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AKTEK DESIGN DEPARTMENT
DOCUMENT CODE/NO
AKTEK F0406GD-TEK113R0-035-F1/IA
EC 13-P113/2
AKTEK TECHNOLOGY ENGINEERING CO.LTD PRESSURE VESSELS DIVISION. www.aktektechnology.com
PRESSURE VESSEL DESIGN CALCULATIONS Item: Vessel No:
40"-48" 600# PIG TRAP TR100 TURKISH PIPELINE NATURAL GAS PETROLEUM TRANSPORTATION GOVERMENT COMPANY C-45490-R56 MECH.ENG.IHSAN AKGUN Çarşamba , Eylül 20, 2006 4048_600# PIG TRAP
Customer: Contract: Designer: Date: Vessel Name:
NQA – 1,2006 Edition #1, Revision 0 Dated 20-10-2006
CONTROLLED #
UNCONTROLLED#
HC
10.2006
IA
IA
10.2006
PM
Name
Date
Name
Name
Date
Status
Prepared, revised
Checked
BAYINDIR – MESCİOĞLU NAZİLLİ İZMİR DOĞALGAZ İLETİM HATTI – FAZ 4
AKTEK Version:00 created 03/98
Project Name 40”-48” 600# PIG L/R TRAP File:00135r02.xls
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DCC
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AKTEK TECHNOLOGY ENGINEERING CO.LTD. TURKEY www.aktektechnology.com
PRESSURE VESSEL DESIGN CALCULATIONS Item:
40"-48" 600# PIG L/R TRAP
Vessel No:
TR100
Customer:
BAYINDIR-MESCIOGLU
Contract:
C-45490-R56
Designer:
MECH.ENG.IHSAN AKGUN
Date:
Çarşamba , Eylül 20, 2006
Vessel Name:
4048_600# PIG TRAP
JOINT VENTURE
Completed
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INDEX 123456789101112131415161718192022232426 27 30 40 43 44 47 50 62 63 75 87 100 112 124 136 150 151 152 159 166 167 184 201 218 235 252 268
Completed
BASIC COVER PAGE DESIGN COVER PAGE INDEX VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID VIEW SOLID REVISION HISTORY Design Basic Settings Summary Deficiensies Summary Nozzle Schedule Nozzle Summary Pressure Summary Thickness Summary Weight Summary Hydrostatic Test Summary Vacuum Summary MAJOR BARREL TRANSITION MINOR BARREL ASME B16.5/16.47 Blind on Flange #35 Straight Flange on Ellipsoidal Head #1 Ellipsoidal Head #1 DREYN NOZZLE - Nozzle #7 (N7) Flange #35 KICKER NOZZLE - Nozzle #1 (N1) KICKER NOZZLE - Nozzle #2 (N2) PIG SIGNALLER - Nozzle #8 (N8) PRESSURE INDICATOR - Nozzle #4 (N4) SAFETY VALVE NOZZLE - Nozzle #5 (N5) VENT NOZZLE - Nozzle #2 (N2) SADDLE #1 Seismic Code Wind Code Lifting Lug #1 Lifting Lug #2 NOZZLE FINITE ELEMENT ANALYSIS KICKER NOZZLE-1 FINITE ELEMENT ANALYSIS SAFETY VALVE NOZZLE FINITE ELEMENT ANALYSIS PRESSURE INDICATOR NOZZLE FINITE ELEMENT ANALYSIS VENT NOZZLE FINITE ELEMENT ELEMENT ANALYSIS DREYN NOZZLE FINITE ELEMENT ANALYSIS KICKER NOZZLE-2 FINITE ELEMENT ANALYSIS PIG SIGNAL FINITE ELEMENT ANALYSIS
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1.1.1.1 Revision History No.
Date
Operator
Notes
0
9/20/2006
IHSAN AKGUN
FOR APPROVED
1
2
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1.1.1.2 Design Basic Settings Summary 1.1.1.3 Units: English 1.1.1.4 Datum Line Location: 0,00" from right seam 1.1.1.5 Design ASME Section VIII Division 1, 2004 Edition Design or Rating: Minimum thickness: Design for cold shut down only: Design for lethal service (full radiography required): Design nozzles for: Corrosion weight loss: UG-23 Stress Increase: Skirt/legs stress increase: Minimum nozzle projection:
Get Thickness from Pressure 1/16" per UG-16(b) No No Design P, find nozzle MAWP and MAP 100% of theoretical loss 1,20 1,0 6,0000" Yes Preheat P-No 1 Materials > 1,25" and <= 1,50" thick: No Pipe under-tolerance is not applied to cylindrical shell thicknesses. Pipe under-tolerance is not applied to nozzle wall thicknesses. Butt welds are tapered per Figure UCS-66.3(a). 1.1.1.6 Hydro/Pneumatic Test Shop Hydrotest Pressure: 1,3 times vessel MAWP Test liquid specific gravity: 1,00 Field Hydrotest Pressure: 1,3 times design P Wind load present @ field: 33% of design Maximum stress during test: 90% of yield 1.1.1.7 Code Interpretations Apply interpretation VIII-1-83-66: Yes Apply interpretation VIII-1-86-175: Yes Apply interpretation VIII-1-83-115: Yes Apply interpretation VIII-1-01-37: Yes Disallow UG-20(f) exemptions: No 1.1.1.8 UG-22 Loadings UG-22 (a) Internal or External Design Pressure : UG-22 (b) Weight of the vessel and normal contents under operating or test conditions: UG-22 (c) Superimposed static reactions from weight of attached equipment (external loads): UG-22 (d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: UG-22 (f) Wind reactions: UG-22 (f) Seismic reactions:
Yes Yes No Yes Yes Yes
Note: UG-22 (b),(c) and (f) loads only considered when supports are present.
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1.1.1.9 Deficiencies Summary No deficiencies found.
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1.1.1.10 Nozzle Schedule Materials Nozzle mark
Service
Size Nozzle
Impact Norm
Fine Grain
Pad
Impact Norm
Fine Grain
Flange
N1
KICKER NOZZLE Nozzle #1
14" Sch 160
SA-106 B Smls pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
N2
VENT NOZZLE Nozzle #2
SA-106 2" XX B Smls Heavy pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
N2
KICKER NOZZLE Nozzle #2
14" Sch 160
SA-106 B Smls pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
N4
PRESSURE INDICATOR Nozzle #4
SA-106 2" XX B Smls Heavy pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
N5
SAFETY VALVE NOZZLE Nozzle #5
SA-106 1" XX B Smls Heavy pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
N7
DREYN NOZZLE Nozzle #7
SA-106 4" XX B Smls Heavy pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
N8
PIG SIGNALLER Nozzle #8
SA-106 2" XX B Smls Heavy pipe
No
No
No
API 5L X65 (user No defined)
No
No
WN A105 600#
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1.1.1.11 Nozzle Summary
Nozzle mark
OD (in)
tn (in)
Reinforcement Pad
Shell
Req tn A1? A2? (in)
Nom t Design t User t (in) (in) (in)
Width (in)
Corr (in)
Aa/Ar (%)
tpad (in)
N1
14,00 1,4060 0,5107 Yes Yes 0,6880 0,6880
6,0000 1,0000 0,0000 103,4
N2
2,38
0,6880 0,6880
4,0000 1,1000 0,0000 102,5
N2
14,00 1,4060 0,5107 Yes Yes 0,6880 0,6880
6,0000 1,0000 0,0000 103,4
N4
2,38
0,4360 0,1347 No
No
0,6880 0,6880
4,0000 1,1000 0,0000 102,5
N5
1,32
0,3580 0,2344 No
No
0,6880 0,6880
4,0000 0,6880 0,1180 115,8
N7
4,50
0,6740 0,2074 Yes Yes 0,6880 0,6880
4,0000 1,2000 0,0000 100,0
N8
2,38
0,4360 0,1347 Yes Yes 0,6880 0,6880
4,0000 1,0000 0,0000 130,4
0,4360 0,1347 No
No
tn: Nozzle thickness Req tn: Nozzle thickness required per UG-45/UG-16 Nom t: Vessel wall thickness Design t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37 User t: Local vessel wall thickness (near opening) Aa: Area available per UG-37, governing condition Ar: Area required per UG-37, governing condition Corr: Corrosion allowance on nozzle wall
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1.1.1.12 Pressure Summary Pressure Summary for Chamber bounded by Ellipsoidal Head #1 and ASME B16.5/16.47 Blind on Flange #35
Identifier
P T MAWP Design Design ( psi) ( psi) (°F)
Total MDMT Rating Te MAEP Corrosion Impact external ( psi) Allowance Test MDMT (°F) Exemption (in) (°F)
MAP ( psi)
ASME B16.5/16.47 Blind on Flange #35
1088,0 150,0
1412,86 1480,00 N/A
MAJOR BARREL
1088,0 150,0
-40,0
Note 1, 2
0,000
No
1882,81 1884,95 125,30 150,0
N/A
N/A
0,000
Yes
Transition #1 1088,0 150,0
1088,00 1748,68 15,00
150,0
N/A
N/A
0,000
Yes
MINOR BARREL
1088,0 150,0
2265,20 2267,20 267,63 150,0
N/A
N/A
0,000
Yes
Straight Flange on Ellipsoidal Head #1
1088,0 150,0
1122,77 1124,74 549,16 150,0
-20,0
Note 4
0,000
No
Ellipsoidal Head #1
1088,0 150,0
1155,31 1157,29 541,99 150,0
-20,0
Note 3
0,000
No
Flange #35
1088,0 150,0
1412,86 1480,00 N/A
150,0
-40,0
Note 1, 2
0,000
No
Saddle #1
1088,0 150,0
1088,00 N/A
N/A
N/A
N/A
N/A
N/A
KICKER NOZZLE Nozzle #1 (N1)
1088,0 150,0
1413,85 1480,00 125,30 150,0
-20,0
Nozzle Note 5
0,000
No
VENT NOZZLE Nozzle #2 (N2)
1088,0 150,0
1415,00 1480,00 125,30 150,0
-55,0
Nozzle Note 6
0,000
No
KICKER NOZZLE Nozzle #2 (N2)
1088,0 150,0
1413,85 1480,00 125,30 150,0
-20,0
Nozzle Note 5
0,000
No
PRESSURE INDICATOR - Nozzle #4 (N4)
1088,0 150,0
1415,00 1480,00 125,30 150,0
-55,0
Nozzle Note 6
0,000
No
SAFETY VALVE NOZZLE Nozzle #5 (N5)
1088,0 150,0
1415,00 1480,00 125,30 150,0
-55,0
Nozzle Note 6
0,118
No
Completed
N/A
150,0
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DREYN NOZZLE Nozzle #7 (N7)
1088,0 150,0
1398,46 1400,50 125,30 150,0
-55,0
Nozzle Note 6
0,000
No
PIG SIGNALLER - Nozzle #8 (N8)
1088,0 150,0
1414,69 1480,00 267,63 150,0
-46,5
Nozzle Note 7
0,000
No
Chamber design MDMT is -20,00°F Chamber rated MDMT is -20,00°F @ 1088,00 psi Chamber MAWP hot & corroded is 1088,00 psi @ 150,0°F This is governed by a juncture of the transition Transition #1. Chamber MAP cold & new is 1124,74 psi @ 70,0°F Chamber MAEP is 15,00 psi @ 150,0°F Vacuum rings did not govern the external pressure rating.
1.1.1.13 Notes for MDMT Rating: Note #
Exemption
Details
1.
UCS-66(b)(1)(b)
2.
Bolts rated MDMT per Fig UCS-66 note (e) = -40 °F
3.
Straight Flange governs MDMT
4.
Material is impact test exempt per UG-20(f)
UCS-66 governing thickness = 0,688 in
5.
Nozzle is impact test exempt per UG-20(f)
UCS-66 governing thickness = 1 in.
6.
Flange rating governs: UCS-68(c) applies. UCS-66(b)(1)(b) Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F
7.
Flange rating governs:
UCS-66(b)(1)(b)
Design notes are available on the Settings Summary page.
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1.1.1.14 Thickness Summary
Component Identifier
Material
Diameter (in)
Length (in)
Nominal t (in)
Design t (in)
Joint E
Load
MAJOR BARREL
API 5L X65 (user defined)
48,00 OD
177,00 0,6880
0,3999
1,0000 Internal
Transition #1
API 5L X65 (user defined)
40,00/48,00 OD
20,00
0,6880
0,4306
1,0000 Internal
MINOR BARREL
API 5L X65 (user defined)
40,00 OD
110,00 0,6880
0,3332
1,0000 Internal
Straight Flange on Ellipsoidal Head #1
SA-516 70
40,00 OD
3,00
1,1000
1,0668
1,0000 Internal
Ellipsoidal Head #1
SA-516 70
40,00 OD
10,55
1,1000*
1,0357
1,0000 Internal
Nominal t: Vessel wall nominal thickness Design t:
Required vessel thickness due to governing loading + corrosion
Joint E:
Longitudinal seam joint efficiency
*
Head minimum thickness after forming
Load internal:
Circumferential stress due to internal pressure governs
external:
External pressure governs
Wind:
Combined longitudinal stress of pressure + weight + wind governs
Seismic:
Combined longitudinal stress of pressure + weight + seismic governs
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1.1.1.15 Weight Summary Weight ( lb) Contributed by Vessel Elements Component
Metal New*
Insulation Piping Operating & Lining + Liquid Supports Liquid
Metal Corroded*
Test Liquid
ASME B16.5/16.47 Blind on Flange 7.329,00 #35
7.329,00
0,00
0,00
0,00
0,00
MAJOR BARREL
5.057,32
5.057,32
0,00
0,00
0,00
10.994,71 10.994,66
Transition #1
569,98
569,98
0,00
0,00
0,00
1.028,06
1.028,06
MINOR BARREL
2.644,24
2.644,24
0,00
0,00
0,00
4.652,58
4.652,58
Ellipsoidal Head #1
664,64
664,64
0,00
0,00
0,00
376,73
376,73
Saddle #1
2.118,00
2.118,00
0,00
0,00
0,00
0,00
0,00
TOTAL:
18.383,18 18.383,18 0,00
0,00
0,00
17.052,08 17.052,03
0,00
* Shells with attached nozzles have weight reduced by material cut out for opening. Weight ( lb) Contributed by Attachments Component
Nozzles & Flanges
Body Flanges New
Corroded
ASME B16.5/16.47 Blind on Flange #35
0,00
MAJOR BARREL
2.855,00 2.855,00
Transition #1
0,00
MINOR BARREL
0,00
New 0,00
Corroded 0,00
Packed Trays & Beds Supports
Rings Vertical & Loads Clips
0,00
0,00
0,00
0,00
1.393,15 1.392,70
0,00
0,00
47,92
0,00
0,00
0,00
0,00
0,00
0,00
0,00
0,00
0,00
0,00
38,26
38,26
0,00
0,00
0,00
0,00
Ellipsoidal Head #1
0,00
0,00
0,00
0,00
0,00
0,00
0,00
0,00
TOTAL:
2.855,00 2.855,00
0,00
0,00
47,92
0,00
1.431,41 1.430,97
Vessel operating weight, Corroded: 39.769 lb Vessel operating weight, New: 39.770 lb Vessel empty weight, Corroded: 22.717 lb Vessel empty weight, New: 22.718 lb Vessel test weight, New: 39.770 lb 1.1.1.16 Vessel center of gravity location (from datum) Vessel Lift Weight, New: 22.718 lb Center of Gravity: 229,87" 1.1.1.17 Vessel Capacity Vessel Capacity** (New): 2.035 US gal Vessel Capacity** (Corroded): 2.035 US gal **The vessel capacity does not include volume of nozzle, piping or other attachments.
Completed
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1.1.1.18 Hydrostatic Test Shop test pressure determination for Chamber bounded by Ellipsoidal Head #1 and ASME B16.5/16.47 Blind on Flange #35 based on MAWP per UG-99(b) Shop hydrostatic test gauge pressure is 1.414,400 psi at 70,00 °F (the chamber MAWP = 1.088,000 psi) The shop test is performed with the vessel in the horizontal position.
Identifier
Local test pressure psi
Test liquid static head psi
Stress during test psi
UG-99 UG-99 stress pressure ratio factor
Allowable test Stress stress excessive? psi
MAJOR BARREL (1)
1.416,392 1,992
1,0000 1,30
48.697
58.500
No
Flange #35
1.416,392 1,992
N/A
NI
NI
NI
Transition #1
1.416,390 1,990
1,0000 1,30
51.572
58.500
No
MINOR BARREL
1.416,392 1,992
1,0000 1,30
40.462
58.500
No
Straight Flange on Ellipsoidal Head #1
1.416,377 1,977
1,0000 1,30
25.037
34.200
No
Ellipsoidal Head #1
1.416,377 1,977
1,0000 1,30
21.902
34.200
No
DREYN NOZZLE - Nozzle #7 (N7)
1.416,702 2,302
1,0000 1,30
17.493
45.933
No
KICKER NOZZLE - Nozzle #1 (N1)
1.415,753 1,353
1,0000 1,30
19.552
41.381
No
KICKER NOZZLE - Nozzle #2 (N2)
1.415,753 1,353
1,0000 1,30
19.552
41.381
No
PIG SIGNALLER - Nozzle #8 (N8)
1.414,973 0,573
1,0000 1,30
16.188
47.250
No
PRESSURE INDICATOR Nozzle #4 (N4)
1.414,684 0,284
1,0000 1,30
18.445
46.724
No
SAFETY VALVE NOZZLE Nozzle #5 (N5)
1.414,684 0,284
1,0000 1,30
23.967
37.124
No
VENT NOZZLE - Nozzle #2 (N2) 1.414,684 0,284
1,0000 1,30
18.445
46.724
No
1,30
Notes: (1) MAJOR BARREL limits the UG-99 stress ratio. (2) NI indicates that test stress was not investigated. (3) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 7782. (4) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress. (5) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange. The test temperature of 70,00 °F is warmer than the minimum recommended temperature of 10,00 °F so the brittle fracture provision of UG-99(h) has been met.
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Field test pressure determination for Chamber bounded by Ellipsoidal Head #1 and ASME B16.5/16.47 Blind on Flange #35 based on design P per UG-99(b) Field hydrostatic test gauge pressure is 1.414,400 psi at 70,00 °F (the chamber design P = 1.088,000 psi)
Identifier
Local test pressure psi
Test liquid static head psi
Stress during test psi
UG-99 UG-99 stress pressure ratio factor
Allowable test Stress stress excessive? psi
MAJOR BARREL (1)
1.416,392 1,992
1,0000 1,30
48.697
58.500
No
Flange #35
1.416,392 1,992
N/A
NI
NI
NI
Transition #1
1.416,390 1,990
1,0000 1,30
51.572
58.500
No
MINOR BARREL
1.416,392 1,992
1,0000 1,30
40.462
58.500
No
Straight Flange on Ellipsoidal Head #1
1.416,377 1,977
1,0000 1,30
25.037
34.200
No
Ellipsoidal Head #1
1.416,377 1,977
1,0000 1,30
21.902
34.200
No
DREYN NOZZLE - Nozzle #7 (N7)
1.416,702 2,302
1,0000 1,30
17.493
45.933
No
KICKER NOZZLE - Nozzle #1 (N1)
1.415,753 1,353
1,0000 1,30
19.552
41.381
No
KICKER NOZZLE - Nozzle #2 (N2)
1.415,753 1,353
1,0000 1,30
19.552
41.381
No
PIG SIGNALLER - Nozzle #8 (N8)
1.414,973 0,573
1,0000 1,30
16.188
47.250
No
PRESSURE INDICATOR Nozzle #4 (N4)
1.414,684 0,284
1,0000 1,30
18.445
46.724
No
SAFETY VALVE NOZZLE Nozzle #5 (N5)
1.414,684 0,284
1,0000 1,30
23.967
37.124
No
VENT NOZZLE - Nozzle #2 (N2) 1.414,684 0,284
1,0000 1,30
18.445
46.724
No
1,30
Notes: (1) MAJOR BARREL limits the UG-99 stress ratio. (2) NI indicates that test stress was not investigated. (3) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 7782. (4) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress. (5) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange. The test temperature of 70,00 °F is warmer than the minimum recommended temperature of 10,00 °F so the brittle fracture provision of UG-99(h) has been met.
