressure and thickness: Sact = 5PL / 6(T-Cass-Cats) per Appendix 1-6 Sact = ( 5 * 100.00 * 43.9375 ) / ( 6 * 0.4375 ) Sact = 8369. psi

INTERMEDIATE CALCULATIONS FOR FLANGED PORTION:


RN = (GODC-GIDC) / 2.0

0.375

in.

Basic Gasket Width,

B0 = RN / 2.0

0.188

in.


BE = B0

0.188

in.

44.250

in.

13.288

sq.in.

Gasket Reaction Diameter, G = (GODC+GIDC) / 2.0

Bolting Information for TEMA Thread Series : Total Area of Bolts Minimum radial distance between hub and bolts

1.125

in.


0.813

in.


1.750

in.

Actual circumferential spacing between bolts

3.264

in.


5.912

in.

BASIC FLANGE AND BOLT LOADS: Hydrostatic End Load due to Pressure

H

153785.9

lb.

Contact Load on Gasket Surfaces

HP

19549.1

lb.

Hydrostatic End Load at Flange ID

HD

152053.1

lb.

Pressure Force on Flange Face

HT

1732.8

lb.

Radial Component of Head Membrane Force

HH

264950.1

lb.

WM1

173334.9

lb.

Operating Bolt Load:

14-12



Example Problems

Gasket Seating Bolt Load Required Bolt Area

Flange Design Bolt Load

WM2

198097.1

AM

9.905

lb. sq.in.

W

231928.5

lb.

HG

19549.0

lb.

Distance to Gasket Load Reaction

DHG

0.7500

in.

Distance to Face Pressure Reaction

DHT

0.8125

in.

Distance to End Pressure Reaction

DHD

0.8750

in.

Gasket Seating Force


Force

Distance

Bolt Corr

Moment

End Pressure,

Md

152053.

0.8750

1.0000

Face Pressure,

Mt

1733.

0.8125

1.0000

117. ft.lb.

Gasket Load,

Mg

19549.

0.7500

1.0000

1222. ft.lb.

Floating Hd. Load, Mh

264950.

0.6875

1.0000

-15179. ft.lb.

Gasket Seating,

231929.

0.7500

1.0000

14496. ft.lb.

Ma

TOTAL MOMENT FOR OPERATION ( Internal Pressure ) TOTAL MOMENT FOR GASKET SEATING ( Int. Pressure )

11087. ft.lb.

2753. ft.lb. 14496. ft.lb.

Required thickness for Main Flange, internal operating conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.710 + SQRT( 0.710 * 0.710 + 1.162 ) T = 2.0001 in.

Required thickness for Main Flange, internal bolt-up conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.000 + SQRT( 0.000 * 0.000 + 6.116 ) T = 2.4731 in.

Required thickness for Main Flange, external operating conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.000 + SQRT( 0.000 * 0.000 + 0.000 ) T = 0.0000 in.

Required thickness for Main Flange, external bolt-up conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.000 + SQRT( 0.000 * 0.000 + 6.116 ) T = 2.4731 in.

SUMMARY OF REQUIRED THICKNESSES: Tubeside (Internal) Pressure

Head 0.2092

Tubeside Gasket Seating Load

Flange 2.0001 in. 2.4731 in.

Shellside Gasket Seating Load

2.4731 in.

Maximum + Corrosion Allowance

0.3967

2.6606 in.

Actual Thickness as Given

0.6250

3.1250 in.

WEIGHT OF HEAD AND FLANGE: Weight of Spherical Head, Uncorroded Weight of Spherical Head, Corroded Weight of Flange Ring, Uncorroded Weight of Flange Ring, Corroded

WHD

286.3

lb.

WHDCA

201.7

lb.

WFL

238.3

lb.

WFLCA

222.4

lb.

The PV Elite Program, (c) 1989-1998 by COADE Engineering Software


14-13

Example Problems


Example Problem #2 INPUT ECHO, Floating Head Analysis:

3,

Floating Head Type

Description: FLOHEAD-EXT

Appendix 1-6 type (d)

Tube Side ( Internal ) Design Pressure

PTS

0.00

psig

Shell Side ( External ) Design Pressure

PSS

55.00

psig

TEMP

360.00

Design Temperature for Spherical Head

Head Material

F

SA-516 70

Head Allowable Stress at Temperature

SOH

17500.00

psi

Head Allowable Stress at Ambient

SAH

17500.00

psi

Crown Radius for Spherical Head

CR

43.8750

in.

Head Thickness

TH

0.6250

in.

CATS

0.0625

in.

Shell Side ( External ) Corrosion Allowance CASS

0.1250

in.

Tube Side ( Internal ) Corrosion Allowance

Flange Material

SA-516 70

Flange Allowable Stress at Temperature

SOC

17500.00

psi

Flange Allowable Stress at Ambient

SAC

17500.00

psi


FOD

47.6250

in.


FID

43.8750

in.

TC

3.1250

in.

Flange Thickness

Bolt Material

SA-193 B7M


SBO

20000.00

psi


SBA

20000.00

psi

DB

45.7500

in.

DBOLT

0.7500

in.


TEMA Thread Series

Number of Bolts

44

Full Face Gasket ( Yes or No )

No


FOD

44.7500

in.


FID

43.8750

in.


GOD

44.6250

in.


GID

43.8750

in.

Gasket Factor, m,

M

3.7500


Y

7600.00


1, Code Sketch 1a


2, Code Column II

psi

Gasket Thickness

0.1250

in.

Flange Face Nubbin Width

0.0000

in.


0.0000

in.

Width

0.0000

in.

0.6875

in.

of Partition Gasket

Distance from Head Centerline to Flange Centroid

The Flange is not Slotted.

14-14



Example Problems

This unit does not have a Backing Ring.

EXTERNAL PRESSURE RESULTS, SPHERICAL HEAD


CS-2

at

360.00


28400000.00

F psi


OD

D/T

0.4375

44.3750

101.43

Factor A

B

0.0012324 12411.07

EMAWP = B/DT = 12411.0674 / 101.4286 = 122.3626


OD

D/T

Factor A

B

0.2470

44.3750

179.64

0.0006958

9880.94

EMAWP = B/DT = 9880.9414 / 179.6388 = 55.0045

INTERMEDIATE CALCULATIONS FOR FLANGED PORTION:



0.375

in.

Basic Gasket Width,

B0 = RN / 2.0

0.188

in.


BE = B0

0.188

in.

44.250

in.

13.288

sq.in.

Gasket Reaction Diameter, G = (GODC+GIDC) / 2.0

Bolting Information for TEMA Thread Series : Total Area of Bolts Minimum radial distance between hub and bolts

1.125

in.


0.813

in.


1.750

in.

Actual circumferential spacing between bolts

3.264

in.


5.912

in.

BASIC FLANGE AND BOLT LOADS: Hydrostatic End Load due to Pressure

H

84582.2

lb.

Contact Load on Gasket Surfaces

HP

10752.0

lb.

Hydrostatic End Load at Flange ID

HD

83629.2

lb.

Pressure Force on Flange Face

HT

953.0

lb.

Radial Component of Head Membrane Force

HH

145805.6

lb.


WM1

95334.2

lb.

Gasket Seating Bolt Load

WM2

198097.1

lb.

AM

9.905

Required Bolt Area

Flange Design Bolt Load

sq.in.

W

231928.5

lb.

HG

10752.0

lb.

Distance to Gasket Load Reaction

DHG

0.7500

in.

Distance to Face Pressure Reaction

DHT

0.8125

in.

Distance to End Pressure Reaction

DHD

0.8750

in.

Gasket Seating Force

SUMMARY OF MOMENTS FOR EXTERNAL PRESSURE: LOADING

Force

Distance

Bolt Corr

Moment

End Pressure,

Md

83629.

0.1250

1.0000

871. ft.lb.

Face Pressure,

Mt

953.

0.0625

1.0000

5. ft.lb.


14-15

Example Problems


Floating Hd. Load, Mh

145806.

0.6875

1.0000

-8353. ft.lb.

Gasket Seating,

231929.

0.7500

1.0000

14496. ft.lb.

Ma

TOTAL MOMENT FOR OPERATION ( External Pressure ) TOTAL MOMENT FOR GASKET SEATING ( Ext. Pressure )

7477. ft.lb. 14496. ft.lb.

Required thickness for Main Flange, internal operating conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.000 + SQRT( 0.000 * 0.000 + 0.000 ) T = 0.0000 in.

Required thickness for Main Flange, internal bolt-up conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.000 + SQRT( 0.000 * 0.000 + 6.116 ) T = 2.4731 in.

Required thickness for Main Flange, external operating conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.390 + SQRT( 0.390 * 0.390 + 3.155 ) T = 2.2089 in.

Required thickness for Main Flange, external bolt-up conditions: T = F + SQRT( F * F + J ) per 1-6(g) T = 0.000 + SQRT( 0.000 * 0.000 + 6.116 ) T = 2.4731 in.

SUMMARY OF REQUIRED THICKNESSES: Shellside (External) Pressure

Head 0.2470

Tubeside Gasket Seating Load

Flange 2.2089 in. 2.4731 in.

Shellside Gasket Seating Load

2.4731 in.

Maximum + Corrosion Allowance

0.4345

2.6606 in.


0.6250

3.1250 in.

WEIGHT OF HEAD AND FLANGE: Weight of Spherical Head, Uncorroded Weight of Spherical Head, Corroded Weight of Flange Ring, Uncorroded Weight of Flange Ring, Corroded

WHD

286.3

lb.

WHDCA

201.7

lb.

WFL

238.3

lb.

WFLCA

222.4

lb.


14-16



&KDSWHU The Horizontal Vessel Module

Introduction This chapter discusses the Horizontal Vessel module of the PVElite program. To use the Horizontal Vessel module the current analysis type should be Horizontal Vessel. This module computes stresses in horizontal pressure vessels created by the combination of internal pressure and the weight of the vessel, its contained liquid and stiffener rings. If included in the analysis, additional loads due to wind per ASCE-95 or 93 and earthquake will be included. The module is based on “Stresses in Large Horizontal Cylindrical Pressure Vessels on Two Saddle Supports”, The Welding Research Supplement, 1951 and subsequent interpretations of that work. This is also termed Zick’s Analysis.

Discussion of Input Main Input Fields Vessel Number Enter the vessel number for this analysis. This number can be up to 15 digits in length. Vessel Description Any combination up to 15 letters and numbers can be used to briefly identify the vessel that is being analyzed. This description is reflected in the output reports and is used in error checking. If you want to use the factor 6.0 instead of 1.5 for the saddle reaction force FWT (due to wind load) or FST (due to seismic load) (equation for Q2 per D. Moss “Pressure Vessel Design Manual” p.109), you need to type the single character “:” at the very end of this input field for description. It is generally conservative to use the factor of 6. The program uses 1.5 as default. Vessel Design Pressure Enter the pressure under which the horizontal vessel is operating. A positive entry here indicates internal pressure while a negative number indicates external pressure. Please note that no external pressure check for adequate wall thickness will be performed. Use the shell program and analyze the geometry before using the HORIZONTAL VESSEL module.

The Horizontal Vessel Module

15-1

Discussion of Input


Vessel Design Temperature Enter the maximum temperature the horizontal vessel will be operating at. The temperature will be used in determining the allowable stress of the material chosen. If the temperature is changed, note that the allowable stress of the material at operating temperature will change accordingly. Corrosion Allowance Enter the allowance given for corrosion in this field. The corrosion allowance cannot be greater than the vessel wall thickness. In addition, it must be greater than 0. Material Specification Enter the material specification for the shell section of the horizontal vessel. An example of a material type is SA-516 70. Define the material by typing in the name. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Allowable Stress at Operating Temperature The stress value at the design/operating temperature should appear in this cell. This number must always be greater than 0. Allowable Stress at Ambient Temperature The stress value at ambient temperature should appear in this cell. This number must always be greater than 0. Density of Stored Liquid Enter the density of the fluid in the horizontal vessel. The program will conservatively assume the vessel is filled with this liquid. The units for fluid density are displayed above. Liquid Height from Bottom of Tank Enter the height of the liquid in the tank. Normally, a Zick analysis is run with the vessel full of water, however, it may be necessary to run a partially filled tank for wind or seismic analysis for an operating type load case. Extra Weight Enter any additional weight present on the vessel. Additional weight may come from insulation, steel structures or piping loads. There is no on screen range checking for this entry since it may be positive or negative. However, if negative, this entry should not be greater than the total weight of the vessel. Check Saddle Webs & Base Plate If you wish PVElite to perform computations on the structure which supports the vessel check this field. PVElite will compute the inertia’s, moments and forces on the members necessary to perform an AISC unity check.

15-2



Discussion of Input

Apply Wind Loads to Vessel If wind loads are to be considered, check this field. If checked, other information such as basic wind speed and input prompts will have to be answered. Apply Seismic Loads to Vessel If seismic loads are a design consideration check this field. Both seismic and wind loads will increase the saddle load reaction forces, and thus higher vessel stresses will result. Shell and Head Diameter Basis If the diameter basis is Inside Diameter enter a 0 in this field. If the basis is Outside Diameter enter a 1 in this field. Shell Diameter Enter the shell diameter with respect to the shell and head diameter basis. The diameter must be greater than 0 and greater than 2.0 times the wall thickness. Shell Length Tangent to Tangent Enter the length of the cylindrical shell from tangent to tangent. In previous versions of PVElite this entry was in inches. Now the default unit for this entry is feet. Shell Thickness Enter the uncorroded thickness of the shell in this cell. PVElite will automatically corrode the wall thickness as necessary. Shell Joint Efficiency Enter the seam efficiency of the shell. This value is greater than 0 and less than or equal to 1.0. This entry is used to compute the required thickness of the shell. Head Type Enter the type of head that is used on the vessel ends. If a flat head is selected then it is assumed to be round and the same diameter as the shell. The acceptable range of input is between 1 and 4. Head Thickness Enter the uncorroded thickness of the head. The value must be greater than 0.0. Effects of corrosion are handled automatically. Head Joint Efficiency Enter the seam efficiency of the head. This value is greater than 0 and less than or equal to 1.0. This entry is used to compute the required thickness of the head. Distance from Saddle to Vessel Tangent Enter the length from the vessel tangent to the saddle support. This distance must be positive and less than 1/2 of the vessel tangent to tangent length.


15-3

Discussion of Input


Saddle Width Enter the width of the surface on the saddle support that will contact the vessel. Saddle Bearing Angle Enter the number of degrees that the saddle bears on the shell surface. Valid entries range from 120 to 180 degrees. Wear Pad Thickness If there is a wear pad on the vessel, enter that thickness here. If the distance from the vessel tangent to the saddle location is less than or equal to 0.5 times the shell radius and the wear pad extension above the horn of the saddle is greater than the shell radius divided by 10.0 then the thickness of the wear pad will be included. If this is not the case then the shell thickness - ca will be used. Wear Pad Extension Above Horn of Saddle If the vessel has a wear pad and it extends above the horn of the saddle enter that extension distance here. For more information on wear pads, see the help text for wear pad thickness. Wear Pad Width If the vessel has a wear pad enter the width here. The width of the wear pad is measured along the long axis of the vessel. Stiffening Ring Present If the vessel is equipped with stiffening rings check this field. Stiffening rings are used to reduce stresses in the vicinity of the saddle supports and are also used to meet external pressure requirements. When equipped with rings the assumption is that there are either 1 or 2 rings located directly over the saddle. The rings are assumed to span (360 - saddle bearing angle) degrees around the vessel. This is mainly used for the calculation of the ring weight.

15-4



Pop-Up Input Fields

Pop-Up Input Fields Base Plate Length Enter the length of the base plate. This is typically referred to as dimension “A”. This value is usually close to the diameter of the vessel. Base Plate Thickness Enter the thickness of the base plate. If you wish to consider any external corrosion or erosion enter the corroded thickness value, not the uncorroded value. The base plate thickness will be computed using a beam bending type equation found in pressure vessel texts. The base plate thickness is not a function of the number of ribs. Base Plate Width Enter the width of the base plate. This is the short dimension. Number of Ribs Enter the number of ribs in your design. This number should include the outside ribs. Thickness of Ribs Enter the thickness of the ribs. The ribs run in a direction that is parallel to the long axis of the vessel. Any external corrosion allowance should be taken into account when this value is entered. Thickness of Web Enter the thickness of the Webs. The webs run in a direction perpendicular to the long axis of the vessel. Any external corrosion should be taken into account when this value is entered. Web Location Center or Side Select the web location. Center webs run through the middle of the middle of the base plate. Side webs will run along the edge of the base plate. Height of Center Web The height of the center web extends from the bottom of the base to the shell ID. Force Coefficient Enter the force coefficient for vessel here. The acceptable range of input is between 0.5 and 1.2. This can be seen as Table 12 in ANSI A58.1. For ASCE 7-95, refer to p32-33. Additional Area The user may wish to consider the additional area exposed to the wind from piping, platforms, insulation etc. PVElite will automatically compute an effective diameter with the input diameter known. Wind Pressure on Vessel If your vessel specification calls out for a constant wind pressure design, and you know what that pressure is, enter it here. Most Wind Design codes have minimum wind pressure


15-5

Pop-Up Input Fields


requirements, so check those carefully. The wind pressure will be multiplied by the area calculated by the program to get a shear load and a bending moment. If you enter a positive number in here, PVElite will use this number regardless of the information in the following cells. Importance Factor ( I ) Enter the value for the importance factor here. The importance factor accounts for the degree of hazard to life and property. If the vessel is 100 miles ( 160 kilometers ) from the hurricane oceanline enter a 1.00. If the vessel is at the hurricane oceanline enter 1.05. Values up to 1.11 are acceptable here. Refer to ASCE #7 and ANSI 58.1 for more information on the importance factor (Table 1 and Table 5 in ANSI A58.1). For ASCE 7-95, refer to Table 6-2). Basic Wind Speed Enter the basic wind speed which the vessel will be subject to. Positive values will be accepted. A minimum value of 70 miles per hour is recommended. Wind Exposure Enter an integer here for the ASCE 7 wind exposure factor. Exposure (A)- “Large city centers with at least 50% of the buildings having a height in excess of 70 ft.” Exposure (B)- “Urban and suburban areas, wooded areas, or other terrain with numerous closely spaced obstructions having the size of single family dwellings.” Exposure (C)- “Open terrain with scattered obstructions having heights generally less than 30 feet. This category includes flat, open country and grasslands.” Exposure (D)- “Flat, unobstructed costal areas directly exposed to wind flowing over large bodies of water.”

Note

Most petrochemical sites use Exposure C.

Height of Vessel Above Grade Enter the height of the vessel above the surface of the earth (grade). Distance from Vessel Centerline to Saddle Base Enter the distance from the center of the vessel to the base of the saddle support on which the vessel sits. Use ASCE 7-95 Code If you choose to use ASCE 7-95 code, check this field. Then enter the following cells. Types of Hill Enter the type of hill. See ASCE 7-95 Fig. 6-2 for details.

15-6

•

None

•

2-D Ridge



Pop-Up Input Fields

•

2-D Escarpment

•

3-D Axisym. Hill

Height of Hill or Escarpment (H) Enter height of hill or escarpment relative to the upwind terrain. See ASCE 7-95 Fig. 6-2 for detail. Distance to Site (x) Enter distance (upwind or downwind) from the crest to the building site. See ASCE 7-95 Fig. 6-2 for detail. Height Above Ground (z) Enter height above local ground level for the vessel. You may use the approximate distance between the center of the vessel to LOCAL ground. See ASCE 7-95 Fig. 6-2 for detail. Distance to Crest (Lh) Enter distance upwind of crest to where the difference in ground elevation is half the height of hill or escarpment. See ASCE 7-95 Fig. 6-2 for detail. Natural Frequency for the Structure (Fn) — Optional (Hz) Enter the natural frequency for the structure. The program will use ASCE 7-95 part 6.6 category III if Fn < 1.0 Hz or TANTAN/OD > 4.0. Damping Ratio (beta) — Optional Enter the damping ratio for the structure if you like to use ASCE 7-95 part 6.6 category III (if Fn < 1.0 Hz or TANTAN/OD > 4.0). Seismic Zone Enter the seismic zone in which your vessel is operating. The seismic zones are pictured in ASCE #7. A value of 0 will not increase the saddle reaction force. A zone entry of 4 will produce the highest saddle load reactions. Distance from Vessel Centerline to Saddle Base Enter the distance from the center of the vessel to the bottom of the saddle support. This distance must be greater than the vessel outside radius. If both wind and seismic loads are both considered simultaneously this value should be the same. User-Entered Seismic Zone Factor CS When you enter a valid seismic zone and leave this field blank or 0, PVElite will look the seismic zone factor up from an applicable table. This number is then used in conjunction with the operating weight of the vessel to compute the forces which act on the saddle supports. If for any reason the table value of Cs is unacceptable, entry of a non-zero value will cause this to be used in lieu of the table value. This might occur if the building code in your project specifications is different from the one used by PVElite.


15-7

Pop-Up Input Fields


Aspect Ratio (D/2H) for Elliptical Heads Enter the aspect ratio for elliptical heads here. A very typical aspect ratio for an elliptical head is 2:1. This would mean entering a 2 in this field. Knuckle Ratio for Torispherical Heads The knuckle ratio for a torispherical head is defined as the crown radius of the head divided by the knuckle radius. This ratio is typically 16.6667:1 which means that a value of 16.667 would be entered here. Note since this is a ratio, this value is unitless. Crown Radius for Torispherical Heads Enter the crown radius of the torispherical head in this cell. Stiffening Ring Location If the stiffening rings are located on the outside of the vessel select ID. If the rings are located inside the vessel select OD. Stiffening Ring Material Specification Enter the material specification for the stiffening ring. An example of a material type is SA-516 70. Define the material by typing in the name. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Stiffening Ring Properties

Moment of Inertia of Stiffening Ring If the stiffening ring properties cannot be defined in the fields above then use these fields. The entry in this cell is for the moment of inertia of the ring about its neutral axis. For typical cross-sections this property can be calculated or “looked up” in a handbook that lists properties of steel shapes. An example of such a book would be the AISC steels handbook. Cross-Sectional Area of Stiffening Ring For the user defined ring enter the cross-sectional area of the ring in this field. This number can be calculated or “looked up” in a steels handbook.

15-8



Pop-Up Input Fields

Distance to Ring Centroid from Shell Surface Enter the distance from the outside surface of the shell to the centroid of the cross-section. The distance units are shown above. Height of Stiffener from Shell Surface If the stiffening ring is on the outside of the vessel then enter the distance from the outside shell surface to the top most part of the ring. If the ring is on the inside of the vessel then enter the distance from the inner surface of the shell to the top of the ring.


15-9



Discussion of Results PVElite will determine the volume of the vessel as well as the empty and full weights. These weights are computed with the vessel in the corroded condition. Knowing the weights may be useful for cost estimating and for design of supporting attachments, such as lifting lugs. The longitudinal stresses displayed in the output include the stress effects due to internal pressure. Since these are normal stresses they add together. The tension allowable is the basic operating allowable times the joint efficiency. The compressive allowable is the factor B taken from UG-23 using the materials chart for the given material. The tangential shear in the shell varies depending on whether the shell is stiffened or the head acts as a stiffener, or neither of these cases. Tangential stress in the head only exists if the head is close enough to the saddle to be used as a stiffener. The allowable stress in shear is 80% of the allowable tensile stress for the head or shell. The stress at the horn of the saddle depends on the location of the saddle and the equivalent thickness of the saddle and wear pad. It is zero if the shell is stiffened by rings. This stress is always compressive and the allowable stress is -1.5 times the allowable tensile stress. Use of the head as a stiffener creates additional tension stress in the head. The allowable additional stress in the vessel head is limited to 0.25 times the allowable tension stress in the head. If pressure is added, the resulting stress must be less than 1.25 times the allowable tensile stress. If the tip of the stiffening ring is in compression its allowable will be -0.5 times the yield stress. If a tensile condition exists the basic material allowable will be used.

15-10



Saddle Wear Plate Design

Saddle Wear Plate Design The horizontal vessels considered by PVElite are assumed to have saddle supports. One of the problems with this type of support is the high localized stresses which exist in the vessel in the region of saddles. Typically, the highest stress is the outside circumferential stress at the saddle horn. The ASME code does not address the details of saddle support design, nor does it offer guidance in the computation of the resulting vessel stresses. Instead, the code directs designers to other references for these methods. To date, the design of saddle supports and their associated stresses are based on past practice and experience, without theoretical analysis. A recent paper published in the Journal of Pressure Vessel Technology addresses the issue of local vessel stresses due to saddle supports. This paper (Effectiveness of Wear Plate at the Saddle Support, Ong Lin Seng, Transactions of the ASME, Journal of Pressure Vessel Technology, Vol 114, February 1992) provides a method for the estimation of the wear plate thickness, extension above the saddle horn, and the amount of stress reduction. (It is interesting to note that this paper suggests some of Zick’s recommendations are non-conservative.) This optimum thickness of the wear plate is a function of the mean radius of vessel, the thickness of vessel, and the width of wear plate. The optimum wear plate thicknesses is determined for both welded and non-welded conditions, with wear plate angular extensions of 5, 10, and 15 degrees. Restrictions of this Method

The restrictions of this method are •

The saddle angle must be greater than 120 degrees. Saddle angles of 120 degrees with an appropriate wear plate can result in a 15 to 40 percent stress reduction at horn of the saddle. Larger saddle angles cause a greater stress reduction for the same wear plate ratios.

•

The value of ( (r/b) * sqrt(r/t) ) must be between 10 and 60, when this term is not within this range, no thickness will be selected. (r = mean radius of the vessel, b = width of the wear plate, t = thickness of the vessel)

Conclusions

The conclusions drawn in this paper are •

The peak stress in the vessel at the saddle horn can be reduce from 15 to 40 percent when a wear plate is used if the wear plate has the same thickness as the vessel and extends at least 5 degrees above the saddle horn.

•

The peak stress in the vessel remains at the saddle horn when using a thin wear plate.

•

The stress reduction does not vary greatly with a variation in saddle support angle.


15-11


•


A welded wear plate reduces stresses better than a non-welded wear plate.

Figure 15A- Geometry for the Horizontal Vessel Module

15-12




Figure 15B - Wear Plate and Saddle Detail for a Typical Horizontal Tank


15-13

Example Problem


Example Problem FileName : CHECKS

------------------------------- Page 1

Horizves Analysis : C TEST

Input Echo, HORIZVES Number

ITEM:

1,

1,

02:36pm,

Description: C TEST


300.00

psig

Design Temperature

650.00

F

Corrosion Allowance for Vessel

Shell Material

.0000

in.

SA-516 70

Shell Operating Allowable Stress

17500.00

psi

Shell Ambient Allowable Stress

17500.00

psi

Head Material

SA-516 70

Head Operating Allowable Stress

17500.00

psi

Head Ambient Allowable Stress

17500.00

psi

Density of Shell and Head Material Liquid Height in Vessel Density of Stored Liquid Extra Weight

Baseplate Length

.2830 108.1180 62.4000

Baseplate Width

lb./cu.in in. lb./cu.ft

11225.000

lb.

60.0000

in.

.5000

in.

12.0000

in.

Baseplate Thickness

Number of Ribs ( inc. outside ribs )

5

Rib Thickness

.5000

in.

Web Thickness

.5000

in.

Web Location

Center

Height of Center Web

8.0000

in.

100.00

F

Design Temperature of Base Structure Saddle\Baseplate\Rib\Web Material

SA-516 70

Operating Allowable Stress

17500.00

psi

Ambient Allowable Stress

17500.00

psi

Use ASCE 7-95

No

Force Coefficient

.600

Extra Area

.0000 sq.in.

Importance Factor Wind Velocity Exposure Category Height above Grade Distance from Center of Vessel to Support

Seismic Loads Present

Diameter Basis for Vessel Shell Diameter Shell Length Tangent to Tangent Thickness of Shell

15-14

05/18/98

1.000 100.000

mile/hr

C 9.9167

ft.

64.0000

in.

N

OD 110.0000

in.

66.0000

ft.

.9410

in.



Example Problem

Shell Joint Efficiency

1.0000

Head Type

Elliptical

Head Thickness

.9290

Head Joint Efficiency

in.

1.0000

Distance from Saddle to Vessel Tangent

30.0000

in.

Saddle Width

10.0000

in.

Saddle Bearing Angle

120.0000

Wear Pad Thickness

degrees

.3750

in.

Wear Pad Extension above Horn of Saddle

10.0000

in.

Wear Pad Width

12.0000

in.

Stiffening Ring Present

N

Results for HORIZVES Number

Shell Allowable Stress

1,

Description: C TEST

used in Calculation

17500.00

psi

Shell Compressive Yield used in Calculation

38000.00

psi

Head Allowable Stress

used in Calculation

17500.00

psi

Ring Allowable Stress

used in Calculation

17500.00

psi

Volume of Vessel

32909.77

Gals.

Weight of Vessel, Empty

90584.07

lb.

365106.40

lb.

Weight of Vessel, Full

Required

Actual

Shell Thickness, Reqd. vs. Actual

.936

.941

in.

Head

Thickness, Reqd. vs. Actual

.929

.929

in.

Shell M.A.W.P. , Reqd. vs. Actual

300.00

301.47

psig

Head

300.00

300.15

psig

M.A.W.P. , Reqd. vs. Actual

Actual

Allowable

of Saddles

8776.65

17500.00

psi

Long. Stress at Bottom of Saddles

8337.89

17500.00

psi

Long. Stress at Top

of Midspan

5041.68

17500.00

psi

Long. Stress at Bottom of Midspan

12072.86

17500.00

psi

Long. Stress at Top

Tangential Shear in Shell

3743.68

14000.00

psi

Circ. Stress at Horn of Saddle

-8102.35

-26250.00

psi

Circ. Stress at Tip of Wear Plate

-6352.63

-26250.00

psi

Ring Compressive Stress in Shell

-9098.41

-19000.00

psi

WIND( ASCE #7 ) and SEISMIC RESULTS :

Transverse Wind Load Component Ft Ft = ( AFT * CF * GH * QZ ) * 0.5 Ft = ( 763.476 * .6000 * 1.3604 * 20.5030 ) * 0.5 Ft = 6388.6830 lb.

Saddle Reaction Force due to Wind Ft Fwt = 1.5 * Ft * B / E Fwt = 1.5 * 6388.7 * 64.0000 / 95.2628 Fwt = 6438.1230 lb.


15-15

Example Problem


Longitudinal Wind Load Component Fl Fl = ( AFL * CF * GH * QZ ) Fl = ( 91.892 * .6000 * 1.3604 * 20.5030 ) Fl = 1537.8800 lb.

Saddle Reaction Force due to Wind Fl Fwl = Fl * B / Ls Fwl = 1537.8800 * 64.0000 / 732.0000 Fwl = 134.4595 lb.

Load Combination Results for Q + Wind or Seismic Q = Wo/2 + Max( Fwl, Fwt, Fsl, Fst ) Q = 182553 + Max( 134, 6438, 0, 0 ) Q = 188991.3000 lb.

OPTIMUM WEAR PLATE THICKNESS RESULTS : Optimum Thickness ( Ext. = 5

WELDED

UNWELDED

deg. )

.9410

.9410

in.

Optimum Thickness ( Ext. = 10 deg. )

1.6468

1.6468

in.

Optimum Thickness ( Ext. = 15 deg. )

1.8820

2.3525

in.

FORMULAS and SUBSTITUTIONS for ZICK ANALYSIS RESULTS Shell and Head Required Thickness and MAWP :

TR = (P*D/2)/(S*E+0.4*P) per App. 1-1 (a)(1) : Shell TR = ( 300.00 * 110.0000 / 2.0 ) / ( 17500 * 1.00 + 0.4 * 300.00 ) + CA TR = .936 in.

MAWP = (S*E*(T-CA))/(D/2-0.4*(T-CA)) per App. 1-1 (a)(1) : Shell MAWP = ( 17500 * 1.00 * ( .9410 - .0000 )) / ( 110.0000 / 2 - 0.4 * ( .9410 - .0000 )) MAWP = 301.5 psig

TR = (P*D*K)/(2*S*E+2*P*(K-0.1)) per App. 1-4 (c) : Elli. Hd. TR = ( 300.00 * 110.0000 * 1.00 ) / ( 2 * 17500 * 1.00 + 2 * 300.00 * ( 1.00 - 0.1 )) + CA TR = .929 in.

MAWP = (2*S*E*(T-CA))/(K*D-2*(T-CA)*(K-0.1)) per App. 1-4 (d) Elli. Hd. MAWP = ( 2 * 17500 * 1.00 * ( .9290 - .0000 )) / ( 1.00 * 110.0000 - 2 * ( .9290 - .0000 ) * ( 1.00 - 0.1 )) MAWP = 300.2 psig

Longitudinal Bending (+-) at Midspan = ( 3 * Q * L * K.2 / ( PI * R^2 * ( TS - CA ))) = ( 3 * 188991 * 66.00 * .8116 ) / ( PI * 54.0590 * 54.0590 * ( .9410 - .0000 ))) = 3515.59 psi

Longitudinal Bending (+-) at Saddle = ( 3 * Q * L * K.1 / ( PI * R^2 * ( TS - CA ))) = ( 3 * 188991 * 66.00 * .0506 ) / ( PI * 54.0590 * 54.0590 * ( .9410 - .0000 )))

15-16



Example Problem

= 219.38 psi Tangential Shear in Shell near Saddle = Q * K.4 * (( L-H-2A )/( L+H ))/( R*(TS-CA)) = 188991 * 1.1707 * (( 66.00 - 2.25 - 2 * 2.50 )/ ( 66.00 + 2.25 ))/( 54.0590 * ( .9410 - .0000 )) = 3743.68 psi

Circumferential Stress at Tip of the Wear Plate = -Q/(4*(TS-CA)*(SADWTH+1.56*SQRT(R*(TS-CA))))-3.0*Q*K13/(2*(TS-CA)^2) = -188991 /( 4 * .9410 * ( 10.00 + 1.56*SQRT( 54.0590 * .9410 ))) -3 * 188991 * .0124 / ( 2 * .8855 ) = -6352.63 psi

Circumferential Stress at Horn of Saddle = -Q /(4*TEM*(SADWTH+1.56*SQRT(R*(TS-CA))))-3.0*Q*K.7/(2*TEB) = -188991 /( 4 * .9410 * ( 10.00 + 1.56*SQRT( 54.0590 * .9410 ))) -3 * 188991 * .0179 / ( 2 * .8855 ) = -8102.35 psi

Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9 * WPDWTH ) ) ) = ( 188991 *( .7603/( 1.3160 * 12.000 ) ) ) = -9098.41 psi

Longitudinal Pressure Stress = DP*((SID/2+CA)-0.4*(TS-CA))/(2.0*(TS-CA)) = 300.0 * (( 108.12 / 2 + .0000 - 0.4 * ( .941 - .0000 )) / ( 2.0 * ( .941 - .0000 )) = 8557.27 psi

RESULTS for VESSEL RIBS, WEB and BASE

Moment of Inertia of Saddle - Lateral Direction

Y Shell

A

AY

Ay^2

21.7619

Wearplate

1.1285

4.5000

5.0782

5.7308

.0527

Web

4.4080

3.0920

13.6295

60.0790

9.8537

7.7500

6.0000

46.5000

360.3750

.1250

13.7570

35.3539

75.4468

431.0023

11.6372

BasePlate Totals

Value Value Value

C1 = äAy/äA

10.2390

Io

.4705

=

2.1340

I = äAy^2 + äIo - C1*äAy =

281.6328

As = äA - Ashell

=

13.5920

4.8174

in. in**4 sq.in.

K1 = (1+Cos(á)-.5*Sin(á)^2 )/(ã-á+Sin(á)*Cos(á)) =

Fh = ( K1 * Q ) =

38463.8400

.2035

lb.

Tension Str., St = ( 2.0 * Fh/As )

=

5659.7770

psi

Allowed Str., Sa = .6 * Yield Stress =

22800.0000

psi

Bending Mom., M


= ( 2.0 * Fh*d

1.6058

)

=

111241.1000

ft.lb.

15-17

Example Problem


Bending Str., Sb = ( M * C1 / I

)

Allowed Str., Sa = .66 * Yield Str.

=

10115.0100

psi

=

25080.0000

psi

Minimum Thickness of Baseplate Baseplate Min., = (3*Q*F/(4*A*SA))^.5 =

1.0632

in.

** LOW **

Calc. of Axial Load, Inter. Values and Comp. Stress

e

= ( BPLEN - 1 ) / ( NRIBS - 1)

e

= ( 60.0000 - 1 ) / ( 5 - 1 ) = 14.7500 in.

AP = e * BPWID / 2 AP = 14.7500 * 12.0000 / 2 = 88.5000 sq.in.

P

= AP * BP

P

= 88.5000 * 262.4880 = 23230.1900 lb.

AR = ( BPWID - 1 - WEBTK ) * RIBTK + e/2 * WEBTK AR = ( 12.000 - 1 - .500 ) * .500 + 14.7500/2 * .500 = 8.938 sq.in.

SC = P/AR SC = 23230.1900 / 8.9375 = 2599.1820 psi

Check of Outside Ribs Inertia of Saddle, Outer Ribs - Axial Direction Y

A

AY

Ay^2

Io

Rib

5.0000

5.2500

26.2500

.0000

41.6615

Web

5.0000

3.6875

18.4375

.0000

.1536

Values

5.0000

8.9375

44.6875

.0000

41.8151

KL/R < Cc ( 15.9773 < 122.7360 ) per AISC 1.5.1.3 Sca = (1-(Klr)^2/(2*Cc^2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr^3)/(8*Cc^3) Sca = ( 1-( 15.98 )^2/(2 * 122.74^2 )) * 29000000 / ( 5/3+3*( 15.98)/(8* 122.74)-( 15.98^3)/(8* 122.74^3) Sca = 21967.05 psi

AISC Unity Check on Outside Ribs ( must be ó 1.0 ) Check = Sc/Sca + Sb/Sba Check = 2599.18 / 21967.05 + 40.98 / 25080.00 Check = .12

Check of Inside Ribs Inertia of Saddle, Inner Ribs - Axial Direction Y Rib

5.5000

Web Values

A

AY

Ay^2

Io

5.2500

28.8750

.0000

55.4531

5.5000

7.3750

40.5625

.0000

.1536

5.5000

12.6250

69.4375

.0000

55.6068

KL/R < Cc ( 4.1381 < 122.7360 ) per AISC 1.5.1.3 Sca = (1-(Klr)^2/(2*Cc^2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr^3)/(8*Cc^3) Sca = ( 1-( 4.14 )^2/(2 * 122.74^2 )) * 29000000 / ( 5/3+3*( 4.14)/(8* 122.74)-( 4.14^3)/(8* 122.74^3) Sca = 22615.54 psi

15-18



Example Problem

AISC Unity Check on Inside Ribs ( must be ó 1.0 ) Check = Sc/Sca + Sb/Sba Check = 3680.03 / 22615.54 + 14.20 / 25080.00 Check = .16



15-19

Example Problem

15-20




&KDSWHU The TEMA Tubesheet Module

Introduction The PVElite TEMA Tubesheet Module performs tubesheet thickness analysis for all tubesheet types, including fixed tubesheet exchangers, based on the Standards of the Tubular Exchanger Manufacturer’s Association, 8th Edition, 2001.

Purpose, Scope, and Technical Basis The PVElite TEMA Tubesheet Module calculates required thickness and Maximum Allowable Working Pressure of tubesheets for all of the exchanger types described in the Seventh Edition of the Standards of the Tubular Exchanger Manufacturers Association (TEMA). It also calculates thermal stresses and forces in the shell and tubes of fixed tubesheet exchangers. The calculations are taken from paragraphs 7.11 through 7.25. This module will analyze the following tubesheet types: •

Stationary tubesheets, gasketed between the shell and the channel.

•

Stationary tubesheets, integral with the shell and the channel.

•

Stationary tubesheets, integral with the shell only.

•

Stationary tubesheets, integral with the channel only.

•

U-tube exchangers, tubesheet gasketed between shell and channel

•

U-tube exchangers, tubesheet integral with channel only.

•

Floating tubesheets, outside packed floating head (P).

•

Floating tubesheets, floating head with backing device (S).

•

Floating tubesheets, pull through floating head (T).

•

Floating tubesheets, externally sealed floating head (W).

•

Floating tubesheets, divided floating head.

•

Fixed tubesheets, stationary at both ends.

The module does the required calculations for the thickness of a tubesheet (stationary or U-tube) which has been extended as a flange. It also calculates the required thickness of the extension. The user must enter the geometry of the flange extension, including the gasket and bolting for the flange. The TEMA Tubesheet module takes into account the following additional loadings for fixed tubesheet exchangers:

The TEMA Tubesheet Module

16-1



•

Expansion joints - thin walled, thick walled, or none.

•

Tubesheets - integral, gasketed, or extended as flanges.

•

Pressure and thermal loads - on shell, tubesheet, tubes and tube-to-tubesheet joints.

•

Differential pressure designs.

The TEMA Tubesheet module calculates required thicknesses in the corroded condition. Occasionally the tubesheet thickness will be governed by the uncorroded condition, so a case with shellside and tubeside corrosion allowances set to zero should be analyzed for most exchangers. Figures 16A, 16B and 16C show geometry for the TEMA Tubesheet Module

Figure 16A - Geometry for the TEMA Tubesheet Module

16-2




Figure 16B - Geometry for the TEMA Tubesheet Module


16-3



Figure 16C - Geometry for the TEMA Tubesheet Module

16-4




Discussion of Input Data Main Input Fields Shell Design Pressure

Enter the design pressure for the shell side of the exchanger. If the shell side has external pressure, enter a negative pressure. The program will correctly combine this pressure with the positive pressure on the other side. Note that if you specify a differential pressure in the differential pressure input field, the values on the shellside and tubeside will usually be ignored. The exception to this is fixed tubesheet exchangers, where the differential pressure field only serves as a flag to indicate to the program that the appropriate calculations for differential pressure should be performed. Shell Metal Design Temperature

Enter the design metal temperature for the shell side components. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Shell\Channel\Tube\Tube Sheet Material Specification

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Allowable Stress, Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the ambient temperature. Shell Wall Thickness

Enter the minimum wall thickness for the shell of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheets, and especially in calculating longitudinal shell stresses for fixed tubesheet exchangers.


16-5



Shell Corrosion Allowance

Enter the shell side corrosion allowance for the exchanger. This value is used to calculated the corroded thickness of the shell and the corroded thickness of the tubesheet. Shell Inside Diameter

Enter the inside diameter for the shell of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheets, and especially in calculating longitudinal shell stresses for fixed tubesheet exchangers. Channel Design Pressure

Enter the design pressure for the tube side of the exchanger. If the tube side has a vacuum design condition, enter a negative pressure. The program will correctly combine this pressure with the positive pressure on the other side. Note that if you specify a differential pressure in the differential pressure input field, the values on the shellside and tubeside will usually be ignored. The exception to this is fixed tubesheet exchangers, where the differential pressure field only serves as a flag to indicate to the program that the appropriate calculations for differential pressure should be performed. Channel Metal Design Temperature

Enter the design metal temperature for the tube side components. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Channel Wall Thickness

Enter the minimum wall thickness for the channel of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheet types. Channel Corrosion Allowance

Enter the tube side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the channel and the corroded thickness of the tubesheet. Channel Inside Diameter

Enter the inside diameter for the channel of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheets. Tubesheet Type

The program analyzes the following tubesheet types: A B C N U V P S

16-6

Stationary tubesheets, gasketed on both sides. Stationary tubesheets, integral with the shell. Stationary tubesheets, integral with the channel. Stationary tubesheets, integral on both sides. U-tube tubesheets gasketed on both sides U-tube tubesheets integral with the channel. U-tube tubesheets integral with the shell. Floating tubesheets, outside packed floating head. Floating tubesheets, head with backing device.




T W D F

Floating tubesheets, pull through floating head. Floating head, externally sealed floating tubesheet. Divided floating tubesheet. Fixed tubesheet exchanger - two stationary tubesheets.

Tube Outside Diameter

Enter the outside diameter of the tubes. This is usually an exact fraction, such as .5, .75, .875, 1.0, or 1.25. The tube diameter, pitch, and pattern are used to calculate the term ‘eta’ in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. Tube Corrosion Allowance

Enter the tube corrosion allowance. Tube Pitch (Distance Between Tube Centers)

Enter the tube pitch, the distance between the tube centers. The tube diameter, pitch, and pattern are used to calculate the term ‘eta’ in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. Tube Pattern (Triangular, Square)

Enter the pattern of the tube layout. The tube diameter, pitch, and pattern are used to calculate the term ‘eta’ in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. Are Tubes Attached by a Groove or Fillet Weld?

Check this field if the tubes are joined to the tubesheet by a fillet or groove weld. Do not check this field if the tubes are not welded to the tubesheet. Perimeter of Tube Layout (if Needed)

Enter the length of a path around the outside edge of the tube layout. This can be calculated by counting the number of tubes on the outside of the layout and multiplying by the tube pitch. When a tubesheet may be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. You will see an error message when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. Area of Tube Layout

Enter the area enclosed by a path around the outside edge of the tube layout. When a tubesheet may be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. You will see an error message when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. Differential Design Pressure (Used if > 0.0)

Enter the differential design pressure if you wish the program to use the differential design rules. The differential pressure is used as the design pressure on both the tubeside and the


16-7



shellside, except for fixed tubesheet exchangers. In this case any number greater than zero serves as a flag to tell the program to turn on the special differential design pressure rules for fixed tubesheets. You must enter the shell side and tube side design pressures for fixed tubesheet exchangers. Depth of Groove in Tubesheet

If the tubesheet has a groove, enter its depth here. This value is used as a candidate when finalizing the required thickness of the tubesheet. The maximum of this value or the channel corrosion allowance plus the shellside corrosion allowance will be added to the computed required tubesheet thickness. If your tubesheet is not grooved, enter a 0 in this field. Tubesheet Thickness

Enter the thickness of the tubesheet, or a reasonable guess at the thickness if the actual thickness is unknown. This thickness should include any allowances for corrosion on the shell side or the tube side. The tubesheet thickness for fixed tubesheet exchangers is also used in the equivalent thermal pressure calculation. When you have finished your design you should come back and put the actual thickness into this field and make sure the required thickness doesn’t change. Tubesheet Corrosion Allowance Shell Side

Enter the tubesheet corrosion allowance for the shell side. This value is combined with the tubesheet corrosion allowance shell side to calculate the corroded thickness of the tubesheet. Tubesheet Corrosion Allowance Channel Side

Enter the tubesheet corrosion allowance for the channel side. his value is combined with the tubesheet corrosion allowance channel side to calculate the corroded thickness of the tubesheet. Tubesheet Metal Design Temperature

Enter the design metal temperature for the tubesheet. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Tubesheet Extended as Flange?

Check this field if the tubesheet is extended and used as a bolted flange. Do not check this field unless the tubesheet actually sees bending moments the bolting. If the tubesheet is bolted between a pair of flanges, the tubesheet itself will not experience a bending moment. It is only when the tubesheet replaces one of the flanges that a moment develops. Tubesheet Gasket (None, Shell, Channel, Both)

Enter the kind of gasketing associated with this tubesheet. If the tubesheet has a circular gasket, even if the gasket is not extended as a flange, you must enter the details of the gasketing, so that the program can correctly evaluate the mean diameter of the gasket load reaction (G).

16-8




Actual Shell Metal Temperature

Enter the actual metal temperature for the shell under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Don’t forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. Actual Tube Metal Temperature

Enter the actual metal temperature for the tubes under a realistic operating condition. It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Don’t forget to evaluate the condition of shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design. Actual TEMA Tubesheets Metal Temperature

Enter the actual metal temperature for the tubesheet under a realistic operating condition. This value does not affect the thermal expansion design, but it is used to determine the elastic modulus of the tubesheet. Number of Tubes

Enter the number of tubes in the tubesheet. This value is used to determine the total tube area and stiffness. Length of Tubes

Enter the overall length of the tubes, the length from the inside face of one tubesheet to the inside face of the other tubesheet. This value is used to determine the thermal expansion of the tubes.


16-9



Tube Wall Thickness

Enter the wall thickness of the tubes. This value is used to determine the total tube area and stiffness. The following table gives thicknesses for some common tube gauges: BWG Gauge

Thickness (inches)

BWG Gauge

Thickness (inches)

7

.180

17

.058

8

.165

18

.049

10

.134

19

.042

11

.120

20

.035

12

.109

22

.028

13

.095

24

.022

14

.083

26

.018

15

.072

27

.016

16

.065

Tube Material Specification

Enter the ASME code material specification as it appears in the PVElite Appendix (Chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Fillet or Groove Weld Leg Length

If the tubes on your exchanger are welded to the tubesheet, then enter the fillet weld or groove weld leg length. Some designs incorporate either only a groove or fillet weld, sometimes both are used. These values are used to determine the weld strengths. PVElite will determine will determine the minimum required weld sizes afm and agm. Refer to paragraph UW-20 in the ASME Code for more details. ASME Tube Joint Reliability Factor

The ASME Code tube joint reliability factor is found in the ASME Code, Section VIII, Division 1, Table A-2, and is used to calculate the allowable tube-to-tubesheet joint loads. A typical value for tubes rolled into two grooves is 0.70. Corroded Expansion Joint Spring Rate

If there is no expansion joint, enter a zero (0.0). If there is a thin walled expansion joint, enter a one (1.0). If there is a thick walled expansion joint, enter the actual spring constant for the joint. The expansion joint spring rate should be calculated using the PVElite THICKJNT program, the rules in TEMA RCB-8, or a similar analysis technique.

16-10




Uncorroded Expansion Joint Spring Rate

If there is no expansion joint, enter a zero (0.0). If there is a thin walled expansion joint, enter a one (1.0). If there is a thick walled expansion joint, enter the actual spring constant for the joint. The expansion joint spring rate should be calculated using the PVElite THICKJNT program, the rules in TEMA RCB-8, or a similar analysis technique. The spring rate reported from the THICKJNT program is reported in units of pounds per inch. As of version 4.1 of PVElite, different inputs for the uncorroded and corroded spring rates will be reported, these will be used for running the multiple load cases in uncorroded and corroded condition. Expansion Joint Inside Diameter

Enter the inside diameter of the outer annular plate. This value is used by the program to calculate the force on the cylinder, and thus the equivalent pressure of thermal expansion. Enter the Unsupported Tube Span, SL for Max (k*SL)

For computing the allowable tube compression, the values of K and SL are required. Where, SL: Unsupported Span of the tube k:

Tube end condition corresponding to the span SL. Here are the different values of k:

k

Condition

0.6

For unsupported spans between two tubesheets.

0.8

For unsupported spans between a tubesheet and a tube support.

1.0

For unsupported spans between two tube supports.

For the worst case scenario enter the values of K and SL, that give a maximum combination of k*SL. SL for example, could be the distance between the tubesheet and the first baffle or the tube span between two support baffles.


16-11



Enter the Tube End Condition k, Corresponding to Span SL

For computing the allowable tube compression, the values of K and SL are required. Where, SL: Unsupported Span of the tube k:

Tube end condition corresponding to the span SL. Here are the different values of k:

For the worst case scenario enter the values of K and SL, that give a maximum combination of k*SL. See above for possible values of k. Is this a Kettle Type Heat Exchanger ?

Check here if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Length of Kettle Port Cylinder (LP)

Enter the length of the Kettle port cyclinder. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Thickness of Kettle Port Cylinder (TP)

Enter the thickness of the Kettle port cyclinder. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Mean Diameter of Kettle Port Cylinder (DP)

Enter the mean diameter of the Kettle port cylinder. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Length of Kettle Cylinder

Enter the length of the Kettle cylinder. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Thickness of Kettle Cylinder

Enter the thickness of the Kettle cylinder. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Mean Diameter of Kettle Cylinder

Enter the mean diameter of the Kettle cylinder. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Axial Length of Kettle Cone (LC)

Enter the axial length of the Kettle cone. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition.

16-12




Thickness of Kettle Cone (KC)

Enter the thickness of the Kettle cone. This dimension is needed if the shell is shaped like a kettle. The kettle-type configuration is illustrated in Figure N-1.2 and Figure N-2 in the TEMA Standard Eighth Edition. Run Multiple Load Cases for Fixed Tubesheet ?

Check this box if you want to run multiple load cases for the tubesheet design, per the TEMA standard.

Load Case #

Load Case Description Corroded

Uncorroded

1

Fvs + Pt - Th + Ca

Fvs + Pt - Th - Ca

2

Ps + Fvt - Th + Ca

Ps + Fvt - Th - Ca

3

Ps + Pt - Th + Ca

Ps + Pt - Th - Ca

4

Fvs + Fvt + Th + Ca

Fvs + Fvt + Th - Ca

5

Fvs + Pt + Th + Ca

Fvs + Pt + Th - Ca

6

Ps + Fvt + Th + Ca

Ps + Fvt + Th - Ca

7

Ps + Pt + Th + Ca

Ps + Pt + Th - Ca

8

Fvs + Fvt - Th + Ca

Fvs + Fvt - Th - Ca

Note: Fts, Fvs - User-defined shell side and tube side vacuum pressures or 0.0. Ps, Pt

- Shell side and tube side design pressures.

Th

- With or without thermal expansion.

Ca

- With or without corrosion allowance.

Enter the Shell/Channel Side Vacuum Pressures

When analyzing the design with the multiple load cases, the user can specify shell/channel side vacuum pressures. This should be a positive entry. For example, for full atmospheric vacuum conditions enter a value of 15.0 psig. If no value is specified then 0 psi is used. Select Load Cases for Detailed Printout

When analyzing the design with the multiple load cases, the program will generate summarized results for all the load cases in tabular form. To see the detailed equations and intermediate calculations for any load cases, select that load case. Outside Diameter of Flanged Portion

Enter the outer diameter of the flange. This value is referred to as “A” in the ASME code.


16-13




Enter the diameter of the bolt circle of the flange. Thickness of Extended Portion of Tubesheet

Enter the flange thickness. This thickness will used in the calculation of the required thickness. The final results should, therefore, agree with this thickness to within about five percent. Nominal Bolt Diameter

Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. If you have bolts that are larger or smaller than this value, enter the nominal size in this field, and also enter the root area of one bolt in the “Thread Series” cell. Thread Series

There are three options for this entry: 1 - TEMA Bolt Table 2 - UNC Bolt Table 3 - User specified root area of a single bolt Bolt Root Area (Used if > 0)

If you exchanger design has non-standard bolts, enter a 3 in the field above this one and enter the root area of a single bolt in this field. Number of Bolts

Enter the number of bolts to be used in the flange analysis. Fillet Weld Between Flange and Shell/Channel

Enter the fillet weld height between the tubesheet flange and the shell or channel outside surface. pvelite will use this number to calculate g1 ( the hub thickness at the large end). Operating Bolt Load ?

Specify the alternate operating bolt load on the tubesheet extended as a flange. This value will be used if it is greater than the operating bolt load computed by the program. Seating Bolt Load ?

Specify the alternate seating bolt load on the tubesheet extended as a flange. This value will be used if it is greater than the seating bolt load computed by the program. Flange Design Bolt Load ?

Specify the alternate flange design bolt load on the tubesheet extended as a flange. This value will be used if it is greater than the flange design bolt load computed by the program. Flange Face Outer Diameter

Enter the outer diameter of the flange face. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. The program uses

16-14




the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Flange Face Inner Diameter

Enter the inner diameter of the flange face. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. Flange Face Facing Sketch

Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations:

Facing Sketch

PVEliteEquivalent

1a

1

flat finish faces

1b

2

serrated finish faces

1c

3

raised nubbin-flat finish

1d

4

raised nubbin-serrated finish

2

5

1/64 inch nubbin

3

6

1/64 inch nubbin both sides

4

7

large serrations, one side

5

8

large serrations, both sides

6

9


Description

Gasket Outer Diameter

Enter the outer diameter of the gasket. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Gasket Inner Diameter

Enter the inner diameter of the gasket. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. For gasket properties, refer to the table in Chapter 12, The Flange Module. Gasket Thickness

Enter the gasket thickness. This value is only required for facing sketches 1c and 1d (PVElite equivalents 3 and 4). Nubbin Width

If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6 (PVElite equivalents 3, 4, 5, and 9). Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring.


16-15




This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. If the pass partition gaskets are a different width than the main gasket, scale the length you enter so that the area of the gasket is correct. Width of Partition Gasket

Enter the width of the pass partition gasket. The gasket properties such as the facing sketch, column, M and Y will be taken from the main gasket. Using these properties and the known width, PVElite will compute the effective seating width and compute the gasket loads contributed by the partition gasket. Intermediate Calculations for Tubesheets Extended as Flanges

Two major additions to the tubesheet calculation occur when a tubesheet is extended as a flange. First, a moment is added to the pressure moment which governs the thickness of most tubesheets. Second, a moment exists on the portion of the tubesheet which serves as the flange, and the effects of this moment must be evaluation. The TEMA standard requires that these conditions be evaluated using the rules in the ASME code, appendix 2. Those rules, in turn, require the complete evaluation of bending moments on the flange. It is those bending moment calculations which are reflected in this section of the output. These calculations represent the basic bolt loading for the flanged portion of the tubesheet, and will be the same for the mating flange. The actual bending moments may change when compared to the mating flange. The flanged extension of the tubesheet is calculated as a ring type flange. Since no stresses are shown, you need to check the adequacy of the bolting by comparing the required to actual area. The bolt spacing correction factor is automatically included in the bending moment, such that the moment is the force times the distance times the bolt correction. Geometric Constants, Pressure and Thickness Calculations

The tube diameter, pitch, and pattern are used to calculate the term ‘eta’ in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. When a tubesheet may be controlled by shear stress, the program requires the perimeter and area of the tubesheet for the shear calculation. You will see an error message when these values are required but not given. The result will be conservative if you overestimate the area and underestimate the perimeter. The G dimension is calculated based on the exchanger type and either the diameter of the pressure component or the mean diameter of the gasket. Similarly, the F dimension is calculated based on the exchanger type and the type of connection to the shell and channel. These calculations are based on Table RCB-7.132 and Table RCB-7.133. Differential Expansion Pressure

The program contains tables of Young’s modulus and coefficient of thermal expansion. It selects these values from the tables based on the materials classification you enter on the material editing screen of the input spreadsheet. You should make sure that the program has selected the right identification number for the material. You should also check the values to make sure that they agree with your expectations. A good place to find this data, and the source of these tables in the program, is the TEMA Standard, tables D-10 and D-

16-16




11. The following list shows the program identification numbers for the materials in this standard: Chart Number

Cross Reference to Elastic Chart

1

3

B31.3:

Carbon Steel

2

4

B31.3:

5Cr-9Cr

3

5

B31.3:

12,17,27Cr

4

6

B31.3:

18Cr-8Ni

5

6

B31.3:

25Cr20Ni

6

8

B31.3:

67Ni30Cu

7

1

B31.3:

3.5Ni

8

10

B31.3:

Aluminum

9

7

B31.3:

Cast Iron

10

13

B31.3:

Bronze

11

12

B31.3:

Brass

12

9

B31.3:

70Cu-30Ni

13

6

B31.3:

Ni-Fe-Cr

14

6

B31.3:

Ni-Cr-Fe

15

7

B31.3:

Ductile Iron

16

14

TEMA:

Plain Carbon Stl & C-Mn Stl.

17

14

TEMA:

C-SI, C-1/2Mo & Cr-1/2Mo

18

16

TEMA:

C-Mn-Si, 1-1/4Cr-1/2Mo

19

14

TEMA:

Mn-Mo

20

20

TEMA:

2-1/2 & 3-1/2 Ni

21

17

TEMA:

2-1/4Cr-1Mo

22

18

TEMA:

5Cr-1/2Mo

23

18

TEMA:

7Cr-1/2Mo & 9Cr-1Mo

24

19

TEMA:

12Cr & 13Cr

25

19

TEMA:

15Cr & 17Cr

26

15

TEMA:

TP316 & TP317

27

15

TEMA:

TP304

28

15

TEMA:

TP321

29

15

TEMA:

TP347

30

15

TEMA:

25Cr-12Ni, 23Cr-12Ni,


Chart Name

16-17



31

23

TEMA:

Aluminum 3003

32

23

TEMA:

Aluminum 6061

33

32

TEMA:

Titanium, Grades 1,2,3,7

34

21

TEMA:

Ni-Cu (Alloy 400

35

24

TEMA:

Ni-Cr-Fe (Alloy 600)

36

25

TEMA:

Ni-Fe-Cr (Alloy 800 & 800H)

37

35

TEMA:

Ni-Fe-Cr-Mo-Cu (Alloy 825)

38

34

TEMA:

Ni-Mo (Alloy B)

39

27

TEMA:

Ni-Mo-Cr (Alloy C-276)

40

28

TEMA:

Nickel (Alloy 200)

41

33

TEMA:

70-30 Cu-Ni

42

22

TEMA:

90-10 & 80-20 Cu-Ni

43

29

TEMA:

Copper

44

30

TEMA:

Brass

45

29

TEMA:

Aluminum Bronze

46

29

TEMA:

Copper-Silicon

47

31

TEMA:

Admiralty

48

37

TEMA:

Zirconium

49

15

TEMA:

Cr-Ni-Fe-Mo-Cu-Cb

50

38

TEMA:

Ni-Cr-Mo-Cb (Alloy 625)

When a fixed tubesheet is analyzed, the following calculation procedure is followed: 1. Calculate G, F, and ETA per RCB-7.132 and RCB-7.133 2. Calculate equivalent differential expansion pressure per RCB-7.161 3. Calculate equivalent bolting pressure per RCB-7.162 4. Calculate effective shell side design pressure per RCB-7.163 5. Calculate effective tube side design pressure per RCB-7.164 6. Calculate required thickness per RCB-7.132 or RCB-7.133 7. Calculate shell longitudinal stress per RCB-7.22 8. Calculate tube longitudinal stress per RCB-7.23 9. Calculate allowable tube compressive stress per RCB-7.24 10. Calculate tube to tubesheet joint loads per RCB-7.25

16-18



Example Problems

Example Problems Example problem 1 is a comparison problem for a fixed tubesheet exchanger that has a thick walled metal bellows expansion joint. The results compare very well to the other exchanger program. There are several additional example problems contained in the files TEXAMPLE. FileName : CHECKS

--------------------------------- Page

Tubesheet Analysis: COMPARISON

INPUT ECHO, TUBESHEET NUMBER

ITEM:

1,

1,

1

02:56pm, 12/14/2000

Description: COMPARISON

Shell Design Pressure Shell Temperature for Internal Pressure

PS

50.00

TEMPS

649.00

Shell Material

psig F

SA-240 304H

Shell Allowable Stress at Temperature

SOS

15900.00

psi

Shell Allowable Stress at Ambient

SAS

18800.00

psi

Shell Thickness

TS

0.2500


CAS

0.0000

Inside Diameter of Shell

DS

Channel Design Pressure Channel Temperature for Internal Pressure

112.0000

PC

50.00

TEMPC

649.00

Channel Material

in. in. in.

psig F

SA-240 304H

Channel Allowable Stress at Temperature

SOC

15900.00

psi

Channel Allowable Stress at Ambient

SAC

18800.00

psi

Channel Thickness

TC

Channel Corrosion Allowance

in.

