Pressure Vessel Design Calculations

Cairo Oil Refining Co.

‫ول‬‫א‬ ‫א‬‫א‬ ‫א‬ ‫ول‬ ‫אא‬‫א‬ ‫א‬ ‫אא‬ª ª‫دد‬

Subsidery of Egyotian Gen. Petroleum Corp.

P.O. Box : Heliopolis 11757 Cairo A.R.E.

‫د‬‫د‬‫א‬ ‫א‬ ١١٧٥٧ ‫س‬‫و‬ ‫و‬‫و‬:..‫ص‬ :..‫ص‬

Tel. : (+2) 02 - 2529821 (5 Lines)

(‫طوط‬ ٥) ٢٠٢ - ٢٥٢٩٨٢١: :‫ن‬ ‫ون‬

Fax : (+2) 02 - 2529826

٢٠٢ - ٢٥٢٩٨٢٦: :‫س‬ ‫س‬

:‫وو‬‫א‬ ‫د א‬ [email protected]:

E-mail : corc2000@ex [email protected] cite.com

Pressure Vessel

DESIGN CALCULATIONS Code : Code Stamp : Client :

ASME Section VIII, Division 1, Edition 2001, Addenda 2002 U Amerya Petroleum Petroleum Refining Co. (APRC)

Project : Location : Item No. : Serial No. : Title : Service : Job No. : Dwg. No. :

Design & Fabrication of Debutanizer Reflux Reliever Drum Alexandria, EGYPT 1-D-5 7434-33-U-2006 Horizontal Pressure Vessel Deputanizer Reflux Reliever Drum 7434-33 7434-33-3A, Rev. 1

Vessel ID Tangent-to-Tangent Length Vessel W all Thickness MAW P Design Temperature MDMT

15 5 6 4 8 20 22 18 65 -12

MM MM MM 2 Kg/CM G o C o C

Vessel capacity Weight of vessel empty (erection weight), W Weight of test liquid (water), W c Tota Totall test test weig weight ht (wei (weigh ghtt of vesse vessell and and test test liqui liquid) d),, Wt Number of saddles

10.1518 7428 1 0152 1758 17580 0 2

M Kg Kg Kg Saddles

3

By

Eng. Abdel Halim Galala Design Sector Manager (assist.)

‫מ‬‫א‬ ‫ع א‬‫ط‬

Design Sector Page : 1 of 126

Sheet 1 of of 2

DESIGN CALCULATIONS OF PRESSURE VESSEL

Page : 2 of 126

According to ASME Code, Section Section VIII, Division 1, Edition 2001, 2001, Addenda 2002 Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (assist.)

Sheet : 2 of 2 Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Job Name : Demineralization Plant

Date : 18.2.2004 Job No. : 7434-33

Serial No. : 7434-33-U-2006

Client : APRC

Dwg. wg. No. : 7434-33-3A, Rev. 1

Vessel Ves sel : Deputa Deputaniz nizer er Ref Reflux lux Rec Receiv eiver er Dru Drum m

Item Ite m No. : 1-D 1-D-5 -5

Capaci Cap acity ty : 10.152 10.152 M3

Type Typ e : Hor Horizo izonta ntall

A. Title (cont.)

DESIGN CALCULATIONS Code : ASME Section Section VIII, Division 1, Edition 2001, Addenda 2002 Client : Amerya Petroleum Petroleum Refining Co. Co. (APRC) Project : Design & Fabrication of Debutanizer Reflux Receiver Drum Location : Alexandria, EGYPT Item No. : 1-D-5 Serial No. : 7434-33-U-2006 Title : Horizontal Pressure Vessel Service : Debutanizer Reflux Receiver Drum Job No. : 7434-33 Dwg. No. : 7434-33-3A, Rev. 1

3 2 1

Issued for approval

0

Issued for comments

18.2.2004 6.4.2003 Desi De sign gned ed by

Rev.

Description

Date

6.4.2003 Revi Re view ewed ed by Date

Revision Table Dwg. No. : 7434-33-3A

Rev. : 1

6.4.2003 Appr Ap prov oved ed by Date

DESIGN CALCULATIONS OF PRESSURE VESSEL According to ASME Code, Section Section VIII, Division 1, Edition 2001, 2001, Addenda 2002 Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (assist.)

Page : 3 of 126 Sheet : 1 of 1 Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Job Name : Demineralization Plant Serial No. : 7434-33-U-2006 Dwg wg.. No. : 7434-33-3A, Rev. 1 Vessel Ves sel : Deputa Deputaniz nizer er Ref Reflux lux Rec Receiv eiver er Dru Drum m Ite Item m No. : 1-D 1-D-5 -5 Cap Capaci acity ty : 10.152 10.152 M3

Date : 18.2.2004 Job No. : 7434-33 Client : APRC Type Typ e : Hor Horizo izonta ntall

B. Copyright.

Copyright 2004 by CORC A.H.Galala, the Design Manager, on behalf of Cairo Oil Refining Co. (CORC) All right reserved.

1st. date of issue - April 6th., 2003

No part of this document may be reproduced in any form, electronic retrieveal system or any otherwise w ithout the prior written permission of Designer.


Page : 4 of 126



Project : Design & Procurement of ASME Pressure Vessel Job Name : Demineralization Plant Serial No. : 7434-33-U-2006 Dwg. wg. No. : 7434-33-3A, Rev. 1 Vessel Ves sel : Deputa Deputaniz nizer er Ref Reflux lux Rec Receiv eiver er Dru Drum m Ite Item m No. : 1-D 1-D-5 -5 Cap Capaci acity ty : 10.152 10.152 M3


C. Revision Description. This page is a record of all revisions of the document, and the following revision(s) has (have) been made to this document.

Rev. 0 1

Date 6.4.2003 1 8 .2 .2 0 0 4

Sheet No. al l al l

Revision Description Issued for comments Issued for approval


Page : 5 of 126





D. Contents.

L. Check of Ellipsoidal Head Thickness for External Pressure (Convex Side), FV.

Page Page : 1 of 126 Page : 3 of 126 Page : 4 of 126 Page : 5 of 126 Page : 6 of 126 Page : 7 of 126 Page : 7 of 126 Page : 8 of 126 Page : 12 of 126 Page : 13 of 126 Page : 14 of 126 Page : 15 of 126

M. Nozzle Neck thicknesses & Nozzle Openings Compensation : Thk., MM N11 1-1/2" M1 10.16 300# WNRF Sch. XXS N8 24" M2 14.27 300# WNRF Sch. 30 M3 Leg 20" 12.7 Sch. 30 N1 8" 12.7 300# WNRF Sch. 60 M4 Integral Type Flange (Blind) N1 8" 300# Thickness Calculation N1 6" 300# WNRF Sch. 80 M5 10.97 N2 6" 300# WNRF Sch. 80 M6 10.97 N9 4" 300# WNRF Sch. 120 M7 11.13 N18 3" M8 8.74 300# WNRF Sch. 160 N3,N4&N7 2" M9 10.16 300# WNRF Sch. XXS 1-1/2" M10 N6&N17 9.09 300# WNRF Sch. XXS M11 N16 1" 10.16 300# WNRF Sch. XXS 10.16 WNRF Sch. XXS M12 N5A,N5B&N12 1-1/2" 300# 7.47 300# WNRF Sch. XXS M13 N10A& N10B 1/2"

Page Page Page Page Page Page Page Page Page Page Page Page Page Page

: 16 of 126 : 21 of 126 : 26 of 126 : 31 of 126 : 36 of 126 : 46 of 126 : 50 of 126 : 55 of 126 : 60 of 126 : 65 of 126 : 70 of 126 : 75 of 126 : 79 of 126 : 85 of 126

N. Design of Saddle Supports. O. Lowest MDMT Without Impact Test. P. Radiography. Q. Hydrostatic Test Pressure. R. Post Weld Heat Treatment (PWHT). S. Vessel Weight Calculation. T. Sresses in Vessel on Two Saddle Supports. U. Check of the Anchor Bolts Due to Seismic and Wind Loading. V. Lifting Lugs Thickness Calculations. W. Mesh Pad (Demister) Calculations. X. References.

Page Page Page Page Page Page Page Page Page Page Page

: 90 of 126 : 97 of 126 : 110 of 126 : 110 of 126 : 110 of 126 : 111 of 126 : 114 of 126 : 122 of 126 : 123 of 126 : 125 of 126 : 126 of 126

Description A. Title. B. Copyright. C. Revision Description. D. Contents. E. Applicable Loading Considered in Design. F. Impact Test Requirements. G. Standarad ASME B16.5 Flange Rating Class. H. Cylindrical Shell Thickness. I. Check of Cylindrical Shell Thickness for f or External Pressure, FV. J. Ellipsoidal Head Thickness Under Internal Pressure. K. Maximum Working Pressure, MWP (New/cold & Operating/corroded).


Page : 6 of 126


Sheet : 1 of 1 Page : 2 of 126



E. Applicable Loading Considered in Design.

[UG-22 & UG-98]

I. By considering UG-22 : 1. The loadings to be considered in design of vessel shall include the following : a. Internal design pressure (see item II below). b. Weight of the vessel and contents under test conditions. c. Attachment of vessel supports such as lifting lugs and saddles. 2. No expected effect for superimposed static reactions such as piping. There is no attached equipment such as motors, machinery, other vessels, lining and insulation. 3. The effect of the following loadings is considered negligible and/or not applicable : a. Cyclic and dynamic reactions due to pressure for thermal variations. b. Wind, snow, and seismic reactions. c. Impact reactions due to fluid chock. d. Temperature gradients and differential thermal expansion. II. By considering UG-21 & UG-98 : The max. allowable working pressure for a vessel part is the max.internal pressure at the highest point of vessel. Since the vessel is intended to be erected horizontaly, the static head equals almost the ID and the hight of leg : 2

16 18 0

Kg/cm G 2 Kg/cm G 2 Kg/cm G

1556 694 894

MM MM MM

2.21023 2.2102 3 PSI PSIG G 3.1960 3.1 9602 2 PSI PSIG G 3.4801 3.4 8011 1 PSI PSIG G

0.1556 0.225 0.245

Kg/cm G 2 Kg/cm G 2 Kg/cm G

257.89 257. 892 2 P PS SIG 258.878 PSIG 259.162 PSIG

18.1556 Kg/cm G 2 18.225 Kg/cm G 2 18.245 Kg/cm G

Max. Operating Pressure Inte In terrna nall de desi sign gn pr pres essu sure re,, P (MAWP WP)) (a (att hi high ghes estt po poin intt of ve vess ssel el)) External design pressure, Pex

227.3 257 25 7 0

PSIG PSIG PS IG PSIG

Vessel ID Max. leg height = 12 + 12 + 503 + 2 + 165 Max. height of drain N4 = 12 + 12 + 502 + 2 + 165 + 200

61.2598 61.259 8 INC INCH H 27.322 27. 3228 8 INC INCH H 35.196 35. 1969 9 INC INCH H

Water sp. gr. o Fluid sp. gr.at 15 C

1 0.5

Max. hydrostatic head at internal bottom of vessel Max. hydrostatic head at bottom of leg Max. hydrostatic head at drain N4 Max ax.. pr pres essu surre fo forr ca calc lcul ulat atio ion n at in inte tern rnal al bo bott ttom om of ve vess ssel el Max. pressure for calculation at bottom of leg Max. pressure for calculation at outlet drain N4

2

2


Page : 7 of 126





F. Impact Test Requirements. Impact test is not mandatory for the following pressure vessels materials : I. Pressure Parts. a. Main Vessel Components : a. Shell : b Heads : c. Flanges : d. Nozzle Necks : e. Fittings, Tees :

ASME SA516 Grade 70 ASME SA516 Grade 70 ASME SA 105 ASME SA 106 Grade B ASME SA 234 Grade W PB

b. Stud Bolts & Nuts : f. Stud Boltshell g. Nuts

ASME SA 193 Grade B7 ASME SA 194 Grade 2H

II. Non-Pressure Parts. a. Saddle plate : b. Lifting lugs & Pads :

ASME SA516 Grade 70 ASME SA516 Grade 70

Thickness of vessel components : - Sh Shel elll & He Head ads s ASM AS ME SA SA51 516 6 Gra rade de 70 - Max. Nozzle Necks Thk. ASME SA 106 Grade B

[UG-22 & UG-98]

P-No. Group No. 1 2 1 2 1 2 1 1 1 1

UNS No. G41400

1 1

Curve D D B B B

[Size < 2-1/2"]

2 2

0.9 0. 9 INCH INCH 0.56181 0.5618 1 INC INCH H

D D

22 14.27

o

Where the MDMT is F 10 -12 in accordance with UG-20(f), UCS-66 and FIG. UCS-66, UCS-66, no impact test is required. Page : 97 of 126 Please refer pages from

MM MM

o

C

Impct Test is not required as per Code, but is required as a client request. G. Standard ASME Flange Rating Class. 1. Standard ASME B16.5 welded neck flanges shall be used. 2. For standard flange, Carbon Steel material in accordance with ASME SA105, P-No. 1, Group No. 2, and for MAWP 255.682 PSIG o F and Design temp. 149 The rating of flanges shall be 150# class, class, which satisfys the requirements of Table 2 of ASME B16.5-1996. 3. As a client request, the rating shall be 300#

18 65

Kg/CM2G o

C

DESIGN CALCULATIONS CALCULATIONS OF PRESSURE VESSEL According to ASME Code, Section VIII , Division 1, Edition 2001, Addenda 2002 Designed by : Eng. Abdel Halim Galala , Design General Manager (assist.)

Page : 8 of 126 Sheet : 1 of 4 Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Job Nam e : Demineralization Pla nt Seri Serial al No. No. : 7434 7434-3 -333-UU-20 2006 06 Dwg. Dwg. No. No. : 7434 7434-3 -333-3A 3A,, Rev Rev. 1 3 Vessel Vess el : Deputani Deputanizer zer Reflux Receiv Receiver er Drum Item No. : 1-D-5 Capacity : 10.152 M

Date : 18.2.2004 Job No. : 7434-33 Cli Client ent : APRC PRC Type : Horizontal

H. Cylindrical Shell Thickness Under Internal Pressure

[UG-27(c)]

Shell material, Killed Carbon Steel,

ASME SA516 Grade 70 Normalized & Notch Toughness Tested

Shell material S pecifications pecifications [Table 1A, Suppart 1, ASME Sec. II, Part D] P-No. Group No. External Pressure Chart No.

1 2 CS-2

Vessel Inside Diameter, D Shell Inside Diameter, D Shell Inside Radius, Ri Shell length from Tangent-to-Tangent Tangent-to-Tangent (T/T), L

61.2598 61.2598 61.2598 61. 2598 30.6299 30. 6299 189.764 189. 764

INCH INCH INCH IN CH INCH IN CH INCH IN CH

1556 1556 778 4820

MM MM MM MM

Max. Design Temperature Min. Design Metal Temperature, MDMT Max. Operating Temperature

149 10 122

o

65 -12 50

o

Max. Operating Pressure Max. Internal Design Pressure, P (MAWP) External Design Pressure (Full Vacuum)

227.273 PSI 227.273 PSIG G 255.682 255. 682 PSI PSIG G 0 PSIG

16 18 0

Kg/CM2G

Shell Inside Diameter, D Shell Inside Radius, R Static Head = Vessel Diam eter Static Head Pressure (water head x sp. gr. 1.0) Internal Design Pressure at bottom of vessel,

61.26 30.63

MM MM M

2.216 PSIG 257.898 257. 898 PSI PSIG G

1556 778 1.556 0.156 18.156

Max. Allowable Allowable Stress @ Design Temp.(65 oC), S o Max. Allowable Allowable Stress @ Test Temp.(40 C), St

20000 20000

PSIG PSIG

1408 1408

Kg/CM2G

332.386 332. 386 PSI PSIG G

23.4

Kg/CM2G

383 83..523 PS PSIG

27

Kg/CM2G

0.236 0.85 15%

6

MM

Not Applicable

F o F o F

INCH INCH

C C o C o

Kg/CM2G Kg/CM2G

Kg/CM2G Kg/CM2G

Kg/CM2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Hydrostatic Test Pressure, Ph = 1.3 x MAWP x (St/S) Hydrostatic Test Pressure, Ph = 1.5 x MAWP x (St/S)

Corrosion Allowance, Allowance, C Joint Efficiency, E [Spot Radiography],

[UG-99(b)] [Client request]

[UG-25] [TABLE UW-12] [Table UCS-57]

INCH

DESIGN CALCULATIONS CALCULATIONS OF PRESSURE VESSEL

Page : 9 of 126

According to ASME Code, Section VIII , Division 1, Edition 2001, Addenda 2002 Designed by : Eng. Abdel Halim Galala , Design General Manager (assist.)


Project : Design & Procurement of ASME Pressure Vessel Job Name : Demineralization Plant Plant Seri Serial al No. No. : 7434 7434-3 -333-UU-20 2006 06 Dwg. Dwg. No. No. : 7434 7434-3 -333-3A 3A,, Rev Rev. 1 Vessel Vess el : Deputani Deputanizer zer Reflux Receiv Receiver er Drum Item No. : 1-D-5 Capacity : 10.152 M3

Date : 18.2.2004

H. Cylinderical Shell Thickness Under Internal Pressure (cont.)

Job No. : 7434-33

Cli Client ent : APRC PRC Type : Horizontal

[UG-27(c)]

Value of 0.385 SE [UG-27(c)(1)] Since P does not exceed 0.385 SE, SE, Use Thin Wall Eq uation: [1] Min. Wall Thickness for Longitudinal Joints, t1 = PR / (SE - 0.6P) [UG-27(c)(1)]

6545

PSIG

460.768

Kg/CM2G

0.469

INCH

11.913

MM

Value of 1.25 SE [UG-27(c)(1)] Since P does not exceed 1.25 SE, SE, Use Thin Wall Equation: [2] Min. Wall Thickness for Circumferential Joints, t2 = PR / (2SE + 0.4P) [UG-27(c)(2)]

212 125 50

PSIIG PS

1496

Kg/CM2G

0.232

INCH

5.893

MM

The min. wall thickness shall be the greater of t1 or t2 By Adding Corrosion Allowance to Wall Tickness, t Use Thickness of Construction, Construction, t (Adopted thick ness) Corroded Thickness = Adopted thk. - Corrosion allowance

0.469 0.705 0.866 0.63

INCH INCH INCH INCH

11.913 17.907 22 16

MM MM MM MM

In c ase of using s hell f ab. f rom pipe '20" Pipe nominal thicknes s , t (Sc h.40)

0.472440945

INCH

12

MM

20" Pipe nominal thickness under tolerance tn = t - 0.125 t

0.472440945

INCH

12

MM

20" Pipe Corroded Thickness = tn - Corrosion allowance

0.236440945

INCH

6

MM

Using 20" pipe sch. 40 is

OK

0.458

INCH

11.633

MM

By using APPENDIX 1-1 (In terms of the Outside Diameter) :

tm = P Ro / (SE + 0.4 P)

Thickness adjusted for wall thickness tolerance :

0.523

INCH

13.284

MM

By Adding Corrosion Allowance to Wall Tickness, t

t = tm / (100%-12.5%)

0.759

INCH

19.284

MM

Using 20" pipe with commercial wall thickness, sch. 40 is

OK

Ladders and Platforms Vessel saddle supports Hot/cold Insulation Post Weld Heat Treatment, PWHT Impact Test Note. Impact test is required as a client request.

N.A. Yes Page : 90 of of 126 N.A. Not required per Co Page : 110 of of 126 Page : 7 of 126 Per Code


Page : 10 of 126




Date : 18.2.2004 Job No. : 7434-33


H. Check of Shell Thickness Under Internal Pressure [ For horizontal pressure vessels, with supplemental loading ] (vessel weight & hydrostatic liquid content) [APPENDIX L-2.2.2] Vessel OD 61.2598 INCH Vessel W all Thickness in the Corroded Condition, t 0.63 INCH Vessel I.D. in the Corroded Condition, 2R = OD - 2 t 59.9998 INCH Shell length from Tangent-to-Tangent Tangent-to-Tangent (T/T), L 189.764 INCH Shell Length from W.L.- to - W.L, L' 186.614 INCH

Joint Efficiency (Longitudinal (Longitudinal Seam s), E Joint Efficiency (Circumferential (Circumferential Seam s), E Weight of Vessel, W Weight of Contents, Wc Total Weight of Vessel and Co ntents, Wt Assume a Total no. of Saddles Reaction at each Saddle, Q Head (Cap) Depth - to - T.L, [Table 8, ASME B16.9-1993] Saddle - to - T.L., A Material to Chart for Compressive Stress,

0.85 0.85 16377. 163 77.3 3 lb 22383. 223 83.2 2 lb 38760. 387 60.5 5 lb 19380.3 19380. 3 lb 15.315 INCH 22.047 INCH

1600 16 1568 4820 4740

MM MM MM MM MM

7428 10152 17580 2 8790 389 560

Kg Kg Kg Kg MM MM

[ FIG.CS-2 CHART, SUBPART 3 , ASME SEC.II , PART D ]

Shell, Ro N.B. See vessel drawing layout,

* Here three cases must be investigated: Case 1. Circumferential Stress due to Internal Pressure, t = PR / ( SE-0.6 P) [UG-27C(1)] Longitudinal Tensile Strength d ue to Bending Case 2. Longitudinal ( at the m idpoint between the saddles) must be added to the longitudinal longitudinal Stress due to Internal Pressure.

31.4961 INCH 800 Page : 91 of 126

MM

0.465

MM

INCH

11.811

[ APPENDIX L-2.2.2]

t

0.238

N.B. Circumferential joint at center of vessel is the point of max. positive moment. Max. negative moment is at supports but there is no joint there.Other circum ferential joint must be investigated using moment at th e joint in calculating the compined stresses.

INCH

6.045

MM


Page : 11 of 126




Date : 18.2.2004 Job No. : 7434-33


H. Check of Shell Thickness Under Internal Pressure (cont.) [ For horizontal pressure vessels, with supplemental loading ] (vessel weight & hydrostatic liquid content) [APPENDIX [APPENDI X L-2.2.2] Case 3 . Longitudinal Compressive Stress due to Bending.

First determine the max. allowable compressive stress : Factor A = 0.125 / (Ro / t ) [UG-23(b)]

0.00344

Therefore, B

16000

[SUBPART 3 OF ASME SEC.II, PART D, FIG.CS-2]

PSIG

1126.4

Kg/CM2G

0.229

MM

NOTES:

1. No need to calculate the value of B by equation B = AE / 2 , since the value of A falls under the applicable Material/Temp. line. [ Suppart 3 of ASME Sec.II, Part D, Fig. CS-2]

2. The general equatioin for thickness thickness is the same as for longitudinal longitudinal tensile stress except the pressure por tion drops out since the most severe condition occurs when there is no pressure in the vessel . 3. The joint efficiency for butt-welded joints shall be taken as unity when investigating longitudinal compression. [UG-23(b)]

[ APPENDIX L-2.2.2]

Thickness ,

t

0.00902 0.0 0902 IN INCH CH


Page : 12 of 126

According to ASME Code, Section VIII , Division 1, Edition 2001, Addenda 2002 Designed by : Eng. Abdel Halim Galala, Galala , Design General Manager (assist.)



Date : 18.2.2004 Job No. : 7434-33


I. Check of Shell Thickness for External Pressure (Full Vacuum) Design Temperature For external pressure on cylinder, use UG-28 and Subpart 3. Determine the effective length of shell without stiffening rings, L

149

o

65

o

Shell length from Tangent-to-Tangent (T/T), L1 Internal Height of Elliptical Head 2:1, h = ID/4 Head Wall Thickness, th Internal Height of Ellipsoidal Head 2:1, ho = h + th Effective shell length without stiffening, L = L1 + 2/3 ho

189.764 15.315 0.7874 16.1024 200.499

INCH

4820 389 20 409 5092.667 5092.667

MM MM MM MM MM

Assume t for internal pressure (at corroded condition) Do = ID + 2 t L / Do Do / t

0.62992 INCH 62.7559 INCH 3.1949 99.625 > 10

16 1594

MM MM

Since Do/t > 10, use UG-28(c)(1) a. Enter Fig. G with L / Do and read across to sloping line of Do/t Read factor A

0.00038 387.2

Kg/CM G

73.6094 PSI

5.1821

Kg/CM G

15

1.056 OK 2024352 2055680

Kg/CM G

b. Enter Fig. CS-2 with A (to find factor B), which falls under the curve. Follow step (6) of UG-28(c)(1) UG-28(c)(1),, and calculate the value of max. allowable external working pressure, PA = 4B / 3 (Do / t) Change t untill PA > 15 PSI (full vacuum) E = Modulus of elasticity at design temp. at amp. temp. Notes. 1. For value of A falling to the left of the material-temp. line, the value of Pa can be calculated as follows : Pa = 2 A E / 3 (Do /t) 2. For L/Do > 50, use L/Do = 50 For L/Do < 0.05, use L/Do = 0.05 3. For Do/t > 10, For Do/t < 10,

use UG-28(c)(1) use UG-28(c)(2)

5500

F

INCH INCH INCH INCH

PSI

PSI

2.9E+07 PSI 2.9E+07 PSI

C

2

2 2

2

Kg/CM G 2

Kg/CM G


Page : 13 of 126




Date : 18.2.2004

J. Ellipsoidal Head Thickness Under Internal Pressure

Job No. : 7434-33


[UG-32(f)]

Head material, Carbon Steel Head type [Seamless] Head m aterial Specifications [Table 1A, Suppart 1, ASME Sec. II, Part D] P-No. Group No. External Pressure Chart No.