Completed
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1.1.1.19 Vacuum Summary
Component
Elevation above Datum (in)
Line of Support
ASME B16.5/16.47 Blind on Flange #35 -
Length Le (in)
327,13
N/A
-
1/3 depth of ASME B16.5/16.47 Blind on Flange #35
319,69
N/A
MAJOR BARREL Top
-
307,00
189,69
MAJOR BARREL Bottom
-
130,00
189,69
Transition #1 Top
-
130,00
18,33
-
Transition #1 Top
130,00
18,33
-
Transition #1 Bottom
110,00
18,33
Transition #1 Bottom
-
110,00
18,33
MINOR BARREL Top
-
110,00
116,15
MINOR BARREL Bottom
-
0,00
116,15
Straight Flange on Ellipsoidal Head #1 Top
-
0,00
116,15
Straight Flange on Ellipsoidal Head #1 Bottom
-
-3,00
116,15
-
1/3 depth of Ellipsoidal Head #1
-6,15
N/A
Ellipsoidal Head #1
-
-13,55
N/A
Note For main components, the listed value of 'Le' is the largest unsupported length for the component.
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1.1.1.20 MAJOR BARREL 1.1.1.21 ASME Section VIII Division 1, 2004 Edition Component: Cylinder Material specification: API 5L X65 (user defined) Pipe NPS and Schedule: 48" Sch 0,688 Not a UCS-66 material. Internal design pressure: P = 1088 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F 1.1.1.22 Static liquid head: Ps =2,1367 psi(SG=1,0000, Hs=59,1920" Operating head) Pth=1,9923 psi(SG=1,0000, Hs=55,1920", Horizontal test head) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" PWHT is performed Radiography: Longitudinal joint Full UW-11(a) Type 1 Left circumferential joint Full UW-11(a) Type 1 Right circumferential joint - Full UW-11(a) Type 1 Estimated weight: New = 5122,3491 lb corr = 5122,3491 lb Capacity: New = 1308,1883 gal corr = 1308,1883 gal OD = 48,0000" Length Lc = 177,0000" t = 0,6880"
1.1.1.23 Design thickness, (at 150,00°F) Appendix 1-1 t = P*Ro/(S*E + 0,40*P) + Corrosion = 1090,1367*24,0000/(65000,0000*1,00 + 0,40*1090,1367) + 0,0000 = 0,3999" 1.1.1.24 Maximum allowable working pressure, (at 150,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) - Ps = 65000,0000*1,00*0,6880 / (24,0000 - 0,40*0,6880) - 2,1367 = 1882,8108 psi 1.1.1.25 Maximum allowable pressure, (at 70,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) = 65000,0000*1,00*0,6880 / (24,0000 - 0,40*0,6880) = 1884,9475 psi 1.1.1.26 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 189,6900/48,0000 = 3,9519 Do/t = 48,0000/0,291693 = 164,5565 From table G: A = 0,000153 From table CD-1: B = 1851,2589 Pa = 4*B/(3*(Do/t)) = 4*1851,2589/(3*(48,0000/0,291693)) 15,0000 psi
=
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1.1.1.27 Design thickness for external pressure Pa = 15,0000 psi = t + Corrosion = 0,291693 + 0,0000 = 0,2917" 1.1.1.28 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 189,6900/48,0000 = 3,9519 Do/t = 48,0000/0,6880 = 69,7674 From table G: A = 0,000544 From table CD-1: B = 6556,4819 Pa = 4*B/(3*(Do/t)) = 4*6556,4819/(3*(48,0000/0,6880)) = 125,3017 psi 1.1.1.29 Allowable Compressive Stress, Hot and Corroded- ScHC, (table CD-1) A = 0,125 / (Ro / t) = 0,125 / (24,0000 / 0,6880) = 0,003583 B = 16895,1758 psi S
= =
65000,0000 / 1,0000 65000,0000 psi
ScHC
=
16895,1758 psi
1.1.1.30 Allowable Compressive Stress, Hot and New- ScHN ScHN = ScHC = 16895,1758 psi 1.1.1.31 Allowable Compressive Stress, Cold and New- ScCN, (table CD-1) A = 0,125 / (Ro / t) = 0,125 / (24,0000 / 0,6880) = 0,003583 B = 17052,7793 psi S
= =
65000,0000 / 1,0000 65000,0000 psi
ScCN
=
17052,7793 psi
1.1.1.32 Allowable Compressive Stress, Cold and Corroded- ScCC ScCC = ScCN = 17052,7793 psi
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1.1.1.33 Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CD-1) A = 0,125 / (Ro / t) = 0,125 / (24,0000 / 0,6880) = 0,003583 B = 16895,1758 psi S
= =
65000,0000 / 1,0000 65000,0000 psi
ScVC
=
16895,1758 psi
Completed
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1.1.1.34 Transition #1 1.1.1.35 ASME Section VIII Division 1, 2004 Edition Component: Material specification:
Transition API 5L X65 (user defined)
Not a UCS-66 material. Internal design pressure: P = 1088,0000 psi @ 150,00°F External design pressure: Pe = 15,0000 psi @ 150,00°F 1.1.1.36 Static liquid head: Ps =1,9904 psi(SG=1,0000, Hs=55,1390" Operating head at small end) Ps =1,9904 psi(SG=1,0000, Hs=55,1390" Operating head at large end) Pth=1,9904 psi(SG=1,0000, Hs=55,1390", Horizontal test head at small end) Pth=1,9904 psi(SG=1,0000, Hs=55,1390", Horizontal test head at large end) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" PWHT is not performed Radiography: Category A joints Full UW-11(a) Type 1 Circ. joint top/left Full UW-11(a) Type 1 Circ. joint right/bottom Full UW-11(a) Type 1 Estimated weight: New = 570,0 lb corr = 570,0 lb Capacity: New = 123,3 US gal corr = 123,3 US gal Axial length = 20,0000" Large End OD = 48,0000" Small End OD = 40,0000" Cone tc = 0,6880" 1.1.1.37 Design thickness, (at 150,00°F) App 1-4(e) (Large End) t
= = =
P*Do 1089,9904*48,0000 / (2*Cos(21,801411)*(65000,0000*1,00 + 0.4*1089,9904)) + 0,0000 0,4306"
Small End design thickness (t = 0,3588") does not govern. 1.1.1.38 MAWP, (Corroded at 150,00°F) App 1-4(e) (Large End) P
= = =
- Ps o 2*65000,0000*1,00*0,6880*Cos(21,801411) / (48,0000 - 0,80*0,6880*Cos(21,801411)) - 1,9904 1746,6886 psi
Small End MAWP (2100,9504 psi) does not govern.
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1.1.1.39 MAP, (New at 70,00°F) App 1-4(e) (Large End) P
= = =
- Ps 2*65000,0000*1,00*0,6880*Cos(21,801411) / (48,0000 - 0,80*0,6880*Cos(21,801411)) - 0,0000 1748,6790 psi o
Small End MAP (2102,9407 psi) does not govern. 1.1.1.40 External Pressure, (Corroded & at 150,00°F) UG-33(f) DL = 48,0000" Le
= (L/2)*(1+Ds/DL) = (20,0000/2)*(1+40,0000/48,0000) = 18,3333"
te = t * Cos( = 0,110385 Le/DL = 18,3333/48,0000 = 0,3819 DL/te = 48,0000/0,110385 = 434,8400 From table G: A = 0,000406 From table CD-1: B = 4891,9722 Pa = 4*B/(3*(DL/te)) = 4*4891,9722/(3*(48,0000/0,110385)) = 15,0001 psi 1.1.1.41 Design thickness for external pressure Pa = 15,0001 psi = te 1.1.1.42 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-33(f) te Le/DL = 18,3333/48,0000 = 0,3819 DL/te = 48,0000/0,6388 = 75,1418 From table G: A = 0,006218 From table CD-1: B = 17974,9922 Pa = 4*B/(3*(DL/te)) = 4*17974,9922/(3*(48,0000/0,6388)) = 318,9522 psi
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1.1.1.43 % Extreme fiber elongation - User defined non-carbon steel material = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 0,7410 / 19,6295) * (1 - 19 = 1,8875 %
Cone juncture large end calculations, P =1.089,990 psi (MAWP = 1.088,000 psi) Appendix 1-5(d) Loading
Area check U-2(g) f1 required analysis (lbf /in) required
Pressure No
No
0,00
QL (lbf /in)
ArL AeL Ring Status (in2) (in2) area (in2)
12.704,93 0,00 2,27 none
OK
Cone large end calculations per Appendix 1-5(d), pressure, corroded f1 = -Wl == 0 lb/in
m)
+ 12*Ml
2 m
)
2
)
P*RL/2 = 12.704,93 lb/in |f1| <= P*RL/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.089,99/(65.000,00*1) = 0,016769 From table 1-
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Cone juncture small end calculations P = 1.090,135 psi (MAWP = 1.088,000 psi) Appendix 1-5(e) Loading
Area check U-2(g) f2 required analysis (lbf /in) required
Pressure Yes
No
0,00
Qs (lbf /in)
Ars Aes Ring Status (in2) (in2) area (in2)
10.526,34 0,60 2,05 none
OK
Cone small end calculations per Appendix 1-5(e), pressure, corroded f2 = -Ws == 0 lb/in
m)
+ 12*Ms
2 m
)
2
)
P*Rs/2 = 10.526,34 lb/in |f2| <= P*Rs/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.090,135/(65.000,00*1) = 0,016771 From table 1-
Qs = P*Rs/2 + f2 = 10.526,34 + 0 = 10.526,34 lb/in Ars = (k*Qs*Rs/(Ss*E1))*(1 = (1*10.526,34*19,312/(65.000,00*1))*(1 - 11,37/21,8014)*tan(21,8014) = 0,5985627 in2 Aes = 0,78*(Rs*ts)0,5*[(ts - t) + (tc - tr = 0,78*(19,312*0,688)0,5*[(0,688 - 0,3271798) + (0,688 - 0,3523834)/cos(21,8014)] = 2,053593 in2 Aes >= Ars therefore the small end juncture is adequately reinforced.
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Cone large end calculations for external pressure of 15,000 psi Appendix 1-8(b) Area U-2(g) check f1 QL ArL AeL Ring Area Loading analysis req'd (lbf /in) (lbf /in) (in2) (in2) area (in2) status req'd Vacuum Yes
No
0,00
180,00 0,03 4,52 none
OK
I's (in4)
I' (in4)
I status
0,9041 0,9279 OK
Cone large end calculations per Appendix 1-8(b), wind + external pressure f1 = Wl
m)
+ 12*Ml
2 m
)
2
)
= 0 lb/in P*RL/2 = 180 lb/in f1 + P*RL/2 is in compression so a U-2(g) analysis is not required. P/(Ss*E1) = 15/(65.000,00*1) = 0,000231 From table 1-
QL = P*RL/2 + f1 = 180 + 0 = 180 lb/in ArL = (k*QL*RL s*E1))*[1 - 0,25*((P*RL-QL)/QL = (1*180*24*tan(21,8014)/(65.000,00*1))*[1 - 0,25*((15*24-180)/180)*(0,58/21,8014)] = 0,0264 in2 AeL = 0,55*(DL*ts)0,5*(ts + tc = 0,55*(48*0,688)0,5*(0,688 + 0,688/cos(21,8014)) = 4,5166 in2 AeL >= ArL therefore the large end juncture is adequately reinforced. 2 2 M = -RL L/2 + (RL - Rs )/(3*RL = -24*tan(21,8014)/2 + 189,69/2 + (242 - 202)/(3*24*tan(21,8014)) = 96,15611
Lc = (L2 + (RL - Rs)2)0,5 = (202 + (24 - 20)2)0,5 = 20,39608 ATL = LL*ts/2 + Lc * tc/2 + As = 189,69*0,688/2 + 20,39608 * 0,688/2 + 0 = 72,26962 FL = P*M + f1 = 15*96,15611 + 0*tan(21,8014) = 1.442,342
Completed
13-P113
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B = 0,75*FL*DL/ATL = 0,75*1.442,342*48/72,26962 = 718,4803 From Table CD-1: A = 0,000059 (shell, 150,00°F) I's = A*DL2*ATL/10,9 = 5,918276E-05*482*72,26962/10,9 = 0,90408 in4 The calculated I' for the combined shell-cone cross section is 0,9279 in4 As I' >= I's the large end is adequately stiffened per Appendix 1-8(b).
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Cone small end calculations for external pressure of 15,000 psi Appendix 1-8(c) U-2(g) f2 Qs Ars Aes Ring Area Loading analysis (lbf /in) (lbf /in) (in2) (in2) area (in2) status req'd Vacuum No
0,00
150,00 0,02 3,37 none
OK
I's (in4)
I' (in4)
I status
0,3576 0,7311 OK
Cone small end calculations per Appendix 1-8(c), wind + external pressure f2 = Ws
m)
+ 12*Ms
2 m
)
2
)
= 0 lb/in P*Rs/2 = 150 lb/in f2 + P*Rs/2 is in compression so a U-2(g) analysis is not required. Qs = P*Rs/2 + f2 = 150 + 0 = 150 lb/in Ars = (k*Qs*Rs s*E1)) = (1*150*20*tan(21,8014)/(65.000,00*1)) = 1,846154E-02 in2 Aes = 0,55*(Ds*ts)0,5*((ts - t) + (tc - tr = 0,55*(40*0,688)0,5*((0,688 - 0,2133743) + (0,688 - 4,308531E-02)/cos(21,8014)) = 3,373519 in2 Aes >= Ars therefore the small end juncture is adequately reinforced. 2 2 N = Rs s/2 + (RL - Rs )/(6*Rs*tan( = 20*tan(21,8014)/2 + 116,15/2 + (242 - 202)/(6*20*tan(21,8014)) = 65,74167
Lc = (L2 + (RL - Rs)2)0,5 = (202 + (24 - 20)2)0,5 = 20,39608 Ats = Ls*ts/2 + Lc * tc/2 + As = 116,15*0,688/2 + 20,39608 * 0,688/2 + 0 = 46,97185 Fs = P*N + f2 = 15*65,74167 + 0*tan(21,8014) = 986,125 B = 0,75*Fs*Ds/Ats = 0,75*986,125*40/46,97185 = 629,8187
Completed
13-P113
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From Table CD-1: A = 0,000052 (shell, 150,00°F) I's = A*Ds2*Ats/10,9 = 5,186052E-05*402*46,97185/10,9 = 0,35758 in4 The calculated I' for the combined shell-cone cross section is 0,7311 in4 As I' >= I's the small end is adequately stiffened per Appendix 1-8(c).
Completed
13-P113
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MAP Cone juncture large end calculations, P =1.748,679 psi Appendix 1-5(d) Loading
Area check U-2(g) f1 required analysis (lbf /in) required
Pressure No
No
0,00
QL (lbf /in)
ArL AeL Ring Status (in2) (in2) area (in2)
20.405,80 0,00 0,20 none
OK
Cone large end calculations per Appendix 1-5(d), pressure, new f1 = -Wl == 0 lb/in
m)
+ 12*Ml
2 m
)
2
)
P*RL/2 = 20.405,80 lb/in |f1| <= P*RL/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.748,679/(65.000,00*1) = 0,026903 From table 1-
Completed
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MAP Cone juncture small end calculations P = 1.748,679 psi Appendix 1-5(e) Loading
Area check U-2(g) f2 required analysis (lbf /in) required
Pressure Yes
No
0,00
Qs (lbf /in)
Ars Aes Ring Status (in2) (in2) area (in2)
16.905,86 0,70 0,82 none
OK
Cone small end calculations per Appendix 1-5(e), pressure, new f2 = -Ws == 0 lb/in
m)
+ 12*Ms
2 m
)
2
)
P*Rs/2 = 16.905,86 lb/in |f2| <= P*Rs/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.748,679/(65.000,00*1) = 0,026903 From table 1-
Qs = P*Rs/2 + f2 = 16.905,86 + 0 = 16.905,86 lb/in Ars = (k*Qs*Rs/(Ss*E1))*(1 = (1*16.905,86*19,312/(65.000,00*1))*(1 - 14,23/21,8014)*tan(21,8014) = 0,697755 in2 Aes = 0,78*(Rs*ts)0,5*[(ts - t) + (tc - tr = 0,78*(19,312*0,688)0,5*[(0,688 - 0,5287251) + (0,688 - 0,5694544)/cos(21,8014)] = 0,8158537 in2 Aes >= Ars therefore the small end juncture is adequately reinforced.