CAC

0.0000

in.

DC

112.0000

in.

Inside Diameter of Channel

TUBESHEET TYPE:

0.2500

Fixed Tubesheet Exchanger


DT

Tube Pitch (Center to Center Spacing)

PT

Tube Layout Pattern

0.7500 1.3500

Triangular

Fillet Weld Leg at Back of Tube

af

0.0000

Groove Weld Leg at Back of Tube

ag

0.0000

Tubesheet Design Metal Temperature

TEMPTS

Tubesheet Material Specification

649.00

in. in. F

SA-240 304H

Tubesheet Allowable Stress at Temperature

SOTS

15900.00

psi

Tubesheet Allowable Stress at Ambient

SATS

18800.00

psi

TTS

2.5625

in. in.

Thickness of Tubesheet

in. in.

Tubesheet Corr. Allowance (Shell side)

CATS

0.000

Tubesheet Corr. Allowance (Chanel side)

CATC

0.000

Depth of Groove in Tube Sheet

GROOVE

in. 0.0000

in.

ADDITIONAL DATA FOR FIXED TUBESHEET EXCHANGERS Actual Metal Temperature for Shell

ACTUAL1

156.00

F

Actual Metal Temperature for Tubes

ACTUAL2

226.00

F

Actual Metal Temperature for Tubesheet

ACTUAL3

233.00

F

Number of Tubes

TNUMT

3100

Length of Tubes

TLENT

Tube Material Tube Allowable Stress at Temperature


152.2500

in.

SS304-WLD-HI SOT

13500.00

psi

16-19

Example Problems


Tube Allowable Stress At Ambient

SAT

16000.00

psi

Tube Yield Stress At Operating Temperature

SYT

18008.00

psi

Tube Wall Thickness

TT

Tube Corrosion Allowance

0.0490

Tbca

ASME Tube Joint Reliability Factor

0.0000

FASME

in. in.

0.7000

Expansion Joint Spring Rate (Corroded)

SJF

49250.00

lbs./in.

Expansion Joint Spring Rate (New and Cold)

Sjnc

49250.00

lbs./in.

Expansion Joint Inside Diameter at Bellows

DJ

117.7500

in.

k

1.0000

in.

Unsupported Tube Length for max. (k*SL) Tube end condition corres. to span (SL)

SL

Run Multiple Load Cases for Fixed Tubesheets Shell side Vacuum Pressure

in.

Yes PEXTS

Chanel side Vacuum Pressure

50.0000

0.0000

PEXTC

Is this a Kettle - type configuration

psi

0.0000

psi

No

ADDITIONAL DATA FOR TUBESHEETS EXTENDED AS FLANGES: Outside Diameter of Flanged Portion

DF

116.2500

in.


DB

114.7500

in.

Thickness of Extended Portion of Tubesheet

TF

5.1250

in.

DBOLT

.6250

in.

Nominal Bolt Diameter Type of Threads

( Thread Series )

Number of Bolts

TEMA Thread Series NUMBER

Bolt Material

176 SA-193 B7


SBO

25000.00

psi


SBA

25000.00

psi

Weld between Flange and Shell/Channel

WLDH

0.0000

in.

ADDITIONAL DATA FOR GASKETED TUBESHEETS: Flange Face Outside Diameter

FOD

113.6250

in.


FID

112.6250

in.


1, Code Sketch 1a


GOD

113.6250

in.


GID

112.6250

in.

Gasket Factor, m,

M

Gasket Design Seating Stress Column for Gasket Seating

3.7500 Y

10000.00

psi

2, Code Column II

Tubesheet Gasket on which Side

SIDE

CHANNEL

INTERMEDIATE CALCULATIONS FOR TUBESHEETS EXTENDED AS FLANGES:


RN = (GOD-GID)/2

Basic Gasket Width,

B0 = RN / 2.0

.250


BE = B0

.250

Gasket Reaction Diameter, G = (GOD+GID) / 2.0

.500

113.125

in. in. in. in.

BASIC FLANGE AND BOLT LOADS: Hydrostatic End Load due to Pressure: H = PI/4 * G * G * PEQ H = ( .7854 * 113.1250 * 113.1250 * 50.0000 ) H = 502547. lb. Contact Load on Gasket Surfaces: HP = 2.0 * BE * PI * G * GM * PEQ HP = 2.0 * 3.1416 * .2500 * 113.1250 * 3.7500 * 50.00 HP = 33318. lb.

16-20



Example Problems

Hydrostatic End Load at Flange ID: HD = PI * B * B * PEQ

/ 4.0

HD = 3.1416 * 112.0000 * 112.0000 * 50.0000 / 4.0 HD = 492602. lb. Pressure Force on Flange Face: HT = H - HD HT = 502547 - 492601 HT = 9946. lb. Operating Bolt Load: WM1 = H + HP +

HPP

WM1 = ( 502547 + 33318 + 0 ) WM1 = 535866. lb. Gasket Seating Bolt Load: WM2 = GY * (( BE * PI * G ) + (BEPG * GLPG) ) WM2 = 10000.00 * (( .2500 * 3.141 * 113.125 ) + ( .00 * .0000 )) WM2 = 888482. lb. Required Bolt Area: AM = Maximum of WM1/ABSTR, WM2/ABASTR AM = Maximum of 535865 / 25000 , 888481 / 25000 AM = 35.5393 sq. in.

Bolting Information for TEMA Thread Series: Total Area of Bolts Minimum radial distance between hub and

35.552

sq.in.

bolts

.938

in.


.750

in.

Minimum circumferential spacing between

bolts

1.500

in.

Actual

circumferential spacing between

bolts

2.048

in.

Maximum circumferential spacing between

bolts

8.485

in.

Flange Design Bolt Load: W = ABASTR * ( AM + AB ) / 2.0 W = 25000 * ( 35.5393 + 35.5520 ) / 2.0 W = 888640.88 lb. Gasket Seating Force: HG = WM1 - H HG = 535865 - 502547 HG = 33318.09 lb.

Distance to Gasket Load Reaction: DHG = (DBCRL - G ) / 2.0 DHG = ( 114.7500 - 113.1250 ) / 2.0 DHG = .8125 in. Distance to Face Pressure Reaction: DHT = ( R + GONE + DHG ) / 2.0 DHT = ( 1.1250 + .2500 + .8125 ) / 2.0 DHT = 1.0938 in. Distance to End Pressure Reaction: DHD = R + GONE / 2.0 DHD = 1.1250 + .2500 / 2.0 DHD = 1.2500 in.


16-21

Example Problems



Force

Distance

Bolt Corr

Moment

End Pressure,

Md

492602.

1.2500

1.0000

Face Pressure,

Mt

9946.

1.0938

1.0000

907. ft.lb.

Gasket Load,

Mg

33318.

.8125

1.0000

2256. ft.lb.

Gasket Seating, Ma

888641.

.8125

1.0000

60169. ft.lb.

TUBESHEET ANALYSIS, TUBESHEET NUMBER

1,

51313. ft.lb.

Description: COMPARISON

TEMA Standards, Seventh Edition, 1988, RCB-7, Tubesheets

Shellside Fixity Factor, F,

per RCB 7.132

FS

1.0000

Shellside Effective Diameter,per RCB 7.132

GS

112.0000

Tubeside

Fixity Factor, F,

per RCB 7.132 FC

Tubeside Effective Diameter, per RCB 7.132 GC TEMA Eta factor used in calculation

in.

1.0000 112.0000 ETA

in.

.7201

MATERIAL PROPERTIES FOR THERMAL EXPANSION ANALYSIS: SHELL

- TEMA

: TP304

Coefficient of Thermal Expansion at Actual Temp. Elastic Modulus at actual Metal Temperature TUBES

- TEMA

psi

: TP304

Coefficient of Thermal Expansion at Actual Temp. Elastic Modulus at actual Metal Temperature TUBESHEET - TEMA

.08684E -05 / deg F

.02782E +08

.08845E -05 / deg F

.27444E +08

psi

: TP304

Coefficient of Thermal Expansion at Actual Temp. Elastic Modulus at actual Metal Temperature

.08859E -05 / deg F

.2740E +08 psi

TEMA RCB-7.161 J Factor for Thermal Expansion

.0030

TEMA RCB-7.161 K Factor for Thermal Expansion

.2672

TEMA RCB-7.161 Fq Factor for Thermal Expansion 8.2034 TEMA RCB-7.161 Differential Expansion / Length

-.63E-03

TEMA RCB-7.161 Equivalent Differential Thermal Expansion Pressure: PD = 4 * RJ * ELAS * TSCA * DLL / ( DOS - 3.0*TSCA ) * ( 1.0 + RJ * RK * FQ ) PD = 4 * .0030 * 27820000 * .2500 * -.0006 / ( 112.5000 - 3.0 * .2500 ) * ( 1.0 + .0030 * .2672 * 10.5620 ) PD = -.48 psig

RCB 7.162 Equivalent Shellside Bolting Pressure: PBS = 6.2 * RMA / ( F**2 * G**3 ) PBS = 6.2 * 722024 / ( 1.0000^2 * 112.0000^3 ) PBS = 3.19 psig RCB 7.162 Equivalent Tubeside Bolting Pressure: PBT = 6.2 * RMO / ( F**2 * G**3 ) PBT = 6.2 * 653701 / ( 1.0000^2 * 112.0000^3 ) PBT = 2.88 psig

TEMA RCB 7.163 Effective Shellside Design Pressure: TEMA RCB-7.163 Fs Factor for Shellside Design

.8610

PSP1 = 0.4 * RJ * ( 1.5 + RK * (1.5 + FFS ) ) = 0.4 * .0030 * ( 1.5 + .2672 * (1.5 + .8610 ) ) PSP2 = ( ( 0.5 - RJ / 2.0 ) * ( DJ**2 / G**2 - 1.0 )

16-22



Example Problems

= ( ( 0.5 - .0030 / 2.0 ) * ( 117.7500**2 / 112.0000**2 - 1.0 ) PSP3 = 1.0 + RJ * RK * FQ = 1.0 + .0030 * .2672 * 8.2034 PSP = PS * ( ( PSP1 - PSP2 ) / PSP3 ) = 50.00 * ( ( .0026 - .0282 ) / 1.0086 ) PSP = -2.48 psig

TEMA RCB-7.163 Eff. Shell Side Design Pressure: PSU = Max (absolute) of PSP : -2.48 or PBS : 3.19 or ( PSP - PD ) / 2 : ( -2.48 - -.48 ) / 2.0 or ( PSP - PD - PBS ) / 2 : ( -2.48 - -.48 - 3.19 ) / 2.0 or ( PBS + PD ) / 2 : ( 3.19 + -.48 ) / 2.0 or ( PSP - PBS ) : ( -2.48 - 3.19 ) PSU =

: 5.66 psig

TEMA RCB 7.163 Shellside Shear Design Pressure, PBS=0: PSS =

: 2.48 psig

RCB 7.164 Effective Tubeside Design Pressure: TEMA RCB-7.164, Ft Factor for Tubeside Design

.8949

PTP1 = 1.0 + 0.4 * RJ * RK * ( 1.5 + FFT ) = 1.0 + 0.4 * .0030 * .2672 * ( 1.5 + .8949 ) PTP2 = 1.0 + RJ * RK * FQ = 1.0 + .0030 * .2672 * 8.2034 PTP = PT * PTP1 / PTP2 = 50.00 * 1.0008 / 1.0067 PTP = 49.71 psig

TEMA RCB-7.164 Effective Tube Side Design Pressure: PTU = Max (absolute) of : ( PTP + PBT + PD ) / 2 : ( 49.71 + 2.88 + -.48 ) / 2.0 or ( PTP + PBT ) : ( 49.71 + 2.88 ) ( PTP - PSP + PBT + PD) / 2 : ( 49.71 - -1.27 + 2.88 + -.48 ) / 2.0 or ( PTP - PSP + PBT ) : ( 49.71 - -1.27 + 2.88 ) PTU =

: 55.07 psig

RCB 7.164 Tubeside Shear Design Pressure (PBT=0): PTS =

: 52.19 psig

TEMA RCB-7.132 Required Thickness for Shellside Pressure : TRS = FS * GS * SQRT ( PSU / ( ETA * SOTS ) ) / 3.0 TRS = 1.0000 * 112.0000 * SQRT( 5.66 / ( .7201 * 15900 ) ) / 3.0 TRS = .8304 in. TEMA RCB-7.132 Required Thickness for Tubeside Pressure : TRC = FC * GC * SQRT ( PTU / ( ETA * SOTS ) ) / 3.0 TRC = 1.0000 * 112.0000 * SQRT( 55.07 / ( .7201 * 15900 ) ) / 3.0 TRC = 2.5892 in. TEMA RCB-7.132 Required Thickness for Bending + CAS + MAX( CAC,GROOVE): TREQ = 2.5892 in.

No Shear Calculation, since Pressure is less than

5025.1846

psig

TEMA RCB-7.134 Required Thickness for Tubesheet Flanged Extension : TFREQ = .98* SQRT((RM*(R^2 - 1 + 3.72* R^2 * LOG(R))) / ( SOTS * ( DF - G ) * ( 1.0 + 1.8 * R^2 ))


16-23

Example Problems


TFREQ = .98* SQRT(( 722024*( 1.04^2 - 1 + 3.72* 1.04^2*LOG( 1.04))) / ( 15900 * ( 116.25 - 112.00 ) * ( 1.0 + 1.8 * 1.04^2 )) TFREQ = .8790 in.

RCB-7.22 Shell Longitudinal Stress : Max. Effective Pressure for Longitudinal Stress,

.77

psig

Min. Effective Pressure for Longitudinal Stress,

-2.48

psig

TEMA RCB-7.22 Maximum Shell Longitudinal Stress : STSMAX = PSSMAX * CS * ( DOS - TSCA ) / ( 4 * TSCA ) STSMAX = .77 * .50 * ( 112.5000 - .2500 ) / ( 4 * .25 ) STSMAX = 43. psi TEMA RCB-7.22 Allowable Shell Longitudinal Stress : STSALL = 15900. psi

TEMA RCB-7.22 Minimum Shell Longitudinal Stress : STSMIN = PSSMIN * CS * ( DOS - TSCA ) / ( 4 * TSCA ) STSMIN = -1.27 * 1.00 * ( 112.5000 - .2500 ) / ( 4 * .25 ) STSMIN = -278. psi TEMA RCB-7.22 Allowable Shell Compressive Stress : External Pressure Chart Geometry Factor, A

HA-1

at

= 0.125/(Ro/t)

Materials Factor, B, Function(A, Chart)

649.00

A

.0005556

B

5038.

F

psi

STSCOM = -5038. psi

RCB-7.23 Tube Longitudinal Stress Results : Max. Effective Pressure for Longitudinal Stress,

51.98

psig

Min. Effective Pressure for Longitudinal Stress,

-.48

psig

TEMA RCB-7.23 Maximum Tube Long. Stress (Tension): STTMAX = PTTMAX*CT*FQ*G*G /(4*TNUMT*TT*(DT-TT)) STTMAX = 50.72* 1.00* 10.56* 112.0000* 112.0000 / ( 4* 3100* .0490*( .7500- .0490) ) STTMAX = 12557.97 psi

TEMA RCB-7.23 Allowable Tube Long. Stress (Tension): STSALL = 13500.00 psi

TEMA RCB-7.23 Minimum Tube Comp. Longitudinal Stress : STTMIN = PTTMIN*CT*FQ*G*G/(4*TNUMT*TT*(DT-TT)) STTMIN = -.48* 1.00* 8.20* 112.0000* 112.0000 / ( 4* 3100* .0490*( .7500- .0490) ) STTMIN = -115.25 psi

Modulus of Elasticity of Tubes at Mean Tube Temperature External Pressure Chart

HA-1

Elastic Modulus for Tube Material,

at ET

226.00

F

27118000.00 psi

TEMA RCB-7.24 Allowable Tube Compressive Stress : STTCOM = -PI**2 * ET / ( FSAF * RKLR**2 ) STTCOM = - 3.14**2 * 27118000 / ( 1.25 * 201.25**2 ) STTCOM = -5286.52 psi

16-24



Example Problems

RCB-7.25 Tube-To-Tubesheet Joint Load : Effective Pressure for

Tube-to-Tubesheet Load :

TEMA

Tube-To-Tubesheet Load :

RCB-7.25

Actual

51.98 psig

WJ = PI * FQ * PTLOAD * G * G / ( 4.0 * TNUMT ) WJ = 3.14 * 8.20 * 50.72 * 112.00 * 112.00 / ( 4.0 * 3100 ) WJ = 1355.14 lb. TEMA RCB-7.25 Allowable Tube-To-Tubesheet Load : WJA = (PI/4.0)*(DT^2-(DT-2*TT)**2)*SOT*FASME WJA = ( 3.14/4.0)*( .7500^2-( .7500-2.0 * .0490)**2) * 13500 * .70 WJA = 1019.75 lb.

Fixed Tubesheet Required Thickness per TEMA 8th Edition:

Case#

Thickness Reqd

----- P r e s s u r e s

Case

Pass/

Tbsht

Pt’

Type

Fail

Extnsn

Ps’

PDif

---------------------------------------------------------------------1c

2.531

0.879

49.72

0.00

0.00

Fvs+Pt-Th+Ca

Ok

2c

0.831

0.879

0.00

-2.48

0.00

Ps+Fvt-Th+Ca

Ok

3c

2.590

0.879

49.72

-2.48

0.00

4c

0.750

0.879

0.00

0.00

-0.48

Fvs+Fvt+Th+Ca

Ok

5c

2.530

0.879

49.71

0.00

-0.48

Fvs+Pt+Th+Ca

Ok

6c

0.830

0.879

0.00

-2.48

-0.48

Ps+Fvt+Th+Ca

Ok

7c

2.589

0.879

49.71

-2.48

-0.48

8c

0.750

0.879

0.00

0.00

0.00

Ps+Pt-Th+Ca Fail

Ps+Pt+Th+Ca Fail Fvs+Fvt-Th+Ca

Ok

---------------------------------------------------------------------Max:

2.590

0.879

in.

Given Tubesheet Thickness:

2.5625 in.

Note: Fvt, Fvs - User-defined Shell-side and Tube-side vacuum pressures or 0.0. Ps, Pt

- Shell-side and Tube-side Design Pressures.

Th

- With or Without Thermal Expansion.

Ca

- With or Without Corrosion Allowance.

Tube and Shell Stress Summary: ---------- Shell Stresses Case# Ten

Allwd

Cmp

Allwd

---------- Tube Stresses Ten

Allwd

Cmp

Allwd

Tube Loads Ld

Allwd

Pass Fail

---------------------------------------------------------------------------1c

32

15900

0

-5038

10689

13500

0

-5458

1153

1020

2c

0

15900

-279

-5038

1867

13500

0

-5458

201

1020

Fail Ok

3c

32

15900

-279

-5038

12556

13500

0

-5458

1355

1020

Fail

4c

27

15900

0

-5038

0

13500

-115

-5287

0

1020

Ok

5c

43

15900

0

-5038

10691

13500

-115

-5287

1154

1020

Fail

6c

27

15900

-278

-5038

1867

13500

-115

-5287

201

1020

Ok

7c

43

15900

-278

-5038

12558

13500

-115

-5287

1355

1020

Fail

8c

0

15900

0

-5038

0

13500

0

-5458

0

1020

Ok

---------------------------------------------------------------------------MAX RATIO

0.003

0.055

0.930

0.022

1.329

The PVELITE Program, (c) 1989-2001 by COADE Engineering Software


16-25

Example Problems

16-26




&KDSWHU The WRC 107/FEA Module

Introduction This chapter discusses the WRC 107/FEA Module in PVElite. To begin, make sure that the current analysis type is WRC 107/FEA. This can be determined when viewing the main menu. From version 4.0 of PVElite, an interface for performing finite element analysis (FEA) of nozzle-shell junctions, is available. You can choose to perform either WRC 107 or FEA. WRC 107 is a method for determining stresses on the shell of a vessel when a nozzle or some rectangular attachment is being loaded. A typical case is to analyze the vessel stresses on a nozzle due to external piping loads. These loads are obtained from a piping flexibility analysis. This type of stress analysis is based on “Local Stresses in Spherical and Cylindrical Shells due to External Loadings,” Welding Research Council Bulletin 107, August 1965, and revision 1979, based on the prior work of P.P. Bijlaard. As of Version 3.3, PVElite features a stress summation capability. The program computes overall stress intensities on a vessel/nozzle intersection in accordance with ASME Section VIII Division 2. Local vessel stress calculations for sustained, expansion, and occasional loads along with pressure stresses are transformed into code-defined stress components. The output, in the form of Pm, Pl, and Q and their appropriate combinations, can be compared with Section VIII Div. 2 allowable values. There are times when the applicability of the WRC bulletin 107 is in question or a particular design is out of the scope of the bulletin. Examples include large nozzles, hillside nozzles, and lateral nozzles. In these cases and others, FEA is the best way to get accurate results. The FEA interface in PVElite uses an encapsulated finite element program (NozzlePro) available from Paulin Research Group (www.paulin.com). To run the FEA, the user should purchase the NozzlePro program and install it in the Nozpro subfolder under the PVElite folder. PVElite will automatically run it and present the results in the PVElite screen.

The WRC 107/FEA Module

17-1

Discussion of Input


Discussion of Input Main Input Fields Enter the Attachment Number for this Analysis

The attachment number should start out at 1 and continue by ones for each successive attachment to be analyzed. These whole integer numbers will be reflected in the input echo generated by the program. This number can be between up to 5 digits in length. Enter the Attachment Description for this Analysis

The Description ID can be any combination of numbers and letters up to 15 characters. This label is for user reference and should be meaningful for the analysis. In addition, note that the attachment description will be reflected in the output and also in the display of errors (if any exist). Merge

Use this option to bring in data from the "Shells and Heads" module. Just select the shell you want to model this nozzle with, and all the appropriate data will be brought in from that shell. Import Nozzle Data

Imports nozzle information from a PVElite input file (.pvi). Choose the analysis type between WRC 107 and FEA

To perform a Finite Element Analysis (FEA) on the nozzle-vessel junction, the user has to purchase the NozPro program from Paulin Research Group (www.paulin.com) and install it under the CodeCalc folder (or PVElite folder if the user has PVElite). Some additional input will be required for the FEA run. Select the Attachment Type

For a WRC 107 analysis possible options are: •

Typical Pipe Nozzle

•

Square Attachment ( lug type )

•

Rectangular Attachment ( lug type )

If the attachment in question is a pipe nozzle then select 'Round'. WRC107 also analyzes other load bearing attachments such as square or rectangle. An example of a rectangular attachment is a vessel support lug. Illustrations of these attachments can be seen in the WRC107 bulletin. At this point FEA can only be performed on round attachments. Hollow or Solid Attachment ?

This input is only required for performing a WRC 107 analysis. One may note that roundhollow attachments are converted to round-solid attachments for the cylinder to cylinder case. In addition, rectangular attachments on spherical shells cannot be analyzed using this method. Also, round-hollow attachments are analyzed on spherical vessels.

17-2



Discussion of Input

Enter the Type of Vessel Being Analyzed

The Welding Research Council Bulletin #107 recognizes two types of vessels in which the stress intensities can be calculated. These are cylindrical and spherical vessels. •

Cylindrical

•

Spherical

If user selects to perform a finite element analysis then following vessel types are permitted: •

Cylindrical

•

Spherical

•

Elliptical

•

Torispherical

•

Conical

•

Flat Head

Enter the Diameter Basis for the Vessel

If the vessel on which you are analyzing has dimensions specified based on the inside diameter, choose ID. If the diameter basis is outside, choose OD. These are the only acceptable inputs for this cell. Diameter of Vessel

Enter the diameter of the vessel in the units displayed. The diameter basis for the vessel is a user defined value and appears above With the vessel wall thickness, diameter basis and corrosion allowance known, PVElite will automatically determine the mean radius. Enter the Vessel Wall Thickness

Enter the thickness of the vessel wall in this field. If, the vessel in question is pipe and a 12.5% mill tolerance is wished to be used then enter the actual thickness of the vessel wall times 0.875. PVElite does not make any modification to this value unless a corrosion allowance is specified. Enter the Corrosion Allowance of the Vessel

If a corrosion allowance is to be used then enter it in this field. The vessel wall thickness will be decreased by this amount and the mean radius will be adjusted accordingly. Material Name

Click the "Material Database" button to look up a material name from the material database. Click the "Material Edit Properties" button to change the properties of the selected material. Users can also choose between the ASME Section VII Div 1 or Div 2 material database. If you enter the name on this input cell, it will retrieve the first material it finds with a matching name. EXAMPLES FOR MATERIAL SPECIFICATION: SA-516 70, SA-285 C


17-3

Discussion of Input


Some typical material names (standard ASME material name): •

•

•

•

Plates & Bolting •

SA-516 55

•

SA-516 60

•

SA-516 65

•

SA-516 70

•

SA-193 B7

•

SA-182-F1

•

SA-182 F1

•

SA-182 F11

•

SA-182 F12

•

SA-182 F22

•

SA-105

•

SA-36

•

SA-106 B

Stainless Steels •

SA-240 304

•

SA-240 304L

•

SA-240 316

•

SA-240 316L

•

SA-193 B8

Aluminum •

SB-209

•

SB-234

Titanium •

•

17-4

SB-265 1

Nickel •

SB-409

•

SB-424



Discussion of Input

Input Vessel Fatigue Curve

Select the fatigue curve based on the type of material. Fatigue curves are listed in ASME Section VIII, Division 2, Appendix 5. Possible entries are. S. No

Material

1

Low Carbon Steels, UTS < 130 ksi

2

Low Alloy Steels to 700 deg. F

3

Martensitic Stainless Steels to 700 deg. F

4

Austenitic Stainless Steel to 800 deg. F

5

Wrought 70 Copper, 30 Nickel.

6

Nickel-Chromium-Moly-Iron Alloys up to 800 deg. F

Input Loads in WRC107 Convention

Check this field if you would like to input the forces and moments in the traditional WRC107 convention. Leave this field unchecked if you would like to input loads in Global Coordinates and perform the stress summation. The program will NOT perform the Div. 2 stress summation and S.I. check if this field is checked. This option is only available when running a WRC 107 calculation. Input Loads in Global Coordinates and Allowable Stresses

Check this field if you would like to input loads in Global Coordinates and input cold/hot Div. II allowable stresses. The program will perform Stress Summation and check against S.I. allowables if Sustained (unrelenting) loadings are known. If you are performing FEA, the program will ask for additional information. Input Sustained (SUS) Loads

Check this field if you would like to input Sustained loads in Global Coordinates. The Stress summation will be performed and the stress intensities will be checked based on the different load cases. Input Expansion (EXP) Loadings/Input Operating (OPE) Loadings

The way this input is used depends on if the user is performing WRC 107 analysis or FEA (finite element analysis). For a WRC 107 run, check this field if you would like to input EXPansion loads in Global Coordinates. In that case, total Stress summation will be performed and the overall stress intensities will be checked for each load case. For a FEA run, check this field if you would like to input OPErating loads in Global Coordinates.

Note

For graphics plot of EXPansion loads—temporarily set sustained and occasional to not checked.


17-5

Discussion of Input


Input Occasional (OCC) Loadings

Check this field if you would like to input Occasional loads in Global Coordinates. For WRC 107, the Stress summation will be performed and the stress intensities will be checked based on loading cases.

Note

17-6

For graphics plot of Occasional loads—temporarily set sustained and expansion to not checked.



Pop-Up Input Fields

Pop-Up Input Fields Enter the Diameter Basis for the Nozzle

If the junction that is being analyzed is a nozzle, enter the diameter basis here. Select the nozzle’s diameter basis from the pull-down menu. Nozzle Wall Thickness

Enter the nozzle wall thickness. The WRC 107 program will use this thickness when the hollow attachment is used. If the standard 12.5% mill tolerance is to be deducted, simply multiply the standard wall thickness by 0.875 directly on the spreadsheet. Nozzle Diameter

Enter the nozzle diameter. Both the nozzle diameter and thickness must be specified. The nozzle diameter should be entered in accordance with the nozzle diameter basis. The units are displayed above. Nozzle Corrosion Allowance

Enter the corrosion allowance for the nozzle. Material Name

This input is only needed for FEA. Press on the "Material Database" button to look up a material name from the material database. Press the "Material Edit Properties" button to change the properties of the selected material. If you type in the name on this input cell, it will retrieve the first material it finds with a matching name. EXAMPLES FOR MATERIAL SPECIFICATION: SA-516 70, SA-285 C Some typical material names (standard ASME material name): •

Plates & Bolting •

SA-516 55

•

SA-516 60

•

SA-516 65

•

SA-516 70

•

SA-193 B7

•

SA-182-F1

•

SA-182 F1

•

SA-182 F11

•

SA-182 F12

•

SA-182 F22

•

SA-105

•

SA-36


17-7

Pop-Up Input Fields


• •

•

•

Stainless Steels •

SA-240 304

•

SA-240 304L

•

SA-240 316

•

SA-240 316L

•

SA-193 B8

Aluminum •

SB-209

•

SB-234

Titanium •

•

SA-106 B

SB-265 1

Nickel •

SB-409

•

SB-424

Reinforcement

Select the type of reinforcement (if present) from the list. Selecting a reinforcement type causes a popup window to appear for prompts concerning reinforcing pad or hub dimensions. In a finite element analysis attachments can have a reinforcement pad or hub type selfreinforcement. Results are available for the some critical locations such as the nozzle-shell junction and the edge of the pad. While in WRC 107 analysis (due to the limitations of the bulletin) only reinforcement pad can be considered. When the reinforcing pad dimensions are included the program performs two analyses for this situation. The first analysis uses the nozzle OD and the vessel wall thickness plus the reinforcing pad thickness. The second run takes the pad into account by making the nozzle OD equal to the reinforcing pad diameter and assuming a solid attachment. Parameter C11 (Full Length of Attachment)

Attachments other than nozzles can be analyzed using the WRC107 method. The dimension C11 is the FULL length of the attachment in the circumferential direction. Most often these types of attachments are lifting lugs or vessel support lugs. Parameter C22 (Full Length of Attachment)

The parameter C22 is the FULL length of the attachment in the longitudinal direction.

17-8



Pop-Up Input Fields

Pad Diameter

Enter the diameter of the reinforcing pad along the surface of the vessel. This information will be used to calculate the stresses at the edge of the reinforcing pad using a solid attachment model. Reinforcement pad is explicitly modeled in the finite element analysis. Pad Thickness

Enter the thickness of the reinforcing pad. If external corrosion is to be considered, enter the corroded pad thickness. In WRC 107, when a pad is used the combined vessel+pad thickness is used for the stress computation at the edge of the nozzle. The corroded vessel thickness is used for the stress computation at the edge of the pad. Reinforcement pad is explicitly modeled in the finite element analysis. Enter Pad Parameter C11 (full length)

With square/rectangle attachment, enter the FULL length of the PAD in the circumferential direction. The definition of C1 in wrc107 is the half length of the attachment in the circumferential direction. The change was done for user convenience. Enter Pad Parameter C22 (full length)

With square/rectangle attachment, enter the FULL length of the PAD in the longitudinal direction. The definition of C1 in wrc107 is the half length of the attachment in the longitudinal direction. The change was done for user convenience. Hub Thickness/Hub height/Bevel Height

Enter in the appropriate dimension based on the diagram below.


17-9

Pop-Up Input Fields


Insert or Abutting Nozzle?

If the nozzle is welded to the outside of the vessel wall, it is abutting the vessel wall. If the hole in the vessel is bigger than the nozzle OD and the nozzle is welded into the hole, it is inserted. Nozzle Outside Projection

Enter the projection of the nozzle from the vessel wall to the nozzle flange. Nozzle Inside Projection

Enter the projection of the nozzle into the vessel, measured along the centerline of the nozzle. Thickness of Nozzle Insert (if different)

Enter the thickness of the internally projected part of the nozzle, if it is different from the nozzle thickness. Weld Leg Size for Fillet between Nozzle and Shell / Pad

It is an optional field. Enter the fillet leg size. Input Nozzle Fatigue Curve

Select the fatigue curve based on the type of material. Fatigue curves are listed in ASME Section VIII, Division 2, Appendix 5. Possible entries are. S. No

Material

1

Low Carbon Steels, UTS < 130 ksi

2

Low Alloy Steels to 700 deg. F

3

Martensitic Stainless Steels to 700 deg. F

4

Austenitic Stainless Steel to 800 deg. F

5

Wrought 70 Copper, 30 Nickel.

6

Nickel-Chromium-Moly-Iron Alloys up to 800 deg. F


Enter the total length of the cylinder or a conical geometry. Attached Shell Length

This is an optional entry. Enter the length of the shell attached to the head. Set this value based on the proximity of the nozzle to the edge of the head, and of the concern for any discontinuity stress in this area. Attached Shell Thickness

This is an optional entry. Enter the thickness of the shell attached to the head. Set this value based on the proximity of the nozzle to the edge of the head, and of the concern for any discontinuity stress in this area. If left blank this entry defaults to the thickness of the head.

17-10



Pop-Up Input Fields

Aspect Ratio for Elliptical Heads

The aspect ratio is the ratio of the major axis to the minor axis for the ellipse. For a standard 2:1 elliptical head the aspect ratio is 2.0. Length of Straight Flange

Enter the length of straight flange portion for Conical or Torispherical heads. Inside Crown Radius for Torispherical Heads

The crown radius for a torispherical head is referred to as the dimension L, per ASME Section VIII Div. 1. This dimension is usually referred to as "DR" in many head catalogues. Even though the head catalogues list these heads as being "OD" heads, the crown radius is given on the inside diameter basis. Note the illustrated picture in the catalogue and where the arrows for "DR" and "IKR" point to ( the inside of the head). For more information see Appendix 1-4 in the Code Inside Knuckle Radius for Torispherical Heads

This dimension is r, per ASME Section VIII Div. 1. This dimension is usually referred to as "IKR" in many head catalogues. Even though the head catalogues list these heads as being "OD" heads, the knuckle radius is given on the inside diameter basis. Note the illustrated picture in the catalogue and where the arrows for "DR" and "IKR" point to ( the inside of the head). For more information see Appendix 1-4 in the Code Small End Diameter

Enter the small end diameter for the cone. Is there a knuckle ?

Check here if this cone has a knuckle. Knuckle Radius at Small End

Enter the Knuckle radius of the small end. Direction of a conical head or shell is from the large end to the small end. So, the large end of the cone is the bottom end and the small end of the cone is the top end. Knuckle Radius at Large End

Enter the Knuckle radius of the large end. Direction of a conical head or shell is from the large end to the small end. So, the large end of the cone is the bottom end and the small end of the cone is the top end. Design Pressure (for input with WRC107 convention)

Enter the design pressure of the vessel in this field using the units above. The pressure stress equation is of the following form: Longitudinal Stress = Hoop Stress =


Pressure * ri^2 / ( ro^2 - ri^2 ) 2.0 * Longitudinal Stress.

17-11

Pop-Up Input Fields


For the spherical case the membrane stress due to internal pressure uses the Lame type equation to compute the stress at both the upper and lower surfaces of the vessel at the edge of the attachment. Radial Load

Enter the value for the load which is trying to push or pull the nozzle in/out of the vessel. Positive loads try to “push” the nozzle while negative loads try to “pull” the nozzle. The program does not account for the effect of pressure thrust. However, if you input in global coordinates (stress summation), the program will consider pressure thrust as default unless you specify NOT to. Circumferential Shear Load

Enter the circumferential shear load VC from B to A in the units above. If the vessel is spherical then enter the shear load V2 from D to C. The sign convention should be in accordance with the WRC107 bulletin. Longitudinal Shear Load

Enter the longitudinal shear load VL from D to C in the units above. If the vessel is spherical then enter the shear load V1 from B to A. The sign convention should be in accordance with the WRC107 bulletin. Circumferential Moment

Enter the circumferential moment MC or M1 in the units displayed above. The sign convention should be in accordance with the WRC107 bulletin. Longitudinal Moment

Enter the longitudinal moment ML or M2 in the units displayed above. The sign convention should be in accordance with the WRC107 bulletin. Torsional Moment

Enter the torsional moment in the units displayed above. The sign convention should be in accordance with the WRC107 bulletin. Compute Maximum Radial Force Compute Maximum Circumferential Moment Compute Maximum Longitudinal Moment

Often times a vessel designer would like to determine the maximum force or moment on an attachment while keeping the other 5 constant. By checking to one of these fields PVElite will iterate and determine the maximum force or moment to produce a desired stress intensity. If your geometry includes a reinforcing pad, PVElite will perform the same type analysis at the edge of the reinforcing pad. The above loads produce the highest

17-12



Pop-Up Input Fields

local bending loads and will usually govern the design. This is why the shear loads and torsional moment are not options. Compare Maximum Stress Intensity to

This entry should be a stress value approximately 3 times the hot allowable stress for the vessel material as taken from Section II Part D of the ASME Code. PVElite will use this number to compare computed stress intensities if one of the “Compute Maximum” fields was checked. Note that in the results PVElite performs the analysis using the input values. After that has been completed, PVElite will then iterate for the maximum force or moment as it has been instructed to. Vessel/Nozzle Centerline Direction Cosines

Enter the vessel/nozzle centerline direction cosine. The direction of nozzle is positive when pointing inwards into the vessel. For finite element analysis these direction cosines are used to determine the angle between the nozzle and the vessel. Also note that the direction for a conical vessel is from the big end to small end. For WRC 107 analysis, the centerlines of the vessel and nozzle are required to be perpendicular to each other. The direction vectors of the vessel and the nozzle centerline must NOT be collinear. If they are, as in the case of a nozzle in head, the vessel direction vector shall be changed so that it is perpendicular to the nozzle centerline. A typical input for a nozzle on the side of a vertical vessel would be: •

Vessel Direction Vector (0.0, -1.0, 0.0)

•

Nozzle Direction Vector (1.0, 0.0, 0.0)

The program uses these direction vectors to transfer the global forces and moments from the CAESAR II static run (from each load case) into the somewhat confusing WRC107 sign/load convention. Note

The sign of the vessel centerline direction vector can be +ve or -ve follows the location of data point (A->D) convention defined by WRC 107, e.g. for a vertical vessel, if point A is at the bottom of the nozzle, then the Y direction cosine of the vessel will be -1.0. Remember points A and B are always lie along the direction of the vessel. The nozzle direction vector is defined as a vector pointing from the nozzle connection to the centerline of the vessel.Cold Stress Intensity Allowable (Smc)

Cold Stress Intensity Allowable (Smc)

Enter the cold stress intensity allowable (Smc) of the vessel as defined per ASME Section VIII, Division 2. They can be located in Table 2A of Section II, Part D of ASME Code. These values are used only for WRC 107 analysis.


17-13

Pop-Up Input Fields


Hot Stress Intensity Allowable (Smh)

Enter the hot stress intensity allowable (Smh) of the vessel as defined per ASME Section VIII, Division 2. They can be located in Table 2A of Section II, Part D of ASME Code. These values are used only for WRC 107 analysis. Override Angle Between Nozzle and Vessel ?

The program computes the angle between the vessel and the nozzle by taking the dot product between their direction cosines. Click here to override that computed value of angle. This value is used only for FEA. Nozzle Orientation Reference Vector

The nozzle orientation reference vector defines the reference axis from where the orientation of the nozzle can be measured by the nozzle orientation angle. For example, if nozzle orientation reference axis is along x-axis and nozzle orientation angle is zero then the nozzle is located along the x-axis as seen in figure below.

Nozzle Orientation Angle from the Reference Vector

This is the angle that describes the nozzle position around the circumference of the vessel from the orientation reference vector. The reference orientation vector should be entered above on this dialog. For example, if nozzle orientation reference axis is along x-axis and nozzle orientation angle is zero then the nozzle is located along the x-axis as seen in the previous figure.

17-14



Pop-Up Input Fields

Nozzle Offset from the Vessel Centerline

Enter the offset distance from Shell/Head Centerline to the Nozzle Centerline. Nozzle Distance from Top End of the Vessel

Enter the distance from the positive end of the vessel to the point where the nozzle or branch centerline intersects the vessel centerline. Global Forces/Moments (SUS, EXP, OCC)

Enter the value of nozzle forces or Moments from the restraint summary of the CAESAR II output and/or other calculations. Three loading sets may be included in these calculations. For WRC 107, enter the loads according to each category shown on the screen, where SUS

Primary Loads (typically Weight+Pressure+Forces)

EXP

Secondary Loads (Thermal Expansion)

OCC

Occasional Loads (typically Wind, Seismic)

For FEA, enter the loads according to each category shown on the screen, where SUS

Primary Loads (typically Weight+Pressure+Forces)

OPE

Operating Loads (typically Weight+Disp+Temp+Pressure+Forces)

OCC

Occasional Loads (typically Wind, Seismic)

Internal Pressure (P)

Enter the system design pressure. It shall always be a positive (or 0) entry. The pressure thrust force P*A will be added to the value of the nozzle radial load UNLESS the user deactivates and disables the following field. This value is used only if the user is performing WRC 107 analysis. Include Pressure Thrust Force

Check this box if you wish to include the pressure thrust force as part of the radial load. This value is used only if the user is performing WRC 107 analysis. Internal Pressure (Pvar)

Enter the DIFFERENCE between the peak pressure of the system and the system design pressure. It shall always be a positive (or 0) entry. The additional thrust load due to this pressure difference will also be accounted for in the nozzle radial loading UNLESS a response of N to “Include Pressure Thrust” was entered above. This entry will be superimposed onto the system design pressure to evaluate the primary membrane stress due to occasional loads. This value is used only if the user is performing WRC 107 analysis.


17-15

Pop-Up Input Fields


Additional Input for VRC107 WRC107 Version

There are 3 options available here. The first option is for the original August 1965 version of this industry standard. The second option is for March 1979 and option 3 is for March 1979 use B1 and B2. In 1979 the Welding Research Council noted that if certain curves were flipped, the computed stress results matched theoretical results more closely. In that same year an adjustment was made to allow this stress computation method to compute a maximum stress that did not lie on the stress points A, B, C or D. This is referred to as computation of the off-angle maximums. Thus, we can infer the third option is probably the most accurate. Use Interactive Control

In many instances, the geometric parameter Beta which is computed for cylindrical shell geometry’s, exceeds the parameter Gamma for certain WRC107 curves. When this occurs PVElite will pause and display a message “Beta too Big” or “Beta too Small”. If the response to Use Interactive Control is “No” then PVElite will use the last point on the curve that is available. If the response to Interactive Control is “Yes” PVElite will pause and ask you to enter what you believe the value of the stress parameter should be. This will involve having the WRC107 bulletin with all of the curves available. Include WRC107 SIF (Kn,Kb)

Check this field to include the WRC107 Stress Concentrations (Kn & Kb). The program will estimate and use the stress concentration factors Kn and Kb per Appendix B of the WRC-107 Bulletin. For normal analysis, do not check this field. And DO NOT include the next field “Pressure Stress Indices Per Div. 2”. Be very careful when using Y for this input and the next input. You may check ASME VIII Div.2 AD-160 to see if you need to consider fatigue effect. Please note that the program currently DOES NOT perform the fatigue analysis per Div.2 Appendix 4 & 5 rules. The program simply multiply the stresses by the factors and/or indices. The user can compare the fatigue effect. Therefore the stress summation results with these factors are intended for your references ONLY. Please review the User’s Guide for detail. Fillet Radius Between Vessel & Nozzle (r)

Enter the fillet radius between the nozzle and the vessel shell. The program will use this value to calculate the stress concentration factors Kn and Kb per Appendix B of the WRC107 Bulletin. Entering 0 here will set Kn and KB = 1.0. If you have a re-pad, the same Kn and Kb will be used for the vessel and pad intersection.

17-16



Pop-Up Input Fields

Include Pressure Stress Indices

Check this field to include the stress indices described in ASME Sec. VIII Div. 2, primarily to account for the fatigue analysis of the vessel nozzle under internal pressure. The stress indices can be found in the Table AD-560.7 of the Code. Compute WRC -386 Pressure Stress per WRC

Check this box to compute pressure, stresses in the shell and nozzle per WRC-386. WRC386 provides a method for calculating the stresses in cylinder to cylinder intersections (such as cylinder to nozzle junction), due to the internal pressure and radial thrust loadings.

Note

Using WRC -368 along with WRC 107/297 is not accurate when calculating the combined stress from pressure and external loads. So, WRC-368 is only active when no external loads are specified and the attachment type is round.

For more information on WRC-368 pressure thrust please read "Modeling of Internal Pressure and Thrust Loads on Nozzles Using WRC-368. You can access this information in the July 2001 edition of the COADE Mechanical Engineering News (pgs. 9-13) or via our Website www.coade.com/newsletters/jul01.pdf.

Additional Input for FEA Specify File Name for FEA

Enter the file name that will form the prefix for FEA analysis files. Filename can up to 7 character log without quotes and spaces. For example, noz and b012. Specify FEA Mesh Density

Select the type of mesh: Fine or Crude. When the user selects a fine mesh they will be prompted to specify the mesh density multiplier. A higher mesh density value produces a finer finite element mesh. Which produces more accurate results but takes more time to solve. Typical values are between 1-2. Crude mesh option along with the "Preview the Finite Element Mesh" option can be used to check the initial mesh. Specify S.C.F. for Vessel

This is an optional input. This is the Notch Effect Multiplication factor for computing the peak stresses. They are defined in the ASME Section VIII, Division 2 Appendix 4. A typical value is 1.35. They will only affect the fatigue failure stress case. Specify S.C.F. for Nozzle

This is an optional input. This is the Notch Effect Multiplication factor for computing the peak stresses. They are defined in the ASME Section VIII, Division 2 Appendix 4. A typical value is 1.35. They will only affect the fatigue failure stress case.


17-17

Pop-Up Input Fields


Number of Operating Cycles

Optional. Used only to select the allowable fatigue stress from S-N curves. It defaults to 7000 cycles if not specified or if 0. Number of Occasional Cycles

Optional. If zero then the occasional load is treated like a static load. If nonzero then it will be assumed that occasional load input is the "range" of occasional loads, and a fatigue analysis of occasional loads will be performed. FEA Design Pressure

Enter the design pressure for the vessel and the nozzle. When performing a finite element analysis, internal pressure is positive and external pressure is -ve. While, WRC 107 can only analyze internal pressure. FEA Design Temperature

Enter the operating temperature for the vessel. This value is used to compute the hot allowable stress for the vessel and the nozzle. Do Not Cut Hole in Header for Branch?

Check this box if there is no opening in the vessel due to the nozzle. For example, in case of a support trunnion there will not be an opening whereas an injector pipe will have one. Consider Thermal Strains?

Check this box if Nozzle and Vessel are at different temperatures or there is a through the wall temperature gradient. Most analysis of single nozzles in pressure vessels "do not" require the analysis of thermal strains. Vessel Inside Temperature, Vessel Outside Temperature, Nozzle Inside Temperature and Nozzle Outside Temperature

Enter the inside and outside surface temperatures for the nozzle and the vessel, used for computing the thermal expansion. Run Analysis in Silent Mode?

Check this box to run in silent mode. In silent mode, when the program is running, the status windows from Nozzle Pro program will not be visible. In some cases these windows provide additional information about possible errors. Preview the finite element mesh?

Check this box to preview the finite element mesh for this problem. Then on running the analysis the finite element mesh will be shown.

17-18




Discussion of Results WRC107 Stress Calculations The program computes stress intensities in accordance with WRC107 and includes the effects of longitudinal and hoop stresses due to internal pressure. If the geometry includes a circular reinforcing pad, PVElite will perform two analyses on the geometry. The first analysis will compute the stresses at the edge of the nozzle. The second stress analysis will be at the edge of the reinforcing pad. PVElite uses the Lamé equation to determine the exact hoop stress at the upper and lower surface of the cylinder around the edge of the attachment. The hoop stress equations, as well as the longitudinal stress equation are as follows: 2

S Long

Pri 2

2

r0 ri

S Hoop (Upper) = 2 S

S Hoop (Lower)

Long

2

2

P ri r0 2

2

r0 ri

For spherical shells the program uses the following equation:

S Long

3 3 P § r0 2ri · ¨¨ 3 3 ¸¸ 2 © r0 ri ¹

S Hoop

S Long

For each run performed a table of dimensionless stress factors for each loading will be displayed for review. Any table figure followed by an exclamation point (!) means that the curve figure for that loading has been exceeded. Why are the stresses at Edge of the Pad the same as at the Edge of the Nozzle? Since the stress is a direct product of the stress factor, the stresses computed at the edge of the pad may be same as those at the edge of the nozzle if the curve parameter for that type of stress has been exceeded. What are the Allowable Stresses ? The stress intensities computed should typically be between 1.5 and 3.0 times the hot allowable stress for the vessel material at operating temperature. If the results are less than 1.5 Sa then the configuration and loading are acceptable. If the load is self-relieving, that is if it would relax or disappear after only a small rotation or translation of the attachment, the allowable stress intensity would increase to 3.0 Sa. Since many geometry do not fall within the acceptable range of what WRC107 will accept, it may be necessary to use a more sophisticated tool to solve the problems where


17-19



the diameter of the vessel is very large in comparison with the nozzle or where the thickness of the vessel or nozzle is small. An example of a more sophisticated tool would be a FEA (finite element analysis) program.

M

M TAXIS V (or V ) 1

C

B

A V (or V ) 2

L

T

V L

A

VC

Upper

B C

C

Lower

M LAXIS

M CAXIS

M 1AXIS (or M ) C

P AXIS

P AXIS

M 2AXIS (or M ) L

M AXIS 1

A

A B

B

C

M L AXIS M2 AXIS

M CAXIS

D

D

C

SPHERICAL SHELLS

CYLINDRICAL SHELLS

To Define WRC Axes: 1. P-axis: Along the Nozzle centerline and positive entering the vessel. 2. M1-axis: Perpendicular to the nozzle centerline along convenient global axis. 3. M2-axis: Cross the P-axis into the M1 axis and the result is the M2-axis.

To Define WRC Axes: 1. P-axis: Along the Nozzle centerline and positive entering the vessel. 2. MC-axis: Along the vessel centerline and positive to correspond with any parallel global axis. 3. M2-axis: Cross the P-axis with the MC axis and the result is the ML-axis.

To Define WRC Stress Points: u—upper, means stress on outside of vessel wall at junction. l—lower, means stress on inside of vessel at junction. A—Position on vessel at junction, along negative M1 axis. B—Position on vessel at junction, along positive M2 axis. C—Position on vessel at junction, along positive M2 axis. D—Position on vessel at junction, along negative M2 axis.

To Define WRC Stress Points: u—upper, means stress on outside of vessel wall at junction. l—lower, means stress on inside of vessel at junction. A—Position on vessel at junction, along negative MC axis. B—Position on vessel at junction, along positive MC axis. C—Position on vessel at junction, along positive ML axis. D—Position on vessel at junction, along negative ML axis. Note: Shear axis "VC" is parallel, and in the same direction as the bending axis "ML." Shear axis "VL" is parallel, and in the opposite direction as the bending axis "MC."

Figure 17A - Geometry for the WRC 107 Module

17-20




Figure 17B - Clarifying WRC 107 convention for a cylinder


17-21

WRC107 Stress Summations


WRC107 Stress Summations The ASME Section VIII, Division 2 code provides for a fairly elaborate procedure to analyze the local stresses in vessels and nozzles (Appendix 4-1 “Mandatory Design Based On Stress Analysis”). Only the elastic analysis approach will be discussed here. The user should always refer to the applicable code if any of the limits described in this section are approached, or if any unusual material, weld, or stress situation exists, or there are non-linear concerns such as the material’s operation in the creep range. The first step in the procedure is to determine if the elastic approach is satisfactory. Section AD-160 contains the exact method and basically states that if all of the following conditions are met, then fatigue analysis need not be done: a. The expected design number of full-range pressure cycles does not exceed the number of allowed cycles corresponding to an Sa value of 3Sm (4Sm for non-integral attachments) on the material fatigue curve. The Sm is the allowable stress intensity for the material at the operating temperature. b. The expected design range of pressure cycles other than startup or shutdown must be less than 1/3 (1/4 for non-integral attachments) the design pressure times (Sa/ Sm), where Sa is the value obtained on the material fatigue curve for the specified number of significant pressure fluctuations. c. The vessel does not experience localized high stress due to heating. d. The full range of stress intensities due to mechanical loads (including piping reactions) does not exceed Sa from the fatigue curve for the expected number of load fluctuations. Once the user has decided that an elastic analysis will be satisfactory, either a simplified or a comprehensive approach may be taken to the vessel stress evaluation. Both methods will be described in detail below, after a discussion of the Section VIII Div. 2 Requirements.

17-22



ASME Section VIII Division 2 - Elastic Analysis of Nozzle

ASME Section VIII Division 2 - Elastic Analysis of Nozzle Ideally in order to address the local allowable stress problem, the user should have the endurance curve for the material of construction and complete design pressure / temperature loading information. If any of the elastic limits are approached, or if there is anything out of the ordinary about the nozzle/vessel connection design, the code should be carefully consulted before performing the local stress analysis. The material Sm table and the endurance curve for carbon steels are given in this section for illustration. Only values taken directly from the code should be used in design. There are essentially three criteria that must be satisfied before the stresses in the vessel wall due to nozzle loads can be considered within the allowables. These three criteria can be summarized as:

Pm < kSmh Pm + Pl + Pb< 1.5kSmh Pm + Pl + Pb + Q < 3Smavg Where Pm, Pl, Pb, and Q are the general primary membrane stress, the local primary membrane stress, the local primary bending stress, and the total secondary stresses (membrane plus bending), respectively; and K, Smh, and Smavg are the occasional stress factor, the hot material allowable stress intensity, and the average material stress intensity (Smh + Smc) / 2. Due to the stress classification defined by Section VIII, Division 2 in the vicinity of nozzles, as given in the Table 4-120.1, the bending stress terms caused by any external load moments or internal pressure in the vessel wall near a nozzle or other opening, should be classified as Q, or the secondary stresses, regardless of whether they were caused by sustained or expansion loads. This causes Pb to disappear, and leads to a much more detailed classification:

P - General primary membrane stress (primarily due to internal pressure); m

P - Local primary membrane stress, which may include: l

Membrane stress due to internal pressure; Local membrane stress due to applied sustained forces and moments. Q - Secondary stresses, which may include: Bending stress due to internal pressure; Bending stress due to applied sustained forces and moments; Membrane stress due to applied expansion forces; Bending stress due to applied expansion forces and moments Membrane stress due to applied expansion moments


17-23



Each of the stress terms defined in the above classifications contain three parts: two stress components in normal directions and one shear stress component. To combine these stresses, the following rules apply: 1. Compute the normal and shear components for each of the three stress types, i.e. Pm, Pl, and Q. 2. Compute the stress intensity due to the Pm and compare it against kSmh. 3. Add the individual normal and shear stress components due to Pmand Pl; compute the resultant stress intensity and compare its value against 1.5kSmh. 4. Add the individual normal and shear stress components due to Pm, Pl, and Q, compute the resultant stress intensity, and compare its value to against 3Smavg. 5. If there is an occasional load as well as a sustained load, these types may be repeated using a k value of 1.2. These criteria can be readily found from Figure 4-130.1 of Appendix 4 of ASME Section VIII, Division 2 and the surrounding text. Note that the primary bending stress term, Pb, is not applicable to the shell stress evaluation, and therefore disappears from the Section VIII, Division 2 requirements. Under the same analogy, the peak stress limit may also be written as: Pl + P b + Q + F < S a The above equation need not be satisfied, provided the elastic limit criteria of AD-160 is met based on the statement explicitly given in Section 5-100, which is cited below: “If the specified operation of the vessel meets all of the conditions of AD-160, no analysis for cyclic operation is required and it may be assumed that the peak stress limit discussed in 4-135 has been satisfied by compliance with the applicable requirements for materials, design, fabrication, testing and inspection of this division.”

17-24





17-25



The equations used in PVElite to qualify the various stress components can be summarized as follows:

Pm(SUS) < Smh Pm(SUS + OCC) < 1.2Smh Pm(SUS) + Pl(SUS) < 1.5Smh Pm(SUS + OCC) + Pl(SUS + OCC) < 1.5(1.2)Smh Pm(SUS + OCC) + Pl(SUS + OCC) + Q(SUS + EXP + OCC) < 1.5(Smc + Smh) If some of the conditions of in ASME VIII Div.2, AD-160 are not satisfied, you probably need to perform the formal fatigue analysis. Peak stresses are required to be calculated or estimated. You may consider using AD-560 “Alternative Rules for Nozzle Design” instead of Article 4-6 “Stresses in Openings for Fatigue Evaluation” to calculate the peak pressure stress for the opening. If all conditions of AD-560.1 through AD-560.6 are satisfied, the stress indices given in Table AD-560.7 may be used. If user says “Yes”, the program will use these pressure stress indices to modify the primary stress due to internal pressure (hoop and longitudinal stresses). For external loads, the highest peak stress are usually localized in fillets and transitions. If the user decides to use WRC107 stress concentration factors (Kn, Kb), the fillet radius between the Vessel and Nozzle is required. (If a reinforcing pad is used, the program assumes the same pad fillet radius.) The program will make a crude approximation and use WRC107 Appendix-B equations (3) and (4) to estimate Kn and Kb. The tension and bending stresses are thus modified using Kn and Kb respectively. The program outputs the local stresses for 4 pairs of points (upper and lower) at the intersection. The user should not direct the program to perform the stress summations. Instead the user should determine which stresses should be added based on locations in order to obtain the peak stress level, then use Appendix-4 & 5 rules and fatigue curves depending on operation cycles. Based on comparisons with finite element analysis, it is known that the top tip of the fillet weld on the nozzle usually experiences the highest peak stress due to external loads. So it is conservative to add all the peak stresses after including both pressure stress indices and concentration factors. Note that the stress summation may ONLY be used to check stress intensities, not stress levels. You need the peak stress level to perform fatigue analysis. The current stress summation routine does not compare stress level with fatigue allowables per Appendix-5. However, you may find the stress summation results useful to compare the combined effect due to the stress concentration factor and pressure stress indices.

17-26



Finite Element Analysis (FEA):

Finite Element Analysis (FEA): Using the interface within PVElite and Paulin Research Group’s NozzlePro program, users can perform FEA and WRC 107 within the same module. FEA can model more types of vessel and nozzle geometries. The FEA program generates graphical results showing various ASME stress states. We will briefly describe the important results: 1. ASME overstressed areas are reported. A sample printout is shown here, ASME Overstressed Areas Pad Edge Weld for Nozzle Pl 20,116 psi

1.5(k)Smh 18,000 psi

1 Primary Membrane Load Case 2 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2

111%

2. Next report is the Highest Primary Stress Report that outlines the stresses at critical location like the nozzle-shell junction and the edge of the pad. 3. Highest Secondary and fatigue Stress Reports are provided. 4. Next, the program lists Nozzle Stress Intensification factors for use in a beam type pipe stress analysis program such as CAESAR II. 5. The NozzlePro program computes the maximum individual allowable loads and simultaneously acting allowable loads. Both Primary and Secondary loads are reported. A typical report is listed here, Allowable Loads SECONDARY Load Type (Range): Axial Force Inplane Moment Outplane Moment Torsional Moment Pressure

(lb. (in. (in. (in. (psi

Maximum Conservative Realistic Individual Simultaneous Simultaneous Occurring Occurring Occurring ) 398030. 120631. 180946. lb.) 5306513. 1137199. 2412363. lb.) 3358105. 719650. 1526608. lb.) 2343568. 710264. 1065396. ) 344. 111. 111.

(lb. (in. (in. (in. (psi

Maximum Conservative Realistic Individual Simultaneous Simultaneous Occurring Occurring Occurring ) 618455. 178300. 267450. lb.) 5998639. 1222872. 2594104. lb.) 5458219. 1182725. 2508939. lb.) 2938301. 847110. 1270665. ) 422. 111. 111.

PRIMARY Load Type: Axial Force Inplane Moment Outplane Moment Torsional Moment Pressure

The conservative simultaneous loads will produce stresses that are approximately 60-to70% of the allowable. The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously, they produce stresses that are closer to 100% of the allowable. The Maximum Individual Occurring Primary Pressure can be taken as a finite element calculation of the MAWP for the nozzle.


17-27

Finite Element Analysis (FEA):


6. Nozzle-Shell junction flexibilities are also available. These flexibilities can be used to accurately model the flexibility of the junction and can be included in the pipe stress program that is used to model the piping system attaching to the nozzle.

Thus, users will have a choice of performing either an WRC 107 or a finite element analysis from within the same module, without redundant input. As with any finite element program users should visually check the finite element mesh for errors and make sure the FEA results make sense for stress analysis perspective. Technical queries regarding FEA results should be addressed to Paulin Research Group (www.paulin.com).

17-28



Examples

Examples The example problem listed below is a comparison problem in our QA series. It can be found in the file CHECKS. COADE Engineering Software WRC 107 Examples including WRC107 Summations PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON FileName : WRC107

----------------------------------- Page 1

WRC107 Analysis : OLD FILE

Input Echo, WRC107 Number

ITEM:

1,

1,

03:10pm,

05/18/98

Description: OLD FILE

Diameter Basis for Vessel

VBASIS

OD

Cylindrical or Spherical Vessel

CYLSPH

Cylindrical


CAS

.0000

in.

Vessel Diameter

DV

120.000

in.

Vessel Thickness

TV

.625

in.

Attachment Type

TYPE

Round

WRC107 Attachment Classification

HOLSOL

Solid


NBASIS

OD


CAN

.0000

in.

Nozzle Diameter

DN

12.750

in.

Nozzle Thickness

TN

.375

in.


DP

275.00

P

-31128.00

lb.

Circumferential Shear

VC

32.00

lb.

Longitudinal Shear

VL

1389.00

lb.

Circumferential Moment

MC

127.00

ft.lb.

Longitudinal Moment

ML

4235.00

ft.lb.

Torsional Moment

MT

65.00

ft.lb.