ASME SA516 Grade 70 Ellipsoidal Ellipsoi dal 2:1

Head ID Head OD Head Outside Radius

61.2598 IN 61.2598 INCH CH 62.9921 62. 9921 IN INCH CH 31.4961 31. 4961 IN INCH CH

[ASME B16.5-1996]

Design Temperature Min. Design Metal Temperature, MDMT Max. Allowable Allowable Work ing Pressure, MAWP Operating Pressure Internal Design Pressure, P Head Skirt Inside Diameter, D Head Inside Radius, L ( ri ) Max. Allowable Allowable Stress @ Design Temp.(60 oC), S o Max. Allowable Allowable Stress @ Test Temp.(40 C), St

1 2 CS-2 1556 1600 800

MM MM MM o

149 10 257.898 257. 898 227.273 227. 273 257.898 257. 898 61.26 30.63 20000 20000

o

PSIG PSIG

65 -12 18.156 16 18.156 1556 778 1408 1408

335. 33 5.27 27

PSIIG PS

23.603

Kg/CM2G

F o F PSIG PSI G PSIG PSI G PSIG PSI G INCH INCH

C C

o

Kg/CM2G Kg/CM2G Kg/CM2G

MM MM Kg/CM2G Kg/CM2G

[TABLE 1A , SUBPART 1 , ASME SEC. II , PART D]

Hydrostatic Test Pressure, Ph = 1.3*MAWP(St/S)

[UG-99(b)]

Corrosion Allowance, Allowance, C [UG-25] Joint Efficiency, E (Seamless & Full Radiography) Radiography) [TABLE UW-12]

0.23622 INCH 0.85

6

MM

Outside Diameter of Head, Do Outside Radius of Head, Ro

62.9921 INCH 31.4961 INCH

1600 800

MM MM

Value of 0.665 SE Since the value of 0.66SE > P, Use Thin Wall Equation for Calculating Calculating the Min. required Thickness of Head, t: t1 = PD / (2SE-0.2P) [UG-32(d)] (1)

113 130 05

795.872

KG/CM2G

PSIIG PS

0.46538 INCH

11.8205 11.82059 9 MM

113 130 05

795.872

Compare to Thickness of Seamless Spherical Shell :

Ps = 0.665 SE Since P < Ps, Calculate Thickness for thin Wall Spherical Shell: t2 = PRo/(2SE+0.8P) [APPENDIX 1-1] (2) For thin Wall ellipsoidal ellipsoidal 2:1 head : t = PD/(2SE-0.2P) [UG-32(d)]

PSIIG PS

KG/CM2G

0.23746 INCH

6.03158 6.031587 7 MM

0.46 0. 4653 538 8 INC NCH H

11.8 11 .820 2059 59 MM


Page : 14 of 126




Date : 18.2.2004

J. Ellipsoidal Head Thickness Under Internal Pressure (cont.)

Head Thickness due to Internal Pressure, t = MAX ( t1 , t2) By adding Corrosion Allowance to W all Thickness, Use Thickness of Construction, Construction, t (Adopted thick ness)

Job No. : 7434-33


[UG-32(f)]

0.46538 INCH 0.7016 INCH 0.787 INCH

11.8205 11.82059 9 MM 17.8205 17.82059 9 MM 20 MM

Corroded Thickness = Adopted thk. - Corrosion allowance

0.55118 INCH

14

In case of using '20" Cap nominal thickness, t (Sch. 40)

0.787401575

INCH

20

MM

20" Cap nominal thickness under tolerance tn = t - 0.125 t

0.787401575

INCH

20

MM

20" Cap Corroded Thickness = tn - Corrosion allowance

0.551181102

INCH

14

MM

Using 20" Cap sch. 80 is

OK

Required Head Thickness : Head tr = PD / (2SE - 0.2 P)

0.46538 INCH

11.8205 11.82059 9 MM

a. For Shell : MWP, New & cold (20 MM) P = SE t /(R + 0.6 t) [UG-27(c)(1)] MWP, Operating & corroded (14 MM) P = SE t /(R + 0.6 t)

472.622 PSIG 345.395 PSIG

33.273 24.316

b. For Head : MWP, New & cold (20 MM) P = 2SE t /(D + 0.2 t) [UG-32(d)(1)] MWP, Operating & corroded (14 MM), P = 2SE t /(D + 0.2 t)

435.675 PSIG 305.362 PSIG

30.67149 Kg/CM2G 21.49751 Kg/CM2G

[ t Represents the Min. Thickness after Forming Forming ]

MM

K. Maximum Working Pressure, MWP (New & Operating)

Kg/CM2G Kg/CM2G


Page : 15 of 126




Date : 18.2.2004 Job No. : 7434-33


L. Check of Ellipsoidal Head Thickness for External Pressure (Convex Side), (Full Vacuum) [UG-33(d)]

Assumed corroded thickness of head, t Outside diameter of the head skirt, Do The equivalent outside spherical, Ro = Ko Do [UG-33(b)] Outside height of the ellipsoidal head (measured from head-bend line), ho Ratio of the major to the minor axis of ellipsoidal head, Do/2ho

0.55118 62.3622 54.342 16.1024 1.93643

Factor depending on the ellipsoidal head proportions Do/2ho, Ko

0.87139

(use interpolatio interpolation) n)

INCH

14 1584 1380.288 1380.288 409

MM MM MM MM

PSI

668.8

Kg/CM G

INCH INCH INCH

[See Table UG-33.1]

The required thickness of an ellipsoidal head having pressure on the convex side, either seamless or of built-up construction with butt joints, shall not be less than that determined by the following procedure : Step 1. Assume a value for t and calculate the value of factor A using the following formula : A = 0.125 / (Ro / t)

0.00127

Step 2. Using the value of A calculate in Step 1, follow the same procedure as that given for spherical shells in UG-28(d) UG-28(d),, Step 2 through 6 : a. Enter Fig. CS-2 with A (to find factor B), which is under the curve, B Follow step (4) of UG-28(d) UG-28(d),, and calculate the value of max. allowable external working pressure, PA = B / (Ro / t) Change t untill PA > 15 PSI (full vacuum)

9500

96.3567 PSI 0

PSI

Notes. 1. For value of A falling to the left of the material-temp. line, the value of Pa can be calculated in accordance with with Step 5 of UG-28(d) UG-28(d),, as 2 follows : Pa = 0.0625 E / (Ro /t) E = Modulus of elasticity at design temp.

2.6E+07 PSI

2

2 6.783514 Kg/CM G

0 OK

2

Kg/CM G


Page : 16 of 126




Date : 18.2.2004 Job No. : 7434-33


M1. Nozzle Mark Mark : N11, 1-1/2"NPS, Sch. Sch. XXS, 300# WNRF(Located entirely within a centrally located circle of head's leg) No. of nozzles, n 1 (Cap 20" NPS, Sch. 30) [UG-27 & Appendix 1-1] Nozzle Neck Thickness Calculation Determine if the op ening and its reinforcement in the ellipsoidal head (cap) are located entirell entirelly y within a centrally located circle which has a diameter equal to 80% of the shell/l shell/leg eg diameter [see UG-37(a) & Appendix L-7.6]

0.8 x Shell/leg ID 2d

15.2 INCH 3.34488 INCH

386.08 84.96

MM MM

Therefore, the required head thickness for reinforcement calculations, tr are to be determined by the hemispherical head formula using a radius of K1D where K1 = 0.9 for 2:1 ellip[soi ellip[soidal dal head.

0.9

Nozzle Size, NPS Nozzle Material

1.5 40 INCH ASME SA 106 Grade B

DN

Design Pressure, P Design Temperature For nominated Design Pressure & Temperature, Flange Rating [Section G]

259.166 PSI 259.166 PSIG G o 149 F 300#

18.2453 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

0.95 INCH 1 0.23622 INCH

24.13

MM

6

MM

0.01431 INCH

0.36350 0.363508 8 MM

0.25053 INCH

6.36350 6.363508 8 MM

0.28185 INCH

7.15894 7.158947 7 MM

0.4

10.16

o

C

[ANSI/ASME [ANSI/AS ME B16.5-1996] o

Max. Allowable Allowable Stress of Nozzle Nozzle Material @ De sign Temp.(75 C), Sn Max. Allowable Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt

PSIG PSIG

Kg/CM2G


Outside Radius of Nozzle, Ron Joint Efficiency of Nozzle, En (Seamless Pipe) Nozzle Corrosion Allowance, Can Nozzle Thickness Calculation :

Longitudinal Longitudinal Stress, S tress, t = PRon /(Sn*En + 0.4 P) By adding Corro sion Allowance, Allowance, t

[APPENDIX 1.1] [UG-25]

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t Use Nozzle 1-1/2" NPS with Selected Neck Sch. XXS,

with Thickness Thickness 0.4" ( 10.15 MM ).

[Table 2 of ANSI B 36.10M-1985-(R-1994)]

INCH

MM


Page : 17 of 126




Date : 18.2.2004 Job No. : 7434-33


M1. Nozzle Nozzle Mark : N11 1-1/2 300# WNRF (cont.) Nozzle Opening Calculation With Reinforcing

[UG-27 & Appendix 1-1]

Nozzle Pipe Size, NPS Nozzle Pipe Sch. Design Pressure, P Design Temparture

1.5 INCH XXS 259.166 259. 166 PSI PSIG G o 149 F

Shell & Head Material Nozzle Material Reinforcing Pad Material Allowable Allowable Stress of Shell Material, Sv Allowable Allowable Stress of Nozzle Material, Sn Allowable Allowable Stress o f Pad Material, Sp

ASME SA516 Grade 70 ASME SA 106 Grade B ASME SA 106 Grade B 200 000 00 PSIIG PS 1408 171 710 00 PSIIG PS 1203.84 200 000 00 PSIIG PS 1408

Shell & Head Thickness Shell & Head Corrosion Allowance, Allowance, Cas Shell & Head Thickness Shell & Head Thickness less Corrosion Allowance

0.5 0.23622 0.2 3622 0.5 0.26378 0.2 6378

INCH INCH IN CH INCH INCH IN CH

12.7 6 12.7 6.7

MM MM MM MM


Reinforced Pad Thickness, te Joint Efficiency of Shell, E Joint Efficiency of Nozzle, En Correction Factor, F [UG-37(a)] E1 [Nozzle in solid plate] Shell & Head Outside Diameter, OD Shell & Head Inside Diameter in Corroded Condition, Condition, 2R = OD - 2 t Shell & Head Inside Radius in Corroded Condition, R

0.4 0.35 0.23622 0.2 3622 0.11378 0.1 1378 0.11378 0.1 1378 0.47244 1 1 1 1 20 19.4724 9.73622

INCH

10.16 8.89 6 2.89 2.89 12

MM MM MM MM MM MM

INCH INCH INCH

508 494.6 247.3

MM MM MM

Nozzle Outside Outside Diameter, OD Nozzle Inside Inside Diameter, ID Nozzle Projection beyond Inner Inner Vessel W all, h = m in. (h1,h2) h1 = 2.5 t h2 = 2.5 ti Nozzle ID ID Without Corrosion Allowance Allowance & 12.5% , d = OD - 2*tn Finished Finished Radius Ra dius of Circular Opening, Rn

1.9 1.1 0 0.65945 0.28445 1.67244 0.83622

INCH INCH INCH INCH INCH INCH INCH

48.26 27.94 0 16.75 7.225 42.48 21.24

MM MM MM MM MM MM MM

less Pipe Tolerance 12.5% (12.5% NA)

& 12.5%, t (12.5% NA)

Nozzle Wall Nom inal Thickness Thickness Nozzle Wall Thickness less Pipe Tolerance 12.5% Nozzle Corrosion Allowance, Can Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti

40

DN

18.24529 Kg/CM2G o 65 C



Page : 18 of 126




Date : 18.2.2004

M1. Nozzle Nozzle Mark : N11 1-1/2 300# WNRF (cont.) Nozzle Opening Calculation With Reinforcing (cont.) [UG-40(b)&FIG.UG-37.1] * Outside Diameter of Reinforced Pad Dp1 = 2 d Dp2 = 2 (Rn + nozzle wall wall thk., tn + vessel wall wall thk., t ) OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2

[UW-16(c)(2)&FIG.UW-16.1] Calculating Size of Fillet Welds : * For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)] Calculation Calculation of tm in. : tmin.1 = 0.75 inch tmin.2 (nozzle wall nominal thickness) tmin.3 (shell wall thickness) thickness ) tmin. = lesser of tm in.1, tmin. & tmin.3 Calculation Calculation of tc : tc1 = 0.25 inch tc2 = 0.7 tmin. tmin. tc = lesser of t c1 & tc2 By Considering Equal Legs Fillet Welds : Leg of Outward Outward Nozzle Weld = SQRT2 * tc Use Leg with Dimension E in Dwg. No. 7434-33-3A [FIG.UW-16 SKETCH (c)] * For Outer Reinforcing Pad Weld tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 ( shell wall thickness) tmin. = lesser of t min.1, t min. 2 & t min.3 1/2 tmin. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(t min./2) Use Leg with Dimension D in Dwg. No. 7434-33-3A [UG-27(c)(1)] * Wall Thickness Required : Head tr = PK PK1D / (2SE - 0.2 P) Nozzle trn = PRn /(SnEn - 0.6 P)

* Strength Reduction Factors : Sp / Sv fr1 = Sn / Sv fr2 = Sn / Sv fr3 = lesser of Sn/Sv or Sp/Sv fr4 = Sp / Sv

Job No. : 7434-33


[UG-27 & Appendix 1-1]

3.34488 INCH 2.42756 INCH 3.34488 INCH

84.96 61.66 84.96

MM MM MM

0.75 0.4 0.47244 0.4 0.25 0.28 0.25

19.05 10.16 12 10.16 6.35 7.112 6.35



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.47244 0.5 0.47244 0.23622

19.05 12 12.7 12 6

MM MM MM MM MM

0.33407 INCH 0.35433 INCH

8.5 9

MM MM

0.13742 INCH 0.01279 INCH

3.49034 3.490341 1 MM 0.32486 0.324866 6 MM

1 0.855 0.855 0.855 1

INCH INCH INCH INCH INCH


Page : 19 of 126




Date : 18.2.2004 Job No. : 7434-33


M1. Nozzle Nozzle Mark : N11 1-1/2 300# WNRF (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can

B*. Wall Thickness Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) Wall Thickness per UG-45(b)(1) UG-45(b)(1),, trnb1 = Min. (trn rnb1 b11 1, trn rnb1 b12 2) trnb11 = tr + Cas (tr for shell or head at E=1) trnb12 = Min Wall Thickness per UG-16(b) UG-16(b),, see below

Wall Thickness per UG-45(b)(2) UG-45(b)(2),, trnb2 (apply to ext external ernal pressu pressure re onl only), y),

0.24901 INCH

6.32486 6.324866 6 MM

0.32997 0.329 299 97 0.37364 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 9.49034 9.490341 1 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM

Wall Thickness per UG-45(b)(3) UG-45(b)(3),, trnb3 (apply to internal & external pressure) = Max. (trnb1, trnb2) 0.32997 INCH Wall Thickness per UG-45(b)(4) UG-45(b)(4),, trnb4 = Min. thickness of std. wall pipe (1-0.125)+ Can 0.3631 INCH

8.38 8.3812 125 5

MM MM MM MM

MM

9.22262 9.222625 5 MM

(Under tolerance12.5% in accordance with ASME B36.10M )

Nominal thickness of std. pipe wall thickness, NPS 1-1/2", 1-1/2", Sch. st 0.145 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) The nominal nozzle pipe wall thk. The min. nozzle nozzle thk. provided = t ( 1-0.125) So, the thickness provided meets the r ules of UG-45.

3.683

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH 0.4 INCH 0.35 INCH OK

8.38 8.3812 125 5 10.16 8.89

MM MM MM

Since there is no superimposed loads, the vessel doesn't req uire a calculationon shear shear stresses caused by UG-22(c) UG-22(c).. * Since the opening is access/inspection, UG-45(b) is not a pplicable [UG-45(b)[

INCH


Page : 20 of 126




Date : 18.2.2004

M1. Nozzle Nozzle Mark : N11 1-1/2 300# WNRF (cont.) Nozzle Opening Calculation With Reinforcing (cont.)

Job No. : 7434-33


[UG-27]

Area of Reinforcemen Reinforcementt (with (w ith Reinforcing Reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

0.23435 0.2 3435 IN INCH CH2

Area Available in Shell, A1: A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) A1 = The Greater of A11 or A12

0.20717 IN 0.20717 INCH CH 0.09125 0.0 9125 IN INCH CH2 0.20717 0.2 0717 IN INCH CH2

2

133.6563 133.6563 MM 58.8712 58.87124 4 MM2 133.6563 133.6563 MM2

Area Available in Nozzle Nozzle Proj ecting Outward, A2 : A21 = 5 (tn - trn) fr2 t A22 = 2 (tn - trn)(2.5tn+te) fr2 A2 = The Lesser of A21 or A22

0.11388 IN 0.11388 INCH CH2 2 0.13071 0.1 3071 IN INCH CH 2 0.11388 0.1 1388 IN INCH CH

73.4718 73.47186 6 MM2 2 84.3281 84.32815 5 MM 2 73.4718 73.47186 6 MM

Area Available in Inward Nozzle, A3 : (Not applicable) A31 = 5 t ti fr2 A32 = 5 ti ti fr2 A33 = 2 h ti fr2 A3 = The Greater of A31, A32 or A33

0.1283 0.12 83 0.05534 0.0 5534 0 0

Area Available in Outward Outward Nozzle W eld, A41: A41 = (LEG)2 fr3

2

MM2

2

2

82.7768 82.77683 3 35.7052 35.70523 3 0 0

MM 2 MM MM2 2 MM

0.10735 0.1 0735 IN INCH CH2

69.255

MM2

Area Available in Outer Reinforcing Reinforcing Pad Weld, A42: A42 = (LEG)2 fr4

0.12555 0.1 2555 IN INCH CH2

81

MM2

Area Available in Inward Inward Nozzle We ld, A43 : 2 A43 = (LEG) fr2

0.10735 0.1 0735 IN INCH CH

69.255

MM

Area Available in Reinforcing Reinforcing Pad, A5 : A5 = (Dp - d - 2tn) 2tn) te fr4

0.68262 0.6 8262 IN INCH CH2

440.4

MM2

Total Area Available, AT : AT = A1 + A2 + A41 + A43 + A5

1.34391 1.3 4391 IN INCH CH

AT is greater than A, therefore opening is adequately reinforced. NOTE. No need for Strength Path Calculations.

INC NCH H 2 INCH IN CH INCH2 2 INCH

151. 151.19 195 5

2

2

2

2

867.0381 867.0381 MM


Page : 21 of 126


Shee t : 1 of 5 Rev. : 1


Date : 18.2.2004 Job No. : 7434-33


M2. Nozzle Mark Mark : N8 24" NPS, Sch. 30, 300# 300# WNRF (Manhole (Manhole Located at Shell with Reinforcement) No. of nozzles, n 1 [UG-27(c) & Appendix 1-1] Nozzle Neck Thickness Calculation


24 INCH 600 ASME SA 106 Grade B

DN

Design Pressure, P Design Temperature For nominated Design Pressure & Temperature, Flange Rating

257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

12 INCH 1 0.23622 INCH

304.8

MM

6

MM

0.1799

INCH

4.56935 4.569353 3 MM

0.41612 INCH

10.5693 10.56935 5 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t

0.46813 INCH

11.8905 11.89052 2 MM

Use Nozzle 24" NPS with Selected Neck Sch. 30 30,, with Thickness Thickness 0.562 0.562"" (14.27 (14.27 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

0.562

INCH

14.2 14.274 748 8

MM

Nozzle Neck Maximum Working Pressure, MWP (New & Operating) Nozzle wall thickness less tolerance 12.5% Nozzle wall thickness less tolerance 12.5% - Corrosion allowance allowance MWP, New & cold (14.275 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] MWP, Operating & corroded (9.49 MM) P = Sn E t /(Ron - 0.4 t)

0.49175 0.25553 712.422 367.258

INCH INCH

MM MM

PSIG PSIG

12.4904 12.49045 5 6.49 6.4904 045 5 50.15448 25.85495

Nozzle Flange Maximum Working Pressure, MWP (New & Operating) MWP, New & cold, cold, 300# @ 100 oF [ASME B.165, Table 2] o MWP, Operating & corroded, 300# @ 149 F [ANSI B16.5, Table 2]

740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G

o

C

[ANSI/ASME [ANSI/ASM E B16.5-1996]

Max. Allowable Allowable Stress of Nozzle Nozzle Material @ De sign Temp.(75 oC), Sn o Max. Allowable Allowable Stress of Nozzle Materiall @ Test Temp.(40 C), Snt

PSIG PSIG

Kg/CM2G



Longitudinal Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) By adding Corro sion Allowance, Allowance, t


Kg/CM2G Kg/CM2G


Page : 22 of 126


Sheet : 2 of 5 Date : 18.2.2004


Client : APRC Job No. : 7434-33


M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.) Nozzle Opening Calculation With Reinforcing

[UG-27(c) & Appendix 1-1]


24 INCH 30 257.898 257. 898 PSI PSIG G o 149 F

Shell Material Nozzle Material Reinforcing Pad Material Allowable Allowable Stress of Shell Material, Sv Allowable Allowable Stress of Nozzle Material, Sn Allowable Allowable Stress o f Pad Material, Sp

ASME SA516 Grade 70 ASME SA 106 Grade B ASME SA516 Grade 70 200 000 00 PSIIG PS 1408 171 710 00 PSIIG PS 1203.84 20000 PSIG 1408

Shell Thickness Shell Corrosion Allowance, Cas Shell Thickness l Shell Thickness less Corrosion Allowance

0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.562 0.49175 0.4 9175 0.23622 0.2 3622 0.25553 0.2 5553 0.25553 0.2 5553 0.86614 1 1 1 1 62.9921 61.7323 30.8661

INCH INCH IN CH INCH IN CH INCH IN CH INCH IN CH INCH

14.2 14.274 748 8 12.4904 12.49045 5 6 6.49 6.4904 045 5 6.49045 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM


609.6 581.0504 581.0504 0 40 16.2261 16.22613 3 596.6191 596.6191 298.3096 298.3096


ess Pipe Tolerance 12.5% (12.5% NA)

& 12.5%, t (12.5% NA)


Reinforced Pad Thickness, te Joint Efficiency of Shell, E Joint Efficiency of Nozzle, En Correction Factor, F [UG-37(a)] E1 [Nozzle in solid plate] Shell Outside Diameter, OD Shell Inside Inside Diameter in Corroded Condition, 2R = OD - 2 t Shell Inside Radius in Corroded Condition, R Nozzle Outside Outside Diameter, OD Nozzle Inside Inside Diameter, ID Nozzle Projection beyond Inner Inner Vessel W all, h = m in. (h1,h2) h1 = 2.5 t h2 = 2.5 ti Nozzle ID Without Wi thout Corrosion Allowance & 12.5% , d = OD - 2*tn

Finished Finished Radius Ra dius of Circular Opening, Rn

24 22.876 0 1.5748 0.63882 23.4889 11.7445

600

DN

18.15602 Kg/CM2G o 65 C



Page : 23 of 126




Date : 18.2.2004 Job No. : 7434-33


M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.) Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1] * Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d Dp2 = 2 (Rn + nozzle wall wall thk. , tn + vessel wall wall thk. , t ) OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 [UW-16(c)(2)&FIG.UW-16.1] Calculating Siz of Fillet Welds : * For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)] Calculation Calculation of tm in. : tmin.1 = 0.75 inch tmin.2 (nozzle wall nominal thickness) tmin.3 (shell wall thickness) thickness ) tmin. = lesser of tm in.1, tmin. & tmin.3 Calculation Calculation of tc : tc1 = 0.25 inch tc2 = 0.7 t min. min. tc = lesser of tc1 & tc2 By Considering Equal Legs Fillet Welds : Leg of Outward Nozzle Nozzle Weld = SQRT2 * tc Use Leg with Dimension E in Dwg. No. 7434-33-3A [FIG.UW-16 SKETCH (c)] * For Outer Reinforcing Pad Weld tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 ( shell wall thickness) tmin. = lesser of tm in.1, tmin. 2 & tmin.3 1/2 tmin. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(tmin./2) Use Leg with Dimension D in Dwg. No. 7434-33-3A

* Wall Thickness Required : Shell Nozzle

46.9779 INCH 25.2598 INCH 46.9779 INCH

1193.23 1193.238 8 MM 641.6 MM 1193.23 1193.238 8 MM

0.75 0.562 0.47244 0.47244 0.25 0.33071 0.25

19.05 14.2 14.274 748 8 12 12 6.35 8.4 6.35



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.17874 INCH

12.0 12.002 029 9 MM 4.54011 4.540115 5 MM


[UG-27(c)(1)]

tr = PR / (SE - 0.6 P) trn = PRn /(SnEn - 0.6 P)


1 0.855 0.855 0.855 1


Page : 24 of 126




Date : 18.2.2004 Job No. : 7434-33


M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.41497 INCH

10.5401 10.54012 2 MM

0.29872 0.298 987 72 0.70878 0.29872

INCH INCH INCH INCH

7.5875 7.5875 18.0 18.002 029 9 7.5875

NA

INCH

#VAL #VALUE! UE! MM


7.5875

MM MM MM MM

MM

14.3343 14.33438 8 MM


Nominal thickness of std. pipe wall thickness, NPS 24", 24", Sch. Std. Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


0.375

9.525

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.29872 INCH

7.5875

MM

0.41497 INCH 0.562 INCH 0.49175 INCH OK

10.5401 10.54012 2 MM 14.2 14.274 748 8 MM 12.4904 12.49045 5 MM

Since there is no superimposed loads, the vessel doesn't req uire a calculationon shear shear stresses caused by UG-22(c) UG-22(c).. access/inspection,, UG-45(b) is not applicable * Since the opening is access/inspection

[UG-45(b)[

INCH


Page : 25 of 126




Date : 18.2.2004

M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.) Nozzle Opening Calculation With Reinforcing (cont.)

Job No. : 7434-33


[UG-27]

Area of Reinforcemen Reinforcementt (witht (w itht Reinforcing Reinforcing element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

11.1348 11. 1348 IN INCH CH2

7183.75 7183.753 3 MM2


3.6847 3.68 47 INC NCH H 0.26702 0.2 6702 IN INCH CH2 3.68 3. 6847 47 INC NCH H2

2

2377.22 2377.221 1 MM 172.2696 172.2696 MM2 2377.22 2377.221 1 MM2



133.4029 133.4029 MM2 2 127.4869 127.4869 MM 2 127.4869 127.4869 MM


0.68812 0.68812 0.27914 0.2 7914 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

2

443.9468 443.9468 180.0884 180.0884 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


19.9021 19. 9021 IN INCH CH2

12840.0 12840.04 4 MM2

Total Area Available, AT : AT = A1 + A2 + A41 + A42 + A43 + A5

24.3029 24. 3029 IN INCH CH

AT is greater than A, therefore ope ning is adequately reinforced. NOTE. No need for Strength Path Calculations.