Completed
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1.1.1.44 MINOR BARREL 1.1.1.45 ASME Section VIII Division 1, 2004 Edition Component: Material specification: Pipe NPS and Schedule:
Cylinder API 5L X65 (user defined) 40" Sch 0,688
Not a UCS-66 material. Internal design pressure: P = 1088 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F 1.1.1.46 Static liquid head: Ps =1,9923 psi(SG=1,0000, Hs=55,1920" Operating head) Pth=1,9923 psi(SG=1,0000, Hs=55,1920", Horizontal test head) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" PWHT is not performed Radiography: Longitudinal joint Full UW-11(a) Type 1 Left circumferential joint Full UW-11(a) Type 1 Right circumferential joint - Full UW-11(a) Type 1 Estimated weight: New = 2645,1021 lb corr = 2645,1021 lb Capacity: New = 557,9369 gal corr = 557,9369 gal OD = 40,0000" Length Lc = 110,0000" t = 0,6880"
1.1.1.47 Design thickness, (at 150,00°F) Appendix 1-1 t
= = =
P*Ro/(S*E + 0,40*P) + Corrosion 1089,9923*20,0000/(65000,0000*1,00 + 0,40*1089,9923) + 0,0000 0,3332"
1.1.1.48 Maximum allowable working pressure, (at 150,00°F) Appendix 1-1 P
= = =
S*E*t/(Ro - 0,40*t) - Ps 65000,0000*1,00*0,6880 / (20,0000 - 0,40*0,6880) - 1,9923 2265,2043 psi
1.1.1.49 Maximum allowable pressure, (at 70,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) = 65000,0000*1,00*0,6880 / (20,0000 - 0,40*0,6880) 2267,1968 psi
Completed
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1.1.1.50 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/0,213458 = 187,3907 From table G: A = 0,000174 From table CD-1: B = 2108,1433 Pa = 4*B/(3*(Do/t)) = 4*2108,1433/(3*(40,0000/0,213458)) = 15,0000 psi 1.1.1.51 Design thickness for external pressure Pa = 15,0000 psi = t + Corrosion = 0,213458 + 0,0000 = 0,2135" 1.1.1.52 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/0,6880 = 58,1395 From table G: A = 0,000970 From table CD-1: B = 11669,8730 Pa = 4*B/(3*(Do/t)) = 4*11669,8730/(3*(40,0000/0,6880)) = 267,6291 psi 1.1.1.53 Allowable Compressive Stress, Hot and Corroded- ScHC, (table CD-1) A = 0,125 / (Ro / t) = 0,125 / (20,0000 / 0,6880) = 0,004300 B = 17279,7852 psi S
= =
65000,0000 / 1,0000 65000,0000 psi
ScHC
=
17279,7852 psi
1.1.1.54 Allowable Compressive Stress, Hot and New- ScHN ScHN = ScHC = 17279,7852 psi 1.1.1.55 Allowable Compressive Stress, Cold and New- ScCN, (table CD-1) A = 0,125 / (Ro / t) = 0,125 / (20,0000 / 0,6880) = 0,004300 B = 17435,6836 psi S
= =
65000,0000 / 1,0000 65000,0000 psi
ScCN
=
17435,6836 psi Completed
13-P113
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1.1.1.56 Allowable Compressive Stress, Cold and Corroded- ScCC ScCC = ScCN = 17435,6836 psi 1.1.1.57 Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CD-1) A = 0,125 / (Ro / t) = 0,125 / (20,0000 / 0,6880) = 0,004300 B = 17279,7852 psi S
= =
65000,0000 / 1,0000 65000,0000 psi
ScVC
=
17279,7852 psi
Completed
13-P113
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1.1.1.58 ASME B16.5/16.47 Blind on Flange #35 This is an ASME B16.5/16.47 rated blind flange. Flange description: 48 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt (2 1/2 < t <= 4) Flange rated MDMT: -40 °F (UCS-66(b)(1)(b)) (Bolts rated MDMT per Fig UCS-66 note (e) = -40 °F) Liquid static head on flange: 2,1367 psi ASME B16.47 flange rating MAWP: 1415 psi@ 150°F ASME B16.47 flange rating MAP: 1480 psi@ 70°F ASME B16.47 flange hydro test: 2225 psi@ 70°F
Completed
13-P113
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1.1.1.59 Straight Flange on Ellipsoidal Head #1 1.1.1.60 ASME Section VIII Division 1, 2004 Edition Component: Material specification:
Straight Flange SA-516 70 (ASME II-D p. 14, ln. 20)
Material is impact test exempt per UG-20(f) UCS-66 governing thickness = 0,688 in Internal design pressure: P = 1088 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F 1.1.1.61 Static liquid head: Ps =1,9774 psi(SG=1,0000, Hs=54,7800" Operating head) Pth=1,9774 psi(SG=1,0000, Hs=54,7800", Horizontal test head) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" Design MDMT = -20,00°F No impact test performed Rated MDMT = -20,00°F Material is not normalized Material is not produced to Fine Grain Practice PWHT is not performed Radiography: Longitudinal joint Seamless No RT Circumferential joint Full UW-11(a) Type 1 Estimated weight: New = 114,1301 lb corr = 114,1301 lb Capacity: New = 14,5741 gal corr = 14,5741 gal OD = 40,0000" Length Lc = 3,0000" t = 1,1000"
1.1.1.62 Design thickness, (at 150,00°F) Appendix 1-1 t
= = =
P*Ro/(S*E + 0,40*P) + Corrosion 1089,9774*20,0000/(20000,0000*1,00 + 0,40*1089,9774) + 0,0000 1,0668"
1.1.1.63 Maximum allowable working pressure, (at 150,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) - Ps = 20000,0000*1,00*1,1000 / (20,0000 - 0,40*1,1000) - 1,9774 = 1122,7670 psi 1.1.1.64 Maximum allowable pressure, (at 70,00°F) Appendix 1-1 P
= = =
S*E*t/(Ro - 0,40*t) 20000,0000*1,00*1,1000 / (20,0000 - 0,40*1,1000) 1124,7444 psi
Completed
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1.1.1.65 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/0,201341 = 198,6675 From table G: A = 0,000156 From table CS-2: B = 2235,0144 Pa = 4*B/(3*(Do/t)) = 4*2235,0144/(3*(40,0000/0,201341)) = 15,0000 psi 1.1.1.66 Design thickness for external pressure Pa = 15,0000 psi = t + Corrosion = 0,201341 + 0,0000 = 0,2013" 1.1.1.67 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/1,1000 = 36,3636 From table G: A = 0,001989 From table CS-2: B = 14976,9785 Pa = 4*B/(3*(Do/t)) = 4*14976,9785/(3*(40,0000/1,1000)) = 549,1559 psi 1.1.1.68 % Extreme fiber elongation - UCS-79(d) = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 1,1000 / 19,4500) * (1 = 2,8278 % 1.1.1.69 Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2) A = 0,125 / (Ro / t) = 0,125 / (20,0000 / 1,1000) = 0,006875 B = 17278,4180 psi S
= =
20000,0000 / 1,0000 20000,0000 psi
ScHC
=
17278,4180 psi
1.1.1.70 Allowable Compressive Stress, Hot and New- ScHN ScHN = ScHC = 17278,4180 psi 1.1.1.71 Allowable Compressive Stress, Cold and New- ScCN, (table CS-2) A = 0,125 / (Ro / t) = 0,125 / (20,0000 / 1,1000) = 0,006875 B = 17278,4180 psi S
= =
20000,0000 / 1,0000 20000,0000 psi Completed
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ScCN
=
17278,4180 psi
1.1.1.72 Allowable Compressive Stress, Cold and Corroded- ScCC ScCC = ScCN = 17278,4180 psi 1.1.1.73 Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2) A = 0,125 / (Ro / t) = 0,125 / (20,0000 / 1,1000) = 0,006875 B = 17278,4180 psi S
= =
20000,0000 / 1,0000 20000,0000 psi
ScVC
=
17278,4180 psi
Completed
13-P113
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1.1.1.74 Ellipsoidal Head #1 1.1.1.75 ASME Section VIII, Division 1, 2004 Edition Component: Material Specification: Straight Flange governs MDMT
Ellipsoidal Head SA-516 70 (ASME II-D p.14, ln. 20)
Internal design pressure: P = 1.088,00 psi @ 150 °F External design pressure: Pe = 15 psi @ 150 °F 1.1.1.76 Static liquid head: Ps= 1,9774 psi (SG=1, Hs=54,78" Operating head) Pth= 1,9774 psi (SG=1, Hs=54,78" Horizontal test head) Corrosion allowance: Inner C = 0" Outer C = 0" Design MDMT = -20°F No impact test performed Rated MDMT = -20°F Material is not normalized Material is not produced to fine grain practice PWHT is not performed Do not Optimize MDMT / Find MAWP
Radiography:
Category A joints Head to shell seam -
Seamless No RT Full UW-11(a) Type 1
Estimated weight*: Capacity*:
new = 664,6 lb new = 45,2 US gal
corr = 664,6 lb corr = 45,2 US gal
* includes straight flange Outer diameter = Minimum head thickness = Head ratio D/2h = Head ratio D/2h = Straight flange length Lsf = Nominal straight flange thickness tsf= Insulation thk*: 0" Insulation support ring 0" spacing: Lining/ref thk*: 0"
40" 1,1" 2 (new) 2 (corroded) 3" 1,1" density: 0 lb/ft3
weight: 0 lb
individual weight: 0 lb 3
density: 0 lb/ft
total weight: 0 lb weight: 0 lb
includes straight flange if applicable
Completed
13-P113
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1.1.1.77 Results Summary The governing condition is internal pressure. Minimum thickness per UG-16 = Design thickness due to internal pressure (t) = Design thickness due to external pressure (te) = Maximum allowable working pressure (MAWP)= Maximum allowable pressure (MAP) = Maximum allowable external pressure (MAEP) =
0,0625" + 0" = 0,0625" 1,0357" 0,0986" 1155,308 psi 1157,286 psi 541,9866 psi
1.1.1.78 Design thickness for internal pressure, (Corroded at 150 °F) UG-32(d)(1) t = P*D/(2*S*E - 0,20*P) + Corrosion = 1089,977*37,8/(2*20000*1 - 0,20*1089,977) + 0 = 1,0357" The head internal pressure design thickness is 1,0357". 1.1.1.79 Maximum allowable working pressure, (Corroded at 150 °F) UG-32(d)(1) P = 2*S*E*t/(D + 0,20*t) - Ps = 2*20000*1*1,1/(37,8 +0,20*1,1) - 1,9774 = 1155,308 psi The maximum allowable working pressure (MAWP) is 1155,308 psi. 1.1.1.80 Maximum allowable pressure, (New at 70 °F) UG-32(d)(1) P = 2*S*E*t/(D + 0,20*t) - Ps = 2*20000*1*1,1/(37,8 +0,20*1,1) - 0 = 1157,286 psi The maximum allowable pressure (MAP) is 1157,286 psi. 1.1.1.81 Design thickness for external pressure, (Corroded at 150 °F) UG-33(d) Equivalent outside spherical radius (Ro) Ro = Ko*Do = 0,8531 * 40 = 34,1232 in A
= = =
0,125 / (Ro/t) 0,125 / (34,1232/0,098556) 0,000361
From Table CS-2: B=5.193,4536 psi Pa
= = =
B/(Ro/t) 5.193,454/(34,1232/0,098556) 15 psi
t
=
0,0986" + Corrosion = 0,0986" + 0" = 0,0986"
Check the external pressure per UG-33(a)(1) UG-32(d)(1) t
= = =
1,67*Pe*D/(2*S*E - 0,20*1,67*Pe) + Corrosion 1,67*15*37,8/(2*20000*1 - 0,20*1,67*15) + 0 0,0237"
The head external pressure design thickness (te) is 0,098556".
Completed
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1.1.1.82 Maximum Allowable External Pressure, (Corroded at 150 °F) UG-33(d) Equivalent outside spherical radius (Ro) Ro = Ko*Do = 0,8531 * 40 = 34,1232 in A
= = =
0,125 / (Ro/t) 0,125 / (34,1232/1,1) 0,00403
From Table CS-2: B=16.813,0293 psi Pa
= = =
B/(Ro/t) 16.813,03/(34,1232/1,1) 541,9866 psi
Check the Maximum External Pressure, UG-33(a)(1) UG-32(d)(1) P
= = =
2*S*E*t/((D + 0,20*t)*1,67) - Ps2 2*20000*1*1,1/((37,8 +0,20*1,1)*1,67) - 0 692,9855 psi
The maximum allowable external pressure (MAEP) is 541,9866 psi. 1.1.1.83 % Extreme fiber elongation - UCS-79(d) = = =
(75*t / Rf)*(1 - Rf / Ro) (75*1,1 / 6,976)*(1 11,8263%
The extreme fiber elongation exceeds 5 percent and the thickness exceeds 5/8 inch;. Heat treatment per UCS-56 is required if fabricated by cold forming.
Completed
13-P113
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1.1.1.84 DREYN NOZZLE - Nozzle #7 (N7) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 1,0000 in tw(upper) = 1,2000 in Leg42 = 1,0000 in Dp = 12,5000 in te = 1,2000 in
Note: round inside edges per UG-76(c)
Located on: MAJOR BARREL Liquid static head included: 2,0171 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 4" XX Heavy Pad material specification: API 5L X65 (user defined) Pad diameter: 12,5 in Flange description: 4 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55 °F (UCS-66(b)(1)(b)) (UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F) Liquid static head on flange: 2,3016 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 180 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 292,59 in End of nozzle to shell center: 31,88 in Nozzle inside diameter, new: 3,152 in Nozzle nominal wall thickness: 0,674 in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 7,88 in
Completed
13-P113
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Reinforcement Calculations for Internal Pressure Available reinforcement per UG-37 governs the MAWP of this nozzle. UG-37 Area Calculation Summary (in2) For P = 1400,47 psi @ 150 °F The opening is adequately reinforced A A A required available 1 2,8520
2,8520
--
A2
A3
0,4872 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
2,1648 0,2000 0,2074
tmin 0,6740
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
185.379,66 185.380,00 673.859,63 60.528,34 701.145,56 201.240,34 859.292,56
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,4718
1,2000
weld size is adequate
Calculations for internal pressure 1400,47 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,15498).
Nozzle UCS-66 governing thk: 0,674 in Nozzle rated MDMT: -155 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 3,152 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Completed
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1400,474*1,576/(17100*1 - 0,6*1400,474) 0,1357 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 3,152*0,688*1 + 2*0,674*0,688*1*(1 - 0,2631) 2,852 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 3,152*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 0,674)*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,4872 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(0,674 - 0,1357)*0,2631*0,688 0,4872 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(0,674 - 0,1357)*(2,5*0,674 + 1,2)*0,2631 0,8172 in2
= = =
Leg2*fr3 0,87182*0,2631 0,2 in2
(Part of the weld is outside of the limits) Completed
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A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (6,304 - 3,152 - 2*0,674)*1,2*1 2,1648 in2
A1 + A2 + A41 + A42 + A5 0 + 0,4872 + 0,2 + 0 + 2,1648 2,852 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,674 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,1358 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5127 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,2074 in The greater of tr2 or tr3: tr5 = 0,5127 in The lesser of tr4 or tr5: tr6 = 0,2074 in
Required per UG-45 is the larger of tr1 or tr6 = 0,2074 in Available nozzle wall thickness new, tn = 0,674 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi Completed
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Strength of welded joints: (1) Inner fillet weld in shear ( i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (2,852 - 0 + 2*0,674*0,2631*(1*0,688 - 1*0,688))*65000 185379,7 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,4872 + 2,1648 + 0,2 + 0)*65000 185380 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,4872 + 0 + 0,2 + 0 + 2*0,674*0,688*0,2631)*65000 60528,34 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,4872 + 0 + 2,1648 + 0,2 + 0 + 0 + 2*0,674*0,688*0,2631)*65000 201240,3 lbf
Load for path 1-1 lesser of W or W1-1 = 185379,7 lbf Path 1-1 through (2) & (3) = 625373,3 + 48486,29 = 673859,6 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 60528,34 lbf Path 2-2 through (1), (4), (6) = 59227,66 + 233919,2 + 407998,7 = 701145,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 185379,7 lbf Path 3-3 through (2), (4) = 625373,3 + 233919,2 = 859292,6 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
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Reinforcement Calculations for MAP Available reinforcement per UG-37 governs the MAP of this nozzle. UG-37 Area Calculation Summary (in2) For P = 1400,5 psi @ 70 °F The opening is adequately reinforced A A A required available 1 2,8520
2,8520
--
A2
A3
0,4872 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
2,1648 0,2000 0,2074
tmin 0,6740
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
185.379,66 185.380,00 673.859,63 60.528,34 701.145,56 201.240,34 859.292,56
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,4718
1,2000
weld size is adequate
Calculations for internal pressure 1400,5 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 3,152 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1400,497*1,576/(17100*1 - 0,6*1400,497) 0,1357 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi Completed
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fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 3,152*0,688*1 + 2*0,674*0,688*1*(1 - 0,2631) 2,852 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 3,152*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 0,674)*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,4872 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(0,674 - 0,1357)*0,2631*0,688 0,4872 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(0,674 - 0,1357)*(2,5*0,674 + 1,2)*0,2631 0,8172 in2
= = =
Leg2*fr3 0,87182*0,2631 0,2 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
(Dp - d - 2*tn)*te*fr4 (6,304 - 3,152 - 2*0,674)*1,2*1 2,1648 in2
Completed
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Area = = =
A1 + A2 + A41 + A42 + A5 0 + 0,4872 + 0,2 + 0 + 2,1648 2,852 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,674 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,1357 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5127 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,2074 in The greater of tr2 or tr3: tr5 = 0,5127 in The lesser of tr4 or tr5: tr6 = 0,2074 in
Required per UG-45 is the larger of tr1 or tr6 = 0,2074 in Available nozzle wall thickness new, tn = 0,674 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi Strength of welded joints: (1) Inner fillet weld in shear ( i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg Completed
f
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(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (2,852 - 0 + 2*0,674*0,2631*(1*0,688 - 1*0,688))*65000 185379,7 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,4872 + 2,1648 + 0,2 + 0)*65000 185380 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,4872 + 0 + 0,2 + 0 + 2*0,674*0,688*0,2631)*65000 60528,34 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,4872 + 0 + 2,1648 + 0,2 + 0 + 0 + 2*0,674*0,688*0,2631)*65000 201240,3 lbf
Load for path 1-1 lesser of W or W1-1 = 185379,7 lbf Path 1-1 through (2) & (3) = 625373,3 + 48486,29 = 673859,6 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 60528,34 lbf Path 2-2 through (1), (4), (6) = 59227,66 + 233919,2 + 407998,7 = 701145,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 185379,7 lbf Path 3-3 through (2), (4) = 625373,3 + 233919,2 = 859292,6 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced A A A required available 1 1,4260
2,9361
--
A2
A3
0,5713 --
A5
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
treq
2,1648 0,2000 0,0625
tmin 0,6740
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,4718
1,2000
weld size is adequate
Calculations for external pressure 125,3 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 3,152 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-28 trn = 0,0428 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(3,152*0,688*1 + 2*0,674*0,688*1*(1 - 0,2631)) 1,426 in2 Completed
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Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 3,152*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 0,674)*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,5713 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(0,674 - 0,0428)*0,2631*0,688 0,5713 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(0,674 - 0,0428)*(2,5*0,674 + 1,2)*0,2631 0,9582 in2
= = =
Leg2*fr3 0,87182*0,2631 0,2 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (6,304 - 3,152 - 2*0,674)*1,2*1 2,1648 in2
A1 + A2 + A41 + A42 + A5 0 + 0,5713 + 0,2 + 0 + 2,1648 2,9361 in2
As Area >= A the reinforcement is adequate.
Completed
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UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,674 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0428 in Wall thickness per UG-45(b)(2): tr2 = 0,0462 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,2074 in The greater of tr2 or tr3: tr5 = 0,0625 in The lesser of tr4 or tr5: tr6 = 0,0625 in
Required per UG-45 is the larger of tr1 or tr6 = 0,0625 in Available nozzle wall thickness new, tn = 0,674 in The nozzle neck thickness is adequate. 1.1.1.85 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,9857/4,5000 = 1,7746 Do/t = 4,5000/0,042791 = 105,1633 From table G: A = 0,000685 From table CS-2: B = 9882,7188 Pa = 4*B/(3*(Do/t)) = 4*9882,7188/(3*(4,5000/0,042791)) = 125,2999 psi 1.1.1.86 Design thickness for external pressure Pa = 125,2999 psi = t + Corrosion = 0,042791 + 0,0000 = 0,0428"
Completed
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1.1.1.87 Flange #35 Flange description: 48 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt (2 1/2 < t <= 4) Flange rated MDMT: -40 °F (UCS-66(b)(1)(b)) (Bolts rated MDMT per Fig UCS-66 note (e) = -40 °F) Liquid static head on flange: 2,1367 psi ASME B16.47 flange rating MAWP: 1415 psi@ 150°F ASME B16.47 flange rating MAP: 1480 psi@ 70°F ASME B16.47 flange hydro test: 2225 psi@ 70°F
Completed
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1.1.1.88 KICKER NOZZLE - Nozzle #1 (N1) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 1,0000 in tw(upper) = 1,0000 in Leg42 = 1,0000 in Dp = 26,0000 in te = 1,0000 in
Note: round inside edges per UG-76(c) Located on: MAJOR BARREL Liquid static head included: 1,1508 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 14" Sch 160 Pad material specification: API 5L X65 (user defined) Pad diameter: 26 in Flange description: 14 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -46,4 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 1,1508 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 270 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 228,03 in End of nozzle to shell center: 42,69 in Nozzle inside diameter, new: 11,188 in Nozzle nominal wall thickness: 1,406 in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 18,69 in
Completed
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Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP. UG-37 Area Calculation Summary (in2) For P = 1415 psi @ 150 °F The opening is adequately reinforced A A A required available 1 9,1230
9,4502
--
A2
A3
0,8317 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
8,3760 0,2425 0,4871
tmin 1,4060
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
592.994,50 614.262,94 1.633.714,25 102.908,52 1.969.786,88 647.348,50 2.028.525,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,5250
1,0000
weld size is adequate
Calculations for internal pressure 1415 psi @ 150 °F Nozzle is impact test exempt per UG-20(f).