Radial Load

Use Interactive Control WRC107 Version

INTACT No VERSION March 1979 ( B1 & B2 )

Include WRC107 SIF(Kn,Kb)—concentration factors

No

Include Pressure Stress Indices per Div. 2

No

Dimensionless Parameters used :

psig

Gamma =

95.50

Dimensionless Loads for Cylindrical Shells ------------------------------------------------------Curves read for

Beta

Figure

Value

-----------------------------------------------------N(PHI) / ( P/Rm )

.093

4C

M(PHI) / ( P )

.093

2C1

N(PHI) / ( MC/(Rm**2 * Beta) )

.093

3A

M(PHI) / ( MC/(Rm

14.994 .059 3.449

* Beta) )

.093

1A

.085

N(PHI) / ( ML/(Rm**2 * Beta) )

.093

3B

10.793

M(PHI) / ( ML/(Rm

.093

1B

.035

.093

3C

12.082

N(x)


/ ( P/Rm )

* Beta) )

17-29

Examples


M(x)

/ ( P )

.093

1C1

N(x)

/ ( MC/(Rm**2 * Beta) )

.093

4A

M(x)

/ ( MC/(Rm

* Beta) )

.093

2A

.045

N(x)

/ ( ML/(Rm**2 * Beta) )

.093

4B

3.511

M(x)

/ ( ML/(Rm

.093

2B

.051

N(PHI) / ( P/Rm )

.093

3C

12.082

M(PHI) / ( P )

.093

1C

.094

.093

1B1

.035

* Beta) )

.097 5.631

STRESS POINTS C & D (MARCH 1979)

M(PHI) / ( ML/(Rm

* BETA) )

N(x)

/ ( P/Rm )

.093

4C

14.994

M(x)

/ ( P )

.093

2C

.060

M(x)

/ ( ML/(Rm

.093

2B1

.052

* BETA) )

Stress Concentration Factors Kn = 1.00,

Kb = 1.00

Stresses in the Vessel at the Nozzle Junction --------------------------------------------------------------------| Type of

Stress Values at

|

(psi

)

--------------------------------------------------------------------Stress

Load|

Au

Al

Bu

Bl

Cu

Cl

Du

Dl

--------------------------------------------------------------------Circ. Memb. DP |

25988

26263

25988

26263

25988

26263

25988

26263

Circ. Memb. P

|

12511

12511

12511

12511

10081

10081

10081

10081

Circ. Bend. P

|

28242 -28242

28242 -28242

44865 -44865

44865 -44865

Circ. Memb. MC |

0

0

0

0

-25

-25

25

25

Circ. Bend. MC |

0

0

0

0

-358

358

358

-358

Circ. Memb. ML |

-2635

-2635

2635

2635

0

0

0

0

Circ. Bend. ML |

-4938

4938

4938

-4938

0

0

0

0

59168

12835

74314

8229

80551

-8188

81317

-8854

| Tot. Circ. Str.|

--------------------------------------------------------------------Long. Memb. DP |

12994

12994

12994

12994

12994

12994

12994

12994

Long. Memb. P

|

10081

10081

10081

10081

12511

12511

12511

12511

Long. Bend. P

|

46473 -46473

46473 -46473

28748 -28748

28748 -28748

Long. Memb. MC |

0

0

0

0

-41

-41

41

41

Long. Bend. MC |

0

0

0

0

-190

190

190

-190

Long. Memb. ML |

-857

-857

857

857

0

0

0

0

Long. Bend. ML |

-7325

7325

7325

-7325

0

0

0

0

77730 -29866

54022

-3094

54484

-3392

| Tot. Long. Str.|

61366 -16930

--------------------------------------------------------------------Shear VC |

2

2

-2

-2

0

0

0

0

Shear VL |

0

0

0

0

-110

-110

110

110

Shear MT |

4

Tot. Shear|

4 6

4 6

4 2

4 2

-106

4 -106

4

4

114

114

--------------------------------------------------------------------Str. Int. |

61366

29765

77730

38095

80551

8190

81317

8856

--------------------------------------------------------------------The PVElite Program, (C) 1989-1998 by COADE Engineering Software

17-30



Examples

The following example problem goes through a comprehensive local stress analysis of a vessel/nozzle using WRC107 and ASME Section VIII, Division 2 criteria.

WRC 107 Example Problem

After confirming that the geometry guidelines per WRC 107 are met, the actual preparation of the WRC 107 calculation input can now begin. One of the most important steps in the WRC 107 procedure is to identify the correlation between the stress output global coordinates and the WRC 107 local axes. The PVElite program performs this conversion automatically. The user will, however, have to identify the vectors defining the vessel as well as the nozzle centerline. The following figure is provided to illustrate the definition of the direction vectors of the vessel and the nozzle.


17-31

Examples


Converting Forces/Moments in CAESAR II Global Coordinates to WRC 107 Local Axes

Notice that in order to define a vessel direction vector, the user first needs to designate the output data points (A->D) as defined by the WRC 107 Bulletin. Note that the line between data points B and A defines the vessel centerline (except for nozzles on heads, where the vessel centerline will have to be defined along a direction which is perpendicular to that of the nozzle). Since, in the vessel/nozzle configuration shown, point A is assigned to the bottom of the nozzle, the vessel direction vector can be written as (0.0, -1.0, 0.0), while the nozzle direction vector is (1.0, 0.0, 0.0). The nozzle direction vector is always defined as the vector pointing from the vessel nozzle connection to the centerline of vessel. For different load cases (SUS, EXP, OCC), the restraint loads (forces and moments) can be obtained from typical piping stress analysis program like CAESAR II. These loads reflect the action of the piping on the vessel. The following is the example loads:

17-32



Examples

Summary of Restraint Loads on the Vessel Load

X (lb)

Y (lb)

MX (ft.lb)

Z (lb)

MY (ft.lb)

MZ (ft.lb)

Sustained

-26

-1389

32

-65

127

4235

Expansion

8573

23715

-5866

31659

-5414

-52583

Moment T(-X)

Moment MC(+Y)

Moment ML(+Z)

WRC 107 Local Components Load

Force P(+X)

Force VL(-Y)

Force VC(+Z)

Sustained

-26

1389

32

65

127

4235

Expansion

8573

-23715

-5866

-31659

-5414

-52583

Restraint Report from CAESAR II

The total sustained axial load on the nozzle may not be reflected in the restraint report. A pressure thrust load will contribute an additional axial load to the nozzle. The pressure thrust force always tends to push the nozzle away from the vessel. For example, with a pressure of 275 psi over the inside area of the 12 inch pipe, the total P load becomes: P

= -26 - P*A = -26 - 275p (122) / 4 = -31,128 The P load may be adjusted automatically for the input by PVElite’s WRC 107 module, if the user so requests. FileName : WRC107

--------------------------------------- Page 1

WRC107 Analysis : CII COMPARISON Input Echo, WRC107 Number

2,

ITEM:

2,

03:10pm,

05/18/98

Description: CII COMPARISON

Diameter Basis for Vessel

VBASIS

OD

Cylindrical or Spherical Vessel

CYLSPH

Cylindrical


CAS

.0000

in.

Vessel Diameter

DV

120.000

in.

Vessel Thickness

TV

.625

in.

Attachment Type

TYPE

Round

WRC107 Attachment Classification

HOLSOL

Solid


NBASIS

OD


CAN

.0000

in.

Nozzle Diameter

DN

12.750

in.

Nozzle Thickness

TN

.375

in.

Vessel Centerline Direction Cosine

VX

.000


VY

-1.000


17-33

Examples



VZ

.000

Nozzle Centerline Direction Cosine

NX

1.000


NY

.000


NZ

.000

Cold S.I. Allowable

Smc

20000.00

psi

Hot

Smh

20000.00

psi

S.I. Allowable

Global Force (SUS)

Fx

-26.00

lb.

Global Force (SUS)

Fy

-1389.00

lb.

Global Force (SUS)

Fz

32.00

lb.

Global Moment (SUS)

Mx

-65.00

ft.lb.

Global Moment (SUS)

My

127.00

ft.lb.

Global Moment (SUS)

Mz

4235.00

ft.lb.

P

275.00

Internal Pressure (SUS) Include Pressure Thrust

psig

Yes

Global Force (EXP)

Fx

8573.00

lb.

Global Force (EXP)

Fy

23715.00

lb.

Global Force (EXP)

Fz

-5866.00

lb.

Global Moment (EXP)

Mx

31659.00

ft.lb.

Global Moment (EXP)

My

-5414.00

ft.lb.

Global Moment (EXP)

Mz

-52583.00

ft.lb.

Use Interactive Control

INTACT

WRC107 Version

VERSION

No March 1979 ( B1 & B2 )

Include WRC107 SIF(Kn,Kb)—concentration factors

No

Include Pressure Stress Indices per Div. 2

No

WRC 107 Stress Calculation for SUStained loads: Radial Load

P

-31127.77

lb.


VC

32.00

lb.

Longitudinal Shear

VL

1389.00

lb.


MC

127.00

ft.lb.

Longitudinal Moment

ML

4235.00

ft.lb.

Torsional Moment

MT

65.00

ft.lb.


Gamma =

95.50

Dimensionless Loads for Cylindrical Shells ---------------------------------------------------------------------------------------------Curves read for

Beta

Figure

Value

----------------------------------------------------------------------------------------------

17-34

N(PHI) / ( P/Rm )

.093

4C

M(PHI) / ( P )

.093

2C1


.093

3A

M(PHI) / ( MC/(Rm

14.994 .059 3.449

* Beta) )

.093

1A

.085


.093

3B

10.793

M(PHI) / ( ML/(Rm

.093

1B

.035

12.082

* Beta) )

N(x)

/ ( P/Rm )

.093

3C

M(x)

/ ( P )

.093

1C1

N(x)

/ ( MC/(Rm**2 * Beta) )

.093

4A

5.631

M(x)

/ ( MC/(Rm

.093

2A

.045

* Beta) )

.097



Examples

N(x)

/ ( ML/(Rm**2 * Beta) )

.093

4B

3.511

M(x)

/ ( ML/(Rm

.093

2B

.051

N(PHI) / ( P/Rm )

.093

3C

12.082

M(PHI) / ( P )

.093

1C

.094

.093

1B1

.035

* Beta) )


M(PHI) / ( ML/(Rm

* BETA) )

N(x)

/ ( P/Rm )

.093

4C

14.994

M(x)

/ ( P )

.093

2C

.060

M(x)

/ ( ML/(Rm

.093

2B1

.052

* BETA) )


Kb = 1.00

Stresses in the Vessel at the Nozzle Junction ------------------------------------------------------------------| Type of

Stress Values at

|

(psi

)

-------------------------------------------------------------------------------------Stress

Load|

Au

Al

Bu

Bl

Cu

Cl

Du

Dl

------------------------------------------------------------------Circ. Memb. P

12510

Circ. Bend. P

28242 -28242

12510

12510

12510

10081

28242 -28242

10081

10081

44865 -44865

10081

44865 -44865

Circ. Memb. MC

0

0

0

0

-25

-25

25

25

Circ. Bend. MC

0

0

0

0

-358

358

358

-358

Circ. Memb. ML

-2635

-2635

2635

2635

0

0

0

0

Circ. Bend. ML

-4938

4938

4938

-4938

0

0

0

0

Tot. Circ. Str.

33179 -13429

48325 -18035

54563 -34451

55329 -35117

-----------------------------------------------------------------Long. Memb. P

10081

Long. Bend. P

46473 -46473

10081

10081

10081

12510

46473 -46473

12510

12510

28748 -28748

12510

28748 -28748

Long. Memb. MC

0

0

0

0

-41

-41

41

41

Long. Bend. MC

0

0

0

0

-190

190

190

-190

Long. Memb. ML

-857

-857

857

857

0

0

0

0

Long. Bend. ML

-7325

7325

7325

-7325

0

0

0

0

Tot. Long. Str.

48372 -29924

64736 -42860

41027 -16089

41489 -16387

------------------------------------------------------------------Shear VC |

2

2

-2

-2

0

0

0

0

Shear VL |

0

0

0

0

-110

-110

110

110

Shear MT |

4

4

4

4

4

4

4

4

6

6

2

2

-106

-106

114

114

| Tot. Shear|

-------------------------------------------------------------------Str. Int. |

48372

29924

64736

42860

54563

34451

55329

35117

---------------------------------------------------------------------

WRC 107 Stress Calculation for EXPansion loads: Radial Load

P

8573.00

lb.


VC

-5866.00

lb.

Longitudinal Shear

VL

-23715.00

lb.


MC

-5414.00

ft.lb.

Longitudinal Moment

ML

-52583.00

ft.lb.


17-35

Examples


Torsional Moment

MT


Gamma =

-31659.00

ft.lb.

95.50

Dimensionless Loads for Cylindrical Shells ------------------------------------------------------Curves read for

Beta

Figure

Value

------------------------------------------------------N(PHI) / ( P/Rm )

.093

4C

M(PHI) / ( P )

.093

2C1

14.994


.093

3A

M(PHI) / ( MC/(Rm

.059 3.449

* Beta) )

.093

1A

.085


.093

3B

10.793

M(PHI) / ( ML/(Rm

.093

1B

.035

12.082

* Beta) )

N(x)

/ ( P/Rm )

.093

3C

M(x)

/ ( P )

.093

1C1

N(x)

/ ( MC/(Rm**2 * Beta) )

.093

4A

M(x)

/ ( MC/(Rm

* Beta) )

.093

2A

.045

N(x)

/ ( ML/(Rm**2 * Beta) )

.093

4B

3.511

M(x)

/ ( ML/(Rm

.093

2B

.051

N(PHI) / ( P/Rm )

.093

3C

12.082

M(PHI) / ( P )

.093

1C

.094

.093

1B1

.035

* Beta) )

.097 5.631


M(PHI) / ( ML/(Rm

* BETA) )

N(x)

/ ( P/Rm )

.093

4C

14.994

M(x)

/ ( P )

.093

2C

.060

M(x)

/ ( ML/(Rm

.093

2B1

.052

* BETA) )


Kb = 1.00

Stresses in the Vessel at the Nozzle Junction -------------------------------------------------------------------| Type of

Stress Values at

|

(psi

)

-------------------------------------------------------------------Stress

Load|

Au

Al

Bu

Bl

Cu

Cl

Du

Dl

-------------------------------------------------------------------Circ. Memb. P

-3445

-3445

-3445

Circ. Bend. P

-7778

7778

-7778

Circ. Memb. MC

0

0

0

0

Circ. Bend. MC

0

0

0

0

Circ. Memb. ML

32727

Circ. Bend. ML

61315 -61315 -61315

Tot. Circ. Str.|

-3445

-2776

-2776

7778 -12356 1076

32727 -32727 -32727 61315

82819 -24255-105265

32921

-2776

-2776

12356 -12356

12356

1076

-1076

-1076

15281 -15281 -15281

15281

0

0

0

0

0

0

0

0

1225

-4625 -31489

23785

-------------------------------------------------------------------Long. Memb. P

|

Long. Bend. P

| -12799

Long. Memb. MC |

17-36

-2776

0

-2776

-2776

-2776

-3445

-3445

-3445

12799 -12799

12799

-7917

7917

-7917

-3445 7917

0

0

0

1758

1758

-1758

-1758

0

0

0

8120

-8120

-8120

8120

10647 -10647 -10647

0

0

0

0

0

0

0

0

Long. Bend. MC |

0

Long. Memb. ML |

10647

Long. Bend. ML |

90951 -90951 -90951

90951



Examples

| Tot. Long. Str.|

86023 -70281-117173

90327

-1484

-1890 -21240

10834

-------------------------------------------------------------------Shear VC |

-468

-468

468

468

0

0

0

0

Shear VL |

0

0

0

0

1894

1894

-1894

-1894

Shear MT |

-2380

-2380

-2380

-2380

-2380

-2380

-2380

-2380

-2848

-2848

-1912

-1912

-486

-486

-4274

-4274

| Tot. Shear|

-------------------------------------------------------------------Str. Int. |

87688

70456 117472

90390

2878

4708

33037

25068

--------------------------------------------------------------------

WRC 107 Stress Summations: Vessel Stress Summation @ Nozzle Junction -------------------------------------------------------------------Type of Stress Int.

|

Stress Values at

|

(psi)

-------------------------------------------------------------------Location

Au

Al

Bu

Bl

Cu

Cl

Du

Dl

-------------------------------------------------------------------Circ. Pm (SUS)

25988

26263

25988

26263

25988

26263

25988

26263

Circ. Pl (SUS)

9875

9875

15145

15145

10056

10056

10106

10106

Circ. Q

(SUS)

23304 -23304

33180 -33180

Circ. Q

(EXP)

82819 -24255-105265

32921

44507 -44507 1225

45223 -45223

-4625 -31489

23785

-------------------------------------------------------------------Long. Pm (SUS)

12994

12994

12994

12994

12994

12994

12994

12994

Long. Pl (SUS)

9224

9224

10938

10938

12469

12469

12551

12551

Long. Q

(SUS)

39148 -39148

53798 -53798

Long. Q

(EXP)

86023 -70281-117173

90327

28558 -28558 -1484

28938 -28938

-1890 -21240

10834

-------------------------------------------------------------------Shear Pm (SUS)

0

0

0

0

0

0

0

0

Shear Pl (SUS)

2

2

-2

-2

-110

-110

110

110

Shear Q

(SUS)

4

4

4

4

4

4

4

4

Shear Q

(EXP)

-2848

-2848

-1912

-1912

-486

-486

-4274

-4274

-------------------------------------------------------------------Pm (SUS)

25988

26263

25988

26263

25988

26263

25988

26263

-------------------------------------------------------------------Pm+Pl (SUS)

35863

36138

41133

41408

36045

36320

36095

36370

-------------------------------------------------------------------Pm+Pl+Q (Total) 148608

87317

39852

60648

81787

12857

50812

16783

--------------------------------------------------------------------

-------------------------------------------------------------------Type of Stress Int.

|

Max. S.I.

|

S.I. Allowable (psi

|

)

Result

|

--------------------------------------------------------------------Pm (SUS)

|

26263

20000

|

Failed

Pm+Pl (SUS)

|

41408

30000

|

Failed

Pm+Pl+Q (TOTAL)|

148608

60000

|

Failed

--------------------------------------------------------------------



17-37

Examples

17-38




&KDSWHU The Leg & Lug Module

Introduction This chapter discusses the Leg & Lug module of the PVElite program. To use the Leg & Lug module the current analysis type should be Leg & Lug. The current analysis type appears on the main menu of PVElite. The basic capabilities of the Leg & Lug module are to analyze structural members (legs), support lugs and lifting lugs. The basic required information for each of these analysis types is shown below. •

Vessel design internal pressure

•

Design temperature for the attachment

•

Vessel outside diameter

•

Weight of vessel operating and dry

•

Vessel dimensions

•

Additional horizontal force on vessel

•

Location of horizontal force above grade

The Leg & Lug Module

18-1

Discussion of Input


Discussion of Input Main Input Fields The design temperature for the attachment is used to compute the material properties for attachment being analyzed. In most cases the actual attachment temperature will be different from the vessel design temperature. The controlling stress for support lug and vessel leg calculations is the yield stress. The material yield stress can be looked up in the tables in ASME Section II Part D. The weight of the vessel should be the weight of the vessel while it is operating. This should include operating fluid, trays, insulation etc. Support lug calculations should use the same loading conditions. However since vessels are typically lifted “dry” the empty weight of the vessel should be used when performing lifting lug calculations. There is a separate field for lifting weight of the vessel. Item Number

Enter the a positive integer value (i.e. 1) in this cell. This number will not be used in the analysis but will be displayed on the screen while PVElite is executing. Vessel Description

Enter a meaningful descriptor for this analysis. This will be displayed on the screen and in the output reports. An example might be Cryogen - 1. A combination of letters and numbers up to 15 may be used. Design Pressure

Enter the design pressure that the vessel will be operating at. This value will not be used by the program, however, the pressure will be an input item for WRC 107. This is also a good number to have for information purposes. Design Temperature of Attachment

The temperature entered in this cell should correspond to the temperature of the attachment in question. It would be reasonable to assume that vessel legs are much cooler than the actual metal temperature of the pressure vessel. The controlling stress for leg and support lug design is the yield stress of the material at the leg/lug temperature. If the attachment is not at ambient, enter the yield stress at that temperature. This value available in ASME Section II Part D. Alternately, the cold yield stress may be multiplied by the ratio of the hot allowable stress to the cold allowable stress. This should be acceptable in most cases. Outside Diameter of Vessel

Enter the outside diameter of the vessel to which the supports are attached. Any factors such as external corrosion should be accounted for at this time. PVElite will assume the vessel is one diameter from the top to the bottom of the vessel. Shell Thickness

Enter the shell thickness. This input is used only in the case of a support lug with a full reinforcement ring. Shell thickness is required to compute the Area and Moment of Inertia of the shell-ring junction.

18-2



Discussion of Input


Enter the shell corrosion allowance. This input, along with the shell thickness is used only in the case of a support lug with a full reinforcement ring. Shell thickness is required to compute the area and Moment of Inertia of the shell-ring junction. Tangent to Tangent Length of Vessel

Enter the vessel length from tangent to tangent. This value in combination with the next input parameter, will be used to compute the height of the top of the tower above grade. Knowing the elevation at the top, the wind pressure can be computed for the support lug and leg calculations. Shell Material

Click the Material Database button to look up a material name from the Material Database. Click the Material Edit Properties button to change the properties of the selected material. If you cannot find the material you need in the Material Database, you can add its specification and properties by selecting Tools, Edit/Add Materials. Type of Analysis

Use the table below to determine the appropriate analysis type:

Analysis Type

Description

Support Lug

If the vessel rests on support lugs select this option. The program prompts you to enter all information necessary to determine the stress in these types of supporting attachments.

Vessel Leg

If the vessel rests on vessel legs select this option. The program prompts you to enter all information necessary to perform an AISC Unity Check on the vessel legs. This option also allows you to design the leg, baseplate and anchor bolts.

Lifting Lug

If the vessel is lifted by lug type attachments select this option. The program prompts you to enter information pertaining to the lifting lugs.

Trunnion

If the vessel is lifted by a trunnion select this option. The program prompts you to enter information pertaining to the trunnion design. Note: You can also perform a local stress analysis on the trunnion per WRC 107 methods.

Analyze Baseplate

Check this box for designing the baseplate and Anchor Bolts per Moss and Bednar. Additional Horizontal Force on Vessel

Enter the additional horizontal force exerted on the vessel due to external loads. An example of such would be the reaction imposed by the thermal expansion of a piping system. For more information see Figure 18A - External Force Illustration.


18-3

Discussion of Input


A Vessel on Legs

A Vessel on Lugs

Figure 18a - External Force Illustration

Location of Horizontal Force on Vessel

Enter the location of the external force above the base point. For more information see Figure 18A - External Force Illustration. Operating Weight of Vessel (total vertical load)

Enter the total weight of the vessel in this cell. This weight should include all operating fluids, equipment loads, and other equipment attached to the vessel. Height of Bottom Tangent Above Grade

Enter the distance from the ground to the bottom tangent of the vessel. If you are performing a leg analysis this distance should be equal to the length of the legs. This value will be used along with the tangent to tangent length to determine the centroid where the wind loads and seismic shear loads are applied. These horizontal shear forces cause bending around the legs and support lugs. For more information see Figure 18A-External Force Illustration. Perform Lifting Lug Analysis

If a vessel is to be lifted by lug type attachments check this field. Prompts will appear asking for information pertaining to the lifting lugs. Occasional Load Factor (AISC A5.2)

With many types of construction codes and occasional load factor can be used to increase the allowable stress for an event that is considered occasional in nature. Such occasional loads are Wind, Seismic, and the lifting of a vessel. The occasional load factor will be multiplied by the other terms in the allowable stress equation to get the overall allowable. If you do not wish to take credit for such an increase in the allowable, enter a 1 in this field. The defaults is 1.33. Apply Wind Loads to Vessel

If you wish to enter wind loads on your vessel check this field. You will then be prompted for the necessary parameters to compute the wind pressure on the vessel.

18-4



Discussion of Input

Apply Seismic Loads to Vessel

If you wish to have a seismic analysis check this field. If you do so, the seismic zone or seismic factor Cs will be needed.


18-5

Pop-Up Input Fields


Pop-Up Input Fields Force Coefficient

Enter the force coefficient for the vessel here. The acceptable range of input is between 0.5 and 1.2. This can be seen as Table 12 in ANSI A58.1. For ASCE 7-95, refer to p32-33. Additional Area

The user may wish to consider the additional area exposed to the wind from piping, platforms, insulation etc. PVElite will automatically compute an effective diameter with the input diameter known. Wind Pressure on Vessel

If your vessel specification calls for a constant wind pressure design, and you know what that pressure is, enter it here. Most Wind Design codes have minimum wind pressure requirements, so check those carefully. The wind pressure will be multiplied by the area calculated by the program to get a shear load and a bending moment. If you enter a positive number here, PVElite will use this number regardless of the information in the following cells. Importance Factor ( I )

Enter the value for the importance factor here. The importance factor accounts for the degree of hazard to life and property. If the vessel is 100 miles ( 160 kilometers ) from the hurricane oceanline enter a 1.00. If the vessel is at the hurricane oceanline enter 1.05. Values up to 1.11 are acceptable here. Refer to ASCE #7 and ANSI 58.1 for more information on the importance factor (Table 1 and Table 5 in ANSI A58.1). For ASCE 7-95, refer to Table 6-2). Basic Wind Speed

Enter the basic wind speed which the vessel will be subject to. Positive values will be accepted. A minimum value of 70 miles per hour is recommended. Wind Exposure

Enter an integer here for the ASCE 7 wind exposure factor.

18-6

Exposure (A)

- “Large city centers with at least 50% of the buildings having a height in excess of 70 ft.”

Exposure (B)

- “Urban and suburban areas, wooded areas, or other terrain with numerous closely spaced obstructions having the size of single family dwellings.”

Exposure (C)

- “Open terrain with scattered obstructions having heights generally less than 30 feet. This category includes flat, open country and grasslands.”

Exposure (D)

- “Flat, unobstructed costal areas directly exposed to wind flowing over large bodies of water.”



Pop-Up Input Fields

Note that most petrochemical sites use Exposure C. Use ASCE 7-95 Code

If you choose to use ASCE 7-95 code, check this field. Then enter the following cells. Type of Hill

Select the type of hill. See ASCE 7-95 Fig. 6-2 for details. •

None

•

2-D Ridge

•

2-D Escarpment

•

3-D Axisym Hill

Height of Hill or Escarpment (H)

Enter height of hill or escarpment relative to the upwind terrain. See ASCE 7-95 Fig. 6-2 for detail. Distance to Site (x)

Enter distance (upwind or downwind) from the crest to the building site. See ASCE 7-95. Distance to Crest (Lh)

Enter distance upwind of crest to where the difference in ground elevation is half the height of hill or escarpment. See ASCE 7-95 Fig. 6-2 for detail. Natural Frequency for the Structure (Fn) — Optional (Hz)

Enter the natural frequency for the structure. The program will use ASCE 7-95 part 6.6 category III if Fn < 1.0 Hz or TANTAN/OD > 4.0. Damping Ratio (beta) — optional

Enter the damping ratio for the structure if you like to use ASCE 7-95 part 6.6 category III (if Fn < 1.0 Hz or TANTAN/OD > 4.0). Seismic Zone

Enter the seismic zone in which your vessel is operating. The seismic zones are pictured in ASCE #7. A value of 0 will slightly increase the reaction force. A zone entry of 4 will produce the highest loads. User-Entered Seismic Zone Factor CS

When you enter a valid seismic zone and leave this field blank or 0, PVElite will look the seismic zone factor up from an applicable table. This number is then used in conjunction with the operating weight of the vessel to compute the forces which act on the supports. If for any reason the table value of Cs is unacceptable, entry of a non-zero value will cause this to be used in lieu of the table value. This might occur if the building code in your project specifications is different from the one used by PVElite.


18-7

Vessel Leg Input


Vessel Leg Input The number of vessel legs must be between 3 and 16. The program computes the number of legs for bending and shear of the vessel. PVElite must have a valid material from which to determine material properties. The material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Currently there are 929 structural shapes in AISC database. PVElite is intended to perform unity checks on I-beam and angle type sections. AISC’s method for computing unity checks for angle sections is rather complicated when compared to the corresponding method used for “I” type sections. Each beam section has a strong and weak orientation. If the beam is attached such that the tangent to the vessel is parallel to the beam’s strong axis this designation is considered strong. If the designation is not strong it must be weak. If the legs are cross braced bending stresses are significantly reduced. The end fixity condition is assumed to be 1.0. Number of Legs

Enter the number of legs attached to the vessel. This number must be greater than or equal to 3 and less than 16. PVElite will determine the effective number of legs for bending and shear of the vessel. Length of Legs

Enter the distance from the bottom leg support point to the attachment point on the vessel. This length term is used in determining the legs resistance to bending. Long legs are more likely to buckle than shorter legs. The distance of the tangent line of the vessel above grade should always be equal to the length of the legs. If they are not the same PVElite will use the maximum of the two when determining the wind pressure and the location of the centroid. Effective Leg End Condition Factor K (used in Kl/r)

Enter in the value of K used as the effective end condition. This value usually ranges from 0.2 to 2.10. For design of pressure vessel legs a value of 1.0 is commonly used. If your design specs call out for a different value enter it here. Material Specification for Legs

Enter the material that the legs are made of. An example of a of a common material is SA516 70. To properly initialize the material, type its name on this line even if the default is shown. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu.

18-8



Vessel Leg Input

Leg Allowable Stress at Design Temperature

The leg allowable stress is not used to check structural steel. The yield stress at the design temperature is used. Leg Allowable Stress at Ambient Temperature

The leg allowable stress is not used to check structural steel. The yield stress at the operating temperature is used. AISC Member Designation

Enter the shape type of the leg on which the vessel is sitting. A complete list of shapes can be found in the AISC structural steel handbook. All material shape information is current with the latest AISC code standard. An example of a shape type may be W8X40 or W36X300. A 2 by 1/4 inch angle section would have the designation L2X2X0.2500. This reference must be exact. If your design incorporates pipe legs, check the pipe-leg selection box and fill in the ID and the OD of the pipe leg. Orientation to the Vessel

Each I - beam and channel has a strong and weak orientation. This means that these sections are more easily bent around one as opposed to the other. If the member is attached such that the tangent to the vessel is parallel to the beams strong axis select the strong option, otherwise select the weak option. If the member is an angle and it is attached to with one leg welded to the vessel or one flat welded to the vessel, select strong. If both legs are welded to the vessel select diagonal. Are the Legs Cross-Braced

If the legs are cross braced check this field. Cross bracing effectively stiffens the legs. Thus they will experience a minimum of bending stress. Are the Legs Pipe Legs

Check this box to activate the pipe ID and OD. Pipe Legs Inside Diameter

Enter the inside diameter of the pipe leg (as determined by which cell you are entering data for) that is attached to the vessel. You must account for any corrosion allowance to the Inner or Outer Diameter when entering this value. Please verify that the inside diameter


18-9

Leg Results


Leg Results When a leg analysis is performed PVElite reads all of the data out of the structural database (AISC89.BIN). The resulting leg loads are compared to the allowable leg compression loads as outlined in AISC paragraph 1.5.1.3. Either the Kl/r > Cc or Kl/r < Cc formula will be shown as appropriate. The combination of stresses due to bending and compression will be compared to the allowable per AISC 1.6.1. This is generally termed the AISC unity check. If the result is greater than 1.0 the member has failed.

18-10



Support Lug Input

Support Lug Input If the number of support lugs to be analyzed is between 3 and 16. PVElite assumes that each support lug has two gussets equally spaced about a bolt hole. The distance between gussets is used to determine the bending stress in the lug bottom plate. The lug bottom plate is analyzed as a beam on simple supports, where the support spacing is the gusset spacing. The allowable stress in bending is 66 percent of the yield stress, per the AISC manual. In addition, the stress in the gusset is one half of the lug force divided by the gusset area. This compression is compared to the AISC compression allowable. Usually when analyzing stresses in the lug plate the stresses in the wall of the vessel at the attachment location should be checked. The support lug portion of the program will print additional forces and moments for WRC107 analysis. This information can then be used for local stress calculations according to the WRC107/297 method. Support Lug Reinforcing Ring ( None, Girder Ring )

Select girder ring if the support lugs are reinforced with rings. If there are no stiffening rings for the support lugs, select none. Number of Support Lugs

Enter the number of support lugs on which the vessel is supported. This number must be greater than 3 and less than 16. The program cannot calculate the lug stresses for 2 support lugs because PVElite does not anticipate the bending reactions at the side lugs, which are necessary for such a support system to work. Location of Support Lugs Above Grade

Enter the height above grade to which the support lugs are attached to the vessel. This is used to determine the reaction load on each support lug. Distance from Vessel OD to Support Contact Point

Enter the distance from the outside wall of the vessel to where the support lug attaches/ rests on/to the supporting member. This distance should be as short as possible to minimize bending on the support lug and the vessel wall. Material Specification for Support Lugs

Enter the material that the lugs are made of. An example of a of a common material is SA516 70. To properly initialize the material, type its name on this line even if the default is shown. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Radial Width of Bottom Support Lug Plate

The radial width of the support lug is how far from the vessel wall the plate extends. For more information see Figure 18B - Geometry for the Leg & Lug Module. Lug Allowable Stress at Operating Temperature

The lug allowable stress is not used as a failure comparison. The yield stress at the operating temperature is used.


18-11

Support Lug Input


Lug Allowable Stress at Ambient Temperature

The lug allowable stress is not used as a failure comparison. The yield stress at the operating temperature is used. Circumferential Length of Bottom Support Lug Plate

Enter the distance measured along the vessel wall that the support lug plate extends. Thickness of the Bottom Support Lug Plate

Enter the thickness of the plate on which the gussets rest. The bottom support plate is analyzed as a beam on simple supports where the support spacing is the distance between gussets. The allowable stress is 66% of the yield stress per the AISC steel construction manual. Distance Between Gussets

Enter the gusset spacing in this cell. PVElite assumes that support lugs have two gussets, equally spaced about a bolt hole (support point). Mean Width of Gusset Plate

Enter the average width of the gusset plate. The width is radially from the OD of the vessel. If the top and bottom of the gussets are different widths, add them up and divide the result by 2. For more information see Figure 18B - Geometry for the Leg & Lug Module. Height of Gusset Plate

Enter the distance along the axis of the vessel that the gusset plate extends. This length will be used in the AISC formulation to determine the stress in the gussets. For more information see Figure 18B - Geometry for the Leg & Lug Module. Thickness of Gusset Plate

Enter the thickness of the gusset plate. For more information see Figure 18B - Geometry for the Leg & Lug Module. Radial Width of Top Bar Plate or Top Ring

The radial width of the top bar/ring is how far from the vessel wall the top plate/ring extends. For more information see Figure 18B - Geometry for the Leg & Lug Module.

Note

If there is no top bar/ring, enter the top width of the gusset.

Thickness of top Bar Plate or top Ring

Enter the thickness of the top bar plate/ring in the units above. If there is no top bar plate or top ring, enter 0 here.

18-12



Lifting Lug Input

Lifting Lug Input Generally there are two types of lifting lug orientations, flat and perpendicular. Flat lugs are generally welded below the top head seam and extend far enough above the seam for the lifting cables to clear the head and its nozzles. Perpendicular lugs (ears) are used to clear some obstruction at or near the top head (such as a body flange) by moving the support point away from the vessel shell. They are also used as tailing lugs. The width of the lug is its dimension in the direction of orientation described above. The length is in the vertical direction relative to the vessel. The length of the welds will also need to be entered. For flat lugs the weld at the bottom will usually be the same as the lug width. For perpendicular lugs the weld length will be the same as the thickness of the lug. PVElite will take the square root of the sum of the squares (W, N, and T) to determine the total shearing load. The forces W and N cause bending loads on flat lugs while W and T cause bending loads on perpendicular lugs. The corner of the weld group is where the stress will be checked at. Review the example problems and see Figure 18A - External Force Illustration for further clarification of input. Material Specification for Lifting Lugs

Enter the material that the lugs are made of. An example of a of a common material is SA516 70. To properly initialize the material, type its name on this line even if the default is shown. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Lug Allowable Stress at Design Temperature

The lug allowable stress is multiplied by 0.6 for comparison to the shear stress above the hole in the lifting lug. It is also multiplied by the arc efficiency to get the allowable weld shear for combined loads. Lug Allowable Stress at Ambient Temperature

The lifting lug allowable stress at ambient temperature should appear in this cell. The allowable stress at the lug operating temperature is used for the allowable stress comparison. Lug Orientation to Vessel

Select "Perpendicular" if the lug extends radially away from the vessel wall. These lugs are referred to as ear-type lugs. They are typically used on the tops of horizontal vessels. If the lug extends in the same direction as the vessel axis, select "Flat." This is a flat orientation. If you are working with a perpendicular lug and there will be no bending stresses in the lug, you will need to set the offset dimensions (moment arms) to 0. The program will run, but may give some warnings. This type of lifting lug would be one on the top of a horizontal vessel and the vessel would be lifted by a spreader bar equally distributing the weight load directly over each lug. Thus there would be no bending.


18-13

Lifting Lug Input


Contract Width or Height (Per. Lug) of Lifting Lug

The width of the lug is its dimension in the direction of orientation described in the lug orientation to vessel wall. For perpendicular lugs this is the total height of the lug. Thickness of Lifting Lug

Enter the thickness of the plate that the lifting lug was constructed from. Diameter of Hole in Lifting Lug

Most lifting lugs have a circular hole cut or drilled into them. Enter the diameter of this hole. Radius of Semi-Circular ARC of Lifting Lug

Enter the RADIUS of the semi-circular part of the lifting lug where the hole is located. Typically this will be circular on flat lugs and semi-circular on perpendicular lugs. Height of Lug from Center of Hole to Bottom

Enter the distance along the axis of the vessel from the center of the hole to the bottom of the lug. Offset from Vessel OD to Center of Hole

Enter the distance from the center of the hole to base of the lifting lug. For perpendicular lugs this will be to the vessel OD. If the orientation is flat, this will be one half the lug thickness. Minimum Thickness of Fillet Weld Around Lug

This minimum is usually the distance from the root to the surface of the fillet weld (root dimension), and is not the fillet weld leg size. Length of Weld Around Sides of Lug

Enter the length of the long welds on the side of the lifting lug. PVElite will multiply this value by two when determining the weld area. Length of Weld Along Bottom of Lifting Lug

Enter the length of the short weld. This is usually the bottom weld. Lift Orientation

Enter the vessel lift orientation for the lifting lug analysis. For more information see Figure 18E - Lifting Orientation. Axial Force

Enter the component of force on the trunnion along the axis of the vessel. For more information see Figure 18E - Lifting Orientation. Normal Force

Enter the component of force on the trunnion perpendicular to the wall of the vessel. For more information see Figure 18E - Lifting Orientation.

18-14



Lifting Lug Input

Tangential Force

Enter the component of force on the trunnion tangent to the wall of the vessel. For more information see Figure 18E - Lifting Orientation. OFFSET OF LIFTING LUG

FLAT LIFTING LUG ARC RADIUS

OFFSET

HOLE DIAMETER

PERPENDICULAR LUG

SIDE FILLET WELD

BOTTOM FILLET WELD

SUPPORT LUG

LEGS CROSS BRACING LEG ORIENTATION: WEAK

GUSSET WIDTH

GUSSET THICKNESS

STRONG

WIDTH

LENGTH THICKNESS

Figure 18B - Geometry for the Leg & Lug Module


18-15

Output


Output PVElite produces three basic types of results in the Leg & Lug module. Results for Legs, using the methods described by AISC, results for Lifting Lugs, using basic engineering principles, and results for Support Lugs, using AISC methods and formulae from pressure vessel text books and other engineering reference texts. The input for this module include some basic vessel parameters such as the vessel tangenttangent length, the diameter and the height of the bottom tangent above grade. If you are performing a Leg or Support Lug calculation, the program follows these basic steps in order to determine the loads. For evaluation of wind loads: 1. Determine the elevation of the top and bottom seam of the vessel. 2. Determine the wind pressure at both elevations, and take the average. 3. Determine the effective diameter of the vessel and its area. 4. Compute the centroid of the vessel. 5. Resolve the wind pressure and the area at the centroid. For evaluation of seismic loads: 1. Determine the seismic zone factor from UBC table 23-I or use the one the user gave. 2. Multiply this value times the operating weight of the vessel. 3. Apply this load at the centroid of the vessel. If both types of loadings are considered, PVElite will compute both and then choose the maximum of the two.

18-16



Examples

Examples The first example presented below involves the horizontal lifting of a vessel that weighs about 73,000 pounds. The design specification stated that if one lug failed, the other lug must be capable of supporting the entire weight of the vessel. In addition, the spreader bar used to pick up the tower was a few inches short and caused a normal load to be generated on the flat lifting lugs. The normal force is simply a function of the angle the chains make with the lug and the load per lug. Ideally this geometry should be analyzed a second time with the lifting weight of the vessel in the erection weight input field. Also the tangent force should be set equal to 0. This would simulate picking the vessel up in its normal operating position or when it is being installed in the field. As you can see the arrangement worked well with the exception of the bending stress in the lug. This is essentially cantilever bending. The remedy for this situation is to place a gusset support between the top head and the flat lug. This would decrease the moment arm and thus lower the bending stress. The next example problem is for a lug supported vessel. This particular arrangement had three support lugs. This vessel is supported in a structure containing piping and other equipment. Bending stress are computed in the bottom support lug plate by two methods. One is a uniform load (as if the lug were sitting on a beam) and the other is a point load. Obviously, the point load on the plate will produce much higher bending stresses. When you are looking at these bending stress results for the bottom plate only one will be applicable. The stress in the gusset plate and its allowable are also computed. The allowable should be greater than the actual stress for the lug to work properly. The results for the gusset plates are computed using rules of the AISC. The final example here is a leg supported vessel. The main point of interest is the AISC Unity Check. The unity check combines forces and moments on the leg and essentially predicts buckling. This result must be less than or equal to 1.0. If your unity check is small, then you should be able to decrease the size of the structural member until you have a unity check that is satisfactory for your design work. Input Echo, LEG&LUG Number 1,

Description: LIFTING LUG


.00

Design Temperature for Attachment

psig

TEMP

70.00

OD

55.0000

in.

Operating Weight of Vessel (vertical load )

W

.00

lb.

Erection Weight of Vessel (Lifting Analysis)

W

.00

lb.

Additional Horizontal Force on Vessel

FF

.00

lb.

Location of Horizontal Force above Base Point

FH

.00

ft.

to the Vessel

N

17045.00

lb.

Horizontal Force Tangent to the Vessel

T

72525.00

lb.

Vessel Outside Diameter

Horizontal Force Normal

Lifting Lug Material Lifting Lug Yield Stress

F

SA-516 70 YIELD

Lifting Lug Orientation to Vessel

38000.00

psi

Flat

Width of Lifting Lug

WLUG

20.0000

in.

Thickness of Lifting Lug

TLUG

1.7500

in.


18-17

Examples


Diameter of Hole in Lifting Lug

DLIF

2.7500

in.

Radius of Semi-Circular Arc of Lifting Lug

RLIF

10.0000

in.

Height of Lug from bottom to Center of Hole

HLIF

37.0000

in.

Offset from Vessel OD to Center of Hole

OLIF

.8750

in.

Minimum thickness of Fillet Weld around Lug TWELD

.6187

in.

Length of weld along sides of Lifting Lug

LWELD

18.0000

in.

Length of Weld along Bottom of Lifting Lug

BWELD

20.0000

in.

OCCFAC

1.33

Occasional Load Factor (AISC A5.2)

RESULTS FOR LIFTING LUGS :

Description:LIFTING LUG

Weld Group Inertia in the Longitudinal Direction

1291.16

Weld Group Centroid distance in the Long. Direction

12.32

Weld Group Inertia in the Circumferential Direction

3192.54

Weld Group Centroid Distance in the Circ. Direction

10.62

in**4 in. in**4 in.

Primary Shear Stress in the Welds due to Shear Loads: Ssll = SQRT(W^2+T^2+N^2)/((2*Lweld+Bweld)*Tweld) Ssll = SQRT( 0^2+ 72525^2+ 17045^2)/((2* 18.0+ 20.0)* .6187) Ssll = 2150.28 psi

Shear Stress in the Welds due to Bending Loads : Sblf = (N*(Hlif-Lweld/2))*YLL/ILL+(W*OLIF*YLL/ILL)+(T*OLIF*YLC/ILC) Sblf = ( 17045*( 37.000- 18.000/2))* 12.325/ 1291.159 + ( 0* .875* 12.325/ 1291.159) + ( 72525* .875* 10.619/ 3192.545) Sblf = 4766.76 psi

Total Shear Stress vs. allowable Shear for Combined Loads : St = ( Ssll + Sblf ) St = ( 2150.276 + 4766.762 ) St = 6917.04 psi

Sta = ( .4 * Yield * Occfac ) AISC Shear All. Sta = ( .4 * 38000 * 1.33 ) Sta = 20216.00 psi

Secondary Shear Stress in the Welds due to Shear Loads: Unit Weld Section Modulus ( Uwsm ) = (2*LWELD+WLUG)^3/12 - LWELD^2(LWELD+WLUG)^2/(2*LWELD+WLUG) = 6280.10 in.^3

Loads on Welds due to Torsional Moment Fth = T * (Hlif-(Lweld-Cent)) * (Bweld/2)/Uwsm Fth = 3604.75 lb./in.

Ftv = T * ( Hlif-(Lweld-Cent)) * Cent / Uwsm Ftv = 4402.94 lb./in.

Fsv = T / ( 2 * Lweld + Wlug ) Fsv = 1295.09 lb./in.

Resultant Load on Weld Group Fr = Sqrt( Fth^2 + ( Ftv+Fsv )^2 )

18-18



Examples

Fr = 6742.53 lb./in.

Resultant Secondary Weld Stress Fws = Fr / Tweld Fws = 10897.91 psi

Allowable Resultant Secondary Weld Stress Psa = ( .4 * Yield * Occfac ) Psa = 20216.00 psi

Shear Stress in Lug above Hole vs. Allowable Base Metal Shear : Shs = SQRT( W^2 + N^2 + T^2 ) / Sha Shs = SQRT( 0^2 + 17045^2 + 72525^2 ) / 30.188 Shs = 2467.94 psi

Sas = ( 0.4 * Yield * Occfac ) Shear Allowable Sas = ( 0.4 * 38000 * 1.33 ) Sas = 20216.00 psi

Pin Hole Bearing Stress Vs. Allowable Bearing Stress Pbs = Sqrt( W^2 + N^2 + T^2 )/( Tlif * Dlif ) Pbs = Sqrt( 0^2 + 17045^2 + 72525^2 )/( 1.750 * 2.750 ) Pbs = 15480.74 psi

Pba = ( 0.75 * Yield ) AISC Bearing All. Pba = ( 0.75 * 38000 ) Pba = 28500.00 psi

Bending Stress in Lug at Weld Vs. Allowable Stress Fbs = N*(HLIF-LWELD)/(WLUG*TLIF^2/6) Fbs = 17045 *( 37.000 - 18.000 )/( 20.000 * 1.750^2 / 6) Fbs = 31724.57 psi

Fba = ( 0.4 * Yield * Occfac ) Shear Allowable Fba = ( 0.4 * 38000 * 1.33 ) Fba = 20216.00 psi



18-19

Examples


Input Echo, LEG&LUG Number

2,

Description: LUG DESIGN


300.00

psig

TEMP

300.00

F

OD

96.0000

in.

TANTAN

30.0000

ft.

40.0000

ft.

Design Temperature for Attachment Vessel Outside Diameter Tangent to Tangent Length of Vessel Height of Bottom Tangent Above Grade


W

83000.00

lb.


W

.00

lb.

Cf

1.000

I

1.110

V

100.000

Expcat

C

Force Coefficient Additional Area

.00

Importance Factor Wind Velocity Exposure Catagory Use ASCE 7-95 Wind Code

sq.in.

mile/hr

No


FF

.00

lb.


FH

.00

ft.

Support Lug with Full Reinforcing Rings?

No

Number of Support Lugs

NLUG

3

Location of Support Lugs above Base Point

LLUG

50.0000

ft.

Distance from Vessel OD to Lug Contact Point DLUG

8.0000

in.

Lug Support Force Bearing Width

4.0000

in.

WFB

Support Lug Material

SA-516 70

Support Lug Yield Stress

38000.00

psi

Radial Width of bottom Support Lug Plate

WPL

12.0000

in.

Circum. Length of Bottom Support Lug Plate

LPL

15.0000

in.

Thickness of bottom Support Lug Plate

TPL

2.0000

in.

Distance between Gussets

DGP

14.0000

in.

Mean Width of Gusset Plate

WGP

11.0000

in.

Height of Gusset Plate

HGP

15.0000

in.

Thickness of Gusset Plate

TGP

.7500

in.

OCCFAC

1.33


COMPUTED PARAMETERS: Effective Wind Area of Vessel

AREA

47001.60

Wind Pressure on Vessel ( ASCE #7 or User ) PWIND

35.57

psf

Location of Centroid above Base Point

55.00

ft.

RESULTS FOR SUPPORT LUGS:

WH

sq.in.

Description:LUG DESIGN

Overturning Moment at Support Lug

58046.

ft.lb.

Weight Load at the top of one Lug

27667.

lb.

3870.

lb.

Shear at top of one Lug

Force on one Lug: Flug = ( W/Nlug + Mlug/( Rlug * Nlug/ 2 ) ) Flug = ( 83000 / 3 + 58045 /( 4.67 * 3 / 2 ) ) Flug = 35958.93 lb.

Bending Stress in bottom Support Plate (Point Load):

18-20



Examples

Spl = ( Flug/2*Dgp/2)/((Wpl/6)*Tpl^2) Spl = ( 35958/2* 14.000/2)/(( 12.00/6)* 2.0000^2) Spl = 15732.03 psi

Bending Stress in bottom Support Plate (Unif. Load) Per Bednar p.156: Spl2 = Beta1 * Flug/(Lpl*Wfb)) * Wfb^2 / Tpl^2 per Roark & Young 5th ed Spl2 = 2.105 * ( 35958.9 / 60.000) * 4.000^2 / 2.000^2 Spl2 = 5046.24 psi

Allowable Stress in the Bottom Support Plate: Spa = ( 0.66 * Ylug ) Spa = ( 0.66 * 38000 ) Spa = 25080.00 psi

Stress in Gusset Plate ( Force / Gusset Plate Area ): Sgp = ( Flug/2 ) / ( Wgp * Tgp ) Sgp = ( 35958/2 ) / ( 11.000* .7500 ) Sgp = 2179.33 psi

Gusset Plate Allowable Stress : Sga = ( 1-(Klr)^2/(2*Cc^2))*Fy / ( 5/3+3*(Klr)/(8*Cc)-(Klr^3)/(8*Cc^3) Sga = ( 1-( 80.00 )^2/(2 * 122.74^2 )) * 38000 / ( 5/3+3*( 80.00)/(8* 122.74)-( 80.00^3)/(8* 122.74^3) Sga = 15948.94 psi

Maximum Compressive Stress in the Gussets per Bednar: SgpB = Flug * ( 3*Dlug - Wpl ) / ( Tgp* Wpl**2 * (SIN(Alph_G))**2 ) SgpB = 35958*( 3* 8.000- 12.000 )/( .7500* 12.000**2*(SIN( 82.41))**2 ) SgpB = 4066.47 psi

Gusset Plate Allowable Compressive Stress per Bednar: SgaB = 18000./ (1.+ (1./18000)* ( Hgp /SIN(Alph_G)/(.289*Tgp) )**2 ) SgaB = 18000/ (1+ (1/18000)* ( 15.000 /SIN( 82.41)/(.289* .7500) )**2 ) SgaB = 14164.33 psi

Additional Results - Forces/Moments for WRC107 Analysis: Axial Load

= Shear / Nlugs

=

3870.

lb.


= Shear / Nlugs

=

3870.

lb.

Longitudinal Shear

= Load

=

35959.

lb.

Longitudinal Moment

= Moment/ Nlugs

=

23973.

ft.lb.

Circumferential Moment = Shear * Distance =

1935.

ft.lb.

/ Lug



18-21

Examples


Input Echo, LEG&LUG Number

3,

Description: LEG DESIGN


300.00

Design Temperature for Attachment

70.00

OD

60.0000

in.

TANTAN

20.0000

ft.

20.0000

ft.

Vessel Outside Diameter Tangent to Tangent Length of Vessel

psig

TEMP

Height of Bottom Tangent Above Grade

F


W

240000.00

lb.


W

.00

lb.

Cf

1.000

I

1.050

V

120.000

Expcat

B

Force Coefficient Additional Area

.00

Importance Factor Wind Velocity Exposure Catagory Use ASCE 7-95 Wind Code

sq.in.

mile/hr

No


FF

.00

lb.


FH

.00

ft.

Number of Legs

NLEG

8

Length of Legs

LLEG

20.0000

K

1.00

Effective Leg End Condition Factor Material for Legs

ft.

SA-516 70

Yield Stress of Leg Material

38000.00

AISC Member Designation

psi

W8X40

Leg Orientation to Vessel Axis

ORIENT

Strong

XB

YES

OCCFAC

1.33

Are the Legs Cross-Braced


COMPUTED PARAMETERS: Effective Wind Area of Vessel

AREA

20736.00

Wind Pressure on Vessel ( ASCE #7 or User ) PWIND

27.43

psf

Location of Centroid above Base Point

30.00

ft.

RESULTS FOR Legs :

WH

sq.in.

Description:LEG DESIGN

Section Properties for the selected Member : Cross Sectional Area for W8X40

11.700

Radius of Gyration ( strong axis )

sq.in

3.530

in.

35.500

in.**3

Overturning Moment at top of Legs

39505.0

ft.lb.

Weight Load at top of one Leg

30000.0

lb.

987.6

lb.

11173.7

lb.

Section Modulus

( strong axis )

Shear at top of one Leg Additional force in Leg due to Bracing

Axial Compression, Leg futhest from N.A. Sma = ((W/Nleg)+(Mleg/(Nlegm*Rn)))/Aleg) Sma = (( 240000 / 8) + ( 39504 /( 4 * 2.84 )))/ 11.700 ) Sma = 2861.10 psi

Axial Compression, Leg closest to

N.A.

Sva = ( W / Nleg + Fadd ) / Aleg

18-22



Examples

Sva = ( 240000 / 8 + 11173 ) / 11.700 Sva = 3519.12 psi

Allowable Comp. for the Selected Leg

(KL/r < Cc ) :

Sa = ( 1-(kl/r)^2/(2*Cc^2))*Fy / ( 5/3+3*(Kl/r)/(8*Cc)-(Kl/r^3)/(8*Cc^3) Sa = ( 1-( 117.65 )^2/(2 * 122.74^2 )) * 38000 / ( 5/3+3*( 117.65 )/(8* 122.74 )-( 117.65^3)/(8* 122.74^3) Sa = 10721.60 psi

Bending at the Bottom of the Leg closest to the N.A.: S = ( Vleg * Rlngth * 12 / Smdsa ) S = ( 987.62 * 20.00 * 12 / 35.50 ) S

= 0.0 since the legs are cross braced

Sb = ( 0.6 * Fy * Occfac ) Sb = ( 0.6 * 38000 * 1.33 ) Sb = 30324.00 psi

AISC Unity Check ( must be < or = to 1.00 ) : Sc = (Sva/Sa)+(0.85*S)/((1-Sva/Spex)*Sb) Sc = ( 3519/ 10721 )+( 0.85 * .000 )/(( 1 - 3519/ 10789 ) * 30324 ) Sc = .3282

Additional Results - Forces/Moments for WRC107 Analysis: Axial Load

= Shear / Nlegs

=

494.

lb.


= Shear / Nlegs

=

494.

lb.

Longitudinal Shear

= Load

=

30000.

lb.

Longitudinal Moment

= Moment/ Nlegs

=

10313.

ft.lb.

Circumferential Moment = Shear * Distance =

339.

ft.lb.

/ Leg



18-23

Baseplate Input


Baseplate Input The Baseplate Thickness calculation is included in the vessel leg analysis for I-beam, pipe, and angle leg only, and can be activated by clicking the Annoyance Baseplate checkbox. The design is based on the method for I-beam leg described in the Pressure Design Manual by D. Moss and is applied to the other leg shapes. CodeCalc will assume the following for all Baseplate Thickness calculations: •

Strong axis leg orientation

•

Bolts are installed along the length sides only (B dimension). For more information see Figure 18C - Baseplate Dimension

•

The leg is attached symmetrically on the baseplate. For more information see Figure 18C - Baseplate Dimension

It is advisable to check the baseplate dimensions using the graphic feature of CodeCalc. Baseplate Length B

Enter the length "B" of the baseplate. For more information see Figure 18C - Baseplate Dimension. Baseplate Width D

Enter the width "D" of the baseplate. For more information see Figure 18C - Baseplate Dimension. Baseplate Thickness BTHK

Enter the available baseplate thickness. Baseplate Material

Click the Material Database button to look up a material name from the database. If a material is not a contained in the database its specification and properties can be entered manually by selecting Tools, Edits/Add Materials from the Main Menu. Bolt Material

Click the Material Database button to look up a material name from the database. If a material is not a contained in the database its specification and properties can be entered manually by selecting Tools, Edits/Add Materials from the Main Menu. Distance from the Edge of the Leg to the Bolt Hole, "z"

Enter the "z" dimension of the baseplate. For more information see Figure 18C- Baseplate Dimension. Nominal Bolt Diameter

Enter the nominal bolt diameter. The bolt diameters included in the program range from 0.5 to 4.0 inches. If you have bolts that are larger or smaller than this value, enter the nominal size in this field and also enter the root area of one bolt in the "Root Area" cell. Bolt Corrosion Allowance

If there is any corrosion allowance for the bolts then enter it here. The nominal bolt size is corrected for this allowance. 18-24



Baseplate Input

Thread Series

There are three options for this entry: •

TEMA Bolt Table

•

UNC Bolt Table

•

User specified root area of a single bolt.

Bolt Root Area

If your geometry uses bolts that are not the standard TEMA or UNC types you must enter the root area of a single bolt in this field. Total Number of Bolts per Baseplate

Enter the total number of bolts per baseplate. At least two bolts are needed for uplift stituations. The program assumes that the bolts are located along the length "B" of the baseplate as shown in Figure 18C - Baseplate Dimension. Number of Bolts in Tension per Baseplate

Enter the total number of bolts in tension per baseplate. If there is an uplift the number of bolts in tension per Baseplate should be at least 1. If there is no uplift the number of bolts in tension per Baseplate is not required. Nominal Compressive Stress of Concrete

Enter the Nominal Compressive Stress of the Concrete to which the basering/baseplate is bolted. This value is f’c in Jawad and Farr of FPC in Meygesy. A typical entry is 3000 psi.

Water Content (gal) per 94 lb. Sack of Cement

f’c 28 day Ultimate Compressive Strength (psi)

7.50

2000

6.75

2500

6.0

3000

5.00

3750


18-25

Baseplate Input


Figure 18C - Baseplate Dimension

18-26



Baseplate Results

Baseplate Results The Baseplate analysis produces the following result: •

The thickness requirement is calculated using the 1.5 allowable plate bending stress and compared to the input thickness.

•

The concrete bearing pressure is compared to the input allowable stress

•

The anchor bolt size is analyzed at the bending level (D. Moss) and the overall vessel moment equilibrium (H. Bednar). In the absence of tension in the bolts you should choose a practical bolt size.


18-27

Trunnion Input


Trunnion Input A hollow or solid circular trunnion with or without pad reinforcement can be analyzed using the Trunnion Design module. The main considerations regarding the trunnion design are stresses at the vessel/trunnion junction and on the trunnion itself. Bending stress, shear stress, bearing stress and the Unity Check are calculated and compared with the appropriate allowables. Local stresses at the junction can be analyzed using the WRC 107 Analysis Selection checkbox. The lifting orientation, vertical and horizontal positions, and the orthogonal input forces are needed for WRC 107 Analysis. CodeCalc assumes that magnitude of the applied loads is acting on one trunnion. Typically vessels are lifted with two trunnions thus the load is divided between them. An option is to analyze the trunnion with the maximum load acting on that trunnion during the lift. The program multiplies this lifting load by the importance factor specified by the user. Before the analysis it is advisable to check the trunnion dimensions and the forces’ magnitude and direction using the graphic feature in CodeCalc. The program does not subtract corrosion allowance (if any) and then enter the dimensions. Trunnion Type (Hollow or Solid)

This input is required for performing shear and bending stress calculations and for WRC 107 Analysis. Trunnion Outside Diameter

Enter the outside diameter of the trunnion. For more information see Figure 18D - Trunnion Geometry. Trunnion Thickness

Enter the thickness of the trunnion. For more information see Figure 18D - Trunnion Geometry. Projection Length

Enter the projection length of the trunnion. For more information see Figure 18D - Trunnion Geometry. Bail/Sling Width

Enter the bail or sling width used during erection. This input is required for locating the the lifting load only. No analysis is performed on the bail or sling. For more information see Figure 18D - Trunnion Geometry. Trunnion Material

Enter the material the trunnion is made of. Depending on the size and the availability, the trunnion can be made of pipe or sheet plate. To properly initialize the material, type its name in this field even if the default displays. If am material is not contained in the database, its specifications and properties can be entered manually by selecting Tools, Edit/ Add Materials from the Main Menu. Reinforcement

This input is required to perform the WRC 107 Analysis.

18-28



Trunnion Input

Ring Outside Diameter

Ring Outside Diameter is only used to display a picture of the trunnion. This is not used in the calculations. For more information see Figure 18D - Trunnion Geometry. Ring Thickness

Ring Thickness is only used to display a picture of the trunnion. This is not used in the calculations. For more information see Figure 18D - Trunnion Geometry. Lift Orientation

Enter the vessel lift orientation for the trunnion analysis. This value will be used to perform WRC 107 Analysis on the trunnion. Axial Force

Enter the component of force on the trunnion along the axis of the vessel. For more information see Figure 18E - Lifting Orientation. Normal Force

Enter the component of force on the trunnion perpendicular to the wall of the vessel. For more information see Figure 18E - Lifting Orientation. Tangential Force

Enter the component of force on the trunnion tangent to the wall of the vessel. For more information see Figure 18E - Lifting Orientation. Importance Factor

When the vessel is lifted from the ground it may be yanked abruptly. The Importance Factor takes this into account. This value typically ranges from 1.5 to 2.0 although values as high as 3.0 may be used. The program multiplies the Lifting Load by the Importance Factor. Perform WRC 107 Analysis on Trunnion

Click this box to perform WRC 107 Analysis on the trunnion/vessel junction.


18-29

Trunnion Input


Figure 18D - Trunnion Geometry

Figure 18E - Lifting Orientation

18-30



Trunnion Result

Trunnion Result The ring outer diameter and thickness are not used in the calculations; they are used to display a picture only. There are four passing criteria used to calculate the trunnion design bending stress, shear stress, bearing stress and the Unity Check. The following allowables are used: •

Bending Stress: 0.66 *Sy*Occfac

•

Shear Stress: 0.40 *Sy*Occfac

•

Bearing Stress: 0.75 *Sy*Occfac

•

WRC 107 Analysis- local stresses at 8 points are evaluated and compared with the allowable (1.5 * S allow). For more information see the WRC 107 module.