INCH INCH 2 INCH IN CH INCH2 2 INCH

2

INC NCH H2

2

2

2

2

15679.2 15679.26 6 MM


Page : 26 of 126




Date : 18.2.2004 Job No. : 7434-33


M3. Nozzle Mark Mark : Leg 20"NPS, Sch. 30 (Leg Located at Shell with Reinforcement) Reinforcement) No. of nozzles, n 1 [UG-27(c) & Appendix 1-1] Nozzle Neck Thickness Calculation



DN


259.166 PSI 259.166 PSIG G o 149 F #VALUE!

18.24529 Kg/CM2G o 65 C

17100 17100

1203.84 1203.84

Kg/CM2G

10 INCH 1 0.23622 INCH

254

MM

6

MM

0.15065 INCH

3.82640 3.826403 3 MM

0.38687 INCH

9.82640 9.826403 3 MM


0.43522 INCH

11.0 11.054 547 7

MM

Use Nozzle 20" NPS with Selected Neck Sch. 30 30,,

0.5

INCH

12.7

MM

MM MM



PSIG PSIG

Kg/CM2G





36.10M-1985-(R-199 5-(R-1994)] 4)] with Thickness Thickness 0.5 0.5"" (12.7 (12.7 MM). [Table 2 of ANSI B 36.10M-198

A cap 20" NPS, Sch. 30, BW in accordance with ASME 16.9 shall be used for leg. Nozzle Neck Maximum Working Pressure, MWP (New & Operating) Nozzle wall thickness less tolerance 12.5% Nozzle wall thickness less tolerance 12.5% - Corrosion allowance allowance MWP, New & cold (12.7 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] MWP, Operating & corroded (8.11 MM) P = Sn E t /(Ron - 0.4 t)

0.4375 0.20128 761.45 346.982

INCH INCH

PSIG PSIG

11.1 11.112 125 5 5.1125 53.60611 24.42751


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G

Kg/CM2G Kg/CM2G


Page : 27 of 126




Date : 18.2.2004 Job No. : 7434-33


M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.) Nozzle Opening Calculation With Reinforcing

[UG-27(c) & Appendix 1-1]


20 INCH 30 257.898 257. 898 PSI PSIG G o 149 F



Shell Shell Shell Shell

0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.5 0.43 0. 4375 75 0.23622 0.2 3622 0.20128 0.2 0128 0.20128 0.2 0128 0.86614 1 1 1 1 62.9921 61.7323 30.8661

INCH INC NCH H INCH IN CH INCH IN CH INCH IN CH INCH

12.7 11.1 11.112 125 5 6 5.1125 5.1125 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM


508 482.6 0 40 12.7812 12.78125 5 497. 497.77 775 5 248.8875 248.8875


Thickness Corrosion Allowance, Cas Thickness Thickness less Corrosion Allowance less Pipe Tolerance 12.5% (12.5% NA)

& 12.5%, t (12.5% NA)




20 19 0 1.5748 0.5032 19.5974 9.79872

500

DN

18.15602 Kg/CM2G o 65 C



Page : 28 of 126




Date : 18.2.2004 Job No. : 7434-33


M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.) Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1] * Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d Dp2 = 2 (Rn + nozzle wall wall thk. , tn + vessel wall wall thk. , t ) OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 [UW-16(c)(2)&FIG.UW-16.1] Calculating Siz of Fillet Welds : * For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)] Calculation Calculation of tm in. : tmin.1 = 0.75 inch tmin.2 (nozzle wall nominal thickness) tmin.3 (shell wall thickness) thickness ) tmin. = lesser of tm in.1, tmin. & tmin.3 Calculation Calculation of tc : tc1 = 0.25 inch tc2 = 0.7 t min. min. tc = lesser of tc1 & tc2 By Considering Equal Legs Fillet Welds : Leg of Outward Nozzle Nozzle Weld = SQRT2 * tc Use Leg with Dimension E in Dwg. No. 7434-33-3A [FIG.UW-16 SKETCH (c)] * For Outer Reinforcing Pad Weld tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 ( shell wall thickness) tmin. = lesser of tm in.1, tmin. 2 & tmin.3 1/2 tmin. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(tmin./2) Use Leg with Dimension D in Dwg. No. 7434-33-3A


39.1949 INCH 21.2598 INCH 39.1949 INCH

995.55 540 995.55

MM MM MM

0.75 0.5 0.86614 0.5 0.25 0.35 0.25

19.05 12.7 22 12.7 6.35 8.89 6.35



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.14913 INCH

12.0 12.002 029 9 MM 3.78793 3.787937 7 MM


[UG-27(c)(1)]



1 0.855 0.855 0.855 1


Page : 29 of 126




Date : 18.2.2004 Job No. : 7434-33


M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.38535 INCH

9.78793 9.787937 7 MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM MM MM MM

MM

19.2016 19.20165 5 MM


Nominal thickness of std. pipe wall thickness, NPS 20", 20", Sch. 40 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


0.594

15.0 15.087 876 6

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.38535 INCH 0.5 INCH 0.4375 INCH OK

9.78793 9.787937 7 MM 12.7 MM 11.1 11.112 125 5 MM

Since there is no superimposed loads, the vessel doesn't req uire a calculationon shear shear stresses caused by UG-22(c) UG-22(c).. access/inspection,, UG-45(b) is not applicable * Since the opening is access/inspection

[UG-45(b)[

INCH


Page : 30 of 126




Date : 18.2.2004

M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.) Nozzle Opening Calculation With Reinforcing (cont.)

Job No. : 7434-33


[UG-27]

Area of Reinforcemen Reinforcementt (witht (w itht Reinforcing Reinforcing element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

9.28846 9.2 8846 IN INCH CH2

5992.54 5992.541 1 MM2



2

1983.72 1983.729 9 MM 162.8512 162.8512 MM2 1983.72 1983.729 9 MM2



90.6000 90.60008 8 MM2 2 78.7 78.779 796 6 MM 2 78.7 78.779 796 6 MM


0.54203 0.54203 0.17319 0.1 7319 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

2

349. 349.69 695 5 111.7385 111.7385 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


16.6255 16. 6255 IN INCH CH2

1072 10726. 6.1 1

MM2


20.3409 20. 3409 IN INCH CH

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.


2

INC NCH H2

2

2

2

2

13123.1 13123.12 2 MM


Page : 31 of 126




Date : 18.2.2004 Job No. : 7434-33


M4. Nozzle Mark Mark : N1 8"NPS, Sch. 80, 300# 300# WNRF (Located at Shell) No. of nozzles, n

1

Nozzle Neck Thickness Calculation Nozzle Size, NPS Nozzle Material


DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

[UG-45, UG-27 & APPENDIX 1-1]

o

C



PSIG PSIG

Kg/CM2G Kg/CM2G


Outside Radius of Nozzle, Ron Joint Efficiency of Nozzle, En (Seamless Pipe) Nozzle Corrosion Allowance, Can

4.3125 INCH 1 0.23622 INCH

109.5375 MM

0.06465 INCH

1.64211 1.642111 1 MM

0.30087 INCH

7.64211 7.642111 1 MM


0.33848 INCH

8.59737 8.597375 5 MM

Use Nozzle 8" NPS with Selected Neck Sch. 80 80,, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.5" ( 12.7 MM ).

0.5

INCH

12.7

MM


0.4375 0.20128 1808.16 813.301

INCH INCH

MM MM

PSIG PSIG

11.1 11.112 125 5 5.1125 127.2943 57.25639


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G

6

MM

Nozzle Thickness Calculation :



Kg/CM2G Kg/CM2G


Page : 32 of 126


Sheet : 2 of 5 Date : 18.2.2004


Client : APRC Job No. : 7434-33


M4. Nozzle Mark : N1 8" 300# WNRF (located at shel shell) l) (cont.) Nozzle Opening Calculation With Reinforcing Nozzle Pipe Size, NPS Nozzle Pipe Sch. Design Pressure, P Design Temparture

8 INCH 80 257.898 257. 898 PSI PSIG G o 149 F




0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.5 0.43 0. 4375 75 0.23622 0.2 3622 0.20128 0.2 0128 0.20128 0.2 0128 0.86614 1 1 1 1 62.9921 61.7323 30.8661

INCH INC NCH H INCH IN CH INCH IN CH INCH IN CH INCH

12.7 11.1 11.112 125 5 6 5.1125 5.1125 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM


219. 219.07 075 5 193. 193.67 675 5 0 40 12.7812 12.78125 5 208.85 104. 104.42 425 5



& 12.5%, t (12.5% NA)




[UG-27(c) & APPENDIX 1-1]

8.625 7.625 0 1.5748 0.5032 8.22244 4.11122

200

DN

18.15602 Kg/CM2G o 65 C



Page : 33 of 126




Date : 18.2.2004 Job No. : 7434-33


M4. Nozzle Mark : N1 8" 300# WNRF (located at shel shell) l) (cont.) Nozzle Opening Calculation With Reinforcing (cont.)


[UG-40(b)&FIG.UG-37.1] * Outside Diameter of Reinforced Pad Dp1 = 2 d Dp2 = 2 (Rn + nozzle wall wall thk. , tn + vessel wall wall thk. , t ) OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2

16.4449 INCH 9.88484 INCH 16.4449 INCH

417.7 251. 251.07 075 5 417.7

MM MM MM

0.75 0.5 0.47244 0.47244 0.25 0.33071 0.25

19.05 12.7 12 12 6.35 8.4 6.35


[UW-16(c)(2)&FIG.UW-16.1] Calculating Size of Fillet Welds : * For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)] Calculation Calculation of tm in. : tmin.1 = 0.75 inch tmin.2 (nozzle wall nominal thickness) tmin.3 (shell wall thickness) thickness ) tmin. = lesser of tm in.1, tmin. & tmin.3 Calculation Calculation of tc : tc1 = 0.25 inch tc2 = 0.7 t min. min. tc = lesser of tc1 & tc2 By Considering Equal Legs Fillet Welds : Leg of Outward Nozzle Nozzle Weld = SQRT2 * tc Use Leg with Dimension E in Dwg. No. 7434-33-3A [FIG.UW-16 SKETCH (c)] * For Outer Reinforcing Pad Weld tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 ( shell wall thickness) tmin. = lesser of tm in.1, tmin. 2 & tmin.3 1/2 t min. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(tmin./2) Use Leg with Dimension D in Dwg. No. 7434-33-3A



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.06257 INCH

12.0 12.002 029 9 MM 1.58929 1.589294 4 MM


[UG-27(c)(1)]



1 0.855 0.855 0.855 1


Page : 34 of 126




Date : 18.2.2004 Job No. : 7434-33


M4. Nozzle Mark : N1 8" 300# WNRF (located at shel shell) l) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) Wall Thickness per UG-45(b)(1) UG-45(b)(1),, trnb1 = Min. (trn rnb1 b11 1, trn rnb1 b12 2) trnb11 = tr + Cas (tr for shell or head at E=1) trnb12 = Min Wall Thickness per UG-16(b) UG-16(b),, see below


0.29879 INCH

7.58929 7.589294 4 MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM MM MM MM

MM

13.1564 13.15645 5 MM


Nominal thickness of std. pipe wall thickness, NPS 8", 8", Sch. Std. 0.322 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) The nominal nozzle pipe wall thk. The min. nozzle nozzle thk. provided = t ( 1-0.125) So, the thickness provided meets the r ules of UG-45. Since there is no superimposed loads, the vessel doesn't req uire a calculationon shear shear stresses caused by UG-22(c) UG-22(c)..

INCH

8.1788

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH 0.5 INCH 0.4375 INCH OK

8.38 8.3812 125 5 12.7 11.1 11.112 125 5

MM MM MM


Page : 35 of 126




Date : 18.2.2004

M4. Nozzle Mark : N1 8" 300# WNRF (located at shel shell) l) (cont.) Nozzle Opening Calculation With Reinforcing (cont.)

Job No. : 7434-33


[UG-27]

Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

3.91314 3.9 1314 IN INCH CH2

2524.60 2524.602 2 MM2



2

828.8676 828.8676 MM 162.8512 162.8512 MM2 828.8676 828.8676 MM2


0.37353 INCH 0.37353 INCH2 2 0.32 0. 3248 48 INC NCH H 2 0.32 0. 3248 48 INC NCH H

240.9873 240.9873 MM2 2 209. 209.54 546 6 MM 2 209. 209.54 546 6 MM


0.54203 0.54203 0.17319 0.1 7319 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

2

349. 349.69 695 5 111.7385 111.7385 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


6.77313 6.7 7313 IN INCH CH2

4369 4369.7 .75 5

MM2


8.90116 8.9 0116 IN INCH CH



2

INC NCH H2

2

2

2

2

5742.67 5742.674 4 MM

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 36 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)


Project : Design & Procurement Procurement of Pressure Vessel Vessel Job Name : Demineralization Demineralization Plant Sheet : 5 Serial No. : 7434-3 -33 3-U -U--2006 Dwg wg.. No. : 7434-33-3 -3A A, Rev. : 1 3 Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M

Date : 18.2.2004 Job No. : 7434-33 Client : APRC Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) Flange Material, [Attached by Bolts] Design Temperature (shell side) Min. Design Metal Temperature, MDMT Bolt-up and Gasket Seating Temperature Assume corrosion, C [UG-25] Operating Pressure Internal Design Pressure, P (MAWP) Allowable Stress of Bolt Material, SB :

[Appendix 2] [FIG. 2-4, Sketch (7)]

ASME SA 105 o F 149 o F 10 o 86 F 0.19685 INCH 227.27 227 .273 3 PS PSIG IG 255.68 255 .682 2 PS PSIG IG

Subjected to internal press.

65 -12 30 5 16 18

o

C C o C MM o

2

Kg/CM G 2

Kg/CM G 2

* at design temp.(operating temp.(operating condition), Sb * or at atmospheric temp./bolt-up temp. (gasket seating), Sa Allowable Stress of Flange Material : * at design temp.(operating condition), condition), SfH

25000 25000

PSIG PSIG

1760 1760

Kg/CM G

20000

PSIG

1408

Kg/CM G

* or at atmospheric temp./bolt-up temp. (gasket seating), SfC Allowable Stress of Nozzle neck, Vessel or Pipe wall Material : * at design temp.(operating condition), condition), SnH

20000

PSIG

1408

Kg/CM G

17100

PSIG

2 1203.84 Kg/CM G

17100

PSIG

2 1203.84 Kg/CM G

* or at atmospheric temp./bolt-up temp.(gasket seating), SnC

2

Kg/CM G 2 2

[Table 1A , SubPart 1 , ASME Sec. II , Part D]

Figure (1)

Nominal bolt dia., dB

No. of bolts

12 0.875

Bolt Hole, d Flange outside diameter, A Flange inside diameter, B Bolt circut diameter (B.C.D.), C = B + 2(g1 + h1+ R) [Appendix 2-3] Hup thickness at small end, go = Shell Thickness t

1 15 6.15591 13 0.43189


25.4 381 156.36 330.2 10.97

MM MM MM MM MM

Hup thickness at back of flange, g1 (assume g1 = 2 go) go )

0.86378

INCH

21.94

MM

[Appendix 2] FIG. 2-4, Sketch (7)

R must not less than 1.5 the bolt hole (see TEMA Table D-5)

Hup length, h (must greater than 1.5 go)

[FIG. 2-4, Sketch 6]

Use max. slope 1:3, h = 3.5 g0

Slope angle, Y = arc Tan [ (g1-go)/h]

Fillet radius, r = 0.25 g1 [but not less than 3/16"(4.7625 MM)] [FIG. 2-4, Sketch 6, Note a]

Use r

h1 = r * Tan (45-Y/2)

E = (A-C)/2

(Check D292 )

1.5

INCH

38

MM

1. 295669291

I NCH

32.91

MM

2. 498031496

I NCH

63.45

MM

9. 80 90 154 45

D eg re e

0. 215944882

I NCH

5. 485

MM

0. 215944882

I NCH

5.485

MM

0. 181813441

I NCH

5

MM

1

INCH

25.4

MM


Page : 37 of 126



Project : Design & Procurement of Pressure Vessel Job Name : Demineralization Plant Sheet : 5 Serial No. : 7434-33 -33-U-U-2006 Dwg. wg. No. : 7434-33-3A -3A, Rev. : 1 Vessel Vessel : Deput Deputani anizer zer Reflux Reflux Rec Receiv eiver er Drum Drum Item Item : 1-D-5 1-D-5 Capac Capacity ity : 10.15 10.152 2 M3

Date : 18.2.2004 Job No. : 7434-33 Client : APRC Type Type : Horizo Horizonta ntall

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Attached by Bolts] Nominal pipe size Pipe Schedule No. of bolts Nominal bolt dia., dB Bolt diameter at root of thread Actual cross-sectional area of each bolt, Total actual cross-sectional area of bolts, Ab

Subjected to internal pressure 8" 60 12 0.875 0.75689

Diameter at location of gasket load reaction, G When bo is larger than 1/4", G = O.D.of gasket contact face - 2 b

N.B. When b > 1/4", the effective gasket seating width, b = 0.5*SQRT(b O)

[Table 2-5.2]

2

INCH

2

INCH

2

15 6.15591 13 0.125 10.2362 8.8189 0.70866


381 156.3 56.36 6 330.2 3.175 260 224 18


0.35433

INCH

9

MM

[Table 2-5.2 0.29763

INCH

7.5597 7.55976 6 MM

270.322 MM 2 3243.86 MM

[Table 2-5.1 3 [Table 2-5.1 10000 PSIG [Table 2-5.1 (1a); Column II

9.64096 [Appendix 2-3]

[Table 2-5.2]

INCH

MM MM

[Table 2-5.2]

Gasket Factor, m Min. Seating Stress, y Facing Sketch

N.B. When b <1/4", the effective gasket seating width, b =bo

22.22 2.225 5 19.22 9.225 5

INCH

0.419 5.028

[TEMA Table D-5]

Flange outside diameter, A Flange inside diameter, B Bolt circut diameter (B.C.D.), C Gasket Details: - Spiral-Wound metal, asbestos filled, stainless steel - Outside diameter = (B.C.D - d) - 2*13 - Inside diameter = O.D - 2N - Width, N Gasket Dimensions: [Table 2-5.2] Basic gasket seating width, bO = N/2 Since bo > 1/4 inch (6.35 MM), Effective gasket seating width, b = 0.5*SQRT(b O)


INCH

2

704

Kg/CM G

244.8 44.88 8

MM


Page : 38 of 126



Project : Design & Procurement of Pressure Vessel Job Name : Demineralization Plant Sheet : 5 Serial No. : 7434-33 -33-U-U-2006 Dwg. wg. No. : 7434-33-3A -3A, Rev. : 1 Vessel Vessel : Deput Deputani anizer zer Reflux Reflux Rec Receiv eiver er Drum Drum Item Item : 1-D-5 1-D-5 Capac Capacity ity : 10.15 10.152 2 M3 Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Attached by Bolts] 1. Bolt loading and size of bolts: [Appendix 2-5(c)] 2 (a) Total hydrostatic end force, H = 0.785 G P [Appendix 2-3] (b) Total joint-contact surface compression load, Hp =2b*3.14GmP

Date

: 18.2.2004

Job No. : 7434-33

Client : APRC Type Type : Horizo Horizonta ntall [Appendix 2] [FIG. 2-4, Sketch (7)]

Subjected to internal pressure

18655.6 18655. 6 13822. 138 22.1 1

lb lb

8462.07 8462.0 7 Kg 6269.6 626 9.63 3 Kg

32477.8 32477. 8 90099. 900 99.9 9

lb lb

14731.7 14731. 7 Kg 40868. 408 68.7 7 Kg

25000 25000

PSIG PSIG

1760 1760

[Appendix 2-3]

(c) Min. required bolt load for operating conditions, Wm1 = H + Hp Min. required bolt load for gasket seating, Wm2 = 3.14 b G y Allowable Bolt Stress at atmospheric atmospheric temp., Sa Allowable Bolt Stress at design temp., Sb

2

Kg/CM G 2

Kg/CM G

[Table 1A , SubPart 1 , ASME Sec. II , Part D]

(d) Total cross-sectional area of bolts at root of thread required for: - operating conditions, Am1 = Wm1 / Sb - Gasket seating, Am2 = Wm2 / Sa

1.29911 3.604

INCH 2 INCH

2

838.135 MM 2 2325.16 MM

2

2

[Appendix 2-3] Total required cross-sectional of bolts, Am = the greater of Am1 & Am2 2

Since the actual bolt area Ab = 18.58 inch , for 20 bolt, 1-1/4 in. dia. bolts, the bolts are adequately enough. (e) Flang design bolt load, W: - For operating conditions, Wo = Wm1 [Appendix 2-5(d)] [Appendix 2-5(d)] - For gasket seating, Wa = 0.5(Am + Ab) * Sa [Appendix 2-5(c)] 2. Total flange moment for design condition: Flange Loads: 2 Hydrostatic end force on area inside flange, HD = 0.785 B P

2

3.604 5.028

INCH 2 INCH

2325.16 MM 2 3243.86 MM

32477.8 32477. 8 1079 10 7900 00

lb lb

14731.7 14731. 7 Kg 48942. 489 42.7 7 Kg

7605.9 760 5.95 5

lb

3450

13822. 138 22.1 1

lb

6269.6 626 9.63 3 Kg

Kg

Gasket load (flange design bolt load - total hydrostatic end force),H force), HG

Gasket seating force

HG = Wm1 - H

Difference bet. total hydrostatic end force and the hydrostatic end force on area inside of flange,HT flange,HT

HT = H - HD

11049. 110 49.7 7

lb

5012.0 501 2.07 7 Kg

[Table 2-6]

2.11 2. 1137 37

INCH IN CH

53.688 53.6881 1 MM

hG = (C - G) / 2

[Table 2-6]

1.6795 1.6 7952 2

INCH IN CH

42.659 42.6598 8 MM

hT = (R' + g1 + hG) / 2

[Table 2-6]

2.1125 2.1 1256 6

INCH IN CH

53.658 53.6589 9 MM

1.6818 1.6 8181 1

INCH IN CH

42.718 42.7181 1 MM

Lever arms: hD = R' + 0.5 g1

Where R' = R + h1


Page : 39 of 126



Project : Design & Procurement of Pressure Vessel Job Name : Demineralization Plant Sheet : 5 Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, 7434-33-3A, Rev. : 1 Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3


Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Attached by Bolts] Flange Moments: Component of moment due to H D, MD = HD hD [Appendix 2- 160 16076. 76.7 7


lb-in lbin

185.22 185 .224 4 Kg-M Kg-M

Component of moment due to H G, MG = HG hG

[Appendix 2- 232 23214. 14.6 6

lb-in lbin

267.46 267 .461 1 Kg-M Kg-M

Component of moment due to H T, MT = HT hT

[Appendix 2- 233 23343. 43.1 1

lb-in lbin

268.94 268 .942 2 Kg-M Kg-M

62634.4 in.-l 62634.4 in.-lb b 5219.5 521 9.53 3 ftft-lb lb

721.62 721 .627 7 Kg-M Kg-M

1079 10 7900 00

lb

48942. 489 42.7 7 Kg

1.67952 1812 18 1220 20

INCH

lb-i lb -in n

42.659 42.6598 8 MM 2087.8 208 7.88 8 Kg-M Kg-M

1812 18 1220 20

lb-i lb -in n

2087.8 208 7.88 8 Kg-M Kg-M

181220

lb-in

2087.8 208 7.88 8 Kg-M Kg-M

15101. 151 01.7 7

ft-lb ftlb

Total moment acting upon the f lange, Mo Mo:: - For operating condition

Subjected to internal presure

[Appendix 2-6]

MO1 = MD + MG + MT

3. Total flange moment for bolt-up condition (Gasket condition): condition): [Appendix 2-6]

Flange Load:

HG = W A = 0.5 (Am + Ab) * Sa

Lever Arm., hG = (C - G) / 2 Flange Moment for gasket condition, MO2 = HG hG = WA (C - G) / 2

(5)

Mo2 * (SfH / SfC ) 4. MO = The greater of MO1 or MO2 (SfH/SfC) 5. Shape constants for flange: K

A

=

From Appendix 2, FIG. 2-7.1: T

Z

Y

=

−

(1.0 4 7 2 0

K2

+1

K2

−

+

2

1.9 4 4 8k )( k − 1)

1.3584 1.40507

1

 K L og og10 K  68 45 45 + 5.7 1 69 69 0  0.6 68  2 K − 1  2

1

K

2 K (1 + 8.5 5 2 4 6 L og10 k ) − 1

=

=

2.43668

B

1

2.31617

2

U

From Appendix 2, FIG. 2-7.2: From Appendix 2, FIG. 2-7.3: From Appendix 2, FIG. 2-7.6: 2

d = (U/V) ho go e = F / ho

=

52 4 6 L o g K (1 + 8.5 52 K)− 1 10 2 1.3 6 1 3 6( K − 1) ( K − 1)

g1/go ho = SQRT(B go) h/ho F V f

(for integral type flanges) [APPENDIX 2-3] (for integral type flanges) [APPENDIX 2-3]

2.54524 2 1.63054 1.53202 0.69863 0.12928 1 5.9877 0.42847

3

INCH

-1

INCH

3

98120.8 MM -1 0.01687 MM


Page : 40 of 126





Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.)