Nozzle UCS-66 governing thk: 1 in Nozzle rated MDMT: -20 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 11,188 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Completed
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1415*5,594/(17100*1 - 0,6*1415) 0,4871 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) 9,123 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,8317 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(1,406 - 0,4871)*0,2631*0,688 0,8317 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(1,406 - 0,4871)*(2,5*1,406 + 1)*0,2631 2,1831 in2
= = =
Leg2*fr3 0,962*0,2631 0,2425 in2
(Part of the weld is outside of the limits) Completed
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A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (22,376 - 11,188 - 2*1,406)*1*1 8,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,8317 + 0,2425 + 0 + 8,376 9,4502 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,4871 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,518 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in The greater of tr2 or tr3: tr5 = 0,518 in The lesser of tr4 or tr5: tr6 = 0,3281 in
Required per UG-45 is the larger of tr1 or tr6 = 0,4871 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi Completed
13-P113
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Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o =
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension Nozzle OD*tw*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 592994,5 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,8317 + 8,376 + 0,2425 + 0)*65000 614262,9 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,8317 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 102908,5 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,8317 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 647348,5 lbf
Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 102908,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP. UG-37 Area Calculation Summary (in2) For P = 1480 psi @ 70 °F The opening is adequately reinforced A A A required available 1 9,1230
9,4288
--
A2
A3
0,8103 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
8,3760 0,2425 0,5107
tmin 1,4060
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
592.994,50 612.871,94 1.633.714,25 101.517,52 1.969.786,88 645.957,50 2.028.525,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,5250
1,0000
weld size is adequate
Calculations for internal pressure 1480 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 11,188 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1480*5,594/(17100*1 - 0,6*1480) 0,5107 in
tr (full area replacement) =0,688 in
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) 9,123 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,8103 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(1,406 - 0,5107)*0,2631*0,688 0,8103 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(1,406 - 0,5107)*(2,5*1,406 + 1)*0,2631 2,127 in2
= = =
Leg2*fr3 0,962*0,2631 0,2425 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (22,376 - 11,188 - 2*1,406)*1*1 8,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,8103 + 0,2425 + 0 + 8,376 9,4288 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,5107 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5415 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in The greater of tr2 or tr3: tr5 = 0,5415 in The lesser of tr4 or tr5: tr6 = 0,3281 in
Required per UG-45 is the larger of tr1 or tr6 = 0,5107 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
,8 lbf
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 592994,5 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,8103 + 8,376 + 0,2425 + 0)*65000 612871,9 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,8103 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 101517,5 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,8103 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 645957,5 lbf
Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 101517,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced A A A required available 1 4,5615
9,7820
--
A2
A3
1,1635 --
A5
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
treq
8,3760 0,2425 0,1204
tmin 1,4060
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,5250
1,0000
weld size is adequate
Calculations for external pressure 125,3 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 11,188 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-28 trn = 0,1204 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631)) 4,5615 in2 Completed
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AKTEK_ENG_13_P113_EC
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Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 1,1635 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(1,406 - 0,1204)*0,2631*0,688 1,1635 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(1,406 - 0,1204)*(2,5*1,406 + 1)*0,2631 3,0543 in2
= = =
Leg2*fr3 0,962*0,2631 0,2425 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (22,376 - 11,188 - 2*1,406)*1*1 8,376 in2
A1 + A2 + A41 + A42 + A5 0 + 1,1635 + 0,2425 + 0 + 8,376 9,782 in2
As Area >= A the reinforcement is adequate.
Completed
13-P113
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UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,1204 in Wall thickness per UG-45(b)(2): tr2 = 0,0462 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in The greater of tr2 or tr3: tr5 = 0,0625 in The lesser of tr4 or tr5: tr6 = 0,0625 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1204 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. 1.1.1.89 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 19,7335/14,0000 = 1,4095 Do/t = 14,0000/0,120413 = 116,2664 From table G: A = 0,000757 From table CS-2: B = 10926,2178 Pa = 4*B/(3*(Do/t)) = 4*10926,2178/(3*(14,0000/0,120413)) = 125,3009 psi 1.1.1.90 Design thickness for external pressure Pa = 125,3009 psi = t + Corrosion = 0,120413 + 0,0000 = 0,1204"
Completed
13-P113
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1.1.1.91 KICKER NOZZLE - Nozzle #2 (N2) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 1,0000 in tw(upper) = 1,0000 in Leg42 = 1,0000 in Dp = 26,0000 in te = 1,0000 in
Note: round inside edges per UG-76(c) Located on: MAJOR BARREL Liquid static head included: 1,1508 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 14" Sch 160 Pad material specification: API 5L X65 (user defined) Pad diameter: 26 in Flange description: 14 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -46,4 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 1,1508 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 270 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 168,976 in End of nozzle to shell center: 42,69 in Nozzle inside diameter, new: 11,188 in Nozzle nominal wall thickness: 1,406 in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 18,69 in
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP. UG-37 Area Calculation Summary (in2) For P = 1415 psi @ 150 °F The opening is adequately reinforced A A A required available 1 9,1230
9,4502
--
A2
A3
0,8317 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
8,3760 0,2425 0,4871
tmin 1,4060
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
592.994,50 614.262,94 1.633.714,25 102.908,52 1.969.786,88 647.348,50 2.028.525,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,5250
1,0000
weld size is adequate
Calculations for internal pressure 1415 psi @ 150 °F Nozzle is impact test exempt per UG-20(f).
Nozzle UCS-66 governing thk: 1 in Nozzle rated MDMT: -20 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 11,188 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Completed
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1415*5,594/(17100*1 - 0,6*1415) 0,4871 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) 9,123 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,8317 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(1,406 - 0,4871)*0,2631*0,688 0,8317 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(1,406 - 0,4871)*(2,5*1,406 + 1)*0,2631 2,1831 in2
= = =
Leg2*fr3 0,962*0,2631 0,2425 in2
(Part of the weld is outside of the limits) Completed
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A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (22,376 - 11,188 - 2*1,406)*1*1 8,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,8317 + 0,2425 + 0 + 8,376 9,4502 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,4871 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,518 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in The greater of tr2 or tr3: tr5 = 0,518 in The lesser of tr4 or tr5: tr6 = 0,3281 in
Required per UG-45 is the larger of tr1 or tr6 = 0,4871 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi Completed
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Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o =
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension ozzle OD*tw*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 592994,5 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,8317 + 8,376 + 0,2425 + 0)*65000 614262,9 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,8317 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 102908,5 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,8317 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 647348,5 lbf
Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 102908,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP. UG-37 Area Calculation Summary (in2) For P = 1480 psi @ 70 °F The opening is adequately reinforced A A A required available 1 9,1230
9,4288
--
A2
A3
0,8103 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
8,3760 0,2425 0,5107
tmin 1,4060
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
592.994,50 612.871,94 1.633.714,25 101.517,52 1.969.786,88 645.957,50 2.028.525,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,5250
1,0000
weld size is adequate
Calculations for internal pressure 1480 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 11,188 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1480*5,594/(17100*1 - 0,6*1480) 0,5107 in
tr (full area replacement) =0,688 in
Completed
13-P113
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Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) 9,123 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,8103 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(1,406 - 0,5107)*0,2631*0,688 0,8103 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(1,406 - 0,5107)*(2,5*1,406 + 1)*0,2631 2,127 in2
= = =
Leg2*fr3 0,962*0,2631 0,2425 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
Completed
13-P113
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(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (22,376 - 11,188 - 2*1,406)*1*1 8,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,8103 + 0,2425 + 0 + 8,376 9,4288 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,5107 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5415 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in The greater of tr2 or tr3: tr5 = 0,5415 in The lesser of tr4 or tr5: tr6 = 0,3281 in
Required per UG-45 is the larger of tr1 or tr6 = 0,5107 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Completed
13-P113
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Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
8 lbf
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 592994,5 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,8103 + 8,376 + 0,2425 + 0)*65000 612871,9 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,8103 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 101517,5 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,8103 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 645957,5 lbf
Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 101517,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced A A A required available 1 4,5615
9,7820
--
A2
A3
1,1635 --
A5
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
treq
8,3760 0,2425 0,1204
tmin 1,4060
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,5250
1,0000
weld size is adequate
Calculations for external pressure 125,3 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 11,188 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-28 trn = 0,1204 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631)) 4,5615 in2 Completed
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Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 1,1635 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(1,406 - 0,1204)*0,2631*0,688 1,1635 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(1,406 - 0,1204)*(2,5*1,406 + 1)*0,2631 3,0543 in2
= = =
Leg2*fr3 0,962*0,2631 0,2425 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (22,376 - 11,188 - 2*1,406)*1*1 8,376 in2
A1 + A2 + A41 + A42 + A5 0 + 1,1635 + 0,2425 + 0 + 8,376 9,782 in2
As Area >= A the reinforcement is adequate.
Completed
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UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,1204 in Wall thickness per UG-45(b)(2): tr2 = 0,0462 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in The greater of tr2 or tr3: tr5 = 0,0625 in The lesser of tr4 or tr5: tr6 = 0,0625 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1204 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. 1.1.1.92 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 19,7335/14,0000 = 1,4095 Do/t = 14,0000/0,120413 = 116,2664 From table G: A = 0,000757 From table CS-2: B = 10926,2178 Pa = 4*B/(3*(Do/t)) = 4*10926,2178/(3*(14,0000/0,120413)) = 125,3009 psi 1.1.1.93 Design thickness for external pressure Pa = 125,3009 psi = t + Corrosion = 0,120413 + 0,0000 = 0,1204"
Completed
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1.1.1.94 PIG SIGNALLER - Nozzle #8 (N8) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 1,0000 in tw(upper) = 1,0000 in Leg42 = 1,0000 in Dp = 10,3750 in te = 1,0000 in
Note: round inside edges per UG-76(c) Located on: MINOR BARREL Liquid static head included: 0,5732 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 2" XX Heavy Pad material specification: API 5L X65 (user defined) Pad diameter: 10,375 in Flange description: 2 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -46,5 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 0,3139 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 55 in End of nozzle to shell center: 27,185 in Nozzle inside diameter, new: 1,503 in Nozzle nominal wall thickness: 0,436 in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 7,185 in
This nozzle passes through a Category A joint.
Completed
13-P113
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Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP. UG-37 Area Calculation Summary (in2) For P = 1415,26 psi @ 150 °F The opening is adequately reinforced A A A required available 1 1,4762
1,9283
--
A2
A3
0,3354 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
1,3760 0,2169 0,1348
tmin 0,4360
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
95.950,20 125.339,49 534.955,50 46.159,30 334.160,25 135.599,30 642.517,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,0000
weld size is adequate
Calculations for internal pressure 1415,26 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11408).
Nozzle UCS-66 governing thk: 0,436 in Nozzle rated MDMT: -155 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Completed
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1415,259*0,7515/(17100*1 - 0,6*1415,259) 0,0654 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) 1,4762 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 1,503*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 0,436)*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,3354 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(0,436 - 0,0654)*0,2631*0,688 0,3354 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(0,436 - 0,0654)*(2,5*0,436 + 1)*0,2631 0,4076 in2
= = =
Leg2*fr3 0,90792*0,2631 0,2169 in2
(Part of the weld is outside of the limits) Completed
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A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1*1 1,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,3354 + 0,2169 + 0 + 1,376 1,9283 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0654 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,4317 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,4317 in The lesser of tr4 or tr5: tr6 = 0,1348 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.
Completed
13-P113
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Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear ( i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 95950,2 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,3354 + 1,376 + 0,2169 + 0)*65000 125339,5 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,3354 + 0 + 0,2169 + 0 + 2*0,436*0,688*0,2631)*65000 46159,3 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,3354 + 0 + 1,376 + 0,2169 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 135599,3 lbf
Completed
13-P113
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Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 46159,3 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 179443,8 = 334160,3 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP. UG-37 Area Calculation Summary (in2) For P = 1480 psi @ 70 °F The opening is adequately reinforced A A A required available 1 1,4762
1,9254
--
A2
A3
0,3325 --
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
treq
1,3760 0,2169 0,1348
tmin 0,4360
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
95.950,20 125.151,00 534.955,50 45.970,80 334.160,25 135.410,80 642.517,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,0000
weld size is adequate
Calculations for internal pressure 1480 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1480*0,7515/(17100*1 - 0,6*1480) 0,0686 in
tr (full area replacement) =0,688 in
Completed
13-P113
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Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) 1,4762 in2
Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 1,503*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 0,436)*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,3325 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(0,436 - 0,0686)*0,2631*0,688 0,3325 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(0,436 - 0,0686)*(2,5*0,436 + 1)*0,2631 0,4041 in2
= = =
Leg2*fr3 0,90792*0,2631 0,2169 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1*1 1,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,3325 + 0,2169 + 0 + 1,376 1,9254 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0686 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,4513 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,4513 in The lesser of tr4 or tr5: tr6 = 0,1348 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Completed
13-P113
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Strength of welded joints: (1) Inner fillet weld in shear ( i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 95950,2 lbf
W1-1 = = =
(A2 + A5 + A41 + A42)*Sv (0,3325 + 1,376 + 0,2169 + 0)*65000 125151 lbf
W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,3325 + 0 + 0,2169 + 0 + 2*0,436*0,688*0,2631)*65000 45970,8 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,3325 + 0 + 1,376 + 0,2169 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 135410,8 lbf
Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 45970,8 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 179443,8 = 334160,3 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 267,63 psi @ 150 °F The opening is adequately reinforced A A A required available 1 0,7381
1,9510
--
A2
A3
0,3581 --
A5
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
treq
1,3760 0,2169 0,0822
tmin 0,4360
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,0000
weld size is adequate
Calculations for external pressure 267,63 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-28 trn = 0,0403 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631)) 0,7381 in2 Completed
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Area available from FIG. UG-37.1 A1 = larger of the following= 0 in2 = = =
d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 1,503*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
= = =
2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) 2*(0,688 + 0,436)*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) 0 in2
A2 = smaller of the following= 0,3581 in2
A41
= = =
5*(tn - trn)*fr2*t 5*(0,436 - 0,0403)*0,2631*0,688 0,3581 in2
= = =
2*(tn - trn)*(2,5*tn + te)*fr2 2*(0,436 - 0,0403)*(2,5*0,436 + 1)*0,2631 0,4351 in2
= = =
Leg2*fr3 0,90792*0,2631 0,2169 in2
(Part of the weld is outside of the limits) A42
= = =
Leg2*fr4 02*1 0 in2
(Part of the weld is outside of the limits) A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1*1 1,376 in2
A1 + A2 + A41 + A42 + A5 0 + 0,3581 + 0,2169 + 0 + 1,376 1,951 in2
As Area >= A the reinforcement is adequate.
Completed
13-P113
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UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0403 in Wall thickness per UG-45(b)(2): tr2 = 0,0822 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,0822 in The lesser of tr4 or tr5: tr6 = 0,0822 in
Required per UG-45 is the larger of tr1 or tr6 = 0,0822 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. 1.1.1.95 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,2203/2,3750 = 3,0401 Do/t = 2,3750/0,040342 = 58,8711 From table G: A = 0,000903 From table CS-2: B = 11816,6680 Pa = 4*B/(3*(Do/t)) = 4*11816,6680/(3*(2,3750/0,040342)) = 267,6282 psi 1.1.1.96 Design thickness for external pressure Pa = 267,6282 psi = t + Corrosion = 0,040342 + 0,0000 = 0,0403"
Completed
13-P113
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1.1.1.97 PRESSURE INDICATOR - Nozzle #4 (N4) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 1,0000 in tw(upper) = 1,1000 in Leg42 = 1,0000 in Dp = 10,3750 in te = 1,1000 in
Note: round inside edges per UG-76(c) Located on: MAJOR BARREL Liquid static head included: 0,2844 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 2" XX Heavy Pad material specification: API 5L X65 (user defined) Pad diameter: 10,375 in Flange description: 2 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55 °F (UCS-66(b)(1)(b)) (UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 257,55 in End of nozzle to shell center: 31,88 in Nozzle inside diameter, new: 1,503 in Nozzle nominal wall thickness: 0,436 in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 7,88 in
This nozzle passes through a Category A joint.
Completed
13-P113
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Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP. UG-37 Area Calculation Summary (in2) For P = 1415,28 psi @ 150 °F The opening is adequately reinforced A A A A A required available 1 2 3 1,4762
1,5136
--
--
A welds
A5
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
1,5136 --
treq
tmin
0,1348
0,4360
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
95.950,20 120.185,00 534.955,50 32.060,80 352.104,66 130.444,80 642.517,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,1000
weld size is adequate
Calculations for internal pressure 1415,28 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11405).
Nozzle UCS-66 governing thk: 0,436 in Nozzle rated MDMT: -155 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Completed
13-P113
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1415,284*0,7515/(17100*1 - 0,6*1415,284) 0,0654 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) 1,4762 in2
Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1,1*1 1,5136 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 1,5136 1,5136 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Completed
13-P113
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UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0654 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5181 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,5181 in The lesser of tr4 or tr5: tr6 = 0,1348 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear OD*Leg*So
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
W1-1 = = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 95950,2 lbf
(A2 + A5 + A41 + A42)*Sv (0,3354 + 1,5136 + 0 + 0)*65000 120185 lbf
Completed
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W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,3354 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 32060,8 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,3354 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 130444,8 lbf
Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 32060,8 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP. UG-37 Area Calculation Summary (in2) For P = 1480 psi @ 70 °F The opening is adequately reinforced A A A A A required available 1 2 3 1,4762
1,5136
--
--
A5
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
1,5136 --
treq
tmin
0,1348
0,4360
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
95.950,20 119.996,50 534.955,50 31.872,31 352.104,66 130.256,30 642.517,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,1000
weld size is adequate
Calculations for internal pressure 1480 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1480*0,7515/(17100*1 - 0,6*1480) 0,0686 in
tr (full area replacement) =0,688 in
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) 1,4762 in2
Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1,1*1 1,5136 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 1,5136 1,5136 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Completed
13-P113
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AKTEK_ENG_13_P113_EC
EC-100
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UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0686 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5415 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,5415 in The lesser of tr4 or tr5: tr6 = 0,1348 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear ( i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
W1-1 = = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 95950,2 lbf
(A2 + A5 + A41 + A42)*Sv (0,3325 + 1,5136 + 0 + 0)*65000 119996,5 lbf
Completed
13-P113
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W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,3325 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 31872,31 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,3325 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 130256,3 lbf
Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 31872,31 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced A A A A A required available 1 2 3 0,7381
1,5136
--
--
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
1,5136 --
treq
tmin
0,0625
0,4360
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,1000
weld size is adequate
Calculations for external pressure 125,3 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-28 trn = 0,0298 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631)) 0,7381 in2 Completed
13-P113
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Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1,1*1 1,5136 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 1,5136 1,5136 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0298 in Wall thickness per UG-45(b)(2): tr2 = 0,0462 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,0625 in The lesser of tr4 or tr5: tr6 = 0,0625 in
Required per UG-45 is the larger of tr1 or tr6 = 0,0625 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.
Completed
13-P113
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1.1.1.98 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,9094/2,3750 = 3,3303 Do/t = 2,3750/0,029784 = 79,7400 From table G: A = 0,000520 From table CS-2: B = 7493,5347 Pa = 4*B/(3*(Do/t)) = 4*7493,5347/(3*(2,3750/0,029784)) = 125,2995 psi 1.1.1.99 Design thickness for external pressure Pa = 125,2995 psi = t + Corrosion = 0,029784 + 0,0000 = 0,0298"
Completed
13-P113
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1.1.1.100 SAFETY VALVE NOZZLE - Nozzle #5 (N5) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 0,5000 in tw(upper) = 0,6880 in Leg42 = 0,5000 in Dp = 9,3150 in te = 0,6880 in
Note: round inside edges per UG-76(c) Located on: MAJOR BARREL Liquid static head included: 0,2844 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 1" XX Heavy Pad material specification: API 5L X65 (user defined) Pad diameter: 9,315 in Flange description: 1 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55 °F (UCS-66(b)(1)(b)) (UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 239,84 in End of nozzle to shell center: 31,88 in Nozzle inside diameter, new: 0,599 in Nozzle nominal wall thickness: 0,358 in Nozzle corrosion allowance: 0,118 in Projection available outside vessel, Lpr: 7,88 in
This nozzle passes through a Category A joint.
Completed
13-P113
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Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP. UG-37 Area Calculation Summary (in2) For P = 1415,28 psi @ 150 °F The opening is adequately reinforced A A A A A required available 1 2 3 0,8178
0,9467
--
--
A welds
A5
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
0,9467 --
treq
tmin
0,2344
0,3580
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
53.159,20 70.504,72 237.865,14 14.617,60 145.366,63 76.152,32 301.370,50
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,1680
0,3500
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,3500
weld size is adequate
Nozzle to pad groove (Upper) 0,1680
0,6880
weld size is adequate
Calculations for internal pressure 1415,28 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11511).