18-31

Trunnion Result

18-32




&KDSWHU The Pipe & Pad Module

Introduction This chapter discusses the Pipe & Pad module in the PVElite program. To use this program make sure the current analysis type is Pipe & Pad. This can be determined by looking on the PVElite main menu. The Pipe & Pad module computes required wall thickness and area of replacement for ANSI B31.3 intersections. These area of replacement rules are based on the 1987 edition of ANSI B31.3 Chemical Plant and Petroleum Refinery Piping Code. Extruded outlet headers are also analyzed.

Discussion of Input Main Input Fields Intersection Number

Enter an intersection number for this analysis. These should be positive integer values and incriminated by ones. Intersection Description

Enter a 15 letter/number identifier for this intersection. This description will not be used in the analysis, however, it will be used in the error checker and in the output reports. This identifier should have some link to the actual intersection. An example might be “Int 12x4”. Design Pressure

Enter the design pressure of the ANSI B31.3 intersection. This should be the pressure that the system will operate at continuously. Most of the internal computations for areas, wall thickness etc. involve the design pressure. Design Temperature

Enter the design temperature of the intersection. This temperature will be used to determine the allowable stress of the branch. The user may note that if a new temperature is input the allowable stress information of the branch is updated automatically. Branch\Header\Pad Material Specification

Enter the material specification in this cell. A list of materials can be found in the PVElite User’s Guide or it can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data-

The Pipe & Pad Module

19-1

Discussion of Input


base, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. An example of a valid material name is A106 B. Valid piping materials available are A-106 B

A-285 C

A-312 304

A-312 304L

A-312 316

A-312 316L

A-516 55

A-516 60

A-516 65

A-516 70

A-53 A

A-53 B

A-335 P1

A-335 P2

A-335 P5

A-335 P11

A-335 P22

A-537 CL1

Any material can be used as long as the hot and cold allowables are properly specified. Allowable Stress, Operating

The allowable stress of the material specified at the design temperature above should appear in this cell. This stress will appear automatically if a valid material is selected. If the temperature is changed the material properties will be updated automatically. Allowable Stress, Ambient

The allowable stress of the material at ambient temperature above should appear in this cell. This stress will appear automatically if a valid material is selected. Branch Dimension Basis

Select the branch dimension basis in this field. Pipe Normal or Actual Outside Diameter

If actual was entered in the field immediately above, then enter the actual outside diameter of the branch in this cell. If nominal was entered above, enter the nominal outside diameter of the branch pipe. An example is “10.” for a 10 inch pipe. Actual Thickness of Branch/Header

If the user has specified a 1 in the branch/header dimension basis field, then the actual wall thickness of the branch will be entered in this cell. PVElite will reduce the wall thickness according to B31.3 if appropriate values are entered for mill tolerance or corrosion allowance. Nominal Thickness of Branch/Header

Enter the schedule for the branch/header wall. Enter a value in this field only if you selected Nominal for the branch diameter and thickness basis. Otherwise enter a thickness in the field above. Type in the schedule for the branch, i.e. SCH 40. Available schedules are SCH 10SCH 80 SCH STD SCH 10SSCH 80SSCH-STG SCH 20SCH 100SCH XX-STG SCH 30SCH 120SCH 40 SCH 140SCH 40SSCH 160 SCH 60

19-2



Discussion of Input

Mill Undertolerance, Percent

The mill undertolerance accounts for manufacturing deficiencies when pipe is produced. If for example a value of 12.5 is entered, then the wall thickness of the pipe will be multiplied by (100 - 12.5)/100 or .875. This is essentially a reduction in wall thickness. Valid entries are between 0 and 99%. Corrosion Allowance

Enter the estimated allowance for corrosion in this field. The difference of (wall thickness - (corrosion allowance + mill tolerance)) must be greater than 0. Basic Quality Factor for Longitudinal Joints

The basic quality factor is used in the wall thickness calculations for pipes under internal pressure only. These factors are listed in the ANSI B31.3 piping code Table A-1B. For seamless and fully radiographed pipe this value is 1.0. For electric resistance welded and spot welded materials it is usually 0.85. Angle Between Branch and Header

Enter the angle between the centerline direction vector of the branch and the header. This is typically 90 degrees. The piping codes do not allow “hillside” type attachments. This angle is referred to as Beta and is shown in Figure 19A. This is the smaller angle between axes. Does the Branch Penetrate a Header Weld

If the branch pipe passes through a weld seam on the header pipe check this field. Refer to ANSI B31.3 paragraph 304.3.3 under “t =” for more information. Rate the Attached B16.5 Flange

If a flange is attached to the branch pipe and you wish to rate it check this field. Header Dimension Basis

Enter the header dimension basis in this field. If the actual outside diameter is known select actual. If the nominal schedule of the header is known select nominal. Reinforcing Pad Present

If the intersection being analyzed has a reinforcing pad, check this field. If selected PVElite will determine the area(s) available in the pad within the appropriate limits of reinforcement. In addition, PVElite will also report the required pad diameter based on the given pad thickness and the required pad thickness based on the given diameter. Thickness of Extruded Outlet, TX

The dimension TX of an extruded outlet header is the corroded finished thickness which is measured at a height equal to the radius of curvature above the outside surface of the header. Height of Extruded Outlet, HX

The dimension Hx of an extruded outlet header is the height of the extruded outlet. This distance must be greater than or equal to the radius of curvature Rx, of the outlet.


19-3

Discussion of Input


Inside Diameter of Extruded Outlet, DX

Dx is the inside diameter of the extruded outlet which is measured at the level of the outside of the header. PVElite will automatically adjust the wall thickness of the outlet if the mill tolerance and/or the corrosion allowance is specified. Radius of Curvature, RX, of Extruded Outlet

Rx is the radius of curvature of the external contoured part of the extruded outlet, which is measured in the plane containing the axes of both the header and the branch.

19-4



Pop-Up Input Fields

Pop-Up Input Fields Class of the Attached B16.5 Flange

If you answered Y to rate the attached B16.5 flange then enter the class of the flange attached to the nozzle neck. Available classes of flanges are: CL 150, CL 300, CL 400, CL 600, CL 900, CL 1500, CL 2500. Grade of the Attached B16.5 Flange

If the flange attached to the nozzle neck is to be rated then the grade of the flange must be entered here. The allowable grades of B16.5 flanges are GR 1.1 GR 1.2 GR 1.4 GR 1.5 GR 1.7 GR 1.9 GR 1.10 GR 1.13 GR 1.14

Med C Steel High C Steel Low C Steel C-1/2Mo 1/2Cr-1/2Mo, Ni-Cr-Mo 1-1/4Cr-1/2Mo 2-1/4Cr-1Mo 5Cr-1/2Mo 9Cr-1Mo

GR 2.1 GR 2.2 GR 2.3 GR 2.4 GR 2.5 GR 2.6 GR 2.7

Type 304 Type 316 Type 304L,316L Type 321 Type 347,348 Type 309 Type 310

Pad Thickness

Enter the thickness of reinforcing element in this cell. All allowances for corrosion should be taken into consideration by the user. Pad Diameter Along Header Surface

Enter the length of the reinforcing element along the longitudinal axis of the header.


19-5

Output


Output PVElite will generate output for maximum allowable working new and cold as well as the corroded condition. The hydrotest pressure is calculated as the maximum allowable working pressure at the design condition times 1.5 the ratio of the allowable stress at ambient temperature to the allowable stress at the design temperature. The replaced area can only be within a certain zone. No credit will be given for reinforcement that lies outside of the zone. Please note that these zones are different for extruded outlets. If a reinforcing element is used PVElite will compute the required diameter for the given thickness and the required thickness for the given diameter. If a pad is used in conjunction with an extruded outlet header consult the piping code for details on this design. If the calculated diameter falls outside the limit of reinforcement a message such as “EXCEEDS D2” or “EXCEEDS L4” will be displayed.

19-6



Output

The MAWP for the given geometry is an estimate because of a slight non-linearity in the required thickness calculation. To verify the MAWP plug the value back into the analysis as the design pressure and check to see if the area required is equal to the area available.

Figure 19A - Geometry for The Pipe & Pad Module


19-7

Output


Figure 19B - Geometry for The Pipe & Pad Module

19-8



Output

Figure 19C - Extruded Outlet


19-9

Example Problem


Example Problem Input Echo, Pipe&Pad Number

1,

Description: PIPE&PAD 1


P

Design Temperature

Header Material

psig

500.00

F

A-PI5L A

Header Allowable Stress Operating Header Allowable Stress Ambient

Sh

16000.00

psi

Shcold

16000.00

psi

Branch Material

A-PI5L A

Branch Allowable Stress Operating Branch Allowable Stress Ambient

Dimension Basis ( Nominal or Actual ) Nominal

300.00

-or- Actual Outside Diameter

Sb

16000.00

psi

Sbcold

16000.00

psi

Header

Branch

Nominal

Nominal

8.0000

4.0000

1.00

1.00

Basic Quality Factor for Long. Joints

E

Mill Tolerance

c

12.5

12.5

Corrosion Allowance

c

.1000

.1000

Pipe Schedule ( Header )

SCH 40

Pipe Schedule ( Branch )

SCH 40

Angle Between Branch and Header

á

Does the Branch Penetrate a Header Weld

% in.

Degrees

No

Thickness of Reinforcing Pad Diameter

90.0000

in.

Tr

of Reinforcing Pad

Reinforcing Pad Material

.3220

in.

6.0000

in.

A-PI5L A

Reinforcing Pad Allowable Stress

Sp

16000.00

psi

— Internal Pressure Calculations for Header and Branch ----------

Header

Branch

Allowable Stress used in Calculations

16000.00

16000.00

psi

Allowable Stress at Ambient Temperature

16000.00

16000.00

psi

8.625

4.500

in.

Nominal Thickness used in Calculations

.322

.237

in.

Coefficient of Effective Stressed Dia.

.400

.400

Required Thickness at Design Pressure

.080

.042

in.

Required Thickness + CA and Mill Tol.

.206

.162

in.

Actual Outside Diameter used in Calc.

Max. Allowable Working Pressure (MAWP)

685.88

778.41

psig

MAWP, New (uncorroded) & Cold (ambient)

1073.38

1531.11

psig

Hydrotest Pressure

1028.82

1167.62

psig

— Calculations for Required Branch Reinforcement ----------

19-10

Height of Reinforcement Zone

L4

.4544

in.

Effective Length removed from Pipe

d1

4.2853

in.



Example Problem

Half Width of Reinforcement Zone

d2

Allowable Stress used for Reinforcement

4.2853

in.

16000.

psi

Required Reinforcement Area

A1

.3439

sq.in.

Area Available in Header Wall

A2

.4349

sq.in.

Area Available in Branch Wall

A3

.0595

sq.in.

Area Available in Branch Weld

A4

.0551

sq.in.

Area Available in Pad

A4

.4830

sq.in.

Area Available in Pad Weld

A4

.0519

sq.in.

Total Area Available (A2+A3+A4+A4+A4)

1.0844

sq.in.

Estimated MAWP of Assembly

606.01

psig

FORMULAS and SUBSTITUTIONS for B31.3 INTERSECTION CALCULATIONS : th = ( P * Dh )/2( Sh * QF + P * Yh ) th = ( 300 * 8.6250 )/2( 16000 * 1.00 + 300 * .40 ) th = .080 in. Required thickness of header

tmh = ( th + c ) / Hmtr tmh = ( .0803 + .1000 ) / .8750 tmh = .206 in. Reqd. thickness + CA + mill tolerance

tb = ( P * Db )/2 ( Sb * QF + P * Y ) tb = ( 300 * 4.5000 )/2 ( 16000 * 1.00 + 300 * .40 ) tb = .042 in. Required thickness of branch

tmb = ( tb + c ) / Bmtr tmb = ( .0419 + .1000 ) / .8750 tmb = .162 in. Reqd. thickness + CA + mill tolerance

--------------- Pressure Results ------------------

Hpo = (Th*Hmtr-c)*2*Sh*He/(Dh-2*(Th*Hmtr-c)*Yh) Hpo = ( .3220 * .875 - .100 ) * 2 * 16000 * 1.000 / ( 8.625 - 2 * ( .322 * .875 - .100 ) * .40 ) Hpo = 685.881 psig M.A.W.P., operation, header

Hpnc = (Th*Hmtr)*2*Shcold*He/(Dh-2*(Th*Hmtr)*HY) Hpnc = ( .3220 * .875 ) * 2 * 16000 / ( 8.625 - 2 * ( .322 * .875 ) * .40 ) Hpnc = 1073.385 psig M.A.W.P., New & Cold, header

Hpht = ( 1.5 * Hpo * Shcold / Sh ) Hpht = ( 1.5 * 685.88 * 16000 ) / 16000 ) Hpht = 1028.822 psig Hydrotest Pressure, header

Bpo = (Tb*Bmtr-c)*2*Sb*Be/(Db-2*(Tb*Bmtr-c)*By) Bpo = ( .2370 * .875 - .100 ) * 2 * 16000 * 1.000 / ( 4.500 - 2 * ( .237 * .875 - .100 ) * .40 ) Bpo = 778.415 psig M.A.W.P., operation, branch


19-11

Example Problem


Bpnc = (Tb*Bmtr)*2*Sbcold*Be/(Db-2*(Tb*Bmtr)*BY) Bpnc = ( .2370 * .875 ) * 2 * 16000 * 1.000/ ( 4.500 - 2 * ( .237 * .875 ) * .40 ) Bpnc = 1531.114 psig M.A.W.P., New & Cold, branch

Bpht = ( 1.5 * Bpo * Sbcold / Sb ) Bpht = ( 1.5 * 778.41 * 16000 ) / 16000 ) Bpht = 1167.622 psig Hydrotest Pressure, branch

----------- Area and Zone Results --------------

L4 = The minimum of ( L4th, L4tb ) L4 = Minimum( .454 , .590 ) L4 = .454 in. Height of reinforcement zone

d1 = ( Db-2*(Tb*Bmtr-c))/SIN( á ) d1 = ( 4.50 - 2 * ( .2370 * .88 - .1000 ))/SIN( 90.0 ) d1 = 4.285 in. Effective Length removed from pipe

d2d2 = ( Tb*Bmtr-c ) + ( Th*Bmtr-c ) + ( d1/2 ) d2d2 = ( .237 * .875 - .1000 ) + ( .322 * .875 - .1000 ) + ( 4.285 / 2) d2d2 = 2.432 in. Candidate for d2 based on Tb + Th

d2 = The Min of ( The Max of ( d1, d2d2 ), Db ) d2 = Min( Max( 4.285, 2.432 ), 8.625 ) d2 = 4.285 in. Half length of reinforcement zone

A1 = ( th * d1 * ( 2 - Sin( á ) ) A1 = ( .080 * 4.285 * ( 2 - Sin( 90.0 ) ) A1 = .344 sq.in. Area required to be replaced

A2 = ( 2 * d2 - d1) * (Th * Hmtr - th - c) A2 = ( 2 * 4.285 - 4.285 ) * ( .322 * .875 - .080 - .100 ) A2 = .435 sq.in. Area available in header

A3 = ( 2*L4*(Tb*Bmtr-tb-c)/Sin(á) A3 = ( 2 * .454 * ( .237 * .8750 - .042 - .100 )/Sin( 90.0 ) A3 = .060 sq.in. Area available in branch

A4 = ( Min( 0.7 * Tb, Minthk ) / 0.707 ) ** 2 A4 = ( Min( 0.7 * .237, .250 ) / 0.707 ) ** 2 A4 = .055 sq.in. Area available in branch weld

A5 = 2*Min(Dpad/2,d2)-(Db/2)/Sin(á))*Min(Tpad,L4)*Padf) A5 = 2*Min( 6.00/2, 4.285 ) - ( 4.500/2) / Sin( 90.0 )) * .322 * 1.00 A5 = .483 sq.in. Area available in reinforcing pad

A6 = If(A5>0&&Dpad+2*Bw

19-12



&KDSWHU The Base Ring Module

Introduction The PVElite base ring module performs thickness calculations and design for annular plate base rings, top rings, bolting, and gussets. These calculations are performed using industry standard calculation techniques as described below.

Calculation Techniques Thickness of a Base Ring Under Compression

The equation for the thickness of the base ring is the equation for a simple cantilever beam. The beam is assumed to be supported at the skirt, and loaded with a uniform load caused by the compression of the concrete due to the combined weight of the vessel and bending moment on the down-wind / down-earthquake side of the vessel. The equation for the cantilever thickness is found in most of the common vessel design textbooks, including Jawad & Farr, Structural Analysis and Design of Process Equipment, page 434, formula 12.12: t

=

SQRT( 3 * fc * l ** 2 / s )

Where fc =

bearing stress on the concrete

l

=

cantilever length of base ring

s

=

allowable bending stress of base ring (typically 1.5 times Code allowable).

There are two commonly accepted methods of determining the bearing stress on the concrete. The approximate method simply calculates the compressive load on the concrete assuming that the neutral axis for the vessel is at the centerline. Thus the load per unit area of the concrete is, from Jawad & Farr equation 12.1, equal to fc = Where W = M = A = c = I =

The Base Ring Module

-W / A - M * c / I Weight of vessel (worst case). Bending moment on vessel (worst case). Cross sectional area of base ring on foundation Distance from the center of the base ring to the edge Moment of inertia of the base ring on the foundation

20-1

Calculation Techniques


However, when a steel skirt and base ring are supported on a concrete foundation, the behavior of the foundation is similar to that of a reinforced concrete beam. If there is a net bending moment on the foundation, then the force upward on the bolts must be balanced by the force downward on the concrete. But because these two materials have different elastic moduli, and because the strain in the concrete cross section must be equal to the strain in the base ring at any specific location, then the neutral axis of the combined bolt/ concrete cross section will be shifted in the direction of the concrete. Several authors, including Jawad & Farr (pages 428 to 433) and Megyesy (pages 70 to 73) have analyzed this phenomenon. The program uses the formulation of Singh and Soler, Mechanical Design of Heat Exchangers and Pressure Vessel Components, pages 957 to 959. This formulation seems to be the most readily adaptable to computerization, as there are no tabulated constants. Singh and Soler provide the following description of their method: In this case a neutral axis parallel to the y axis exists. The location of the neutral axis is identified by the angle alpha. The object is to determine the peak concrete pressure p and the angle alpha. For narrow base plate rings an approximate solution may be constructed using numerical iteration. It is assumed that the concrete annulus under the base plate may be treated as a thin ring of mean diameter c. Assuming the foundation to be linearly elastic, and the base plate to be relatively rigid, Brownnell and Young have developed an approximate solution which, can be cast in a form suitable for numerical solution. Let the total tensile stress area of all foundation bolts be A. Within the limits of accuracy sought, it is permissible to replace the bolts with a thin shell of thickness t and mean diameter equal to the bolt circle diameter c, such that t = A / PI * c. We assume that the discrete tensile bolt loads, acting around the ring, are replaced by a line load, varying in intensity with the distance from the neutral plane. Let n be the ratio of Young’s moduli of the bolt material to that of the concrete; n normally varies between 10 and 15. Assuming that the concrete can take only compression (nonadhesive surface) and that the bolts are effective only in tension (untapped holes in base plate), an analysis [similar to that given above] yields the following results: p s alpha

= = =

(2 * W + r2 * t * c * s) / [(t3 - t) * r1 * c] (2 * (M - W * r4 * c) / (r2 * r3 * t * c ** 2) acos [(s - n * p) / ( s + n * p )]

Where width of base ring (similar to l in Jawad & Farr’s equations above) bolt circle diameter four constants based on the neutral axis angle, and defined in Singh & Soler equations 20.3.12 through 20.3.17, not reproduced here. These equations give the required 7 non-linear equations to solve for 7 unknowns, namely p, c, alpha, and the ri (i = 1, 4) parameters. The simple iteration scheme described below converges rapidly. The iterative solution is started with assumed values of s and p; say so and po [the program takes these from the approximate analysis it has just performed]. Then alpha is determined via the above equation. Knowing alpha the dimensionless parameters r1, r2, r3, and r4 are computed. This enables computation of corrected values of p and s (say po’ and so’). The next iteration is started with s1 and p1 where we choose:

20-2

t3 c r1-r4

= = =

s1 = p1 =

.5 * (so + so’) .5 * (po + po’)




This process is continued until the errors ei and Ei at the ith iteration stage are within specified tolerances, (ei = Ei = 0.005 is a practical value), Where ei = (si’ - si) / si Ei = (pi’ - pi) / pi Actual numerical tests show that the convergence is uniform and rapid regardless of the starting values of so and po.

Once the new values of bolt stress and bearing pressure are calculated, the thickness of the base ring is calculated again using the same formula given above for the approximate method. Thickness of Base Ring Under Tension

On the tensile side, if there is no top ring but there are gussets, there is disagreement on how to do the analysis. For example, Megyesy uses a ‘Table F’ to calculate an equivalent bending moment, Dennis R. Moss uses the same approach but gives the table (page 126129), and Jawad & Farr use a ‘yield-line’ theory (page 435-436). Since Jawad & Farr is both accepted and explicit, the program uses their equation 12.13: t = Where x = y = z = F = a = b = l = d =

SQRT{ (3.91 * F) / [Sy * ( x + y + z)]} 2*b/a a / (2 * l) d * ( 2 / a + 1 / [2 * l]) Bolt Load = Allowable Stress * Area Distance between gussets Width of base plate that is outside of the skirt Distance from skirt to bolt circle Diameter of bolt hole

Thickness of Top Ring Under Tension

If there is a top ring or plate, its thickness is calculated using a simple beam formula. Taking the plate to be a beam supported between two gussets with a point load in the middle equal to the maximum bolt load, we derive the following equation: t = SQRT(6 * M / s) Where M = 2 * Ft * Cg / 8.0, bending moment from Megyesy, beam formulas, case 11, fixed beam. Ft = Bolt Load = Allowable Stress * Area s = Allowable stress, 1.5 * plate allowable Z = Section Modulus, from Megyesy, Properties of Sections Z = Wt * t2 / 6.0 Wt = (Do/2.- Ds/2.- db) = Width of Section Required Thickness of Gussets in Tension

If there are gussets, they must be analyzed for both tension and compression. The stress formula in tension is just the force over the area, where the force is taken to be the allow-


20-3



able bolt stress times the bolt area, and the area of the gusset is the thickness of the gusset times one half the width of the gusset (because gussets normally taper). Required Thickness of Gussets in Compression

In compression (as a column) we must iteratively calculate the required thickness. Taking the actual thickness as the starting point, we perform the calculation in AISC 1.5.1.3. The radius of gyration for the gusset is taken as 0.289 t per Megyesy, Fifth edition, page 404. The actual compression is calculated as described above, then compared to the allowed compression per AISC. The thickness is then modified and another calculation performed until the actual and allowed compressions are within one half of one percent of one another. Base Ring Design

When the user requests a base ring design, the program performs the following additional calculations to determine the design geometry. Selection of Number of Bolts

This selection is made on the basis of Megyesy’s table in Pressure Vessel Handbook (Table C, page 67 in the fifth edition). Above the diameter shown, the selection is made to keep the anchor bolt spacing at about 24 inches. Calculation of Load per Bolt

This calculation is made per Jawad & Farr, equation 12.3: P = Where W = N = R = M =

-W / N + 2 * M / (N * R) Weight of vessel Number of bolts Radius of bolt circle Bending moment

Calculation of Required Area for each Bolt

This is just the load per bolt divided by the allowable stress. Selection of the Bolt Size

The program has a table of bolt areas, and selects smallest bolt with area greater than the area calculated above. Selection of Preliminary Base Ring Geometry

The table of bolt areas also contains the required clearances in order to successfully tighten the selected bolt (wrench clearances and edge clearances). The program selects a preliminary base ring geometry based on these clearances. Values selected at this point are the bolt circle, base ring outside diameter, and base ring inside diameter. Analysis of Preliminary Base Ring Geometry

Using the methods described above for the analysis section, the program determines the approximate compressive stress in the concrete for the preliminary geometry.

20-4




Selection of Final Base Ring Geometry

If the compressive stress calculated above is acceptable, then the preliminary geometry becomes the final geometry. If not, then the bolt circle and base ring diameters are scaled up to the point where the compressive stress will be acceptable. These become the final base ring geometry values. Analysis of Base Ring Thicknesses

The analysis then continues through the thickness calculation described above, determining required thicknesses for the base ring, top ring, and gussets. Basic Skirt Thickness The required thickness of the skirt under tension and compression loads is determined using the same formula used for the compressive stress in the concrete, except using the thickness of the skirt rather than the width of the base ring: s = -W / A - M * c / I Where W = Weight of vessel (worst case). M = Bending moment on vessel (worst case). A = Cross sectional area of skirt. c = Distance from the center of the base ring to the skirt (radius of skirt). I = Moment of inertia of the skirt cross section. In tension this actual stress is simply compared to the allowable stress, and the required thickness can be calculated directly by solving the formula for t. In compression, the allowable stress must be calculated from the ASME Code, per paragraph UG-23, where the geometry factor is calculated from the skirt thickness and radius, and the materials factor is found in the Code external pressure charts. As with all external pressure chart calculations, this is an iterative procedure. A thickness is selected, the actual stress is calculated, the allowable stress is determined, and the original thickness is adjusted so that the allowable stress approaches the actual stress. Stress in Skirt due to Gussets or Top Ring

If there are gussets or gussets and a top ring included in the base plate geometry, there is an additional load in the skirt. Jawad & Farr have analyzed this load and determined that the stress in the skirt due to the bolt load on the base plate is calculated as follows: s = (1.5 * F * b) / (PI * h * t ** 2) Where F = Total load in one bolt = load on one gusset b = Width of the gusset at the base t = thickness of the skirt h = height of the gusset. Jawad & Farr note that this stress should be combined with the axial stress due to weight and bending moment, and should then be less than three times the allowable stress. They thus categorize this stress as secondary bending. The program performs the calculation of this stress, and then repeats the iterative procedure described above to determine the required thickness of the skirt at the top of the base ring.


20-5

Discussion of Input


Discussion of Input Main Input Fields Base Ring Number

The base ring number should start out at 1 and increment by 1 for each successive base ring analyzed. A blank entry for the base ring number will cause PVElite not to analyze the data for that base ring. Base Ring Description

Enter an optional alpha-numeric description for the base ring to be analyzed. This may be a project number that will help keep track of the base ring. Analyze or Design Base Ring

The Base Ring program in PVElite can either analyze existing base rings or design new ones. Two valid entries are Analyze—Existing Base rings Design—New Base rings When in design mode, PVElite may change the following items: •

Number of Bolts

•

Size of Bolts

•

Bolt Circle Diameter

•

Outside Diameter of the Base ring

•

Inside Diameter of the Base ring

Temperature of Base Ring

Normally base rings operate at temperatures which are near ambient. If the base ring is at a higher temperature, enter it here, otherwise leave the default temperature. Thickness of Base Ring

Enter the actual thickness of base ring. Any allowances for corrosion or mill tolerance etc. should be subtracted from this entered thickness. PVElite will compute the required base ring thickness using the simplified method and the neutral axis shift method. The user entered thickness value will be used only for comparison. Base Ring\Skirt\Bolt Material Specification

Enter the base ring material. Plate materials such as SA-516 70 and SA-36 are commonly used. The material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If your material is not present, enter the allowable stresses at the base ring design metal temperature. Allowable Stress at Operating Temperature

If your base ring material is not in the database, enter the hot allowable stress here.

20-6



Discussion of Input


This field is for the base ring ambient allowable stress. Inside Diameter of Base Ring

Enter the inside diameter of the base ring. This entry must be greater than 0 and less than the bolt circle diameter and the base ring OD. If the you have specified the program to design the base ring, PVElite may change this value. A good approximation for the base ring ID should be entered when using either the analyze or design option. Outside Diameter of Base Ring

Enter the outside diameter of the base ring. This entry must be greater than the base ring ID and the bolt circle diameter. When in design mode, PVElite may change this value. Nominal Bolt Diameter

The nominal bolt diameters accepted by PVElite range between 1/2 and 4 inches (1.27 and 10.16) centimeters. Values outside of this range will not be accepted. When in design mode PVElite may change the nominal bolt diameter. The bolt diameters are Bolt Size(inches)

Root Area (sq. in.)

1/2 5/8 3/4 7/8 1 1 1/8 1 1/4 1 3/8 1 1/2 1 5/8 1 3/4 1 7/8 2 2 1/4 2 1/2 2 3/4 3 3 1/4 3 1/2 3 3/4 4

0.126 0.202 0.302 0.419 0.551 0.728 0.929 1.155 1.405 1.680 1.980 2.304 2.652 3.423 4.292 5.259 6.324 7.487 8.749 10.108 11.566

This information was adapted from Jawad & Farr, Structural Analysis and Design of Process Equipment, (c) 1984, p 425.


20-7

Discussion of Input


Number of Bolts

Enter the bolts that the base ring design calls for. If the BASE RINGS program is in design mode, it may change the number of bolts being used. The bolts are sized based on the maximum load per bolt in the operating case. The computation of the load per bolt is referenced in Jawad and Farr, equation 12.3. The number of bolts can be between 4 and 120. Diameter at Bolt Circle

Enter the diameter of the bolt circle. This value must be greater than the base ring Id and less than the base ring OD. When in design mode, PVElite may change the bolt circle diameter. Whenever this happens, it will be reported in the output. The word DESIGN will appear followed by the value and description of the input the program has changed. Bolt Table (TEMA, UNC, USER)

Enter the thread series identifier. If the option is picked you will be prompted to enter the root area of a single bolt. This information can be obtained from a standard engineering handbook. Nominal Compressive Stress of Concrete

Enter the Nominal Compressive stress of the Concrete to which the base ring is bolted. This value is f’c in Jawad and Farr or FPC in Meygesy. A typical entry is 3000 psi. Are Gussets to be Used?

If your base ring design includes the use of gusset plates, check this field, otherwise continue. Thickness of Top Ring Plate (if any)

If your base ring design incorporates a top ring, enter its thickness here. If a thickness greater than 0.0 is entered, PVElite will compute the required thickness of the top plate. If no top ring thickness is entered, PVElite will not perform top ring thickness calculations. Radial Width of Top Ring/Plate (if any)

Enter the radial width of the top ring or plate, if any. This is simply the half of (top ring OD - top ring ID). This value must be entered if you entered last field, and must be positive. Top Ring/Plate Type per Moss ( Type 3-Cap Plate, 4-Continuous Ring )

Enter the type of top Ring or Plate per Moss (Type 3 = Cap Plate, 4-Continuous Ring). Refer to Dennis Moss “Pressure Vessel Design Manual” p129. If type 3 or 4 is entered, the program will calculate per p130. External Corrosion Allowance

Enter the corrosion allowance that would be applied to the skirt, base plate, gussets and top ring. The external corrosion allowance will simply be added to the required thickness of these components.

20-8



Discussion of Input

Skirt Thickness

Enter the thickness of the skirt here. This entry must be greater than 0. PVElite will automatically compute the required skirt thickness for both combinations of bending and axial stress. PVElite uses the ASME code compression allowable B for axial stresses. Skirt Temperature

If the skirt is at an elevated temperature, enter it here. Normally, skirts are at ambient temperature. Outside Diameter of Skirt at Base

Enter the skirt Od at the junction of the skirt and base ring. This value should be greater than the base ring ID and less than the base ring bolt circle. Joint Efficiency for Skirt Weld at Bottom Head

Enter the joint efficiency for the weld that joins the skirt to the bottom head. This value depends on the weld detail used. Typical values range between 0.49 and 1.0. Skirt Diameter at Bottom Head

Enter the diameter of the skirt at the bottom head of the vessel. Not all skirts are cylindrical. Some skirts are cone shaped and as such have different diameters at the top and bottom. Dead Weight of Vessel

Enter the weight of the vessel with all peripheral equipment (ladders, cages, catwalks, packing) etc. The working fluid of the vessel should not be included here. This entry is optional and can be 0. Operating Weight of Vessel

Enter the operating weight of the vessel here. This includes all contents and associated “hardware”. This value must be greater than 0. Test Weight of Vessel

Enter the test weight of the vessel here. This weight will include the fluid used for the hydrotest of the vessel. This entry is optional and can be 0. Operating Moment of Base Ring

Enter the total moment exerted on the skirt by the wind, reboilers, attached piping etc. when the vessel is operating. This value must be greater than 0. Test Moment on Base Ring

Enter the test moment on the base ring. The entry for the test moment is optional and can be 0. Are Stress Multipliers to be Used?

If you wish to increase the allowable stress the program uses for the skirt design, check this field.


20-9

Pop-up Input Fields


Pop-up Input Fields User-Specified Root Area of a Single Bolt

If your base ring design calls out for special bolts, enter the root area of a single bolt in this filed. Note, however, this option is mutually exclusive from the design option. If this condition is detected, the numbers from Table 2 (UNC) will be used. Thickness of Gusset Plates

Enter the thickness of the gusset plates to be used for this base ring. Any allowances for corrosion should be considered when making this entry. Temperature for Gussets (if not ambient)

Enter the temperature for the gusset plates. Normally, the gussets will operate at ambient temperature. If the temperature is above ambient, enter it here. Height of Gussets

Enter the gusset dimension from the base ring to the top of the gusset plate. The forces in the skirt are transmitted to the anchor bolts through the gussets. Distance from Bolts to Gussets

Enter the distance from a bolt to the nearest gusset. Normally, each bolt will have two gussets. This distance would be 1/2 of the spacing between the gusset plates. Average Width of Gusset Plates

Enter the average width of the gusset plates. Number of Gussets per Bolt

Enter the number of gussets per bolt. Usually, each bolt will have 2 gusset plates associated with it. For base rings that have a large number of bolts, this may not always be the case. In these occasions, each bolt may have a single gusset plate associated with it. Elastic Modules for Plates

The elastic modulus is used to determine the allowable stress for plates in compression according to AISC. This is a required value. For most common steels, this value is 29E6 psi. Factor for the Skirt Allowable at the Skirt Top

This factor is multiplied by the skirt operating allowable wherever it is used. For example: The skirt allowable stress at the top would be = stress multiplier X joint efficient X skirt operating allowable. If you do not wish to use this value, enter a 1.00 for this value. This multiplier is usually between 1 and 2. Skirt Comp Allowable Mult for (B) at Base (OPE)

This factor will be multiplied by the Code compression allowable B for the operating case. PVElite will look at the minimum of this factor times its allowable and the skirt yield stress times its allowable multiplier. This minimum value will then be used, as a comparison to the actual compressive stress in the skirt.

20-10



Pop-up Input Fields

Skirt Comp Allowable Mult for (B) at Base (TEST)

This factor will be multiplied by the Code compression allowable B for the test case. PVElite will look at the minimum of this factor times its allowable times 1.5 and the skirt yield stress times its allowable multiplier. This minimum value will then be used, as a comparison to the actual compressive stress in the skirt. Skirt Comp Allowable Mult for (SY) at Base (OPE)

PVElite will multiply the skirt yield stress by this factor. The minimum of this result and the basic hot allowable stress times its factor will be the skirt operating allowable stress. This minimum value will then be used, as a comparison to the actual compressive stress in the skirt. Skirt Comp Allowable Mult for (SY) at Base (TEST)

PVElite will multiply the skirt yield stress by this factor. The minimum of this result and the basic hot allowable stress times its factor will be the skirt test allowable stress. This


20-11

Pop-up Input Fields


minimum value will then be used, as a comparison to the actual compressive stress in the skirt.

TOPWTH TTA

HG

DS DI DC DO

TBA

BND

CG TGA

Figure 20A - Geometry for The Base Ring Module

20-12



Example Problem


------------------------------------- Page

Basering Analysis : PVHB EXAMPLE

Input Echo, BASERING Number

1,

Analyze or Design the Basering Design Temperature for Basering Thickness of Basering

ITEM:

1,

04:10pm,

1

05/18/98

Description: PVHB EXAMPLE

AORD

A

RNGTMP

300.00

F

TBA

2.0000

in.

Basering Material

SA-516 70

Basering Operating Allowable Stress

BASOPE

17500.00

psi

Basering Ambient

BASAMB

17500.00

psi

Diameter of Basering

DI

47.0000

in.

Outside Diameter of Basering

DO

66.2500

in.

2.0000

in.

Inside

Allowable Stress

Nominal Diameter of Bolts

BND

Bolt Material

SA-193 B7

Bolt Operating Allowable Stress Bolt Ambient

Allowable Stress

Number of Bolts Diameter of Bolt Circle

Nominal Compressive Stress of Concrete

Thickness of Gusset Plates

SA

25000.00

psi

SABAMB

25000.00

psi

NGIV

12

DC

59.5000

in.

FPC

3000.0

psi

in.

TGA

.7500

Temperature for Gusset Plates

GUSTMP

100.0000

Average Width of Gusset Plates

AVGWDT

5.0000

Material for Gussets Gusset Plate Elastic Modulus

F in.

SA-516 70 E

29000000.0

psi

Gusset Plate Yield Stress

SY

38000.00

psi

Height of Gussets

HG

12.0000

in.

Distance from Bolts to Gussets

CG

4.0000

in.

Number of Gussets per bolt

NG

2

Thickness of Top Ring/Plate Radial Width of the Top Ring/Plate Top Ring or Plate Type per Moss

External Corrosion Allowance

Skirt Thickness Skirt Temperature

TTA

2.0000

in.

TOPWTH

6.1250

in.

TOPTYPE

4

CA

.0000

in.

TS

.5000

in.

SKTTEM

100.0000

Skirt Material

F

SA-516 70

Skirt Operating Allowable Stress

SKTOPE

17500.00

psi

Skirt Ambient

SKTAMB

17500.00

psi

DS

54.0000

in.

Outside Diameter of Skirt at Bottom Head

SKTHED

54.0000

in.

Joint Efficiency of Skirt Weld

ARCJNT

.4900

Allowable Stress

Outside Diameter of Skirt at Base

Dead Weight of Vessel Operating Weight of Vessel Test Weight of Vessel


DW

36000.0

lb.

ROW

36000.0

lb.

TW

36000.0

lb.

20-13

Example Problem


Operating Moment on Basering

ROM

692100.0

ft.lb.

TM

692100.0

ft.lb.

Test Moment on Basering

The Skirt Allowable Stress Multiplier

SAM

1.0000

The Skirt Allowable Multiplier (Operating) BXOPE

1.0000

The Skirt Allowable Multiplier (Test)

BXHYD

1.0000

Skirt Yield Stress Multiplier (Operating) SYXOPE

1.0000

Skirt Yield Stress Multiplier (Test)

1.0000

SYXHYD

RESULTS FOR BASERING ANALYSIS : ANALYZE OPTION Calculation of Load per Bolt, Operating Condition: W/Bolt = (( 4 * M/DC ) - W ) / RN per Jawad & Farr, Eq. 12.3 W/Bolt = (( 4 * 8305200 / 59.500) - 36000 ) / 12 W/Bolt = 43527.7300 lb.

Required Area for Each Bolt, Based on Max Load

1.7411

sq.in.

Area Available in a Single Bolt

2.6520

sq.in.

Area Available in all the Bolts

31.8240

sq.in.

Bolt Stress Based on Approximate Analysis

16413.17

Concrete Contact Area of Base Ring Concrete Contact Section Modulus of Base Ring

1712.22 21315.69

psi

sq.in. in.^3

Calculation of Concrete Load, Operating Condition: SC = ((ABT*SA+W)/CA) + M/CZ per Jawad & Farr Eq. 12.1 SC = (( 31.8240* 25000+ 36000)/ 1712.22) + 8305200/ 21315.69 SC = 875.31 psi

Calculation of Basering Thickness, (Simplified): TB = RW * SQRT( 3 * SC / S ) + CA per Jawad & Farr Eq. 12.12 TB = 6.1250 * SQRT( 3 * 875 / 26250 ) + .0000 TB = 1.9372 in.

Results of Neutral Axis Shift Calculation: Bearing Pressure on Concrete Stress in Bolt

478.85

psi

12548.70

psi

Calculation of Basering Thickness, (N.A. Shift): TBNA = RW * SQRT( 3 * SCNA / S) + CA per Jawad & Farr Eq. 12.12 TBNA = 6.1250 * SQRT( 3 * 478 / 26250 ) + .0000 TBNA = 1.4328 in.

Required Thickness of Top Ring/Plate in Tension: (Calculated as a fixed beam per Megyesy) FT = (SA*ABSS),

Bolt Allowable Stress * Area

RM = (FT*2.0*CG)/8.0,

Bending Moment

SB = (1.5*BASOPE),

Allowable stress * 1.5

WT = (TOPWTH

-

BND), Width of Section

T = SQRT( 6 * RM / ( SB * WT )) + CA T = SQRT( 6 * 66300 / ( 26250 * 4.1250 )) + .0000 T = 1.9167 in.

Required Thickness of Continuous Top Ring per Moss:

20-14



Example Problem

a

= ( Dc-Ds )/2

Skirt Distance to Bolt Circle

P

= Sa * Abss

Maximum Bolt Load

l

= Avgwdt

Average Gusset Width

g1 = Gamma 1

Constant Term f( b/l )

g2 = Gamma 2

Constant Term f( b/l )

g = Flat distance/2 Nut 1/2 Dimension (from Tema) Fb = ( 1.5 * Basope )

Allowable Stress

Mo = P/(4ã)[1.3(ln((2lsin(ãa/l)/(ãg)))+1]-g1*P/(4ã) Tc = ( 6 * Mo / Fb )^1/2 + CA

Required Thickness

Tc = ( 6 * 9425 / 26250 )^1/2 + .0000 Tc = 1.4678 in.

Required Thickness of Gusset in Tension: T = ( SA*ABSS )/( NG*S*( AVGWDT )) + CA Required thickness based on average cross-section

.3789

in.

Actual thickness as entered by user

.7500

in.

Required Thickness of Gusset in Compression, per AISC 1.5.1.3: 1. Allowed Compression at Given Thickness: Factor Kl/r Per 1.5.1.3.1

110.7266

Factor Cc Per 1.5.1.3.1

122.7360

All. Buckling Str. per 1.5.1.3.3

11779.41

psi

8840.00

psi

.6725

in.

Act. Buckling Str. at Given Thickness

Required Gusset thickness, + CA 2. Allowed Compression at Calculated Thickness: Factor Kl/r Per 1.5.1.3.1

123.4821

Factor Cc Per 1.5.1.3.1

122.7360

All. Buckling Str. per 1.5.1.3.2

9793.61

psi

Act. Buckling Str. at Calculated Thickness

9858.35

psi

Required Basering Thickness (simplfied)

1.9372

in.

Required Basering Thickness (N.A. Shift)

1.4328

in.

Actual Basering Thickness as entered by user

2.0000

in.

Required Top Ring/Plate Thickness as a Fixed-Beam

1.9167

in.

Required Top Ring Thickness per Moss(Type 4)

1.4678

in.

Actual Top Ring Thickness as entered by user

2.0000

in.

Required Gusset thickness, + CA

.6725

in.

Actual Gusset Thickness as entered by user

.7500

in.

SUMMARY OF BASERING THICKNESS CALCULATIONS

TENSILE STRESS CALCULATIONS FOR SKIRT AT TOP HEAD: S =

M/( PI*R^2*T ) - F/(2*PI*R*T)

Skirt Rad. Given by User Skirt Thkn. Given by User Bndg. Mom. Given by User Axial Force Given by User

Operating

Dead Load

27.0000

27.0000

.5000

.5000

692100

692100

Test Load 27.0000 in. .5000 in. 692100 ft.lb.

36000

36000

Actual Stress in Skirt

6828

6828

6828 psi

Allowed Stress in Skirt

8575

8575

12862 psi


36000 lb.

20-15

Example Problem


THICKNESS CALCULATION FOR SKIRT: Required Thickness

.3982

.3982

.2654 in.


.5000

.5000

.5000 in.

COMPRESSIVE STRESS CALCULATIONS AT BASE OF SKIRT: S = M/(PI*R^2*T) + F/(2*PI*R*T)

Skirt Rad. Given by User Skirt Thkn. Given by User Bndg. Mom. Given by User Axial Force Given by User Actual Stress in Skirt Allowed Stress in Skirt

Operating

Dead Load

27.0000

27.0000

Test Load

.5000

.5000

692100

692100

36000

36000

7677

7677

7677 psi

15506

15506

23260 psi

27.0000 in. .5000 in. 692100 ft.lb. 36000 lb.

THICKNESS CALCULATION FOR SKIRT AXIAL COMPRESSION: Required Thickness

.2835

.2835

.2092 in.


.5000

.5000

.5000 in.

SUMMARY OF SKIRT THICKNESS:

Operating

Dead Load

Test Load

Req. Thickness, Tension

.3982

.3982

.2654 in.

Req. Thickness, Comp.

.2835

.2835

.2092 in.


.5000

.5000

.5000 in.


20-16



&KDSWHU The Thin Joint Module

Introduction The Thin Joint Module calculates the stresses in a metal bellows expansion joint of the type typically used in piping systems and heat exchangers. The module does elastic stress analysis for stresses due to internal pressure and closing or opening of the joint. The maximum combined stress is used to calculate the cycle life of the joint, which is based on the appropriate formula in the ASME Code, Section VIII, Division 1, Appendix 26, 2001, A2001.

Purpose, Scope, and Technical Basis The purpose of the Thin Joint Module is to allow engineers and designers to evaluate or design metal bellows expansion joints. Since the module uses the ASME Code procedure for evaluating these joints, the calculations will be acceptable to fabricators, engineering contractors, and petrochemical companies. Thus a consistent design basis and a simple way to perform the calculations will be established, and individual engineers will be effective in evaluating these critical components. The module calculates the required thickness and elastic stresses using formulas in the ASME Section VIII Code, Division 1, Appendix 26. These formulas take into account both internal pressure and axial joint movement. The appendix covers expansion joints up to 1/8 inch thick, with multiple convolutions, and includes both reinforced and unreinforced expansion joints. Each curve in the appendix 26 was digitized. The program picks points off of the curves and interpolates for the results used in the stress calculations. These parameters are displayed as part of the output. If the selected joint is reinforced or unreinforced PVElite will perform the various stress and cycle life computations for that type of joint. Thus, there will be no extraneous output for a joint type that is not of interest. In addition, for reinforced expansion joints, the stresses in the reinforcing element and any bolted fastener which may be holding the ring together are calculated as well.

The Thin Joint Module

21-1



Discussion of Input Data Main Input Fields Item Number

Enter the thin walled expansion joint number. This should typically start out at 1 and increase by one for each expansion joint in the file. Description

Enter an alphanumeric description of the expansion joint in this field. This should relate in some way to the expansion joint i.e. (a project id). Design Cycle Life, Number of Cycles

Enter the number of cycles that the expansion joint is to be designed for. This value is to be compared to the total number of cycles that this design will be capable of handling. Design Temperature

Enter the design temperature of the expansion joint. During normal operation, expansion joints typically run cooler than the piping/pressure vessel. Determine that temperature and enter it here. Design Internal Pressure

Enter the internal pressure to be exerted on the expansion joint. This analysis is limited to internal pressure only. External pressure is not considered. Expansion Joint Opening Per Convolution

This is the value : e = design axial movement of joint per convolution For example, for a total design movement of 1 inch with an expansion joint that had 8 convolutions, this would result in e = 1/8 = .125 in/conv. Expansion Joint Bellows Material

Typical expansion joints are formed from various stainless steels, monels and inconels. An example of a material is SA-516 70. Allowable Stress at Operating Temperature

Enter the allowable stress of the bellows material at the operating temperature. If your material is not in the tables, these properties must be entered manually. Allowable Stress at Ambient Temperature

Enter the allowable stress of the bellows material at the ambient temperature. If your material is not in the tables, these properties must be entered manually.

21-2




Elastic Modulus at Design Temperature

Enter the modulus of elasticity for the bellows material at the bellows operating temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING. The table is C-6. Elastic Modulus at Ambient Temperature

Enter the modulus of elasticity for the bellows material at the bellows ambient temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING. The table is C-6. Material Category for Cycle Life Evaluation

Materials: Carbon Steel Low Alloy Steel Martensitic Stainless Austenitic Stainless Nickel Chrome Iron Nickel Copper Inside Diameter of Bellows

Enter the inside diameter of the bellows. This value will normally be equal to the pipe or vessel inside diameter. Some geometries are larger in diameter than the attached cylinder. Thus, the bellows id (d) will be larger than the vessel/pipe id. Convolution Depth

The convolution depth is the distance from the “top” of the convolution to the “trough” of the convolution. This is referred as the variable w in the ASME Code. Convolution Pitch

This is the distance between the “tops” of successive bellows convolutions. This is referred to as q in the ASME Code. Bellows Minimum Thickness Before Forming

Enter the nominal thickness of the plate that the expansion joint is to be made of before it is pressed or formed. Expansion joints are typically thin compared to the matching pipe. Reinforcing Ring Present

Some applications of expansion joints include a continuous reinforcing ring which lies in the convolutions. If your application includes a reinforcing ring, check this field. Fastener Bolt Present

If the expansion design includes a reinforcing ring, it may be held together by a bolted geometry in lieu of a welded ring geometry. If your application includes a fastener, check this field.


21-3

Pop-Up Input Fields


Pop-Up Input Fields Reinforcing Ring Cross-Sectional Area

Enter the cross sectional metal area of the reinforcing ring. Typical reinforcing rings can be circular in shape or tear-drop shaped. Reinforcing Ring Material

Enter the reinforcing ring material. An example of a material is SA-516 70. The material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Ring Material Allowable Stress at Operating Temperature

Enter the allowable stress of the ring material at the operating temperature. If your material is not in the tables, these properties must be entered manually. Ring Material Allowable Stress at Ambient Temperature

Enter the allowable stress of the ring material at the ambient temperature. If your material is not in the tables, these properties must be entered manually. Elastic Modulus at Ambient Temperature

Enter the modulus of elasticity for the bellows material at the bellows ambient temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING. The table is C-6. Fastener Cross-Sectional Area

Enter the cross-sectional root area of one bolt that retains the reinforcing ring. Effective Length of Fastener Bolt

Enter the effective length of the bolt that is being stressed. This is typically the distance from the center of the nut to the center of the head on the bolt. Fastener Material Specification

Enter the fastener material. An example of a material is SA-516 70. The material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Fastener Allowable Stress at Operating Temperature

Enter the allowable stress of the fastener material at the operating temperature. If your material is not in the tables, these properties must be entered manually. Fastener Allowable Stress at Ambient Temperature

Enter the allowable stress of the fastener material at the ambient temperature. If your material is not in the tables, these properties must be entered manually.

21-4



Pop-Up Input Fields

Elastic Modulus at Ambient Temperature

Enter the modulus of elasticity for the bellows material at the bellows ambient temperature. Tables of elasticity versus temperature can be found in the ANSI/ASME B31.3 CODE for PRESSURE PIPING. The table is C-6. q

W

d diam

tm UNREINFORCED BELLOWS

F

A-A

A Reinforcing rings

AF Equalizing ring

q A End equalizing ring

W tm Ar Ar

d diam

REINFORCED BELLOWS

Figure 21A - Geometry for the Thin Joint Module


21-5

Example Problems


Example Problems The following two example problems were adapted from ASME Section VIII Div. 1 Appendix 26. The first example is for an unreinforced geometry, while the second example is for a reinforced geometry. Agreement for the results is excellent with the exception of the reinforced example problem. As of this printing the value Ar (area in the reinforcement) in the ASME problem was incorrect. Thus the computed value in the Code for Sarcoma is also incorrect. All of the other results are in good agreement. FileName: CHECKS --------------------------------- Page

Thinjnt Analysis :APP BB-8, A

Input Echo, THINJNT Number

ITEM:

1,

1,

04:23pm,

1

05/18/98

Description: APP BB-8, A

Design Cycle Life, Number of Cycles

NCYC

1800

Design Temperature of Expansion Joint

TEMP

200.0

F


P

150.0

psig

Expansion Joint Opening Per Convolution

E

.1250

in.

MAT1

SA-240 304

Material of Expansion Joint Bellows Bellows Operating Allowable Stress

ALLST1

17800.0

psi

Bellows Elastic Modulus at Design Temp.

EMOD1

.27700E+08

psi

Bellows Elastic Modulus at Ambient Temp.

EAMB1

.2830E+08

psi

Material Category for Cycle Life Evaluation AUSTENITIC STAINLESS

Inside Diameter of Bellows

D

24.0

in.

Convolution Depth

W

1.0000

in.

Convolution Pitch

Q

1.1250

in.

Bellows Minimum Thickness before Forming

TM

.0500

in.

Fatigue Strength Reduction Factor

Kg

1.0000

Nominal Bellows Thickness Based on given Minimum T = ( TM * SQRT( D/( D + W ) ) ) T = ( .0500 * SQRT( 24.00/( 24.00 + 1.0000 ) ) ) T =

.0490 in.

Cross Sectional Area of Bellows AB = ( 0.571 * Q + 2.0 * W ) * T AB = ( 0.571 * 1.1250 + 2.0 * 1.0000 ) * .0490 AB =

.1294 sq.in

Final Reinforcement Ratio = 1.0000

Minimum Required Thickness for Unreinforced Bellows Tu = P*(D+W)/(ALLST1*(1.14+4.0*W/Q)) Tu =

150.0*( 24.0+ 1.0000)/( 17800.0*(1.14+4.0* 1.0000/ 1.1250))

Tu =

.0449 in.

Required Bellows Thickness for Pressure = .0449 in.

Actual Knuckle Radius for one Convolution

21-6



Example Problems

RKN = ( Q / 4 - TM / 2 ) RKN = ( 1.1250 / 4 - .0500 / 2 ) RKN = .2562 in.

Allowed Knuckle Radius for one Convolution TM3 = 3.0 * TM = .1500 in.

Stiffening Factor for Bellows Under Pressure RKS = 0.3-( 100.0/( 0.6 * P**1.5 + 320.0 ) )**2 RKS = 0.3-( 100.0/( 0.6 * 150.0**1.5 + 320.0 ) )**2 RKS = .2951

SUMMARY for PRESSURE CALCULATIONS : Nom. Bellows Thickness based on given Minimum

T

.0490

in.

TREQ

.0449

in.

Knuckle Radius for One Convolution

RKN

.2562

in.

Allowed Knuckle Radius for One Convolution

3*TM

.1500

in.

Cross-Sectional Area for One Convolution

Ab

.1294

sq.in.

Fraction of Pressure Resisted by Bellows

R

1.0000

RKS

.2951

q/2W

.56250

q/(2.2((d+w)**.5 *t))

.46207

Required Bellows Thickness for Pressure Actual

Stiffening Factor for Bellows under Pressure

SUMMARY of FIGURES BB-3, BB-4, BB-5 Horizontal Figure Factor Vertical

Figure Factor

Value Interpolated from Figure BB-3, Cp

Cp

.63207

Value Interpolated from Figure BB-4, Cf

Cf

1.74880

Value Interpolated from Figure BB-4, Cd

Cd

1.78330

STRESS RESULTS for UNREINFORCED BELLOWS Circumferential Stress in the Bellows SCMPU = P*(D+W)/(T*(1.14+4.0*W/Q)) SCMPU = 150.0*( 24.0+ 1.0000)/( .0490*(1.14+4.0* 1.0000/ 1.1250)) SCMPU = 16301.9 psi

Meridional Membrane Stress due to Pressure SMMPU = ( P*W )/( 2.0*T ) SMMPU = ( 150.0 * 1.0000 )/( 2.0 * .0490 ) SMMPU = 1530.9 psi

Meridional Bending Stress due to Pressure SMBPU = ( P * W * W * CP )/( 2.0 * T * T ) SMBPU = ( 150.0* 1.0000* 1.0000* .63207 )/( 2.0 * .0490 * .0490 ) SMBPU = 19752.2 psi

Meridional Membrane Stress due to Deflection SMMDU = ( EAMB1*T*T*E )/(2.0*W^3*Cf ) SMMDU = ( 28300000* .0490* .0490* .1250 )/(2.0* 1.0000^3* 1.74880 ) SMMDU = 2427.4 psi

Meridional Bending Stress due to Deflection SMBDU = 5.0*EAMB1*T*E/(3.0*W*W*CD) SMBDU = 5.0* 28300000* .0490* .1250/(3.0* 1.0000* 1.0000* 1.78330) SMBDU = 161967.2 psi


21-7

Example Problems


Summation of all Meridional Stresses STOTU = (SMBDU+SMMDU+SMBPU+SMMPU) = 185677 psi

The Total Cycle Life CYCU = (FM/((FN*RKG*STOTU/EMOD1)-FO))** 2.00 CYCU = (

2.5/(( 14.2* 1.0000* 185677/ 27700000)- .020))**2

CYCU = 1106.

Maximum Stress for Given Cycle Life SMAXC = (FM/(RNCYC**(1/2.00))+FO)*(EMOD1/FN*RKG) SMAXC = ( 2.5/( 1800**(1/2.00))+ .020)*( 27700000/ 14.2* 1.0000) SMAXC = 153960.4 psi

STRESSES in BELLOWS, psi

Actual

Allowed

Circumferential membrane, pressure

Scmp

16301

17800

Meridional Membrane, pressure

Smmp

1530

17800

Meridional Bending , pressure

Smbp

19752

Meridional Membrane, deflection

Smmd

2427

Meridional Bending , deflection

Smbd

161967

Meridional Membrane + Bending , pressure Summation of all Meridional Stresses

Stress Amplitude for Cycle Life Evaluation Cycle Life for Bellows

21283

26700

185677

153960

185677 1105


21-8



Example Problems

FileName : CHECKS

------------------------------------

Thinjnt Analysis :APP BB-8, B

Input Echo, THINJNT Number

2,

ITEM:

2,

Page

04:23pm,

1 05/18/98

Description: APP BB-8,

Design Cycle Life, Number of Cycles

NCYC

900

Design Temperature of Expansion Joint

TEMP

200.0

F


P

450.0

psig

Expansion Joint Opening Per Convolution

E

.1000

in.

MAT1

SA-240 304

Material of Expansion Joint Bellows Bellows Operating Allowable Stress

ALLST1

17800.0

psi

Bellows Elastic Modulus at Design Temp.

EMOD1

.27700E+08

psi

Bellows Elastic Modulus at Ambient Temp.

EAMB1

.2830E+08

psi

B

Material Category for Cycle Life Evaluation AUSTENITIC STAINLESS

Inside Diameter of Bellows

D

24.0

in.

Convolution Depth

W

1.2500

in.

Convolution Pitch

Q

1.1250

in.

Bellows Minimum Thickness before Forming

TM

.0600

in.

Fatigue Strength Reduction Factor

Kg

1.0000

Reinforcing Ring Cross Sectional Area Reinforcing Ring Material Operating Allowable Stress of Ring Ambient Elastic Modulus of Ring

AR

.1963

MAT2

SA-240 304

sq.in.

ALLST2

17800.0

psi

EMOD2

27700000.0

psi

Nominal Bellows Thickness Based on given Minimum T = ( TM * SQRT( D/( D + W ) ) ) T = ( .0600 * SQRT( 24.00/( 24.00 + 1.2500 ) ) ) T =

.0585 in.

Cross Sectional Area of Bellows AB = ( 0.571 * Q + 2.0 * W ) * T AB = ( 0.571 * 1.1250 + 2.0 * 1.2500 ) * .0585 AB =

.1838 sq.in

Reinforcement Ratio, Reinforcement RC = ( AB * EMOD1 )/( AR * EMOD2 ) RC = ( .1838 * 27700000 )/( .1963 * 27700000 ) RC =

.9364

Final Reinforcement Ratio = .9364

Minimum Required Thickness for Reinforced Bellows Tr = P*(D+W)/(ALLST1*(1.14+4*W/Q))*(R/(R+1.0)) Tr =

450.0*( 24.0+ 1.2500)/( 17800.0*(1.14+4.0* 1.2500/ 1.1250)) * ( .9364 /( .9364 + 1.0 ) )

Tr =

.0553 in.

Required Bellows Thickness for Pressure = .0553 in.

Actual Knuckle Radius for one Convolution


21-9

Example Problems


RKN = ( Q / 4 - TM / 2 ) RKN = ( 1.1250 / 4 - .0600 / 2 ) RKN = .2512 in.

Allowed Knuckle Radius for one Convolution TM3 = 3.0 * TM = .1800 in.

Stiffening Factor for Bellows Under Pressure RKS = 0.3-( 100.0/( 0.6 * P**1.5 + 320.0 ) )**2 RKS = 0.3-( 100.0/( 0.6 * 450.0**1.5 + 320.0 ) )**2 RKS = .2997

SUMMARY for PRESSURE CALCULATIONS : Nom. Bellows Thickness based on given Minimum

T

.0585

in.

TREQ

.0553

in.

Knuckle Radius for One Convolution

RKN

.2512

in.

Allowed Knuckle Radius for One Convolution

3*TM

.1800

in.

Cross-Sectional Area for One Convolution

Ab

.1838

sq.in.

Fraction of Pressure Resisted by Bellows

R

.9364

RKS

.2997

q/2W

.45000

q/(2.2((d+w)**.5 *t))

.42076

Required Bellows Thickness for Pressure Actual

Stiffening Factor for Bellows under Pressure

SUMMARY of FIGURES BB-3, BB-4, BB-5 Horizontal Figure Factor Vertical

Figure Factor

Value Interpolated from Figure BB-3, Cp

Cp

.68792

Value Interpolated from Figure BB-4, Cf

Cf

1.62577

Value Interpolated from Figure BB-4, Cd

Cd

1.62942

STRESS RESULTS for REINFORCED BELLOWS Circumferential Stress in the Bellows SCMPR = P*(D+W)/(T*(1.14+4*W/Q))*(R/(R+1.0)) SCMPR = 450.0*( 24.0+ 1.2500)/( .0585*(1.14+4.0* 1.2500/ 1.1250)) * (

.9364 / ( .9364 + 1.0 ) )

SCMPR = 16820.4 psi

Meridional Membrane Stress due to Pressure SMMPR = P*( W-RKS*RKG*Q )/( 2.0 *T ) SMMPR = 450.0*( 1.2500- .2997* 1.0000* 1.1250 )/( 2.0 * .0585 ) SMMPR = 3511.0 psi

Meridional Bending Stress due to Pressure SMBPR = (P/2.0)*CP*((W-RKS*RKG*Q)/T)^2 SMBPR = ( 450.0 / 2.0 ) * .68792 * ( ( 1.2500- .2997* 1.0000* 1.1250)/T )^2 SMBPR = 37690.3 psi

Meridional Membrane Stress due to Deflection SMMDR = (EAMB1*T*T*E)/(2*CF*(W-RKS*RKG*Q)^3) SMMDR = ( 28300000 * .0585 * .0585 * .1000 ) / ( 2 * 1.62577 * ( 1.2500- .2997* 1.0000* 1.1250 )^3 ) SMMDR = 3915.7 psi

Meridional Bending Stress due to Deflection SMBDR = (5*EAMB1*T*E)/(3*CD*(W-RKS*RKG*Q)^2)

21-10



Example Problems

SMBDR = 5 * 28300000 * .0585 * .1000 / ( 3.0*

1.62942 * ( 1.2500- .2997* 1.0000* 1.1250 )^2 )

SMBDR = 203222.1 psi

Stresses in the Reinforcement SRCMP = (P*Q*(D+W)*(1/(RC+1)))/(2*AR) SRCMP = ( 450.0* 1.1250*( 24.0+ 1.2500)*(1/( .9364+1)))/(2* .1963) SRCMP = 16814.3 psi

Summation of all Meridional Stresses STOTR = (SMBDR+SMMDR+SMBPR+SMMPR) = 248339 psi

The Total Cycle Life CYCR = (FM/((FN*RKG*STOTR/EMOD1)-FO))** 2.00 CYCR = (

2.5/(( 14.2* 1.0000* 248339/ 27700000)- .020))**2

CYCR = 543.