Subjected to internal pressure

[Attached by Bolts]

6. Calculation of flange actual stresses Assume t Fact Factor or L

=

te

+

1

T

+

t^3 d

[Appendix 2-3]

Where t = flange thickness factor e = F/ ho (for integral type flanges) e = FL/ ho (for loose type flanges) F = factor for integral integral type flanges flanges T = factor involving K 2 d = (U/V) ho go

[Appendix 2-3] [Appendix 2-3] [Fig. 2-7.2] [Fig. 2-7.1] [Appendix 2-3]

1.42126 1.4212 6 1.66392

INCH IN CH

0.42847 NA 0.69863 1.3584 5.9877

INCH

For integral type flange, actual stresses (calculated) : [Fig. 2-4, Sketch (6a)] 2 1. a. Longitudinal hub stress, operating SH = f Mo / L g 1 B (6) [Appendix 2- 237 23712. 12.4 4 2 b. Longitudinal hub stress, seating SH = f Mo2 / L g 1 B (6) [Appendix 2- 23712.4 2

2. a. Radial flange stress, operating SR = (1.33 t e +1) Mo / L t B (7) [Appen 15869. 15869.9 9 2 b. Radial flange stress, seating SR = (1.33 t e +1) Mo2 / L t B (7) [Appen 158 15869. 69.9 9 2

3. a. Tangential flange stress, operating ST = (Y Mo / t B) - Z SR (8) [Appendi 114 11456. 56.6 6 b. Tangential flange stress, seating

2

ST = (Y Mo2 / t B) - Z SR (8) [Append 114 11456. 56.6 6

36.1

MM

-1

-1

0.01687 MM

INCH

3

98120.8 MM

PSIG PS IG

2 1669.35 Kg/CM G

PSIG

1669.35 Kg/CM G

PSIG PS IG

2 1117.24 Kg/CM G

PSIG PS IG

2 1117.24 Kg/CM G

PSIG PS IG

2 806.545 Kg/CM G

PSIG PS IG

2 806.545 Kg/CM G

3

2

4. a. Flange stress, operating

0.5 (SH + SR)

[Appendix 2-8(a)(4)]

19791. 197 91.1 1

PSIG PS IG

1393.3

Kg/CM G

b. Flange stress, seating

0.5 (SH + SR)


19791. 197 91.1 1

PSIG PS IG

1393.3

Kg/CM G

5. a. Flange stress, operating

0.5 (SH + ST)


17584. 175 84.5 5

PSIG PS IG

2 1237.95 Kg/CM G

b. Flange stress, seating

0.5 (SH + ST)


17584. 175 84.5 5

PSIG PS IG

2 1237.95 Kg/CM G

6459.39 6459.3 9 17919. 179 19.6 6 0

PSIG PSIG PSIG PS IG PSIG

454.741 Kg/CM2G 1261.54 Kg/CM2G 2 Kg/CM G 0

7. Actual Stresses (Calculated (Calculated)) Compared with Allowable Stresses [APPENDIX 2-8] 7.a. For Operating Condition : Allowable design stress of flange at operating condiotion, Sf 20000 PSIG Allowable design stress of nozzle/vessel at operating condition, condition, Sn 17100 PSIG Assume flange thickness (without C.A), toperating 1.42126 INCH

2 Kg/CM G 1408 1203.84 Kg/CM2G 36.1 MM

6. a. Bolt stress, operating = Wm1 / Ab b. Bolt stress, seating = Wm2 / Ab 7. a. Shear stress carried by the fillet weld

Allowable stresses PSIG

Longitudinal Hub Stress SH1 = 1.5 Sf

[Appendix 2-8(a)(1)(b)]

30000

Longitudinal Hub Stress SH2 = 2 Sn


34200

The calculated (actual) hub stress SH < SH (min.) allowable Radial Flange Stress SR = Sf


The calculated (actual) radial stress SR < SR allowable

Kg/CM2

2

Actual stresses (Calculated ) Kg/CM2 PSIG

30000

>

23712.4

20000

>

15869.9


Page : 41 of 126





Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) Tangential Flange Stress ST = Sf



20000

Subjected to internal pressure > 11456.6

20000

>

19791.1

20000

>

17584.5

25000

>

6459.39

20000 17100 1.42126

PSIG PSIG

2 Kg/CM G 1408 1203.84 Kg/CM2G 36.1 MM

The calculated (actual) tangential stress ST < ST allowable

0.5(SH + SR) = Sf The calculated (actual) stress

< Allowable stress 0.5(SH + ST) = Sf

The calculated (actual) stress Bolt stress = Wm1 / Ab

< Allowable stress

The calculated (actual) stress

< Allowable stress

7.b. For Gasket Seating : Allowable design stress of flange at gasket seating, Sf Allowable design stress of nozzle/vessel at gasket seating, seating, Sn

Assume flange thickness (without C.A), tgasket

INCH Allowable stresses

PSIG

Longitudinal Hub Stress SH1 = 1.5 Sf

2

Kg/CM

Actual stresses (Calculated ) 2 Kg/CM PSIG

[Appendix 2-8(a)(1)(b)] 30000

Longitudinal Hub Stress SH2 = 2 Sn


The calculated (actual) hub stress SH < SH (min.) allowable Radial Flange Stress SR = Sf


34200 30000

>

23712.4

20000

>

15869.9

20000

>

11456.6

20000

>

19791.1

20000

>

17584.5

25000

>

17919.6

1.42126

INCH

36.1

The calculated (actual) radial stress SR < SR allowable Tangential Flange Stress ST = Sf


The calculated (actual) tangential stress ST < ST allowable

0.5(SH + SR) = Sf The calculated (actual) stress

< Allowable stress 0.5(SH + ST) = Sf

The calculated (actual) stress

< Allowable stress

Bolt stress = Wm2 / Ab The calculated (actual) stress

< Allowable stress

The min. flange thickness, t = Max. (t (toperating, tgasket)

MM


Page : 42 of 126



Project : Design & Procurement of Pressure Vessel Job Name : Demineralization Plant Sheet : 5 Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, 7434-33-3A, Rev. : 1 Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3




Subjected to internal pressure Since all actual stresses are less than the allowable stresses, stresses, the selection of t is adequate. If an optimum min. thicknessof flange is desired, calculations must be operated with a smaller value of t until one of the the actual stresses or stress combination is approximately approximately equal to to the allowable stress even though other actual stresses are less than the allowable stress for that actual stress. Flange thickness with C.A & RF = t + 2*corrosion all. + raised face

1.8149 1.8 1496 6

INCH IN CH

46.1

MM

Use flange thickness for construction

1.8503 1.8 5039 9

INCH IN CH

47

MM

BOLT SUMMARY Factor K = A/B Gasket width, N Total required cross-sectional area of bolts Actual bolt cross-sectional area, Ab Nominal bolt dia., dB

2.43668 0.7086 0.7 0866 6 3.604 5.028 0.875

INCH IN CH

18 2325.16 3243.86 22.22 2.225 5

MM 2 MM 2 MM MM

1. Actual Edge distance, E from drawing = 1/2 (A - C)

1

Min. Edge distance,E distance, E (for bolt size 0.75")

0.8125

Min. Edge distance, E (for bolt size 7/8")

[TEMA Table D-5]

M in. Edge distance, E (f o r bolt si ze 1")

1. 0625

Min. Edge distance, E (for bolt size 1-1/8")

Min. Edge distance, E (for bolt size 1-1/4")

0.93 0. 9375 75

[TEMA Table D-5]

2. Actual Bolt spacing, B from drawing

2

INCH

2

INCH INCH INCH

INCH IN CH I NCH

25.4 20.6375

MM MM

23.812 23.8125 5 MM 26.9875

MM

1. 125

I NCH

28.575

MM

1. 25

I NCH

31.75

MM

3.36465

Min. Bolt spacing, B (for bolt size 0.75")

INCH

1.75

INCH INCH

85.462 44.45

MM MM

M i n. B o lt s p ac i ng , B ( f o rb o tl s i ze 7 / 8" )

2 . 06 2 5

I N CH

52.3875

MM

M in. Bolt spaci ng, B (f or bo lt size 1")

2. 25

I NCH

57.15

MM

M in. Bolt spaci ng, B (f or bo lt size 1-1/8")

2. 5

I NCH

63.5

MM

INCH

71.4375 MM 106.336 MM 59.98 MM

[TEMA Table D-5] Min. Bolt spacing, B (for bolt size 1-1/4") 2.8125 Max. Recommended bolt spacing, Bmax = 2 dB + 6 t / (m + 0.5) [TEMA RCB 4.18645

3. Actual Radial distance, Rh from drawing = (C-B)/2-(g1+h1 (C-B)/2-(g1+ h1)) Min. Radial distance, Rh (for bolt size 0.75")

Min. Radial distance, Rh(for Rh(for bolt size 7/8")

M in. Radial di stance, Rh (f or bo lt size 1" )

[TEMA Table D-5]

Use construction flange thickness, including corrosion allowance [The same thickness for 8" 300# blind flange in accordance with ASME B16.5]

INCH INCH

1.125

INCH

28.575

1. 25

I NCH

31.75

1. 375

M in. Radial di stance, Rh (f or bo lt size 1-1/ 8")

Min. Radial distance, Rh (for bolt size 1-1/4")

2.36142

I NCH

MM

MM

34.925

MM

MM

1. 5

I NCH

38.1

1.75

INCH

44.45

MM

1.6181 1.6 1811 1

INCH IN CH

41.1

MM


Page : 43 of 126



Project : Design & Procurement of Pressure Vessel Job Name : Demineralization Plant Sheet : 5 Serial No. : 7434-3 -33 3-U -U--2006 Dwg wg.. No. : 7434-33-3 -3A A, Rev. : 1 Vessel Ves sel : Deput Deputani anizer zer Ref Reflux lux Rec Receiv eiver er Dru Drum m Item Ite m : 1-D 1-D-5 -5 Cap Capac acity ity : 10 10.15 .152 2 M3

Date : 18.2.2004 Job No. : 7434-33 Client : APRC Type Ty pe : Hor Horizo izonta ntall

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) FLANGE FACTORS (a) For Integral Flanges E6 F = 3 Factor F per Fig. 2-7.2 is then solved by C 1 / 4 (1 + A ) [

2.73

]


Subjected to internal pressure 0.69863

C

E4 2.73 1/ 4 [ ] (1 + A )3 C

Factor V per Fig. 2-7.3 is then solved by

V =

Factor f per Fig. 2-7.6 is then solved by

f = C36 / (1 + A)

0.12928

1

h/SQRT(BG 1.532023693

The values used in the above equations are solved using Eqs. (1) through (45) below based on the v alues g1, g0, h and h as defined by 2-3. When g1 = go, F = 0.908920, V = 0.550103, and f = 1; 1; thus Eqs. (1) through (45) need not be solved. (b) For Loose Hub Flanges Factor FL per Fig. 2-7.4 is solved by  1  2

C 1 8  F L

=

+

A  6 

+

 1  4

C 2 1 

+

11A 



+

84 

 C     2 .7 3 

1 / 4

 1  7 0

C 2 4  (1

+

A)

+

A

 

105

−

 1   4 0

−

A   72 

3

0.70076

C

1

Factor VL per Fig. 2-7.5 is solved by

V L

=

4

−

C24 5

 2.73     C 

−

3C 21 2

−

C 18

0.13057

1/ 4

(1 + A )

3

Factor f per Fig. 2-7.6 is set equal to 1. f=1 1 The values used in the above equations are solved using Eqs. (1) through (5), (7), (9), (10), (12), (14), (16), (18), (20), (23), and (26) below based on the values of g1, g0, h, and ho as defined by 2-3. go

0.43189

INCH IN

10.97

MM

g1

0.86378 2.49803 1.63 1. 6305 054 4 6.15591

IIN NCH INCH INCH IN CH INCH

21.94 63.45 41.4 41 .415 158 8 156.36

MM MM MM MM

h ho = SQRT(B go), Effective hub length B (1) (2) (3)

A = (g1/go) - 1 4 C = 43.68(h/ho) C1 = 1/3 + A/12

1 240.627 0.41667

(4)

C2 = 5/42 + 17 A / 336

0.16964

(5)

C3 = 1/210 + A/360

0.00754

(6)

C4 = 11/360 + 59 A/5040 + ( 1+3 A)/C

(7)

3

C5 = 1/90 + 5 A/1008 - (1+ A) /C

0.05889 -0.01718


Page : 44 of 126





Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) FLANGE FACTORS (CONT.) (8) C6 = 1/120 + 17 A/5040 +1 /C 2


Subjected to internal pressure 0.01586

3

(9)

C7 = 215/2772 + 51 A/1232 + (60/7 + 225 A/14 + 75A /7 + 5 A /2)/C 0.27628

(10)

C8 = 31/6930 + 128 A/45045 + (6/7 + 15 A/7 + 12A /7 + 5 A /11)/C

2

3

2

0.0288

3

(11)

C9 = 533/30240 + 653 A/73920 + (1/2 + 33 A/14 + 39 A /28 + 25 A /8 0.04536

(12)

C10 = 29/3780 + 3 A/704 - (1/2 + 33 A/14 + 81 A /28 + 13 A /12)/C

(13) (14)

C11 = 31/6048 + 1763 A/665280 + (1/2 + 6 A/7 + 15 A /28 + 5 A /42)/ 0.01614 2 3 C12 = 1/2925 + 71 A/300300 + (8/35 + 18 A /35 + 156 A /385 + 6 A / 0.0058

(15)

C13 = 761/831600 + 937 A/1663200 + (1/35 + 6 A /35 + 11 A /70 + 3 0.00314

(16)

C14 = 197/415800 197/415800 + 103 A/332640 - (1/35 + 6 A /35 + 17 A /70 + A / -0.00147

(17)

C15 = 233/831600 + 97 A/554400 + (1/35 + 3 A /35 + A /14 + 2 A /1 0.00131

(18)

C16 = C1C7C12 + C2C8C3 + C3C8C2 - (C3 C7 + C8 C1 + C2 C12)

2

3

2

-0.01646

3

2

2

3

2

2

2

3

2

0.00021

2

(19)

C17 = [C4C7C12 + C2C8C13 + C3C8C9 - (C13C7C3 + C8 C4 + C12C2C9)] / 0.0917

(20)

C18 = [C5C7C12 + C2C8C14 + C3C8C10 - (C14C7C3 + C8 C5 + C12C2C10) -0.02242

(21)

C19 = [C6C7C12 + C2C8C15 + C3C8C11 - (C15C7C3 + C8 C6 + C12C2C11) 0.01666

(22)

C20 = [C1C9C12 + C4C8C3 + C3C13C2 - (C3 C9 + C13C8 C1 + C12C4C2)] / 0.1323

(23)

C21 = [C1C10C12 + C5C8C3 + C3C14C2 - (C3 C10 + C14C8 C1 + C12C5C2)] -0.04642

(24)

C22 = [C1C11C12 + C6C8C3 + C3C15C2 - (C3 C11 + C15C8 C1 + C12C6C2)] 0.05587

(25)

C23 = [C1C7C13 + C2C9C3 + C4C8C2 - (C3C7C4 + C8C9 C1 + C2 C13)] / C -0.23441

(26)

C24 = [C1C7C14 + C2C10C3 + C5C8C2 - (C3C7C5 + C8C10 C1 + C2 C14)] / 0.00573

(27)

C25 = [C1C7C15 + C2C11C3 + C6C8C2 - (C3C7C6 + C8C11 C1 + C2 C15)] / -0.07383

(28)

C26 = - (C/4)

(29)

C27 = C20 - C17 - 5/12 + C 17C26

-0.63146

(30)

C28 = C22 - C19 - 1/12 + C 19C26

-0.0905

2 2

2

2 2

2

2 2

1/4

-2.78497

C29 = - (C/4)

1/2

-7.75608

(32)

C30 = - (C/4)

3/4

-21.6005

(33)

C31 = 3 A/2 - C 17 C30

3.4808

(34)

C32 = 1/2 - C 19 C30

0.85979

(35)

C33 = 0.5 C26C32 + C28C31C29 - (0.5 C30C28 + C32C27C29)

-3.94227

(36)

C34 = 1/12 + C 18 - C21 - C18C26

0.04488

(31)

3/4

(37)

C35 = - C18 (C/4)

0.48436

(38)

C36 = (C28C35C29 - C32C34C29)/C33

-0.16217

(39)

C37 = [0.5 C26C35 + C34C31C29 - (0.5 C30C34 + C35C27C29)] / C33

0.95722

(40)

E1 = C17C36 + C18 + C19C37

-0.02135

(41)

E2 = C20C36 + C21 + C22C37

-0.01439

(42)

E3 = C23C36 + C24 + C25C37

-0.02693

(43)

E4 = 1/4 + C 37/12 + C36/4 - E3/5 - 3E2/2 - E1

0.33755

(44)

E5 = E1 (1/2 + A/6) + E2(1/4 + 11A/84) + E3(1/70 + A/105)

-0.02036

(45)

E6 = E5 - C36(7/120 +A/36 + 3A/C) - 1/40 - A/72 - C37(1/60 +A/120 + 1/ -0.07117


Page : 45 of 126







Subjected to internal pressure APPENDIX 2-3 When B < 20 g1, g1, it will be optional for the designer to substitute B1 in the 2 formula stress SH = f * Mo /( L * g 1 * B). B). 20 * g1 B

17.2756 INCH 6.15591 INCH

B1 = B + g1 for loose & integral type flanges have f <1 ( the min. f permitted is 7.0196 7.01969 9 B1 = B + go for integral type flanges when f = > 1 6.58 6. 5878 78

INCH INCH INCH IN CH

438.8 156.3 56.36 6

MM MM

178.3 167.3 67.33 3

MM MM


Page : 46 of 126




Date : 18.2.2004 Job No. : 7434-33


M5. Nozzle Mark Mark : N1 6" NPS, Sch. 80 300# WNRF (Located at Blind Blind Flange of N1) No. of nozzles, n 1 NOZZLE NECK T HICKNESS CALCULATION Nozzle Size, NPS Nozzle Material


DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

PSIG PSIG

1203.84 1203.84

Kg/CM2G

3.3125 INCH 1 0.23622 INCH

84.1375

MM

6

MM

0.04966 INCH

1.26133 1.261332 2 MM

0.28588 INCH

7.26133 7.261332 2 MM


0.32161 INCH

8.16899 8.168998 8 MM

Use Nozzle 6" NPS with Selected Neck Sch. 80 80,, [Table 2 of ANSI B 36.10M-198 36.10M-1985-(R-199 5-(R-1994)] 4)] with Thickness Thickness 0.432 ( 10.97 MM ).

0.432

INCH

10.9 10.972 728 8

MM


0.378 0.14178 2044.67 744.652

INCH INCH

MM MM

PSIG PSIG

9.6012 3.6012 143.9444 52.42352

Nozzle Flange Maximum Working Pressure, MWP (New & Operating) o MWP, New & cold, cold, 300# @ 100 F [ASME B.165, Table 2] o MWP, Operating & corroded, 300# @ 149 F [ANSI B16.5, Table 2]

740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G

[UG-45 , UG-27 & APPENDI APPENDIX X 1-1]

o

C


Allowable Allowable Stress of Nozzle Material, Sn o Max. Allowable Allowable Stress of Nozzle Materiall @ Test Temp.(40 C), Snt

Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 47 of 126


Sheet : 2 of 4 Date : 18.2.2004


Client : APRC

M5. Nozzle Mark : N1 6" NPS 300# WNRF (located (located at Blin Blind d Flange Flange of Nozzle Opening Calculation Without Reinforcing Nozzle Pipe Size, NPS Nozzle Pipe Sch. Design Pressure, P Design Temparture

Job No. : 7434-33


N1) (cont.) [UG-27(c) & APPENDIX 1-1]

6 INCH 80 257.898 257. 898 PSI PSIG G o 149 F

150

18.15602 Kg/CM2G o 65 C

Shell Material Nozzle Material Blind Flkange Material Reinforcing Pad Material Allowable Allowable Stress of Shell Material, Allowable Allowable Stress of Nozzle Material, Sn Allowable Allowable Stress o f Pad Material, Sp Allowable Allowable Stress of Blind Flange Material, Sv (nozzl (nozzle e located at blind) Shell (Blind Flange Flange 8" 300#) Thickness Shell (Blind Flange 8" 300#) Corrosion Allowance, Allowance, Cas Shell (Blind Flange 8" 300#)Thickness less Tolerance Shell Thickness less Corrosion Allowance t

ASME SA516 Grade 70 ASME SA 106 Grade B ASME SA 105 N.A. 200 000 00 PSIIG PS 1408 171 710 00 PSIIG PS 1203.84 0 PSIG 0 20000 PSIG 1408 1.61811 1.6 1811 IN INCH CH 41.1 0.19685 0.1 9685 IN INCH CH 5 1.55811 1.5 5811 IN INCH CH 39.576 1.36126 1.3 6126 IN INCH CH 34.576

Nozzle Wall Nom inal Thickness Thickness Nozzle Wall Thickness less Pipe Tolerance 12.5% Nozzle Corrosion Allowance, Can

0.432 0.378 0.19685 0.1 9685 0.18115 0.1 8115 0.18115 0.1 8115 0 1 1 1 1 62.9921 60.2696 30.1348

& 12.5%,

(12.5% NA)

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti

Reinforced Pad Thickness, te Joint Efficiency of Shell, E Joint Efficiency of Nozzle, En Correction Factor, F [UG-37(a)] E1 [Nozzle in solid plate] Shell Outside Diameter, OD Shell Inside Inside Diameter in Corroded Condition, 2R = OD - 2 t Shell Inside Radius in Corroded Condition, R Nozzle Outside Outside Diameter, OD Nozzle Inside Inside Diameter, ID Nozzle Projection beyond Inner Inner Vessel W all, h = min. (h1,h2) (h1,h2) h1 = 2.5 t h2 = 2.5 ti Nozzle ID Without Wi thout Corrosion Allowance & 12.5% , d = OD - 2*tn


6.625 5.761 0.45287 3.40315 0.45287 6.2627 3.13135


DN

Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G

MM MM MM MM

INCH

10.9 10.972 728 8 9.6012 5 4.6012 4.6012 0

MM MM MM MM MM MM

INCH INCH INCH

1600 MM 1530.84 1530.848 8 MM 765. 765.42 424 4 MM


168. 168.27 275 5 146.3294 146.3294 11.503 86.44 11.503 159.0726 159.0726 79.5 79.536 363 3



Page : 48 of 126




Date : 18.2.2004 Job No. : 7434-33


M5. Nozzle Mark : N1 6" NPS 300# WNRF (located at Blind Blind Flange of N1) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d Dp2 = 2 (Rn + nozzle wall wall thk. , tn + vessel wall wall thk. , t ) OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 [UW-16(c)(2)&FIG.UW-16.1] Calculating Size of Fillet Welds : * For Outward Nozzle Weld 41 [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)] Calculation Calculation of tm in. : tmin.1 = 0.75 inch tmin.2 (nozzle wall nominal thickness) tmin.3 [shell (blind) wall thickness] thickness ] tmin. = lesser of tm in.1, tmin. & tmin.3 Calculation Calculation of tc : tc1 = 0.25 inch tc2 = 0.7 t min. min. tc = lesser of tc1 & tc2 By Considering Equal Legs Fillet Welds : Leg of Outward Nozzle Nozzle Weld = SQRT2 * tc Use Leg with Dimension E in Dwg. No. 7434-33-3A

* For Outer Reinforcing Pad Weld (NA) [FIG.UW-16 SKETCH (c)] tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 [shell (blind) wall thickness] thickness ] tmin. = lesser of tm in.1, tmin. 2 & tmin.3 1/2 t min. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(tmin./2) Use Leg with Dimension D in Dwg. No. 7434-33-3A

12.5254 INCH 9.34752 INCH 0 INCH

318.1452 318.1452 MM 237. 237.42 427 7 MM 0 MM

0.75 0.432 1.61811 0.432 0.25 0.3024 0.25

19.05 10.9 10.972 728 8 41.1 10.9 10.972 728 8 6.35 7.68 7.6809 096 6 6.35


0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0 1.61811 0 0


19.05 0 41.1 0 0

MM MM MM MM MM

0 0

INCH INCH

0 0

MM MM

[UG-27(c)(1)] * Wall Thickness Required : Shell (blind) tr Nozzle trn = PRn /(SnEn - 0.6 P)

1.3363 INCH 0.04766 INCH


0 0.855 0.855 0.855 0

See file T-109, Sheet 15 for design calculation


33.942 MM 1.21050 1.210501 1 MM


Page : 49 of 126




Date : 18.2.2004 Job No. : 7434-33


M5. Nozzle Mark : N1 6" NPS 300# WNRF (located at Blind Blind Flange of N1) (cont.) MIN. NOZZLE NECK WALL THICKNESS CHECK PER UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.24451 INCH

6.21050 6.210501 1 MM

0.2906 0.290 906 6 1.53315 0.2906

INCH INCH INCH INCH

7.38 7.3812 125 5 7.38 7.3812 125 5 38.942 7.38 7.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


MM MM MM MM

7.38 7.3812 125 5

MM

11.223

MM

7.112

MM

0.25935 INCH 0.44685 INCH

6.5875 11.35

MM MM

0.2906

INCH

7.38 7.3812 125 5

MM

0.2906

INCH

7.38 7.3812 125 5

MM

0.2906 0.432 0.378 OK

INCH INCH INCH

7.38 7.3812 125 5 10.9 10.972 728 8 9.6012

MM MM MM


Nominal thickness of std. p ipe wall thickness, NPS 6", Sch.Std. Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + C.A. II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + C.A. III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + C.A. Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


0.28

INCH


Page : 50 of 126




Date : 18.2.2004 Job No. : 7434-33


M6. Nozzle Nozzle Mark : N2 6" NPS, Sch. Sch. 80, 300# WNRF (located at shell) (cont.) No. of nozzles, n 1 NOZZLE NECK T HICKNESS CALCULATION Nozzle Size, NPS Nozzle Material


DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

PSIG PSIG

1203.84 1203.84

Kg/CM2G

3.3125 INCH 1 0.23622 INCH

84.1375

MM

6

MM

0.04966 INCH

1.26133 1.261332 2 MM

0.28588 INCH

7.26133 7.261332 2 MM


0.32161 INCH

8.16899 8.168998 8 MM


0.432

INCH

10.9 10.972 728 8

MM


0.378 0.14178 2044.67 744.652

INCH INCH

MM MM

PSIG PSIG

9.6012 3.6012 143.9444 52.42352


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G

[UG-45 , UG-27 & APPENDI APPENDIX X 1-1]

o

C



Kg/CM2G




[Appendix 1.1] [UG-25]

Kg/CM2G Kg/CM2G


Page : 51 of 126


Sheet : 2 of 5 Date : 18.2.2004


Client : APRC

M6. Nozzle Mark :

Job No. : 7434-33


N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing Nozzle Pipe Size, NPS Nozzle Pipe Sch. Design Pressure, P Design Temparture

80 257.898 257. 898 PSI PSIG G o 149 F




0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.432 0.378 0.23622 0.2 3622 0.14178 0.1 4178 0.14178 0.86614 1 1 1 1 62.9921 61.7323 30.8661

INCH INCH INCH IN CH INCH IN CH INCH INCH

10.9 10.972 728 8 9.6012 6 3.6012 3.6012 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM

6.625 5.761 0 1.5748 0.35445 6.34144 3.17072


168. 168.27 275 5 146.3294 146.3294 0 40 9.003 161.0726 161.0726 80.5 80.536 363 3



& 12.5%, t (12.5% NA)




[UG-27(c) & APPENDIX 1-1] [UG-45 , INCH 0

DN

18.15602 Kg/CM2G o 65 C



Page : 52 of 126




Date : 18.2.2004 Job No. : 7434-33


M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell shell)) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d Dp2 = 2 (Rn + nozzle wall wall thk. , tn + vessel wall wall thk. , t ) OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 CALCULATING SIZE OF FILLET WELDS :

12.6829 INCH 7.88484 INCH 12.6829 INCH

322.1452 322.1452 MM 200. 200.27 275 5 MM 322.1452 322.1452 MM

0.75 0.432 2.89259 0.432 0.25 0.3024 0.25

19.05 10.9 10.972 728 8 73.4718 73.47186 6 10.9 10.972 728 8 6.35 7.68 7.6809 096 6 6.35

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)] Calculation Calculation of tm in. : tmin.1 = 0.75 inch tmin.2 (nozzle wall nominal thickness) tmin.3 (shell wall thickness) thickness ) tmin. = lesser of tm in.1, tmin. & tmin.3 Calculation Calculation of tc : tc1 = 0.25 inch tc2 = 0.7 t min. min. tc = lesser of tc1 & tc2 By Considering Equal Legs Fillet Welds : Leg of Outward Nozzle Nozzle Weld = SQRT2 * tc Use Leg with Dimension E in DWG. No. 7434-33-3A * For Outer Reinforcing Pad Weld (Not Applicable)



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.04826 INCH

12.0 12.002 029 9 1.22 1.2257 572 2

MM MM

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 ( shell wall thickness) tmin. = lesser of tm in.1, tmin. 2 & tmin.3 1/2 t min. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(tmin./2) Use Leg with Dimension D in DWG. No. 7434-33-3A [UG-27(c)(1)] * Wall Thickness Required : Shell tr = PR / (SE - 0.6 P) Nozzle trn = PRn /(SnEn - 0.6 P) * Strength Reduction Factors : Sp / Sv fr1 = Sn / Sv fr2 = Sn / Sv fr3 = lesser of Sn/Sv or Sp/Sv fr4 = Sp / Sv

1 0.855 0.855 0.855 1



Page : 53 of 126




Date : 18.2.2004 Job No. : 7434-33


M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell shell)) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.28448 INCH

7.22 7.2257 572 2

MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

MM MM MM MM

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM

12.223

MM

7.112

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH 0.432 INCH 0.378 INCH OK

8.38 8.3812 125 5 10.9 10.972 728 8 9.6012

MM MM MM




INCH


Page : 54 of 126




Date : 18.2.2004 Job No. : 7434-33


M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell shell)) (cont.) [UG-27] Nozzle Opening Calculation With Reinforcing Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

3.01611 3.0 1611 IN INCH CH2

1945.87 1945.874 4 MM2



2

639.6485 639.6485 MM 152.5214 152.5214 MM2 639.6485 639.6485 MM2


0.25185 INCH 0.25185 INCH2 2 0.19 0. 1952 52 INC NCH H 2 0.19 0. 1952 52 INC NCH H

162.4828 162.4828 MM2 2 125.9364 125.9364 MM 2 125.9364 125.9364 MM


0.3818 0.38 18 0.08593 0.0 8593 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

2

246.3221 246.3221 55.4409 55.44094 4 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


5.24698 5.2 4698 IN INCH CH2

3385.14 3385.144 4 MM2

Total Area Available, AT : AT = A1 + A2 + A41 + A42 A42 + A43 + A5 A5

6.64833 6.6 4833 IN INCH CH



2

INC NCH H2

2

2

2

2

4289.23 4289.239 9 MM


Page : 55 of 126




Date : 18.2.2004 Job No. : 7434-33


M7. Nozzle Mark Mark : N9 4" NPS, Sch. 120, 120, 300# 300# WNRF (Located at Sh Shell) ell) No. of nozzles, n 1 Nozzle Neck Thickness Calculation Nozzle Size, NPS Nozzle Material


DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

2.25 INCH 1 0.23622 INCH

57.15

MM

6

MM

0.03373 INCH

0.85675 0.856754 4 MM

0.26995 INCH

6.85675 6.856754 4 MM


0.30369 INCH

7.71384 7.713848 8 MM


0.438

INCH

11.1 11.125 252 2

MM


0.38325 0.14703 3125.66 1147.42

INCH INCH

MM MM

PSIG PSIG

9.73 9.7345 455 5 3.73 3.7345 455 5 220.0466 80.77811


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



PSIG PSIG

Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 56 of 126


Sheet : 2 of 5 Date : 18.2.2004


Client : APRC

M7. Nozzle Mark :

Job No. : 7434-33


N9 4" NPS, Sch. 120, 300# WNRF (located at shell) (cont.)