Nozzle UCS-66 governing thk: 0,358 in Nozzle rated MDMT: -155 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,3455 in Normal to the vessel wall outside: 2,5*(tn - Cn) + te = 1,288 in
Completed
13-P113
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1415,284*0,4175/(17100*1 - 0,6*1415,284) 0,0364 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 0,835*0,688*1 + 2*0,24*0,688*1*(1 - 0,2631) 0,8178 in2
Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (2,691 - 0,835 - 2*0,24)*0,688*1 0,9467 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 0,9467 0,9467 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,24 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,168 in tc(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in
Completed
13-P113
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AKTEK_ENG_13_P113_EC
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UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,1544 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5181 in Wall thickness per UG-16(b): tr3 = 0,1805 in Standard wall pipe per UG-45(b)(4): tr4 = 0,2344 in The greater of tr2 or tr3: tr5 = 0,5181 in The lesser of tr4 or tr5: tr6 = 0,2344 in
Required per UG-45 is the larger of tr1 or tr6 = 0,2344 in Available nozzle wall thickness new, tn = 0,358 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear ( i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
W1-1 = = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (0,8178 - 0 + 2*0,24*0,2631*(1*0,688 - 1*0,688))*65000 53159,2 lbf
(A2 + A5 + A41 + A42)*Sv (0,138 + 0,9467 + 0 + 0)*65000 70504,72 lbf
Completed
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W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,138 + 0 + 0 + 0 + 2*0,24*0,688*0,2631)*65000 14617,6 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,138 + 0 + 0,9467 + 0 + 0 + 0 + 2*0,24*0,688*0,2631)*65000 76152,32 lbf
Load for path 1-1 lesser of W or W1-1 = 53159,2 lbf Path 1-1 through (2) & (3) = 233014,1 + 4851,03 = 237865,1 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 14617,6 lbf Path 2-2 through (1), (4), (6) = 8653,82 + 68356,4 + 68356,4 = 145366,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 53159,2 lbf Path 3-3 through (2), (4) = 233014,1 + 68356,4 = 301370,5 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP. UG-37 Area Calculation Summary (in2) For P = 1480 psi @ 70 °F The opening is adequately reinforced A A A A A required available 1 2 3 0,7751
0,9467
--
--
A welds
A5
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
0,9467 --
treq
tmin
0,1164
0,3580
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
50.382,47 79.442,22 239.455,94 26.331,84 145.366,63 87.866,55 301.370,50
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,3500
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,3500
weld size is adequate
Nozzle to pad groove (Upper) 0,2506
0,6880
weld size is adequate
Calculations for internal pressure 1480 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,3455 in Normal to the vessel wall outside: 2,5*(tn - Cn) + te = 1,583 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1480*0,2995/(17100*1 - 0,6*1480) 0,0273 in
tr (full area replacement) =0,688 in
Completed
13-P113
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Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 0,599*0,688*1 + 2*0,358*0,688*1*(1 - 0,2631) 0,7751 in2
Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (2,691 - 0,599 - 2*0,358)*0,688*1 0,9467 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 0,9467 0,9467 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,358 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in
Completed
13-P113
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UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0273 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5415 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1164 in The greater of tr2 or tr3: tr5 = 0,5415 in The lesser of tr4 or tr5: tr6 = 0,1164 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1164 in Available nozzle wall thickness new, tn = 0,358 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear zle dia*tn*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
W1-1 = = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (0,7751 - 0 + 2*0,358*0,2631*(1*0,688 - 1*0,688))*65000 50382,47 lbf
(A2 + A5 + A41 + A42)*Sv (0,2755 + 0,9467 + 0 + 0)*65000 79442,22 lbf
Completed
13-P113
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W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,2755 + 0 + 0 + 0 + 2*0,358*0,688*0,2631)*65000 26331,84 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,2755 + 0 + 0,9467 + 0 + 0 + 0 + 2*0,358*0,688*0,2631)*65000 87866,55 lbf
Load for path 1-1 lesser of W or W1-1 = 50382,47 lbf Path 1-1 through (2) & (3) = 233014,1 + 6441,83 = 239455,9 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 26331,84 lbf Path 2-2 through (1), (4), (6) = 8653,82 + 68356,4 + 68356,4 = 145366,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 50382,47 lbf Path 3-3 through (2), (4) = 233014,1 + 68356,4 = 301370,5 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
13-P113
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced A A A A A required available 1 2 3 0,4089
0,9467
--
--
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
0,9467 --
treq
tmin
0,1805
0,3580
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,1680
0,3500
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,3500
weld size is adequate
Nozzle to pad groove (Upper) 0,1680
0,6880
weld size is adequate
Calculations for external pressure 125,3 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,3455 in Normal to the vessel wall outside: 2,5*(tn - Cn) + te = 1,288 in
Nozzle required thickness per UG-28 trn = 0,0215 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(0,835*0,688*1 + 2*0,24*0,688*1*(1 - 0,2631)) 0,4089 in2 Completed
13-P113
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Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (2,691 - 0,835 - 2*0,24)*0,688*1 0,9467 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 0,9467 0,9467 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,24 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,168 in tc(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,1395 in Wall thickness per UG-45(b)(2): tr2 = 0,0462 in Wall thickness per UG-16(b): tr3 = 0,1805 in Standard wall pipe per UG-45(b)(4): tr4 = 0,2344 in The greater of tr2 or tr3: tr5 = 0,1805 in The lesser of tr4 or tr5: tr6 = 0,1805 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1805 in Available nozzle wall thickness new, tn = 0,358 in The nozzle neck thickness is adequate.
Completed
13-P113
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1.1.1.101 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,8890/1,3150 = 5,9992 Do/t = 1,3150/0,021462 = 61,2712 From table G: A = 0,000400 From table CS-2: B = 5758,1777 Pa = 4*B/(3*(Do/t)) = 4*5758,1777/(3*(1,3150/0,021462)) 125,3046 psi = 1.1.1.102 Design thickness for external pressure Pa = 125,3046 psi = t + Corrosion = 0,021462 + 0,1180 = 0,1395"
Completed
13-P113
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1.1.1.103 VENT NOZZLE - Nozzle #2 (N2) ASME Section VIII Division 1, 2004 Edition
tw(lower) = 0,6880 in Leg41 = 1,0000 in tw(upper) = 1,1000 in Leg42 = 1,0000 in Dp = 10,3750 in te = 1,1000 in
Note: round inside edges per UG-76(c) Located on: MAJOR BARREL Liquid static head included: 0,2844 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5) Nozzle longitudinal joint efficiency: 1,00 Nozzle description: 2" XX Heavy Pad material specification: API 5L X65 (user defined) Pad diameter: 10,375 in Flange description: 2 inch 600# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55 °F (UCS-66(b)(1)(b)) (UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 1415 psi@ 150°F ASME B16.5 flange rating MAP: 1480 psi@ 70°F ASME B16.5 flange hydro test: 2225 psi@ 70°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0,688 in Nozzle center line offset to datum line: 275,26 in End of nozzle to shell center: 31,88 in Nozzle inside diameter, new: 1,503 in Nozzle nominal wall thickness: 0,436 in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 7,88 in
This nozzle passes through a Category A joint.
Completed
13-P113
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Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP. UG-37 Area Calculation Summary (in2) For P = 1415,28 psi @ 150 °F The opening is adequately reinforced A A A A A required available 1 2 3 1,4762
1,5136
--
--
A welds
A5
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
1,5136 --
treq
tmin
0,1348
0,4360
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
95.950,20 120.185,00 534.955,50 32.060,80 352.104,66 130.444,80 642.517,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,1000
weld size is adequate
Calculations for internal pressure 1415,28 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11405).
Nozzle UCS-66 governing thk: 0,436 in Nozzle rated MDMT: -155 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Completed
13-P113
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Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1415,284*0,7515/(17100*1 - 0,6*1415,284) 0,0654 in
tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) 1,4762 in2
Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1,1*1 1,5136 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 1,5136 1,5136 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Completed
13-P113
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UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0654 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5181 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,5181 in The lesser of tr4 or tr5: tr6 = 0,1348 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear n*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
W1-1 = = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 95950,2 lbf
(A2 + A5 + A41 + A42)*Sv (0,3354 + 1,5136 + 0 + 0)*65000 120185 lbf
Completed
13-P113
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W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,3354 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 32060,8 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,3354 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 130444,8 lbf
Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 32060,8 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
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Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP. UG-37 Area Calculation Summary (in2) For P = 1480 psi @ 70 °F The opening is adequately reinforced A A A A A required available 1 2 3 1,4762
1,5136
--
--
A5
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
1,5136 --
treq
tmin
0,1348
0,4360
Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads Weld load Weld load W W1-1
Path 1-1 strength
Weld load W2-2
Path 2-2 strength
Weld load W3-3
Path 3-3 strength
95.950,20 119.996,50 534.955,50 31.872,31 352.104,66 130.256,30 642.517,25
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,1000
weld size is adequate
Calculations for internal pressure 1480 psi @ 70 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-27(c)(1) trn
= = =
P*Rn/(Sn*E - 0,6*P) 1480*0,7515/(17100*1 - 0,6*1480) 0,0686 in
tr (full area replacement) =0,688 in
Completed
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Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
d*tr*F + 2*tn*tr*F*(1 - fr1) 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) 1,4762 in2
Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1,1*1 1,5136 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 1,5136 1,5136 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Completed
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UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0686 in (E =1) Wall thickness per UG-45(b)(1): tr2 = 0,5415 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,5415 in The lesser of tr4 or tr5: tr6 = 0,1348 in
Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0,74*65000 = 48100 psi Nozzle wall in shear: 0,7*17100 = 11970 psi Inner fillet weld in shear: 0,49*17100 = 8379 psi Outer fillet weld in shear: 0,49*65000 = 31850 psi Upper groove weld in tension: 0,74*65000 = 48100 psi
Strength of welded joints: (1) Inner fillet weld in shear i
f
(2) Outer fillet weld in shear o
f
(3) Nozzle wall in shear zle dia*tn*Sn
f
(4) Groove weld in tension w*Sg
f
(6) Upper groove weld in tension w*Sg
f
Loading on welds per UG-41(b)(1) W
= = =
W1-1 = = =
(A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 95950,2 lbf
(A2 + A5 + A41 + A42)*Sv (0,3325 + 1,5136 + 0 + 0)*65000 119996,5 lbf
Completed
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W2-2 = = =
(A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv (0,3325 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 31872,31 lbf
W3-3 = = =
(A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv (0,3325 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 130256,3 lbf
Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 31872,31 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).
Completed
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Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2) For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced A A A A A required available 1 2 3 0,7381
1,5136
--
--
--
UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45
A welds
A5
1,5136 --
treq
tmin
0,0625
0,4360
Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary Required weld Actual weld throat size (in) throat size (in)
Weld description
Status
Nozzle to pad fillet (Leg41)
0,2500
0,7000
weld size is adequate
Pad to shell fillet (Leg42)
0,3440
0,7000
weld size is adequate
Nozzle to pad groove (Upper) 0,3052
1,1000
weld size is adequate
Calculations for external pressure 125,3 psi @ 150 °F
Limits of reinforcement per UG-40 Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in
Nozzle required thickness per UG-28 trn = 0,0298 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1 A
= = =
0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) 0,5*(1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631)) 0,7381 in2 Completed
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Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations. A5
= = =
Area = = =
(Dp - d - 2*tn)*te*fr4 (3,751 - 1,503 - 2*0,436)*1,1*1 1,5136 in2
A1 + A2 + A41 + A42 + A5 0 + 0 + 0 + 0 + 1,5136 1,5136 in2
As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in
Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in tw(min) = 0,5*tmin = 0,344 in tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in
UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): tr1 = 0,0298 in Wall thickness per UG-45(b)(2): tr2 = 0,0462 in Wall thickness per UG-16(b): tr3 = 0,0625 in Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in The greater of tr2 or tr3: tr5 = 0,0625 in The lesser of tr4 or tr5: tr6 = 0,0625 in
Required per UG-45 is the larger of tr1 or tr6 = 0,0625 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.
Completed
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1.1.1.104 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,9094/2,3750 = 3,3303 Do/t = 2,3750/0,029784 = 79,7400 From table G: A = 0,000520 From table CS-2: B = 7493,5347 Pa = 4*B/(3*(Do/t)) = 4*7493,5347/(3*(2,3750/0,029784)) = 125,2995 psi 1.1.1.105 Design thickness for external pressure Pa = 125,2995 psi = t + Corrosion = 0,029784 + 0,0000 = 0,0298"
Completed
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1.1.1.106 SADDLE #1
Saddle material: ASTM A36 Saddle construction is: Centered web Saddle allowable stress: Ss = 20.000,00 psi Saddle yield stress: Sy = 38.000,00 psi Saddle distance to datum: 55,0000 in Tangent to tangent length: L = 322,6900 in Saddle separation: Ls = 212,2800 in Vessel radius: R = 24,0000 in Tangent distance left: Al = 52,4100 in Tangent distance right: Ar = 58,0000 in Saddle height: Hs = 53,5400 in Saddle contact angle: θ = 120 ° Wind pressure: 27,1536 psf Wear plate thickness: tp = 0,6880 in Wear plate width: Wp = 26,8500 in Wear plate contact angle: θw = 132 ° Web plate thickness: ts = 0,6880 in Base plate length: E = 43,3000 in Base plate width: F = 15,7400 in Base plate thickness: tb = 1,0000 in Number of stiffener ribs: n= 6 Largest stiffener rib spacing: di = 8,3850 in Stiffener rib thickness: tw = 0,3750 in Saddle width: B = 15,7400 in Anchor bolt size & type: 1 inch series 8 threaded Anchor bolt material: ASTM A193 Anchor bolt allowable shear: 15.000,00 psi Anchor bolt corrosion allowance: 0,0000 in Anchor bolts per saddle: 4 Base coefficient of friction: 0,45
Weight on left saddle: operating = 26.794,00 lb, test = 26.802,00 lb Weight on right saddle: operating = 10.857,00 lb, test = 10.850,00 lb Weight of saddle pair = 2.118,00 lb
Completed
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Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels on Two Saddle Supports" by L.P. Zick. Seismic base shear on vessel Vessel is assumed to be a rigid structure. Method of seismic analysis: UBC 1997 ground supported Vertical seismic accelerations considered: Yes Force Multiplier: 0,4 Minimum Weight Multiplier: 0,2 Seismic zone: 4 Importance factor: I = 1,5 Soil profile: SD Near source factor: Na = 1 V = 0,7 * Ca * I * W/1,4 = 0,7 * 0,44 * 1,5 * 37.651,00/1,4 = 12.424,83 lb Saddle reactions due to weight + seismic Vv = vertical seismic force acting on right saddle V = horizontal seismic shear acting on right saddle (worst case if not slotted) Seismic longitudinal reaction, Ql (right saddle): Ql = V * Hs / Ls + Vv = 12.424,83 * 53,54 / 212,28 + 2.171,40 = 5.305,117 lb Seismic transverse reaction, Qt (right saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) + Vv = 3.582,81*53,54/(20*Sin( 120 /2 )) + 2.171,40 = 13.246,34 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 10.857,00 + 13.246,34 = 24.103,34 lb Vv = vertical seismic force acting on left saddle V = horizontal seismic shear acting on left saddle (worst case if not slotted) Seismic longitudinal reaction, Ql (left saddle): Ql = V * Hs / Ls + Vv = 12.424,83 * 53,54 / 212,28 + 5.358,80 = 8.492,517 lb Seismic transverse reaction, Qt (left saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) + Vv = 8.842,02*53,54/(24*Sin( 120 /2 )) + 5.358,80 = 28.135,35 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 26.794,00 + 28.135,35 = 54.929,35 lb Completed
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Transverse wind shear on vessel Vwt = Pw*G*(Cf(shell)*(Projected shell area) + Cf(saddle)*(Projected saddle area)) = 27,1536*0,85*(0,4*103,8682 + 2*6,894995) = 1.277,215 lb End wind shear on vessel 2 o
Vwe = Pw*G*(Cf(shell)*
/ 144 + Cf(saddle)*(Projected saddle area)) / 144 + 2*10,08516)
2
= 813,5891 lb Saddle reactions due to weight + wind V = horizontal wind shear acting on right saddle (worst case if not slotted) Wind longitudinal reaction, Ql (right saddle): Ql = V * H s / L s = 624,07 * 53,54 / 212,28 = 157,3992 lb Wind transverse reaction, Qt (right saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) = 610,3115*53,54/(20*Sin( 120 /2 )) = 1.886,554 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 10.857,00 + 1.886,554 = 12.743,55 lb V = horizontal wind shear acting on left saddle (worst case if not slotted) Wind longitudinal reaction, Ql (left saddle): Ql = V * H s / L s = 813,5891 * 53,54 / 212,28 = 205,1986 lb Wind transverse reaction, Qt (left saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) = 666,9037*53,54/(24*Sin( 120 /2 )) = 1.717,907 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 26.794,00 + 1.717,907 = 28.511,91 lb
Completed
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Vessel condition
Load
Bending + pressure between saddles Bending + pressure at the saddle (psi) (psi) S1 (+)
allow (+)
S1 (-)
allow (-)
S2 (+)
allow (+)
S2 (-)
allow (-)
Seismic Operating 19.679
78.000
1.210
20.274
20.043
78.000
1.574
20.274
Seismic Vacuum
78.000
1.464
20.274
3.060
78.000
3.270
20.274
1.210
Wind
Operating 19.097
78.000
628
20.274
19.780
78.000
1.311
20.274
Wind
Test
24.599
97.500
603
20.463
25.308
97.500
1.311
20.463
Wind
Vacuum
628
78.000
882
20.274
2.550
78.000
2.760
20.274
Load
Tangential shear (psi)
Vessel condition
S3
Circumferential stress (psi) S4 S4 (Wear (horns) plate)
allow
allow (+/-)
Stress over saddle (psi) S5
Splitting (psi)
allow
S6
allow
Seismic Operating 3.394 52.000 -5.056
-8.459 97.500 3.144 19.000 466
13.333
Seismic Vacuum
3.394 52.000 -5.056
-8.459 97.500 3.144 19.000 466