Maximum Stress for Given Cycle Life SMAXC = (FM/(RNCYC**(1/2.00))+FO)*(EMOD1/FN*RKG) SMAXC = ( 2.5/( 900**(1/2.00))+ .020)*( 27700000/ 14.2* 1.0000) SMAXC = 201572.8 psi

STRESSES in BELLOWS, psi

Actual

Allowed

Circumferential membrane, pressure

Scmp

16820

17800

Meridional Membrane, pressure

Smmp

3511

17800

Meridional Bending , pressure

Smbp

37690

Meridional Membrane, deflection

Smmd

3915

Meridional Bending , deflection

Smbd

203222

Meridional Membrane + Bending , pressure Summation of all Meridional Stresses

41201

53400

248339

201572

Stress Amplitude for Cycle Life Evaluation

248339

Cycle Life for Bellows

542

STRESSES in REINFORCEMENT, psi Circumferential Membrane,

pressure

Actual

Allowed

16814

17800



21-11

Example Problems

21-12




&KDSWHU The Thick Joint Module

Introduction This module applies to fixed tubesheet exchangers which require flexible elements to reduce shell and tube longitudinal stresses, tubesheet thickness, or tube-to-tubesheet joint loads. Light gauge bellows type expansion joints within the scope of the Standards of the Expansion Joint Manufacturers Association (EJMA) are not included within the purview of this paragraph. The analysis contained within these paragraphs are based upon the equivalent geometry used in “Expansion Joints for Heat Exchangers” by S. Kopp and M.F. Sayre; however, the formulas have been derived based upon the use of plate and shell theory. Flanged-only and flanged-and-flued types of expansion joints can be analyzed with this method. (TEMA 8th Edition, Paragraph RCB-8, page 61). The formulas contained in the module are applicable based on the following assumptions: •

Applied loadings are axial

•

Torsional loads are negligible

•

The flexible elements are sufficiently thick to avoid instability.

•

The flexible elements are axisymmetric.

•

All dimensions are in inches and all forces are in pounds.

(TEMA Eighth Edition, Paragraph RCB-8.1, page 61: note that other systems of units may be used for input and output, since the program converts these to inches and pounds for its internal calculations.) The sequence of calculation used by the program is as follows: 1. Select a geometry for the flexible element per RCB-8.21 (user input) 2. Determine the effective geometry constants per RCB-8.22. 3. Calculate the flexibility factors per RCB-8.3 4. Calculate the flexible element geometry factors per RCB-8.4 5. Calculate the overall shell spring rate with all contributions from flexible shell elements per RCB-8.5 6. Calculate Fax for each condition as shown in Table RCB-8.6. This requires that you run the PVElite Tubesheet module to determine the differential expansion and shellside and tubeside equivalent pressures. 7. Calculate the flexible element stresses per RCB-8.7

The Thick Joint Module

22-1

Introduction


8. Compare the flexible element stresses to the appropriate allowable stresses per the Code, for the load conditions as noted in step 6. 9. Modify the geometry and rerun the program if necessary.

Note

More than one analysis may be needed to evaluate hydrotest and uncorroded conditions.

Figure 22A shows geometry for the Thick Joint module. (TEMA Figure RCB-8.21 and RCB-8.22). Both the input geometry and the equivalent geometry used for the analysis are shown. The discussion of input data below uses the nomenclature shown on this figure. A recent computational change was made to the program to allow users to better comply with the design rules for allowable stresses per appendix CC of the ASME Code. In previous versions, the program designed expansion joints based on fatigue analysis techniques. The default behavior for computation of the allowables has not changed. If you prefer to design per CC then check the Use App CC box. Also the program uses the minimum of the expansion joint allowable stress and the shell allowable stress for the default to use when designing for the shellside pressure case. If you wish to use the expansion joint allowable only, then check the Use EXP. Jt. Allowables box.

22-2




Discussion of Input Data Main Input Fields Expansion Joint Number

Enter an ID number for the Expansion Joint. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Expansion Joint Description

Enter an alpha-numeric description for this item. This entry is optional. Design Temperature for Shell and Expansion Joint

Enter the temperature associated with the internal design pressure. The PVElite program will automatically update materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Expansion Joint Inside Diameter

Enter the inside diameter of the expansion joint bellows. Note that this is not the diameter at the shell, but the inside diameter at the outside of the bellows. This value is shown on Figure 22A as ID. Expansion Joint Outside Diameter

Enter the outside diameter of the expansion joint bellows. Note that this is not the diameter at the shell, but the outside diameter at the outside of the bellows. This value is shown on Figure 22A as OD. Expansion Joint Flange (Minimum) Wall Thickness

Enter the minimum thickness of the flange or web of the expansion joint, after forming. This will usually be somewhat thinner than the unformed metal. This value is shown on Figure 22A as te. Expansion Joint Corrosion Allowance

Enter the corrosion allowance for the expansion joint. This value will be subtracted from the minimum thickness of the flange or web for the joint. Material Name

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not con-


22-3



tained in the database, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Note that the program uses the external pressure charts to determine the modulus of elasticity and material type for the analysis. Allowable Stress at Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Expansion Joint Allowable Stress at Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the ambient temperature. Shell Inside Diameter

Enter the inside diameter of the shell at the point where the expansion joint is attached. This value is shown on Figure 22A as G. Shell Wall Thickness

Enter the actual wall thickness of the shell at the point where the expansion joint is attached. This value is shown on Figure 22A as ts. Shell Corrosion Allowance

Enter the corrosion allowance for the shell wall. Shell Cylinder Length

Enter the length of the shell cylinder to the nearest body flange or head. TEMA Paragraph RCB 8-21 included the following note: lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if less than the cylinder length. This value is shown on Figure 22A as li.

22-4




Expansion Joint Inside Knuckle Offset (Straight Flange)

Enter the distance from the shell cylinder to the beginning of the knuckle for an expansion joint with an inside knuckle. Enter the distance from the shell cylinder to the intersection of the expansion joint web and the shell diameter for joints with a square inside corner. Note that in both cases this distance is frequently zero. This value is shown on Figure 22A as fa. Expansion Joint Inside Knuckle Radius

Enter the knuckle radius for an expansion joint with an inside knuckle. Enter zero for an expansion joint with a sharp inside corner. This value is shown on Figure 22A as ra. Expansion Joint Outside Knuckle Offset

Enter the distance from the outer cylinder to the beginning of the knuckle for an expansion joint with an inside knuckle. Enter the distance from the outer cylinder to the intersection of the expansion joint web and the outer diameter for joints with a square outside corner. Note that in both cases this distance is frequently zero, and that for an expansion joint with a outside radius but no outside cylinder, this distance is the distance from the end of the knuckle to the symmetrical centerline of the joint. This value is shown on Figure 22A as fb. Expansion Joint Outside Knuckle Radius

Enter the knuckle radius for an expansion joint with an outside knuckle. Enter zero for an expansion joint with a sharp outside corner. (Flanged Only) This value is shown on Figure 22A as rb. Use Appendix CC ?

Check this box to use the ASME Sec. VIII, Div.1, APP-CC design rules for allowable stresses. Otherwise the program will use the fatigue analysis techniques. Use Expansion Joint Allowable Stress

The program uses the minimum of the expansion joint allowable stress and the shell allowable stress for the shellside pressure case. Check this box if you wish to use the expansion joint allowable value only. Is There an Outer Cylinder?

Check this field if there is a cylindrical section attached to the expansion joint at the OD. This will always be true when you have an expansion joint with only a half convolute. It may also be true when there is a relatively long cylindrical portion between two half convolutes, as in the case of certain inlet nozzle geometries for heat exchangers.


22-5



Differential Expansion Pressure (from Tubesheet)

You need to run the PVElite Tubesheet program in order to determine this value. It is listed in the output from the TEMA tubesheet analysis of fixed tubesheet exchangers. Shellside Design Pressure

You do not need to run the PVElite Tubesheet program to get this value - it is simply the design pressure for the shell. Shellside Prime Design Pressure (from Tubesheet)

You need to run the PVElite Tubesheet program in order to determine this value. It is listed in the output from the TEMA tubesheet analysis. Shellside Prime Design Pressure (from Tubesheet) Corroded

You need to run the PVElite Tubesheet program in order to determine this value. It is listed in the output from the TEMA tubesheet analysis. As of version 4.1 of PVElite, the TEMA tubesheet module computes the Shellside Prime Design Pressure, in both corroded and uncorroded conditions. Tubeside Design Pressure

You do not need to run the PVElite Tubesheet program to get this value - it is simply the design pressure for the channel. Tubeside Prime Design Pressure (from Tubesheet)

You need to run the PVElite Tubesheet program in order to determine this value. It is listed in the output from the TEMA tubesheet analysis. Tubeside Prime Design Pressure (from Tubesheet) Corroded

You need to run the PVElite Tubesheet program in order to determine this value. It is listed in the output from the TEMA tubesheet analysis. As of version 4.1 of PVElite, the TEMA tubesheet module computes the Tubeside Prime Design Pressure, in both corroded and uncorroded conditions. Analyze Differential Expansion?

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Differential Expansion Pressure (from Tubesheet) Corroded

You need to run the PVElite Tubesheet program in order to determine this value. It is listed in the output from the TEMA tubesheet analysis. As of version 4.1 of PVElite, the TEMA tubesheet module computes the Differential Expansion Pressure, in both corroded and uncorroded conditions.

22-6




Analyze Shellside Pressure

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Analyze Tubeside Pressure

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Analyze Shellside + Tubeside Pressure

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Analyze Shellside + Differential Expansion

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Analyze Tubeside + Differential Expansion

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout. Analyze Shellside + Tubeside + Differential Expansion

Check this field if you wish to run an analysis for this case. We recommend that you analyze all the cases at first, but you may wish to eliminate some cases that are not controlling from the final printout.

Pop-Up Input Fields Outer Cylindrical Element Thickness

Enter the actual wall thickness of the outer cylindrical element at the point where the expansion joint is attached. This value is shown on Figure 22A as to. Outer Cylindrical Element Corrosion Allowance

Enter the corrosion allowance for the outer cylindrical element. Outer Cylindrical Element Length

Enter the length of the outer cylinder to the nearest body flange or head, or to the centerline of the convolute. TEMA Paragraph RCB 8-21 includes the following note: lo and li are the lengths of the cylinders welded to the flexible shell elements except, where two flexible shell elements


22-7



are joined with a cylinder between them, lo or li as applicable shall be taken as half the cylinder length. If no cylinder is used, lo and li shall be taken as zero. Entering a very long length for this value will not disturb the results, since the TEMA procedure automatically takes into account the decay length for shell stresses and uses this length if less than the cylinder length. This value is shown on Figure 22A as lo.

22-8




Discussion of Results The three most significant results for the THICK JOINT analysis are the spring constant for the joint, the stresses in the joint, and the cycle life for the joint. These are discussed below. Spring Constant

The program does not calculate the deflection of the joint. Instead it calculates the spring constant for the joint, which can be used in the Tubesheet program or elsewhere to determine the effect of the joint on the heat exchanger design. Stresses

The program calculates the combined meridional bending and membrane stresses in the expansion joint and the attached cylinders. According to ASME, Section VIII, Division 1, Appendix CC, this stress should be limited to KS, where K is 1.5 for flat sections (the annular ring or cylinders) and 3.0 for curved areas of the inner and outer torus (or sharp corners). S is the basic allowable stress for the expansion joint material at operating temperature. Note, however, that this stress limit applies only to the stresses due to pressure stresses due to deflection are limited by fatigue considerations rather than stress allowables. Thus the program only prints the allowable membrane plus bending stress for the case of shellside pressure. Cycle Life

The cycle life of the joint is analyzed using the rules in the ASME Code, Section VIII, Division 1, Appendix CC. For Series 3xx stainless steels, nickel-chromium iron alloys, nickel-iron chromium alloys and nickel-copper alloys, the equation for cycle life is as follows: N < [(2.2)/(( 14.2*Kg*Sn)/Eb - 0.03 )]^2.17 For carbon and low alloy steels, Series 4xx stainless steels, and high alloy steels, the equation for cycle life is: N < [(2.0)/(( 15*Kg*Sn)/Eb - 0.011 )]^2.17 Where: Kg = fatigue strength reduction factor which accounts for geometrical stress concentration factors due to local thickness variations, weld geometries, and other surface conditions. The range of Kg is 1.0 <= Kg <= 4.0 with its minimum value for smooth geometrical shapes and its maximum for 90 deg. welded corners and fillet welds. The program uses a Kg of 1.0 when the knuckle radius is greater than three times the expansion joint thickness. Sn = Maximum combined meridional membrane and bending stress range in a flexible element due to the cyclic components of pressure and deflection. Eb = Modulus of elasticity at design temperature. The program determines both the modulus of elasticity and the material type from the name of the external pressure chart given by


22-9



the user. To check the name of the external pressure chart in your input, move to the material name and press [E] (Material Edit).

Figure 22A - Geometry for the Thick Joint Module

22-10



Example Problem


---------------------------------- Page

Thickjnt Analysis : COMP. TO ANSYS

Input Echo, THICKJNT Number

ITEM:

1,

Design Temperature for Expansion Joint

1,

1

04:30pm,

05/18/98

Description: COMP. TO ANSYS

TEMP

214.3000

Inside Diameter of Expansion Joint

RID

33.0000

in.

Outside Diameter of Expansion Joint

ROD

34.0000

in.

TE

.4378

in.

CAE

.0000

in.

Wall thickness of Expansion Joint Corrosion Allowance for Expansion Joint Material for Expansion Joint

F

SA-240 316

Operating Allowable Stress, Expansion Joint

SOE

18742.80

psi

Ambient

SAE

18800.00

psi

Allowable Stress, Expansion Joint


G

25.2500

in.

TS

.3750

in.

Corrosion Allowance for Shell

CAS

.0000

in.

Length of Shell Cylinder

RLI

40.0000

in.

Wall thickness of Shell

Material for Shell

SA-516 70

Operating Allowable Stress, Shell

SOS

17500.00

psi

Ambient

SAS

17500.00

psi

Length of Straight Flange, Joint ID

FA

1.0000

in.

Radius of Knuckle, Joint ID

RA

1.5000

in.

Length of Straight Flange, Joint OD

FB

1.0000

in.

Radius of Knuckle, Joint OD

RB

1.5000

in.

Allowable Stress, Shell

Thickness of Outer Cylinder

TO

.5000

in.

Corrosion Allowance for Outer Cylinder

CAO

.0000

in.

Length of Outer Cylinder

RLO

1.0000

in.

Outer Cylinder Material Name

SA-240 316

Operating Allowable Stress, Outer Cylinder

SOO

18742.80

psi

Ambient

SAO

18800.00

psi

Differential Expansion Pressure

PD

515.9200

psig

Shellside Design Pressure

PS

200.0000

psig

PSP

-38.7500

psig

PT

100.0000

psig

PTP

86.8900

psig

Allowable Stress, Outer Cylinder

Shellside Prime Design Pressure Tubeside Design Pressure Tubeside Prime Design Pressure

Analyze for Differential Expansion

Y

Analyze for Shellside Pressure

Y

Analyze for Tubeside Pressure

Y

Analyze for Shellside + Tubeside Pressure

Y

Analyze for Shellside + Differential Expansion

Y

Analyze for Tubeside

Y

+ Differential Expansion

Analyze for Shellside + Tubeside + Differential

N

Results per TEMA 1988 :

TEMA Paragraph RCB 8.22 Effective Geometry Constants:


22-11

Example Problem


Ta

= IF(RA<>0,Te,Ts)

.4378

in.

Tb

= IF(RA<>0,Te,To)

.4378

in.

A

= ( G + TA ) / 2.0

12.8439

in.

B

= (ROD-TB)/2-(4-PI)*(RA+RB)/4

16.1373

in.

RLA = FA + PI * RA / 4.0 + TE / 2.0

2.3970

in.

RLB = FB + PI * RB / 4.0 + TE / 2.0

2.3970

in.

YA

= MIN ( RLA + RLI, 2 * SQRT ( A * TA ) )

4.7426

in.

YB

= MIN ( RLB + RLO, 2 * SQRT ( B * TB ) )

3.3970

in.

TEMA Paragraph RCB 8.30 Element Flexibility Factors: Elastic Modulus for Expansion Joint Material EE

.272E+08 psi

Elastic Modulus for Shell Material

ES

.290E+08 psi

Elastic Modulus for Outer Cylinder Matl.

EO

.272E+08 psi

EA = IF (RA <> 0, EE, ES)

.272E+08 psi

EB = IF (RB <> 0, EE, EO)

.272E+08 psi

Ba = 1.285 / SQRT( A * TA )

.5419 1/in.

Bb = 1.285 / SQRT( B * TB )

.4834 1/in.

Da = 0.0916 * EA * TA**3

209069.20 in. lb.

Db = 0.0916 * EB * TB**3

209069.20 in. lb.

De = 0.0916 * EE * TE**3

209069.20 in. lb.

Wa

= 2 * BA * YA

5.1400

RJ1A = SIN( WA / 2.0 ) * SINH( WA / 2 )

3.5134

RJ2A = COS( WA / 2.0 ) * COSH( WA / 2 )

-5.5266

ZZA = RJ1A**2 + RJ2A**2 RK0A =

42.8877

SINH( WA ) + SIN( WA )

84.4450

RK1A = ( COSH( WA ) + COS( WA ) ) / RK0A

1.0158

RK2A = ( SINH( WA ) - SIN( WA ) ) / RK0A

1.0216

RK3A = ( COSH( WA ) - COS( WA ) ) / RK0A

1.0059

Wb

= 2 * BB * YB

3.2845

RJ1B = SIN( WB / 2.0 ) * SINH( WB / 2 )

2.4803

RJ2B = COS( WB / 2.0 ) * COSH( WB / 2 )

-.1914

ZZB = RK0B =

RJ1B**2 + RJ2B**2 SINH( WB ) + SIN( WB )

6.1887 13.1872

RK1B = ( COSH( WB ) + COS( WB ) ) / RK0B

.9386

RK2B = ( SINH( WB ) - SIN( WB ) ) / RK0B

1.0216

RK3B = ( COSH( WB ) - COS( WB ) ) / RK0B

1.0887

TEMA Paragraph RCB 8.31 Cylinder Flexibility Factors: C1A = ( RLA / SQRT( A * TA ) ) C2A = ( TS / TA ) C3A = ( EA / ES ) C4A = -0.364661+(0.338172/C2A)-(0.0366351/C2A**2

1.0108 .8566 .9379 -.0198

C5A = -1.06871+(1.01164/C2A)-(0.122627/C2A**2)

-.0548

C6A = 0.0696709+(1.76415*C2A)-(5.46103*C2A**3)

-1.8512

C7A = -0.142734+(0.918656*C2A)-(2.00749*C2A**3)

-.6174

C8A = (C5A/C1A**2-C6A/C1A**3+C7A/C1A**4-C4A) /(C3A**0.2) EAA = 2.718**C8A

C1B = ( RLB / SQRT( B * TB ) ) C2B = ( TO / TB )

22-12

1.1821 3.2609

.9018 1.1421



Example Problem

C3B = ( EB / EO ) C4B = (3.3731-1.707962*C2B+0.226216*C2B**2)/1000

1.0000 .0017

C5B = -0.403287+0.320037*C2B-0.0307508*C2B**2

-.0779

C6B = -0.684978+0.582549*C2B-0.0547812*C2B**2

-.0911

C7B = -0.201334+0.168201*C2B-0.015728*C2B**2

-.0298

C8B = (C5B/C1B**2-C6B/C1B**3+C7B/C1B**4-C4B) /(C3B**0.2) EBB = 2.718**C8B

-.0182 .9819

TEMA Paragraph RCB 8.40 Element Geometry Factors: RY1 = (EAA*(RK3A-RK2A**2/(2*RK1A))/(DA*BA))

14.1679 / 10^6

RY2 = (EBB*(RK3B-RK2B**2/(2*RK1B))/(DB*BB))

5.1753 / 10^6

C

= (A**2 / (B**2 - A**2))

1.7284

D

= ( B / A )

RX1 = -A * C * (0.769 + 1.428 * D * D) / DE RX2 = 2.2 * A * C * D * D / DE

1.2564 -321.0036 / 10^6 368.7490 / 10^6

RX3 = -A*A*(1.538+LN(D)*(2+C*(2+3.71*D*D))) /(4*DE) RX4 = ( -2.2 * B * C ) / DE RX5 = (B * C * (0.769 * D * D + 1.428) / DE) RX6 = (-A*B*(1.538 + 5.714*C*ln(D)) / (4*DE)) XBOT = (RX1 - RY1) * (RX5 + RY2) - (RX2 * RX4)

-1.0049 / 10^3 -293.4925 / 10^6 352.4486 / 10^6 -939.8965 / 10^6 -.0116 / 10^6

RX7 = (RX2 * RX6 - RX3 * RX5 - RX3 * RY2) / XBOT

-1.0980

RX8 = (RX3 * RX4 - RX1 * RX6 + RX6 * RY1) / XBOT

1.7271

RQ1 = 0.385 * A * A + 1.429 * C * B * B * ln(D) RQ2 = ( -0.385 - 1.429 * C * ln(D)) * B * B RQ3 = .25*A*B*B*(1.269/(C*D*D)+3.714*C*ln(D)^2) GG

= ( A / B )

GST = (GG**4 * ln(GG) / (1-GG**2)) RM1 = 0.51 - 0.635 * GG**2 + GST RM2 = 0.635 * (1 - GG**2 ) + GST RM3 = 2.357 * GG**2 + 3.714 * GST

210.3250 -247.0719 668.5906 .7959 -.2499 -.1422 -17.1808 / 10^3 .5649

TEMA RCB 8.50 Flexible Element Stiffness (lbs/in): SJ

= 2*PI*A*DE/( RX7*RQ1 + RX8*RQ2 + RQ3 )

SJF = (1.0 / (1.0 / SJ + 1.0 / SJ))

1.5418 * 10^6 .7709 * 10^6

Analysis of Differential Expansion

TEMA Paragraph RCB 8.60 Induced Axial Force: Tubeside Equivalent Pressure for this case, P1C Shellside Prime Pressure for this case, PSPC Differential Expansion Pressure for this Case, PDC Shellside Pressure for this Case, PSC Equivalent Pressure, PSS = P1C + PSPC - PDC Induced Axial Force, FAX = A * PSS / 2.0

.000 psig .000 psig 515.920 psig .000 psig -515.920 psig -3313.213 lb.

TEMA Paragraph RCB 8.70 Flexible Element Moments THA = ( (Ps*B^3) / (8*DE) ) * (-2*GG*RM2-RM3/GG-GG^3/2-2*GG^3*LN(GG)) = THB = (Ps*B**3)*(-2*RM2-RM3+0.5-GG**2)/(8*DE)


ZA

= (Ps*A**2-0.3*A*FAX)/(EA*TA)

ZB

= (Ps*B^2-0.3*(A*FAX+((B^2-A^2)/2)*Ps))

.0000 / 10^6 .0000 / 10^6 1.0721 / 10^3

22-13

Example Problem


/ (EB*TB)

1.0721 / 10^3

MT1A = (RX5+RY2)*(-THA-FAX*RX3-BA*ZA)

-1.1909 / 10^3

MT2A = RX2*(FAX*RX6+THB-(BB*RK2B*ZB/RK1B))

1.1481 / 10^3

RMA

3.6737 * 10^3

= (MT1A+MT2A)/XBOT

MT1B = (RY1-RX1) * (THB+FAX*RX6-(BB*RK2B*ZB/RK1B))

1.0436 / 10^3

MT2B = RX4*(FAX*RX3+THA+BA*ZA)

-977.3136 / 10^6

RMB = (MT1B+MT2B)/XBOT

-5.6912 * 10^3

TEMA Paragraph RCB 8.72 Flexible Element Moments RA11 = -C*RMA+C*D*D*RMB+0.65*A*C*FAX*ln(GG)

-10.9644 * 10^3

RA12 = PSS*(0.325*RM2*B*B+0.4125*A*A) RA1

.0000 / 10^6

= (RA1D1-RA12)

-10.9644 * 10^3

RA21 = C*RMA-C*RMB-0.65*A*C*FAX*ln(GG)

5.2732 * 10^3

RA22 = 0.0875*RM3*PSS*B*B RA2

= B*B*(RA21+RA22)

RA3

= 0.206*PSS

RA4

= 0.65*A*(FAX-0.5*A*PSS)

.0000 / 10^6 1.3732 * 10^6 .0000 / 10^6 -27.6605 * 10^3

Stress in Expansion Joint Flange: SBX(R) = (6.0 / TE**2) * (RA1 + RA2/(R*R) + RA3*R*R + RA4*ln(R/B)) Stress Summary: Location:

(A)

12.8439

in.,

115001.80

psi

Location:

(B)

16.1373

in.,

-178157.20

psi

TEMA Paragraph RCB 8.73 Cylindrical Element Stresses

For the Inner Cylinder at X = YA DEA = +RRA*(PSS*RRA-0.3*F2A)/(EA*TYA) B1A = (1/ZZA)*(RJ2A*RMA/(2*BA^2*EAA*DA)-RJ1A*DEA

1.2516 / 10^3 -1.2849 / 10^3

B2A = (1/ZZA)*(-RJ1A*RMA/(2*BA*BA*EAA*DA) -RJ2A*DEA) U1A = +BA*(YA-YA)

-590.3668 / 10^6 .0000 / 10^6

U2A = B1A*SIN(U1A)*SINH(U1A)+B2A*COS(U1A) *COSH(U1A) SMYA = EA*(DEA+U2A)/RRA

-590.3668 / 10^6 1.4003 * 10^3

For the Inner Cylinder at X = LA DEA = RRA*(PSS*RRA-0.3*F2A)/(EA*TYA)

1.2516 / 10^3

B1A = (1/ZZA)*(RJ2A*RMA/(2*BA^2*EAA*DA)-RJ1A*DEA

-1.2849 / 10^3

B2A = (1/ZZA)*(-RJ1A*RMA/(2*BA^2*EAA*DA)-RJ2A*DE

-590.3668 / 10^6

U1A = BA*(YA-LA) U2A = B1A*SIN(U1A)*SINH(U1A)+B2A*COS(U1A)*COSH(U SMYA = EA*(DEA+U2A)/RRA

1.2711 -2.3509 / 10^3 -2.3281 * 10^3

For the Outer Cylinder at X = YB DEB = RRB*(PSS*RRB-0.3*F2B)/(EB*TYB)

1.0721 / 10^3

B1B = (1/ZZB)*(RJ2B*RMB/(2*BB^2*EBB*DB)-RJ1B*DEB

1.4046 / 10^3

B2B = (1/ZZB)*(-RJ1B*RMB/(2*BB^2*EBB*DB)-RJ2B*DE

23.8024 / 10^3

U1B = BB*(YB-YB)

.0000 / 10^6

U2B = B1B*SIN(U1B)*SINH(U1B)+B2B*COS(U1B) *COSH(U1B) SMYB = EB*(DEB+U2B)/RRB

22-14

23.8024 / 10^3 41.9267 * 10^3



Example Problem

For the Outer Cylinder at X = LB DEB = RRB*(PSS*RRB-0.3*F2B)/(EB*TYB)

1.0721 / 10^3

B1B = (1/ZZB)*(RJ2B*RMB/(2*BB^2*EBB*DB)-RJ1B*DEB

1.4046 / 10^3

B2B = (1/ZZB)*(-RJ1B*RMB/(2*BB*BB*EBB*DB)-RJ2B*D

23.8024 / 10^3

U1B = BB*(YB-RLB)

.4834

U2B = B1B*SIN(U1B)*SINH(U1B)+B2B*COS(U1B) *COSH(U1B)

23.9138 / 10^3

SMLB = EB*(DEB+U2B)/RRB

42.1145 * 10^3

TEMA Paragraph RCB 8.74 Maximum Cyclic Stresses Evaluated per ASME A-97 Appendix CC, Paragraph CC-3(c):

For the Inner Cylinder: SCLA = ABS(6.0*RMA/ (T*T)) + ABS(F2A/T)

.1226 * 10^6

RNA= 47.11*EXP((ln(SCLA*28.3E6/EB)-14.12)**2/1.023

11.1028 * 10^3

For the Outer Cylinder: SCLB = ABS(6.0*RMB/ (T*T)) + ABS(F2B/T)

.1842 * 10^6

RNB= 47.11*EXP((ln(SCLB*28.3E6/EB)-14.12)**2/1.023

1.9882 * 10^3

Analysis of Shellside Pressure

TEMA Paragraph RCB 8.60 Induced Axial Force: P1C =

.000

PSPC=

-38.750

PDC =

.000

PSC =

200.000

PSS =

-38.750

FAX =

-248.851

TEMA Paragraph RCB 8.70 Flexible Element Moments THA

-.354

THB

-.334

ZA

2.851 /10^3

ZB

4.214 /10^3

MT1A

36.591 /10^6

MT2A

-37.612 /10^6

RMA

87.651

MT1B

-34.187 /10^6

MT2B

30.030 /10^6

RMB

357.143

TEMA Paragraph RCB 8.72 Flexible Element Moments RA11

1.643 *10^3

RA12

13.319 *10^3

RA1

-11.676 *10^3

RA21

-1.285 *10^3

RA22

2.574 *10^3

RA2

.336 *10^6

RA4

-12.800 *10^3

RA3

41.200


(A)

12.8439

in.,

2406.65

psi

Location:

(R)

14.0268

in.,

-2191.15

psi

Location:

(B)

16.1373

in.,

10695.02

psi


For the Inner Cylinder at X = YA DEA

3.329 /10^3

B1A

-300.896 /10^6

B2A

411.004 /10^6

U1A

.000 /10^6

U2A

411.004 /10^6

SMYA

7.920 *10^3

For the Inner Cylinder at X = LA DEA

3.329 /10^3

B1A

-300.896 /10^6

B2A

411.004 /10^6

U1A

1.271

U2A

-238.757 /10^6

SMLA

6.544 *10^3


22-15

Example Problem


For the Outer Cylinder at X = YB DEB

4.214 /10^3

B1B

-1.804 /10^3

B2B

-1.361 /10^3

U1B

.000 /10^6

U2B

-1.361 /10^3

SMYB

4.808 *10^3

For the Outer Cylinder at X = LB DEB

4.214 /10^3

U1B

.483

B1B

-1.804 /10^3

B2B

-1.361 /10^3

U2B

-1.770 /10^3

SMLB

4.119 *10^3


For the Inner Cylinder: SCLA

3.312 *10^3

RNA

1.000 *10^6

RNB

1.000 *10^6

For the Outer Cylinder: SCLB

12.079 *10^3

Analysis of Tubeside Pressure


13.110

PSPC=

.000

PDC =

.000

PSC =

.000

PSS =

13.110

FAX =

84.192


.000 /10^6

THB

.000 /10^6

ZA

-27.242 /10^6

ZB

-27.242 /10^6

MT1A

30.261 /10^6

MT2A

-29.174 /10^6

RMA

-93.352

MT1B

-26.518 /10^6

MT2B

24.834 /10^6

RMB

144.618


278.616

RA12

.000 /10^6

RA1

278.616

RA21

-133.998

RA22

.000 /10^6

RA2

-34.895 *10^3

RA3

.000 /10^6

RA4

702.878


(A)

12.8439

in.,

-2922.30

psi

Location:

(B)

16.1373

in.,

4527.14

psi



-31.805 /10^6

B1A

32.650 /10^6

B2A

U1A

.000 /10^6

U2A

15.002 /10^6

SMYA

15.002 /10^6 -35.584

For the Inner Cylinder at X = LA DEA U1A

-31.805 /10^6 1.271

B1A

32.650 /10^6

B2A

U2A

59.740 /10^6

SMLA

15.002 /10^6 59.159

For the Outer Cylinder at X = YB

22-16

DEB

-27.242 /10^6

B1B

-35.692 /10^6

B2B

-604.840 /10^6

U1B

.000 /10^6

U2B

-604.840 /10^6

SMYB

-1.065 *10^3



Example Problem

For the Outer Cylinder at X = LB DEB

-27.242 /10^6

U1B

.483

B1B

-35.692 /10^6

B2B

-604.840 /10^6

U2B

-607.672 /10^6

SMLB

-1.070 *10^3



3.115 *10^3

RNA

1.000 *10^6

RNB

1.000 *10^6


4.680 *10^3

Analysis of Shellside + Tubeside Pressure


13.110

PSPC=

-38.750

PDC =

.000

PSC =

200.000

PSS =

-25.640

FAX =

-164.659


-.354

THB

-.334

ZA

2.824 /10^3

ZB

4.187 /10^3

MT1A

66.852 /10^6

MT2A

-66.786 /10^6

RMA

-5.701

MT1B

-60.705 /10^6

MT2B

54.864 /10^6

RMB

501.762


1.921 *10^3

RA12

13.319 *10^3

RA1

-11.398 *10^3

RA21

-1.419 *10^3

RA22

2.574 *10^3

RA2

.301 *10^6

RA4

-12.097 *10^3

RA3

41.200


(A)

12.8439

in.,

-515.62

psi

Location:

(R)

13.6401

in.,

-2565.13

psi

Location:

(B)

16.1373

in.,

15222.18

psi



3.297 /10^3

B1A

-268.246 /10^6

B2A

426.006 /10^6

U1A

.000 /10^6

U2A

426.006 /10^6

SMYA

7.884 *10^3


3.297 /10^3

B1A

-268.246 /10^6

B2A

426.006 /10^6

U1A

1.271

U2A

-179.018 /10^6

SMLA

6.603 *10^3


4.187 /10^3

B1B

-1.840 /10^3

B2B

-1.966 /10^3

U1B

.000 /10^6

U2B

-1.966 /10^3

SMYB

3.743 *10^3

For the Outer Cylinder at X = LB DEB U1B


4.187 /10^3 .483

B1B

-1.840 /10^3

B2B

-1.966 /10^3

U2B

-2.378 /10^3

SMLB

3.048 *10^3

22-17

Example Problem




554.577

RNA

1.000 *10^6

RNB

1.000 *10^6


16.759 *10^3

Analysis of Shellside + Differential Expansion


.000

PSPC=

-38.750

PDC =

515.920

PSC =

200.000

PSS =

-554.670

FAX =

-3562.063


-.354

THB

-.334

ZA

3.923 /10^3

ZB

MT1A

-1.154 /10^3

MT2A

5.286 /10^3 1.110 /10^3

RMA

3.761 *10^3

MT1B

1.009 /10^3

MT2B

-947.284 /10^6

RMB

-5.334 *10^3


-9.322 *10^3

RA12

13.319 *10^3

RA1

-22.641 *10^3

RA21

3.988 *10^3

RA22

2.574 *10^3

RA2

1.709 *10^6

RA4

-40.461 *10^3

RA3

41.200


(A)

12.8439

in.,

117408.10

psi

Location:

(B)

16.1373

in.,

-167462.10

psi



4.580 /10^3

B1A

-1.586 /10^3

B2A

-179.361 /10^6

U1A

.000 /10^6

U2A

-179.361 /10^6

SMYA

9.320 *10^3


4.580 /10^3

B1A

-1.586 /10^3

B2A

-179.361 /10^6

U1A

1.271

U2A

-2.590 /10^3

SMLA

4.215 *10^3


5.286 /10^3

B1B

-399.321 /10^6

B2B

22.441 /10^3

U1B

.000 /10^6

U2B

22.441 /10^3

SMYB

46.735 *10^3


5.286 /10^3 .483

B1B

-399.321 /10^6

B2B

22.441 /10^3

U2B

22.144 /10^3

SMLB

46.233 *10^3


22-18



Example Problem


.126 *10^6

RNA

9.822 *10^3

RNB

2.589 *10^3


.172 *10^6

Analysis of Tubeside + Differential Expansion


13.110

PSPC=

.000

PDC =

515.920

PSC =

.000

PSS =

-502.810

FAX =

-3229.021


.000 /10^6

THB

.000 /10^6

ZA

1.045 /10^3

ZB

1.045 /10^3

MT1A

-1.161 /10^3

MT2A

1.119 /10^3

RMA

3.580 *10^3

MT1B

1.017 /10^3

MT2B

-952.479 /10^6

RMB

-5.547 *10^3


-10.686 *10^3

RA12

.000 /10^6

RA1

-10.686 *10^3

RA21

5.139 *10^3

RA22

.000 /10^6

RA2

1.338 *10^6

RA3

.000 /10^6

RA4

-26.958 *10^3


(A)

12.8439

in.,

112079.20

psi

Location:

(B)

16.1373

in.,

-173630.10

psi



1.220 /10^3

B1A

-1.252 /10^3

B2A

-575.363 /10^6

U1A

.000 /10^6

U2A

-575.363 /10^6

SMYA

1.365 *10^3


1.220 /10^3

B1A

-1.252 /10^3

B2A

-575.363 /10^6

U1A

1.271

U2A

-2.291 /10^3

SMLA

-2.269 *10^3


1.045 /10^3

B1B

1.369 /10^3

B2B

23.198 /10^3

U1B

.000 /10^6

U2B

23.198 /10^3

SMYB

40.861 *10^3


1.045 /10^3 .483

B1B

1.369 /10^3

B2B

23.198 /10^3

U2B

23.306 /10^3

SMLB

41.044 *10^3



.119 *10^6

RNA

12.514 *10^3

For the Outer Cylinder:


22-19

Example Problem


SCLB

.180 *10^6

RNB

2.195 *10^3

STRESS SUMMARY: Analysis of Differential Expansion

Annular Element

Inside Junction

Outside Junction

Actual

Actual

Allowed

115002. (Fatigue)

Allowed

-178157. (Fatigue)

psi

16.137

178157. (Fatigue)

psi

Cyl. at point Y

1400. (Fatigue)

41927. (Fatigue)

psi

Cyl. at point L

-2328. (Fatigue)

42114. (Fatigue)

psi

122570. (Fatigue)

184181. (Fatigue)

psi

Annular Element Max. at R =

Max. Cycle Stress Max. Cycle Life

11103. Cycles

1988. Cycles

STRESS SUMMARY: Analysis of Shellside Pressure

Annular Element

Inside Junction

Outside Junction

Actual

Actual

2407.


Allowed 52500. 14.027

Allowed

10695.

52500. psi

-2191.

28114. psi

Cyl. at point Y

7920.

17500.

4808.

17500. psi

Cyl. at point L

6544.

17500.

4119.

17500. psi

Max. Cycle Stress

3312. (Fatigue)

Max. Cycle Life

999999. Cycles

12079. (Fatigue)

psi

999999. Cycles

STRESS SUMMARY: Analysis of Tubeside Pressure

Annular Element

Inside Junction

Outside Junction

Actual

Actual

Allowed

-2922. (Fatigue)

Allowed

4527. (Fatigue)

psi

16.137

4527. (Fatigue)

psi

Cyl. at point Y

-36. (Fatigue)

-1065. (Fatigue)

psi

Cyl. at point L

59. (Fatigue)

-1070. (Fatigue)

psi

3115. (Fatigue)

4680. (Fatigue)

psi



999999. Cycles

999999. Cycles

STRESS SUMMARY: Analysis of Shellside + Tubeside Pressure

Annular Element

Inside Junction

Outside Junction

Actual

Actual

Allowed

-516. (Fatigue)

Allowed

15222. (Fatigue)

psi

13.640

-2565. (Fatigue)

psi

Cyl. at point Y

7884. (Fatigue)

3743. (Fatigue)

psi

Cyl. at point L

6603. (Fatigue)

3048. (Fatigue)

psi

555. (Fatigue)

16759. (Fatigue)

psi



999999. Cycles

999999. Cycles

STRESS SUMMARY: Analysis of Shellside + Differential Expansion Inside Junction

Outside Junction

Actual

Actual

Allowed

Allowed

Annular Element

117408. (Fatigue)

-167462. (Fatigue)

psi

Cyl. at point Y

9320. (Fatigue)

46735. (Fatigue)

psi

Cyl. at point L

4215. (Fatigue)

46233. (Fatigue)

psi

125881. (Fatigue)

172102. (Fatigue)

psi


9822. Cycles

2589. Cycles

STRESS SUMMARY: Analysis of Tubeside + Differential Expansion

22-20

Inside Junction

Outside Junction

Actual

Actual

Allowed

Allowed



Example Problem

Annular Element

112079. (Fatigue)

-173630. (Fatigue)

psi

16.137

173630. (Fatigue)

psi

Cyl. at point Y

1365. (Fatigue)

40861. (Fatigue)

psi

Cyl. at point L

-2269. (Fatigue)

41044. (Fatigue)

psi

119455. (Fatigue)

179500. (Fatigue)

psi



12514. Cycles

2195. Cycles



22-21

Example Problem

22-22




&KDSWHU The ASME Tubesheets Module

Introduction This module computes the required thickness for tubesheets according to the ASME Code Section VIII Division 1 Appendix AA, A-2001. Currently ASME addresses required thickness for both U-tube tubesheets as well as fully fixed tubesheets. Other tubesheet types such as floating tubesheets are not supported by ASME at this time.

Purpose, Scope, and Technical Basis The ASME Tubesheets module is based on the ASME Code Section VIII Division 1 Appendix AA. This module will also compute loads on the tubes and compare them to their allowable loads per the appropriate equation in Appendix A. Gasketed geometries for both fixed and U-tube exchangers are also analyzed as well as the thickness of the flanged extension (the TEMA equation has been used). This module is good for both square or rectangular tube patterns. When this module is executed it will display the output (equations and all) for the given input. Afterwards, PVElite will iterate for the required thickness of the tubesheet. The shell side and tubeside corrosion allowances will then be added to these final results. PVElite also performs the plasticity calculations for fixed tubesheets if high discontinuity stresses exist at the attachment between the tubesheet and shell or channel. PVElite contains all of the graphs and functions that appear in appendix AA.

The ASME Tubesheets Module

23-1



Figure 23A shows the geometry for the ASME Tubesheets Module.

23-2




Figure 23A - Geometry for the ASME Tubesheets Module


23-3



Discussion of Input Data Main Input Fields Tubesheet Number

Enter an ID number for the Tubesheet. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Note, that more than one pressure or temperature case can be run. Use the page down key, enter a new tubesheet number and change the relevant input items. Tubesheet Description

Enter an alpha-numeric description for this item. This entry is optional. Entering a description will help you to keep up with each item when reviewing the output. Shell Design Pressure

Enter the design pressure for the shell side of the exchanger. If the shell side has external pressure, enter a negative pressure. The program will add this pressure with the positive on the tube (channel) side. Shell Wall Thickness

Enter the minimum wall thickness for the shell of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheets. It is used in the computation of the Beta parameter as well as the spring rate and other factors. Shell Corrosion Allowance

Enter the shell side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the shell. Shell Inside Diameter

Enter the uncorroded inside diameter of the exchanger shell. Channel Design Pressure

Enter the design pressure for the tube side of the exchanger. If the tube side has a vacuum design condition, enter a negative pressure. The program will add the absolute value of this pressure with the positive pressure on the other side. Channel Wall Thickness

Enter the minimum wall thickness for the channel of the exchanger. This value is used by the program to calculate the characteristic diameter for all tubesheet types. An example of such a parameter is the Beta dimension for fixed tubesheet exchangers. Channel Corrosion Allowance

Enter the tube side corrosion allowance for the exchanger. This value is used to calculate the corroded thickness of the channel. Channel Inside Diameter

Enter the uncorroded inside diameter of the exchanger channel.

23-4




Tubesheet Metal Design Temperature

Enter the design metal temperature for the tubesheet. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Tubesheet Material Specification

Enter the ASME code material specification as it appears in the PVElite Appendix (chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Tubesheet Allowable Stress, Operating Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the design temperature the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Tubesheet Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Tubesheet Corrosion Allowance (Shellside/Tubeside) Enter the shellside and tubeside corrosion allowance for the tubesheet. This is used to calculate the corroded thickness of the tubesheet. Tubesheet Thickness

Enter the tubesheet thickness that you are going to be using. For fixed exchangers, all of the initial calculations will be performed and printed using the original tubesheet thickness. PVElite will converge on the minimum required tubesheet thickness for the given loading condition. For U-Tube geometries, PVElite will simply compute the required thickness for the geometry. Type of Tubesheet

ASME has two distinct types of tubesheets for analysis purposes. These are fixed and Utube exchangers. A fixed tubesheet exchangers is one that is subject to loads arising from differential thermal expansion. Based on the selected tubesheet type, the program will automatically reset other inputs on this dialog, such as tubesheet Gasketed with which side or tubesheet integral with which side. The list below identifies the tubesheet types supported: U-Tube Tubesheet Exchangers:

(U)

U-tube tubesheets gasketed on both sides.

(V)

U-tube tubesheets integral with the channel.


23-5



U-tube tubesheets integral with the shell. U-tube tubesheets integral with both shell and channel. Fixed tubesheet exchanger - two stationary tubesheets: (F, A) Configuration A- tubesheet integral on both sides. (F, B) Configuration B- shell integral, channel Gasketed, tubesheet extended as flange. (F, C) Configuration C- shell integral, channel Gasketed, tubesheet not extended as flange. (F, D) Configuration D- tubesheet Gasketed on both sides. Number of Tubes

Enter the number of tubes in the tubesheet. This value is used to determine the total tube area and stiffness.

Note

For U-tube exchangers, this is the number of tube holes in the tubesheet. (Normally equal to 2 times the number of tubes.)

Tube Wall Thickness

Enter the wall thickness of the tubes. This value is used to determine the total tube area and stiffness. The following table gives thicknesses for some common tube gauges:

B.W.G. Gauge

Thickness (Inches)

B.W.G. Gauge

Thickness (Inches)

7

.180

17

.058

8

.165

18

.049

10

.134

19

.042

11

.109

22

.028

13

.095

24

.022

14

.083

26

.018

15

.072

27

.016

16

.065


Enter the outside diameter of the tubes. This is usually an exact fraction, such as .5, .75, .875, 1.0, or 1.25. The tube diameter, pitch, and pattern are used to calculate the term ‘eta’ in the tubesheet formulas. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts.

23-6




Design Temperature of Tubes

Enter the design temperature of the tubes. This value will be used to look up the allowable stress values for the tube material from the material tables. Tube Material Specification

Enter the ASME code material specification as it appears in the PVElite Appendix (Chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Tube Material Allowable Stress, Operating Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the design temperature the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Tube Material Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Tube Pattern (Triangular, Square)

Enter the pattern of the tube layout. The tube diameter, pitch, and pattern are used to calculate the term ‘eta’ in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. In the ASME, code square patterns have a 90 degree layout angle and triangular patterns have a 60 degree angle. Tube Pitch

Enter the tube pitch, the distance between the tube centers. The tube diameter, pitch, and pattern are used to calculate the term mustar in the tubesheet thickness equation. These rules are same for triangular and rotated triangular layouts. The rules are also the same for square or rotated square layouts. Distance between Innermost Tube Centers (UL)

The ASME defines this input also as the largest center-to-center distance between adjacent tube rows. This is not the tube pitch, however the values for the tube pitch and this value may be the same. Length of Expanded Portion of Tube

The expanded portion of a tube is that part which is radially expanded outward. When the tube is expanded it is also pressed into the tubesheet. Simply enter this expanded length. Some tubes are welded into place and this value may be 0. The maximum this value can be is the thickness of the tubesheet.


23-7



Radius to Outermost Tube Hole Center

Enter the distance from the centerline of the exchanger to the centerline of outermost tube. Tube Side Pass Partition Groove Depth (hg)

Enter the tube side pass partition groove depth. Enter the Bolting Information

Check this box to enter the bolting information. If it is a U-tube tubesheet exchanger then this information is needed if the tubesheet is extended as flange. For a Fixed tube tubesheet exchanger this information is needed if the tubesheet is Gasketed with channel or shell, irrespective of the tubesheet’s extension as a flange. Programs (PVElite from version 4.1) now require, the bolting information for tubesheet not extended as flange. Tubesheet Gasket (None, Shell, Channel, Both)

Select NONE if the tubesheet is not gasketed on either side. Select SHELL if the gasket is only on the shell side of the exchanger. Select CHANNEL 2.0 if the gasket is only on the channel side of the exchanger. Select BOTH if the gaskets are on both sides of the exchanger. Tubesheet Integral With

This input is used with U-Tube and Fixed type exchangers. For U-Tube exchangers, the elastic properties of either the shell or channel are needed to properly compute reduced bending moment in the second elastic iteration. While for Fixed Tubesheet exchangers, just the information that, which side the tubesheet is integral with is needed. Enter the Dimension G for the Backing Flange

This input is only required for fixed tubesheet exchanger configuration C. G is the midpoint of the contact between the backing flange and the tubesheet. Enter the Outside Diameter of the Tubesheet

This value is referred to as "A" in the ASME code. For the tubesheet extended as flange, this will be the diameter of the extended portion of the tubesheet. Is There a Shell Band

The shell band can be used to reduce the bending stresses in the tubesheet, shell, or channel. Fixed tubesheets where the shell is integral to the tubesheet, configuration a, b, or c, can have a different thickness of shell adjacent to the tubesheet. The band of shell can be made of a a different material as well. If that is the case then check this box.

23-8




Shellband Heat Exchanger


23-9



Pop-Up Input Fields Shell Temperature for Internal Pressure

Enter the design metal temperature for the shell. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Shell Material Specification

Enter the ASME code material specification as it appears in the PVElite Appendix (chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Shell Allowable Stress, Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the design temperature the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Shell Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Channel Temperature for Internal Pressure

Enter the design metal temperature for the shell. This is the design temperature for determining allowable stresses only. This temperature is not assumed to be the metal temperature for thermal expansion. There is a separate input field for the actual metal temperature. Channel Material Specification

Enter the ASME code material specification as it appears in the PVElite Appendix (chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Channel Allowable Stress, Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the design temperature the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature.

23-10




Channel Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Length of Tubes

Enter the overall length of the tubes, the length from the inside face of one tubesheet to the inside face of the other tubesheet. This value is used to determine the thermal expansion of the tubes. Corroded Expansion Joint Spring Rate

If there is no expansion joint, enter a zero (0.0). If there is a thin walled expansion joint, enter a one (1.0). If there is a thick walled expansion joint, enter the actual spring constant for the joint. The expansion joint spring rate should be calculated using the PVElite THICKJNT program, the rules in TEMA RCB-8, or a similar analysis technique. The spring rate reported from the THICKJNT program is reported in units of pounds per inch. As of version 4.1 of PVElite, different inputs for the uncorroded and corroded spring rates will be required, these will be used for running the multiple load cases in uncorroded and corroded condition. Uncorroded Expansion Joint Spring Rate

If there is no expansion joint, enter a zero (0.0). If there is a thin walled expansion joint, enter a one (1.0). If there is a thick walled expansion joint, enter the actual spring constant for the joint. The expansion joint spring rate should be calculated using the PVElite THICKJNT program, the rules in TEMA RCB-8, or a similar analysis technique. The spring rate reported from the THICKJNT program is reported in units of pounds per inch. As of version 4.1 of PVElite, different inputs for the uncorroded and corroded spring rates will be required, these will be used for running the multiple load cases in uncorroded and corroded condition. Expansion Joint Projection from Shell OD

For fixed tubesheet heat exchangers that have an expansion joint enter the value (wj). This distance is measured from the OD of the shell to the ID of the expansion joint. This is the dimension hj in Fig. AA-2.0 of ASME Code VIII Div. 1 (pg. 644, 1998 ed) pressure vessel code.


23-11



Enter the Unsupported Tube Span, SL for MAX (k*SL)

For computing the allowable tube compression, the values of k and SL are required. Where, SL : Unsupported Span of the tube k : Tube end condition corresponding to the span SL. The table below displays the different values of k: K

End Condition

0.6

For unsupported spans between two tubesheets

0.8

For unsupported spans between a tubesheet and a tube support

1.0

For unsupported spans between two tube supports

For the worst case scenario enter the values of k and SL that the give maximum combination of k*SL. SL for example, could be the distance between the tubesheet and the first baffle or the tubespan between two support baffles. Enter the Tube End Condition, K Corresponding to Span SL

For computing the allowable tube compression, the values of k and SL are required. Where, SL : Unsupported Span of the tube k : Tube end condition corresponding to the span SL. The table below displays the different values of k: K

End Condition

0.6

For unsupported spans between two tubesheets

0.8

For unsupported spans between a tubesheet and a tube support

1.0

For unsupported spans between two tube supports

For the worst case scenario enter the values of k and SL that the give maximum combination of k*SL. SL for example, could be the distance between the tubesheet and the first baffle or the tubespan between two support baffles. Metal Temperatures

It is important, especially when evaluating fixed tubesheets without expansion joints, that you enter accurate values for metal temperatures for each operating condition. You may have to run the analysis more than once to check several metal temperature cases. Frequently the metal temperatures will be less severe than the design temperatures, due to thermal resistances. For example, if the shellside fluid has a good heat transfer coefficient and the tubeside fluid has a relatively poor heat transfer coefficient, then the tube temperature will be quite close to the shell temperature. Don’t forget to evaluate the condition of

23-12




shellside or tubeside loss of fluid. Especially for shellside loss of fluid, this design condition may govern the exchanger design.

Mean Shell Metal Temperatures. Enter the actual metal temperature for the shell along its length, under realistic operating conditions.

Mean Tube Metal Temperatures. Enter the actual metal temperature for the tube along its length, under realistic operating conditions.

Tubesheet Metal Temperature at the Rim. Enter the actual metal temperature for the tubesheet at the rim, under realistic operating conditions.

Shell Metal Temperature at Tubesheet. Enter the actual metal temperature for the shell at the tubesheet, under realistic operating conditions. Channel Metal Temperature at Tubesheet. Enter the actual metal temperature for the channel at the tubesheet, under realistic operating conditions. Classification for Tube Joint Connection (1 - 11)

Enter a value between 1 and 11 based on the following table from ASME VIII appendix A table A-2 (pg. 463 1992 ed.).

Type

Joint

Description

Fr.(test)

Fr.(no test)

1

a

welded only, a ≥ 1.4t

1.00

.80

2

b

welded only t ≤ a < 1.4t

.70

.55

3

c

brazed examined

1.00

.80

4

d

brazed not fully examined

0.50

.40

5

e

welded a ≥ 1.4t, exp.

1.00

.80

6

f

welded a < 1.4t,exp,2 grooves

.95

.75

7

g


.85

.65

8

h


.70

.50

9

i

expanded 2 or more grooves

.90

.70

10

j

expanded single groove

.80

.65

11

k

expanded no grooves

.60

.50

Table A-2 Efficiencies and Joint Types


Enter a value between .40 and 1.0 based on the following table from ASME VIII appendix A table A-2 (Pg. 463 1992 ed.). This is needed when the tube connection class is not specified above. See the table above for these factors.


23-13




Enter the diameter of the bolt circle of the flange. Thickness of Extended Portion of Tubesheet

Enter the flange thickness. This thickness will be used ion the calculation of the required thickness. The final results should therefore, agree with this thickness to within about five percent. Since ASME does not have a single equation to compute this required thickness, the appropriate formula from TEMA 7th edition was used. Run Multiple Load Cases for Fixed Tubesheet ?

Check this box if you want to run multiple load cases for the tubesheet design, per the ASME standard.

Load Case #

Load case description Corroded

Uncorroded

1

Fvs + Pt - Th + Ca

Fvs + Pt - Th - Ca

2

Ps + Fvt - Th + Ca

Ps + Fvt - Th - Ca

3

Ps + Pt - Th + Ca

Ps + Pt - Th - Ca

4

Fvs + Fvt + Th + Ca

Fvs + Fvt + Th - Ca

5

Fvs + Pt + Th + Ca

Fvs + Pt + Th - Ca

6

Ps + Fvt + Th + Ca

Ps + Fvt + Th - Ca

7

Ps + Pt + Th + Ca

Ps + Pt + Th - Ca

8

Fvs + Fvt - Th + Ca

Fvs + Fvt - Th - Ca

Note: Fvt, Fvs - User defined Shellside and Tubeside vacuum pressures or 0.0. Ps, PT - Shell side and Tube side Design Pressures. Th

- With or without Thermal Expansion.

Ca

- With or without Corrosion Allowance

Enter the Shell/Channelside Vacuum Pressures

When analyzing the design with the multiple load cases, the user can specify shell/channel side vacuum pressures. This should be a positive entry. For example for full atmospheric vacuum condition enter a value of 15.0 psig. If no value is specified then 0 psi will be used.

23-14




Select Load Cases for Detailed Printout

When analyzing the design with the multiple load cases, the program will generate summarized results for all the load cases in tabular form. To see the detailed equations and intermediate calculations for one or more load cases select those load cases. Is This a Pressure Only Case ?

The program designs the tubesheet under all the load cases. If you manually want to run the load cases then use this input. If you check this box the allowable stress amplification factor of 2 will be used and there will be no stresses due to differential thermal expansion. Nominal Bolt Diameter

Enter the nominal bolt diameter. The tables of bolt diameter included in the program range from 0.5 to 4.0 inches. Thread Series (TEMA,UNC)

There are two options for this entry: •

TEMA Bolt Table

•

UNC

Bolt Table

Number of Bolts

Enter the number of bolts to be used in the flange analysis. This is usually an even number. Bolt Material Specification

Enter the ASME code material specification as it appears in the PVElite Appendix (Chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Bolt Allowable Stress, Design Temp

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Bolt Allowable Stress, Ambient Temp

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Flange Face Outer Diameter

Enter the outer diameter of the flange face. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket.


23-15



Flange Face Inner Diameter

Enter the inner diameter of the flange face. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket. Flange Face Facing Sketch

Using Table 2-5.2 of the ASME code, select the facing sketch number according to the following correlations: Facing Sketch

PVElite Equivalent

1a 1b 1c 1d 2 3 4 5 6

1 2 3 4 5 6 7 8 9

Description flat finish faces serrated finish faces raised nubbin-flat finish raised nubbin-serrated finish 1/64 inch nubbin 1/64 inch nubbin both sides large serrations, one side large serrations, both sides metallic O-ring type gasket

Gasket Outer Diameter

Enter the outer diameter of the gasket. The program uses the minimum of the flange face outer diameter and the gasket outer diameter to calculate the outside flange contact point, but uses the maximum in design when selecting the bolt circle. This is done so that the bolts do not interfere with the gasket. The program uses the maximum of the flange face ID and the gasket ID to calculate the inside contact point of the gasket. Gasket Inner Diameter

Enter the inner diameter of the gasket. The program uses the maximum of the Flange Face ID and the Gasket ID to calculate the inner contact point of the gasket.

Note

For gasket properties, refer to the table in Chapter 12, The Flange Module.

Gasket Thickness

Enter the gasket thickness. This value is only required for facing sketches 1c and 1d (PVElite equivalents 3 and 4). Nubbin Width

If applicable, enter the nubbin width. This value is only required for facing sketches 1c, 1d, 2 and 6 (PVElite equivalents 3, 4, 5, and 9). Note that for sketch 9 this is not a nubbin width, but the contact width of the metallic ring. Length of Partition Gasket

This is the cumulative length of all the heat exchanger pass partition gaskets associated with this flange. If the pass partition gaskets are a different width than the main gasket, scale the length you enter so that the area of the gasket is correct.

23-16




Width of Partition Gasket

Enter the width of the pass partition gasket. The gasket properties such as the facing sketch, column, M and Y will be taken from the main gasket. Using these properties and the known width, PVElite will compute the effective seating width and compute the gasket loads contributed by the partition gasket. Design Temperature for Integral Part

Enter the actual metal temperature for either the channel or shell part. This temperature will be used to retrieve the elastic properties from the material tables. Material Specification for Integral Part

Enter the ASME code material specification as it appears in the PVElite Appendix (chapter 21). The name to be used is labeled as the range name and is in the center column. Alternatively, the material can be selected from the material database by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the database, its specification and properties can be entered manually by selecting Tools, Edit/ Add Materials, from the Main Menu. Allowable Stress, Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the design temperature the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D. Shell Band Material

Specify the material for the shell band. This material can be different than the shell material. Shell Band Input

Fixed Tubesheets in which the shell is integral to the tubesheet configuration A, B, or C, can have a different thickness of shell adjacent to the tubesheet. The band of shell can be made of a different material as well. This procedure can be used to reduce the bending stresses in the tubesheet, shell, or channel.


23-17



Shellband Heat Exchanger

23-18




Discussion of Results Appendix AA of the Code is divided into two major sections. One section is for the UTube exchangers and the other is for fixed types. There is a sequence of steps to go through when performing calculations for each type of exchanger. PVElite will perform each individual; step and print the applicable formula substitution and answer for each step. All results shown are for the given geometry. In addition, the program will iterate for the minimum thickness of the tubesheet. If needed PVElite will also perform the second elastic iteration if high discontinuity stresses exist. As of version 4.1 of PVElite, the program can run multiple load cases for the fixed tubesheet design as per the ASME code. The table below displays the load cases that are considered.

Load Case #

Load case description

1

Corroded Fvs + Pt - Th + Ca

Uncorroded Fvs + Pt - Th - Ca

2

Ps + Fvt - Th + Ca

Ps + Fvt - Th - Ca

3

Ps + Pt - Th + Ca

Ps + Pt - Th - Ca

4

Fvs + Fvt + Th + Ca

Fvs + Fvt + Th - Ca

5

Fvs + Pt + Th + Ca

Fvs + Pt + Th - Ca

6

Ps + Fvt + Th + Ca

Ps + Fvt + Th - Ca

7

Ps + Pt + Th + Ca

Ps + Pt + Th - Ca

8

Fvs + Fvt - Th + Ca

Fvs + Fvt - Th - Ca

Note: Fvt, Fvs - User-defined Shell side and Tubeside vacuum pressures or 0.0. Ps, Pt

- Shell side and Tube side Design Pressures

Th

- With or without Thermal Expansion.