4 INCH 120 257.898 257. 898 PSI PSIG G o 149 F




0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.438 0.38325 0.3 8325 0.23622 0.2 3622 0.14703 0.1 4703 0.14703 0.86614 1 1 1 1 62.9921 61.7323 30.8661

INCH INCH IN CH INCH IN CH INCH IN CH INCH INCH

11.1 11.125 252 2 9.73 9.7345 455 5 6 3.73 3.7345 455 5 3.73 3.7345 455 5 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM

4.5 3.624 0 1.5748 0.36757 4.20594 2.10297


114.3 92.0 92.049 496 6 0 40 9.33637 9.336375 5 106.8309 106.8309 53.4154 53.41545 5



& 12.5%, t (12.5% NA)





100

DN

18.15602 Kg/CM2G o 65 C



Page : 57 of 126




Date : 18.2.2004 Job No. : 7434-33


M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at s shell hell)) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


8.41188 INCH 5.75984 INCH 8.41188 INCH

213.6618 213.6618 MM 146.3 MM 213.6618 213.6618 MM

0.75 0.438 5.25208 0.438 0.25 0.3066 0.25

19.05 11.1 11.125 252 2 133.4029 133.4029 11.1 11.125 252 2 6.35 7.78 7.7876 764 4 6.35

[UW-16(c)(2)&FIG.UW-16.1]




0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.03201 INCH

12.0 12.002 029 9 MM 0.81295 0.812955 5 MM



1 0.855 0.855 0.855 1



Page : 58 of 126




Date : 18.2.2004 Job No. : 7434-33


M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at shell shell)) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.26823 INCH

6.81295 6.812955 5 MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM MM MM MM

MM

11.2673 11.26733 3 MM




INCH

6.0198

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH 0.438 INCH 0.38325 INCH OK

8.38 8.3812 125 5 11.1 11.125 252 2 9.73 9.7345 455 5

MM MM MM


Page : 59 of 126




Date : 18.2.2004 Job No. : 7434-33


M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at s shell hell)) (cont.) [UG-27] Nozzle Opening Calculation With Reinforcing Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

2.00769 2.0 0769 IN INCH CH2



2

422.6846 422.6846 MM 153.4329 153.4329 MM2 422.6846 422.6846 MM2



199.8371 199.8371 MM2 2 156.5542 156.5542 MM 2 156.5542 156.5542 MM


0.39594 0.39594 0.09242 0.0 9242 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

MM2

2

2

255.4432 255.4432 59.6228 59.62284 4 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


3.38824 3.3 8824 IN INCH CH2

2185 2185.9 .96 6

MM2


4.50076 4.5 0076 IN INCH CH



1295 1295.2 .28 8

INC NCH H2

2

2

2

2

2903.70 2903.708 8 MM


Page : 60 of 126




Date : 18.2.2004 Job No. : 7434-33


M8. Nozzle Nozzle Mark : N18 3" NPS, Sch. Sch. 160, 300# WNRF (Located at Shell) Shell) No. of nozzles, n 1 [For vessels not subject to rapid fl actuations in pressure, do not require reinforcem ent other than that inherent in the construction under the following c



DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

1.75 INCH 1 0.23622 INCH

44.45

MM

6

MM

0.02623 INCH

0.66636 0.666364 4 MM

0.26246 INCH

6.66636 6.666364 4 MM


0.29526 INCH

7.49 7.4996 966 6

MM

Use Nozzle 3" NPS with Selected Neck Sch. 160 160,, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.438" (11.125 MM).

0.438

INCH

11.1 11.125 252 2

MM


0.38325 0.14703 4104.45 1486.65

INCH INCH

MM MM

PSIG PSIG

9.73 9.7345 455 5 3.73 3.7345 455 5 288.9533 104.6602


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



PSIG PSIG

Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 61 of 126




Date : 18.2.2004

M8. Nozzle Mark :

Job No. : 7434-33


N18 3" NPS, Sch. 160, 300# WNRF (located at shell shell)) (cont.)


3 INCH 160 257.898 257. 898 PSI PSIG G o 149 F




0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.438 0.38325 0.3 8325 0.23622 0.2 3622 0.14703 0.1 4703 0.14703 0.86614 1 1 1 1 62.9921 61.7323 30.8661


11.1 11.125 252 2 9.73 9.7345 455 5 6 3.73 3.7345 455 5 3.73 3.7345 455 5 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM

3.5 2.624 0 1.5748 0.36757 3.20594 1.60297


88.9 66.6 66.649 496 6 0 40 9.33637 9.336375 5 81.4 81.430 309 9 40.7154 40.71545 5



& 12.5%, t (12.5% NA)





80

DN

18.15602 Kg/CM2G o 65 C



Page : 62 of 126




Date : 18.2.2004 Job No. : 7434-33


M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located (located at s shell hell)) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


6.41188 INCH 4.75984 INCH 6.41188 INCH

162.8618 162.8618 MM 120.9 MM 162.8618 162.8618 MM

0.75 0.438 5.25208 0.438 0.25 0.3066 0.25

19.05 11.1 11.125 252 2 133.4029 133.4029 11.1 11.125 252 2 6.35 7.78 7.7876 764 4 6.35

[UW-16(c)(2)&FIG.UW-16.1]




0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.0244 INCH

12.0 12.002 029 9 MM 0.61966 0.619668 8 MM



1 0.855 0.855 0.855 1



Page : 63 of 126




Date : 18.2.2004 Job No. : 7434-33


M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located (located at shell shell)) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.26062 INCH

6.61966 6.619668 8 MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


MM MM MM MM

8.38 8.3812 125 5

MM

10.8 10.800 006 6

MM

INCH

5.4864

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH 0.438 INCH 0.38325 INCH OK

8.38 8.3812 125 5 11.1 11.125 252 2 9.73 9.7345 455 5

MM MM MM





Page : 64 of 126




Date : 18.2.2004 Job No. : 7434-33


M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located (located at s shell hell)) (cont.) [UG-27] Nozzle Opening Calculation With Reinforcing Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

1.53513 1.5 3513 IN INCH CH2

990.4066 990.4066 MM2


0.4978 0.49 78 INC NCH H 0.23782 0.2 3782 IN INCH CH2 0.49 0. 4978 78 INC NCH H2

2

321.1583 321.1583 MM 153.4329 153.4329 MM2 321.1583 321.1583 MM2



213.0579 213.0579 MM2 2 166.9116 166.9116 MM 2 166.9116 166.9116 MM


0.39594 0.39594 0.09242 0.0 9242 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


0.10735 0.1 0735 IN INCH CH

applicable) e) Area Available in Reinforcing Reinforcing Pad, A5 : (Not applicabl A5 = (Dp - d - 2tn) 2tn) te fr4

2.52 2. 5221 21

INC NCH H2


3.49 3. 4933 33

INC NCH H


2


INC NCH H2

2

2

2

2

255.4432 255.4432 59.6228 59.62284 4 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

69.255

MM

1627 1627.1 .16 6

MM2

2

2

2253.73 2253.739 9 MM


Page : 65 of 126




Date : 18.2.2004 Job No. : 7434-33


M9. Nozzle Nozzle Mark : N3, N4 & N7 2" NPS, Sch.160, 300# WNRF (Located at Shell) Shell) No. of nozzles, n 3 [For vessels not subject to rapid fl actuations in pressure, do not require reinforcem ent other than that inherent in the construction under the following c



DN


258.324 PSI 258.324 PSIG G o 149 F 300#

18.186 65

Kg/CM2G

17100 17100

PSIG PSIG

1203.84 1203.84

Kg/CM2G

1.1875 INCH 1 0.23622 INCH

30.1625

MM

6

MM

0.01783 INCH

0.45291 0.452918 8 MM

0.25405 INCH

6.45291 6.452918 8 MM


0.28581 INCH

7.25953 7.259533 3 MM

Use Nozzle 2" NPS with Selected Neck Sch. 160 160,, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.344" (8.74 MM).

0.344

INCH

8.7376

MM


0.301 0.06478 4823.45 953.634

INCH INCH

MM MM

PSIG PSIG

7.6454 1.6454 339.5707 67.13583


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 66 of 126




Date : 18.2.2004

M9. Nozzle Mark :

Job No. : 7434-33


N3, N4 N4 & N7 2" NPS, Sch. Sch. 160, 300# WNRF (located (located at shel shell) l) (cont.)

Nozzle Opening Calculation Without Reinforcing Nozzle Pipe Size, NPS Nozzle Pipe Sch. Design Pressure, P Design Temparture

2 INCH 160 258.324 258. 324 PSI PSIG G o 149 F



Shell Thickness Shell Corrosion Allowance, Cas Shell Thickness l Shell Thickness less Corrosion Allowance

0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.344 0.301 0.19685 0.1 9685 0.10415 0.1 0415 0.10415 0.86614 1 1 1 1 62.9921 61.7323 30.8661


8.7376 7.6454 5 2.6454 2.6454 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM

2.375 1.687 0 1.5748 0.26037 2.1667 1.08335


60.325 42.8 42.849 498 8 0 40 6.6135 55.0 55.034 342 2 27.5 27.517 171 1


ess Pipe Tolerance 12.5% (12.5% NA)

& 12.5%, t (12.5% NA)





50

DN

18.18601 Kg/CM2G o 65 C



Page : 67 of 126




Date : 18.2.2004 Job No. : 7434-33


M9. Nozzle Mark : N3, N4 N4 & N7 2" NPS, Sch. Sch. 160, 300# WNRF (l (located ocated at shel shell) l) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


4.3334 INCH 3.63484 INCH 4.3334 INCH

110.0684 110.0684 MM 92.325 MM 110.0684 110.0684 MM

0.75 0.344 9.48769 0.344 0.25 0.2408 0.2408

19.05 8.7376 240.9873 240.9873 8.7376 6.35 6.11 6.1163 632 2 6.11 6.1163 632 2

[UW-16(c)(2)&FIG.UW-16.1]




0.34054 INCH 0.35433 INCH

8.64978 8.649783 3 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47334 INCH 0.01652 INCH

12.0229 12.02291 1 MM 0.41949 0.419494 4 MM



1 0.855 0.855 0.855 1



Page : 68 of 126




Date : 18.2.2004 Job No. : 7434-33


M9. Nozzle Mark : N3, N4 N4 & N7 2" NPS, Sch. Sch. 160, 300# WNRF (located (located at shel shell) l) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.21337 INCH

5.41949 5.419494 4 MM

0.2906 0.290 906 6 0.70956 0.2906

INCH INCH INCH INCH

7.38 7.3812 125 5 7.38 7.3812 125 5 18.0229 18.02291 1 7.38 7.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM

INCH

7.38 7.3812 125 5

MM

INCH

8.42 8.4226 265 5

MM

INCH

3.9116

MM

0.25935 INCH 0.44685 INCH

6.5875 11.35

MM MM

0.2906

INCH

7.38 7.3812 125 5

MM

0.2906

INCH

7.38 7.3812 125 5

MM

0.2906 0.344 0.301 OK

INCH INCH INCH

7.38 7.3812 125 5 8.7376 7.6454

MM MM MM

Wall Thickness per UG-45(b)(3) UG-45(b)(3),, trnb3 (apply to internal & external pressure) = Max. (trnb1, trnb2) 0.2906 Wall Thickness per UG-45(b)(4) UG-45(b)(4),, trnb4 = Min. thickness of std. wall pipe (1-0.125)+ Can 0.3316

MM MM MM MM





Page : 69 of 126




Date : 18.2.2004 Job No. : 7434-33


M9. Nozzle Mark : N3, N4 N4 & N7 2" NPS, Sch. Sch. 160, 300# WNRF (l (located ocated at shel shell) l) (cont.) [UG-27] Nozzle Opening Calculation Without Reinforcing Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

1.03989 1.0 3989 IN INCH CH2

670.8949 670.8949 MM2



2

215.8248 215.8248 MM 145.2577 145.2577 MM2 215.8248 215.8248 MM2



152. 152.25 252 2 MM2 2 108.9115 108.9115 MM 2 108.9115 108.9115 MM


0.28047 0.28047 0.04637 0.0 4637 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

2

180.9454 180.9454 29.9170 29.91705 5 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


1.69625 1.6 9625 IN INCH CH2

1094.35 1094.355 5 MM2


2.41429 2.4 1429 IN INCH CH



2

INC NCH H2

2

2

2

2

1557.60 1557.601 1 MM


Page : 70 of 126




Date : 18.2.2004 Job No. : 7434-33


M10. Nozzle Nozzle Mark : N6 & N17 1-1/2" NPS, NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located at Shell) Shell) No. of nozzles, n 2 [For vessels not subject to rapid fl actuations in pressure, do not require reinforcem ent other than that inherent in the construction under the following c


1.5 INCH 40 ASME SA 106 Grade B

DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

0.95 INCH 1 0.23622 INCH

24.13

MM

6

MM

0.01424 INCH

0.36 0.3617 174 4

MM

0.25046 INCH

6.36 6.3617 174 4

MM


0.28177 INCH

7.15695 7.156958 8 MM

Use Nozzle 1-1/2" NPS with Selected Neck Sch. XXS, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.4" (10.16 MM).

0.4

INCH

10.16

MM


0.35 0.11378 7388.89 2151.08

INCH INCH

MM MM

PSIG PSIG

8.89 2.89 520.1778 151.4363


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



PSIG PSIG

Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 71 of 126




Date : 18.2.2004

M10. Nozzle Mark :

Job No. : 7434-33


N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located (located at shel shell) l) (cont.)






0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.4 0.35 0.23622 0.2 3622 0.11378 0.1 1378 0.11378 0.86614 1 1 1 1 62.9921 61.7323 30.8661


10.16 8.89 6 2.89 2.89 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM

1.9 1.1 0 1.5748 0.28445 1.67244 0.83622


48.26 27.94 0 40 7.225 42.48 21.24



& 12.5%, t (12.5% NA)





40

DN

18.15602 KG/CM2G o 65 C

KG/CM2G KG/CM2G KG/CM2G


Page : 72 of 126




Date : 18.2.2004 Job No. : 7434-33


M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located (located at shel shell) l) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


3.34488 INCH 3.15984 INCH 3.34488 INCH

84.96 80.26 84.96

MM MM MM

0.75 0.4 19.7318 0.4 0.25 0.28 0.25

19.05 10.16 501.1874 501.1874 10.16 6.35 7.112 6.35


[UW-16(c)(2)&FIG.UW-16.1]



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.01273 INCH

12.0 12.002 029 9 MM 0.32326 0.323262 2 MM



1 0.855 0.855 0.855 1



Page : 73 of 126




Date : 18.2.2004 Job No. : 7434-33


M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located (located at shel shell) l) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.24895 INCH

6.32326 6.323262 2 MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM MM MM MM

MM

9.22262 9.222625 5 MM


Nominal thickness of std. pipe wall thickness, NPS 1-1/2" 1-1/2",, Sch. 0.145 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


3.683

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM


8.38 8.3812 125 5 10.16 8.89

MM MM MM

INCH


Page : 74 of 126




Date : 18.2.2004 Job No. : 7434-33


M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located (located at shel shell) l) (cont.) [UG-27] Nozzle Opening Calculation With Reinforcing Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

0.80591 0.8 0591 IN INCH CH2

519.9429 519.9429 MM2



2

166.4467 166.4467 MM 147.6604 147.6604 MM2 166.4467 166.4467 MM2



175.5649 175.5649 MM2 2 128.2721 128.2721 MM 2 128.2721 128.2721 MM


0.3064 0.30 64 0.05534 0.0 5534 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


2

2

197. 197.67 676 6 35.7052 35.70523 3 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

0.10735 0.1 0735 IN INCH CH

69.255

MM


1.25147 1.2 5147 IN INCH CH2

807.4

MM2


1.92298 1.9 2298 IN INCH CH



2

INC NCH H2

2

2

2

2

1240.62 1240.629 9 MM


Page : 75 of 126




Date : 18.2.2004 Job No. : 7434-33


M11. Nozzle Nozzle Mark : N16 1" NPS, Sch.XXS, Sch.XXS, 300# 300# WNRF (Pipin (Piping g branch from N4) No. of nozzles, n 1 [For vessels not subject to rapid fl actuations in pressure, do not require reinforcem ent other than that inherent in the construction under the following c



DN


258.324 PSI 258.324 PSIG G o 149 F 300#

18.186 65

Kg/CM2G

17100 17100

PSIG PSIG

1203.84 1203.84

Kg/CM2G

0.6575 INCH 1 0.23622 INCH

16.7005

MM

6

MM

0.00987 INCH

0.25077 0.250774 4 MM

0.24609 INCH

6.25077 6.250774 4 MM


0.27686 INCH

7.03 7.0321 212 2

MM

Use Nozzle 1" NPS with Selected Neck Sch. XXS, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.358" (9.093 MM).

0.358

INCH

9.0932

MM


0.31325 0.07703 10065 2101.85

INCH INCH

MM MM

PSIG PSIG

7.95 7.9565 655 5 1.95 1.9565 655 5 708.5736 147.9703


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 76 of 126




Date : 18.2.2004

M11. Nozzle Mark :

Job No. : 7434-33


N16 1" NPS, Sch. XXS, 300# WNRF (Piping (Piping branch from N4) (cont.)


1 INCH XXS 258.324 258. 324 PSI PSIG G o 149 F




0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.358 0.31325 0.3 1325 0.23622 0.2 3622 0.07703 0.0 7703 0.07703 0.86614 1 1 1 1 62.9921 61.7323 30.8661


9.0932 7.95 7.9565 655 5 6 1.95 1.9565 655 5 1.95 1.9565 655 5 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM

1.315 0.599 0 1.5748 0.19257 1.16094 0.58047


33.401 15.2 15.214 146 6 0 40 4.89137 4.891375 5 29.4 29.487 879 9 14.7439 14.74395 5



& 12.5%, t (12.5% NA)





25

DN

18.18601 Kg/CM2G o 65 C



Page : 77 of 126




Date : 18.2.2004 Job No. : 7434-33


M11. Nozzle Mark : N16 1" 1" NPS, Sch. XXS, 300# WNRF (Piping (Piping branch from N4) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


2.32188 INCH 2.57484 INCH 2.57484 INCH

58.9 58.975 758 8 65.401 65.401

MM MM MM

0.75 0.358 6.39696 0.358 0.25 0.2506 0.25

19.05 9.0932 162.4828 162.4828 9.0932 6.35 6.36 6.3652 524 4 6.35


[UW-16(c)(2)&FIG.UW-16.1]



0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47334 INCH 0.00885 INCH

12.0229 12.02291 1 MM 0.22476 0.224769 9 MM



1 0.855 0.855 0.855 1



Page : 78 of 126




Date : 18.2.2004 Job No. : 7434-33


M11. Nozzle Mark : N16 1" 1" NPS, Sch. XXS, 300# WNRF (Piping (Piping branch from N4) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.24507 INCH

6.22476 6.224769 9 MM

0.32997 0.329 299 97 0.70956 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0229 18.02291 1 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM MM MM MM

MM

8.95592 8.955925 5 MM


Nominal thickness of std. pipe wall thickness, NPS 1" 1",, Sch. Std. 0.133 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


INCH

3.3782

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH 0.358 INCH 0.31325 INCH OK

8.38 8.3812 125 5 9.0932 7.95 7.9565 655 5

MM MM MM


Page : 79 of 126


Sheet : 1 of 6

Project : Design & Procurement of ASME Pressure Vessel Job Nam e : Demineralization Pla nt Seri Serial al No. No. : 7434 7434-3 -333-UU-20 2006 06 Dwg. Dwg. No. No. : 7434 7434-3 -333-3A 3A,, Rev Rev. 1 Vessel Vess el : Deputani Deputanizer zer Reflux Receiv Receiver er Drum Item No. : 1-D-5 Capacity : 10.152 M3


Rev. : 1

M12. Nozzle Nozzle Mark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located at Head, F = 0.5) No. of nozzles, n 3 [For vessels not subject to rapid fl actuations in pressure, do not require reinforcem ent other than that inherent in the construction under the following c



DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

0.95 INCH 1 0.23622 INCH

24.13

MM

6

MM

0.01424 INCH

0.36 0.3617 174 4

MM

0.25046 INCH

6.36 6.3617 174 4

MM


0.28177 INCH

7.15695 7.156958 8 MM

Use Nozzle 1-1/2" NPS with Selected Neck Sch. XXS, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.4" (10.16 MM).

0.4

INCH

10.16

MM


0.35 0.11378 7388.89 2151.08

INCH INCH

MM MM

PSIG PSIG

8.89 2.89 520.1778 151.4363


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



PSIG PSIG

Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 80 of 126





M12. Nozzle Mark :

N5A, N5B & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located (located at shel shell) l) (cont.)






0.86614 0.86614 0.23622 0.2 3622 0.86614 0.8 6614 0.62992 0.6 2992


22 6 22 16

MM MM MM MM

0.4 0.35 0.23622 0.2 3622 0.11378 0.1 1378 0.11378 0.86614 1 1 1 1 62.9921 61.7323 30.8661

INCH INCH INCH IN CH INCH IN CH INCH

10.16 8.89 6 2.89 2.89 22

MM MM MM MM MM MM

INCH INCH INCH

1600 1568 784

MM MM MM


48.26 27.94 0 40 7.225 42.48 21.24



& 12.5%, t (12.5% NA)


Reinforced Pad Thickness, te Joint Efficiency of Shell, E Joint Efficiency of Nozzle, En Correction Factor, F [UG-37(a)] E1 [Nozzle in solid plate] Shell Outside Diameter, OD Shell Inside Inside Diameter in Corroded Condition, 2R = OD - 2 t Shell Inside Radius in Corroded Condition, R Nozzle Outside Outside Diameter, OD Nozzle Inside Inside Diameter, ID Nozzle Projection beyond Inner Inner Vessel W all, h = m in. (h1,h2) h1 = 2.5 t h2 = 2.5 ti Nozzle ID Without Wi thout Corrosion Allowance & 12.5% , d' = OD - 2*tn

Radius of Circular Opening, Rn


1.9 1.1 0 1.5748 0.28445 1.67244 0.83622

INCH

40

DN

18.15602 Kg/CM2G o 65 C


0.5


Page : 81 of 126





M12. Nozzle Mark : N5A, N5B & N17 1-1/2" 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) shell) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


7.26139 INCH 3.15984 INCH 7.26139 INCH

184.4394 184.4394 MM 80.26 MM 184.4394 184.4394 MM

0.75 0.4 6.39696 0.4 0.25 0.28 0.25

19.05 10.16 162.4828 162.4828 10.16 6.35 7.112 6.35

[UW-16(c)(2)&FIG.UW-16.1]




0.35355 INCH 0.35433 INCH

8.98025 8.980256 6 MM 9 MM

0.75 0.86614 0.86614 0.75 0.375

19.05 22 22 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.47256 INCH 0.01273 INCH

12.0 12.002 029 9 MM 0.32326 0.323262 2 MM



1 0.855 0.855 0.855 1



Page : 82 of 126





M12. Nozzle Mark : N5A, N5B & N17 1-1/2" 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) shell) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) [UG-45 , UG-27(c) & APPENDIX 1-1]

* Calculation of the Opening Finished Cord Length, Length, d at the Midsurface of Shell Thickness Thickness :

Shell thickness less corrosion allowance, t Min. required shell thickness, tr Shell inside radius in corroded condition condition,, R Distance between center o f nozzle and vessel centerline, L Inside radius of nozzle circular opening, Rn Nozzle wall thickness less corrosion allowance & 1 2.5%, tn Shell mean radius, Rm = R + tr/2 O1 = ASIN((L-Rn)/Rm) O2 = ASIN((L+Rn)/Rm)) O = O2 - O1 Finished Finish ed cord co rd length, d = 2 Rm *SQRT(1 - COS^2(O/2))

N.B. The opening finished cord length , d , of nozzle N8A is the same as for nozzle N8B due to similarity of both nozzles nozzl es around vessel centerline centerline ( L= 700 MM ).