13.333
Wind
Operating 1.587 52.000 -2.624
-4.391 97.500 1.632 19.000 242
13.333
Wind
Test
1.504 78.000 -2.519
-4.215 97.500 1.567 34.200 232
34.200
Wind
Vacuum
1.587 52.000 -2.624
-4.391 97.500 1.632 19.000 242
13.333
Load Case 1: Seismic ,Operating
Longitudinal stress between saddles (Seismic ,Operating, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (
2
*t)
2
*0,688)
= 1.209,723 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S1t = S1 + Sp = 19.678,67 psi Maximum compressive stress (shut down) S1c = S1 = 1.209,723 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the left saddle (Seismic ,Operating) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in Completed
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Seismic vertical acceleration coefficient m = 0,6060606*0,33 = 0,2 w = Wt*(1 + m)/Le = 37.651,00*(1 + 0,2)/334,6833 = 134,9969 lb/in Bending moment at the left saddle: Mq = w*(2*H*Al/3 + Al2/2 - (R2 - H2)/4) = 134,9969*(2*7,44*52,41/3 + 52,412/2 - (242 - 7,442)/4) = 202.926,8 lb-in S2 = +- Mq*K1'/ (
2
*t)
2
*0,688)
= 1.573,681 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S2t = S2 + Sp = 20.042,63 psi Maximum compressive stress (shut down) S2c = S2 = 1.573,681 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Seismic ,Operating) Qshear = Q - w*(a + 2*H/3) = 54.929,35 - 134,9969*(52,41 + 2*7,44/3) = 47.184,58 lb S3 = K2,2*Qshear/(R*t) = K2,2*47.184,58/(23,656*0,688) = 3.394,032 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi) Circumferential stress at the left saddle horns (Seismic ,Operating) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t2+tp2)) = -54.929,35/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*54.929,35/(2*(0,6882+0,6882)) = -5.056,105 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Seismic ,Operating) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t2) = -54.929,35/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*54.929,35/(2*0,6882) = -8.458,564 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Seismic ,Operating) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*54.929,35/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 3.144,262 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi)
Completed
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Saddle splitting load (left, Seismic ,Operating) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in2 S6 = K8*Q / Ae = 0,2035*54.929,35 / 23,9768 = 466,2058 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi) Load Case 2: Seismic ,Vacuum
Longitudinal stress between saddles (Seismic ,Vacuum, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (
2
*t)
2
*0,688)
= 1.209,723 psi Sp = P*R/(2*t) = 15*23,312/(2*0,688) = 254,1279 psi Maximum tensile stress (shut down) S1t = S1 = 1.209,723 psi Maximum compressive stress S1c = S1 + Sp = 1.463,851 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the right saddle (Seismic ,Vacuum) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in Seismic vertical acceleration coefficient m = 0,6060606*0,33 = 0,2 w = Wt*(1 + m)/Le = 37.651,00*(1 + 0,2)/334,6833 = 134,9969 lb/in Bending moment at the right saddle: Mq = w*(2*H*Ar/3 + Ar2/2 - (R2 - H2)/4) = 134,9969*(2*10,55*58/3 + 582/2 - (202 - 10,552)/4) = 272.391,1 lb-in S2 = +- Mq*K1'/ (
2
*t)
2
*0,688)
= 3.059,585 psi Sp = P*R/(2*t) = 15*19,312/(2*0,688) = 210,5233 psi
Completed
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Maximum tensile stress (shut down) S2t = S2 = 3.059,585 psi Maximum compressive stress S2c = S2 + Sp = 3.270,108 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Seismic ,Vacuum) Qshear = Q - w*(a + 2*H/3) = 54.929,35 - 134,9969*(52,41 + 2*7,44/3) = 47.184,58 lb S3 = K2,2*Qshear/(R*t) = K2,2*47.184,58/(23,656*0,688) = 3.394,032 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi) Circumferential stress at the left saddle horns (Seismic ,Vacuum) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t2+tp2)) = -54.929,35/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*54.929,35/(2*(0,6882+0,6882)) = -5.056,105 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Seismic ,Vacuum) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t2) = -54.929,35/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*54.929,35/(2*0,6882) = -8.458,564 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Seismic ,Vacuum) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*54.929,35/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 3.144,262 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi) Saddle splitting load (left, Seismic ,Vacuum) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in2 S6 = K8*Q / Ae = 0,2035*54.929,35 / 23,9768 = 466,2058 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi) Completed
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Load Case 3: Wind ,Operating
Longitudinal stress between saddles (Wind ,Operating, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (
2
*t)
2
*0,688)
= 627,9251 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S1t = S1 + Sp = 19.096,87 psi Maximum compressive stress (shut down) S1c = S1 = 627,9251 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the left saddle (Wind ,Operating) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in w = Wt/Le = 37.651,00/334,6833 = 112,4974 lb/in Bending moment at the left saddle: Mq = w*(2*H*Al/3 + Al2/2 - (R2 - H2)/4) = 112,4974*(2*7,44*52,41/3 + 52,412/2 - (242 - 7,442)/4) = 169.105,7 lb-in S2 = +- Mq*K1'/ (
2
*t)
2
*0,688)
= 1.311,401 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S2t = S2 + Sp = 19.780,34 psi Maximum compressive stress (shut down) S2c = S2 = 1.311,401 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Wind ,Operating) Qshear = Q - w*(a + 2*H/3) = 28.511,91 - 112,4974*(52,41 + 2*7,44/3) = 22.057,93 lb S3 = K2,2*Qshear/(R*t) = K2,2*22.057,93/(23,656*0,688) = 1.586,648 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi)
Completed
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Circumferential stress at the left saddle horns (Wind ,Operating) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t2+tp2)) = -28.511,91/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*28.511,91/(2*(0,6882+0,6882)) = -2.624,447 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Wind ,Operating) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t2) = -28.511,91/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*28.511,91/(2*0,6882) = -4.390,545 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Wind ,Operating) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*28.511,91/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 1.632,077 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi) Saddle splitting load (left, Wind ,Operating) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in2 S6 = K8*Q / Ae = 0,2035*28.511,91 / 23,9768 = 241,9911 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi) Load Case 4: Wind ,Test
Longitudinal stress between saddles (Wind ,Test, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (
2
*t)
2
*0,688)
= 602,7526 psi Sp = P*R/(2*t) = 1.416,392*23,312/(2*0,688) = 23.996,32 psi Maximum tensile stress S1t = S1 + Sp = 24.599,07 psi Maximum compressive stress (shut down) S1c = S1 = 602,7526 psi Tensile stress is acceptable (<= 0,9*Sy = 97.500,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.463,34 psi)
Completed
13-P113
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Longitudinal stress at the left saddle (Wind ,Test) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in w = Wt/Le = 37.652,00/334,6833 = 112,5004 lb/in Bending moment at the left saddle: Mq = w*(2*H*Al/3 + Al2/2 - (R2 - H2)/4) = 112,5004*(2*7,44*52,41/3 + 52,412/2 - (242 - 7,442)/4) = 169.110,1 lb-in S2 = +- Mq*K1'/ (
2
*t)
2
*0,688)
= 1.311,435 psi Sp = P*R/(2*t) = 1.416,392*23,312/(2*0,688) = 23.996,32 psi Maximum tensile stress S2t = S2 + Sp = 25.307,75 psi Maximum compressive stress (shut down) S2c = S2 = 1.311,435 psi Tensile stress is acceptable (<= 0,9*Sy = 97.500,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.463,34 psi) Tangential shear stress in the shell (left saddle, Wind ,Test) Qshear = Q - w*(a + 2*H/3) = 27.368,91 - 112,5004*(52,41 + 2*7,44/3) = 20.914,76 lb S3 = K2,2*Qshear/(R*t) = K2,2*20.914,76/(23,656*0,688) = 1.504,419 psi Tangential shear stress is acceptable (<= 0.8*S = 78.000,00 psi) Circumferential stress at the left saddle horns (Wind ,Test) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t2+tp2)) = -27.368,91/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*27.368,91/(2*(0,6882+0,6882)) = -2.519,238 psi Circumferential stress at saddle horns is acceptable (<= 0,9*Sy = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Wind ,Test) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t2) = -27.368,91/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*27.368,91/(2*0,6882) = -4.214,535 psi Circumferential stress at wear plate horns is acceptable (<= 0,9*Sy = 97.500,00 psi)
Completed
13-P113
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Ring compression in shell over left saddle (Wind ,Test) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*27.368,91/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 1.566,649 psi Ring compression in shell is acceptable (<= 0,5*Sy = 34.200,00 psi) Saddle splitting load (left, Wind ,Test) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in2 S6 = K8*Q / Ae = 0,2035*27.368,91 / 23,9768 = 232,2901 psi Stress in saddle is acceptable (<= 0,9*Sy = 34.200,00 psi) Load Case 5: Wind ,Vacuum
Longitudinal stress between saddles (Wind ,Vacuum, left saddle loading and geometry govern) 2
S1 = +- 3*K1 = 3*0,330 = 627,9251 psi
*t)
2
*0,688)
Sp = P*R/(2*t) = 15*23,312/(2*0,688) = 254,1279 psi Maximum tensile stress (shut down) S1t = S1 = 627,9251 psi Maximum compressive stress S1c = S1 + Sp = 882,053 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the right saddle (Wind ,Vacuum) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in w = Wt/Le = 37.651,00/334,6833 = 112,4974 lb/in Bending moment at the right saddle: Mq = w*(2*H*Ar/3 + Ar2/2 - (R2 - H2)/4) = 112,4974*(2*10,55*58/3 + 582/2 - (202 - 10,552)/4) = 226.992,6 lb-in S2 = +- Mq*K1'/ (
2
*t)
2
*0,688)
Completed
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= 2.549,654 psi Sp = P*R/(2*t) = 15*19,312/(2*0,688) = 210,5233 psi Maximum tensile stress (shut down) S2t = S2 = 2.549,654 psi Maximum compressive stress S2c = S2 + Sp = 2.760,177 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Wind ,Vacuum) Qshear = Q - w*(a + 2*H/3) = 28.511,91 - 112,4974*(52,41 + 2*7,44/3) = 22.057,93 lb S3 = K2,2*Qshear/(R*t) = K2,2*22.057,93/(23,656*0,688) = 1.586,648 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi) Circumferential stress at the left saddle horns (Wind ,Vacuum) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t2+tp2)) = -28.511,91/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*28.511,91/(2*(0,6882+0,6882)) = -2.624,447 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Wind ,Vacuum) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t2) = -28.511,91/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*28.511,91/(2*0,6882) = -4.390,545 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Wind ,Vacuum) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*28.511,91/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 1.632,077 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi) Saddle splitting load (left, Wind ,Vacuum) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in2 S6 = K8*Q / Ae = 0,2035*28.511,91 / 23,9768 = 241,9911 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi) Completed
13-P113
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Shear stress in anchor bolting, one end slotted Maximum seismic or wind base shear = 12.424,83 lb Thermal expansion base shear = W* Corroded root area for a 1 inch series 8 threaded bolt = 0,551 in2 ( 4 per saddle ) Bolt shear stress = 12.533,85/(0,551* 4) = 5686,86 psi Anchor bolt stress is acceptable (<= 15.000,00 psi) Web plate buckling check (Escoe pg 251) Allowable compressive stress Sc is the lesser of 20.000,00 or 225.868,6 psi: (20.000,00) *E/(12*(1 - 0,32)*(di/tw)2) *29.000.000/(12*(1 - 0,32)*(8,385/0,688)2) = 225.868,6 psi Sc = Ki
2
2
Allowable compressive load on the saddle be = di*ts/(di*ts + 2*tw*(b - 1)) = 8,385*0,688/(8,385*0,688 + 2*0,375*(15,74 - 1)) = 0,3428983 Fb = n*(As + 2*be*tw)*Sc = 6*(5,6445 + 2*0,3428983*0,688)*20.000,00 = 733.959,4 lb Saddle loading of 55.988,35 is <= Fb; satisfactory. Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted) b = V * (Hs - xo)* y / I + Q / A = 12.424,83 * (53,54 - 16,53987)* 7,87 / 732,2853 + 54.929,35 / 57,70002 = 5.892,677 psi
The primary bending + axial stress in the saddle <= 20.000 psi; satisfactory. Secondary bending + axial stress in the saddle due to end loads (includes thermal expansion, assumes one saddle slotted) b = V * (Hs - xo)* y / I + Q / A = 24.958,68 * (53,54 - 16,53987)* 7,87 / 732,2853 + 54.929,35 / 57,70002 = 10.876,72 psi
The secondary bending + axial stress in the saddle < 2*Sy= 76.000 psi; satisfactory. Saddle base plate thickness check (Roark sixth edition, Table 26, case 7a) where a = 8,3850, b = 7,5260 in 2 0,5 tb 1*q*b /(1,5*Sa)) = (0,8058*82,14953*7,5262/(1,5*20.000,00))0,5 = 0,3535 in
The base plate thickness of 1,0000 in is adequate.
Completed
13-P113
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Foundation bearing check Sf = Qmax / (F*E) = 55.988,35 / (15,74*43,3) = 82,14953 psi Concrete bearing stress < 750 psi ; satisfactory.
Completed
13-P113
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1.1.1.107 Seismic Code Seismic calculations are reported in the saddle report.
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1.1.1.108 Wind Code Wind calculations are reported in the saddle report.
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1.1.1.109 Lifting Lug #1
1.1.1.110 Geometry Inputs Attached To
MAJOR BARREL
Orientation
Longitudinal
Length of Lug, L
10,0000"
Height of Lug, B
5,0000"
Thickness of Lug, t
1,0000"
Hole Diameter, d
2,0000"
Load eccentricity, a1
1,0000"
Distance from Load to shell or pad, a2 2,5000" Weld size, tw
0,2500"
Width of Pad, Bp
6,0000"
Length of Pad, Lp
12,0000"
Pad Thickness, tp
0,5000"
Pad weld size, twp
0,2500"
Load angle normal to vessel, β
-20,2800 °
Angular Position
0,00°
Load angle from vertical, υ
-20,2800 °
1.1.1.111 Intermediate Values Load factor
1,5000
Vessel Weight (new, incl. Load Factor), W
34076 lb
Lug Weight (new), Wlug
24 lb
Distance from center of gravity to this lug, x1
63,1254"
Distance from center of gravity to second lug, x2 83,8746" Allowable stress, tensile, σt
20000 psi
Allowable stress, shear, σs
13500 psi
Allowable stress, bearing, σp
30000 psi
Allowable stress, bending, σb
22000 psi
Allowable stress, weld shear, τallowable
13500 psi
1.1.1.112 Summary Values Required Lift pin diameter, dreqd 0,9887" Required Lug thickness, treqd
Completed
0,3455"
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Lug Stress Ratio, σratio
0,20
Weld Shear Stress Ratio, τratio
0,74
Lug design
Acceptable
Local stresses (WRC 107)
Acceptable
1.1.1.113 Lift Forces Fr = force on vessel at lug Fr = [W / cos(υ1)] * (1 - x1 / (x1 + x2)) = (34076,270) / cos(-20,2800) * (1 - 63,125/ (63,125 + 83,875)) = 20728 lbf where 'x1' is the distance between this lug and the center of gravity 'x2' is the distance between the second lift lug and the center of gravity 1.1.1.114 Lug Pin Diameter - Shear stress dreqd = (2*Fr / (π*σs))0.5 = (2*20728,0039 / (π*13500,0))0.5 = 0,9887" dreqd / d=
0,9887 / 2,0000
σ
Fr / A Fr / (2*(0.25*π*d2)) 20728,0039 / (2*(0.25*π*2,00002))=
= = =
=
0,49
Acceptable
3298,9641 psi
σ / σs = 3298,96 / 13500,00 = 0,24 1.1.1.115 Lug Thickness - Tensile stress treqd = Fr / ((L-d)*σt) = 20728,0039 / ((10,0000 - 2,0000)*20000,0)=
0,1296"
treqd / t=
0,1296 / 1,0000
0,13
σ
Fr / A Fr / ((L - d)*t) 20728,0039 / ((10,0000 - 2,0000)*1,0000) =
= = =
=
σ / σt = 2591,00 / 20000,00 1.1.1.116 Lug Thickness - Bearing stress treqd = Fv / (d*σp) = 20728,0039 / (2,0000*30000,0) = 0,3455"
=
treqd / t
=
0,3455 / 1,0000
=0,35
σ
= = =
Fv / Abearing Fv / (d*(t)) 20728,0039 / (2,0000 *(1,0000))=
Acceptable
Acceptable
2591,0005 psi 0,13
Acceptable
Acceptable
10364,0020 psi
σ / σp = 10364,00 / 30000,00 = 0,35 Acceptable 1.1.1.117 Lug Plate Stress Lug stress tensile + bending during lift: σ ratio = Ften / (Aten*σt) + Mbend / (Zbend*σb) ≤ 1.0 = (Fr * cos(α) ) / (t * L * σt) + (6 * abs(Fr * sin(α) * Hght - Fr * cos(α) * a1) ) / (t * L2 * σb) ≤ 1.0 20728*cos(-20,3) / (1,0000*10,0000*20000,0) + 6*abs(20728*sin(-20,3)*2,5000 - 20728*cos(= 20,3)*1,0000) / (1,0000*10,00002*22000,0)
0,20
Acceptable
Completed
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1.1.1.118 Weld Stress Weld stress, tensile, bending and shear during lift: Shear stress at lift angle -20,28°; lift force = 20728,0039 lbf Aweld =(0.707)*h*2*(L + t) =(0.707)*0,2500*2*(10,0000 + 1,0000) τt τb
τs
= 3,8885 in²
=Fr * cos(α) / Aweld =20728 * cos(-20,3) / 3,8885
= 5000,1475 psi
=M * c / I =3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * L * (3*t + L)) 3 * abs(20728 * sin(-20,3) * 2,5000 - 20728 * cos(-20,3) * 1,0000) / = (22,9775)
= 4883,6011 psi
=Fr * sin(α) / Aweld = -1847,6267 psi
=20728 * sin(-20,3) / 3,8885 =sqr( (τt + τb)2 + τs2 ) / τallowable ≤ 1.0 =sqr ( (5000,1475 + 4883,6011)2 + (-1847,6267)2 ) / 13500,00 Pad Weld Stress, tensile, bending and shear during lift: Shear stress at lift angle -20,28°; lift force = 20728,0039 lbf Aweld =(0.707)*hp*2*(Lp + Bp) =(0.707)*0,2500*2*(12,0000 + 6,0000) τ ratio
τt τb
τs
= 0,74
= 6,3630 in²
=Fr * cos(α) / Aweld =20728 * cos(-20,3) / 6,3630
= 3055,6458 psi
=M * c / I =3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * Lp * (3*Wp + Lp)) 3 * abs(20728 * sin(-20,3) * 3,0000 - 20728 * cos(-20,3) * 1,0000) / = (63,6300)
= 1932,8885 psi
=Fr * sin(α) / Aweld = -1129,1053 psi
=20728 * sin(-20,3) / 6,3630 τ ratio
Acceptable
=sqr( (τt + τb)2 + τs2 ) / τallowable ≤ 1.0 =sqr ( (3055,6458 + 1932,8885)2 + (-1129,1053)2 ) / 13500,00
Completed
= 0,38
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1.1.1.119 WRC 107 Analysis 1.1.1.120 Geometry Height(radial):
5,0000" Pad Thickness: 0,5000"
Width (circumferential): 1,0000" Pad Width:
6,0000"
Length
10,0000" Pad Length:
12,0000"
Fillet Weld Size:
0,2500" Pad Weld Size: 0,2500"
Location Angle:
0,00°
Applied Loads Radial load: Pr = -19.443,07 lbf Circumferential moment: Mc = 0,00 lbf-in Circumferential shear: Vc = 0,00 lbf Longitudinal moment: ML = -2.110,42 lbf-in Longitudinal shear: VL = -7.184,50 lbf Torsion moment: Mt = 0,00 lbf-in Internal pressure: P = 0,000 psi Mean shell radius: Rm = 23,6560 in Shell yield stress: Sy = 65.000,00 psi Maximum stresses due to the applied loads at the lug edge (includes pressure) Rm/t =19,9125 C1 = 0,7500, C2 = 3,0000 in Note: Actual lug C1/C2 < 1/4, C1/C2 = 1/4 used as this is the minimum ratio covered by WRC 107. Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 20.072,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 2.675,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.
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Stresses at the lug edge per WRC Bulletin 107 Figure
value
Au
Al
Bu
Bl
Cu
Cl
Du
Dl
3C*
3,5135
0,0938
0
0
0
0
2.431
2.431
2.431
2.431
4C*
3,8176
0,0761
2.641
2.641
2.641
2.641
0
0
0
0
1C
0,2129
0,0558
0
0
0
0
17.598
17.598 17.598 17.598
2C-1
0,1768
0,0558
14.614
14.614 0 14.614 14.614
0
0
0
3A*
0,1706
0,0503
0
0
0
0
0
0
0
0
1A
0,1067
0,0654
0
0
0
0
0
0
0
0
3B*
1,2733
0,0799
34
34
-34
-34
0
0
0
0
1B-1
0,0588
0,0715
312
-312
-312
312
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
0
Total circumferential stress
17.601
16.909 20.029 20.029 12.251 11.695 15.167 15.167
Primary membrane circumferential stress*
2.675
2.675
2.607
2.607
2.431
2.431
2.431
2.431
3C*
3,6687
0,0761
2.538
2.538
2.538
2.538
0
0
0
0
4C*
3,7303
0,0938
0
0
0
0
2.581
2.581
2.581
2.581
1C-1
0,1839
0,0793
15.201
15.201 0 15.201 15.201
0
0
0
2C
0,1402
0,0793
0
0
0
0
11.589
11.589 11.589 11.589
4A*
0,2297
0,0503
0
0
0
0
0
0
0
0
2A
0,0598
0,0911
0
0
0
0
0
0
0
0
4B*
0,3363
0,0799
16
16
-16
-16
0
0
0
0
2B-1
0,0870
0,0985
335
-335
-335
335
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
0
Total longitudinal stress
18.090
17.388 14.170 -9.008 12.982 12.344
14.170 -9.008
Primary membrane longitudinal stress*
2.554
2.554
2.522
2.522
2.581
2.581
2.581
2.581
Shear from Mt
0
0
0
0
0
0
0
0
Circ shear from Vc
0
0
0
0
0
0
0
0
Long shear from VL
0
0
0
0
504
504
-504
-504
Total Shear stress
0
0
0
0
504
504
-504
-504
Combined stress (PL+Pb+Q)
18.090
17.388 20.072 20.072 12.982 12.344 15.208 15.208
Note: * denotes primary stress.