Ca

- With or without Corrosion Allowance

When running these load cases the program automatically adjusts the allowable stresses. For pressure only load cases (!, 2, 3, 8) the tubesheet, shell and channel allowable stresses are 1.5 * their allowable tensile stresses respectively. For cases involving thermal and/or pressure (4, 5, 6, 7) the tubesheet, shell and channel allowable stresses are 3.0 * their allowable tensile stresses respectively. Upset conditions may need to be analyzed. The user can enter his own shell/channel vacuum pressures for the multi-case analysis, e.g. 0, 15 psi. This will simulate one of the process fluid streams being stopped, while the other stream continues. In addition to satisfying stress criteria for the tubesheet, the tubes must also be capable of withstanding the axial forces imposed on them due to the differential thermal expansion. These forces must be less than the allowable force on the tube per the ASME code equations (App A). Tube stresses are also checked against the criteria in appendix AA.


23-19



Finally, the discontinuity stresses must be less than their allowables. If these allowables are exceeded, PVElite will perform a second elastic iteration. This is where the plasticity of the integral component is considered. Typically, when this iteration is performed, the stresses will come down below their allowables. If for any reason they do not, the geometry of the unit must be reconsidered. If your tubesheet contains a center groove, the groove depth should be subtracted from the overall tubesheet thickness. Bending stress in the tubesheet, shell, or the channel can also be reduced by having a local shell thickness adjacent to the tubesheet.

23-20




Example Problem The following example problem is a comparison to another Heat Exchanger Program. Both programs were in excellent agreement, including the values read from each of the various figures. The stress results were less than .1 percent different. FileName : CHECKS

-------------------------------

ASMETube Analysis : TEMP + PRESS

INPUT ECHO, TUBESHEET NUMBER

ITEM:

1,

1,

Page

1

04:46pm,

05/18/01

Description: TEMP + PRESS

Shell Design Pressure

Ps

50.00

psig

Shell Thickness

Hs

.2500

in.

CAS

.0000

in.


Ds

112.0000

in.

Channel Design Pressure

Pt

50.00

psig

Channel Thickness

HC

.2500

in.

CAC

.0000

in.

DC

112.0000

in.


Channel Corrosion Allowance Inside Diameter of Channel

Tubesheet Design Metal Temperature

TEMPTS

Tubesheet Material Specification Tubesheet Allowable Stress at Temperature Tubesheet Allowable Stress at Ambient

F

S

15900.00

psi

SATS

18800.00

psi

H

1.8125

in.

649.00

F

Thickness of Tubesheet

TUBESHEET TYPE:

649.00 SA-240 304

Fixed Tubesheet Exchanger

ADDITIONAL DATA FOR FIXED TUBESHEET EXCHANGERS Shell Temperature for Internal Pressure

DELTs

Shell Material Shell Allowable Stress at Temperature Shell Allowable Stress at Ambient Channel Temperature for Internal Pressure

SA-240 304 Ss

15900.00

psi

SAS

18800.00

psi

DELTC

649.00

Channel Material Channel Allowable Stress at Temperature

F

SA-240 304 Sc

15900.00

psi

SAC

18800.00

psi

RL

152.25

in.

SYT

20000.00

psi

Expansion Joint Spring Rate ( lbs./in. )

Sj

49250.

lbs./in.

Expansion Joint Projection from Shell OD

wj

2.6250

in.

Maximum Unsupported Tube Length

SL

50.00

in.

SLT

50.0000

in.

wu

.0000

in.

%ED

100.00

rc

55.2813

Channel Allowable Stress at Ambient Length of Tubes Tube Yield Stress At Operating Temperature

Tube Span Between Baffle and Tubesheet Width of Diametral Lane Percent Expanded Depth of Tube Radius to Outermost Tube Hole Center

in.

Actual Metal Temperature for Shell

156.00

F

Actual Metal Temperature for Tubes

226.00

F

Actual Metal Temperature for Tubesheet

233.00

F


FASME

.70

Classification for Tube Joint Type

TJNT

A


23-21



Number of Tubes

RNTUBS

3100

Tube Wall Thickness

t

.0490

in.


D

.7500

in.

Design Temperature of the Tubes

649.00

Tube Layout Pattern

Square

Tube Material

F

SA-249 TP304

Tube Allowable Stress at Temperature

SOT

13500.00

psi

Tube Allowable Stress At Ambient

SAT

16000.00

psi

P

1.3500

in.

Tube Pitch (Center to Center Spacing)

ADDITIONAL DATA FOR TUBESHEETS EXTENDED AS FLANGES: Flanged Tubesheet Outside Diameter

DF

116.2500

in.


DB

114.7500

in.

Flange Thickness

TF

5.1250

in.

DBOLT

.6250

in.

Nominal Bolt Diameter Type of Threads

TEMA Thread Series

Number of Bolts

176

Bolt Material

SA-193 B7


SBO

25000.00

psi


SBA

25000.00

psi


FOD

113.6250

in.


FID

112.6250

in.

ADDITIONAL DATA FOR GASKETED TUBESHEETS:


1, Code Sketch 1a


GOD

113.6250

in.


GID

112.6250

in.

M

3.75

Y

10000.00

Gasket Factor, m, Gasket Design Seating Stress Column for Gasket Seating

psi

2, Code Column II

Gasket Thickness

.1250

Tubesheet Gasket on which Side

SIDE

in.

CHANNEL

Installation Temperature of Assembly

70.00

F

ASME TUBE SHEET RESULTS PER APP. AA, 1995 WITH A-97 :



.500

in.

Basic Gasket Width,

B0 = RN / 2.0

.250

in.


BE = B0

.250

in.

113.125

in.

888640.80

lb.

Gasket Reaction Diameter, G = (GODC+GIDC) / 2.0 Flange Design Bolt Load

W

Required Thickness of Flanged Extension Per TEMA 7th Edition FTREQ = .98*SQRT((RM*(R^2-1+3.72*R^2*LOG(R))/((A-G)*(1+1.8*R^2)) FTREQ = .98*SQRT(( 722024*( 1.0276^2-1+3.72* 1.0276^2*LOG( 1.0276))/ (( 116.2500- 113.1250)*(1+1.8* 1.0276^2)) FTREQ = .8857 in.

Elasticity/Expansion Material Properties :

Shell

23-22

- TEMA

: TP304

Coefficient of Thermal Expansion at Actual Temp.

.9608E-05 / deg F

Elastic Modulus at actual Metal Temperature

.2505E+08 psi




Channel

- TEMA

: TP304


.9608E-05 / deg F


.2505E+08 psi

Tubes

- TEMA

: TP304


.9608E-05 / deg F


.2505E+08 psi

TubeSheet - TEMA

: TP304


.9608E-05 / deg F


.2505E+08 psi

Results for ASME Fixed Tubesheet Calculations, Original Thickness :

Results for Step 1 :

d* = d - 2t*( Et/E )( %ED/100 )( St/S ) d* = .7500-2* .0490*( 25054998/ 25054998)( 100/100)*( 13500/ 15900) d* = .6668 in.

a = rc + d* / 4 a = 55.2813 + .6668 / 4 a = 55.4480 in.

Au = 2 * rc * wu Au = 2 * 55.2813 * .0000 Au = .0000 in.^2

x = ã * a^2 - Au x = 3.14159 * 55.4480^2 - .0000 x = 9658.7590 in.^2

P‘ = P * SQRT( 1 + Au/x ) P‘ = 1.3500 * SQRT( 1 + .0000/ 9658.76 ) P‘ = 1.3500 in.

ETA = 1 - d* / P‘ ETA = 1 - .6668 / 1.3500 ETA = .5061

K = b/a K = 56.1250/ 55.4480 K = 1.0122

Kbar = a1/a Kbar = 58.1250/ 55.4480 Kbar = 1.0483

Kc = ac/a Kc = 56.5625/ 55.4480 Kc = 1.0201


XI = 2/n*(b/d)(hs/t)(1/(1-t/d))*(Es/Et) XI = 2 / 3100 *( 56.1250 / .7500 )( .2500 / .0490 ) *


23-23



( 1/( 1- .0490 / .7500 ))( 25054998 / 25054998 ) XI = .2635

ás = 1.285/SQRT( b * hs ) ás = 1.285/SQRT( 56.1250 * .2500 ) ás = .3430 ( = 0.0 if Gasketed )

ác = 1.285/SQRT( ac * hc ) ác = 1.285/SQRT( 56.5625 * .2500 ) ác = .0000 ( = 0.0 if Gasketed )


J = 1/( 1 + ( 2*ã*b*Es*hs)/Sj*L ) J = 1/(1+(2*ã*56.1250*25054998*.2500)/49250*152.25) J = .0034 ( = 1.0 if No Exp. Joint )

Lambdas = .3(b/hs) + Es/Et(d/t) * [(.3/2+(a^2/n*d^2)(1/(1-t/d))*(1-n*d^2/4*a^2))] Lambdas = .3(56.1250/.2500)+25054998/25054998(.7500/.0490)* [(.3/2+(55.4480^2/3100*.7500^2)(1/(1-.0490/.7500))* (1-3100*.7500^2/4*55.4480^2))] Lambdas = 94.4252

Lambdat = .3/2(d/t)*(1-2t/d)+a^2/(ndt(1-t/d)) * [1-nd^2/(4a^2)(1-4t/d+4t^2/d^2)] Lambdat = .3/2(.7500/.0490)*(1-2*.0490/.7500)+55.4480^2/ (3100*.7500*.0490*(1-.0490/.7500))* [1-3100*.7500^2/(4*55.4480^2) (1-4*.0490/.7500+4.0490^2/.7500^2)] Lambdat = 27.7752

Qe = J(àt*Tt-às*Ts)+J*Lambdas(Ps/Es)

-

(Pt/Et)[J*Lamdat+0.5*Et*b/(Es*hs)] - Ps(1-J)*wj/( Es*hs ) Qe = .00((.961E-05)*156-(.961E-05)*86)+.00*94.4252(50.00/25054998)(50.00/25054998)[.00*27.7752+0.5*25054998*56.1250/(25054998*.2500) -50.00(1-.00)*.0000/(25054998*.2500) QE = -.000221282


e = ( E*/E )*( 0.91 /( 1 - v*^2 ) e = ( .6083 )*( .91 /( 1 - .3009*^2 ) e = .6087

Xa = 2.161(n*Et*t(d-t)/(e*E*L*a)^.25 * (a/h)^.75 Xa = 2.161(3100*25054998*.0490(.7500-.0490)/ (.6087*25054998*152.25*55.4480)^.25*(55.4480/1.8125)^.75 Xa = 10.6654

Mu = 2.198/(E*h^3)[ás*hs^3*Es*b(1+ás*h+ás^2*h^2/2) + ác*hc^3*Ec*ac*(1+ác*h+ác^2*h^2/2)] Mu = 2.198/(25054998*1.8125^3)[.3430*0^3*25054998*56.1250 (1+.3430*1.8125+.3430^2*1.8125^2/2)+.0000*.2500^3*

23-24




25054998*56.5625*(1+.0000*1.8125+.0000^2*1.8125^2/2)] Mu = .2016

Gammabs = ás^2*hs^2*K^3(1+ás*h)/5.46 Gammabs = .3430^2*.2500^2*1.0122^3(1+.3430*1.8125)/5.46 Gammabs = .0023

Gammabt = ác^2*hc^2*Kc^3(1+ác*h)/5.46 Gammabt = .0000^2*.2500^2*1.0201^3(1+.0000*1.8125)/5.46 Gammabt = .0000

Gammat = 0.25*(Kc^2-1)(Kc+1)-0.5(Kc^3-K)+Gammabt Gammat = 0.25*(1.0201^2-1)(1.0201+1)-0.5(1.0201^3-1.0122)+.0000 Gammat = -.0041

Gammab = KC - DUNDB/a ( Fig. AA-2.1 (c) ) Gammab = 1.0201 - 57.3750/ 55.4480 Gammab = -.0147


Curve Values from Figure AA-2.3 Zm

=

.143346

Zv*Xa/Xa =

.008752

PHI(è) = 0.91/e * ( Ln(kbar) + Mu ) PHI(è) = 0.91 / .6087 * ( Ln( 1.0483) + .2016 ) PHI(è) = .3719

Q1 = (K-1-è*Zv)/( 1 + è*Zm ) Q1 = ( 1.0122-1- .3719* .0088)/( 1 + .3719* .1433 ) Q1 = .0085

Delta T*s = 1/2( Delta Ts + Delta Tr ) Delta T*s = 1/2( 86.00 + 135.00 ) Delta T*s = 110.5000 F

Delta T*c = 1/2( Delta Tc + Delta Tr ) Delta T*c = 1/2( 156.00 + 135.00 ) Delta T*c = 145.5000 F

DeltaT r = 1/3( DeltaTc + DeltaTs + DeltaTts) DeltaT r = 1/3( 156.00 + 86.00 + 163.00 ) DeltaT r = 135.0000 F

P*t = Ec*hc/ac(àc*DeltaT*c - àts*DeltaTr) P*t = 25054998*.2500/56.5625((.961E-05)*145.50-(.961E-05)*135.00) P*t = 11.1724 psig

P*s = Es*hs/b (às*DeltaT*s - àts*DeltaTr) P*s = 25054998*.2500/56.1250((.961E-05)*110.50-(.961E-05)*135.00) P*s = -26.2721 psig


23-25



Q2 = (a^2(Pt*Gammat+P*t*Gammabt+Ps*Gammas-P*Gammabs)+B*dundb*Gammab)/ ( 1 + è*Zm ) Q2 = (55.4480^2(50.00*-.0041+11.1724*.0000+50.00 *-.0022—26.2721*.0023)+2465*57.3750*-.0147)/(1+.3719*.1433) Q2 = -2719.0950


Curve Values from Figures AA-2.4 and AA-2.5 QZ1 =

8.351214

QZ2 =

65.097820

U1 = 0.5 * Xa^4 [ Zv + (K-1) * Zm ] U1 = 0.5* 10.6654^4[ .0088 + ( 1.0122-1) * .1433 ] U1 = 67.9465

Equivalent Uniform Pressure Pea^2/2 = (bEshsQe-(JXIQ2)U1-0.5(Ps-Pt)a^2(K^2-1))(1+JXI[QZ1+(K-1)QZ2]) Pea^2/2 = (56.1250*25054998*.2500*-.0002-(.00*.2635* -2719.1)*67.9465-0.5*(50.00-50.00)*55.4480^2(1.0122^2-1))/ (1+.00*.2635*[8.3512+(1.0122-1)*65.0978]) Pea^2/2 = -76999.6200 lb.

Q3 = Q1 + Q2/(Pea^2/2) Q3 = .0085 + -2719.1/( -76999) Q3 = .0438


Curve Value from Figure AA-2.6 Fm =

.039082

The Tubesheet Bending Stress - Original Thickness: å = (2a/h)^2 ( 1.5 Fm Pe / ETA ) å = (2 * 55.4480 / 1.8125)^2 ( 1.5 * .0391 * -50.09 / .5061 ) å = -21720.5400 psi

The Allowable Tubesheet Bending Stress : å allowed = 1.5 * ê * S å allowed = 1.5 * 2.6667 * 15900.00 å allowed = 63600.0000 psi

The Tubesheet Bending Stress - Final Thickness: åf = (2a/h)^2 ( 1.5 Fm Pe / ETA ) åf = (2 * 55.4480 / .9680)^2 ( 1.5 * .0326 * -50.11 / .5061 ) åf = -63597.4200 psi

Required Tubesheet Thickness for Given Loadings : Including CAS &CAC H reqd. = H + CAS + CAC H reqd. = .9680 + .0000 + .0000 H reqd. = .9680 in.

Curve Values from Figure AA-2.4 ( Original Thickness ) Q3

23-26

=

.044




Xa

=

QZ1* = Pe

=

10.665 10.300 -50.090

psi

qt = Pe * QZ1* qt = -50.09 * 10.3001 qt = -515.9258 psi

STEP 8 The Tube Stress in the Outermost Tube Row :

Intermediate Constants fs and ft. fs = 1 - (nd^2)/(4a^2) fs = 1-(3100*.7500^2)/(4*55.4480^2) fs = .8582

ft = 1 - (nd^2)/(4a^2)[1-2t/d]^2 ft = 1-(3100*.7500^2)/(4*55.4480^2)[1-2*.0490/.7500]^2 ft = .8928

The Tube Stress in the Outermost Tube row. å = a^2/(n*t*d(1-t/d))*(Ps*fs-Pt*ft-qt) å =

55.4480^2/(3100*.0490*.7500(1-.0490/.7500))* (50.00*.8582-50.00*.8928—515.9258)

å = 14846.4700 psi

The Force on the Outermost Tube : TubeForce = TubeStress * Tube Area TubeForce = 14846.47 * .10791 TubeForce = 1602.0910 lb.

The Allowable Tube Force Per Appendix A VIII 1 Force Allowed = Area * Sot * FASME Force Allowed = .1079 * 13500.00 * .70 Force Allowed = 1019.7550 lb.

STEP 9 Bending Stresses in the Channel and Shell : åLc ( Channel ) = 5656.25 psi

åLs ( Shell ) = 124.78 psi

åc ( Channel ) = .00 psi

ås ( Shell ) = -13928.75 psi

CHANNEL STRESS SUMMATION vs. ALLOWABLE |åc| + |åLc| =< 1.5 * ê * Sc | 0 | + | 5656 | =< 1.5 * 2.6667 * 15900 5656.25 must be < or = 63600.0000

SHELL STRESS SUMMATION vs. ALLOWABLE |ås| + |åLs| =< 1.5 * ê * Ss | -13928 | + | 124 | =< 1.5 * 2.6667 * 15900 14053.53 must be < or = 63600.0000


23-27



SUMMARY of RESULTS for ASME Tubesheet Calculations Reqd Tubsheet Thickness+CAS+MAX(CAC,GRV)

HREQ

.9680

in.

HH

1.8125

in.

Required Thickness for the Flanged Portion FTREQ

.8857

in.

5.1250

in.

TubeForce ( on the outmost Tube )

1602.0910

lb.

TubeForce Allowed

1019.7550

lb.

Actual Tubsheet Thickness as Given

Actual

Thickness for the Flanged Portion

TF


23-28



&KDSWHU The Half-Pipe Module

Introduction The PVElite Half-Pipe Module performs pressure calculations for half-pipe jackets attached to cylindrical shells using the ASME Code, Section VIII, Division 1 rules.

Purpose, Scope, and Technical Basis The PVElite Half-Pipe Module performs required thickness and Maximum Allowable Working Pressure calculations for cylindrical shells with half-pipe jackets attached. The module is based on the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, 2001, A-2001. Specifically, the module is based on the rules in Paragraph EE-1, Appendix EE. The module first performs shell thickness calculations based on both the internal pressure and the externally applied half-pipe jacket pressure. In addition to the thickness calculations, the jacket MAWP is computed for both the input shell thickness and the required shell thickness. Once the required thickness of the shell is determined, the half-pipe jacket thickness is calculated. Finally, based on the shell and jacket thicknesses, an appropriate fillet weld size is calculated. It is important to note the limitations of the Half-Pipe Module. First, the half-pipe jacket analysis performed is only valid for the cylindrical geometries shown in Figure EE-4. These are the only two geometries addressed by paragraph EE-1. The analysis of rectangular or square jacketed geometries is not supported. The second limitation on the HalfPipe Module is the acceptable Nominal Pipe Sizes. Appendix EE only includes charts for Nominal Pipe Sizes 2, 3, and 4. Therefore, Nominal Pipe Sizes greater than 4 or less than 2 will not be accepted in the input. Although there are no charts for Nominal Pipe Sizes 2.5 and 3.5, the Half-Pipe Module will accept these sizes and perform iterations between the given charts. Additionally, if the half-pipe is a nonstandard pipe size or has a formed radius, the actual radius is used in the calculations. The Half-Pipe Module takes full account of corrosion allowance. Actual thickness values and corrosion allowances are entered, and the program adjusts thicknesses and diameters when making calculations for the corroded condition.

The Half-Pipe Module

24-1



Figure 24A shows the geometries accepted by the Half-Pipe Module.

Figure 24A - Acceptable Geometries for the Half-Pipe Module

24-2




Discussion of Input Data Item Number

Enter the Shell Section ID number. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Half-Pipe Section Description

Enter an alpha-numeric description for this item. This entry is optional. Inside Diameter of Shell

Enter the inside diameter of the shell or head. The value entered should be the uncorroded dimension of the inside diameter. This analysis is only valid for cylindrical shells, therefore, inputting inside diameter values for torispherical, elliptical, spherical, or conical heads will produce erroneous results. Thickness of Shell

Enter the thickness of the shell used to withstand the internal pressure. This thickness value will be tested to see if it can withstand both the internal shell pressure and the externally applied jacket pressure. Internal Pressure in Shell

Enter the internal design pressure used in the vessel analysis. This value will be used as an initial check on the required thickness of the shell. The value entered should be a positive value, i.e. 14.7 psia. Design Temperature for Internal Pressure

Enter the temperature associated with the internal design pressure. The PVElite program will automatically update material properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Shell Section Material Name

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Shell Allowable Stress at Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature.


24-3



Shell Allowable Stress at Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the ambient temperature. Shell Corrosion Allowance

Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter. Joint Efficiency for Longitudinal Seams

Enter the efficiency of the welded joint for shell sections with welded seams. This will be the efficiency of the longitudinal seam in the cylindrical shell. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. Nominal Pipe Size of Half-Pipe Jacket

Enter the nominal pipe size of the half-pipe jacket. The pipe size entered must lie within the range of values supported in ASME Section VIII, Div. 1, Appendix EE. The supported sizes range between NPS 2 inch and NPS 4 inch. If working in SI units, the proper conversion values must be entered. For example, if working with a NPS 50 pipe, the corresponding SI value of 5.08 cm must be entered. The following table lists the accepted values for the NPS. English Input NPS

NPS

2.0 in 2.5 in 3.0 in 3.5 in 4.0 in

50658090100-

SI PVElite Input 5.08 cm 6.35 cm 7.62 cm 8.89 cm 10.16 cm

Inside Radius of Formed Half-Pipe Jacket

Enter the radius of the formed half-pipe. This value will be used rather than the standard nominal pipe sizes. Thickness of Half-Pipe Jacket

Enter the thickness of the jacket used to withstand the internal pressure. If the thickness value of the jacket is not adequate to withstand the internal pressure, an acceptable thickness will be determined. Therefore, if the program is used for design purposes, enter a minimal value for jacket thickness. The program will determine an appropriate pipe schedule through iteration. It is important to note that the program selected pipe schedules include a standard mill tolerance of 0.875 (a reduction of 12.5%). This tolerance will not, however, be included in

24-4




the user input value of thickness. This allows users to include their own mill tolerance in their input value, without having this value further adjusted. Design Pressure in Jacket

Enter the internal design pressure used in the half-pipe jacket analysis. This value will be used to determine the required thickness of both the shell and the jacket. The value entered should be a positive value, i.e. 14.7 psia. Design Temperature for Jacket Pressure

Enter the temperature associated with the internal jacket pressure. The PVElite program will automatically update material properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Jacket Material Name

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Jacket Allowable Stress, Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the jacket, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Jacket Allowable Stress, Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the jacket, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code, Section II Part D at the ambient temperature. Corrosion Allowance of Jacket

Enter the corrosion allowance. The program adjusts both the actual thickness and the inside diameter for the corrosion allowance you enter.


24-5



Discussion of Results Shell Thickness Calculations

The first calculation the Half-Pipe Module performs is the required thickness of the shell due to the internal pressure. This value of required thickness is calculated using Equation 1 from Paragraph UG-27 of the ASME Code. The corroded value of thickness is used in this calculation. Because the exterior of the shell wall is also used as the internal half-pipe jacket wall (see Figure 24A), both the corrosion allowance of the shell and the corrosion allowance of the jacket must be accounted for. Both the calculation and the result are displayed in this section of the output. Once the required thickness due to inside pressure is determined, the required thickness due to the external pressure (jacket pressure) is determined and displayed. This value is obtained through the pressure calculations discussed in the next section. Pressure Calculations for Input Shell Thickness

The calculations displayed in this section of the output are the external (jacket) pressure calculations, performed using the input value of shell thickness. The first step in the pressure calculations is to determine the K-factor from the appropriate chart. The chart is selected based on the Nominal Pipe Size of the jacket and the K-factor is a factor of the shell inside diameter and the shell thickness. Both the chart and K-factor are displayed in the output. As stated earlier, for Nominal Pipe Size 2.5 or 3.5, an iteration is performed between the charts to obtain the K-factor. When this is the case, the output will display the two charts from which the iteration was performed. The next step in the external pressure calculations is to determine the longitudinal stress. This calculation accounts for the corrosion allowance by using a corroded value of the shell inside radius, as well as the corroded value of the shell thickness. Using the longitudinal stress and the previously determined K-factor, the permissible jacket pressure is determined using Equation 1, Paragraph EE-1, Appendix EE. The permissible jacket pressure is considered the Maximum Allowable Working Pressure for the input shell thickness, and it is compared to the input jacket design pressure. Half-Pipe Jacket Thickness Calculations

The input jacket thickness is tested to see if it is adequate to withstand the internal pressure of the jacket. The calculation is based on Equation 2, Paragraph EE-1, Appendix EE. As in previous calculations, the corrosion allowance is included in the thickness calculation. If the input thickness is not adequate, the program iterates for an appropriate pipe thickness. The iteration begins with Schedule 5S pipe and continues on until an acceptable schedule is found. As mentioned in the Discussion of Input section, the program selected pipe schedule is adjusted by a standard mill tolerance value (0.875). The user input value of thickness, however, does not use the mill tolerance adjustment. In the event that the input thickness is not adequate, both the selected pipe schedule and the adjusted thickness are displayed in the output. Minimum Fillet Weld Size Calculations

As mentioned in Paragraph EE-1, “The fillet weld attaching the half-pipe jacket to the vessel shall have a throat thickness not less than the smaller of the jacket or shell thickness.”

24-6




Therefore, the program selects the smaller of the two thicknesses, multiplies by a weld factor (1.414), and uses this value as the minimum fillet weld size. The output report indicates which of the two thicknesses that the calculation was based upon. Summary of Results

The first values displayed in the summary section are the shell thickness values. The echo of the input thickness is displayed along with the results of the two required thickness calculations. The comparison of these results provides a quick check of whether the thickness of the shell is governed by the internal or external pressure. The next three displayed values are the jacket pressure results. The input design pressure is shown along with the MAWP for both the input thickness and the required thickness. The next displayed values are those of the half-pipe jacket thickness. The input thickness is shown along with the required thickness. Additionally, if the input thickness is not adequate, the thickness selected by the program is displayed. Finally, the minimum fillet weld size is shown.


24-7

Example Problem


Example Problem The example problem is taken from the ASME Code, Section VIII, Division 1, Appendix EE. The Code example problem asks to find the required thickness of a cylindrical shell subjected to an inside pressure of 190 psi and a half-pipe jacket pressure of 300 psi. The ID of the shell is 40 inches, the allowable stress of the shell is 16,000 psi, the joint efficiency is 1.0, the half-pipe jacket is NPS 3, the allowable stress of the jacket is 12,000 psi, and there is no corrosion allowance. FileName : CHECKS

-----------------------------

HalfPipe Analysis : ASME EXAMPLE INPUT ECHO, HALF-PIPE

1,

Inside Diameter of Shell Thickness of Shell Internal Pressure in Shell

ITEM:

Page

04:56pm,

DIN

40.0000

in.

TS

.3125

in.

P

190.00

psig

716.67

F

Shell Section Material S

16000.00

psi

SA

17500.00

psi

Corrosion Allowance of Shell

CA

.0000

in.

E

1.00

Nominal Pipe Size of Half-Pipe Jacket

NPS

3.0000

in.

Minimum Thickness of Half-Pipe Jacket

TJCK

.0730

in.

P1

300.00

psig

800.00

F

Design Pressure in Jacket Design Temperature for Jacket Jacket Material Name Jacket Allowable Stress, Design Temp

05/18/98

SA-516 70

Shell Allowable Stress, Ambient

Joint efficiency for Shell Joint

1

Description: ASME EXAMPLE


Shell Allowable Stress, Design Temp

1,

SA-516 70 S1

12000.00

psi

Jacket Allowable Stress, Ambient

S1A

17500.00

psi

Corrosion Allowance of Jacket

CAJ

.0000

in.

SHELL THICKNESS CALCULATIONS:

Required Thickness of Shell per UG-27 Eqn(1) (Includes CA): Tr = ( P * R ) / ( S * E - 0.6 * P ) + ( CA + CAJ ) Tr = ( 190.00 * 20.000 )/( 16000.00 * 1.00 - 0.6 * 190.00 ) + .000 Tr = .2392 in.

Required Thickness of Shell to Withstand Jacket Pressure: Trj = .2813 in.

PRESSURE CALCULATIONS FOR INPUT SHELL THICKNESS:

Input Value of Shell Thickness: Ts = .3125 in.

Chart Used to Find the K-Factor: FIG. EE - 2

24-8



Example Problem

K-Factor Read from Chart: K = 46.5000

Longitudinal Stress in Shell due to Internal Pressure (Includes CA): SPrime = ( P * R ) / ( 2 * Ts ) Sprime = ( 190.0000 * 20.0000 ) / ( 2 * .3125 ) Sprime = 6080.0000 psi

Permissible Jacket Pressure per Appendix EE-1, Equation (1): Pprime = ( 1.5 * S - Sprime ) / K Pprime = ( 1.5 * 16000.00 - 6080.0000 ) / 46.50 Pprime = 385.3765 psig

HALF-PIPE JACKET THICKNESS CALCULATIONS:

Input Half-Pipe Jacket Thickness: Tj = .0730 in.

Req‘d Half-Pipe Jacket Thickness per App. EE-1, Eqn. (2) (Includes CA): T = ( P1 * R ) / ( .85 * S1 - .6 * P1 ) + CAJ T = ( 300.0000 * 1.6770 ) / ( .85 * 12000.00 - .6 * 300.0000 ) + .0000 T = .0502 in.

MINIMUM FILLET WELD SIZE CALCULATIONS:

Minimum Fillet Weld Size (Based on Jacket Thickness): Fillet = Tj / .875 * 1.414 Fillet = .0730 / .875 * 1.414 Fillet = .1180 in.

SUMMARY OF RESULTS:

Input Thickness of Shell

.3125

in.

Req.d Thickness of Shell due to Internal P.

.2392

in.

Req.d Thickness of Shell due to Jacket P.

.2813

in.

Pressure Used for Jacket Design

300.0000

psig

M.A.W.P. of Jacket for Input Thickness

385.3765

psig

M.A.W.P. of Jacket for Required Thickness

323.8394

psig

Input Thickness of Half-Pipe Jacket

.0730

in.

Required Thickness of Half-Pipe Jacket

.0502

in.

Minimum Acceptable Fillet Weld Size

.1180

in.



24-9

Example Problem

24-10




&KDSWHU The Large Opening Module

Introduction The PVElite Large Opening Module calculates the stresses and their allowables which act on integrally attached flat heads that have a large centrally located opening. This program is based on the ASME Code Section VIII Division 1, Appendix 2 and Appendix 14 of the 2001 Code, A-2001.

Purpose, Scope, and Technical Basis This module computes three different kinds of stresses which act on flat heads that have a hole or nozzle whose inside diameter is greater than 1/2 of the outside diameter of the flat head. Geometries with or without an attached nozzle may be analyzed. The first step in this process is to analyze the flange as a flat head and determine the total moment acting on the flange for the operating case. Since there is no gasket, the gasket seating case is neglected. The radial flange, tangential flange and longitudinal hub stresses are computed in accordance with Appendix 2. These three stresses, Sr*, St*, Sh* and some geometry constants are used to determine the actual radial, tangential, and longitudinal hub stresses. Two sets of stresses are computed, one for the head/shell juncture, and the second for the opening head juncture. If all of the computed stresses are below their allowables, the geometry is considered O.K. If any stress is greater than its allowable, the geometry must be reconsidered.

The Large Opening Module

25-1



Figure 25A shows the geometry for an attached nozzle. Figure 25B shows the geometry for an opening without an attached nozzle.

Figure 25A

Figure 25B

25-2




Discussion of Input Data Main Input Fields Large Central Opening Number

Enter the Flange ID number. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Opening Description

Enter an alpha-numeric description for this item. This entry is optional. It is however printed on output reports. This field should be meaningful to the item you are analyzing. Design Temperature

Enter the design temperature for this flange. This value will be used to look up the stress values for the material you have chosen from the material tables. Design Internal Pressure

Enter the design internal pressure for this flange. The pressure is used to compute the forces which act on the inside of the flange. One such example would be the hydrostatic end force. Note that only positive (internal) pressures are considered. Flat Head Thickness

Enter the thickness of the plate to be used to construct the flat head. Opening Inside Diameter

Enter the Inside Diameter (Bn) of the Opening here. Appendix 14 states that the opening should be centrally located in the flat head. The diameter of the opening should also be greater than 1/2 of the flange outside diameter. If your opening does not meet these criteria, do not use this module to analyze the opening. Flat Head Outside Diameter

Enter the outer diameter of the flat head. This is the dimension A as it appears in Appendix 14. It is normally the shell outside diameter. Shell Side Hub Thickness, Small End

Enter the thickness of the shell. This is referred to as value g0 in the ASME code. PVElite will use this value to compute the shell inside diameter Bs. Shell Side Hub Thickness, Large End

Enter the Large End hub thickness on the shell side. This value is g1 in the ASME Code. This will typically be the leg dimension of the weld which attaches the flat head to the shell. Shell Side Hub Length

Enter the length of the Hub on the shell side of the flange. This will usually be the length of the weld leg. The ASME Code refers to this as dimension h (shell). The hub length and


25-3



other hub dimensions g1 and g0 are used to determine the flange stress factors from Appendix 2. Corrosion Allowance

If your specification includes a corrosion allowance enter it here. PVElite corrects all dimensions such as the flange ID, and all hub thicknesses for the effect of corrosion. The CA cannot be greater than any of the entered shell hub or flange thickness dimensions. This will be flagged as an error. Material Specification

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Material Allowable Stress at Design Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section VIII Division 1 at the design temperature. Material Allowable Stress at Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. When you change the internal design temperature, or the thickness of the shell, the program will automatically update this field, but only for BUILT-IN materials. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section VIII Division 1 at the ambient temperature. Nozzle Side Hub Thickness, Small End

If there is a nozzle attached to the flat head enter the hub thickness here. If there is no nozzle attached, then enter a 0.0 here. This dimension will usually be the nozzle neck thickness. This dimension is referred to as g0 for the nozzle. Nozzle Side Hub Thickness, Large End

If there is a nozzle attached to the flat head enter the hub thickness of the large end. If there is no nozzle attached, enter a 0.0 . This dimension will usually be the weld leg dimension. This dimension is referred to as g1 for the nozzle. Nozzle Side Hub Length

If there is a nozzle attached to the flat head enter the hub length here. If there is no nozzle attached, enter a 0.0 . This dimension will usually be the weld leg dimension. This dimension is referred to as h for the nozzle.

25-4



Example Problem


------------------------------

Lgcenter Analysis : SENIOR GB TEST

INPUT ECHO, LGCENTER NUMBER

ITEM:

4,

Design Temperature

Page

4,

1

05:04pm,

05/18/98

Description: SENIOR GB TEST

TEMP

300.00

F

Design Pressure

P

225.00

psig

Integral Flat Head Thickness

T

2.5000

in.

Opening Inside Diameter

B

13.2500

in.

Flat Head Outside Diameter

A

24.0000

in.

Shell Side Hub Thickness, Small End

SG0

.3750

in.

Shell Side Hub Thickness, Large End

SG1

.3750

in.

5.0000

in.

.0000

in.

Shell Side Hub Length Corrosion Allowance

FCOR

Flange and Nozzle Material

SA-516 70

Allowable Stress at Design Temperature

SFO

17500.00

psi


SFA

17500.00

psi

Nozzle Side Hub Thickness, Small End

NG0

.3750

in.

Nozzle Side Hub Thickness, Large End

NG1

.3750

in.

Nozzle Side Hub Length

NHL

5.0000

in.

Diameter of the Load Reaction G = C per App. 14 G = FLGOD - 2.0 * SG1 + 2.0 * FCOR G = 24.0000 - 2.0 * .3750 + 2.0 * .0000 G = 23.2500 in. The Flange K Factor K = Flange OD / Flange ID K = 24.0000 / 13.2500 K = 1.8113 The Flange Radial Distance Dimension R R = 0.5 * ( G - FLGCID ) - ( SG1 - FCOR ) R = 0.5 * ( 23.2500 - 13.2500 ) - ( .3750 - .0000 ) R = 4.6250 in. The Hydrostatic End Force Hd Hd = PI/4 * Flange ID ^ 2 * P Hd = PI/4 * 13.2500^2 * 225.0000 Hd = 31024.4600 lb. The Moment Md Md = HD * ( R + 0.5 * ( SG1 - FCOR ) ) Md = 31024.46 * ( 4.6250 + 0.5 * ( .3750 - .0000 ) ) Md = 12442.1000 ft.lb. The Total Hydrostatic End Force H H = PI/4 * G^2 * P H = PI/4 * 23.2500^2 * 225.0000 H = 95525.2800 lb.


25-5

Example Problem


The Differential End Force Ht Ht = H - Hd Ht = 95525.28 - 31024.46 Ht = 64500.8300 lb. The Moment Mt Mt = 0.5 * Ht * ( R + SG1 ) Mt = 0.5 * 64500.83 * ( 4.6250 + ( .3750 - .0000 ) ) Mt = 13437.6700 ft.lb. The Total Moment Mo Mo = Md + Mt Mo = 12442.10 + 13437.67 Mo = 25879.7700 ft.lb.

Flange Factors ( Opening ) :

Factors from Figure 2-7.1

K =

1.811

T =

1.580

U =

3.779

Y =

3.439

Z =

1.877

Effective Hub Length,

H0 = SQRT(B*GZERO)

2.229 in.

Hub Ratio,

HRAT = HBLNG / H0

2.243

Thickness Ratio,

GRAT = (GONE/GZERO)

1.000


.908

Factor V per 2-7.3

.542

Factor f per 2-7.6

1.000 d =

2.185 in.^3

e =

Stress Factors

.407 in.^-1

ALPHA =

2.018

BETA =

2.358

GAMMA =

1.278

DELTA =

7.151

LAMBDA =

8.429

Longitudinal Hub Stress, Operating: SH* = ( F * RMO / B ) / ( RLAMBDA * GONE^2 ) SH* = ( 1.0000 * 310557 / 13.2500 ) / ( 8.4287 * .3750^2 ) SH* = 19774. psi Radial Flange Stress, Operating: SR* = ( BETA * RMO / B ) / ( RLAMBDA * TH^2 ) SR* = ( 2.3577 * 310557 / 13.2500 ) / ( 8.4287 * 2.5000^2 ) SR* = 1049. psi Tangential Flange Stress, Operating: ST* = ( Y*RMO / TH*TH*B ) - Z*SRO ST* = ( 3.4389 * 310557 / 2.5000^2 * 13.2500 ) - 1.8769 * 1048 ST* = 10927. psi

The Value for E Theta Star ( Integral Nozzle ) Et* = 0.91*(NG1/NG0)^2*B1*V*Sh*/(f*ho) Et* = 0.91*( .375 / .375 )^2 * 13.625 * .542 * 19774/( 1.000 * 2.229) Et* = 59630.8300 psi

Flange Factors ( Shell ) :

Effective Hub Length, Hub Ratio,

25-6

H0 = SQRT(B*GZERO) HRAT = HBLNG / H0

2.976 in. 1.680



Example Problem

Thickness Ratio,

GRAT = (GONE/GZERO)

1.000


.909

Factor V per 2-7.3

.547

Factor f per 2-7.6

1.000 d =

2.891 in.^3

e =

.305 in.^-1

Moment Acting at the Shell to Flat Head Juncture Mh = Et*/[(1.74*ho*V/(SG0^3*B1))+Et*/Mo*(1+Ft/ho)] Mh = 59630 /[(1.74 * 2.9765 * .5472 /( .3750^3 * 23.6250 ))+ 59630 / 310557 * ( 1 + .9086 * 2.5000 / 2.9765 ) Mh = 1901.4780 ft.lb.

The X1 Factor X1 = ( Mo - Mh( 1 + Ft/ho ) ) / Mo X1 = ( 310557 - 22817 ( 1 + .9086 * 2.5000 / 2.9765 ) ) / 310557 X1 = .8705

Stress Results for the Head/Shell Juncture :

Longitudinal Hub Stress in the Shell : Shs = (X1)(Eé*)(1.10*ho*f)/((g1/g0)^2*Bs*V) Shs = ( .87)( 59630)(1.10 * 2.976 * 1.000)/(( 1.000)^2 * 23.25) .547 ) Shs = 13357.6200 in.

Radial Stress at the Outside Diameter : Srs = 1.91*Mh(1+F*t/ho)/(Bs*t^2) + 0.64*F*Mh/(Bs*ho*t) Srs = 1.91 * 1901( 1 + .909 * 2.500 / 2.976 )/( 23.250 * 6.250^2 ) + 0.64 * .909* 1901/( 23.250 * 2.976 * 2.500 ) Srs = 605.5016 psi

Tangential Stress at the Outside Diameter : Sts = X1*Eé**t/Bs - .57(1+F*t/ho)Mh/(Bs*t^2) + .64*F*Z*Mh/(Bs*ho*t) Sts = .870 * 59630.830* 2.500 / 23.250 .57( 1 + .909 * 2.500 / 2.976) 1901 /( 23.250 * 6.2500^2 ) + .64 * .909 * 1.877 * 1901 /( 23.250 * 2.976 * 2.500 ) Sts = 5567.4130 psi

where Z = (K^2+1)/(K^2-1) = ( 3.281 + 1 )/( 3.281 - 1 ) = 1.877

Stress Results for the Opening Head Juncture :

Longitudinal Hub Stress in Central Opening : Sho = X1 ù Sh* = ( .870 * 19774.440 ) = 17212.740 psi

Radial Stress at Central Opening : Sro = X1 ù Sr* = ( .870 * 1048.993 ) = 913.100 psi

Tangential Stress at Diameter of Central Opening : Sto = X1*St*

+

.64*F*Z1*Mh/(Bs*ho*t)

Sto = .870 * 10927.420 + .64 * .9086 * 2.877 * 1901 / ( 23.250 * 2.976 * 2.500 ) Sto = 9732.4580 psi


25-7

Example Problem


where Z1 = 2*K^2/(K^2-1) = (2* 3.281 + 1 )/( 3.281 - 1 ) = 2.877

Flange Stress Results per Appendix 14

Long.

Hub

Radial Tangential

Head/Shell

Allowed

Opening

Allowed

13357

26250

17212

26250

psi

605

17500

913

17500

psi

5567

17500

9732

17500

psi

M.A.W.P. for the given Geometry

343.133

psig

Estimated Finished Weight of Forging

245.2

lb.

Approximate Minimum Flange Thickness

2.0640

in.


25-8



&KDSWHU The Rectangular Vessel Module

Introduction The PVElite Rectangular Vessel Module performs internal pressure calculations for rectangular vessels using the ASME Code, Section VIII, Division 1 rules.

Purpose, Scope, and Technical Basis The PVElite Rectangular Vessel Module performs stress calculations and Maximum Allowable Working Pressure calculations for the rectangular, obround, and circular vessels described in the ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, 2001, A-2001, Appendix 13. The calculations are taken from sections 13-6 through 13-13. The module will analyze the following vessels: •

Fig. 13-2 (a)(1) -Vessel with equal long-side and short-side thickness. (Figure 26A)

•

Fig. 13-2 (a)(2)-Vessel with differing long-side thickness. (Figure 26B)

•

Fig. 13-2 (a)(3)-Vessel with rounded corners. (Figure 26C)

•

Fig. 13-2 (a)(4)-Reinforced vessel. (Figure 26D)

•

Fig. 13-2 (a)(5)-Non-continuous reinforced vessel with rounded corners.(Figure 26E)

•

Fig. 13-2 (a)(6)-Non-continuous reinforced vessel with rounded corners. (Figure 26EE)

•

Fig. 13-2 (a)(7) -Rectangular vessel with single stay plate/row of bars. (Figure 26F)

•

Fig. 13-2 (a)(8)-Rectangular vessel with two stay plates/rows of bars. (Figure 26G)

•

Fig. 13-2 (b)(1) -Obround vessel. (Figure 26H)

•

Fig. 13-2 (b)(2)-Reinforced obround vessel. (Figure 26I)

•

Fig. 13-2 (b)(3) - Obround vessel with single stay plate/row of bars. (Figure 26J)

•

Fig. 13-2 (c)(1)-Circular vessel with single diametral plate. (Figure 26K)

The program first performs ligament efficiency calculations for those vessels with holes in the side plates. The membrane and bending ligament efficiencies are used to adjust the stress calculations at the mid-side of the plates. The ligament efficiency calculations are based on section 13-6, and are performed for both uniform and multi diameter hole patterns. Once the ligament efficiencies are determined, the individual stress calculations are performed. Membrane, bending, and total stress calculations are performed as prescribed by

The Rectangular Vessel Module

26-1



the Code in Sections 13-7 through 13-13. These stresses are compared to their allowables, and a highest percentage of allowable calculation is performed. The final calculation performed by the Rectangular Vessel module is the Maximum Allowable Working Pressure calculation. The program computes a M.A.W.P. for all three types of stresses (Membrane, Bending, and Total). Additionally, depending on the specific geometry of those vessels stayed by bars, an additional M.A.W.P. is computed per Equation 2 of UG-47. The Rectangular Vessel module takes full account of corrosion allowance. The program uses the corroded condition for all dimensions in its calculations. The only exception is the reinforcement calculations. The reinforcing member is assumed to be entered in its corroded state.

Figure 26A - Rectangular vessel with equivalent long side thickness (Type A1)

26-2




Figure 26B - Rectangular vessel with different long side thickness (Type A2)

Figure 26C - Rectangular vessel with rounded corner (Type A3)


26-3



Figure 26D - Reinforced rectangular vessel (Type A4)

Figure 26E - Non-continuously reinforced rectangular vessel (Type A5)

26-4




Figure 26EE - Non-continuously reinforced vessel with rounded corners (Type A6)

Figure 26F - Vessel stayed by stay plate/stay bars (Type A7 or A7-B)


26-5



Figure 26G - Vessel stayed by stay plates/stay bars (Type A8 or A8-B)

Figure 26H - Obround vessel (Type B1)

26-6




Figure 26I - Reinforced obround vessel (Type B2)

Figure 26J - Obround vessel stayed by stay plate/stay bars (Type B3 or B3-B)


26-7



Figure 26K - Circular vessel stayed by single diametral plate (Type C1)

26-8




Discussion of Input Data Main Input Fields Item Number

Enter the Rectangular Vessel ID number. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Rectangular Vessel Description

Enter an alpha-numeric description for this item. This entry is optional. Design Internal Pressure

Enter the Internal Design Pressure. The internal design pressure is a required entry. For vessel type C1 (Figure 26K), this is the entry for P1. If analyzing vessel type C1 be aware that the P1 value is associated with only one of the two chambers. If both chambers are operating at the same pressure, then an equal value must be entered for P2. Design Temperature for Internal Pressure

Enter the temperature associated with the internal design pressure. The PVElite program will automatically update materials properties for BUILT-IN materials when you change the design temperature. If you entered the allowable stresses by hand, you are responsible to update them for the given temperature. Material Name

Enter the ASME code material specification as it appears in the ASME material allowable tables. Alternatively, the material can be selected from the material data base by right clicking and selecting Database, while the cursor is in this field. If a material is not contained in the data base, its specification and properties can be entered manually by selecting Tools, Edit/Add Materials, from the Main Menu. Material Allowable Stress at Design Temperature

This entry is automatically filled in by the program by entering a material specification. When the material temperature is specified, all material properties associated with that temperature will be automatically updated for materials that appear in the database. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the design temperature. Material Allowable Stress at Ambient Temperature

This entry is automatically filled in by the program by entering a material specification. If you enter the allowable stress by hand, be sure to double check your entry to assure conformance with the latest edition of the ASME Pressure Vessel Code Section II Part D at the ambient temperature.


26-9



Minimum Yield Stress for This Material

Enter the yield stress for this material. The ASME Code, Section II Part D lists the yield stress for the material at ambient temperature. For many kinds of analysis, this is the appropriate value to enter. If you need to use the yield stress at design temperature, you can probably find it in the ASME Code, Section II Part D. If analyzing a reinforced vessel this is a required entry for both the shell material and the reinforcement material. These entries are used in determining an allowable stress for both bending and total stresses, and if this entry is left blank, the program will assume zero for the allowable stress. Figure Number for Type of Vessel

Enter the ID of the type of rectangular vessel to be analyzed. The possible ID types are as follows:

ID

Figure

Vessel Type

A1

Figure 26A

Rectangular vessel with equal long-side plate thickness

A2

Figure 26B

Rectangular vessel with unequal long-side thickness

A3

Figure 26C

Rectangular vessel with rounded corners

A4

Figure 26D

Reinforced rectangular vessel

A5

Figure 26E

Non-continuously reinforced rectangular vessel

A6

Figure 26EE

Non-continuous reinforced with rounded corners

A7

Figure 26F

Rectangular vessel with single stay plate

A7-B

Figure 26F

Rectangular vessel with single row of bars

A8

Figure 26G

Rectangular vessel with two stay plates

A8-B

Figure 26G

Rectangular vessel with double row of bars

B1

Figure 26H

Obround vessel

B2

Figure 26I

Reinforced obround vessel

B3

Figure 26J

Obround vessel with single stay plate

B3-B

Figure 26J

Obround vessel with single row of bars

C1

Figure 26K

Circular vessel with single diametral plate

Short-Side Length Dimension

Enter the design length of the short-side of the vessel. This dimension is dependent on the particular vessel being analyzed. For Figure:

26-10

A1 H

Inside length of long-side of vessel

A2 H


A3 L1

Half-length of short-side minus the corner radius




A4 H

Inside length of short-side of vessel

A5 L3

Half-length of short-side of vessel

A6 L3

Half-length of short-side of vessel

A7 h


A7-Bh


A8 h


A8-Bh


B1 2R

Inside Diameter of Rounded Short-side

B2 2R


B3 2R


B3-B2R


C1 *** No Entry Required *** Minimum Thickness of Short-Side Plate

Enter the minimum thickness of the short-side plate used to build the vessel, or the minimum thickness measured for an existing vessel. The short-side thickness value is a required entry for all vessel types. For those vessels that the Code specifies a single thickness (A3 and C1), the short-side thickness is used for both t1 and t2. Joint Efficiency for Welded Seams

Enter the efficiency of the welded joint for vessels with welded joints. This joint efficiency value will be used to adjust the corner and the mid-side allowable stress values. The midside joint efficiencies will not be used if there are holes on the side of the vessel. Instead, the ligament efficiencies will be used to adjust the actual stress values. Please be sure to refer to Section VIII, Div. 1, Table UW-12 for help in determining this value. Typical values are •

1.00 Full Radiography

•

0.85 Spot X - Ray

•

0.70 No - Radiography

Threaded Holes in Plates

If the plate has uniform or multi diameter holes, check this field in order to enter the pitch, diameter, and depth parameters. Ligament efficiency calculations will be performed in order to adjust the calculated actual stress values. Type of Reinforcement

Enter the index for the type of reinforcement on the rectangular vessel. When a reinforced vessel is selected, the first responses are those of the pitch distance and the delta value.


26-11



Long-Side Length Dimension

Enter the design length of the long-side of the vessel. This dimension is dependent on the particular vessel being analyzed. For Figure: A1 h


A2 h


A3 L2

Half-length of long-side minus the corner radius

A4 h


A5 L4

Half-length of long-side

A6 L4

Half-length of long-side of vessel

A7 h


A7-Bh


A8 h


A8-Bh


B1 L2

Half length of long-side of vessel

B2 L2


B3 L2


B3-BL2


C1 *** No Entry Required *** Minimum Thickness of Long-Side Plate

Enter the minimum thickness of the long-side plate used to build the vessel, or the minimum thickness measured for an existing vessel. Per Appendix 13, vessels A3 and C1 (Figure 26C and 26K, respectively) are assumed to have equivalent long and short-side thickness’. Thus, the long-side thickness is not a required entry for these two vessel types. Minimum Thickness of End Plate

Enter the minimum thickness of the end plate. If a valid thickness is entered, the end plate will be analyzed per UG-34. If the thickness value is entered as zero, or left blank, no calculations will be performed on the end plate. Corrosion Allowance

Enter the appropriate corrosion allowance. The program adjusts the actual thickness and the inside diameter of the vessel, and adjusts the actual thickness and the outside diameter of the stay plate/bar. C Factor for End Closure Plate/Vessel Head

The C Factor is used in the equation to compute the required thickness of welded end plates. Typical values are 0.2 or 0.3. See UG-34 for details.

26-12




Pop-Up Input Fields Design External Pressure

Enter the design external pressure for figure A1 or A2 if you wish to have the external pressure calculations performed. When entered external pressure stress calculations as well as vessel stability calculations will be performed. Modulus of Elasticity

If an external pressure has been input, enter the Elastic Modulus of the material from Subpart 3 of Section II, Part D at design temperature. Length of Vessel

Enter length dimension of vessel type C1. Minimum Thickness of 2nd Long-Side Plate

Enter the minimum thickness of the 2nd long-side plate used to build the vessel, or the minimum thickness measured for an existing vessel. This entry is only used in the analysis of vessel A2 (Figure 26B). Appendix 13 allows vessels of this type to have differing long-side thickness. If analyzing a type A2 vessel this is a required entry. Radius of Corner Section

Enter the radius of the corner section for vessels A3 and A5. The program assumes each of the corner sections to have equivalent radii. Pitch Distance Between Reinforcement

Enter the maximum pitch distance between reinforcing members. This value must be greater than or equal to the width of the reinforcing member. C-Factor

The C-factor is an attachment factor for braced and stayed surfaces. This factor is taken from UG-47, and will default to 2.1. Delta

Material parameter used to calculate pitch. Materials listed in Appendix 13, Table 13-8(3):


26-13


Material


English

Carbon Steel 6000 Austinitic SS 5840 Ni-Cr-Fe 6180 Ni-Fe-Cr 6030 Aluminum 3560 Nickel Copper 5720 Unalloyed Titanium 4490

SI 15754.54 15334.42 16227.17 15833.31 9347.69 15019.33 11789.65

Unreinforced Length Dimension

Enter the unreinforced length dimension for figure A6. This dimension is L11 for the short-side and L21 for the long-side. Minimum Thickness/Diameter of Stay Plate/Rod (T3)

Enter the minimum thickness of the stay plate, or the diameter of the rod, if analyzing a stayed vessel. This is a required entry if analyzing type A7, A7-B, A8, A8-B, B3, or B3-B. Minimum Thickness/Diameter of Stay Plate/Rod (T4)

Enter the minimum thickness of the stay plate, or the diameter of the rod, if analyzing a stayed vessel. This is a required entry if analyzing type A8, or A8-B. Is the Stay Plate/Rod Welded to the End Plate?

If you do not check this box, PVElite will perform the end plate calculations based on the entire long-side length. If you do check this box, the program will use the dimensions of the compartment formed by the stay plate. Pitch Distance Between Bars

Enter the maximum pitch distance between stay bars. This value must be greater than or equal to the calculated maximum pitch of the stay bars. Vessel Radius

Enter the inside radius of the vessel type C1. Pressure in 2nd Compartment

Enter the internal pressure of the 2nd compartment in vessel C1. You must enter an internal design pressure that is less than or equal to P1. In the event that the two compartments have equivalent pressure, the value entered for P2 must equal the value entered for P1. If left blank, a value of zero is used for P2. Center to Center Distance Between Poles

Enter the maximum pitch distance between holes in the side plates of the vessel being analyzed. This pitch distance is shown in Figure 26L. This value must be greater than the hole diameter.

26-14




Figure 26L - Plate with multicomputer holes

Diameter of Hole

Enter the diameter (d0, d1, d2) of the hole of corresponding length (T0, T1, T2). If the hole is of uniform diameter, then a value for d0 is the only required entry. Refer to Figure 26L. The values for d0, d1, and d2 must be entered in decreasing diameter size. Depth of Hole

Enter the depth (T0, T1, T2) of the hole of corresponding diameter (d0, d1, d2). If the hole is of uniform diameter, then a value for T0 is the only required entry. Refer to Figure 26L. The sum of the values for T0, T1, and T2 must equal to the entire side thickness. Type of Reinforcing Ring

Three types of reinforcement are available: None—No reinforcing ring Simple Bar Geometry—Enter the width, thickness, and length (if necessary) of the bar. Distance from Outside of Vessel

Enter the distance from the outer surface of the vessel to the outermost point on the reinforcing bar or beam. Width of Reinforcing Member

Enter the width of the reinforcing member. This value is the distance that the reinforcement remains in contact with the vessel wall. This value cannot be greater than the reinforcement pitch, as that would indicate that the reinforcement if overlapping. Length of Reinforcing Member

For vessel type A5, this entry represents the entire length of the discontinuous reinforcement. No entry is required for other vessel types.


26-15



General Beam Section—Enter the moment of inertia, cross-sectional area, and the distance from the centroid. Cross-Sectional Area of Reinforcing Section

Enter the cross sectional area for the beam section which is being used as reinforcement. Moment of Inertia of Reinforcing Member

Enter the moment of inertia for the beam section which is being used as a reinforcement, in the direction parallel to the surface of the vessel. Centroid Distance from Outside of Vessel

Enter the distance from the surface of the vessel to the centroid of the reinforcing ring. This distance should be measured normal to the vessel surface. Length of Reinforcing Member

For vessel type A5, this entry represents the entire length of the discontinuous reinforcement. No entry is required for other vessel types. In all cases the program includes the vessel wall in the calculation of the moment of inertia.

26-16




Discussion of Results Ligament Efficiency Calculations

When the side plates have uniform or multi diameter holes, ligament efficiency calculations are performed according to Section 13-6. For the case of uniform diameter holes, the ligament efficiency factors em and eb for membrane and bending stresses, respectively, are considered to be the same. In the case of multi diameter holes (see Figure 26L), the neutral axis of the ligament may no longer be at mid thickness of the plate; in this case, for bending loads, the stress is higher at one of the plate surfaces than at the other surface. If the calculated values of em and eb are lower than the entered midpoint joint efficiencies, the calculated stress values are divided by these calculated ligament efficiencies. It is important to note that if the stresses have been adjusted by the ligament efficiencies, then the calculations for the allowable stresses will assume an E value of 1.0. This avoids incorrectly increasing the stress values while decreasing the allowables at the same time. Reinforcement Calculations

The reinforcement calculations performed for vessels A4, A5, and B2 (Figures 26D, 26E, and 26I), are discussed in section 13-8. The rectangular vessel program only addresses those vessels in which the reinforcement on opposite side plates have the same moment of inertia. Additionally, the reinforcement for vessels A4 and B2 is assumed to be continuous, while A5 is assumed to be non-continuous. The first reinforcement calculation is that of the maximum pitch between reinforcing member center lines. Equation 1 of UG-47 is used to set a basic maximum distance. Using this maximum value, equations (1a)-(1d) in Section 13-8 are used to obtain a maximum value for both the long and short-side plates. The minimum calculated value shall be considered the maximum distance between reinforcement center lines. In addition to the above calculations, the geometry of the reinforcement must be checked. Specifically, the width of the reinforcing members cannot physically exceed the pitch. Once the pitch is determined, the moment of inertia of the composite section (shell and reinforcement) is determined by the Area-Moment method. The moment of inertia calculations are performed for locations where the plate is in compression, and then also performed for locations where the plate is in tension. Equation (2) of Section 13-8 is used to calculate the maximum width of the shell plate which can be used to compute the effective moments of the composite section at locations where the shell plate is in compression. At locations where the shell plate is in tension, an effective width equal to the actual pitch distance is used in the computations. Stress Calculations

The stress calculations are performed for membrane, bending, and total stresses. The calculations are performed for both the inner and outer surface of the long and short-side plates. These actual stress values are displayed along with their allowables in tabular form. A positive (+) stress indicates tensile stress, while a negative (-) stress indicates compressive stress. As previously discussed, the calculated values for the membrane and bending stresses are adjusted by the ligament efficiency calculations if em and eb are less than the joint efficiency E. At the mid-side locations, the stresses are increased by dividing the calculated value by the membrane or bending ligament efficiency. In the event that the plates have


26-17



holes but the ligament efficiencies are higher than the joint efficiency E, there is no adjustment to the stress calculations, rather the allowables are adjusted by the value E. Calculations performed on stay plates/bars are membrane stresses, and these stresses are used in the M.A.W.P. calculations for membrane stresses. Computation of the stresses on end plates is performed if a thickness value for the end plate is input. The calculations are performed per UG-34 with a C factor entered by the user. These stresses are not used in the computation of the MAWP. Allowable Calculations

Membrane stresses are in general compared to the adjusted allowable stress, SE. Note that for reinforced members the program compares the membrane stress to the lower of the plate allowable stress or beam allowable stress. Note also that when there are holes in the side, the joint efficiency may be set to 1.0 in favor of a membrane efficiency which is factored into the actual stress calculation as necessary. Bending stresses and total stresses are in general compared to 1.5 times the adjusted allowable stress, SE. Note that for reinforced members the program compares the actual stress to the lower of the plate allowable stress or beam allowable stress, and also to the lower of 2/3 times the plate yield stress or beam yield stress. It chooses the lowest of these four combinations as the allowable for reinforced cases. Note also that when there are holes in the side, the joint efficiency at the mid-side may be set to 1.0 in favor of a membrane efficiency which is factored into the actual stress calculations as necessary. Highest Percentage of Allowable Calculations

After performing the actual stress calculation and computing the allowable stresses at all locations, the program computes the highest stress/allowable ratio for each of the three stress types. The program displays the highest percentage of the allowable used, and the actual stress value that this percentage relates to. MAWP Calculations

The Maximum Allowable Working Pressure is calculated for each of the three stress types. The computation of the M.A.W.P. is performed by setting the stress equations equal to the allowables, and solving for P. The minimum computed P value is considered to be the maximum allowable working pressure for the particular stress type. When analyzing vessels A7-B or A8-B (Figures 26G and 26H stayed by bars), an additional pressure rating is computed. If the long-side height is greater than the pitch of the stay bars, then a pressure rating is computed per Eq. (2) of UG-47 with the long-side height substituted for the pitch. If this value of pressure is less than the previously calculated M.A.W.P.s, then this becomes the vessel pressure rating. Similarly for vessel B3-B (Figure 26J stayed by bars), if (L2 + R/2) is greater than the pitch, then an additional pressure rating is computed per Eq. (2) of UG-47 with (L2 + R/2) substituted for the pitch. External Pressure Calculations

External pressure calculations are performed on vessel A1 and A2 if the user has entered a value for external pressure. These calculations are performed per Appendix 13, Section 13-14. First, the external pressure is substituted for internal pressure, and the calculations discussed previously are performed again. Next, the four side plates and the end plates are

26-18




checked for stability per equation (1) of 13-14(b). Finally, the entire cross section is checked for column stability in accordance with equation (1) from paragraph 13-14(c).