0.62992 0.62992 0.47256 0.4 7256 30.8661 30. 8661 27.5591 27. 5591 0.83622 0.8 3622 0.11378 0.1 1378 31.1024 31. 1024

INCH INCH INCH IN CH INCH IN CH INCH IN CH INCH IN CH INCH IN CH INCH IN CH

16 12.0 12.002 029 9 784 700 21.24 2.89 790.0015 790.0015


59.2256 DEG 59.2256 DEG.. 65.9177 65. 9177 DEG DEG.. 6.69214 6.6 9214 DEG DEG.. 3.63 3. 6307 07

INC NCH H

92.2196 92.21968 8 MM


Page : 83 of 126





M12. Nozzle Mark : N5A, N5B & N17 1-1/2" 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) shell) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.24895 INCH

6.32326 6.323262 2 MM

0.32997 0.329 299 97 0.70878 0.32997

INCH INCH INCH INCH

8.38 8.3812 125 5 8.38 8.3812 125 5 18.0 18.002 029 9 8.38 8.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


8.38 8.3812 125 5

MM MM MM MM

MM

9.22262 9.222625 5 MM


Nominal thickness of std. pipe wall thickness, NPS 1-1/2" 1-1/2",, Sch. 0.145 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


3.683

MM

0.29872 INCH 0.48622 INCH

7.5875 12.35

MM MM

0.32997 INCH

8.38 8.3812 125 5

MM

0.32997 INCH

8.38 8.3812 125 5

MM


8.38 8.3812 125 5 10.16 8.89

MM MM MM

INCH


Page : 84 of 126





M12. Nozzle Mark : N5A, N5B & N17 1-1/2" 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) shell) (cont.) [UG-27] Nozzle Opening Calculation With Reinforcing Area of Reinforcemen Reinforcementt (with (w ith reinforcing reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

1.73 1. 7313 13


INC NCH H2

1116.96 1116.963 3 MM2


2

365.2611 365.2611 MM 147.6604 147.6604 MM2 365.2611 365.2611 MM2



175.5649 175.5649 MM2 2 128.2721 128.2721 MM 2 128.2721 128.2721 MM


0.3064 0.30 64 0.05534 0.0 5534 0 0


0.10735 0.1 0735 IN INCH CH2


0.30 0. 3038 38


0.10735 0.1 0735 IN INCH CH


2.94 2. 9476 76


3.92727 3.9 2727 IN INCH CH

AT is greater than A, therefore opening is adequately reinforced.


2


INC NCH H2

2

INC NCH H2

2

2

2

197. 197.67 676 6 35.7052 35.70523 3 0 0

MM 2 MM MM2 2 MM

69.255

MM2

196

MM2

69.255

MM

2

1901.67 1901.673 3 MM2

2

2533.71 2533.716 6 MM


Page : 85 of 126





M13. Nozzle Nozzle Mark Mark : N10A & N10B 1/2" NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located at Leg) No. of nozzles, n 2 [For vessels not subject to rapid fl actuations in pressure, do not require reinforcem ent other than that inherent in the construction under the following c



DN


257.898 PSI 257.898 PSIG G o 149 F 300#

18.156 65

Kg/CM2G

17100 17100

1203.84 1203.84

Kg/CM2G

0.42 INCH 1 0.23622 INCH

10.668

MM

6

MM

0.0063

INCH

0.15992 0.159927 7 MM

0.24252 INCH

6.15992 6.159927 7 MM


0.27283 INCH

6.92991 6.929918 8 MM

Use Nozzle 1/2" NPS with Selected Neck Sch. XXS, [Table 2 of ANSI B 36.10M-1985-(R-1994)] with Thickness Thickness 0.294" (7.47 MM).

0.294

INCH

7.4676

MM


0.25725 0.02103 13872.5 873.701

INCH INCH

MM MM

PSIG PSIG

6.53 6.5341 415 5 0.53 0.5341 415 5 976.6252 61.50854


740 708.15

PSIG PSIG

Kg/CM2G 52.096 49.85376 Kg/CM2G


o

C



PSIG PSIG

Kg/CM2G





Kg/CM2G Kg/CM2G


Page : 86 of 126




Date : 18.2.2004

M13. Nozzle Mark :

Job No. : 7434-33


N10A & N10B, 1/2" NPS, Sch. XXS, 300# WNRF (located (located at leg) leg) (cont.)





Shell (leg) Thickness Shell (leg) Co rrosion Allowance, Cas Shell (leg) Thickness less Pipe Tolerance 12.5% Shell (leg) Thickness less Corrosion Allowance Allowance & 12.5%, t

0.5 0.23622 0.2 3622 0.43 0. 4375 75 0.20128 0.2 0128

INCH INCH IN CH INC NCH H INCH IN CH

12.7 6 11.1 11.112 125 5 5.1125

MM MM MM MM

Nozzle Wall Nom inal Thickness Thickness Nozzle Wall Thickness less Pipe Tolerance 12.5% Nozzle Corrosion Allowance, Can

0.294 0.25725 0.2 5725 0.15748 0.1 5748 0.09977 0.0 9977 0.09977 0.86614 1 1 1 1 20 19.5974 9.79872


7.4676 6.53 6.5341 415 5 4 2.53 2.5341 415 5 2.53 2.5341 415 5 22

MM MM MM MM MM MM

INCH INCH INCH

508 MM 497. 497.77 775 5 MM 248.8875 248.8875 MM

0.84 0.252 0 0.5032 0.24942 0.64046 0.32023


21.336 6.4008 0 12.7812 12.78125 5 6.33537 6.335375 5 16.2 16.267 677 7 8.13 8.1338 385 5

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti

Reinforced Pad Thickness, te Joint Efficiency of Shell, E Joint Efficiency of Nozzle, En Correction Factor, F [UG-37(a)] E1 [Nozzle in solid plate] Shell (leg) Outside Diameter, OD Shell (leg) Inside Inside Diameter in Corrod Corroded ed Condition, 2R = OD - 2 t Shell (leg) Inside Radius in Corro ded Condition, R Nozzle Outside Outside Diameter, OD Nozzle Inside Inside Diameter, ID Nozzle Projection beyond Inner Inner Vessel W all, h = m in. (h1,h2) h1 = 2.5 t h2 = 2.5 ti Nozzle ID Without Wi thout Corrosion Allowance & 12.5% , d = OD - 2*tn



15

DN

18.15602 Kg/CM2G o 65 C




Page : 87 of 126




Date : 18.2.2004 Job No. : 7434-33


M13. Nozzle Mark : N10A & N10B, N10B, 1/2" 1/2" NPS, Sch. XXS, 300# WNRF (located (located at leg) (cont.) [UG-27(c) & APPENDIX 1-1] Nozzle Opening Calculation With Reinforcing (cont.) * Outside Diameter of Reinforced Pad (if (if used) used)

[UG-40(b)&FIG.UG-37.1]


1.28092 INCH 1.24256 INCH 1.28092 INCH

32.5 32.535 354 4 31.561 32.5 32.535 354 4

MM MM MM

0.75 0.294 6.39696 0.294 0.25 0.2058 0.2058

19.05 7.4676 162.4828 162.4828 7.4676 6.35 5.22 5.2273 732 2 5.22 5.2273 732 2


[UW-16(c)(2)&FIG.UW-16.1]



0.29105 INCH 0.31496 INCH

7.39254 7.392547 7 MM 8 MM

0.75 0.86614 0.5 0.75 0.375

19.05 22 12.7 19.05 9.525

MM MM MM MM MM

0.53033 INCH 0.55118 INCH

13.5 14

MM MM

0.12734 INCH 0.00487 INCH

3.23440 3.234404 4 MM 0.12379 0.123793 3 MM


tmin.1 = 0.75 inch tmin.2 ( te = thk. of reinforcing element) tmin.3 ( shell wall thickness) tmin. = lesser of tm in.1, tmin. 2 & tmin.3 1/2 t min. By Considering Equal Legs Fillet Welds : Leg of Outer Pad Weld = SQRT(2)*(tmin./2) Use Leg with Dimension D in DWG. No. 7434-33-3A * Wall Thickness Required : Shell (leg) Nozzle * Strength Reduction Factors :


[UG-27(c)(1)]


Sp / Sv fr1 = Sn / Sv fr2 = Sn / Sv fr3 = lesser of Sn/Sv or Sp/Sv fr4 = Sp / Sv

1 0.855 0.855 0.855 1


Page : 88 of 126




Date : 18.2.2004 Job No. : 7434-33


M13. Nozzle Mark : N10A & N10B, N10B, 1/2" 1/2" NPS, Sch. XXS, 300# WNRF (located (located at leg) (cont.) Min. Nozzle Neck Wall Thickness Check Per UG-45 A. Wall Thickness per UG-45(a) :

trna = trn + Can



0.16235 INCH

4.12379 4.123793 3 MM

0.25123 0.251 512 23 0.36356 0.25123

INCH INCH INCH INCH

6.38 6.3812 125 5 6.38 6.3812 125 5 9.23440 9.234404 4 6.38 6.3812 125 5

NA

INCH

#VAL #VALUE! UE! MM


6.38 6.3812 125 5

MM MM MM MM

MM

6.42252 6.422525 5 MM


Nominal thickness of std. pipe wall thickness, NPS 1/2" 1/2",, Sch. St 0.109 Wall Thickness per UG-16(b) UG-16(b),, trnb12 I - Min. Wall Thickness 1/16" + Cas II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas III - Min. Wall Thickness of Shell/Head in Compressed Air Service, Steam Service, and Water Service = 3/32" + Cas Selected Vessel Service in our case is : Case III (compressed air) So, the Min. W all Thickness Thickness per UG-16(b) UG-16(b),, trnb12


INCH

2.7686

MM

0.21998 INCH 0.40748 INCH

5.5875 10.35

MM MM

0.25123 INCH

6.38 6.3812 125 5

MM

0.25123 INCH

6.38 6.3812 125 5

MM

0.25123 INCH 0.294 INCH 0.25725 INCH OK

6.38 6.3812 125 5 7.4676 6.53 6.5341 415 5

MM MM MM


Page : 89 of 126




Date : 18.2.2004 Job No. : 7434-33


M13. Nozzle Mark : N10A & N10B, N10B, 1/2" 1/2" NPS, Sch. XXS, 300# WNRF (located (located at leg) (cont.) [UG-27] Nozzle Opening Calculation Without Reinforcing Area of Reinforcemen Reinforcementt (withou (w ithoutt reinforcing Element) : Required Area, A = d tr F + 2 tn tr F(1-fr1)

0.08524 0.0 8524 IN INCH CH2

54.9932 54.99329 9 MM2



2

29.1720 29.17209 9 MM 27.3420 27.34207 7 MM2 29.1720 29.17209 9 MM2

Area Available in Nozzle Nozzle Proj ecting Outward, A2 : A21 = 5 (tn - trn) fr2 t A22 = 5 (tn - trn) fr2 tn A2 = The Lesser of A21 or A22


52.6806 52.68061 1 MM2 2 26.1125 26.11258 8 MM 2 26.1125 26.11258 8 MM


0.08585 0.08585 0.04255 0.0 4255 0 0


0.08482 0.0 8482 IN INCH CH2


0.30 0. 3038 38


0.08482 0.0 8482 IN INCH CH

applicable) e) Area Available in Reinforcing Reinforcing Pad, A5 : (Not applicabl A5 = (Dp - d - 2tn) 2tn) te fr4

0.38 0. 3819 19

Total Area Available, AT : AT = A1 + A2 + A41 + A42 + A43

0.25532 0.2 5532 IN INCH CH

AT is greater than A, therefore ope ning is adequately reinforced.


2


INC NCH H2

2

INC NCH H2

2

2

2

55.3862 55.38622 2 27.4536 27.45369 9 0 0

MM 2 MM MM2 2 MM

54.72

MM2

196

MM2

54.72

MM

2

246.3868 246.3868 MM2

2

164.7247 164.7247 MM


Page : 90 of 126




Date : 18.2.2004 Job No. : 7434-33


N. Design of Saddle Supports

The design of saddle supports for horizontal cylindrical cylindrical pressure vessel shall include include the required plate thicknesses calculations calculations for the following saddle components : I. Top flange (reinforcement/wear) thickness , tf tf.. II. Web (saddle plate) thickness , tw tw.. III. Stiffener (rip plates) thickness , ts ts.. IV. Base plate thickness , tb tb.. The Design Data is as Follows : Vessel type & position Design pressure , P Design temperature Radiography (only for pressure parts, BW) Vessel inside dia., D Vessel outside dia., Do Vessel outside radius, Ro Vessel wall thickness, t Corrosion allowance, C Material : shell heads saddles Min. tensile stress : shell heads saddles Min. yield stress, sy : shell & heads saddles Allowable tensile stress: shell heads saddles Vessel weight , empty , W liquid (water), Wc Vessel total weight , Wt Number of saddles used Load per saddle , Q Saddle angle of contact , B Saddle width, b Ring stiffeners adjacent to saddle

Cylindrical & Horizontal 257.898 PSI 18.156 o 149 F 65 85% 61.2598 INCH 1556 62.9921 INCH 1600 31.4961 INCH 800 0.86614 INCH 22 0.23622 INCH 6 ASME SA516 Grade 70 ASME SA516 Grade 70 ASME SA283 Grade C 60000 4224 PSIG 60000 4224 PSIG 55000 PSIG 3872 32000 PSIG 2252.8 30000 2112 PSIG 20000 1408 PSIG 20000 1408 PSIG 15700 1105.28 PSIG 16377.3 lb 7428 22383.1 lb 10152 38760.4 lb 17580 2 19380.2 lb 8790 120 DEG 11.811 INCH 300 N.A.

Kg/CM2G o

C

MM MM MM MM MM

Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg Kg Kg Kg MM


Page : 91 of 126




Date : 18.2.2004 Job No. : 7434-33


N. Design of Saddle Supports (cont.) Vessel Layout :

Figure (3)

Shell Inside Inside Diame ter, D Shell wall thickness, ts Head wall thickness (min.), th Distance from tangent line - to - sadd le support , A Head depth - to - tangent line , Ho = ID / 4 + th Shell length from Tangent - to - tangent (T/T) , L Distance from tangent line - to - weldin welding g line (Skirt), l Shell length from Welding - to - welding (W/W) , L' Saddle - to - saddle distance distance (S/S) , L" = L - 2 A

61.2598 0.86614 0.7874 22.0472 16.1024 189.764 1.5748 186.614 145.669

INCH INCH INCH INCH INCH INCH INCH INCH INCH

1556 22 20 560 409 4820 40 4740 3700

MM MM MM MM MM MM MM MM MM

Total Ellipsoidal Head depth (external depth), H = Ho + l Total vessel overall length = L + 2 Ho

17.6772 INCH 221.969 INCH

449 5638

MM MM

16377.3 lb 22383.1 lb 38760.4 lb

7428 10152 17580

Kg Kg Kg

Vessel weight ,

empty , W liquid (water) (water),, Wc Vessel total weight (water) (water),, Wt

Figure (4)


Page : 92 of 126




Date : 18.2.2004 Job No. : 7434-33


N. Design of Saddle Supports (cont.) (a) Determining the number of stiffeners (rip plates) and its thickness, ts *An approximate approach for determ ining ining the number of stiffeners, N is : N = m" / 24 + 1 (empirical formula) where m" = total length of base plate plate , in. = 0.8 x vessel O.D. , in. 50.3937 50. 3937 IN INCH CH N 3.09974 Use 4 stiffeners, n

1280

MM

4

* Total length length of base plate m , can also be calculated calculated in accordance with saddle angle of contact, B : m' = 2 (Ro + tf) sin B Use m

55.5075 INCH 62.9921 INCH

1409.88 1409.889 9 MM 1600 MM

* The stiffener (rip plate) thickness (ts) is 3/8" (9.5 mm) min. for vessels up to 6 ft (1830 mm) in diameter , Therefore use 4 stiffeners stiffeners with thickness thickness , ts

0.55118 0.5 5118 IN INCH CH

14

MM

Baseplate-Stiffeners' fillet weld clearance, cl = Min. (ts , tb)

0.59055 INCH

15

MM

The stiffeners are equaly spaced by, Ss = [m- 2(0.5ts+cl)]/(n-1) Use equally spaced stiffeners, Ss

20.4199 IN 20.4199 INCH CH 20.4 20 .419 199 9 INCH INCH

518.6667 518.6667 MM 518. 51 8.66 6667 67 MM

11.811 11.8 11 INC NCH H 5.03937 5.0 3937 IN INCH CH 37.8346 37. 8346 IN INCH CH

300 128 961

Use b Use rip plate width, Rw = 1/2[b - (2*cl + tw)] Use distance, c

MM MM MM


Page : 93 of 126




Date : 18.2.2004 Job No. : 7434-33


N. Design of Saddle Supports (cont.) (b) Calcul Ca lculation ation of top flange f lange (reinforcement) thickness thickness,, tf : Flange thickness , tf = SQRT(6*Mb / Sb) Where , Mb = Bending Moment, lb-in. lb-in. Sb = Allowable Allowable design bending stress = 0.66 Sy ( per AISC Spesifications)

M

b

P b b II = ---- x ---- x ---- = P b 2 4

II

198 980 00

PSIIG PS

1393.92

19380.2 19380. 2 31.4961 31. 4961 120 120

lb 8790 INCH IN CH 800 Degree Degree

Kg/CM2G

b ----8

Pll = Linear load per unit lengh , lb/in. lb/in. Q 1 + cos B = ---- [ -------------- -----------II Ro II - B + cos B * sin sin B

P

Q = load per one saddle , lb Ro = Vessel outside radius radius , in. in. 0 = Angle of contact , deg. B

= 180 - 0 /2

Kg MM

500.925 500. 925 lb/ lb/in in

8945.49 8945.495 5 Kg/M

739.555 739. 555 lblb-in in

8.52058 8.520584 4 Kg-M

Flange thickness , tf = SQRT(6*Mb / Sb) Use top flange plate thickness , tf

0.4734 0.47 34 INC NCH H 0.55118 0.5 5118 IN INCH CH

12.0243 12.02436 6 MM 14 MM

Use top flange plate width, B = 2* Rip width + 2*(55) + tw

14.9606 14. 9606 IN INCH CH

380

. . PI

. . Bending moment , Mb

MM


Page : 94 of 126




Date : 18.2.2004 Job No. : 7434-33


N. Design of Saddle Supports (cont.) (c) Calculation of web (saddle) plate t hick hickness ness , tw :

Use 0.5" thick plate min. ( i.e. assume tw = 0.5" ) Calculate the max. allowable height h of a 1" wide wide strip column 0.5" thick under PII . Area , a = 1 x 0.5 IN.2 Min. radius of gyration , k = 0.289 tw

From

P

= ----a

0.5

INCH

13

MM

18000 ---------------------------] 1

h

1+ -------- [ ---- ] 18000

2

k

We get h = tw * SQRT [(1500/PII)(18000 [(1500/PII)(18000 tw - PII )] = 2127 MM > distance c (961 MM) W here c

79.7655 79. 7655 IN INCH CH

2026.04 2026.044 4 MM

37.8346 INCH

961

MM

Use web ( saddle ) with thickness thickness , tw

0.55118 0.5 5118 IN INCH CH

14

MM

tb = SQRT [(Q * b) / 26400 * m]

0.371

9.42348 9.423482 2 MM

Use base plate with thickness , tb

0.98425 0.9 8425 IN INCH CH

(d) Calculation of base plate thickness , tb :

* Check for the bearing pressure : Bearing pressure = Q / (b*m)

INCH

25

MM

26.0486 PSI 26.0486 PSIG G 1.833821 Kg/CM2G < 750 PSI allowable OK


Page : 95 of 126




Date : 18.2.2004 Cli Client ent : APRC PRC Type : Horizontal

N. Design of Saddle Supports (cont.) D. Stresses in Shell Due to Temperature Expansion : Expansion Expansion dl = a * l * dT Where dl = a = Thermal Thermal expansion expansion coefficent l = Tangent Tangent - to - tangent distance (T/T) , in. in. dT = Difference in temp. = 167-70 (consider ampient temp. 70 oF ) Expansion , dl

79 F o 70 F 0.10644 INCH

o

26.11111 C 21.11111 oC 2.70353 2.703538 8 MM

0.1 1938. 193 8.02 02 26.047 3.28084 37.8346 70.8661

lb INCH ft. INCH INCH

879 661.5947 661.5947 1000 961 1800

Kg MM MM MM MM

INCH INCH INCH INCH

1600 300 380 270

MM MM MM MM

Job No. : 7434-33

7.1E-06 o

Therefore use slots for anchor bolts located in the sliding sliding saddle with distance c/c 65 MM , and provide lubrite plates underneath the sliding saddle . Friction coefficient, fo Shear force at the saddle base, fo * Q Centroid of saddle arc, xo = ro * sin sin 60 / rad. 60 Use Saddle height under vessel Distance, c Elevation , Z =Ro + tf + c + tb Support Saddle Detail :

Figure (5)

m b B Width of outside stiffeners, Sw = 2 Rw + tw

62.9921 11.811 14.9606 10.6299


Page : 96 of 126




Date : 18.2.2004 Job No. : 7434-33


N. Design of Saddle Supports (cont.)

Bending moment = fo * Q ( Z - xo xo ) This bending moment is counteracted by the weight of the vessel , Q * b/2 . i.e fo * Q ( Z - xo ) = Q * b/2 Therefore , the min. value for b = 2 * BM /Q ( the value used for b = 300 MM > 227.68 MM )

86860.3 8686 0.3 lblb-in in..

1000.73 1000.738 8 Kg-M

8.96382 8.9 6382 IN INCH CH 227.6811 227.6811 MM OK < 300 MM


Page : 97 of 126




Date : 18.2.2004 Job No. : 7434-33


O. Lowest MDMT Without Impact Test [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

Min. Design Metal Temperature, MDMT

o

10

F

THIICK TH CK..

THIC TH ICK. K.

1. Pressure Parts Materials ASME SA516 Grade 70 (normalized) a. Shell Plat e : b. Formed Heads : ASME SA516 Grade 70 (normalized) c. Flanges : ASME SA105 (normalized/tempered) (Castings) d. Nozzle Necks : ASME SA106 Grade B (Seamless Pipe Nozzles)

INCH

MM

0.9 0.8 0.94

22 20 24

M1. Nozzle Nozzle Mark : M2. Nozzle Nozzle Mark : M3. Nozzle Nozzle Mark : M4. Nozzle Nozzle Mark : M5. Nozzle Nozzle Mark : M6. Nozzle Nozzle Mark : M7. Nozzle Nozzle Mark : M8. Nozzle Nozzle Mark Mark : M9. Nozzle Nozzle Mark Mark : M10. Nozzle Nozzle Mark M11. Nozzle Nozzle Mark M12. Nozzle Nozzle Mark

0.4 0.56 0.5 0.5 0.43 0.43 0.44 0.44 0.34 0.4 0.36 0.4

10.16 14.27 12.7 12.7 10.97 10.97 11.13 11.13 8.74 10.16 9.09 10.16

0.4

10.16

0.29

7.47

N11, 1-1/2"NPS, Sch. XXS, 300# WNRF(Located entirely N8 24" NPS, Sch. 30, 300# WNRF (Manhole (Manhole Located at S Leg 20"NPS, Sch. 30 (Leg Located at Shell with Reinforce N1 8"NPS, Sch. 80, 300# WNRF (Located at Shell) N1 6" NPS, Sch. 80 300# WNRF (Located at Blind Flange N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.) (cont.) N9 4" NPS, Sch. 120, 300# WNRF (Located at Shell) Shell) N18 3" NPS, Sch. Sch. 160, 300# WNRF (Located at Shell) Shell) N3, N4 & N7 2" NPS, Sch.160, Sch.160, 300# WNRF (Located at S : N6 & N17 1-1/2" NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located a : N16 1" NPS, Sch.XXS, 300# WNRF (Piping branch branch from : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, Sch.XXS, 300# WNRF (Lo

M12. Nozz le Mark : N16 1-1/2" NPS, Sc h.XXS, 300# WNRF (Loc ated at Shell, F = 0.5)

M13. Nozzle Nozzle Mark : N10A & N10B 1/2" NPS, Sch.XXS, 300# WNRF (Locate

o

-12

C

P No Gr Gr No

CURVE CUR VE

1 1 1 1

2 2 2 1

D D B B

1

1

B

Note : Rest of nozzles are N17, N18 and N19 which represent the instruments for LC & LG.

e. Fittings : Half Coupling : ASME SA 105

f. Stud Bolts : g. Nuts :

Tees : ASME SA234 WPB N1, 3/4"

3000#

0.4

ASME SA193 Gr ade B7, Galvanized ASME SA194 Grade 2 H, Galvaanized

2. Non-Pressure Parts Materials ASME SA516 Grade 70 a. Saddle Plate : b. Lifting Lug Reinf. Plate : ASME SA516 Grade 70 (if required)

10.97

2.5 2.5

0.6 0.9

63.5 63.5 to be checked

14 22

1 1

2 2

0

D D


Page : 98 of 126




Date : 18.2.2004

O. Lowest MDMT Without Impact Test (cont.) 1. Pressure Parts Materials a. For cylindrical shell Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Point of combination of MDMT & thkickness Required thickness, tr Corrosion allowance, Cas Joint efficiency, E = E* MDMT without impact testing (for thickness 0.551") Ratio = tr . E / (tn -c) [Fig. UCS-66.2] Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adj usted MDMT w/o im pact testing Impact testing required ?

b. For formed heads Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Point of combination of MDMT & thkickness Required thickness, tr Corrosion allowance, Cah Joint efficiency, E = E* MDMT without impact testing (for thickness 1.3385827") Ratio = tr . E / (tn -c) [Fig. UCS-66.1] Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adj usted MDMT w/o im pact testing Impact testing required ?

Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

ASME SA516 Grade 70 Norm alized D o 10 F -12 0.86614 0.8 6614 IN INCH CH 22

o

C MM

Below,, so we have to check ratio tr.E/(tn-c) Below

0.47256 0.47256 0.23622 0.2 3622 0.85 -36.2835 0.63765 35 -71.2835 NO

INCH INCH INCH IN CH

12.0 12.002 029 9 6

o

-37.93526 oC

F > 0.35 o F o F

MM MM

[Fig. UCS-66-1]

1.666667 -57.3797

ASME SA516 Grade 70 Norm alized D o 10 F -12 0.787 INCH 20

o

C C

o

o

C MM

Below, we have to check ratio tr.E/(tn-c)

0.46538 IN 0.46538 INCH CH 0.23622 0.2 3622 IN INCH CH 0.85 o -39.632 F 0.7182 > 0.35 o 30 F o -69.632 F No

11.8205 11.82059 9 MM 6 MM o

-39.79556 C [Fig. UCS-66-1] o

-1.111111 C -56.46222 oC


Page : 99 of 126




Date : 18.2.2004

O. Lowest MDMT Without Impact Test (cont.) c. For B16.5 flan flanges ges : Material ASME/ANSI Condition Curve MDMT Impact testing exemption temp.

Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

ASME SA105 B16.5

[UCS-66(c)(1)]

B 10 -20

o

F F

o

Ferritic Steel

-12 -29

o

C C

o

Note. The same condition apply for flanges B16.47, split loose flanges of SA216 Grade WCB and LWN flanges. [UCS-66(c)(2),(3)&(4)]

For bli blind nd flanges : - M2, N8 24" NPS, 300# : Material ASME/ANSI Condition Curve MDMT Blind thickness, tA

Governing Governin g thickness, tg1 = tA/4

ASME SA105 B16.5

Ferritic Steel

B o 10 F 2.75197 2.7 5197 INCH INCH

-12 69.9

o

0.68799

17.475

MM

C MM

[Fig. UCS-66.3(c)]

MDMT without impact testing (for thickness 2.9374016")

For bli blind nd flanges : - M4, N1 8" NPS, 300# : Material ASME/ANSI Condition Curve MDMT Blind thickness, tA

Governing Governin g thickness, tg1 = tA/4

10.0394

o

F

ASME SA105 B16.5

-12.20035 oC

Ferritic Steel

B o 10 F 1.61811 1.6 1811 INCH INCH

-12 41.1

o

0.40453

10.275

MM

-16.6929 oF

-27.05162 oC

C MM

[Fig. UCS-66.3(c)]

MDMT without impact testing (for thickness 2.9374016")


Page : 100 of 126




Date : 18.2.2004

O. Lowest MDMT Without Impact Test (cont.)

Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

d. M1. Nozzle M Mark ark : N11, 1-1/2"NPS, Sch. XXS, 300# WNRF(Loca ted entirely within a centrally located circle of hea Material ASME SA 106 Grade B Condition Tempered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.01279 0.0 1279 IN INCH CH 0.32486 0.324866 6 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 2.9374016") -17.2 F -27.33333 oC [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.06638 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o o Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2 F -102.3333 C Impact testing required ? No

M2. Nozzle Mark Mark : N8 24" NPS, Sch. 30, 300# 300# WNRF (Manhole (Manhole Located at Shell with Reinforcement) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.56181 0.5 6181 IN INCH CH 14.27 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.17874 0.1 7874 IN INCH CH 4.54011 4.540115 5 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 1.8759843") -1.06614 F -18.37008 Ratio = tr . E / (tn -c) 0.46664 < 0.35 [Fig. UCS-66-1] [Fig. UCS-66.1] o o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 C o Adjusted MDMT w/o impact testing [UCS-66(b)] -136.066 F -93.37008 oC Impact testing required ? No


Page : 101 of 126




Date : 18.2.2004


Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M3. Nozzle Mark Mark : Leg 20"NPS, Sch. 30 (Leg Located at Shell with Reinforcement) Reinforcement) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.5 INCH 12.7 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we need to check ratio tr.E/(tn-c) Required thickness, tr 0.06257 0.0 6257 IN INCH CH 1.58929 1.589294 4 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o o MDMT without impact testing (for thickness 1.6259843") -7 F -21.66667 C [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.20163 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o Adjusted MDMT w/o impact testing [UCS-66(b)] -142 F -96.66667 oC Impact testing required ? No

M4. Nozzle Mark Mark : N1 8"NPS, Sch. 80, 300# 300# WNRF (Located at Shell) Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, Can Joint efficiency, E = E* MDMT without impact testing (for thickness 1.1496063") [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA 106 Grade B Tem pered B o o 10 F -12 C 0.5 INCH 12.7 MM Bel elo ow, we have to check ratio tr.E/(tn-c) 0.06257 0.0 6257 IN INCH CH 1.58929 1.589294 4 MM 0.23622 0.2 3622 IN INCH CH 6 MM 0.85 o -7 F -21.66667 oC 0.20163 < 0.35 [Fig. UCS-66-1] o 135 F 57.22222 oC o o -142 F -96.66667 C No


Page : 102 of 126




Date : 18.2.2004


Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M5. Nozzle Mark Mark : N1 6" NPS, Sch. 80 300# WNRF (Located at Blind Blind Flange of N1) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.43189 0.4 3189 IN INCH CH 10.97 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.F/(tn-c) Required thickness, tr 0.04766 0.0 4766 IN INCH CH 1.21050 1.210501 1 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 1.1496063") -7 F -21.66667 oC [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.20703 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o o Adjusted MDMT w/o impact testing [UCS-66(b)] -142 F -97 C Impact testing required ? No

#REF!

Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, Can Joint efficiency, E = E* MDMT without impact testing (for thickness 1.1496063") [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA 106 Grade B Tem pered B o o 10 F -12 C 0.43189 0.4 3189 IN INCH CH 10.97 MM Bel elo ow, we have to check ratio tr.E/(tn-c) 0.04826 0.0 4826 IN INCH CH 1.22 1.2257 572 2 MM 0.23622 0.2 3622 IN INCH CH 6 MM 0.85 -13.6283 oF -25.34908 oC 0.20963 < 0.35 [Fig. UCS-66-1] o 135 F 57.22222 oC o o -148.628 F -100.3491 C No


Page : 103 of 126




Date : 18.2.2004 Job No. : 7434-33



[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M7. Nozzle M Mark ark : N9 4" NPS, Sch. 120, 120, 300# 300# WNRF (Located at Shell) Shell) Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, Can Joint efficiency, E = E* MDMT without impact testing (for thickness 1.1496063") [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA 106 Grade B Tem pered B o o 10 F -12 C 0.43819 0.4 3819 IN INCH CH 11.13 MM Bel elo ow, we have to check ratio tr.E/(tn-c) 0.03201 0.0 3201 IN INCH CH 0.81295 0.812955 5 MM 0.23622 0.2 3622 IN INCH CH 6 MM 0.85 -12.9339 oF -24.96325 oC 0.1347 < 0.35 [Fig. UCS-66-1] o 135 F 57.22222 oC o o -147.934 F -99.96325 C No

M8. Nozzle Nozzle Mark : N18 3" NPS, Sch. Sch. 160, 300# WNRF (Located at Shell) Shell) Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, Can Joint efficiency, E = E* MDMT without impact testing (for thickness 1.1496063") [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA 106 Grade B Tem pered B o o 10 F -12 C 0.43819 0.4 3819 IN INCH CH 11.13 MM Bel elo ow, we have to check ratio tr.E/(tn-c) 0.02 0. 0244 44 INC NCH H 0.61966 0.619668 8 MM 0.23622 0.2 3622 IN INCH CH 6 MM 0.85 -12.9339 oF -24.96325 oC 0.10267 < 0.35 [Fig. UCS-66-1] o 135 F 57.22222 oC o o -147.934 F -100 C No


Page : 104 of 126




Date : 18.2.2004


Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M9. Nozzle Nozzle Mark : N3, N4 & N7 2" NPS, Sch.160, 300# WNRF (Located at Shell) Shell) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.34409 0.3 4409 IN INCH CH 8.74 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.01652 0.0 1652 IN INCH CH 0.41949 0.419494 4 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 1.1496063") -20 F -28.88889 oC [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.13013 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o o Adjusted MDMT w/o impact testing [UCS-66(b)] -155 F -103.8889 C Impact testing required ? No

M10. Nozzle Nozzle Mark : N6 & N17 1-1/2" NPS, NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located at Shell) Shell) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.01273 0.0 1273 IN INCH CH 0.32326 0.323262 2 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 1.1496063") -17.2 F -27.33333 oC [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.06605 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o o Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2 F -102 C Impact testing required ? No


Page : 105 of 126




Date : 18.2.2004


Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M11. Nozzle Nozzle Mark : N16 1" NPS, Sch.XXS, Sch.XXS, 300# 300# WNRF (Pipin (Piping g branch from N4) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.35787 0.3 5787 IN INCH CH 9.09 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.00885 0.0 0885 IN INCH CH 0.22476 0.224769 9 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 1.1496063") -20 F -28.88889 oC [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.06183 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o o Adjusted MDMT w/o impact testing [UCS-66(b)] -155 F -103.8889 C Impact testing required ? No

M12. Nozzle Nozzle Mark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located at Head, F = 0.5) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.01273 0.0 1273 IN INCH CH 0.32326 0.323262 2 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o MDMT without impact testing (for thickness 1.1496063") -17.2 F -27.33333 oC [Fig. UCS-66.1] Ratio = tr . E / (tn -c) 0.06605 < 0.35 [Fig. UCS-66-1] o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 oC o o Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2 F -102 C Impact testing required ? No


Page : 106 of 126




Date : 18.2.2004


Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M12. Nozzle M ark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Head, F = 0.5)

Mater ial

A SME SA 106 Grade B

Condition

Tempered

Curve

B

MDMT

10

Nominal thickness, tn (adoptedthickness)

0.4

Point of combination of MDMT & thkickness

Below, we have to check ratio tr.E/(tn-c)

Requiredthickness, tr

0.0 127 268 38

INCH

0.323261675

MM

Corrosion allowance, Can

0.2 362 204 72

INCH

6

MM

Joint efficiency, E = E*

0.85

MDMT without impact tes ting (for thickness 1.1496063")

-17.2

Ratio = tr . E / (tn -c)

0.066051063

[Fig. UCS-66.1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1]

135

Adjust ed MDMT w/o impact testing [UCS-66(b)]

-152.2

Impacttesting required ?

No

o

F

-12

INCH

10.16

o

F

< 0.35 o

F

o

F

-27.33333333

o

C

MM

o

C

[Fig. UCS-66-1]

57.22222222

-102.3333333

o

C

o

C

M13. Nozzle Nozzle M Mark ark : N10A & N10B 1/2" NPS, Sch.XXS, Sch.XXS, 300# WNRF (Located at Leg) Material ASME SA 106 Grade B Condition Tem pered Curve B o o MDMT 10 F -12 C Nominal thickness, tn (adopted thickness) 0.29409 0.2 9409 IN INCH CH 7.47 MM Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Bel elo ow, we have to check ratio tr.E/(tn-c) Required thickness, tr 0.00487 0.0 0487 IN INCH CH 0.12379 0.123793 3 MM Corrosion allowance, Can 0.23622 0.2 3622 IN INCH CH 6 MM Joint efficiency, E = E* 0.85 o o MDMT without impact testing (for thickness 1.1496063") -20 F -28.88889 C Ratio = tr . E / (tn -c) 0.07158 < 0.35 [Fig. UCS-66-1] [Fig. UCS-66.1] o o Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135 F 57.22222 C o o Adjusted MDMT w/o impact testing [UCS-66(b)] -155 F -104 C Impact testing required ? No


Page : 107 of 126




Date : 18.2.2004

O. Lowest MDMT Without Impact Test (cont.) e. Stud bolts : Material Curve Size MDMT Impact testing exemption [Fig. UCS-66, Bolting]

Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

ASME SA193 Grade B7 0 1.25 INCH 31.75 o 10 F -12 o -55 F -48

MM C o C o

[Size 1.25" < 2.5"]

Nuts :

Material Curve Size MDMT Impact testing exemption

[Fig. UCS-66, Bolting] [Size 1.25" < 2.5"]

f. Fittings Fittings : For equal equal tee : 1.5" x 1.5" Size, NPS Sch. Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, C Joint efficiency, E = E* MDMT without impact testing (for thickness 1.0669291") [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA 194 Grade 2H 0 1.25 INCH 31.75 o 10 F -12 o -55 F -48

MM C o C o

1.5 INCH XXS ASME SA234 Grade W PB Tempered B o o 10 F -12 C 0.4 INCH 10.16 MM Bel elo ow, we have to check ratio tr.E/(tn-c) 0.01273 0.0 1273 IN INCH CH 0.32326 0.323262 2 MM 0.23622 0.2 3622 IN INCH CH 6 MM 0.85 o -17.2 F -27.33333 oC 0.06605 < 0.35 [Fig. UCS-66-1] o 135 F 57.22222 oC o o -152.2 F -102.3333 C No


Page : 108 of 126




Date : 18.2.2004


f. Fittings Fittings (con (cont.): t.): For equal tee : 2" x 1" Size, NPS Sch. Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, C Joint efficiency, E = E* MDMT without impact testing (for thickness 1.0669291") [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

Job No. : 7434-33


[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

2 INCH XXS ASME SA234 Grade W PB Tempered B o o 10 F -12 C 0.34409 0.3 4409 IN INCH CH 8.74 MM Bel elo ow, we have to check ratio tr.E/(tn-c) 0.01652 0.0 1652 IN INCH CH 0.41949 0.419494 4 MM 0.23622 0.2 3622 IN INCH CH 6 MM 0.85 -23.4614 oF -30.8119 oC 0.13013 < 0.35 [Fig. UCS-66-1] o 135 F 57.22222 oC o -158.461 F -105.8119 oC No


Page : 109 of 126





O. Lowest MDMT Without Impact Test (cont.) 2. For Non-Pressure Parts :

[UG-20(f)] , [UCS-66] & [FIG.UCS-66]

a. Saddle Plate (tf) : Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) (tf) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, C Joint efficiency, E = E* MDMT without impact testing [Fig. UCS-66.1] Ratio = tr . E / (tn -c) Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA516 Grade 70 Normalized D o o 10 F -12 C 0.55118 0.5 5118 IN INCH CH 14 MM Bel elo o, we have to check ratio tr.E/(tn-c) 0.47 0. 4734 34 INC NCH H 12.0243 12.02436 6 MM 0 INCH 0 MM 0.85 o o -51.7244 F -46.51356 C 0.73005 > 0.35 [Fig. UCS-66-1] o 20 F -6.666667 oC -71.7244 oF -57.62467 oC No

b. Lifting Lug Reinf. Plate : Material Condition Curve MDMT Nominal thickness, tn (adopted thickness) Poi oin nt of comb mbiinat atiion of MDMT & thki kic ckn kne ess Required thickness, tr Corrosion allowance, C Joint efficiency, E = E* MDMT without impact testing Ratio = tr . E / (tn -c) [Fig. UCS-66.1] Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] Adjusted MDMT w/o impact testing [UCS-66(b)] Impact testing required ?

ASME SA516 Grade 60 Normalized D o o 10 F -12 C 0.86614 0.8 6614 IN INCH CH 22 MM Above, no need to check ratio tr.E/(tn-c) 0.86614 0.8 6614 IN INCH CH 22 MM 0 INCH 0 MM 1 o o -31.5669 F -35.31496 C 1 > 0.35 [Fig. UCS-66-1] o o 0 F -17.77778 C -31.5669 oF -35.31496 oC No

Conclusion : MDMT without without Impact Testing for W hole Vessel

10

o

F

-12

o

C

So, the vessel can be oper ated at the nominated MDMT with impact test exemption in accordance with UG-20(f), UCS-66 and Fig. UCS-66.


Page : 110 of 126




Date : 18.2.2004

P. Radiography

Job No. : 7434-33


Spot

RT3 Q. Hydrostatic Test Pressure Design Temperature Test Temperature Internal Design Pressure, P (MAWP)

[UG-99(b)] o

Max. Allowable Allowable Stress @ Design Temperature, S Max. Allowable Allowable Stress @ Test Temperature, St

149 F o 86 F 255.682 PSI

65 30 18

o

200 000 00 200 000 00

1408 1408

Kg/CM2G

PSIG PSI PSIIG PS

C C

o

Kg/CM2G

Kg/CM2G

[TABLE 1A, SUBPART 1, ASME SEC. II, PART D]

Hydrostatic Test Pressure, Ph = 1.3 * MAWP (St/S)

332.386 PSI

23.4

Kg/CM2G

Client Request for Hydrostatic Test Pressure, Ph = 1.5 * MAWP (St/S)

383.523 PSI

27

Kg/CM2G

Check for hydrostatic test : For shell, shell, S = Ph ( R + 0.6 t ) / E t

16229. 1622 9.6 6 PSI PSIG 20000 PSIG

2 1142.5 1142 .561 61 KG/CM G OK

< Max. Working Pressure (New & Cold) for Whole of Vess el , MWPn

43 5. 67 458 08

PS G I

30.67149147

Kg/CM2G

Max. Working Pressure (Operating & corroded) for Whole of Vessel, MWPo

30 5. 36 231 62

PS G I

21.49750775

Kg/CM2G

Shop Hydrostatic Test Pressure (new & cold), Ph = 1.3 * MWPn (St/S)

566.3769551

PSI

39.87293891

Kg/CM2G

Check for shop hydrostatic test : For shell, S = Ph ( R + 0.6 t ) / E t

23967.41693

PSIG

1687.306187

KG/CM2G

20000

PSIG

OK

<

R. Post Weld Heat Treatment (PWHT) [UW-40 & TABLE UCS-56]

Shell Material P- No. Gr. No. Max. Welded Nominal Thickness (Shell) Max. Welded Nom inal Thickness Thickness (N1 8" 300# Blind)

ASME SA516 Grade 70 1 2 0.866 INCH 22 0.63 INCH 41.1

MM MM

a. According to UW-40 & UCS-56(f), the vessel material is exempted from PWHT. b. According to UW-40, UCS-56 and Table UCS-56 , the joint between nozzle 6" NPS N1 & Blind Flange, the vessel component shall be partially postweld postweld heat treated in accordance to the following following procedure :

1. Heating up to temp. Starting from 350oC for a time 2. Holding temp. for a time 3. Cooling up to for a time Up to room temp.

1148 1 1148 1 572 1 86

o

F Hour o F Hour o F Hour o F

620 58 620 50 300 52 30

o

C Minute o C Minute o C Minute o C


Page : 110a of 126




Date : 18.2.2004

C1 O

Heating Time = (Thickness, t) (C2-C1) / (Heating Rate, R h)

Holding,

C2

Heating Rate, Rh

O

o

from, C to, to, C 350 620

Heating

Job No. : 7434-33


1.967 1.9 6797 97

Hour Ho ur

1

Hr

C /Hr/inch Inch 222 1.61811 58

Min. Holding Time per Thickness

Holding Time = (Thickness, t) (Min. Holding Time per Thickness, Th)

1 1.61811 1

C3 Cooling Cooling Time = (Thickness, t) (C3-C4) / (Cooling Rate, R c)

O

Hr Hr

1.86257 1.862 57 1

50

C4

Cooling Rate, Rc

O

o

from, C to, to, C 620 300 Hour Hour Hr

Thickness

Minutes Mi

hr/Inch

Minutes

Thickness

C /Hr/inch Inch 278 1.61811 52

Minutes Mi

Note : 593 oC can be assumed to be 620 oC + /- 25 oC


Page : 111 of 126




Date : 18.2.2004

S. Calculation of Vessel Weight 1.Volume of vessel : Shell volume volume = 3.14 * R2 * L' 2 Head volume = 3.14 * R * (2 (2*KD/3 + l ) ( where KD = Depth of head ), K =

Head skirt, l Total volume of vessel Tangent - to - Tangent Tangent distance distance (T/T) , L Welding - to - Welding distance distance (W/W ) , L' 2.W eight of liquid water , W c Total Oveall Length Length = L + 2 H0 3.Weight of vessel empty , W : a. weight of shell = II *(Ro2 - R2 ) * L' * $ ( where $ = steel d ensity ) b.weight of two ellipsoidal ellipsoidal heads 2 3 3 =(3.14/4) * D * (4/3) * KD *$ = (3.14/3)*K*(Do -D )*$ = 8*(3.14/3)*K*(Ro3 - R3)*$ + weight of 2 skirts 2 2 Weight of skirt of two ellipsoidal heads = II *(Ro - R ) * 2 Skirt* $ c. weight of saddles : - Base plate, 1600x400x25 Saddle plate length - Saddle plate, 17 90x480x14 90x480x14 Web plate ( saddle plate ) height, h = Z - (R o+tf) cos(B/2) Web plate ( saddle plate ) width, Lw = m - 2*(ts + cl) angle b = B/2 where h1 = height of segment y = m - m' = (m-2cl) - 2 (Ro+tf) sin(B/2) Area of segment, As = (R o+tf)2 [(3.14 * b) b)/180 - Sin b* Cos b] b]

0.00984 INCH 1.5748 INCH 189.764 186.614 22381.1 221.969

INCH INCH

lb. INCH

9.013374 0.569199 0.25 40 10.15177 4820 4740 10151.77 5638

M3 3 M MM MM M3 MM MM Kg MM

8946.77 8946 .77 lb.

4058. 4058.14 145 5 Kg 3 7850 Kg/M

1789.08 1789 .08 lb.

811. 811.504 5047 7 Kg

137.099 137. 099 lb.

62.1 62 .1864 8644 4 KG

207.678 lb. 207.678 70.4724 70. 4724 IN INCH CH 164.806 164. 806 lb.

94.2 Kg 1790 MM 74.7 74.7539 5398 8 Kg

54.8425 54.8425 60.7087 60. 7087 60 17.0079 6.30357

INCH INCH INCH IN CH Deg.

1393 1542

INCH INCH

432 MM 160.1106 160.1106 MM 2 0.406956 M

2

Area of web plate excluding segment, A = (m -2cl) * h - As - 2y /SQRT(3) - Weight of web plate (1542x1393x14) = A * tw * $ Rip plates weights (per saddle) : Rip plates, thickness, ts Rip plates # 1 width, Rw Rip plates # 1 , height Weight of rip plates # 1 (no. off 4 ) , 1006x178x14 Rip plates # 2 width, Sw Rip plates # 2 , height Weight of rip plates # 2 (no. off 2 ) , 1393x370x14 - Weight of rip plates ( per one saddle ) - Weight of one saddle - W eight of two ( 2 ) saddles

Job No. : 7434-33


MM MM

2

424.118 424. 118 lb.

1.750452 M 192. 192.374 3747 7 Kg

0.55118 0.55118 5.03937 5.0 3937 39.5046 39. 5046 124.476 10.6299 10. 6299 54.8425 54. 8425 182.256 306.732 1103.33 1103 .33 2206.67

14 128 1003.41 1003.416 6 56.461 270 1393 82.66898 139.13 500. 500.458 4587 7 1000. 1000.91 917 7

INCH INCH INCH IN CH INCH IN CH lb. INCH IN CH INCH IN CH lb. lb. lb. lb.

MM MM MM Kg MM MM Kg Kg Kg Kg


Page : 112 of 126




Date : 18.2.2004 Job No. : 7434-33


S. Calculation of Vessel Weight (cont.)

Weight of leg : weight of pipe 20" Sch. 30, L = 600 MM weight of cap 20" Sch.30 - weight of Pad =3.14/4 (Dp2-OD2) te p

205.191 lb. 205.191 99..20 99 209 9 lb. 219.209 219. 209 lb.

93.072 Kg 45 Kg 99.4 99.4304 3042 2 Kg

e. W eight of nozzles 3434.11 lb. 1557.671 i. Weight of Nozzle, N12 24" Sch. 30, WNRF 300# - weight of WN flange 544.547 544. 547 lb. 247 - weight of nozzle pipe (184 MM) 85.0415 85. 0415 lb. 38.57376 - weight of Blind Flange 753.989 753. 989 lb. 342 - weight of Stud Bolts & Nuts 74.0761 74. 0761 lb. 33.6 2 2 - weight of Pad =3.14/4 (Dp -OD ) te p 314.645 314. 645 lb. 142. 142.719 7193 3 ii. Weight of Nozzle, N1 10" Sch. 60, WNRF 300# : - weight of SO flange 90.3905 90. 3905 lb. 41 - weight of nozzle pipe (180 MM) 32..36 32 362 2 lb. 14.679 - weight of Blind Flange 127.869 127. 869 lb. 58 - weight of Stud Bolts & Nuts 15.6618 15. 6618 lb. 7.104 2 2 - weight of Pad =3.14/4 (Dp -OD ) te p 37.8217 37. 8217 lb. 17.1 17.1554 5545 5 iii. Weight of Nozzle, N1 8" Sch. 80, WNRF 300# : - weight of WN flange 66.1394 66. 1394 lb. 30 - weight of nozzle pipe (180+2000 MM) 310.668 310. 668 lb. 140.9152 iv. Weight of Nozzle, N6 & N9 2" Sch. 160, WNRF 300# : - weight of WN flange 26.4557 26. 4557 lb. 12 - weight of nozzle pipe (1490 MM) 218.973 218. 973 lb. 99.3234 - weight of Pad =3.14/4 (Dp2-OD2) te p 7.60 7. 6038 38 lb. 3.44 3.44898 8988 8 v. Weight of Nozzle, N3 & N7 3" Sch. 160, WNRF 300# : - weight of WN flange 15.4325 15. 4325 lb. 7 - weight of nozzle pipe (160 MM) 7.53107 7.5 3107 lb. 3.416 2 2 - weight of Pad =3.14/4 (Dp -OD ) te p 5.56824 5.5 6824 lb. 2.52 2.52568 5687 7 vi. Weight of Nozzle, N10 & N14 6" Sch. 120, WNRF 300# : - weight of WN flange 0 lb. 0 - weight of nozzle pipe (160 MM) 0 lb. 0 2 2 - weight of Pad =3.14/4 (Dp -OD ) te p 0 lb. 0 vii. Weight of Nozzle, N9 4" Sch. 120, WNRF 300# : - weight of WN flange 24.2511 24. 2511 lb. 11 - weight of nozzle pipe (160 MM) 9.98969 9.9 8969 lb. 4.5312 2 2 - weight of Pad =3.14/4 (Dp -OD ) te p 9.74459 9.7 4459 lb. 4.42 4.42002 0027 7 viii. Weight of Nozzle, N2, N3, N4, N8A, N8B, N11, N13 & N16 1-1/2" Sch. 160, WNRF 300# : - weight of WN flange 46.2976 46. 2976 lb. 21 - weight of nozzle pipe (160 MM) 45.1864 45. 1864 lb. 20.496 2 2 - weight of Pad =3.14/4 (Dp -OD ) te p 4.78483 4.7 8483 lb. 2.17 2.17033 0339 9

Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg Kg


Page : 113 of 126




Date : 18.2.2004 Job No. : 7434-33


S. Calculation of Vessel Weight (cont.)

ix. Weight of Nozzle, N15 1" Sch. XXS, WNRF 300# : - weight of WN flange - weight of nozzle pipe (160 MM) - weight of Pad =3.14/4 (Dp2-OD2) te p x. Weight of Nozzle, N5A & N5B 1/2" Sch. 160, WNRF 300# : - weight of WN flange - weight of nozzle pipe (160 MM) - weight of Pad =3.14/4 (Dp2-OD2) te p xi. Weight of Nozzle, N4 3/4", half coupling 3000# :

Weight of vessel emp ty (erection weight), W Weight of test liquid liquid (water) (water),, Wc Total test weight (weight of vessel and test liquid), liquid), Wt

4.40929 lb. 4.40929 7.53107 7.5 3107 lb. 0.94545 0.9 4545 lb.