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Maximum stresses due to the applied loads at the pad edge (includes pressure) Rm/t =34,3837 C1 = 3,2500, C2 = 6,2500 in Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 23.981,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 5.739,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.
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Stresses at the pad edge per WRC Bulletin 107 Figure
value
Au
Al
Bu
Bl
Cu
Cl
Du
Dl
3C*
2,5429
0,2490
0
0
0
0
3.038
3.038
3.038
3.038
4C*
4,7378
0,2149
5.660
5.660
5.660
5.660
0
0
0
0
1C
0,0849
0,1759
0
0
0
0
20.924
20.924 20.924 20.924
2C-1
0,0512
0,1759
12.619
12.619 0 12.619 12.619
0
0
0
3A*
1,3452
0,1709
0
0
0
0
0
0
0
0
1A
0,0829
0,1856
0
0
0
0
0
0
0
0
3B*
3,5667
0,2125
79
79
-79
-79
0
0
0
0
1B-1
0,0291
0,1986
166
-166
-166
166
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
0
Total circumferential stress
18.524 -7.046
18.034 -6.872
23.962
23.962 17.886 17.886
Primary membrane circumferential stress*
5.739
5.739
5.581
5.581
3.038
3.038
3.038
3.038
3C*
3,0442
0,2149
3.637
3.637
3.637
3.637
0
0
0
0
4C*
4,3987
0,2490
0
0
0
0
5.255
5.255
5.255
5.255
1C-1
0,0689
0,2210
16.981
16.981 0 16.981 16.981
0
0
0
2C
0,0382
0,2210
0
0
0
0
9.415
-9.415
9.415
-9.415
4A*
2,3239
0,1709
0
0
0
0
0
0
0
0
2A
0,0384
0,2264
0
0
0
0
0
0
0
0
4B*
1,4019
0,2125
45
45
-45
-45
0
0
0
0
2B-1
0,0400
0,2350
192
-192
-192
192
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
0
Total longitudinal stress
20.855
20.381 14.670 -4.160 13.491 13.197
14.670 -4.160
Primary membrane longitudinal stress*
3.682
3.682
3.592
3.592
5.255
5.255
5.255
5.255
Shear from Mt
0
0
0
0
0
0
0
0
Circ shear from Vc
0
0
0
0
0
0
0
0
Long shear from VL
0
0
0
0
418
418
-418
-418
Total Shear stress
0
0
0
0
418
418
-418
-418
Combined stress (PL+Pb+Q)
20.855
20.381 23.981 23.981 13.491 13.197 17.899 17.899
Note: * denotes primary stress.
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1.1.1.121 Lifting Lug #2
1.1.1.122 Geometry Inputs Attached To
MAJOR BARREL
Orientation
Longitudinal
Length of Lug, L
10,0000"
Height of Lug, B
5,0000"
Thickness of Lug, t
1,0000"
Hole Diameter, d
2,0000"
Load eccentricity, a1
1,0000"
Distance from Load to shell or pad, a2 2,5000" Weld size, tw
0,2500"
Width of Pad, Bp
6,0000"
Length of Pad, Lp
12,0000"
Pad Thickness, tp
0,5000"
Pad weld size, twp
0,2500"
Load angle normal to vessel, β
20,2800 °
Angular Position
0,00°
Load angle from vertical, υ
20,2800 °
1.1.1.123 Intermediate Values Load factor
1,5000
Vessel Weight (new, incl. Load Factor), W
34076 lb
Lug Weight (new), Wlug
24 lb
Distance from center of gravity to this lug, x1
83,8746"
Distance from center of gravity to second lug, x2 63,1254" Allowable stress, tensile, σt
20000 psi
Allowable stress, shear, σs
13500 psi
Allowable stress, bearing, σp
30000 psi
Allowable stress, bending, σb
22000 psi
Allowable stress, weld shear, τallowable
13500 psi
1.1.1.124 Summary Values Required Lift pin diameter, dreqd 0,8577" Required Lug thickness, treqd
Completed
0,2600"
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Lug Stress Ratio, σratio
0,08
Weld Shear Stress Ratio, τratio
0,31
Lug design
Acceptable
Local stresses (WRC 107)
Acceptable
1.1.1.125 Lift Forces Fr = force on vessel at lug Fr = [W / cos(υ1)] * (1 - x1 / (x1 + x2)) = (34076,270) / cos(20,2800) * (1 - 83,875/ (83,875 + 63,125)) = 15600 lbf where 'x1' is the distance between this lug and the center of gravity 'x2' is the distance between the second lift lug and the center of gravity 1.1.1.126 Lug Pin Diameter - Shear stress dreqd = (2*Fr / (π*σs))0.5 = (2*15600,2559 / (π*13500,0))0.5 = 0,8577" dreqd / d=
0,8577 / 2,0000
σ
Fr / A Fr / (2*(0.25*π*d2)) 15600,2559 / (2*(0.25*π*2,00002))=
= = =
=
0,43
Acceptable
2482,8577 psi
σ / σs = 2482,86 / 13500,00 = 0,18 1.1.1.127 Lug Thickness - Tensile stress treqd = Fr / ((L-d)*σt) = 15600,2559 / ((10,0000 - 2,0000)*20000,0)=
0,0975"
treqd / t=
0,0975 / 1,0000
0,10
σ
Fr / A Fr / ((L - d)*t) 15600,2559 / ((10,0000 - 2,0000)*1,0000) =
= = =
=
σ / σt = 1950,03 / 20000,00 1.1.1.128 Lug Thickness - Bearing stress treqd = Fv / (d*σp) = 15600,2559 / (2,0000*30000,0) = 0,2600"
=
Acceptable
1950,0320 psi 0,10
Acceptable
treqd / t
=
0,2600 / 1,0000
σ
= = =
Fv / Abearing Fv / (d*(t)) 15600,2559 / (2,0000 *(1,0000))=
7800,1279 psi
=
7800,13 / 30000,00
0,26
σ / σp
=0,26
Acceptable
=
Acceptable
Acceptable
1.1.1.129 Lug Plate Stress Lug stress tensile + bending during lift: Completed
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σ ratio
= =
Ften / (Aten*σt) + Mbend / (Zbend*σb) ≤ 1.0 (Fr * cos(α) ) / (t * L * σt) + (6 * abs(Fr * sin(α) * Hght - Fr * cos(α) * a1) ) / (t * L2 * σb) ≤ 1.0 15600*cos(20,3) / (1,0000*10,0000*20000,0) + 6*abs(15600*sin(20,3)*2,5000 = 15600*cos(20,3)*1,0000) / (1,0000*10,00002*22000,0) = 0,08 Acceptable 1.1.1.130 Weld Stress Weld stress, tensile, bending and shear during lift: Shear stress at lift angle 20,28°; lift force = 15600,2559 lbf Aweld =(0.707)*h*2*(L + t) =(0.707)*0,2500*2*(10,0000 + 1,0000) = 3,8885 in² τt
=Fr * cos(α) / Aweld =15600 * cos(20,3) / 3,8885
= 3763,1978 psi
τb
=M * c / I =3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * L * (3*t + L)) =3 * abs(15600 * sin(20,3) * 2,5000 - 15600 * cos(20,3) * 1,0000) / (22,9775)= 145,6101 psi
τs
=Fr * sin(α) / Aweld =15600 * sin(20,3) / 3,8885
= 1390,5560 psi
=sqr( (τt + τb)2 + τs2 ) / τallowable ≤ 1.0 =sqr ( (3763,1978 + 145,6101)2 + (1390,5560)2 ) / 13500,00 Pad Weld Stress, tensile, bending and shear during lift: Shear stress at lift angle 20,28°; lift force = 15600,2559 lbf Aweld =(0.707)*hp*2*(Lp + Bp) =(0.707)*0,2500*2*(12,0000 + 6,0000) τ ratio
τt
= 0,31
Acceptable
= 6,3630 in²
=Fr * cos(α) / Aweld =15600 * cos(20,3) / 6,3630
= 2299,7322 psi
τb
=M * c / I =3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * Lp * (3*Wp + Lp)) =3 * abs(15600 * sin(20,3) * 3,0000 - 15600 * cos(20,3) * 1,0000) / (63,6300)= 74,8862 psi
τs
=Fr * sin(α) / Aweld =15600 * sin(20,3) / 6,3630
= 849,7842 psi
=sqr( (τt + τb)2 + τs2 ) / τallowable ≤ 1.0 =sqr ( (2299,7322 + 74,8862)2 + (849,7842)2 ) / 13500,00
= 0,19
τ ratio
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1.1.1.131 WRC 107 Analysis 1.1.1.132 Geometry Height(radial):
5,0000" Pad Thickness: 0,5000"
Width (circumferential): 1,0000" Pad Width:
6,0000"
Length
10,0000" Pad Length:
12,0000"
Fillet Weld Size:
0,2500" Pad Weld Size: 0,2500"
Location Angle:
0,00°
Applied Loads Radial load: Pr = -14.633,20 lbf Circumferential moment: Mc = 0,00 lbf-in Circumferential shear: Vc = 0,00 lbf Longitudinal moment: ML = 30.854,73 lbf-in Longitudinal shear: VL = 5.407,18 lbf Torsion moment: Mt = 0,00 lbf-in Internal pressure: P = 0,000 psi Mean shell radius: Rm = 23,6560 in Shell yield stress: Sy = 65.000,00 psi Maximum stresses due to the applied loads at the lug edge (includes pressure) Rm/t =19,9125 C1 = 0,7500, C2 = 3,0000 in Note: Actual lug C1/C2 < 1/4, C1/C2 = 1/4 used as this is the minimum ratio covered by WRC 107. Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 18.480,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 2.484,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.
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Stresses at the lug edge per WRC Bulletin 107 Figure
value
Au
Al
Bu
Bl
Cu
Cl
Du
Dl
3C*
3,5135
0,0938
0
0
0
0
1.829
1.829
1.829
1.829
4C*
3,8176
0,0761
1.988
1.988
1.988
1.988
0
0
0
0
1C
0,2129
0,0558
0
0
0
0
13.244
13.244 13.244 13.244
2C-1
0,1768
0,0558
10.999
10.999 0 10.999 10.999
0
0
0
3A*
0,1706
0,0503
0
0
0
0
0
0
0
0
1A
0,1067
0,0654
0
0
0
0
0
0
0
0
3B*
1,2733
0,0799
-496
-496
496
496
0
0
0
0
1B-1
0,0588
0,0715
-4.563 4.563
4.563
-4.563
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
0
Total circumferential stress
7.928
-4.944
18.046
15.073 15.073 13.078 11.415 11.415
Primary membrane circumferential stress*
1.492
1.492
2.484
2.484
1.829
1.829
1.829
1.829
3C*
3,6687
0,0761
1.910
1.910
1.910
1.910
0
0
0
0
4C*
3,7303
0,0938
0
0
0
0
1.942
1.942
1.942
1.942
1C-1
0,1839
0,0793
11.440
11.440 0 11.440 11.440
0
0
0
2C
0,1402
0,0793
0
0
0
0
8.722
-8.722
8.722
-8.722
4A*
0,2297
0,0503
0
0
0
0
0
0
0
0
2A
0,0598
0,0911
0
0
0
0
0
0
0
0
4B*
0,3363
0,0799
-233
-233
233
233
0
0
0
0
2B-1
0,0870
0,0985
-4.897 4.897
4.897
-4.897
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
0
Total longitudinal stress
8.220
-4.866
18.480
10.664 -6.780 14.194
10.664 -6.780
Primary membrane longitudinal stress*
1.677
1.677
2.143
2.143
1.942
1.942
1.942
1.942
Shear from Mt
0
0
0
0
0
0
0
0
Circ shear from Vc
0
0
0
0
0
0
0
0
Long shear from VL
0
0
0
0
-379
-379
379
379
Total Shear stress
0
0
0
0
-379
-379
379
379
Combined stress (PL+Pb+Q)
8.220
-4.944
18.480
15.105 15.105 14.194 11.446 11.446
Note: * denotes primary stress. Maximum stresses due to the applied loads at the pad edge (includes pressure) Rm/t =34,3837 Completed
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C1 = 3,2500, C2 = 6,2500 in Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 18.986,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 5.412,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.
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Stresses at the pad edge per WRC Bulletin 107 Figure
value
Au
Al
Bu
Bl
Cu
Cl
Du
Dl
3C*
2,5429
0,2490
0
0
0
0
2.286
2.286
2.286
2.286
4C*
4,7378
0,2149
4.260
4.260
4.260
4.260
0
0
0
0
1C
0,0849
0,1759
0
0
0
0
15.748
15.748 15.748 15.748
2C-1
0,0512
0,1759
9.497
-9.497
9.497
-9.497
0
0
0
0
3A*
1,3452
0,1709
0
0
0
0
0
0
0
0
1A
0,0829
0,1856
0
0
0
0
0
0
0
0
3B*
3,5667
0,2125
-1.152 -1.152
1.152
1.152
0
0
0
0
1B-1
0,0291
0,1986
-2.423 2.423
2.423
-2.423
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
Total circumferential stress
10.182 -3.966
17.332 -6.508
18.034
18.034 13.462 13.462
Primary membrane circumferential stress*
3.108
3.108
5.412
5.412
2.286
2.286
2.286
2.286
3C*
3,0442
0,2149
2.737
2.737
2.737
2.737
0
0
0
0
4C*
4,3987
0,2490
0
0
0
0
3.955
3.955
3.955
3.955
1C-1
0,0689
0,2210
12.780
12.780 0 12.780 12.780
0
0
0
2C
0,0382
0,2210
0
0
0
0
7.086
-7.086
7.086
-7.086
4A*
2,3239
0,1709
0
0
0
0
0
0
0
0
2A
0,0384
0,2264
0
0
0
0
0
0
0
0
4B*
1,4019
0,2125
-655
-655
655
655
0
0
0
0
2B-1
0,0400
0,2350
-2.814 2.814
2.814
-2.814
0
0
0
0
Pressure stress*
0
0
0
0
0
0
0
Total longitudinal stress
12.048 -7.884
18.986
11.041 -3.131 12.202
11.041 -3.131
Primary membrane longitudinal stress*
2.082
2.082
3.392
3.392
3.955
3.955
3.955
3.955
Shear from Mt
0
0
0
0
0
0
0
0
Circ shear from Vc
0
0
0
0
0
0
0
0
Long shear from VL
0
0
0
0
-314
-314
314
314
Total Shear stress
0
0
0
0
-314
-314
314
314
Combined stress (PL+Pb+Q)
12.048 -7.884
18.986
18.048 18.048 12.202 13.472 13.472
0
0
Note: * denotes primary stress.
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NOZZLES ( FEA ) FINITE ELEMENT ANALYSIS Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
ANALYSIS SOFTWARE ANSYS 9.0 PREPARED BY : MECH.ENG.IHSAN AKGUN ( PRESSURE VESSELS ENGINEER )
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Tabular Results – KICKER NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:52:43 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
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Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness Fillet Along Shell
: : :
48.000 in. 0.688 in. 1.000 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 14.000 in. Thickness : 1.406 in. Length : 19.034 in. Nozzle Weld Length : 1.000 in. RePad Width : 6.000 in. RePad Thickness : 1.000 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 78.970 in. Distance from Bottom : 98.030 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1089.2 psi Vessel Pressure : 1089.2 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run.
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SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
: 0.000 0.000 1.000 : -1.000 0.000 0.000
Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial)
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4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion) 7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
Solution Data Maximum Solution Row Size = 972 Number of Nodes = 2028 Number of Elements = 668 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 570809133121069. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 17771940538827. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 29191. 29191. 0. 0. 0. 0. 29191.
FY 0. 0. 0. 0. 0. 0. 0.
Completed
FZ 1914718. 1914718. -2164368. 0. 0. 0. 1914718.
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Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 570809133121069. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 2 69926728300438. 1-to-10% 201 18847533543418. .1-to- 1% 410 1428818046465. .01-to-.1% 300 251646588286. .001-to-.01% 56 25768600257. .0001-TO-.001% 11198 110499319.
OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 8 16918108624334. 70-to-90% 31 13930091755029. 50-to-70% 45 10316248571499. 30-to-50% 93 7060982396331. 10-to-30% 516 2980979054368. 1-to-10% 2391 614741686375. .1-to- 1% 8469 58244264347. .01-to-.1% 7898 7931343623. .001-to-.01% 2985 765396589. .0001-TO-.001% 531298 5127749.
ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
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ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,913 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 25%
Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,824 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 96%
Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 8,172 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 31%
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 42,248 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 43%
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 38,192 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 39%
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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 43,493 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
22%
Branch at Junction Pl+Pb+Q 39,358 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
76%
Branch Transition Pl+Pb+Q 9,212 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
17%
Pad Outer Edge Weld Pl+Pb+Q 58,419 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
29%
Header Outside Pad Area Pl+Pb+Q 48,561 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
24%
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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 29,358 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 22215.8 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 26,567 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 30187.7 4% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 4,606 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 39,433 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 8438.8 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 24,280 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 39793.5 4% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Completed
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Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.279 1.237 1.894 1.324 1.171 1.962 0.494 0.965 0.988 1.956 2.388 2.897 1.038 1.112 1.538
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 6.380 Inplane 7.825 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 7.825 Inplane 7.825 Outplane 7.825 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.829 Inplane 7.825 Outplane 3.829 Torsional
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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2125186. 164900. 247350. Inplane Moment (in. lb.) 6126511. 336141. 713062. Outplane Moment (in. lb.) 31475014. 2516291. 5337860. Torsional Moment (in. lb.) 3564401. 276573. 414859. Pressure (psi ) 1419.60 1089.15 1089.15
PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2145783. 23027. 34541. Inplane Moment (in. lb.) 6285948. 47700. 101186. Outplane Moment (in. lb.) 16113937. 280636. 595319. Torsional Moment (in. lb.) 4210393. 45184. 67776. Pressure (psi ) 1125.38 1089.15 1089.15
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 14.000 in. Wall Thickness = 1.406 in.
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The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness
Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Tabular Results – SAFETY VALVE NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:58:43 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness : Fillet Along Shell :
: 48.000 in. 0.688 in. 0.500 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 1.315 in. Thickness : 0.240 in. Length : 8.224 in. Nozzle Weld Length : 0.500 in. RePad Width : 4.000 in. RePad Thickness : 0.688 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 67.160 in. Distance from Bottom : 109.840 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Completed
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Yield Strength (Amb) : Yield Strength (Hot) : Elastic Modulus (Amb) : Poissons Ratio : Weight Density :
35000.0 psi 32900.0 psi 29400000.0 psi 0.300 0.283 lb./cu.in. (NOT USED)
Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.3 psi Vessel Pressure : 1088.3 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
Completed
: 0.000 0.000 1.000 : 0.000 1.000 0.000
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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)
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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
Solution Data Maximum Solution Row Size = 1554 Number of Nodes = 9444 Number of Elements = 3140 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 4295943931706271. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 154868293220201. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 0. 0. 0. 0. 0. 0. 0.
FY -690. -690. 0. 0. 0. 0. -690.
FZ 1913428. 1913428. -3260. 0. 0. 0. 1913428.
Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 4295943931706271. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 169 72613018143028. .1-to- 1% 505 20362590987501. .01-to-.1% 11 3954054177645. .001-to-.01% 360 164677717581. .0001-TO-.001% 55618 59830311.