26-19

Example Problems


Example Problems Example problem 1 analyzes vessel type A1 (Figure 26A). This vessel has holes in the two long-side plates, and uses the ligament efficiency calculations. This is the Code example problem 13-17(a). Rectangular Vessels Per ASME VIII Div.1 Appendix 13 PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON

FileName : RCTEXMPL -------------------------------- Page

Rectves Analysis : EXAMPLE A1


ITEM:

1,

05:15pm,

05/18/98

Description: EXAMPLE A1

Figure Number Analyzed


1,

1

A1

P

115.0000

psig

Temp

650.0000

F

S

17500.0000

psi


SA

17500.0000

psi

Shell Yield Stress at Design Temperature

Sy

.0000

psi

Design Temperature

VESSEL MATERIAL DATA: Material Specification Shell Allowable Stress at Design Temp

SA-516 70

SHORT-SIDE VESSEL DATA: Short-side Length Dimension Minimum Thickness of Short-side Plates Mid-side Joint Efficiency on Short-side Corner Joint Efficiency on Short-side

H

6.0000

in.

t1

.6250

in.

E

.8000

EC

.8000

LONG-SIDE VESSEL DATA: Long-side Length Dimension Minimum Thickness of Long-side Plates Mid-side Joint Efficiency on Long-side

h

13.5000

in.

t2

1.0000

in.

E

.8000

t5

.5000

in.

ADDITIONAL VESSEL DATA: Minimum Thickness of End Plate

LIGAMENT EFFICIENCY DATA: Long-side Plate # 1, Pitch Distance

p

3.7500

in.

Uniform Hole Diameter

d0

1.5000

in.

Depth of Holes

T0

1.0000

in.

Long-side Plate # 2, Pitch Distance # 1: Hole Diameter Hole Depth # 2: Hole Diameter Hole Depth

p

3.7500

in.

d0

1.7500

in.

T0

.6250

in.

d1

1.2500

in.

T1

.3750

in.

INTERNAL PRESSURE RESULTS, RECTANGULAR VESSEL # 1, Desc: EXAMPLE A1

26-20



Example Problems

PRELIMINARY CALCULATION RESULTS: Moment of Inertia of a Strip of the Vessel Wall: Thickness

t1, I1

= .0203 in**4

Thickness

t2, I2

= .0833 in**4

Ligament Efficiency Calculations (Section 13-6, Equations (1)-(6)): Em

Eb

Ci

Short-side 1

.800

.800

.313

-.313

2

.800

.800

.313

-.313

1

.600

.600

.500

-.500

2

.583

.564

.473

-.527

Long-side

Co

Rectangular Vessel Parameters: Alpha = K

H / h

= .4444

= (I2/I1)*Alpha = 1.8204

MEMBRANE STRESSES:

Membrane Stress Calculations per Section 13-7, Equations (1) and (2). (psi) :

STRESS LOCATIONS

Actual

Allowable

Short-side 1

1242.00

14000.00

Short-side 2

1242.00

14000.00

Short-side Corner

1242.00

14000.00

Long-side

1 at A

575.00

17500.00

Long-side

2 at A

591.43

17500.00

345.00

14000.00

Long-side Corner

BENDING STRESSES:

Bending Stress Calculations per Section 13-7, Equations (3-6). (psi) :

STRESS LOCATIONS

Inner

Outer

Allowable

Short-side 1 at N

4983.24

-4983.24

21000.00

at Q

12932.04

-12932.04

21000.00

Short-side 2 at N

4983.24

-4983.24

21000.00

at Q

12932.04

-12932.04

21000.00

1 at M

-17779.14

17779.14

26250.00

at Q

5051.58

-5051.58

21000.00

2 at M

-17909.12

19936.57

26250.00

at Q

4780.96

-5322.20

21000.00

Long-side

Long-side

TOTAL STRESSES:

Total Stress Calculations per Section 13-7, Equations (7-10). (psi) :

STRESS LOCATIONS

Inner

Outer

Allowable

Short-side 1 at N

6225.24

-3741.24

21000.00

at Q

14174.04

-11690.04

21000.00

Short-side 2 at N

6225.24

-3741.24

21000.00

at Q

14174.04

-11690.04

21000.00

Long-side 1 at M at Q Long-side


18354.14

26250.00

5396.58

-4706.58

21000.00

2 at M

-17317.69

20527.99

26250.00

at Q

5125.96

-4977.20

21000.00

END PLATE STRESSES (psi) : End Plate

-17204.14

Actual 7728.00

Allowable 17500.00

26-21

Example Problems


SUMMARY OF RESULTS (INTERNAL PRESSURE):

MEMBRANE STRESS SUMMARY, High Stress (Highest % of Allowable) High Stress Percentage M.A.W.P. for Membrane Stresses

1242.00 8.87 1296.30

psi % psig

BENDING STRESS SUMMARY, High Stress (Highest % of Allowable) High Stress Percentage M.A.W.P. for Bending Stresses

19936.57 75.95 151.42

psi % psig

TOTAL STRESS SUMMARY, High Stress (Highest % of Allowable) High Stress Percentage M.A.W.P. for Total Stresses

20527.99 78.20 147.06

psi % psig


26-22



Example Problems

Example problem 2 analyzes vessel type A4 (Figure 26D). This reinforced vessel is the Code example problem 13-17(d). Rectangular Vessels Per ASME VIII Div.1 Appendix 13 PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON

FileName : RCTEXMPL ----------------------------------- Page



ITEM:

4,

05:15pm,

05/18/98




4,

1

A4

P

15.0000

Temp

400.0000

S

13800.0000

psi


SA

13800.0000

psi


Sy

25700.0000

psi

Design Temperature

psig F


SA-285 C

SHORT-SIDE VESSEL DATA: Short-side Length Dimension Minimum Thickness of Short-side Plates Mid-side Joint Efficiency on Short-side Corner Joint Efficiency on Short-side

H

61.6250

in.

t1

.3750

in.

E

.8500

EC

1.0000

LONG-SIDE VESSEL DATA: Long-side Length Dimension

h

83.6250

in.

t2

.3750

in.

E

.8500

Reinf Allowable Stress at Design Temp

Sr

14500.0000

psi

Reinf Allowable Stress at Ambient

SA

14500.0000

psi

Reinf Yield Stress at Design Temp

Sy

30800.0000

psi

14.0000

in.

Minimum Thickness of Long-side Plates Mid-side Joint Efficiency on Long-side

REINFORCEMENT MATERIAL DATA: Reinforcement Material Specification

Pitch Distance for Reinforcement

SA-36

C-Factor for Reinforcement ( from UG-47)

2.1000

DELTA (Reinforcement Material Parameter)

6000.0000

SHORT-SIDE SECTIONAL DATA: Cross-sectional Area of Reinforcement Moment of Inertia of Reinforcement

3.6100 21.8000

sq.in. in**4

Outside Distance from Outside of Vessel

6.0000

in.

Centroid Distance from Outside of Vessel

3.0000

in.

Width of Reinforcing Member

7.0000

in.

5.3400

sq.in.

LONG-SIDE SECTIONAL DATA: Cross-sectional Area of Reinforcement


26-23

Example Problems


Moment of Inertia of Reinforcement

56.9000

in**4

Outside Distance from Outside of Vessel

8.0000

in.

Centroid Distance from Outside of Vessel

4.0000

in.

Width of Reinforcing Member

7.0000

in.

RECTANGULAR VESSEL RESULTS, ITEM NUMBER

4, Description: EXAMPLE A4

REINFORCEMENT CALCULATIONS: Maximum Distance B/W Reinforcing Member (Eq.(1) of UG-47): p = 16.4829 in.

Beta and J Values Taken from Table 13-8(d): Short-side BETA = 3.7387 J Long-side

= 2.0261

BETA = 5.0734 J

= 2.0000

Max Pitch Values for Long and Short-side Based on Equations (1a)-(1d) from Section 13-8: Short-side p1 = 16.1904 in. Long-side

p2 = 16.0857 in.

Maximum Pitch ( Minimum of p, p1, and p2 ) pmax = 16.0857 in.

Effective Width of Shell Plate at Locations where the Plate is in Compression ( Section 13-8, Eq. (2) ): w = 14.0000 in.

Effective Width of Shell Plate at Locations where the Plate is in Tension: w = 14.0000 in.

Effective Area of Reinforcement on Shell ( t * w ): Short-side Ap = 5.2500 sq.in. Long-side

Ap = 5.2500 sq.in.

Moment of Inertia of Effective Area of Reinforcement ( w * t**3 / 12 ): Short-side Is = .0615 in**4 Long-side

Il = .0615 in**4

Moment of Inertia of Combined Reinforcement and Effective Width: In Compression I11 = 43.5952 in**4 I21 = 103.3825 in**4 In Tension

I11 = 43.5952 in**4 I21 = 103.3825 in**4

Distance from Neutral Axis of Cross Section of Composite Section to the Inside Surface of the Vessel (in.): Ci

Co

1.4862

-4.8888

in Tension

1.4862

-4.8888

in Compression

2.2990

-6.0760

in Tension

2.2990

-6.0760

Short-side, in Compression

Long-side,

26-24



Example Problems

Rectangular Vessel Reinforcement Parameters: Alpha1 =

H1 / h1

= .7787

k(comp)= (I22/I11)*Alpha1 = 1.8466 k(tens)= (I22/I11)*Alpha1 = 1.8466

MEMBRANE STRESSES:

Membrane Stress Calculations per Section 13-8, Equations (3) and (4). (psi) :

STRESS LOCATIONS

Actual

Allowable

Short-side 1

991.04

11730.00

Short-side 2

991.04

11730.00

Short-side Corner

991.04

13800.00

Long-side

1 at A

611.01

11730.00

Long-side

2 at A

611.01

11730.00

611.01

13800.00

Long-side Corner

BENDING STRESSES:


STRESS LOCATIONS

Outer

Allowable

Short-side 1 at N

-291.75

959.65

17133.33

at Q

3106.81

-10219.35

17133.33

Short-side 2 at N

-291.75

959.65

17133.33

at Q

3106.81

-10219.35

17133.33

1 at M

-2055.69

5432.82

17133.33

at Q

2026.58

-5355.88

17133.33

2 at M

-2055.69

5432.82

17133.33

at Q

2026.58

-5355.88

17133.33

Long-side

Long-side

TOTAL STRESSES:

Inner


STRESS LOCATIONS

Inner

Short-side 1 at N

699.30

1950.69

17133.33

at Q

4097.85

-9228.31

17133.33

Short-side 2 at N

699.30

1950.69

17133.33

at Q

4097.85

-9228.31

17133.33

1 at M

-1444.68

6043.83

17133.33

at Q

2637.59

-4744.87

17133.33

2 at M

-1444.68

6043.83

17133.33

at Q

2637.59

-4744.87

17133.33

Long-side

Long-side

Outer

Allowable

Note: The following can be used for outer stress: Short-side 1 at N, outer allowable

18487.50 psi

Short-side 2 at N, outer allowable

18487.50 psi

Long-side

1 at M, outer allowable

18487.50 psi

Long-side

2 at M, outer allowable

18487.50 psi

At Corner Q, outer allowable

20533.33 psi

SUMMARY OF RESULTS:


991.04 8.45 177.54

psi % psig

BENDING STRESS SUMMARY,


26-25

Example Problems


High Stress (Highest % of Allowable)

-10219.35

psi

High Stress Percentage

59.65

%

M.A.W.P. for Bending Stresses

25.15

psig

TOTAL STRESS SUMMARY, High Stress (Highest % of Allowable)

-9228.31

psi


53.86

%

M.A.W.P. for Total Stresses

27.85

psig


26-26



Example Problems

Example problem 3 analyzes vessel type A7 (Figure 26F). This vessel which is stayed by a single plate is a COADE generated example problem. Rectangular Vessels Per ASME VIII Div.1 Appendix 13 PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON

FileName : RCTEXMPL ---------------------------------- Page



ITEM:

5,

05:15pm,

05/18/98




5,

1

A5

P

20.0000

Temp

500.0000

S

17500.0000

psi


SA

17500.0000

psi


Sy

30800.0000

psi

Short-side Length Dimension

L3

25.0000

in.

Minimum Thickness of Short-side Plates

t1

.7500

in.

E

1.0000

EC

1.0000

Long-side Length Dimension

L4

30.0000

in.

Minimum Thickness of Long-side Plates

t2

1.0000

in.

E

1.0000

R

7.5000

Reinf Allowable Stress at Design Temp

Sr

17500.0000

psi

Reinf Allowable Stress at Ambient

SA

17500.0000

psi

Reinf Yield Stress at Design Temp

Sy

30800.0000

psi

Pitch Distance for Reinforcement

7.0000

in.

C-Factor for Reinforcement ( from UG-47)

2.1000

DELTA (Reinforcement Material Parameter)

6000.0000

Design Temperature

psig F


SA-515 70

SHORT-SIDE VESSEL DATA:

Mid-side Joint Efficiency on Short-side Corner Joint Efficiency on Short-side

LONG-SIDE VESSEL DATA:

Mid-side Joint Efficiency on Long-side

ADDITIONAL VESSEL DATA: Radius of Corner Sections

in.

REINFORCEMENT MATERIAL DATA: Reinforcement Material Specification

SA-515 70

SHORT-SIDE RECTANGULAR BEAM DATA: Outside Distance from Outside of Vessel Length of Reinforcing Member Width of Reinforcing Member

3.0000

in.

14.0000

in.

.7500

in.

LONG-SIDE RECTANGULAR BEAM DATA:


26-27

Example Problems


Outside Distance from Outside of Vessel Length of Reinforcing Member Width of Reinforcing Member

RECTANGULAR VESSEL RESULTS, ITEM NUMBER

3.0000

in.

18.0000

in.

.7500

in.

5, Description: EXAMPLE A5

REINFORCEMENT CALCULATIONS: Maximum Distance B/W Reinforcing Member (Eq.(1) of UG-47): p = 32.1496 in.

Beta and J Values Taken from Table 13-8(d): Short-side BETA = 1.0887 J Long-side

= 4.2489

BETA = 1.3997 J

= 3.3196

Max Pitch Values for Long and Short-side Based on Equations (1a)-(1d) from Section 13-8: Short-side p1 = 45.7300 in. Long-side

p2 = 53.8952 in.

Maximum Pitch ( Minimum of p, p1, and p2 ) pmax = 32.1496 in.

Effective Width of Shell Plate at Locations where the Plate is in Compression ( Section 13-8, Eq. (2) ): w = 7.0000 in.

Effective Width of Shell Plate at Locations where the Plate is in Tension: w = 7.0000 in.

Effective Area of Reinforcement on Shell ( t * w ): Short-side Ap = 5.2500 sq.in. Long-side

Ap = 7.0000 sq.in.

Moment of Inertia of Effective Area of Reinforcement ( w * t**3 / 12 ): Short-side Is = .2461 in**4 Long-side

Il = .5833 in**4

Moment of Inertia of Combined Reinforcement and Effective Width: In Compression I11 = 7.4707 in**4 I21 = 9.1644 in**4 In Tension

I11 = 7.4707 in**4 I21 = 9.1644 in**4

Distance from Neutral Axis of Cross Section of Composite Section to the Inside Surface of the Vessel (in.): Ci Short-side, in Compression

Long-side,

26-28

Co

.9375

-2.8125

in Tension

.9375

-2.8125

in Compression

.8919

-3.1081

in Tension

.8919

-3.1081



Example Problems

Rectangular Vessel Reinforcement Parameters: In Compression, K4 (Sec.13-8, Eqn.39) = -216.1620 Ma =

p * P * K4

Theta (Sec.13-8 )

= -30262.6900 = 37.8778

Mr (Sec.13-8, Eqn.38) = 16729.4200 In Tension, K4 (Sec.13-8, Eqn.39) = -216.1620 Ma =

p * P * K4

= -30262.6900

Mr (Sec.13-8, Eqn.38) = 16729.4200

MEMBRANE STRESSES:

Membrane Stress Calculations per Section 13-8, Equations (21-23). (psi) :

STRESS LOCATIONS

Actual

Allowable

Long-side

1 at A

500.00

17500.00

at B

500.00

17500.00

at C

500.00

17500.00

2 at A

500.00

17500.00

at B

500.00

17500.00

at C

500.00

17500.00

Short-side 1 at F

800.00

17500.00

at G

800.00

17500.00

at H

800.00

17500.00

Short-side 2 at F

800.00

17500.00

at G

800.00

17500.00

at H

800.00

17500.00

960.12

17500.00

Long-side

Corner Sections

BENDING STRESSES:


STRESS LOCATIONS Long-side

Inner

Outer

Allowable

1 at A

-2945.20

10263.58

20533.33

at B

-21079.45

21079.45

26250.00

at C

4435.55

-4435.55

26250.00

2 at A

-2945.20

10263.58

20533.33

at B

-21079.45

21079.45

26250.00

at C

4435.55

-4435.55

26250.00

Short-side 1 at F

15885.43

-15885.43

26250.00

at G

-11554.57

11554.57

26250.00

at H

-1381.98

4145.95

20533.33

Short-side 2 at F

15885.43

-15885.43

26250.00

at G

-11554.57

11554.57

26250.00

at H

-1381.98

4145.95

20533.33

14339.50

-14339.50

26250.00

Long-side

Corner Sections

TOTAL STRESSES:



Long-side


Inner

Outer

Allowable

1 at A

-2445.20

10763.58

20533.33

at B

-20579.45

21579.45

26250.00

at C

4935.55

-3935.55

26250.00

2 at A

-2445.20

10763.58

20533.33

at B

-20579.45

21579.45

26250.00

at C

4935.55

-3935.55

26250.00

26-29

Example Problems


Short-side 1 at F

16685.43

-15085.43

26250.00

at G

-10754.57

12354.57

26250.00

at H

-581.98

4945.95

20533.33

Short-side 2 at F

16685.43

-15085.43

26250.00

at G

-10754.57

12354.57

26250.00

at H

-581.98

4945.95

20533.33

15299.62

-13379.38

26250.00

Corner Sections

SUMMARY OF RESULTS:


960.12 5.49 364.54

psi % psig

BENDING STRESS SUMMARY, High Stress (Highest % of Allowable)

21079.45

psi


80.30

%


24.91

psig


21579.45

psi


82.21

%


24.33

psig


26-30



Example Problems

Example problem 4 analyzed vessel type B1 (Figure 26H). This obround vessel is the Code example problem 13-17(f). Rectangular Vessels Per ASME VIII Div.1 Appendix 13 PVElite Licensee: COADE ENGINEERING SOFTWARE, INC. HOUSTON

FileName : RCTEXMPL ---------------------------------- Page

Rectves Analysis : EXAMPLE B1


ITEM: 11,

11,

1

05:15pm,

05/18/98

Description: EXAMPLE B1


B1


P

20.0000

Temp

650.0000

S

17500.0000

psi


SA

17500.0000

psi


Sy

30800.0000

psi

Short-side Length Dimension

2R

20.0000

in.

Minimum Thickness of Short-side Plates

t1

.5000

in.

E

1.0000

EC

1.0000

Long-side Length Dimension

L2

10.0000

in.

Minimum Thickness of Long-side Plates

t2

.7500

in.

E

1.0000

t5

.6250

Design Temperature

psig F

VESSEL MATERIAL DATA: Material Specification

SA-515 70

Shell Allowable Stress at Design Temp

SHORT-SIDE VESSEL DATA:

Mid-side Joint Efficiency on Short-side Corner Joint Efficiency on Short-side

LONG-SIDE VESSEL DATA:

Mid-side Joint Efficiency on Long-side

ADDITIONAL VESSEL DATA: Minimum Thickness of End Plate

in.

RECTANGULAR VESSEL RESULTS, ITEM NUMBER 11, Description: EXAMPLE B1

PRELIMINARY CALCULATION RESULTS: Moment of Inertia of a Strip of the Vessel Wall: Thickness

t1, I1

= .0104 in**4

Thickness

t2, I2

= .0352 in**4

Rectangular Vessel Parameters: Alpha2 =

I2 / I1

= 3.3750

Gamma

L2 / R

= 1.0000

=

A

( Section 13-5 ) = 126.0288

C1

( Section 13-5 ) = 7430.8630

MEMBRANE STRESSES:

Membrane Stress Calculations per Section 13-10 Equations (1-3). (psi) :

STRESS LOCATIONS


Actual

Allowable

26-31

Example Problems


Long-side

1 at A

266.67

17500.00

at B

266.67

17500.00

2 at A

266.67

17500.00

at B

266.67

17500.00

Short-side 1 at B

400.00

17500.00

at C

800.00

17500.00

Short-side 2 at B

400.00

17500.00

at C

800.00

17500.00

Long-side

BENDING STRESSES:



Inner

Outer

Allowable

1 at A

20964.14

-20964.14

26250.00

at B

-10297.47

10297.47

26250.00

2 at A

20964.14

-20964.14

26250.00

at B

-10297.47

10297.47

26250.00

Short-side 1 at B

-23169.32

23169.32

26250.00

at C

24830.68

-24830.68

26250.00

Short-side 2 at B

-23169.32

23169.32

26250.00

at C

24830.68

-24830.68

26250.00

Long-side

TOTAL STRESSES:



Inner

Outer

Allowable

1 at A

21230.81

-20697.47

26250.00

at B

-10030.81

10564.14

26250.00

2 at A

21230.81

-20697.47

26250.00

at B

-10030.81

10564.14

26250.00

Short-side 1 at B

-22769.32

23569.32

26250.00

at C

25630.68

-24030.68

26250.00

Short-side 2 at B

-22769.32

23569.32

26250.00

at C

25630.68

-24030.68

26250.00

Long-side

END PLATE STRESSES (psi) : End Plate

Actual

Allowable

4096.00

17500.00

SUMMARY OF RESULTS:


800.00 4.57 437.50

psi % psig

BENDING STRESS SUMMARY, High Stress (Highest % of Allowable)

-24830.68

psi


94.59

%


21.14

psig


25630.68

psi


97.64

%


20.48

psig


26-32



&KDSWHU 7KH:5&$QQH[* 0RGXOH Introduction The WRC 297 analysis module performs local stress calculations on cylinder to cylinder attachments according to the Welding Research Council’s bulletin number 297 or PD 5500, Annex G.

Purpose, Scope, and Technical Basis The WRC 297 bulletin was published in 1984 and attempts to extend the existing analysis of WRC 107 for cylinder to cylinder intersections. In many cases the d/D ratio is beyond the limit of WRC 107 and the limit of WRC 297 extends this ratio from 0.3 to 0.5. Another important difference is that WRC 297 computes the stresses in the nozzle wall where the WRC 107 analysis does not. This module provides inputs for all of the information required to perform this analysis. Please note that this method does not perform stress analysis of nozzles on spheres as WRC 107 does, nor does it address square or rectangular attachments.

Discussion of Input Data Item Number

Enter the item’s ID number. This may be the item number on the drawing, or numbers that start at 1 and increase sequentially. Description

Enter an alpha-numeric description for this item. This entry is optional. Diameter Basis for Vessel

The dimension basis can be specified on either inside (Id) or outside (Od) dimension basis. Vessel Diameter

Enter in the actual diameter of the vessel using the Id or Od as specified above. Vessel Wall Thickness

Enter in the wall thickness of the vessel. This thickness should be measured at the intersection of the nozzle and the vessel.

The WRC 297/Annex G Module

27-1



Vessel Corrosion Allowance

Enter in the corrosion allowance if there is any. The program will adjust the Id and thickness appropriately. Design Pressure

The design pressure will be used to compute membrane stresses on the nozzle and vessel wall. It will also be used to compute axial pressure thrust if instructed to do so. Design Temperature

This is design temperature for the vessel. This value is used to look up allowable stresses for the vessel and nozzle materials from the ASME Section II Part D material table. Vessel Material

The vessel material can be typed in selected from the material database. Right Click on this field to access the properties for this material or access the database. Vessel Stress Concentration Factor

This value typically varies from 1 to 3 and is a function of the quality of the weld and the local dimensions in the immediate vicinity of the weld. Stress concentration factors are a measure of a very local stress riser because of sharp corners, no filet radii, etc. This stress concentration factor will apply for the stress calculations in the vessel on both the inside and outside of the vessel. This stress concentration factor is not used in any way with the pressure stress calculations. Is there a Reinforcing Pad?

If this nozzle has a pad check this button and you will be prompted to enter in the diameter of the pad along the vessel surface and the pad thickness. This will cause the program to perform stress calculations at the edge of the pad. Diameter Basis for Nozzle

The dimension basis can be specified on either inside (Id) or outside (Od) dimension basis. Diameter of Nozzle

Enter in the actual inside or outside diameter of the nozzle as appropriate. Nozzle Wall Thickness

Enter in the minimum nozzle wall thickness at the shell to nozzle junction. This value should include any allowances for mill tolerance. Nozzle Corrosion Allowance

Enter in the corrosion allowance for the nozzle. This value typically ranges from 0 to 3/ 16" or more depending on the service and design specifications.

27-2




Axial Force "P" (IN WRC 107 ) or FR (IN PD 5500)

Enter the value for the load which is trying to push or pull the nozzle in/out of the vessel. The program does not account for the effect of pressure thrust. In WRC 107 convention: Positive loads to "push" the nozzle while negative loads try to "pull" the nozzle. While in PD 5500 convention Positive loads try to "pull" the nozzle while negative loads try to "push" the nozzle. The following figures should clarify these conventions. Shear Force VC (IN WRC 107 ) or FC (IN PD 5500)

Enter the longitudinal shear load VC (or FC in PD 5500 convention) in the units above. Enter this value in accordance with the convention used either WRC 107 or PD 5500. The following figure should clarify these conventions. Shear Force VL (IN WRC 107 ) or FL (IN PD 5500)

Enter the longitudinal shear load VL (or FL in PD 5500 convention) in the units above. Enter this value in accordance with the convention used either WRC 107 or PD 5500. The following figure should clarify these conventions. Torsional Moment MT

Enter the torsional moment in the units displayed above. Enter this value in accordance with the convention used either WRC107 or PD 5500. The following figures should clarify these conventions. Circumferential Moment MC

Enter the circumferential moment MC or M1 in the units displayed above. Enter this value in accordance with the used either WRC 107 or PD 5500. The following figures should clarify these conventions. Note that this moment has opposite signs in these conventions.


27-3



Longitudinal Moment ML

Enter the longitudinal moment ML or M2 in the units displayed above. Enter this value in accordance with the convention used either WRC107 or PD 5500. The following figures should clarify these conventions.

WRC 107 Naming Convention

27-4




PD 5500 Naming Convention

Add Axial Pressure Thrust ?

If this box is checked the force due to pressure times the internal pipe area will be added to or subtracted from the radial load "P". Use Stress Indices (AD 560.7)?

If this box is checked the nominal computed pressure stress on the vessel wall as defined in paragraph AD-560.7 will be multiplied by the stress indices as they are listed in that paragraph of the ASME Code Section VIII Division 2. This is essentially the computation of the surface stress intensity. If the design specification requires the use of these indices, check this box. Please note that these indices are not used in the calculation of the pressure stress on the nozzle. The program will multiply the pressure stress on the nozzle by a factor of 1.2.


27-5



Additional Input for PD 5500, Annex G

Allowable Stress Increase Factor (Membrane + Bending) This factor is multiplied by the allowable stress f, to obtain an allowable stress for the maximum membrane plus bending stress intensity. These stresses are in rows 27, 28 and 29 in the printout samples in PD 5500 Annex G. This entry normally has a value of 2.25 or lower. The program will use a value of 2.0 for this factor for stresses computed at the edge of the pad.

Allowable Stress Increase Factor (Membrane) This factor is multiplied by the allowable stress f, to obtain an allowable stress for the maximum membrane stress intensity. These stresses are in rows 32, 33 and 34 in the printout samples in PD 5500 Annex G. This entry normally has a value of 1.2 or lower.

Nozzle Inside Projection If this nozzle has a projection inside of the vessel, enter that length into this field. This value is used to determine the pressure stress intensification factor from the graphs in Section 3 of the PD 5500 Code. These curves for Cers/eps have been digitized and are used by the program. All of the curves for protruding and flush nozzles are included for analysis.

Stiffened Length of Vessel Section Enter in the length of the vessel on which this nozzle lies. For vessels without stiffeners or cones this would be the entire vessel length accounting for the heads as necessary. This value is used along with the "Distance from left Tangent" field to compute the equivalent length for off center loading.

Offset from Left Tangent Line Enter in the distance that the centerline of the nozzles is with respect to the left tangent line or appropriate line of support. This value is used in conjunction with the vessel length to compute the equivalent length for off center loading.

Is the Location of the Nozzle in the Vessel Spherical? If the nozzle is located within the spherical portion of an elliptical or torispherical head or is in a spherical head then check this box. If you are entering this data manually ensure that you are entering the spherical diameter. This is especially important for nozzle located in elliptical heads. Checking this box causes the program to access the various curves used to compute the spherical factors for nozzles connected to spheres per Annex G.

27-6



Sample Calculation

Sample Calculation Input Echo, WRC297 Item

1,

Description: WRC NOZ

Diameter Basis for Vessel Corrosion Allowance for Vessel Vessel Diameter Vessel Thickness Vessel Stress Concentration Factor

Vbasis Cas Dv Tv Scfn

OD 0.0000 120.000 1.000 0.000

in. in. in.

Diameter Basis for Nozzle Corrosion Allowance for Nozzle Nozzle Diameter Nozzle Thickness Nozzle Stress Concentration Factor

Nbasis Can Dn Tn Scfv

OD 0.0000 12.000 0.375 0.000

in. in. in.

Dp P Vc Vl Mt Mc Ml

100.00 100.00 200.00 300.00 400.00 0.00 0.00

psig lb. lb. lb. ft.lb. ft.lb. ft.lb.

Design Internal Pressure Radial Load Circumferential Shear Longitudinal Shear Torsional Moment Circumferential Moment Longitudinal Moment Include Axial Pressure Thrust

No

Stress Computations at the Edge of the Nozzle --------------------------------------------WRC 297 Curve Access Parameters: Nr/P Mr/P M0/P N0/P MrD/Mc NrDL/Mc M0d/Mc N0DL/Mc MrD/Ml NrDL/Ml M0D/Ml N0DL/Ml

= = = = = = = = = = = =

0.082 0.109 0.084 0.209 0.185 0.118 0.174 0.150 0.143 0.098 0.121 0.300

VESSEL Stresses LONGITUDINAL PLANE (Stresses Normal to longitudinal plane)

Au Al Bu Bl Top Top Bottom Bottom Outside Inside Outside Inside -----------(psi )-----------Outplane Membrane (P ) 0 0 0 0 Outplane Bending (P ) 0 0 0 0 Outplane Membrane (Mc) 0 0 0 0 Outplane Bending (Mc) 0 0 0 0 Outplane Membrane (ML) 0 0 0 0 Outplane Bending (ML) 0 0 0 0 Normal Pressure Stress 7139 18444 7139 18444 ----------------------- -------- -------- -------- -------Outplane Stress Summary 7139 18444 7139 18444 VESSEL Stresses LONGITUDINAL PLANE (Stresses Normal to longitudinal plane)


Au Top Outside

Al Top Inside

Bu Bottom Outside

Bl Bottom Inside

27-7

Sample Calculation


-----------(psi )-----------Inplane Membrane (P ) 0 0 0 0 Inplane Bending (P ) 0 0 0 0 Inplane Membrane (Mc) 0 0 0 0 Inplane Bending (Mc) 0 0 0 0 Inplane Membrane (ML) 0 0 0 0 Inplane Bending (ML) 0 0 0 0 Inplane Pressure Stress 5949 -1189 5949 -1189 ----------------------- -------- -------- -------- -------Inplane Stress Summary 5949 -1189 5949 -1189 VESSEL Stresses LONGITUDINAL PLANE (Shear stress normal to longitudinal plane)

Au Al Bu Bl Top Top Bottom Bottom Outside Inside Outside Inside -----------(psi )-----------Outplane Shear (Vc) 10 10 -10 -10 Outplane Shear (Vl) 0 0 0 0 Outplane Shear (Mt) 21 21 21 21 ----------------------- -------- -------- -------- -------Shear Stress Summary 31 31 11 11 VESSEL Stresses LONGITUDINAL PLANE (Stress Intensities

Two * Max Shear Stress

Au Al Top Top Outside Inside -----------(psi 7139 19633

Bu Bl Bottom Bottom Outside Inside )-----------7139 19633

VESSEL Stresses CIRCUMFERENTIAL PLANE (Stresses Normal to circumferential plane)

Cu Cl Du Dl Left Left Right Right Outside Inside Outside Inside -----------(psi )-----------Outplane Membrane (P ) 0 0 0 0 Outplane Bending (P ) 0 0 0 0 Outplane Membrane (Mc) 0 0 0 0 Outplane Bending (Mc) 0 0 0 0 Outplane Membrane (ML) 0 0 0 0 Outplane Bending (ML) 0 0 0 0 Normal Pressure Stress 12494 5949 12494 5949 ----------------------- -------- -------- -------- -------Outplane Stress Summary 12494 5949 12494 5949 VESSEL Stresses CIRCUMFERENTIAL PLANE (Stresses parallel to circumferential plane)

Cu Cl Du Dl Left Left Right Right Outside Inside Outside Inside -----------(psi )-----------Inplane Membrane (P ) 0 0 0 0 Inplane Bending (P ) 0 0 0 0 Inplane Membrane (Mc) 0 0 0 0 Inplane Bending (Mc) 0 0 0 0 Inplane Membrane (ML) 0 0 0 0 Inplane Bending (ML) 0 0 0 0 Inplane Pressure Stress 15469 -1189 15469 -1189 ----------------------- -------- -------- -------- -------Inplane Stress Summary 15469 -1189 15469 -1189 VESSEL Stresses CIRCUMFERENTIAL PLANE (Shear stress normal to circumferential plane) Outplane

27-8

Shear

(Vc)

Cu Cl Left Left Outside Inside -----------(psi 0 0

Du Dl Right Right Outside Inside )-----------0 0



Sample Calculation

Outplane Shear (Vl) -15 -15 15 15 Torsional Shear (Mt) 21 21 21 21 ----------------------- -------- -------- -------- -------Shear Stress Summary 6 6 36 36 VESSEL Stresses CIRCUMFERENTIAL PLANE (Stress Intensities

Two * Max Shear Stress

Cu Cl Left Left Outside Inside -----------(psi 15469 7138

Du Dl Right Right Outside Inside )-----------15469 7138

NOZZLE Stresses LONGITUDINAL PLANE (Stresses in the hoop direction)

Au Al Bu Bl Top Top Bottom Bottom Outside Inside Outside Inside -----------(psi )-----------Hoop Membrane (P ) 0 0 0 0 Hoop Bending (P ) 0 0 0 0 Hoop Membrane (Mc) 0 0 0 0 Hoop Bending (Mc) 0 0 0 0 Hoop Membrane (ML) 0 0 0 0 Hoop Bending (ML) 0 0 0 0 Hoop Pressure Stress 1741 1861 1741 1861 ----------------------- -------- -------- -------- -------Hoop Stress Summary 1741 1861 1741 1861 NOZZLE Stresses LONGITUDINAL PLANE (Stresses Normal to pipe cross-section)

Au Al Bu Bl Top Top Bottom Bottom Outside Inside Outside Inside -----------(psi )-----------Axial Membrane (P ) 0 0 0 0 Axial Bending (P ) 0 0 0 0 Axial Membrane (Mc) 0 0 0 0 Axial Bending (Mc) 0 0 0 0 Axial Membrane (ML) 0 0 0 0 Axial Bending (ML) 0 0 0 0 Axial Pressure Stress 870 870 870 870 ----------------------- -------- -------- -------- -------Axial Stress Summary 870 870 870 870 NOZZLE Stresses LONGITUDINAL PLANE (Shear stress)

Au Al Bu Bl Outside Inside Outside Inside -----------(psi )-----------Shear due to (Vc) 28 28 -28 -28 Shear due to (Vl) 0 0 0 0 Shear due to Torsion 56 56 56 56 ----------------------- -------- -------- -------- -------Shear Stress Summary 84 84 28 28 NOZZLE Stresses LONGITUDINAL PLANE (Stress Intensities Two * Max Shear Stress NOZZLE Stresses CIRCUMFERENTIAL PLANE (Stresses in the hoop direction) Hoop Membrane (P ) Hoop Bending (P )


Au Al Outside Inside -----------(psi 1749 1868

Bu Bl Outside Inside )-----------1741 1861

Cu Cl Left Left Outside Inside -----------(psi 0 0 0 0

Du Dl Right Right Outside Inside )-----------0 0 0 0

27-9

Sample Calculation


Hoop Membrane (Mc) 0 0 0 0 Hoop Bending (Mc) 0 0 0 0 Hoop Membrane (ML) 0 0 0 0 Hoop Bending (ML) 0 0 0 0 Hoop Pressure Stress 1741 1861 1741 1861 ----------------------- -------- -------- -------- -------Hoop Stress Summary 1741 1861 1741 1861 NOZZLE Stresses CIRCUMFERENTIAL PLANE (Stresses Normal to pipe cross-section)

Cu Cl Du Dl Left Left Right Right Outside Inside Outside Inside -----------(psi )-----------Axial Membrane (P ) 0 0 0 0 Axial Bending (P ) 0 0 0 0 Axial Membrane (Mc) 0 0 0 0 Axial Bending (Mc) 0 0 0 0 Axial Membrane (ML) 0 0 0 0 Axial Bending (ML) 0 0 0 0 Axial Pressure Stress 870 870 870 870 ----------------------- -------- -------- -------- -------Axial Stress Summary 870 870 870 870 NOZZLE Stresses CIRCUMFERENTIAL PLANE (Shear stress)

Cu Cl Du Dl Outside Inside Outside Inside -----------(psi )-----------Shear due to (Vc) 0 0 0 0 Shear due to (Vl) -42 -42 42 42 Shear due to Torsion 56 56 56 56 ----------------------- -------- -------- -------- -------Shear Stress Summary 14 14 98 98 NOZZLE Stresses CIRCUMFERENTIAL PLANE (Stress Intensities Two * Max Shear Stress

27-10

Cu Cl Outside Inside -----------(psi 1741 1861

Du Dl Outside Inside )-----------1751 1870




Discussion of Results The WRC 297 stress evaluation method computes stress intensities in the nozzle and vessel wall at the junction of the intersection on the upper and lower surface at eight different points. Typically, stress intensities can be compared with the yield stress of the material at operating temperature. However, users should read the WRC 297 bulletin carefully for further clarification and evaluation of stress results. Since this method produces quite a bit of output, it may be useful to use the option to produce only the summary of results. To do this use the tools -> configuration option (miscellaneous tab) and check the appropriate box to produce the results in a summary fashion. Note that this directive will affect all of the generated reports in the file.


27-11

Appendix G Sample Problem


Appendix G Sample Problem Input Echo, Annex G Item 1, Description: test Diameter Basis for Vessel Vbasis OD Corrosion Allowance for Vessel Cas 0.1587 Vessel Diameter Dv 3048.000 Vessel Thickness Tv 25.400 Vessel Shell Design Allowable Stress f 137.900 Vessel Shell Yield Strength fy 218.916 Allowable Stress Intensity Factor (Mem + Bend) 2.25 Allowable Stress Intensity Factor (Membrane) 1.20 Diameter Basis for Nozzle Nbasis OD Corrosion Allowance for Nozzle Can 0.0000 Nozzle Diameter Dn 304.800 Nozzle Thickness Tn 25.400 Nozzle Inside Projection h 0.000 Stiffened Length of Vessel Section L 2540.00 Offset from Left Tangent Line Dx 1270.00 Design Internal Pressure Dp 0.69 Radial Load Fr -9785.60 Circumferential Shear Fc 7005.60 Longitudinal Shear Fl 0.00 Torsional Moment Mt -1171843.2 Circumferential Moment Mc 7595280.3 Longitudinal Moment Ml 3058456.6

mm. mm. mm. N./mm² N./mm²

mm. mm. mm. mm. mm. mm. N./sq.mm. N. N. N. N.mm. N.mm. N.mm.

Stress Calculations at the Edge of the Nozzle Neck :

==================================================

Intermediate Values

L o n g i t u d i n a l At Point A

Circ.

Point B

Radial

At C

---------------------------------------------------------------------------K Factor K Load over the Area W Equivalent Length Le Parameter Cx Parameter Cø Parameter 64r(Cx/r) Parameter 2Cx/Le Parameter Cø/Cx G6 G7 G8 G9

Curve Curve Curve Curve

G6 G7 G8 G9

at at at at

Circ. Long. Circ. Long.

27-12

Value Value Value Value

Zero Zero Zero Zero

8.0000 19317.4 2530.1311 39.5817 118.7450 2.6284 0.0313 3.0000

8.0000 -19317.4 2530.1311 39.5817 118.7450 2.6284 0.0313 3.0000

1.5748 47972.2 2540.0000 118.7450 39.5817 23.6552 0.0935 0.3333

0.1425 0.1381 -0.1917 -0.1427

0.1425 0.1381 -0.1917 -0.1427

0.1774 0.1074 -0.1601 -0.1491

0.3139 0.2267 -0.2050 -0.1609

0.3139 0.2267 -0.2050 -0.1609

value value value value

Mø Mx Nø Nx

0.4539 0.6092 0.9352 0.8867

0.4539 0.6092 0.9352 0.8867

Curve Value Curve Value

Mø3/W Mx3/W

0.1058 0.0376

0.1058 0.0376

9785.6 2540.0000 118.7450 118.7450 23.6552 0.0935 1.0000




Curve Value Curve Value

Nø3/W Nx3/W

-0.0550 -0.0982

-0.0550 -0.0982

Value Value Value Value

Mø2/W Mx2/W Nø2/W Nx2/W

0.0480 0.0229 -0.0514 -0.0870

0.0480 0.0229 -0.0514 -0.0870

Mø/W Mx/W Nøt/W Nxt/W

0.0945 0.1152 -0.1403 -0.0557

0.0945 0.1152 -0.1403 -0.0557

Circ. Long. Circ. Long.

value value value value

Pressure Stress SIF

0.1774 0.1074 -0.1601 -0.1491

0.1232 0.0838 -0.1538 -0.1427

2.0455

PD 5500 Annex G Nozzle to Cylinder Stress Evaluation ------------------------------------------------------Quadrant Surface

Q1 In

Q2 Out

Q3

Q4

In

Out

In

Out

In

Out

Circumferential Stresses: Membrane Component (Nø/t) due to: Radial Load -2. -2. -2. Circ. Moment -12. -12. -12. Long. Moment -4. -4. 4. Sub-Total loc. -19. -19. -10. Pressure (fp) 84. 84. 84. Sub-Total(føm) 66. 66. 74.

-2. -12. 4. -10. 84. 74.

-2. 12. 4. 14. 84. 98.

-2. 12. 4. 14. 84. 98.

-2. 12. -4. 5. 84. 90.

-2. 12. -4. 5. 84. 90.

Bending Component (6Mø/t²) due to: Radial Load 11. -11. 11. Circ. Moment 80. -80. 80. Long. Moment 17. -17. -17. Sub-Total(føb) 109. -109. 74.

-11. -80. 17. -74.

11. -80. -17. -86.

-11. 80. 17. 86.

11. -80. 17. -52.

-11. 80. -17. 52.

-----------------------------------------------------------------------------Tot. Circ. Str

174.

-43.

149.

0.

12.

184.

38.

141.

Longitudinal Stresses: Membrane Component (Nx/t) due to: Radial Load -2. -2. -2. Circ. Moment -11. -11. -11. Long. Moment -2. -2. 2. Sub-Total loc. -15. -15. -12. Pressure (fp) 84. 84. 84. Sub-Total(fxm) 69. 69. 73.

-2. -11. 2. -12. 84. 73.

-2. 11. 2. 11. 84. 95.

-2. 11. 2. 11. 84. 95.

-2. 11. -2. 7. 84. 92.

-2. 11. -2. 7. 84. 92.

Bending Component (6Mx/t²) due to: Radial Load 8. -8. 8. Circ. Moment 49. -49. 49. Long. Moment 21. -21. -21. Sub-Total(fxb) 77. -77. 35.

-8. -49. 21. -35.

8. -49. -21. -62.

-8. 49. 21. 62.

8. -49. 21. -20.

-8. 49. -21. 20.

-----------------------------------------------------------------------------Tot. Long. fx

147.

-8.

108.

37.

33.

157.

72.

112.

Shear Stresses due to: Torsion Moment 0. Circ. Shear 1. Long. Shear 0.

0. 1. 0.

0. 1. 0.

0. 1. 0.

0. 1. 0.

0. 1. 0.

0. 1. 0.

0. 1. 0.


27-13



-----------------------------------------------------------------------------Tot. Shear tau

1.

1.

1.

1.

1.

1.

1.

1.

Check of Total Stress Intensity (membrane + bending) f1 Principle 174. -8. 149. 37. 33. f2 Principle 147. -43. 108. 0. 12. f2-f1 -28. -35. -41. -37. -21.

184. 157. -27.

72. 38. -34.

141. 112. -30.

Check of Buckling Stress (only if Row 4, 15 in Compression) Row 4 + Row 10 90. -127. 64. -84. 0. 0. Row15 + Row 21 62. -92. 24. -47. 0. 0.

0. 0.

0. 0.

Check the Maximum Stresses versus defined Allowables N./mm²: ----------------------------------------------------Max. Stress Intensity (Membrane + Bending) : Max. Compressive Stress : Max. Membrane Stress :

184.36 Allowable: 0.00 Allowable: 98.62 Allowable:

310.28 -197.02 165.48


27-14



&KDSWHU The Appendix Y Module

Introduction This module performs stress evaluation of Class 1, category 1, 2, or 3 flanges that form identical flange pairs. This module conforms to the latest version (A-2001) of the ASME Code Section VIII Division 1 Appendix Y.

Purpose, Scope, and Technical Basis The analysis of an Appendix Y flange is similar in many ways to the Appendix 2 evaluation. However, these flanges have metal-to-metal contact outside the bolt circle, unlike the types evaluated in Appendix 2. These flanges typically have a soft, self sealing o-ring gasket that sits in recess in one of the flange faces. The loads on the flanges are generated in a very similar manner to those in Appendix 2. The actual stress evaluation however is different. This program evaluates flanges with or without hubs. A category 1 flange is an integral flange. The integral type must have the hub information specified. A category 2 flange is a loose type with a hub where the hub strengthens the assembly. A category 3 flange is a loose type where no credit is taken for the strengthening effect of the hub. Based on the user input (especially flange type and hub information), the category is automatically determined.

The Appendix Y Module

28-1

Gasket and Gasket Factors


Gasket and Gasket Factors One critical value the program computes is the diameter of the load reaction. This value is termed G and is a function of where the gasket sits on the flange face. The value of G is typically the average of the gasket inner and outer diameters. For these types of flanges the gasket ID is usually equal the flange face ID and the gasket OD is usually equal to the flange face OD. Two other important factors m and Y. The value of m is the leak pressure ratio and Y is the gasket design seating stress. This Appendix takes these gaskets to be self sealing (see the definition of Hg in the Code). Thusly the m and Y factors should both be 0.0. If any other value is entered the user values will be echoed but the program will use values of 0.0 for both.

28-2



Sample Calculation

Sample Calculation Input Echo, App Y Flange Item

1,

Description: APPY

Description of Flange Geometry (Type)

Integral Weld Neck

Design Pressure

P

150.00

psig

100.00

F

FCOR

0.0000

in.


B

10.0000

in.


A

16.0000

in.

Flange Thickness

T

0.6250

in.

Thickness of Hub at Small End

G0

0.2500

in.

Thickness of Hub at Large End

G1

0.3750

in.

Length of Hub

HL

1.0000

in.

Design Temperature Corrosion Allowance

Flange Material

SA-240 316L

Flange Allowable Stress At Temperature

SFO

16300.00

psi

Flange Allowable Stress At Ambient

SFA

16300.00

psi

Bolt Material

SA-193 B7


SBO

18000.00

psi


SBA

18000.00

psi

C

14.2500

in.

DB

0.7500

in.


UNC Thread Series

Number of Bolts

12


GOD

12.1000

in.


GID

11.9000

in.

Gasket Factor, m,

M

0.0000


Y

0.00

psi

Material at Des. Temp

29538461

psi

Elastic Modulus of Flange Material at Des. Temp

28138460

psi

Elastic Modulus of Bolt

FLANGE ANALYSIS of Identical Flange Pairs Per Appendix Y

Corroded Flange ID,

BCOR = B+2.0*FCOR

10.000

in.

Corroded Large Hub,

G1COR = G1-FCOR

0.375

in.

Corroded Small Hub,

G0COR = G0-FCOR

0.250

in.

Code R Dimension,


1.750

in.

Code R Dimension,


1.750

in.


28-3

Sample Calculation



0.100

in.

Basic Gasket Width,

B0 = N / 2.0

N = (GOD-GID) / 2

0.050

in.


BE = B0

0.050

in.

12.000

in.

0.875

in.

Gasket Reaction Diameter, Radial Contact Dist.,

G = (GOD+GID) / 2.0

hcmax = (A - C) / 2

BASIC FLANGE AND BOLT LOADS: Hydrostatic End Load due to Pressure: H = 0.785 * G * G * PEQ H = 0.785 * 12.0000 * 12.0000 * 150.0000 H = 16956. lb. Contact Load on Gasket Surfaces: HP = 2.0 * BE * 3.14 * G * M * PE HP = 2.0 * 0.0500 * 3.14 * 12.0000 * 0.0000 * 150.00 HP = 0. lb. Hydrostatic End Load at Flange ID: HD = 0.785 * B² * PEQ HD = 0.785 * 10.0000² * 150.0000 HD = 11775. lb. Pressure Force on Flange Face: HT = H - HD HT = 16956 - 11775 HT = 5181. lb.

MOMENT ARM CALCULATIONS: Distance to Gasket Load Reaction: DHG = (C - G ) / 2.0 DHG = ( 14.2500 - 12.0000 ) / 2.0 DHG = 1.1250 in. Distance to Face Pressure Reaction: DHT = ( R + G1COR + DHG ) / 2.0 DHT = ( 1.7500 + 0.3750 + 1.1250 ) / 2.0 DHT = 1.6250 in. Distance to End Pressure Reaction: DHD = R + ( G1COR / 2.0 ) DHD = 1.7500 + ( 0.3750 / 2.0 ) DHD = 1.9375 in.

SUMMARY OF MOMENTS FOR INTERNAL PRESSURE:

28-4



Sample Calculation

LOADING

Force

Distance

Bolt Corr

Moment

End Pressure,

MD

11775.

1.9375

1.0000

1901. ft.lb.

Face Pressure,

MT

5181.

1.6250

1.0000

702. ft.lb.

Gasket Load,

MG

0.

1.1250

1.0000

0. ft.lb.

Gasket Seating, MA

41094.

1.1250

1.0000

3853. ft.lb.

Gasket Seating, MA

41094.

1.1250

1.0000

3853. ft.lb.

TOTAL MOMENT FOR OPERATION,

RMO

2603. ft.lb.

TOTAL MOMENT FOR GASKET SEATING, RMA

3853. ft.lb.

Effective Hub Length, H0 = SQRT(BCOR*G0COR)

1.581

Hub Ratio,

HRAT = HL / H0

0.632

Thickness Ratio,

GRAT = (G1COR/G0COR)

1.500

in.


0.831

Factor V per 2-7.3

0.289

Factor f per 2-7.6

1.000

Factors from Figure 2-7.1

K =

1.600

T =

1.668

U =

4.732

Y =

4.306

Z =

2.282

Stress Analysis of a Class 1 Assembly

Compute the Factor:

F’

= g0² * ( h0 + F * T ) / V = 0.2500 * ( 1.5811 + 0.8308 * 0.6250 ) / 0.2894 = 0.4535

Factor:

Js

= 1/B1 * ( 2*hd/ß + hc/a ) + pi*rb = 1/10.375(2*1.937/1.1867+0.8750/1.4578)+3.14159*0.009012 = 0.4009

Factor:

Jp

= 1/B1 * ( hd/ß + hc/a ) + pi*rb = 1/10.375(1.937/1.1867+0.8750/1.4578)+3.14159*0.009012 = 0.2435

Flange Moment due to Flange-Hub Interaction:


Ms

28-5

Sample Calculation


= -( Jp * F’ * Mp )/( t^3 + Js * F’ ) = -( 0.2435 * 0.4535 * 31233.18 )/( 0.6250 + 0.4009 * 0.4535 ) = -674.8762 ft.lb.

Slope of the Flange at the ID times E (Elastic Modulus): Ethetab = 5.46/(pi*t^3) * ( Js*Ms + Jp*Mp ) = 5.46/(3.14159 * 0.6250^3) * ( 0.4009* -8098.51 + 0.2435* 31233.18 ) = 31034. psi

Contact Force between Flanges at hc:

Hc

= ( Mp + Ms ) / hc = ( 31233.18 + -8098.51 ) / 0.8750 ) = 26440. lb.


Wm1

= H + Hg + Hc = 16956.00 + 0.00 + 26439.60 = 43396. lb.

Operating Bolt Stress:

Sigmab

= Wm1 / Ab = 43395.60 / 3.6240 = 11975. psi

Design Prestress in the Bolts:

Si

= Sigmab - 1.159 * hc² * (Mp+Ms)/( a * t^3 * l * re * B1 ) = 11974-1.159*0.875²*(23134)/(1.458*0.6250^3*2.000*2.000 = 9195. psi

Radial Flange Stress at the Bolt Circle:

Sr

= 6 * (Mp + Ms)/( t² * ( pi*C - n*D ) ) = 6 * ( 31233 + -8098)/( 0.6250²( pi * 14.2500 - 12 * 0.8750 ) ) = 10370. psi

Radial Flange Stress at the Inside Diameter:

SRid

= -(( 2*F*t)/(h0+F*t)+6))*Ms/(pi*B1*t²) = -((2*0.831*0.625)/(1.581+0.831*0.625)+6))*-8098/(pi*-8098.514 = -3501.9504 psi

Tangential Flange Stress at the Inside Diameter:

STid

= (t*Ethetab/B1) + ((2*F*t*Z)/(h0+F*t) - 1.8) * Ms/(pi*B1*t²) = ( 0.6250* 31033.87/ 10.3750) + ((2* 0.8308* 0.6250* 2.2821)/( 1.5811+ 0.8308* 0.6250) - 1.8) *

28-6



Sample Calculation

-8098.51/(pi* 10.375* 0.6250²) = 2297. psi

Longitudinal Hub Stress:

Sh

= ( h0 * Ethetab * f )/((0.91*(g1/g0)²*B1*V) = (1.5811*31033.9*0.831)/((0.91*(0.3750/0.2500)²*10.3750*10.3750 = 6630. psi

Summary of Flange Stresses : Actual Radial Flange Stress at the Bolt Circle

Allowable

10369.78

16300.00 psi

2296.76

16300.00 psi

-3501.95

16300.00 psi

Longitudinal Hub Stress

6630.05

24450.00 psi

Average of Sh and Sr

1564.05

16300.00 psi

Average of Sh and St

4463.40

16300.00 psi

11974.50

18000.00 psi

Tangential Flange Stress at the ID Radial Flange Stress at the ID

Bolt Stress

Results for Required Thickness and M.A.W.P. Minimum Required Flange Thickness

0.4509

in.

Estimated M.A.W.P.

235.78

psig


28-7



Discussion of Results Based on the given input the program computes the MAWP for the given geometry. With the given loading conditions the required thickness is also computed. The program computes flange stresses and compares those stresses with the appropriate allowables as described in paragraph Y-7 of the ASME Code.

28-8



&KDSWHU Miscellaneous Processors

File Manager

The file manager window allows the users to browse drives and directories for a file that will be created, opened, saved or deleted. The following options are available: •

Filename - This field contains the name of the file you wish to create, open, save or delete. Enter the name of the desired file then press [Enter] or select the OK button. The filename is composed of two portions, the (job)name and the extension (such as .PVI, .FIL, etc. ). The user can enter the full filename (name+extension) or just the name; in which case, the program will add the appropriate extension. The first portion of the filename must be eight characters or less, and only consists of letters, numbers or ‘_’. The program will check the filename you entered (or selected) to make sure it is valid.

•

Directories - Contains the directories that may be browsed. A directory can be selected from the list by pressing on the list’s up or down arrow, moving the cursor to the desired directory then pressing [Enter].

•

Drives - Contains the active drives on the system. The drives in this field can be selected by pressing on the list’s up or down arrow, moving cursor to the desired drive,

Miscellaneous Processors

29-1

File Manager


then pressing [Enter]. If the drive is available the directory and file fields will be updated. Otherwise an error message is presented. The OK button causes the information in the filename field to be processed by the program. If the process is successful the file manager window is then removed from the screen. In most cases, a message window will appear after pressing this button. The user should answer the questions presented by the message window so that the process can be fully carried out. The only circumstances where the message window does not appear is when there is no previously opened file. In the DELETE option, after the process is finished, the file manager window is not removed from the screen, instead the file list is updated and the program is waiting for another DELETE event. If the user does not wish to delete any more files, press the CANCEL button to close the file manage window. Selecting the CANCEL button causes the file manage window to be removed without any further processing. The HELP button displays information about this window.

29-2



Heading Edit

Heading Edit

Heading Edit mode allows the user to input and edit the heading and the title page for the current job.


29-3

Material Definition


Material Definition Element materials may be selected for the Material button on the Define screen. When clicking on the Material button, the following screen is presented:

By clicking on the material name, the material parameters are displayed:

By clicking on the OK button, the material name and the appropriate material parameters are loaded in the element. These parameters may be reviewed and modified through the Material Edit Window by pressing the Enter key when the cursor is in the Material field. Material Edit Window lets the user display and modify the material properties of the current element or detail. Note that if the material is newly selected, the data displayed here

29-4



Material Definition

are directly from the program’s material database, otherwise the data are from the data structure of the current element or detail. If a newly selected material can not be found in the program’s material database, the program will assume that is a “User-defined material”, in this case the user must define all material properties in this window.

The following buttons are available in this window: •

OK - Allows the user to save the data to the memory then close the window.

•

Cancel - Allows the user to close the window without saving the data.

•

Help - Displays information about this window.


29-5

Material Name


Material Name Enter the name of the material for this element. This program contains a database which includes most of materials in ASME Code, Section II, Part D, Table 1A, 1B, and 3.

Allowable Stress at Ambient Temperature Enter the allowable stress for the element material at ambient temperature. ( Ambient temperature for most vessel will be 70 F or 100 F or 30 C). You can find this value in the ASME Code, Section II, Part D, Table 1A, 1b, and 3. Under normal circumstances, the program will look up this allowable stress for you. If you enter a valid material name in the material input field, the program will look into its database and determine the allowable stress for the material at ambient temperature, and enter it into this cell. The program will also determine this stress when you select a material name from the material selection window.

Allowable Stress at Operating Temperature Enter the allowable stress for the element material at operating temperature. ( Operating temperature for most vessels is defined to be the same as the design metal temperature for internal pressure). You can find this value in the ASME Code, Section II, Part D, Table 1A, 1b, and 3. Under normal circumstances, the program will look up this allowable stress for you. If you enter a valid material name in the material input field, the program will look into its database and determine the allowable stress for the material at design temperature, and enter it into this cell. The program will also determine this stress when you select a material name from the material selection window.

Allowable Stress at Hydrotest Temperature Enter the allowable stress for the element material at Hydrotest temperature. ( Operating temperature for most vessel will be 40 F or 70 F or 10 C). You can calculate this value in the ASME Code, Section II, Part D, Table 1A, 1b, and 3. Most times the allowed hydrotest stress will just be 1.5 times the allowable stress for the vessel at ambient temperature. Under some circumstances you may choose to use an allowable hydrotest stress of 0.9 times the yield stress of the material at ambient temperature. This is especially helpful in the case of tall vertical process tower where the hydrotest pressure is increased by height of the water used for testing. Use of the higher hydrotest allowable stress may prevent the hydrotest case from controlling the thickness of the vessel. Under normal circumstances, the program will calculate this allowable stress for you. If you enter a valid material name in the material input field, the program will look into its database and determine the allowable stress for the material at ambient temperature, multiply it by 1.5, and enter it into this cell. The program will also calculate this stress when you select a material name from the material selection window.

Nominal Density of this Material Enter the nominal density of the material. Note that the program will use this value to calculate component weights for this analysis. The typical density for carbon steel is 0.2830 lbs/in3.

29-6



Material Name

P Number Thickness Enter the thickness for this P number. Table UCS-57 of the ASME Code, Section VIII, Division 1 lists the maximum thickness above which full radiography is required for welded seams. This thickness is base on the P number for the material listed in the allowable stress tables of the Code. This value is used only for error checking.

Yield Stress, Operating Enter the yield stress for the material at the operating temperature. This value is found in the ASME Code, Section II, Part D. If the yield stress at operating temperature is significantly different than the yield stress at ambient temperature, and if some of the items in the model make use of yield stress (i.e. vessel legs), then you should carefully check and enter this value.

UCS-66 Chart Number Enter values 1 through 4 to specify the UCS-66 Carbon Steel Material Curves A through D, respectively. Enter 0 for materials which are not carbon steel. Note that the material database returns the non-normalized curve number; adjust the curve number if you are using normalized material produced to fine grain practice.