2 Kg 3.416 Kg 0.42 0.42884 8843 3 Kg

6.61394 6.61394 15.0621 15. 0621 0.36083 0.3 6083 0.55116 0.5 5116

3 6.832 0.16 0.16366 3669 9 0.25

Kg Kg Kg Kg

7428 10152 17580

Kg Kg Kg

lb. lb. lb. lb.

16376.1 lb. 16376.1 22381.6 2238 1.6 lb. 38757.7 3875 7.7 lb.


Page : 114 of 126



Project : Design & Procurement of ASME Pressure Vessel Project : Design & Procureme Procurement nt of ASME Pressure Vessel Seri Serial al No. No. : 7434 7434-3 -333-UU-20 2006 06 Dwg. Dwg. No. No. : 7434 7434-3 -333-3A 3A,, Rev Rev. 1 Vessel Vess el : Deputani Deputanizer zer Reflux Receiv Receiver er Drum Item No. : 1-D-5 Capacity : 10.152 M3

Date : 18.2.2004 Job No. : 7434-33


T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method

Shell material Heads material Saddles material Heads type Design temperature Vessel internal pressure, P Allowable stress in shell, Sts Allowable Allowable stress in heads, Sth Allowable stress in web, Sw Shell compression yield point, Y Saddle & anchor bolt com pression yield yield point, Re Outer shell diameter, Do Wall nominal thickness of shell, ts Wall nominal thickness of heads (min.), th Corrosion allowance for shell & heads, Cas Shell joint efficiency, Es Head j oint efficiency, efficiency, Eh

ASME SA516 Grade 70 ASME SA516 Grade 70 ASME SA283 Grade C Ellipsoidal Ellipsoi dal 2:1 o 149 F 65 255.682 255. 682 PSI PSIG G 18 200 000 00 PSIIG PS 1408 200 000 00 PSIIG PS 1408 157 570 00 PSIIG PS 1105.28 320 200 00 PSIIG PS 2252.8 300 000 00 PSIIG PS 2112 62.9918 62. 9918 IN INCH CH 1600 0.866 INCH 22 0.7874 INCH 20 0.236 INCH 6 0.85 0.85

Head internal depth, h Head depth -to- tangent line (external depth), Ho Insulation thickness, tis Wear (reinf./top flange) plate width, B Wear (reinf./top flange) plate thickness, tf Wall corroded thickness of shell Wall corroded thickness of heads Wall corroded thickness of shell + reinf. plate Outer shell radius, Ro = Do / 2 Shell length from Tangent - to - tangent (T/T), L Saddle - to - saddle distance distance (S/S), L" Transverse distance between anchor bolts, Y

15.315 15.3 15 16.1 16 .102 02 0 14.9 14 .961 61 0.551 0.236 0.551 0.787 31.4 31 .496 96 189.764 189. 764 145.669 145. 669 39.3701 39. 3701

INC NCH H INC NCH H INCH INC NCH H INCH INCH INCH INCH INC NCH H INCH IN CH INCH IN CH INCH IN CH

389 409 0 380 14 6 14 20 800 4820 3700 1000

MM MM MM MM MM MM MM MM MM MM MM MM

Distance from tangent line -to- center of saddle support, A Saddle contact angle, B Longitudinal Longitudinal width of sad dle at shell, b Transverse width of saddle at shell (baseplate length), m Height of saddle to vessel center line, Z Web width of saddle, hs Web thickness of saddle, tw Equivalent Equivalent diameter of vessel, Deq = 1.5 (Do + 2 * tis) Equivalent length of vessel, Leq = L + 2Ho + 2 tis

22.047 22.0 47 120 14.9 14 .961 61 62.9 62 .992 92 70.8 70 .866 66 62.9 62 .992 92 0.551 94.4 94 .488 88 221.969 221. 969

INC NCH H Degree INC NCH H INC NCH H INC NCH H INC NCH H INCH INC NCH H INCH IN CH

560

MM

380 1600 1800 1600 14 2400 5638


o

C

Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G

MM MM MM MM


Page : 115 of 126




Date : 18.2.2004

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) 1. Seismic & wind forces on vessel UBC-1997 a. Seismic force Tot otal al de des sign fo forc rce e or sh shea earr at the ba base se,, F = z . I . C . Wt / Rw 5329 53 29.1 .18 8 lb Seismic Zone 2A : For zone 2A : z = Seismic zone factor 0.15 [Table No. 23-I] I = Importance factor 1 [Table No. 23-L] C = Numerical Num erical coefficient 2.75 Max. [Table No. 23-P] Rw = Numerical coefficient 3 [TableS NoS. 23-O & 23-Q]

Job No. : 7434-33


2417 2417.2 .25 5

Kg

17580

Kg

= 3 ( horizontal vessel vessel on pier) pier)

Total vessel dead weight, Wt

38757. 387 57.7 7 lb

b. Wind force F = Cf . Gh . qz . Af qz = 0.00256 . kz . (I V) 2 For exposure C : h = Height kz = Velocity V elocity pressure exposure coefficient Wind Velocity, V = Basic wind speed Gh = Gust response factor Cf = Force coefficient

ANSI A58.1 27.084 27. 0848 8 PSF

13.49792 N/M2

0-15 0.8 115 1.32 0.8

51.3 51.399 99

M/Sec /Sec..

2417 2417.2 .25 5 6.58192 192 919. 919.122 1228 8 2417 2417.2 .25 5

Kg 2 M Kg Kg

Ft MPH

c. Forces in longitudinal direction

Figure ( 6 )

Seismic longitudinal force, Fls = z . I . C . Wt / Rw Wind longitudinal exposed area, Afl = (pi/8*Deq + Z) * Deq Wind longitudinal force, Flw = Cf . Gh . qz . Afl Fl = Greater value of Fls & Flw

5329.18 5329. 18 70.847 70. 8472 2 2026. 202 6.34 34 5329. 532 9.18 18

lb 2 Ft lb lb


Page : 116 of 126




Date : 18.2.2004 Job No. : 7434-33


T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) d. Forces in transverse direction

Figure ( 7 )

Seismic transverse force, Fts = 0.5 Fls = 0.5 x z x I x C x Wt / Rw Wind transvere exposed area, Aft = Deq * Leq Wind transverse force, Ftw = 0.5 x Cf x Gh x x qz x Aft Ft = Greater value of Fts & Ftw

2664.59 2664. 59 145.6 145 .649 49 2082. 208 2.89 89 2664. 266 4.59 59

lb Ft2 lb lb

1208. 1208.62 625 5 13.5312 312 944. 944.772 7727 7 1208. 1208.62 625 5

Kg M2 Kg Kg

19378. 193 78.8 8 lb

8790

Kg

2. Reaction force per saddle support a. Reaction due to full vessel weight, Qo = Wt/2 b. Reaction in longitudinal direction due to earthquake & wind : By taking moments about saddle support support : Fl . Z = Ql . L" Ql = Fl . Z / L" c. Reaction in transverse direction due to earthquake & wind : By taking moments about saddle support support : Ft . Z = Qt . (m/2) Qt = 3 ( 2 . Ft . Z / m)

2592.57 lb

1175. 1175.95 959 9 Kg

17986

lb

8158. 8158.21 219 9 Kg

d. Max. reaction due to earthquake & wind, Qmax. = Max. (Ql , Qt)

17986

lb

8158. 8158.21 219 9 Kg

e. Total reaction due to full vessel weight, weight, earthquake and wind, Q Total longitudinal reaction, Qlt = Qo + Ql Total transverse reaction, Qtt = Qo + Qt Q = Greater value of Qlt & Qtt

21971.4 21971. 4 lb 37364. 373 64.8 8 lb 37364. 373 64.8 8 lb

9965. 9965.95 959 9 Kg 16948 16948.2 .22 2 Kg 16948 16948.2 .22 2 Kg

3. Modified stresses at saddles : Ratio (Qo + Qmax.) / Qo

1.92813

a. Modified circumferential stresses, SIG5' = Ratio .

b. Modified tangential stress es,

<

OK

SIG 5' = Ratio .

<

OK

SIG 4' = Ratio .

<

OK

<

OK

SIG 2' = Ratio .


Page : 117 of 126




Date : 18.2.2004 Cli Client ent : APRC PRC Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) a. Stresses in longitudinal direction Longitudinal Longitudin al force, for ce, Fl 5329. 532 9.18 18 lb Max. moment, Mmax. = Fl . Z 377658 3776 58 lblb-in in..

2417. 2417.27 278 8 Kg 4351.09 4351.091 1 Kg-M

Job No. : 7434-33

Figure ( 8 )

Cross-sectional Area, A = Lw * tw + 2 Sw * ts+ 2(n-2) Rw * ts 3 3 3 3 Moment of inertia, Ix-x = Lw*tw /12+(n-2) ts*Sw /12+2ts(Sw -tw )/12 2 2 3 3 Section modulus, Wx-x =Lw*tw /6+2ts*Sw /6+2ts(Sw -tw )/(6 Sw) Dimension X1 = Ix-x / Wx-x Bending stress, Sb = Mmax. / Wx-x Allowable Allow able bending stress, S' = 1.2 . S Shear stress, T = Fl / A Allowable Allow able shear stress, S' = 0.5 . S b. Stresses in transverse direction Transverse force, Ft Max. moment, Mmax. = Ft . Z

56.2899 56.2899 221.512 221. 512 44.5915 44. 5915 4.96758 4.9 6758 8469.26 8469 .26 188 884 40 94.6738 94. 6738 7850 OK

INCH2 INCH 4 INCH IN CH 3 INCH IN CH INCH IN CH PSIG PSI G PSIIG PS PSIG PSI G PSIG

2664.59 2664. 59 lb 188829 1888 29 lblb-in in..

36316 92200201 730724. 730724.6 6 126.1764 126.1764 596.2362 1326.336 6.665034 552.64

MM2 4 MM 3 MM MM Kg/CM2G Kg/CM2G Kg/CM2G Kg/CM2G

1208. 1208.63 639 9 Kg 2175.54 2175.546 6 Kg-M

Figure ( 9 )

Cross-sectional Area, A 56.2899 56. 2899 3 3 3 Moment of inertia, Iy-y = tw*Lw /12+Sw[(Lw+2ts) -Lw ]/12+2Rw((Ss(n-1-2)+ts) 2242 22429.5 9.5 2 3 3 Section modulus, Wy-y =tw*Lw /6+Sw*[(Lw+2ts) -Lw ]/6(Lw+2ts)]+2Rw[(Ss+ts 80 804. 4.78 78 Dimension Y1 = Iy-y / Wy-y 27.8703 27. 8703 Bending stress, Sb = Mmax. / Wy-y 234.6 234 .634 34 Allowable Allow able bending stress, S' = 1.2 . S 18840 OK Shear stress, T = Ft / A 47.336 47. 3369 9 Allowable Allow able shear stress, S' = 0.5 . S 7850 OK

2

2

INCH INCH INCH IN CH4 3 INC NCH H INCH IN CH PSI PSI

36316 9.34E+0 9.34E+09 9 13187989 707.9063 707.9063 16.51823 1326.336

MM MM4 3 MM MM

PSI PSI

3.332517 Kg/CM2G Kg/CM2G 552.64

Kg/CM2G Kg/CM2G


Page : 118 of 126




Date : 18.2.2004 Job No. : 7434-33


T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) 1. Bending moment & bending stress at saddles Bending moment at sad dle in tension & compression, M1

M

1

=

 A R 2 −H  1− + L 2A L  Q A  1− 4H 1+   3L 

2

      

2

823586 823 586

lb-i lb -in n

9488.74 9488.744 4 Kg-M 2

-1589.87 PSIG

201.4689 Kg/CM G 2 -111.9271 Kg/CM G

3333925 lb-i lb-in n

38411.0 38411.02 2 Kg-M

Longitudinal Longitudinal bending stress at midspan, S1' = - M1' / 3.14 R2 ts

-1235.31 PSIG

-86.9661

Kg/CM G

3. Stress in the shell due to internal pressure, S = P R / (2 Es ts)

5470.01 PSIG

385. 385.08 089 9

Kg/C Kg/CM M2

4. Sum of tensile stress Value of S1 + S

8331.79 8331 .79 PSI PSIG G -2825.19 PSIG

586.5578 Kg/CM G 2 -198.8932 Kg/CM G

8331.79 8331 .79 PSI PSIG G

586.5578 Kg/CM G

200 000 00 PSIIG PS 0.41659 < 1

1408 Passed

1106.25 1106 .25 PSI PSIG G

77.8801 77.88014 4 Kg/CM Kg/CM G

160 600 00 PSIIG PS 0.06914 < 1

1126. 26.4

Longitudinal Longitudinal bending stress in tension, S1 = M1 / K1 R ts

2861.77 2861 .77 PSI PSIG G 2

Longitudinal Longitudinal bending stress in comp ression, S1 = - M1 / K8 R ts 2. Bending moment & bending stress at midspan Bending moment at midspan, M2 ' 1 =

M

 R 2 − H2  1+ 2 L2 QL  4H  1+  3L 

 

−

4 A L 

 

'

Value of S1 + S Greater value of (S 1 + S) &

(S1'

+ S)

Shell allowable tensile stress Stress ratio = Greater stress/Allowable stress/Allowable stress

2

2

2

Kg/CM G

5.Tangential shear stress, S2 5.a. Tangential shear stress on shell, S 2 In case of A > R/2 and ring not used or rings are adjacent to the saddle. 

S2

=

K2 Q L  R ts  L





− +

2 A  4 H

2



3 

Shell allowable tangential tangential stress = 0.8 S Stress ratio = S2 / 0.8 S

Passed

Kg/ Kg/CM2G


Page : 119 of 126




Date : 18.2.2004 Job No. : 7434-33


T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) 5.b. Tangential shear stress on shell, S 2 In case of A > R/2 and ring used in plane of saddle. K

Q

  L −2A   L+ 4H  3 

     

301.362 301. 362 PSI PSIG G

21.2158 21.21585 5 Kg/CM Kg/CM2G

160 600 00 PSIIG PS 0.01884 < 1

1126. 26.4

1216.68 1216 .68 PSI PSIG G

85.6541 85.65414 4 Kg/CM Kg/CM G

Head allowable tangential tangential stress = 0.8 S Stress ratio = S 2 / 0.8 S

160 600 00 PSIIG PS 0.07604 < 1

1126. 26.4

5.d. Tangential shear stress on shell In case of A <= R/2 S2 = K4 Q / R ts Shell allowable tangential tangential stress = 0.8 S Stress ratio = S2 / 0.8 S

1205.51 PSIG 160 600 00 PSIIG PS 0.07534 < 1

84.8681 84.86817 7 Kg/CM Kg/CM G 1126. 26.4 Kg/ Kg/CM2G

5.e. Tangential shear stress on head In case of A <= R/2

1325.85 1325 .85 PSI PSIG G

93.33971 Kg/CM G

160 600 00 PSIG PSI 0.08287 < 1

1126. 26.4

S2

=

3

R ts

Shell allowable tangential tangential stress = 0.8 S Stress ratio = S 2 / 0.8 S

Kg/ Kg/CM2G

Passed

5.c. Tangential shear stress on head, S 2h In case of A > R/2 and ring not used or rings are adjacent to th saddle. S

2h

=

K

2

R t

Q h

   L−2A  4H  L+ 3 

     

S2 = K4 Q / R t h

Shell allowable tangential tangential stress = 0.8 S Stress ratio = S2 / 0.8 S 5.f. Additional tangential shear stress in head In case of A <= R/2 S3 = K5 Q / R t h

2

Kg/ Kg/CM2G

Passed

2

Passed

2 2

Kg/ Kg/CM G

Passed

604.1 604 .165 65 PSI

2 42.53321 Kg/CM G

S3 + stress due to int. pres. (PR/(2Es ts)

5470.01 PSI

385. 385.08 089 9

Kg/C Kg/CM MG

Head allowable tensile stress = 1.25 S Stress ratio = S3 / 1.25 S

25000 0.2188

1760

Kg/CM2G

PSI <1

Passed

2


Page : 120 of 126




Date : 18.2.2004 Job No. : 7434-33


T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) 6. Circumferential stress 6.a. Circumferential stress at saddle horn In case of L >= 8 R (unstiffened) S 4

=−

Q

.56 Rts ) 4ts (b+1

−

3K 6Q 2

2ts

Shell allowable circumferential circumferential stress = 1.5 S Stress ratio = S4 / 1.5 S

2

-1806.46 PSIG

-127.1747 -127.1747 Kg/CM G

300 000 00 PSIIG PS 0.06022 < 1

2112

-2828.5

-199.1262 -199.1262 Kg/CM G

Kg/CM2G

Passed

6.b. Circumferential stress at saddle horn In case of L < 8 R (unstiffened)

S4 =−

Q

12K6 QR

4 ts (b +1.56 R ts )

−

2 Lts

Shell allowable circumferential circumferential stress = 1.5 S Stress ratio = S4 / 1.5 S

PSIG

2

Kg/CM2G

300 000 00 PSIG PSI 0.09428 < 1

2112

-1419.03 PSIG

-99.89967 -99.89967 Kg/CM G

160 600 00 PSIIG PS 0.08869 < 1

1126. 26.4

22531

Effective web area, Aw = hs tw

lb 2 34.7086 INCH

10219 10219.7 .78 8 Kg 2 22392.6 MM

Stress in web, Sw = Fw / Aw Allowable Allowable stress in web, Saw = 0.6 Y Stress ratio = Sw / 0.6 Y

649.147 PSI 649.147 PSIG G 180 800 00 PSIIG PS 0.03606 < 1

45.6999 45.69996 6 Kg/CM Kg/CM G 1267. 67.2 Kg/ Kg/CM2G

Vertical force in in web, Fv Fv = Q Stress in web, Sv = Fv / Aw Allowable Allowable stress in web (compressiuon), Saw = 0.33 Y Stress ratio = Sv / 0.33 Y

37364.8 37364. 8 1076. 107 6.53 53 9900 0.10874

16948 16948.2 .22 2 Kg 488. 488.300 3004 4 Kg 2 696.96 6.96 Kg/ Kg/CM G

Passed

6.c. Circumferential stress at bottom of shell (stiffened or unstiffened)

S

5

=

K

−

t

s

(b

+

7

Q

1 . 56

R t

0.5 compression yield point of shell material Stress ratio = S5 / 0.5 S 7. Check tension in web saddle Horizontal force in web, Fw = K8 Q

s

2

)

lb lb PSIG <1

2

Kg/ Kg/CM G

Passed

2

Passed

Passed


Page : 121 of 126




Date : 18.2.2004 Job No. : 7434-33


T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.) 8. Check of the saddle at the lowest section (web plate thickness) : The saddle at the lowest section must resist the horizontal force (F). The effective cross section of the saddle to resist this load is R/3.

Figure (10)

F = K11 . Q To resist this force, the effective area of web plate, A = (R/3) . tw The calculated stress, Scal. = F / A The allowable stress, Sall. = (2/3) Sw Stress ratio = Scal. / Sall. So, the thickness of the web plate is satisfactory for horizontal force (F).

Values of Constant K For contact angle B = 120o : K1 (K1 = 3.14 if the shell is stiffened by ring or head, A > R/2)

7622.42 7622. 42 5.78668 5.7 8668 1317.24 1317 .24 10466.7 1046 6.7 0.12585

lb INCH IN CH2 PSIG PSI G PSIG PSI G <1

3457. 3457.43 437 7 3733.33 3733.333 3 92.7334 92.73342 2 736.8534 736.8534

Kg MM2 Kg/CM Kg/CM2G 2 Kg/CM Kg/CM G

Passed

120o 0.335

K2

1.171

K3 (K3 is constant for any contact angle)

0.319

K4

0.88

K5

0.401

handbook) K6 (K6 depends on the ratio A/R, see chart in vessel handbook)

K6 for A/R > 1.00

0.053

K6 for A/R < 0.5

0.013 22.0 22 .047 47 INC NCH H 560 31.4 31 .496 96 INC NCH H 800 0.69999 0.0238 [From table]

A R A/R K6 for A/R = 0.69 K7

0.76

K8

0.603

K11

0.204

MM MM


Page : 122 of 126




Date : 18.2.2004 Job No. : 7434-33


U. Check for the Anchor Bolts Due to Seismic and Wind Loading 1. For longitudinal forces, Fl

Figure (11)

Fl Max. moment, Mmax. = Fl . Z Cross-sectional area per anchor bolt, Ab (7/8" M26) No. of anchor bolts per saddle, nb Total cross-sectional area of anchor bolts, A = nb . Ab

5329.18 377658 3776 58 0.419 4 1.676

lb. lb-in lbin.. INCH2 each INCH2

2417 2417.2 .25 5 Kg 4351.09 4351.091 1 Kg-M 270. 270.32 322 2 MM2

Shear stress, T = Fl / A Bending stress, Sb = Mmax. / (A . L") Resultant stress, Si = SQRT (Sb 2 + 3 T2 ) Allowable Allow able stress, S' = 0.5 . Re

3179.7 3179 .7 1546.88 1546 .88 5720.52 5720 .52 150 500 00

PSIG PSI PSIG PSI G PSIG PSI G PSIIG PS

223. 223.85 851 1 108.9005 108.9005 402.7246 402.7246 1056 OK

1081.28 1081.288 8 MM2 Kg/C Kg/CM M2G 2 Kg/CM Kg/CM G Kg/CM Kg/CM2G Kg/CM2G

2. For transverse forces, Ft

Figure (12)

Ft Max. moment, Mmax. = Ft . Z Cross-sectional area per anchor bolt, Ab (7/8" M26) No. of anchor bolts per saddle, nb Total cross-sectional area of anchor bolts, A = nb . Ab

2664.59 188829 1888 29 0.419 4 1.676

lb. lb-in lbin.. 2 INCH each 2 INCH

1208. 1208.63 639 9 Kg 2175.54 2175.546 6 Kg-M 2 270. 270.32 322 2 MM

Shear stress, T = Ft / A Bending stress, Sb = 2 Mmax. / (A . Y) 2 2 Resultant stress, Si = SQRT (T + 3 Sb ) Allowable Allow able stress, S' = 0.5 . Re

1589.85 1589.85 5723.45 5723 .45 100 004 40 150 500 00

PSIG PSIG PSIG PSI G PSIIG PS PSIIG PS

111.9255 111.9255 402.9309 402.9309 706.8149 706.8149 1056 OK

2

1081.28 1081.288 8 MM

2

Kg/CM Kg/CM G Kg/CM Kg/CM2G 2 Kg/CM Kg/CM G Kg/CM2G


Page : 123 of 126




Date : 18.2.2004 Job No. : 7434-33


V. Lifting Lugs Thickness Calculations (Reference : Pressure Vessel Handbook) Check of the thickness of lifting lugs : Material Allowable tensile strength Allowable Allowable shear strength = 0.49 St By neglecting the effect of b oth wind loads and pipe thrust, assume 2 (two) lifting lugs with dimensions shown in Figure (13). Leg of fillet fillet weld, h = the thinner thinner of thicknesses thicknesses joined = 10 MM (0.394 INCH)

ASME SA 516 Grade 70 200 000 00 PSIIG PS 1408 9800 PSIG 689.92 9.92

Kg/CM2G Kg/ Kg/CM2G

Figure (13)

Height of lifting lug, L Thickness of lifting lug, b Fillet weld, h Length of lifting lug, l F = Wt / (SQRT2) Vertical component of F, F1 = F/ SQRT2 Horizontal component of F, F2 = F1 Average unit stress = 0.707 * F1 / h * I Max. expected expected normal stress : 2 2 = F2 / (h*I *(b+h))*SQRT(2L +(b+h) )) < Allowable shear strength

6.49606 6.49606 0.86614 0.8 6614 0.64961 0.6 4961 7.08661 7.0 8661 27405.8 2740 5.8 19378.8 1937 8.8 19378.8 1937 8.8 3241.38 3241 .38

INCH INCH INCH IN CH INCH IN CH INCH IN CH lb. lb. lb. PSIG PSI G

298.273 PSI 298.273 PSIG G 9800 PSIG PS OK

165 22 16.5 180 12430 12430.9 .94 4 8790 8790 2.28192 2.281928 8

MM MM MM MM Kg Kg Kg 2 Kg/CM Kg/CM G 2

0.20998 0.209984 4 Kg/CM Kg/CM G 6.8992 Kg/ Kg/CM2G


Page : 124 of 126




Date : 18.2.2004 Job No. : 7434-33


V. Lifting Lugs Thickness Calculations (cont.) (Reference : Pressure Vessel Handbook)

Figure (14)

L b l R r

6.49606 6.49606 0.86614 0.8 6614 7.08661 7.0 8661 2.95276 2.9 5276 1.18 1. 1811 11

INCH INCH INCH IN CH INCH IN CH INCH IN CH INC NCH H

165 22 180 75 30

MM MM MM MM MM


Page : 125 of 126

According to ASME Code, Section VIII , Division 1, Edition 2001, Addenda 2002 Designed by : Eng. Abdel Monem Mohamed, Process Design Dept.Manager



Date : 18.2.2004 Job No. : 7434-33


W. Mesh Pad/Blanket (Demister) Calculation.

Mesh Pad (Dem ister) Material, Stainless Steel

TP 316

Denisty of liquid, p l

31.786

lb/ft

Denisty of vapour, p v

1.3162

3

3

509.48

Kg/M

lb/ft

21.0966

Kg/M

ft//Se ft Sec. c.

0.51328 0.513283 3 M/Sec. M/Sec.

Factor, K

1.684 1.68 4 0.35

Design velocity, VD = 0.75 Va Mesh pad thickness

1.263 1.26 3 6

ft//Se ft Sec. c. INCH

0.38496 0.384963 3 M/Sec. M/Sec. 152.4 MM

0.5

Allowable Allowabl e superficial vapour velocity across inlet f ace of m esh,V a a = K [pl - p v v ]/p v v ]

2

Pressure drop through wire mesh, Delta P = 0.12 V D p v

3

0.25195 0.2 5195 IN INCH CH Water

3


Page : 126 of 126




Date : 18.2.2004

X. References

The following following references are used in the design calculations of saddles and lifting lugs of pressure vessel under considerations. 1. ASME Boiler and Pressure Vessel Code, Section VIII, without Addendum. Division 1, 2001 Edition, without 2. "Pressure Vessel Design Handbook", Handbook" , Edition 1981, by Henry H. Bednar, P.E. published by Van Nostrand Reinhold Reinhold Co. 135 west 50th. street, New York, N.Y. 10020, USA. 3. "Modern Welding Technology", Technology", Edition 1989, by Howard B. Carry, Prentice Hall, Englewood Cliffs, New Jersey 07632, USA.. 4. "Pressure Vessel Handbook", Handbook" , Fifth Edition January 1981, by Eugene F. Megyese, Publishing Inc., P.O. Box 35365, Tulsa, OK 74135, USA.

‫د אא‬ª 

Job No. : 7434-33


Pressure Vessel Design Calculations

Recommend Documents