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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 154868293220201. 70-to-90% 0 0. 50-to-70% 8 83061024980278. 30-to-50% 26 58496018324935. 10-to-30% 365 25187989629765. 1-to-10% 2069 5031908829842. .1-to- 1% 2729 642071029000. .01-to-.1% 3695 58547066491. .001-to-.01% 3130 5784637537. .0001-TO-.001% 2601802 4005482.
ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 22,045 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 22%
Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 16,388 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 63%
Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,576 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 10%
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 40,422 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 41%
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 38,009 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 38%
Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,065 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 11%
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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 54,202 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
27%
Branch at Junction Pl+Pb+Q 32,728 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
63%
Branch Transition Pl+Pb+Q 3,454 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
6%
Pad Outer Edge Weld Pl+Pb+Q 58,577 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
30%
Header Outside Pad Area Pl+Pb+Q 42,513 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
21%
Branch removed from Junction Pl+Pb+Q 4,820 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
9%
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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 36,586 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 10898.3 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 22,091 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 55243.8 3% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 1,727 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 39,539 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 8371.5 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 21,256 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 66876.1 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
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Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,410 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.480 1.223 2.192 1.489 1.206 2.206 0.278 0.424 0.428 1.997 2.147 2.959 1.042 1.065 1.543
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.354 Inplane 1.689 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 1.689 Inplane 1.689 Outplane 1.689 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 4.842 Inplane 1.689 Outplane 4.842 Torsional
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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 31792. 3837. 5755. Inplane Moment (in. lb.) 7421. 633. 1343. Outplane Moment (in. lb.) 85193. 14656. 31091. Torsional Moment (in. lb.) 3970. 479. 719. Pressure (psi ) 1705.85 1088.28 1088.28
PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 35510. 4274. 6411. Inplane Moment (in. lb.) 8267. 704. 1493. Outplane Moment (in. lb.) 43035. 6163. 13075. Torsional Moment (in. lb.) 4475. 539. 808. Pressure (psi ) 1703.36 1088.28 1088.28
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 1.315 in. Wall Thickness = 0.240 in.
The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness
Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Tabular Results – PRESSURE INDICATOR NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:56:43 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness : Fillet Along Shell :
: 48.000 in. 0.688 in. 1.000 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 2.375 in. Thickness : 0.436 in. Length : 8.224 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.100 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 49.450 in. Distance from Bottom : 127.550 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Completed
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Yield Strength (Amb) : Yield Strength (Hot) : Elastic Modulus (Amb) : Poissons Ratio : Weight Density :
35000.0 psi 32900.0 psi 29400000.0 psi 0.300 0.283 lb./cu.in. (NOT USED)
Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.3 psi Vessel Pressure : 1088.3 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
Completed
: 0.000 0.000 1.000 : 0.000 1.000 0.000
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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)
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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
Solution Data Maximum Solution Row Size = 1374 Number of Nodes = 5388 Number of Elements = 1788 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 2260959841002897. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 73008354295878. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 0. 0. 0. 0. 0. 0. 0.
FY -1920. -1920. 0. 0. 0. 0. -1920.
FZ 1913380. 1913380. -19315. 0. 0. 0. 1913380.
Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 2260959841002897. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 230 40789786900638. .1-to- 1% 284 11204893314808. .01-to-.1% 305 387555834680. .001-to-.01% 56 212116879908. .0001-TO-.001% 31452 124814867.
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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 73008354295878. 70-to-90% 2 56021239410099. 50-to-70% 14 44699733559599. 30-to-50% 69 26999937560756. 10-to-30% 391 12349623514344. 1-to-10% 2168 2451306080096. .1-to- 1% 2966 257418927152. .01-to-.1% 3902 27272436386. .001-to-.01% 7093 2346311195. .0001-TO-.001% 1469682 4606847.
ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 16,573 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 16%
Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 13,842 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 53%
Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,655 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 10%
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 43,451 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 44%
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 37,954 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 38%
Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,153 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 12%
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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 45,267 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
23%
Branch at Junction Pl+Pb+Q 24,945 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
48%
Branch Transition Pl+Pb+Q 4,074 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
7%
Pad Outer Edge Weld Pl+Pb+Q 58,655 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
30%
Header Outside Pad Area Pl+Pb+Q 43,002 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
22%
Branch removed from Junction Pl+Pb+Q 5,490 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
10%
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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 30,555 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 19649.2 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 16,838 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 172851.5 2% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,037 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 39,592 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 8338.4 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 21,501 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 63183.1 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Completed
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Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,745 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.608 1.251 2.383 1.630 1.234 2.416 0.298 0.488 0.496 2.292 2.150 3.395 1.043 1.145 1.545
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.939 Inplane 2.374 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 2.374 Inplane 2.374 Outplane 2.374 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.745 Inplane 2.374 Outplane 3.745 Torsional
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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 151117. 25878. 38817. Inplane Moment (in. lb.) 63651. 7707. 16350. Outplane Moment (in. lb.) 434539. 79965. 169632. Torsional Moment (in. lb.) 31216. 5346. 8018. Pressure (psi ) 2238.04 1088.28 1088.28
PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 161974. 24856. 37284. Inplane Moment (in. lb.) 67811. 7358. 15609. Outplane Moment (in. lb.) 220458. 31735. 67319. Torsional Moment (in. lb.) 34756. 5333. 8000. Pressure (psi ) 2016.70 1088.28 1088.28
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 2.375 in. Wall Thickness = 0.436 in.
The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness
Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Tabular Results – VENT NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:55:26 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness : Fillet Along Shell :
: 48.000 in. 0.688 in. 1.000 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 2.375 in. Thickness : 0.436 in. Length : 8.224 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.100 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 31.740 in. Distance from Bottom : 145.260 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Completed
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Yield Strength (Amb) : Yield Strength (Hot) : Elastic Modulus (Amb) : Poissons Ratio : Weight Density :
35000.0 psi 32900.0 psi 29400000.0 psi 0.300 0.283 lb./cu.in. (NOT USED)
Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.3 psi Vessel Pressure : 1088.3 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
Completed
: 0.000 0.000 1.000 : 0.000 1.000 0.000
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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)
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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
Solution Data Maximum Solution Row Size = 1176 Number of Nodes = 5298 Number of Elements = 1758 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 2260959840151130. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 73008354252872. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 0. 0. 0. 0. 0. 0. 0.
FY -1920. -1920. 0. 0. 0. 0. -1920.
FZ 1913380. 1913380. -19315. 0. 0. 0. 1913380.
Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 2260959840151130. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 230 40789785583809. .1-to- 1% 284 11204892004910. .01-to-.1% 305 387555834680. .001-to-.01% 56 212116879908. .0001-TO-.001% 30912 126271357.
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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 73008354252872. 70-to-90% 2 56021239344498. 50-to-70% 14 44699733493634. 30-to-50% 69 26999937240812. 10-to-30% 391 12349622944205. 1-to-10% 2168 2451305982331. .1-to- 1% 2966 257418924999. .01-to-.1% 3902 27272436376. .001-to-.01% 7066 2350575336. .0001-TO-.001% 1444481 4629580.
ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 16,523 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 16%
Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 13,720 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 53%
Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,651 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 10%
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 43,445 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 44%
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 37,981 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 38%
Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,141 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 12%
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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 45,003 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
23%
Branch at Junction Pl+Pb+Q 24,783 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
48%
Branch Transition Pl+Pb+Q 4,051 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
7%
Pad Outer Edge Weld Pl+Pb+Q 59,511 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
30%
Header Outside Pad Area Pl+Pb+Q 42,896 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
21%
Branch removed from Junction Pl+Pb+Q 5,438 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
10%
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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 30,377 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 20006.4 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 16,728 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 176973.2 2% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,026 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 40,170 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 7987.3 7% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 21,448 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 63962.8 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
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Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,719 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.617 1.254 2.396 1.639 1.237 2.429 0.298 0.489 0.496 2.302 2.151 3.411 1.058 1.144 1.568
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.939 Inplane 2.374 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 2.374 Inplane 2.374 Outplane 2.374 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.745 Inplane 2.374 Outplane 3.745 Torsional
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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 150769. 25978. 38967. Inplane Moment (in. lb.) 63500. 7737. 16412. Outplane Moment (in. lb.) 434417. 79869. 169427. Torsional Moment (in. lb.) 31219. 5379. 8069. Pressure (psi ) 2252.73 1088.28 1088.28
PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 161555. 25047. 37570. Inplane Moment (in. lb.) 67631. 7414. 15728. Outplane Moment (in. lb.) 220353. 31705. 67257. Torsional Moment (in. lb.) 34732. 5385. 8077. Pressure (psi ) 2034.56 1088.28 1088.28
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 2.375 in. Wall Thickness = 0.436 in.
The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness
Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Tabular Results – DREYN NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:53:32 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness : Fillet Along Shell :
: 48.000 in. 0.688 in. 1.000 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 4.500 in. Thickness : 0.674 in. Length : 8.224 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.200 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 14.410 in. Distance from Bottom : 162.590 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Completed
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Yield Strength (Amb) : Yield Strength (Hot) : Elastic Modulus (Amb) : Poissons Ratio : Weight Density :
35000.0 psi 32900.0 psi 29400000.0 psi 0.300 0.283 lb./cu.in. (NOT USED)
Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1090.0 psi Vessel Pressure : 1090.0 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
Completed
: 0.000 0.000 1.000 : 0.000 -1.000 0.000
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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)
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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
Solution Data Maximum Solution Row Size = 870 Number of Nodes = 3078 Number of Elements = 1018 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 1067930861985906. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 23954670027870. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 0. 0. 0. 0. 0. 0. 0.
FY 4508. 4508. 0. 0. 0. 0. 4508.
FZ 1916348. 1916348. -107195. 0. 0. 0. 1916348.
Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 1067930861985906. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 217 25770767440426. .1-to- 1% 162 6738753807609. .01-to-.1% 360 417757334730. .001-to-.01% 220 23442179964. .0001-TO-.001% 17508 106026062.
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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 4 23820449237183. 70-to-90% 26 18754250496661. 50-to-70% 47 13966185990012. 30-to-50% 154 9172528380065. 10-to-30% 642 4009353278465. 1-to-10% 2024 949099084778. .1-to- 1% 3434 89909508913. .01-to-.1% 7690 7525601847. .001-to-.01% 7535 1048777024. .0001-TO-.001% 823413 3827609.
ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 18,168 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 18%
Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 14,361 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 55%
Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 4,317 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 16%
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 44,297 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 45%
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 39,872 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 40%
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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 46,181 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
23%
Branch at Junction Pl+Pb+Q 27,251 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
53%
Branch Transition Pl+Pb+Q 6,875 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
13%
Pad Outer Edge Weld Pl+Pb+Q 63,783 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
32%
Header Outside Pad Area Pl+Pb+Q 63,313 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
32%
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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 31,172 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 18477.3 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 18,394 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 125706.0 3% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 3,438 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 43,053 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 6502.6 7% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 31,657 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 17621.2 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Completed
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Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.638 1.271 2.427 1.675 1.254 2.482 0.375 0.594 0.751 2.403 2.187 3.560 1.132 1.165 1.677
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 2.997 Inplane 3.669 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 3.669 Inplane 3.669 Outplane 3.669 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.745 Inplane 3.669 Outplane 3.745 Torsional
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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 424782. 66379. 99568. Inplane Moment (in. lb.) 358275. 39588. 83979. Outplane Moment (in. lb.) 1764885. 322184. 683456. Torsional Moment (in. lb.) 215483. 33673. 50509. Pressure (psi ) 2051.99 1090.02 1090.02
PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 438902. 64391. 96587. Inplane Moment (in. lb.) 370939. 38481. 81630. Outplane Moment (in. lb.) 1115420. 155394. 329640. Torsional Moment (in. lb.) 195135. 28628. 42942. Pressure (psi ) 1946.91 1090.02 1090.02
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 4.500 in. Wall Thickness = 0.674 in.
The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness
Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Tabular Results – KICKER NOZZLE 2 Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:51:30 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness : Fillet Along Shell :
: 48.000 in. 0.688 in. 1.000 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 14.000 in. Thickness : 1.406 in. Length : 19.034 in. Nozzle Weld Length : 1.000 in. RePad Width : 6.000 in. RePad Thickness : 1.000 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 138.024 in. Distance from Bottom : 38.976 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Completed
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Yield Strength (Amb) : Yield Strength (Hot) : Elastic Modulus (Amb) : Poissons Ratio : Weight Density :
35000.0 psi 32900.0 psi 29400000.0 psi 0.300 0.283 lb./cu.in. (NOT USED)
Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1089.2 psi Vessel Pressure : 1089.2 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
: 0.000 0.000 1.000 : -1.000 0.000 0.000
Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed.
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THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion) 7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
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Solution Data Maximum Solution Row Size = 864 Number of Nodes = 2028 Number of Elements = 668 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 570809133119139. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 17771940538827. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 29191. 29191. 0. 0. 0. 0. 29191.
FY 0. 0. 0. 0. 0. 0. 0.
FZ 1914718. 1914718. -2164368. 0. 0. 0. 1914718.
Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 570809133119139. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 2 69926728300522. 1-to-10% 201 18847557330940. .1-to- 1% 410 1428819278905. .01-to-.1% 300 251646588286. .001-to-.01% 56 25768600257. .0001-TO-.001% 11198 110503057.
OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 8 16918108629091. 70-to-90% 31 13930091981812. 50-to-70% 45 10316249594375. 30-to-50% 93 7060985608352. 10-to-30% 516 2980979810043. 1-to-10% 2391 614741859315. .1-to- 1% 8469 58244265101. .01-to-.1% 7898 7931343623. .001-to-.01% 3033 758503730. .0001-TO-.001% 531125 5104309.
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ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,632 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 25%
Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,487 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 95%
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Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 7,803 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 30%
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 42,347 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 43%
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 38,392 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 39%
Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 42,293 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
21%
Branch at Junction Pl+Pb+Q 38,759 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
75%
Branch Transition Pl+Pb+Q 9,007 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Plot Reference: psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
17%
Pad Outer Edge Weld Completed
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Pl+Pb+Q 63,431 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
32%
Header Outside Pad Area Pl+Pb+Q 48,924 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Plot Reference: psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
25%
Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 28,548 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 24208.0 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 26,163 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 31643.1 4% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 4,504 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
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Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 42,816 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 6610.0 7% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 24,462 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 38892.4 4% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.306 1.249 1.935 1.351 1.183 2.002 0.495 0.966 0.990 1.971 2.393 2.920 1.127 1.115 1.670
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in.
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B31.3 Peak Stress Sif .... 0.000 Axial 6.380 Inplane 7.825 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 7.825 Inplane 7.825 Outplane 7.825 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.829 Inplane 7.825 Outplane 3.829 Torsional
Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2101248. 171222. 256833. Inplane Moment (in. lb.) 6055901. 348936. 740206. Outplane Moment (in. lb.) 31427594. 2597257. 5509615. Torsional Moment (in. lb.) 3548691. 289168. 433753. Pressure (psi ) 1441.55 1089.15 1089.15
PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2122541. 32086. 48129. Inplane Moment (in. lb.) 6216399. 66449. 140959. Outplane Moment (in. lb.) 16106408. 389178. 825571. Torsional Moment (in. lb.) 4191913. 63369. 95053. Pressure (psi ) 1140.89 1089.15 1089.15
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. Completed
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4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 14.000 in. Wall Thickness = 1.406 in.
The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness
Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Tabular Results – PIG SIGNAL NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2. Analysis Time Stamp: Sat Sep 23 21:51:31 2006.
Model Notes Load Case Report Solution Data ASME Code Stress Output Plots ASME Overstressed Areas Highest Primary Stress Ratios Highest Secondary Stress Ratios Highest Fatigue Stress Ratios Stress Intensification Factors Allowable Loads Flexibilities Graphical Results
Model Notes Input Echo: Model Type
: Cylindrical Shell
Parent Outside Diameter Thickness : Fillet Along Shell :
: 40.000 in. 0.688 in. 1.000 in.
Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 2.375 in. Thickness : 0.436 in. Length : 7.529 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.000 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 55.000 in. Distance from Bottom : 55.000 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Completed
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Yield Strength (Amb) : Yield Strength (Hot) : Elastic Modulus (Amb) : Poissons Ratio : Weight Density :
35000.0 psi 32900.0 psi 29400000.0 psi 0.300 0.283 lb./cu.in. (NOT USED)
Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.6 psi Vessel Pressure : 1088.6 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector Nozzle Orientation Vector
: 0.000 0.000 1.000 : 0.000 1.000 0.000
Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed.
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THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating
(Fatigue Calc Performed)
Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion) 7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1
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Solution Data Maximum Solution Row Size = 1188 Number of Nodes = 3738 Number of Elements = 1238 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 1094857341535433. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 31822879340700. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # 1 2 3 4 5 6 7
FX 0. 0. 0. 0. 0. 0. 0.
FY -1552. -1552. 0. 0. 0. 0. -1552.
FZ 1321342. 1321342. -19315. 0. 0. 0. 1321342.
Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Percentile Coefficients
Average Stiffness
90-to-100% 1 1094857341535433. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 226 20637178549270. .1-to- 1% 221 6648541463801. .01-to-.1% 360 223528405812. .001-to-.01% 0 0. .0001-TO-.001% 21620 117408155.
OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 31822879340700. 70-to-90% 4 25732179681041. 50-to-70% 16 18294382104461. 30-to-50% 77 11990350168488. 10-to-30% 495 5385767706974. 1-to-10% 2214 1138166925784. .1-to- 1% 3054 96904740640. .01-to-.1% 3274 11506959077. .001-to-.01% 9109 1109032375. .0001-TO-.001% 1009012 3797905.
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ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 14,167 97,500 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 14% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1
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Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 11,360 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 44% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1
Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,629 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 10% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1
Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 35,684 97,500 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 36% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1
Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 31,577 97,500 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 32% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1
Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,018 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 11% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1
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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 37,238 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 19% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
Branch at Junction Pl+Pb+Q 21,043 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 41% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
Branch Transition Pl+Pb+Q 3,913 psi 7%
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q 49,869 psi
3(Smavg) Primary+Secondary (Outer) Load Case 2 195,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 25% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2
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Header Outside Pad Area Pl+Pb+Q 36,054 psi
3(Smavg) Primary+Secondary (Inner) Load Case 2 195,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 18% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
Branch removed from Junction Pl+Pb+Q 5,045 psi 9%
3(Smavg) Primary+Secondary (Inner) Load Case 2 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2
Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 25,136 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 35781.1 4% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 14,204 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 361481.8 2% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
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Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 1,956 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 33,662 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 14588.1 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2
Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 18,027 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 135174.8 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,523 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2
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Stress Intensification Factors Branch/Nozzle Sif Summary
Axial : Inplane : Outplane: Torsion : Pressure:
Peak Primary Secondary 1.596 1.249 2.365 1.620 1.228 2.399 0.341 0.572 0.580 2.276 2.135 3.371 1.064 1.128 1.576
The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : Pipe Thk: Z approx: Z exact :
40.000 in. 0.688 in. 835.080 cu.in. 820.968 cu.in.
B31.3 Peak Stress Sif .... 0.000 Axial 1.767 Inplane 2.145 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 2.145 Inplane 2.145 Outplane 2.145 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.384 Inplane 2.145 Outplane 3.384 Torsional
Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 150888. 29665. 44497. Inplane Moment (in. lb.) 63697. 8855. 18784. Outplane Moment (in. lb.) 371554. 71402. 151467. Torsional Moment (in. lb.) 31664. 6225. 9338. Pressure (psi ) 2653.77 1088.57 1088.57
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PRIMARY Load Type:
Maximum Conservative Realistic Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 156944. 29146. 43718. Inplane Moment (in. lb.) 65798. 8640. 18329. Outplane Moment (in. lb.) 188188. 29991. 63620. Torsional Moment (in. lb.) 34211. 6353. 9530. Pressure (psi ) 2457.95 1088.57 1088.57
NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.
Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiffnesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 2.375 in. Wall Thickness = 0.436 in.
The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness Completed
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Finite Element Model
Finite Element Model
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 1 2) Qb < 3(Smh) (SUS Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7
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Index of Revisions Rev .
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Remark, kind of revision Statu s IFI FOR APPROVED
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