29-7


External Pressure Chart Name The program uses the chart name to calculate the B value for all external pressure and buckling calculations. It is important that this name be entered correctly. Under normal circumstances, the program will look up this chart name for you. If you enter a valid mate-

29-8



rial name in the material input field, the program will look into its database and determine the external pressure chart name for this material, and enter it into this cell. The program will also determine this chart name when you select a material name from the material selection window. The following are the acceptable external pressure chart names:

Carbon Steel Materials CS-1 CS-2 CS-3 CS-4 CS-5 CS-6

UCS-28.1, Carbon and Low Alloy, Sy<30000 UCS-28.2, Carbon and Low Alloy, Sy>30000 UCS-28.3, Carbon and Low Alloy, Sy>38000 UCS-28.4, SA-537 UCS-28.5, SA-508, SA-533, SA-541 UCS-28.6, SA-562 or SA-620

Heat Treated Materials HT-1 HT-2

UHT-28.1, SA-517 and SA-592 A, E, and F UHT-28.2, SA-508 Cl. 4a, SA-543,B,C

Stainless Steel (High Alloy) Materials HA-1 HA-2 HA-3 HA-4 HA-5

UHA-28.1, Type 304 UHA-28.2, Type 316, 321, 347, 309, 310, 430B UHA-28.3, Type 304L UHA-28.4, Type 316L, 317L UHA-28.5, Alloy S31500

Non Ferrous Materials NFA-1 NFA-2 NFA-3 NFA-4 NFA-5 NFA-6 NFA-7 NFA-8 NFA-9 NFA-10 NFA-11 NFA-12 NFA-13 NFA-14 NFC-1 NFC-2 NFC-3 NFC-4 NFC-5 NFC-6 NFN-1 NFN-2


UNF-28.2, AL3003, O and H112 UNF-28.3, AL3003, H14 UNF-28.4, AL3004, O and H112 UNF-28.5, AL3004, H34 UNF-28.13, AL5154, O and H112 UNF-28.14, C61400 (Aluminum Bronze) UNF-28.17, AL1060, O UNF-28.18, AL5052, O and H112 UNF-28.19, AL5086, O and H112 UNF-28.20, AL5456, O UNF-28.23, AL5083, O and H112 UNF-28.30, AL6061, T6, T651, T6510 and T6511 UNF-28.31, AL6061, T4, T451, T4510 and T4511 UNF-28.32, AL5454, O and H112 UNF-28.9, Annealed Copper UNF-28.10, Copper-Silicon A and C UNF-28.11, Annealed 90-10 Copper Nickel UNF-28.12, Annealed 70-30 Copper Nickel UNF-28.43, Welded Copper Iron Alloy Tube UNF-28.48, SB-75 and SB-111 Copper Tube UNF-28.1, Low Carbon Nickel UNF-28.6, Ni

29-9

TEMA Number


NFN-3 NFN-4 NFN-5 NFN-6 NFN-7 NFN-8 NFN-9 NFN-10 NFN-11 NFN-12 NFN-13 NFN-14 NFN-15 NFN-16 NFN-17 NFN-18 NFN-19 NFN-20 NFT-1 NFT-2 NFT-3 NFZ-1 NFZ-2

UNF-28.7, Ni Cu Alloy UNF-28.8, Annealed Ni Cr Fe UNF-28.15, Ni Mo Alloy B UNF-28.24, Ni Mo Cr Fe UNF-28.25, Ni Mo Cr Fe Cu UNF-28.27, Ni Fe Cr Alloy 800 UNF-28.29, Ni Fe Cr Alloy 800H UNF-28.33, Ni Moly Chrome Alloy N10276 UNF-28.34, Ni Cr Fe Mo Cu Alloys G and G-2 UNF-28.36, Cr Ni Fe Mo Cu Co, SB-462, 463, etc. UNF-28.37, Ni Fe Cr Si Alloy 330 UNF-28.38, Ni Cr Mo Grade C-4 UNF-28.39, Ni Mo Alloy X UNF-28.40, Ni Mo Alloy B-2 UNF-28.44, Ni Cr Mo Co N06625 (Alloy 625) UNF-28.45, Ni Mo Cr Fe Cu (Grade G-3) UNF-28.46, Ni Mo Cr Fe Cu (Grade G-3, >3/4) UNF-28.47, Work Hardened Nickel UNF-28.22, Unalloyed Titanium, Grade 1 UNF-28.28, Unalloyed Titanium, Grade 2 UNF-28.42, Titanium, Grade 1 UNF-28.35, Zirconium, Alloy 702 UNF-28.41, Zirconium, Alloy 705

The user may add material data to the standard material database using the Edit/Add Materials option from Tools on the Main Menu.

TEMA Number The TEMA number is used to determine the modulus of elasticity for materials at design temperature. These values range from 1 to 52. They can be found in the TEMA tubesheet chapter.

29-10



Keyboard Commands

Keyboard Commands The following movements are defined for the keyboard within the program: Begin line

Begin list

Delete character

Delete prev. char

Delete window

End line

End list

Exit

Help

Hot key

Insert toggle

Left word

Mark

Maximize

Menu control

Minimize

Move window

Next cell

Next Character

Next field

Next window

Page down

Page up

Previous cell

Previous character

Previous field

Refresh

Right word

Select

Size window

System button


29-11

Mouse Operation


Mouse Operation The following movements are defined for the mouse within the program: In window objects: Choose Select

In vessel graphics: Select element Select detail

29-12



&KDSWHU Vessel Example Problems

Introduction The purpose of this chapter is to provide a listing for a typical vertical and horizontal vessel. The actual modeling instructions have been previously outlined in the chapter 3. At this point it is assumed that you can use the input program to create a vertical vessel or horizontal tank. In addition to the following examples, this program comes with many examples that reside in the EXAMPLES subdirectory underneath the main program directory. If you wish to access these examples, you can use the File Open command sequence while in the vessel building part of PVElite. Once you get into the file open screen, you can choose the directory option to switch directories. Once in the EXAMPLES subdirectory, you can open any of the existing examples and analyze them.

Vessel Example The Vertical and Horizontal Vessel problems can now be accessed at www.COADE.com.

Vessel Example Problems

30-1

Vessel Example

30-2


Vessel Example Problems


Index Numerics 1.60D.5 6-44 1.60D10 6-45 1.60D2 6-44 1.60D5 6-44 1.60D7 6-44 3D Viewer 3-32

A Above Ground Height 6-22, 15-7 Absolute 6-46 Abutting Nozzle Insertion 5-16, 11-7 Acc Based Factor Fv 6-46 Acc.Based Factor Fa 6-46 Acceleration Zone 6-34 Acceptance of terms of agreement by the user 1-2 AD-540.2 sketch b 3-25 Adding Details 3-42 Additional Area 15-5, 18-6 Additional Data for Reinforcing Pad 5-17 Additional Horizontal Force on Vessel 18-3 AISC Member Designation 18-9 Allowable Calculations, Highest Percentage of 26-18 Allowable Stress, Ambient 19-2 Allowable Stress, Ambient Tempature 14-4 Allowable Stress, Ambient Temperature 16-5, 23-17 Allowable Stress, Design Temperature 14-4, 16-5, 23-17 Allowable Stress, Operating 19-2 Amplification Factor ac 6-30 Analysis Type 12-5 Analysis, Performing an 9-20 Analyze Baseplate 18-3 Analyze Menu 3-22, 9-6 Analyze Shellside + Differential Expansion 22-7 Analyze Shellside + Tubeside + Differential Expansion 22-7 Analyze Shellside + Tubeside Pressure 22-7 Analyze Shellside Pressure 22-7 Analyze Tubeside + Differential Expansion 22-7 Analyze Tubeside Pressure 22-7 Angle Between Branch and Header 19-3 Angle Between Nozzle and Shell 5-13 Angle Between Nozzle and Shell (Usually 90) entered in description field 5-13 Angle Sections Rolled the Hard Way 6-7 ANSI Flange MAWP 7-4 Apex Angle 10-10, 11-11 Appendix Y Flanges 1-7 Appendix Y Module 28-1

Applications Available 1-4 Are the Legs Pipe Legs 18-9 Area 2 Setting 5-14 Area Calculations for Small Nozzles 9-10 AREA1 or AREA2 Equal to 0 11-5 Area1 Setting 5-14 ASCE 6-44 ASCE 7-88 Seismic Data 6-28 ASCE 7-93 Importance Factor 6-15 ASCE 7-93 Seismic Data 6-30 ASCE 7-95 Code 15-6, 18-7 ASCE 95 Wind Data 6-21 ASCE Roughness Factor 6-16 ASCE Wind Data 6-15 ASCE-95 Seismic Data 6-37 ASME Code Weld Type 5-17 ASME Section VIII Division 2 - Elastic Analysis of Nozzle 17-23 ASME Tube Joint Reliability Factor 16-10, 23-13 ASME Tubesheets 1-5 ASME Tubesheets Module 23-1 ASME UG-99(b) 6-2 ASME UG-99(b) footnote 32 6-3 ASME UG-99(b) footnote 34 6-3 ASME UG-99(c) 6-2 Aspect Ratio (D/2H) for Elliptical Heads 15-8 Aspect Ratio for Elliptical Heads 10-9, 11-10 Assigning Details to Elements 5-3 Attached B16.5 Flange Rating 19-3 Attached Flange Rating 11-5 Attachment Description 17-2 Attachment Factor for Flat Head 10-10 Attachment Factor for Welded Flat Heads 11-11 Attachment Number for this Analysis 17-2 Axial Force 12-12, 18-14, 18-29 Axial Force for External Pressure Case 13-7 Axial Force for Internal Pressure Case 13-7 Axial Forces on the Cone 13-4 Axial Length of Kettle Cone (LC) 16-12 Axial Pressure Thrust 27-5 Axial Thickness of Reinforcing Ring 13-8 Axial Thrust Load "P" 27-3

B B16.5 Flange 5-13, 11-11, 19-5 B16.5 Flange, Grade for Attached 5-13, 11-11, 19-5 Backing Ring 14-7 Backing Ring Actual Thickness 14-8 Backing Ring Inside Diameter 14-8

i


Bail/Sling Width 18-28 Bar Thickness 6-7 Base Elevation 6-15, 6-17, 6-19, 6-21, 6-24 Base Plate Length 15-5 Base Plate Thickness 15-5 Base Plate Width 15-5 Base Ring Design 20-4 Base Ring Thicknesses, Analysis of 20-5 Base Rings 1-5 Baseplate Input 18-24 Baseplate Length 5-27 Baseplate Length B 18-24 Baseplate Material 18-24 Baseplate Results 18-27 Baseplate Thickness 5-27 Baseplate Thickness BTHK 18-24 Baseplate Width 5-27 Baseplate Width D 18-24 Basering Description 20-6 Basering Diameter, Outside 20-7 Basering Geometry, Analysis of 20-4 Basering Inside Diameter 20-7 Basering Module 20-1 Basering Number 20-6 Basering Under Compression, Thickness of 20-1 Basering Under Tension, Thickness of 20-3 Basering, Analyze or Design 20-6 Basering, Thickness of 20-6 Beam Section, General 26-16 Bellows Inside Diameter 21-3 Bellows Minimum Thickness Before Forming 21-3 Bending Moment 12-12 Blind Flange Thickness for Reinforcement 3-25 Blind Flanges and Channel Covers 12-14 Bolt Allowable Stress, Ambient Temp 23-15 Bolt Allowable Stress, Design Temp 23-15 Bolt Area Calculation 20-4 Bolt Circle, Diameter at 20-8 Bolt Circle, Diameter of 12-8, 14-5, 16-14, 23-14 Bolt Correction Factor 3-26 Bolt Corrosion Allowance 18-24 Bolt Diameter 12-8, 14-5, 16-14, 20-7 Bolt Holes Center, Perimeter of 12-12 Bolt Material 18-24 Bolt Material Specification 23-15 Bolt Root Area 14-8, 18-25 Bolt Root Area (Used if > 0) 16-14 Bolt Size, Selecting 20-4 Bolt Table (TEMA, UNC, USER) 20-8 Bolts and Gussets 20-10 Bolts, Number of 12-8, 14-5, 16-14, 20-8, 23-15 Bottom Lug Support Plate, Length of 5-19

ii

Bottom Plate, Thickness of 5-20 Bottom Support Lug Plate 18-12 Bottom Support Lug Plate, Thickness of 18-12 Bottom Support Plate 5-19 Branch Dimension Basis 19-2 Branch Penetration of a Header Weld 19-3 Branch/Header Thickness 19-2 Branch/Header, Thickness 19-2 British Standard BS5500 7-4

C C Factor for End Closure Plate/Vessel Head 26-12 Calculated Value of M for Torispherical Heads 9-10 Calculation Techniques 20-1 Calculations for Flanged Portion of Head 14-9 Calculations for Tubesheets Extended as Flanges 16-16 Calculations, Allowable 26-18 Carbon Steel Materials 29-9 Category Value 6-38 Center to Center Distance Between Poles 26-14 Center Web Height 5-27, 15-5 Centerline Dimension 5-26 Centerline Offset 4-35 Central Opening Number, Large 25-3 Centroid 13-8 Centroid Distance from Outside of Vessel 26-16 C-Factor 26-13 Channel Allowable Stress, Ambient Temperature 23-11 Channel Allowable Stress, Design Temperature 23-10 Channel Corrosion Allowance 16-6, 23-4 Channel Cover Deflection 12-12 Channel Design Pressure 16-6, 23-4 Channel Inside Diameter 16-6, 23-4 Channel Material Specification 23-10 Channel Metal Design Temperature 16-6 Channel Metal Temperature at Tubesheet. 23-13 Channel Temperature for Internal Pressure 23-10 Channel Wall Thickness 16-6, 23-4 Circumferential Moment 17-12 Circumferential Moment MC 27-3 Circumferential Shear Load 17-12 COADE Technical Support Phone Numbers 1-9 Code Case 2168 for Nozzle Design 6-13 Code Case 2260/2261 3-26 Coefficient Cd 6-47 Cold Stress Intensity Allowable (Smc) 17-13 Combination Method 6-45 Compare Maximum Stress Intensity to 17-13 Component Analysis 7-9, 8-4 Component Analysis Main Menu 9-2 Component Analysis Module 9-1 Component Analysis Tutorial 9-1


Componsite Stiffener Height 5-26 Compressed Air, Water, or Steam Service 11-8 Compressive Stress of Concrete 20-8 Computation Control Tab 9-9 Cone Actual Thickness 13-3 Cone Axial Length 13-4 Cone Circumferential Joint Efficiency 13-6 Cone Corrosion Allowance 13-3 Cone Description 13-2 Cone Diameter at Large End 13-4 Cone Diameter at Small End 13-4 Cone Diameter Basis 13-4 Cone Half Apex Angle 13-4 Cone Joint Efficiency 13-3 Cone Number 13-2 ConeCylinderRingKnuckle Material Name 13-3 Configuration 9-9 Conical Sections 1-4 Conical Sections Module 13-1 Construction Type 6-3 Contract Width or Height (Per. Lug) of Lifting Lug 1814 Convolution Depth 21-3 Convolution Pitch 21-3 Corroded Expansion Joint Spring Rate 16-10, 23-11 Corroded Hydrotest 6-5 Corrosion Allowance 10-7, 12-6, 15-2, 19-3, 25-4, 26-12 Corrosion Allowance of Jacket 24-5 Corrosion Allowance of the Vessel 17-3 Corrosion Allowance, External 20-8 Corrosion in Flange Thickness Calculations 12-6 Crest Distance 6-22, 15-7, 18-7 Critical Damping Ratio 6-19 Cross-Sectional Area 5-8 Cross-Sectional Area of Reinforcing Ring 10-11 Cross-Sectional Area of Reinforcing Section 13-8, 26-16 Cross-Sectional Area of Stiffening Ring 15-8 Crown Radius 11-10, 14-4 Crown Radius for Torispherical Heads 10-9, 15-8 Cycle Life 22-9 Cycle Life Evaluation 21-3 Cylinder Actual Thickness, Large 13-5 Cylinder Actual Thickness, Small 13-4 Cylinder Axial Length, Large 13-5 Cylinder Axial Strength, Small 13-5 Cylinder Corrosion Allowance, Large 13-5 Cylinder Corrosion Allowance, Small 13-5 Cylinder Joint Efficiency, Large 13-5 Cylinder Joint Efficiency, Small 13-4 Cylinder Volumn Calculations 10-9 Cylinder, Outer 22-5 Cylindrical Element Corrosion 22-7

Cylindrical Element Length 22-7 Cylindrical Element Thickness 22-7

D Damping Factor 6-22, 6-36 Damping Ratio 15-7, 18-7 Datum Line Distance 6-2 Dead Weight of Vessel 20-9 Default units file 9-12 Delta 26-13 Density of Material 29-6 Design Cycle Life, Number of Cycles 21-2 Design Data 6-2 Design External Pressure 10-5, 11-3, 26-13 Design Internal Pressure 6-2, 10-5, 11-3, 21-2, 25-3, 269 Design Internal Temperature 6-2 Design Length for Cylinder Volumn Calculations 10-9 Design Length of Section 10-9 Design Modification 6-9 Design Pressure 6-12, 12-5, 17-11, 18-2, 19-1, 27-2 Design Pressure + Static Head 6-12 Design Pressure in Jacket 24-5 Design Pressure, External 13-2 Design Temperature 11-3, 12-5, 14-3, 19-1, 21-2, 25-3, 27-2 Design Temperature for External Pressure 10-5 Design Temperature for Integral Part 23-17 Design Temperature for Internal Pressure 10-5, 24-3, 269 Design Temperature for Jacket Pressure 24-5 Design Temperature for Shell and Expansion Joint 22-3 Design Temperature of Attachment 18-2 Design Temperature of Tubes 23-7 Design Temperature, External 13-2 Design Wind Speed 6-15, 6-17, 6-19, 6-21 Detail Definition Buttons 5-4 Detail ID 5-6 Details, Definition of 5-6 Diagnostics Menu 3-29, 9-16 Diameter and Thickness, Actual 5-15 Diameter at Leg Centerline 5-29 Diameter Basis 10-7 Diameter Basis for Nozzle 27-2 Diameter Basis for the Nozzle 17-7 Diameter Basis for the Vessel 17-3 Diameter Basis for Vessel

Vessel Diameter 27-1 Diameter for Non-Circular Welded Flat Heads, Large 10-10 Diameter Limit 11-6 Diameter Nozzle Calculations, Large 11-14

iii


Diameter of Nozzle, Actual 5-14, 11-6 Diamter, Minimum 5-15 Differential Design Pressure 16-7 Differential Expansion 22-6 Differential Expansion Pressure 16-16, 22-6 Differential Expansion Pressure (from Tubesheet) Corroded 22-6 Disclaimer - CAESAR II 1-4 Discussion of Results 23-19 Distance between Gussets 5-20, 18-12 Distance between Tube Centers 23-7 Distance from Bolts to Gussets 20-10 Distance from Flange Centroid to Head Centerline 14-7 Distance from Ring Centroid to Shell Surface 10-11 Distance from Saddle to Vessel Tangent 15-3 Distance from the Edge of the Leg to the Bolt Hole, "z" 18-24 Distance from Vessel Centerline to Saddle Base 15-6, 15-7 Distance from Vessel OD to Lug Midpoint 5-19 Distance from Vessel OD to Support Contact Point 1811 Distance to Centroid of Reinforcing Section 13-8 Distance to Crest 15-7, 18-7 Distance to Ring Centroid 5-8 Distance to Ring Centroid from Shell Surface 15-9 Distance to Site 6-22, 15-7, 18-7 DXF File Generation Option 3-53

E Earthquake Load Calculation 7-6 EarthQuake Parameters Fa and Fv 6-41 Edit Menu 9-5 EigenSolver 3-27 El Centro 6-44 Elastic Modules for Plates 20-10 Elastic Modulus at Ambient Temperature 21-3, 21-4, 215 Elastic Modulus at Design Temperature 21-3 Element’s From Node 4-2 Element’s To Node 4-3 End Reinforcing, Large 13-5 Enter the Dimension G for the Backing Flange 23-8 Enter the Outside Diameter of the Tubesheet 23-8 Enter the Shell/Channel Side Vacuum Pressures 16-13 Enter the Shell/Channelside Vacuum Pressures 23-14 Enter the Tube End Condition k, Corresponding to Span SL 16-12 Enter the Tube End Condition, K Corresponding to Span SL 23-12 Enter the Unsupported Tube Span, SL for Max (k*SL) 16-11

iv

Enter the Unsupported Tube Sran, SL for MAX (k*SL) 23-12 Entire agreement 1-3 Equipment Class 6-25 Error Checking 3-9, 7-3 Escarpment 15-7, 18-7 ESL Installation on a Network 2-7 ESL Menu 3-38, 9-17 Example Problem 10-16, 11-16, 12-19, 13-11, 13-14, 1318, 14-11, 14-14, 15-14, 16-19, 19-10, 20-13, 21-6, 2211, 23-19, 24-8, 25-5, 26-20 Examples 17-29, 18-17 Expanded Portion of Tube, Length of 23-7 Expansion Joint Allowable Stress at Ambient Temperature 22-4 Expansion Joint Bellows Material 21-2 Expansion Joint Corrosion Allowance 22-3 Expansion Joint Description 22-3 Expansion Joint Flange Wall Thickness 22-3 Expansion Joint Inside Diameter 16-11, 22-3 Expansion Joint Inside Knuckle Offset (Straight Flange) 22-5 Expansion Joint Inside Knuckle Radius 22-5 Expansion Joint Number 22-3 Expansion Joint Opening Per Convolution 21-2 Expansion Joint Outside Diameter 22-3 Expansion Joint Outside Knuckle Offset 22-5 Expansion Joint Outside Knuckle Radius 22-5 Expansion Joint Projection from Shell OD 23-11 Exposure Constant 6-15, 6-17, 6-19, 6-21 Extended Portion of Tubesheet, Thickness of 16-14 External Loads, Specifying 12-10 External Pressure 10-5, 11-3, 26-13 External Pressure calculations 7-3 External Software Lock 2-1 Extruded Outlet Height 19-3 Extruded Outlet Inside Diameter 19-4 Extruded Outlet, Thickness of 19-3

F Failure Path Calculations 11-15 Fastener Allowable Stress at Ambient Temperature 21-4 Fastener Allowable Stress at Operating Temperature 214 Fastener Bolt Length 21-4 Fastener Bolt Present 21-3 Fastener Cross-Sectional Area 21-4 Fastener Material Specification 21-4 File Manager 29-1 File Menu 3-17, 9-2 Fillet or Groove Weld Leg Length 16-10 Fillet Radius Between Vessel & Nozzle (r) 17-16


Fillet Weld Between Flange and Shell/Channel 16-14 Fillet Weld Leg Connecting Ring to Shell 10-10 Fillet Weld Size 24-6 Final Basering Geometry, Selection of 20-5 Fireproofing with Insulation 5-35 Flange Centroid 14-7 Flange Depth 14-8 Flange Design 12-17 Flange Designation 12-4 Flange Diameter, Outside 14-5, 16-13, 23-14 Flange Distance to Top 6-3 Flange Face Facing Sketch 12-9, 14-6, 16-15, 23-16 Flange Face Inner Diameter 12-7, 14-6, 16-15, 23-16 Flange Face Outer Diameter 12-6, 14-6, 16-14, 23-15 Flange Face to Attached Head 14-8 Flange ID 12-6 Flange Inside Diameter 14-5 Flange Module 12-1 Flange Number 12-4 Flange OD 12-6 Flange Rigidity Calculations 12-17 Flange Stresses, Allowable 12-15 Flange Thickness 12-6 Flange Type 12-4 Flange, Slotted 14-7 Flange, Thickness of 14-5 Flange/Bolt Material Specification 12-6 Flanged Portion of Head 14-9 Flanges 1-4, 1-6 Flanges with Different Bending Moments 12-14 Flanges, Loose-Type 12-5 Flat Face Flanges with Full Face Gaskets 12-5 Flat Head Outside Diameter 25-3 Flat Head Thickness 25-3 Floating Head Description 14-3 Floating Head Identification Number 14-3 Floating Head Module 14-1 Floating Head Type (b, c, d) 14-3 Floating Heads 1-5 Flohead Calculation 9-10 Force Coefficient 15-5, 18-6 Force Factor 6-37 Force in X, Y, or Z Direction 5-23 Force Modification Factor 6-33 Forces and Moments 5-23 From Node 5-6 Full Face Gasket 14-5 Full Run 1-10

G Gasket and Gasket Factors 28-2 Gasket Inner Diameter 12-7, 14-6, 16-15, 23-16

Gasket Outer Diameter 12-7, 14-6, 16-15, 23-16 Gasket Thickness 12-9, 14-6, 16-15, 23-16 Generating Output 8-1 Geometric Constants, Pressure and Thickness Calculations 16-16 Global Forces/Moments (SUS, EXP, OCC) 17-15 Groove in Tubesheet, Depth of 16-8 Groove Weld Between Nozzle and Vessel 5-16, 11-12 Groove Weld Between Pad and Nozzle Neck 11-12 Groove Weld between Pad and Nozzle Neck 5-17 Gusset Plate Height 18-12 Gusset Plate, Mean Width 18-12 Gusset Plates, Thickness of 18-12, 20-10 Gussets 5-20, 18-12, 20-8 Gussets and Bolts 20-10 Gussets Height 5-20, 20-10 Gussets per Bolt, Number of 20-10 Gussets, Mean Width 5-20 Gussets, Thickness of 5-20 Gust Response Factor 6-25

H Half Apex Angle for Conical Sections 10-10, 11-11 Half-Pipe Jacket 1-6, 24-4 Half-Pipe Jacket Thickness Calculations 24-6 Half-Pipe Jacket, Thickness of 24-4 Half-Pipe Module 24-1 Half-Pipe Section Description 24-3 Head Joint Efficiency 15-3 Head Thickness 15-3 Head Type 15-3 Head, Thickness of 14-4 Header Dimension Basis 19-3 Heading Edit 29-3 Heat-Treated Materials 29-9 Height above Ground 6-22 Height above Ground (z) 15-7 Height of Center Web 5-27, 15-5 Height of Composite Stiffener 5-26 Height of Extruded Outlet, HX 19-3 Height of Gusset Plate 18-12 Height of Gussets 5-20, 20-10 Height of Hill (H) 6-22 Height of Hill or Escarpment (H) 15-7, 18-7 Height of Liquid Column Hydrotest 10-9 Height of Liquid Column Operating 10-9 Height of Liquid Column, Operating 11-10 Height of Liquid on Tray 5-28 Height of Lug from Center of Hole to Bottom 18-14 Height of Packed Section 5-31 Height of Stiffener from Shell Surface 15-9 Height of Vessel above Grade 15-6

v


Height/Length of Insulation 5-35 Height/Length of Lining 5-36 Height/Length of Liquid 5-33 Help Menu 3-39, 9-19 Higher Long Stresses 6-4 Hill Height 6-22, 15-7, 18-7 Hill, Types of 15-6 Hills, Types of 6-22, 18-7 Hole in Lifting Lug, Diameter of 18-14 Hole, Depth of 26-15 Hole, Diameter of 26-15 Hoops license grant 1-6 Horizontal Force Factor 6-29, 6-31 Horizontal Force Normal to the Vessel 18-13 Horizontal Vessel Module 15-1 Horizontal Vessels 1-4, 1-6 Hot Stress Intensity Allowable (Smh) 17-14 Hub Length 12-7 Hub Thickness, Large End 12-7 Hub Thickness, Small End 12-7 Hydro. Allowable Unmodified (Y/N) 6-4 Hydrostatic Head Component 10-5, 11-4 Hydrotest Calculations 7-3 Hydrotest Position 6-3 Hydrotest Type 6-2 Hydrotest, Seismic 6-29, 6-30, 6-31, 6-34, 6-36, 6-37, 638 Hydrotest, Wind 6-15, 6-17, 6-19, 6-21, 6-24, 6-26

I IBC 6-44 Impact Factor 6-7 Importance 6-45 Importance Factor 6-22, 6-28, 6-31, 6-33, 6-36, 6-37, 641, 6-45, 15-6, 18-6, 18-29 Include Missing Mass Components 6-47 India’s Earthquake Standard IS-1893 RSM and SCM 636 Individual Heads 1-4 Individual Shells 1-4 Input 15-1, 17-2, 18-2, 19-1, 20-6 Input Data 10-5, 11-3, 12-4, 14-3, 16-5, 21-2, 22-3, 234, 24-3, 25-3, 26-9, 27-1 Input Echo 7-3 Input Expansion (EXP) Loadings 17-5 Input Loads in Global Coordinates and Allowable Stresses 17-5 Input Loads in WRC107 Convention 17-5 Input Menu 3-20 Input Occasional (OCC) Loadings 17-6 Input Processor 3-3 Input Processors 3-6

vi

Input Sustained (SUS) Loads 17-5 Inside Crown Radius (L) of the Torispherical Head 1110 Inside Crown Radius of Head 14-4 Inside Diameter of Basering 20-7 Inside Diameter of Bellows 21-3 Inside Diameter of Extruded Outlet 19-4 Inside Diameter of Flange 14-5 Inside Diameter of Ring 5-8 Inside Diameter of Shell 24-3 Inside Knuckle Radius of the Torispherical Head 11-10 Inside Radius of Formed Half-Pipe Jacket 24-4 Installation on a Network Drive 2-7 Installation Options 6-6 Installation Procedure 2-2 Installation/Configuration Process 2-1 Installing PVElite 2-4 Insulation 5-35 Insulation Density 5-35 Insulation or Fireproofing, Thickness of 5-35 Interactive Control 17-16 Internal Design Pressure 13-2 Internal Design Temperature 13-2 Internal Pressure 6-2, 10-5, 11-3, 21-2, 25-3, 26-9 Internal Pressure (P) 17-15 Internal Pressure (Pvar) 17-15 Internal Pressure Calculations 7-3 Internal Pressure in Shell 24-3 Internal Pressure Results 13-9 Internal Pressure Results for the Head 14-9 Internal Temperature 6-2 Intersection Description 19-1 Intersection Number 19-1 Invoking the Drawing 3-55 IS 875 Wind Code 6-24 Is There a Shell Band 23-8 Is This a Heat Exchanger 6-5 Is this a Kettle Type Heat Exchanger ? 16-12 Is This a Pressure Only Case ? 23-15 Item Number 18-2, 21-2, 24-3, 26-9, 27-1

J Jacket Allowable Stress, Ambient Temperature 24-5 Jacket Allowable Stress, Design Temperature 24-5 Jacket Material Name 24-5 Joint Efficiency for Longitudinal Seams 10-6, 24-4 Joint Efficiency for Skirt Weld at Bottom Head 20-9 Joint Efficiency for Welded Seams 26-11 Joint Efficiency of Nozzle Neck 5-15 Joint Efficiency of Shell Seam through which Nozzle Passes 5-15


K Keyboard Commands 29-11 Knuckle Bend Radius, Large End 13-8 Knuckle Bend Radius, Small End 13-8 Knuckle Radius for Torispherical Heads 10-9 Knuckle Radius of Torispherical Head 11-10 Knuckle Ratio for Torispherical Heads 15-8 Knuckle Thickness, Large End 13-8 Knuckle Thickness, Small End 13-8

L Lap Joint Contact Inside Diameter 12-11 Lap Joint Contact Outside Diameter 12-11 Lap Joint Flanges 12-5 Large Opening Module 25-1 Lease 1-10 Leg & Lug Module 18-1 Leg Allowable Stress at Ambient Temperature 18-9 Leg Allowable Stress at Design Temperature 18-9 Leg End Condition Factor K 18-8 Leg Orientation 5-29 Leg Results 18-10 Legs 5-29 Legs & Lugs 1-7 Legs Cross-Braced 18-9 Legs, Length of 5-30, 18-8 Legs, Number of 5-20, 5-30, 18-8 Length of Kettle Cylinder 16-12 Length of Kettle Port Cylinder (LP) 16-12 Length of Section 10-9 LGCENTER 1-6 License agreement, CAESAR II 1-2 License grant 1-2 Licenses 1-10 Lift Orientation 18-14, 18-29 Lifting Lug 1-5 Lifting Lug Input 18-13 Lifting Lug, Thickness of 18-14 Ligament Efficiency Calculations 26-17 Liguid on Tray 5-28 Limitations of remedies 1-3 Limited Run 1-10 Limited warranty 1-3 Lines of Support for External Pressure 13-7 Lining 5-36 Lining Density 5-36 Lining, Thickness of 5-36 Liquid 5-33 Liquid Column Hydrotest Height 10-9 Liquid Column Operating Height 10-9 Liquid Density 5-33 Liquid Height from Bottom of Tank 15-2

Liquid on Tray, Density of 5-28 Load Case 6-10 Load per Bolt, Calculation of 20-4 Load Reaction, Diameter of 12-12 Loads and Design Constraints 3-45 Local Shell Thickness 5-16 Local Stress Calculation Due To Attached Loads 1-5 Location of the Nozzle in the Vessel Spherical 27-6 Longitudinal Allowable Stresses 7-6 Longitudinal Joints, Quality Factor for 19-3 Longitudinal Moment 17-12, 27-4 Longitudinal Shear Load 17-12 Longitudinal Stress Constants 7-6 Longitudinal Stresses 7-6 Long-Side Length Dimension 26-12 Lug Allowable Stress at Ambient Temperature 18-12, 18-13 Lug Allowable Stress at Design Temperature 18-13 Lug Allowable Stress at Operating Temperature 18-11 Lug Bearing Width 5-19 Lug Distances from Base 6-8 Lug Height 5-20 Lug Height (only if no Top Ring 4-35 Lug Midpoint 5-19 Lug Orientation to Vessel 18-13 Lug Thickness 4-35 Lug Width 5-20 Lugs 5-19

M M.A.W.P. and Static Head 6-12 Main Input Fields 10-5, 11-3, 12-4, 14-3, 15-1, 16-5, 172, 18-2, 19-1, 20-6, 21-2, 22-3, 23-4, 25-3, 26-9 Main Menu 3-16 Manway or Inspection Opening 11-8 Material Allowable Stress, Ambient Temperature 13-3, 25-4, 26-9 Material Allowable Stress, Design Temperature 13-3, 25-4, 26-9 Material Category, Cycle Life Evaluation 21-3 Material Definition 29-4 Material Diameter and Thickness Limits 11-14 Material Name 22-3, 26-9, 29-6 Material Specification 14-3, 15-2, 19-1, 20-6, 25-4 Material Specification for Integral Part 23-17 Material Specification for Legs 18-8 Material Specification for Lifting Lugs 18-13 Material Specification for Support Lugs 18-11 Material Yield Stress 5-27 Mating Flange Bolt Load, Operating 12-13 Mating Flange Bolt Load, Seating 12-13 Mating Flange Design Bolt Load 12-13

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Mating Flange Loads 12-10 Max. Mapped Res. Acc. Sl 6-46 Max. Mapped Res. Acc. Ss 6-46 Maximum Allowable Pressure, New & Cold 11-3 Maximum Allowable Working Pressure 10-13, 12-16 Maximum Allowable Working Pressure Calculation 1115 Maximum Allowable Working Pressure Calculations 26-18 Maximum Allowable Working Pressure, New & Cold 10-14 Maximum Circumferential Moment 17-12 Maximum Longitudinal Moment 17-12 Maximum Radial Force 17-12 Mean Diameter of Kettle Cylinder 16-12 Mean Diameter of Kettle Port Cylinder (DP) 16-12 Mean Shell Metal Temperatures 23-13 Mean Tube Metal Temperatures 23-13 Mean Width of Gusset Plate 18-12 Mean Width of Gussets 5-20 Meridional 22-9 Metal Temperature 6-3, 10-7, 11-15, 23-13 Metal Temperatures 10-14, 23-12 Mill Undertolerance, Percent 19-3 Minimum Design Metal Temperature 10-7, 11-15 Minimum Diameter and Thickness 5-15 Minimum Fillet Weld Size Calculations 24-6 Minimum Metal Tempatures 10-14 Minimum Metal Temperature 6-3 Minimum Thickness of 2nd Long-Side Plate 26-13 Minimum Thickness of End Plate 26-12 Minimum Thickness of Fillet Weld Around Lug 18-14 Minimum Thickness of Long-Side Plate 26-12 Minimum Thickness of Pipe or Plate 10-7 Minimum Thickness of Short-Side Plate 26-11 Minimum Thickness/Diameter of Stay Plate/Rod (T3) 26-14 Minimum Thickness/Diameter of Stay Plate/Rod (T4) 26-14 Minimum Yield Stress for This Material 26-10 Miscellaneous Tab 9-11 Modulus of Elasticity 26-13 Moment about X, Y, or Z Axis 5-23 Moment of Inertia 5-8 Moment of Inertia of Reinforcing Member 26-16 Moment of Inertia of Reinforcing Section 13-8 Moment of Inertia of Stiffening Ring 15-8 Moment of Reinforcing Ring 10-11 Moment Reduction Factor Tau 6-41 Mouse Operation 29-12

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N Natural Frequency Calculation 7-6 Natural Frequency for the Structure 15-7, 18-7 NBC Seismic Data 6-33 NBC Wind Data 6-19 Network ESLs 2-8 Network Installation / Usage 2-7 Node Number 12-12 Nominal Bolt Diameter 12-8, 14-5, 16-14, 18-24, 20-7, 23-15 Nominal Compressive Stress of Concrete 18-25, 20-8 Nominal Density of Material 29-6 Nominal Diameter and Thickness 5-15 Nominal of Average Thickness of Pipe or Plate 10-7 Nominal Pipe Size of Half-Pipe Jacket 24-4 Nominal Schedule of Nozzle 5-15 Nominal Thickness of Branch/Header 19-2 Nominal Thickness of Nozzle 11-6 Non-Circular Flat Heads 11-11 Non-Ferrous Materials 29-9 Normal Force 18-14, 18-29 Novell File Server ESL Installation 2-8 Novell Workstation ESL Installation 2-8 Nozzle 17-7 Nozzle Analysis 5-11 Nozzle Angle Geometry 11-8 Nozzle Corrosion Allowance 5-15, 11-7, 17-7, 27-2 Nozzle Description 5-13, 11-3 Nozzle Design Modifications 6-12 Nozzle Design Pressure 6-12 Nozzle Diameter 17-7, 27-2 Nozzle Diameter and Thickness, Actual 11-13 Nozzle Diameter Basis 5-14, 11-6 Nozzle Diameter Limit 5-14, 11-6, 11-11 Nozzle Input Data 5-13 Nozzle Insertion 5-16, 11-7 Nozzle Inside Projection 5-16, 11-12 Nozzle Material Specification 5-14 Nozzle Module 11-1 Nozzle Outside Projection 5-16, 11-12 Nozzle Schedule 5-15 Nozzle Side Hub Length 25-4 Nozzle Side Hub Thickness, Large End 25-4 Nozzle Side Hub Thickness, Small End 25-4 Nozzle Size and Thickness Basis 5-14, 11-6 Nozzle Thickness 3-25, 9-9, 11-6 Nozzle Thickness Limit 5-14, 11-12 Nozzle Wall Thickness 27-2 Nozzle Weight 5-10 Nozzle, Diameter of 27-2 Nozzle, Thickness of Actual 5-15 Nozzles 1-6, 5-10


Nozzles, Small 3-25 Nubbin Width 12-10, 14-7, 16-15, 23-16 Number of Bolts in Tension per Baseplate 18-25 Number of Bolts, Selecting 20-4

O Occasional Load Factor 18-4 OD as the Basis for the shell Radius in Zick 3-26 Offset Distance from Cylinder/Head Centerline 5-13 Offset from Centerline 5-22 Offset from Left Tangent Line 27-6 Offset from Vessel OD to Center of Hole 18-14 Opening Inside Diameter 25-3 Openings, Large 1-6 Operating Liquid Density 10-9, 11-10 Operating Moment of Basering 20-9 Operating Weight of Vessel 20-9 Ordinate Type 6-47 Outer Cylindrical Element Corrosion 22-7 Outer Cylindrical Element Length 22-7 Outer Cylindrical Element Thickness 22-7 Output 18-16, 19-6 Output / Review 8-1 Output Menu 3-23, 9-8 Output Review 3-12 Outside Diameter of Basering 20-7 Outside Diameter of Flange 14-5 Outside Diameter of Flanged Portion 16-13, 23-14 Outside Diameter of Ring 5-8 Outside Diameter of Skirt at Base 20-9 Outside Diameter of Vessel 18-2 Outside Diamter 5-29 Overall M.A.W.P. and Static Head 6-12

P P instead of MAWP for UG-99B 9-10 P Number Thickness 29-7 Packed Section Height 5-31 Packing 5-31 Packing Density 5-31 Pad Diameter 17-9 Pad Diameter Along Header Surface 19-5 Pad Length 5-21 Pad Material 5-17 Pad Outside Diameter Along Vessel Surface 11-12 Pad Outside Diameter along Vessel Surface 5-17 Pad Parameter C11 (full length) 17-9 Pad Parameter C22 (full length) 17-9 Pad Thickness 5-17, 5-21, 11-12, 17-9, 19-5 Pad Weld Leg Size as Outside Diameter 5-17 Pad Weld Leg Size at Outside Diameter 11-12 Pad Width 5-20

Parameter C11 (Full Length of Attachment) 17-8 Parameter C22 (Full Length of Attachment) 17-8 Parameters, Required 3-53 Partition Gasket 12-10 Partition Gasket, Length of 12-12, 14-7, 16-16, 23-16 Perform WRC 107 Analysis on Trunnion 18-29 Perform WRC 107 Calc 5-20 Performance Criteria Factor P 6-30 Pin Hole Diameter 4-35 Pipe & Pad 1-5 Pipe & Pad Module 19-1 Pipe Legs Inside Diameter 18-9 Pipe Normal or Actual Outside Diameter 19-2 Pitch Distance Between Bars 26-14 Pitch Distance Between Reinforcement 26-13 Plates 5-27 Platform Clearance 5-25 Platform End Angle (degrees) 5-24 Platform Force Coefficient 5-25 Platform Grating Weight 5-24 Platform Height 5-25 Platform Length 5-25 Platform Railing Weight 5-24 Platform Start Angle (degrees) 5-24 Platform Weight 5-24 Platform Width 5-25 Platform Wind Area 5-24 Platform Wind Area Calculation 5-25 Platforms 5-24 Plotting the Vessel Image 3-43 Pop-Up Input Fields 11-10, 12-11, 13-7, 14-8, 15-5, 177, 18-6, 19-5, 21-4, 22-7, 23-10, 26-13 Pop-up Input Fields 10-9, 20-10 Pre-1999 Addenda 9-11 Preliminary Base Ring Geometry, Selecting 20-4 Pressure 12-5, 17-11, 18-2, 19-1, 27-2 Pressure Calculations for Input Shell Thickness 24-6 Pressure Calculations, External 26-18 Pressure Chart Name, External 29-8 Pressure in 2nd Compartment 26-14 Pressure in Jacket 24-5 Pressure Results for the Head, External 14-9 Pressure Results, External 13-9 Pressure Stress Indices 17-17 Pressure Thrust Force 17-15 Printing Equations and Substitutions 3-25 Printing Intermediate Calcs for External Pressure 11-10 Printing or Saving Reports to a File 9-27 Printing the Reports 9-27 Printing Water Volume in Gallons 3-24, 9-10 Printout in Rows, External 9-12 Processors, Miscellaneous 29-1

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Program Structure and Control 3-1 Program Support / User Assistance 1-9 Projection from Bottom 6-3 Projection from Top 6-3 Projection Length 18-28 PV Elite Component Analysis New Features 1-11 PV Elite Component Analysis New Features Version 4.1 1-14 PV Elite Component Analysis New Features Version 4.3 1-14 PVElite Analysis 7-1 PVElite Definition 1-1 PVElite Documentation 1-8 PVElite Startup 3-40

Q Quick Start with PVElite 3-40

R Radial Force 17-12 Radial Load 17-12 Radial Width of Bottom Support Plate 5-19 Radial Width of Reinforcing Ring 13-8 Radial Width of Top Bar Plate or Top Ring 18-12 Radial Width of Top Plate/Ring 5-20 Radial Width of Top Ring/Plate 20-8 Radiography, Degree of 6-4 Radius of Corner Section 26-13 Radius of Curvature, RX, of Extruded Outlet 19-4 Radius of Half-Pipe Jacket 24-4 Radius of Semi-Circular ARC of Lifting Lug 18-14 Radius to Outermost Tube Hole Center 23-8 Range Type 6-47 Recording the Model 3-43 Rectangular Vessel Description 26-9 Rectangular Vessel Module 26-1 Rectangular Vessels 1-6 Redesign Pads to Reinforce Openings 6-13 Reinforcement 18-28 Reinforcement Calculations 26-17 Reinforcement Calculations Under External Pressure 1310 Reinforcement Calculations Under Internal Pressure 139 Reinforcement Limit Modification 11-5 Reinforcement Type 26-11 Reinforcing Cone, Location of 13-7 Reinforcing Limits, Modification of 5-14 Reinforcing Member, Length of 26-15, 26-16 Reinforcing Pad 11-7, 27-2 Reinforcing Pad Present 19-3 Reinforcing Pad, Selecting 11-14

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Reinforcing Ring 13-8, 26-15 Reinforcing Ring Cross-Sectional Area 21-4 Reinforcing Ring Material 21-4 Reinforcing Ring Present 21-3 Reinforcing Ring Type 10-7, 26-15 Reinforcing Ring, Thickness of 10-10 Reinforcing Section 13-8 Reinforcing, Small End 13-5 Reloading last file at Startup 9-12 Report Content 9-12 Report Generation 3-12 Required and Available Areas 11-14 Required Parameters, Setting Up 3-53 Required Thickness Calculations 14-9 Required Thickness of Gussets in Compression 20-4 Required Thickness of Gussets in Tension 20-3 Required Thickness of Nozzle 11-7 Required Thickness of Shell and Nozzle 11-13 Required Thicknesses 11-5 Response 6-43 Response Modification Factor R 6-41 Response Modification R 6-46 Response Spectrum 6-43 Response Spectrum Name 6-43 Restrictions of this Method 15-11 Results 10-13, 11-13, 12-14, 13-9, 14-9, 15-10, 17-19, 22-9, 24-6, 26-17, 27-11, 28-8 Results for a Whole Vessel 9-28 Results for Maximum Allowable External Pressure 1014 Results for Required Thickness for External Pressure 1015 Results Per Pressure, Area, and UG-45 11-15 Reverse Geometry Flange 12-5 Review 8-3 Review Screen 8-2 Reviewing the Results 3-49 Reviewing the Results - The Output Option 9-25 Rib Thickness 5-27 Ribs, Number of 5-27, 15-5 Ribs, Thickness of 15-5 Rigging Data 6-7 Ring Angle Rolled the Hard Way 10-12 Ring Centroid 10-11, 15-9 Ring Centroid Distance 5-8 Ring Diameter, Outside 5-8 Ring Flanges 12-4 Ring Inside Diameter 5-8 Ring Material 5-8 Ring Material Allowable Stress at Ambient Temperature 21-4 Ring Material Allowable Stress at Operating Tempera-


ture 21-4 Ring Outside Diameter 18-29 Ring Thickness 18-29 Ring Type to Satisfy Inertia and Area Requirements 1011 Ring Weld Attachment Style (Intermittent, Continuous, Both) 10-11 Ring, Location of 10-11 Ring, Thickness of 5-8 Rings 5-7 Risk Factor 6-24 Roughness Factor 6-20, 6-22 Round Thickness to Nearest Nominal Size? 3-25 Run Multiple Load Cases for Fixed Tubesheet ? 16-13, 23-14 Running the Analysis 3-48

S Saddle 15-3 saddle 15-4 Saddle Base 15-6, 15-7 Saddle Bearing Angle 15-4 Saddle Check 5-27 Saddle Contact Angle 5-26 Saddle Dimension A 5-27 Saddle Wear Plate Design 15-11 Saddle Webs & Base Plate 15-2 Saddle Width 15-4 Saddles 5-26 Sample Calculation 27-7, 28-3 Schedule of Nozzle, Actual 11-6 Section Identifier 5-30 Section Type 5-8 Seismic 5-23 Seismic Coefficient Av 6-30 Seismic Coefficient Ca 6-37 Seismic Coefficient Cc 6-30 Seismic Coefficient Cv 6-37 Seismic Data 6-27 Seismic Design Category 6-41 Seismic Design Code 6-27 Seismic for Hydrotest 6-29, 6-30, 6-31, 6-34, 6-36, 6-38, 6-43 Seismic for Hydrotest, Percent 6-37 Seismic Load Input in G’s 6-40 Seismic Loads to Vessel, Applying 15-3 Seismic Zone 6-29, 6-32, 15-7, 18-7 Select Load Cases for Detailed Printout 16-13, 23-15 Select the Addenda for the Material Database 9-11 Shear and Bending Moments due to Wind and Earthquake 7-6 Shear Force VC 27-3

Shear Force VL 27-3 Shell Allowable Stress at Ambient Temperature 10-6, 24-4 Shell Allowable Stress at Design Temperature 10-5, 24-3 Shell Allowable Stress, Ambient Temperature 23-10 Shell Allowable Stress, Design Temperature 23-10 Shell and Head Diameter Basis 15-3 Shell Corrosion Allowance 11-5, 16-6, 18-3, 22-4, 23-4, 24-4 Shell Cylinder Length 22-4 Shell Design Length for External Pressure 11-10 Shell Design Pressure 16-5, 23-4 Shell Diameter 15-3 Shell Diameter Basis 11-4 Shell Diameter or Crown Radius for Torispherical Head 11-5 Shell Inside Diameter 16-6, 22-4, 23-4, 24-3 Shell Joint Efficiency 15-3 Shell Length Tangent to Tangent 15-3 Shell Material 18-3 Shell Material Specification 23-10 Shell Metal Design Temperature 16-5 Shell Metal Temperature at Tubesheet. 23-13 Shell Metal Temperature, Actual 16-9 Shell Metal Temperatures 23-13 Shell Module 10-1 Shell or Head Type 10-6, 11-4 Shell or Head, Diameter of 10-7 Shell Seam Efficiency 11-7 Shell Section Material Name 10-5, 24-3 Shell Side (External) Corrosion Allowance 14-5 Shell Side (External) Design Pressure 14-3 Shell Side Hub Length 25-3 Shell Side Hub Thickness, Large End 25-3 Shell Side Hub Thickness, Small End 25-3 Shell Surface 10-11, 15-9 Shell Temperature for Internal Pressure 23-10 Shell Thickness 15-3, 18-2 Shell Thickness Calculations 24-6 Shell Thickness, Modification of 6-12 Shell Tr Value 5-16 Shell Wall Thickness 16-5, 22-4, 23-4 Shell, Nozzle, or Pad Material Name 11-3 Shell, Thickness of 11-5, 24-3 Shell/Head Material Normalized 10-6 Shell/Head/Nozzle Material Normalized 11-4 ShellChannelTubeTube Sheet Material Specification 165 Shells & Heads 1-6 Shellside Design Pressure 22-6 Shellside Prime Design Pressure (from Tubesheet) 22-6 Shellside Prime Design Pressure (from Tubesheet) Cor-

xi


roded 22-6 Shock Scale X|Y dir 6-45 Short-Side Length Dimension 26-10 Simple Bar Geometry 26-15 Site Distance 6-22, 15-7, 18-7 Skirt Allowable at the Skirt Top 20-10 Skirt at Base, Outside Diameter 20-9 Skirt Comp Allowable Mult for (B) at Base (OPE) 20-10 Skirt Comp Allowable Mult for (B) at Base (TEST) 2011 Skirt Comp Allowable Mult for (SY) at Base (OPE) 2011 Skirt Comp Allowable Mult for (SY) at Base (TEST) 2011 Skirt Diameter at Bottom Head 20-9 Skirt Temperature 20-9 Skirt Thickness 20-9 Skirt Thickness, Basic 20-5 Slip-on Flanges 12-4 Soehren’s Calculation 14-7 Soehren’s Calculations 14-9 Software Lock 2-1 Soil Factor 6-36 Soil Type 6-28, 6-31, 6-33 Special Service 6-4 Specifying Global Data 3-45 Splits in Backing Ring, Number of 12-11, 14-8 Spring Constant 22-9 SRSS 6-45 Stainless Steel (High Alloy) Materials 29-9 Standard Bar Ring 6-8 Status Bar 10-13, 11-13, 12-14 Stay Plate/Rod Welded to the End Plate 26-14 Steps for Calculating and Displaying Vessel-Analysis Results 7-3 Stiffener from Shell Surface 15-9 Stiffener Type 6-6 Stiffening Ring Location 15-8 Stiffening Ring Material Specification 15-8 Stiffening Ring Present 15-4 Stiffening Ring Properties 15-8 Stiffening Rings for External Pressure, Selecting 6-9 Stored Liquid Density 15-2 Straight Flange, Length of 10-9 Stress at Ambient Temperature, Allowable 11-4, 12-6, 15-2, 20-7, 21-2, 29-6 Stress at Design Temperature, Allowable 11-3, 12-6, 224 Stress at Given Pressure and Thickness, Actual 10-14 Stress at Hydrotest Temperature, Allowable 29-6 Stress at Operating Temperature , Allowable 20-6 Stress at Operating Temperature, Allowable 15-2, 21-2,

xii

29-6 Stress Calculations 26-17 Stress due to Combined Loads 7-6 Stress in Skirt due to Gussets or Top Ring 20-5 Stress Multipliers 20-9 Stresses 22-9 Summary 1-7 Summary of External Pressure Results 10-15 Summary of Internal Pressure Results 10-14 Summary of PVElite Version 4.00 Improvements 1-12 Summary of Results 24-7 Support Contact Point 18-11 Support Lug Input 18-11 Support Lug Reinforcing Ring ( None, Girder Ring ) 1811 Support Lugs Above Grade, Location of 18-11 Support Lugs, Number of 18-11 System and Hardware Requirements 2-1

T Tail Lug Type 4-35 Tailing Lug Analysis 4-35 Tangent to Tangent Length of Vessel 18-3 Tangential Force 18-15, 18-29 Tapped Hole Area Loss 5-17 Technical Basis 10-1, 11-1, 12-1, 13-1, 14-1, 16-1, 21-1, 23-1, 24-1, 25-1, 26-1, 27-1, 28-1 TEMA Channel Cover 12-12 TEMA Number 29-10 TEMA Tubesheet Module 16-1 TEMA Tubesheets 1-5 TEMA Tubesheets Metal Temperature, Actual 16-9 Temperature 10-5, 11-3, 12-5, 14-3, 19-1, 21-2, 22-3, 23-7, 23-17, 24-3, 24-5, 25-3, 26-9, 27-2 Temperature for Gussets (if not ambient) 20-10 Temperature of Basering 20-6 Term 1-2 Terrain Category 6-24 Test Moment on Basering 20-9 Test Weight of Vessel 20-9 Thick Joint Module 22-1 Thickness Due to Internal Pressure 10-13 Thickness of Kettle Cone (KC) 16-13 Thickness of Kettle Cylinder 16-12 Thickness of Kettle Port Cylinder (TP) 16-12 Thickness of Pipe or Plate 10-7 Thickness, Minimum 5-15 Thickness, Required 11-5 Thick-Walled Expansion Joints 1-5 Thin Joint Module 21-1 Thin-Walled Expansion Joints 1-5 Thread Series 12-8, 14-5, 16-14, 18-25


Thread Series (TEMA,UNC) 23-15 Threaded Holes in Plates 26-11 Tools Menu 3-11, 3-24, 9-9 Top Bar Plate 18-12 Top Bar Plate or top Ring, Thickness of 18-12 Top Plate/Ring 5-20, 20-8 Top Plate/Ring, Thickness of 5-20 Top Ring 18-12 Top Ring Plate, Thickness of 20-8 Top Ring Under Tension, Thickness of 20-3 Top Ring/Plate Type per Moss ( Type 3-Cap Plate, 4Continuous Ring ) 20-8 Torsional Moment 17-12 Torsional Moment MT 27-3 Total Number of Bolts per Baseplate 18-25 Total weight and detail moment 7-5 Tower Deflection, Allowable 3-26 Tray Spacing 5-28 Tray Weight Per Unit Area 5-28 Trays 5-28 Trays, Number of 5-28 Trunnion Input 18-28 Trunnion Material 18-28 Trunnion Outside Diameter 18-28 Trunnion Result 18-31 Trunnion Thickness 18-28 Trunnion Type (Hollow or Solid) 18-28 Tube Centers 23-7 Tube Corrosion Allowance 16-7 Tube Joint Connection 23-13 Tube Layout, Area of 16-7 Tube Layout, Perimeter of 16-7 Tube Material Allowable Stress, Ambient Temperature 23-7 Tube Material Allowable Stress, Operating Temperature 23-7 Tube Material Specification 16-10, 23-7 Tube Metal Temperature, Actual 16-9 Tube Metal Temperatures 23-13 Tube Outside Diameter 16-7, 23-6 Tube Pattern (Triangular, Square) 16-7, 23-7 Tube Pitch 23-7 Tube Pitch (Distance Between Tube Centers) 16-7 Tube Side (Internal) Corrosion Allowance 14-4 Tube Side (Internal) Design Pressure 14-3 Tube Side Pass Partition Groove Depth (hg) 23-8 Tube Wall Thickness 16-10, 23-6 Tubes Attached by a Groove or Fillet Weld 16-7 Tubes, Length of 16-9, 23-11 Tubes, Number of 16-9, 23-6 Tubesheet Allowable Stress, Ambient Temperature 23-5 Tubesheet Allowable Stress, Operating Temperature 23-

5 Tubesheet Corrosion Allowance (Shellside/Tubeside) 23-5 Tubesheet Corrosion Allowance Chanel Side 16-8 Tubesheet Corrosion Allowance Shell Side 16-8 Tubesheet Description 23-4 Tubesheet Extended as Flange? 16-8 Tubesheet Gasket (None, Shell, Channel, Both) 16-8, 23-8 Tubesheet Integral With 23-8 Tubesheet Material Specification 23-5 Tubesheet Metal Design Temperature 16-8, 23-5 Tubesheet Metal Temperature at the Rim. 23-13 Tubesheet Number 23-4 Tubesheet Thickness 16-8, 23-5 Tubesheet Type 16-6 Tubesheets Extended as Flanges 16-16 Tubeside Design Pressure 22-6 Tubeside Prime Design Pressure (from Tubesheet) 22-6 Tubeside Prime Design Pressure (from Tubesheet) Corroded 22-6 Tutorial / Master Menu 3-1 Tutorial Problem Printout 9-29 Type of Analysis 18-3 Type of Tubesheet 23-5

U UBC 1997 Earthquake Data 6-38 UBC Earthquake Importance Factor 6-38 UBC Horizontal Force Factor 6-39 UBC Near Source Factor 6-38 UBC Seismic Coefficient CA 6-38 UBC Seismic Coefficient CV 6-38 UBC Seismic Data 6-31 UBC Seismic Zone 6-38 UBC Wind Data 6-17 UBC Wind Importance Factor 6-17 UCS-66 Chart Number 29-7 UG-45 Minimum Nozzle Neck Thickness 11-14 Uncorroded Expansion Joint Spring Rate 16-11, 23-11 Unreinforced Length Dimension 26-14 Updates 1-10 Use Appendix CC ? 22-5 Use Code Case 2260? 9-11 Use Expansion Joint Allowable Stress 22-5 Use Pre-99 Addenda Division 1 only 3-26 Use Stress Indices (AD 560.7)? 27-5 User Border Creation 3-54 User Defined 6-44 User-Defined Hydrostatic Test Pressure 6-5 User-Defined MAWP/MAPnc 6-5 User-Defined Wind Profile 6-26

xiii


User-Entered Seismic Zone Factor CS 15-7, 18-7 User-Specified Root Area of a Single Bolt 20-10

V Velocity Zone 6-35 Version 3.5 Improvements 1-11 Version 3.6 Improvements 1-11 Version 4.1 Improvements 1-13 Version 4.3 Improvements 1-14 Vertical Vessels 1-4 Vessel 17-3 Vessel above Grade 15-6 Vessel Analysis Calculations 7-8 Vessel Centerline 15-6, 15-7 Vessel Centerline, Distance or Offset 5-6 Vessel Components (Details), Individual 3-50 Vessel Corrosion Allowance 27-2 Vessel Data, General 6-1 Vessel Description 15-1, 18-2 Vessel Description, Rectangular 26-9 Vessel Design Pressure 15-1 Vessel Design Temperature 15-2 Vessel Detail Data 5-1 Vessel Details, Design and Analysis of 3-14 Vessel Diameter 27-1 Vessel Example Problems 30-1 Vessel Leg Input 18-8 Vessel Material 27-2 Vessel Nozzles 1-4 Vessel Number 15-1 Vessel OD 5-19, 18-11 Vessel Orientation 18-9 Vessel Radius 26-14 Vessel Stress Concentration Factor 27-2 Vessel Tangent 15-3 Vessel Type 17-3, 26-10 Vessel Wall Thickness 17-3, 27-1 Vessel, Basic Definition of 3-40 Vessel, Diameter of 17-3 Vessel, Distance from Outside of 26-15 Vessel, Length of 26-13 Vessel, Outside Diameter 18-2 Vessel/Nozzle Centerline Direction Cosines 17-13 Vessels, General 1-4 Vibration Period 6-36 View Menu 3-30, 9-17 Vortex Shedding 6-5

W Wall Thickness for Axial Stress, Selecting 6-9 Wall Thickness for External Pressure, Selecting 6-9 Wall Thickness for Internal Pressure, Selecting 6-9

xiv

Wear Pad Extension Above Horn of Saddle 15-4 Wear Pad Thickness 15-4 Wear Pad Width 15-4 Wear Plate Contact Angle (degrees) 5-27 Wear Plate, Thickness of 5-26 Web Location 5-27 Web Location Center or Side 15-5 Web Thickness 5-27 Web, Thickness of 15-5 Weight 5-22, 15-2 Weight & Volume Results, No Corrosion Allowance 1014 Weight of Details 7-4 Weight of Elements 7-4 Weight of One Lug 5-20 Weight, Miscellaneous 5-22, 6-4 Weld Along Bottom of Lifting Lug, Length of 18-14 Weld Around Sides of Lug, Length of 18-14 Weld Leg at Back of Ring 12-11 Weld Leg Size Between Inward Nozzle and Inside Shell 5-16, 11-12 Weld Leg Size for Fillet Between Nozzle and Shell or Pad 5-16, 11-12 Weld Neck Flanges 12-4 Weld Size Calculations 11-15 Weld Size Thickness 4-35 Weld Strength Calculations 11-15 Width of Gusset Plates, Average 20-10 Width of Partition Gasket 14-7, 16-16, 23-17 Width of Reinforcing Member 26-15 Width of Reinforcing Ring 10-10 Width of Saddle 5-26 Width of the Pass Partition Gasket 12-12 Width of Wear Plate 5-26 Wind 5-23 Wind & Seismic Data 6-14 Wind Data 6-14 Wind Deflection 7-6 Wind Design Code 6-14 Wind Exposure 15-6, 18-6 Wind for Hydrotest 6-15, 6-17, 6-19, 6-21, 6-24, 6-26 Wind Load Calculation 7-6 Wind Loads to Vessel, Applying 15-3 Wind Pressure on Vessel 15-5, 18-6 Wind Profile Data 6-26 Wind Shape Factor 3-26 Wind Speed 6-15, 6-17, 6-19, 6-21 Wind Speed, Basic 15-6, 18-6 Wind Zone Number 6-24 Windows Server Installation 2-8 Working Pressure 10-13, 10-14, 11-15, 12-16 WRC 107 1-7


WRC 107 Module 17-1 WRC 107 SIF (Kn,Kb) 17-16 WRC 107 Stress Calculations 17-19 WRC 107 Stress Summations 17-22 WRC 107 Version 17-16 WRC 297 1-7 WRC 297 Module 27-1

X XY Coordinate Calculations 7-3

Y Yield Stress, Operating 29-7

Z Zero Period Acceleration 6-45 Zone Number 6-36

xv

COADE, Inc. 12777 Jones Rd., Suite 480 Houston, Texas 77070 Phone: (281)890-4566 Fax: (281)890-3301 E-mail: [email protected] WWW: www.coade.com

PVElite USER'S GUIDE V E R S I O N 4.30 ( L A S T R E V I S E D 1/2002 )

PVElite Manual

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