341-v90
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Ingenieria Strycon
Cra 13 # 35 - 43
COMPRESS Pressure Vessel Design Calculations
Item: Separador PrimarioVessel No: V-90Customer: Plant process Equipment INC.
Contract: -Designer: Carlos Alvarez
Date: 13/02/2013Location: Servicios Auxiliares y varios - Proyecto Star
Purchaser: PACIFIC RUBIALESVessel Name: Comp1.CW7
Service: Separador PrimarioTag Number: 341-V-90
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Deficiencies Summary
No deficiencies found.
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Nozzle Schedule
Nozzlemark
Service SizeMaterials
Nozzle Impact Norm FineGrain Pad Impact Norm Fine
Grain Flange
N1 Nozzle #1 NPS 8 Sch 80 (XS) SA-106 B Smlspipe No No No N/A N/A N/A N/A WN A105 Class
150
N10 Nozzle#10 NPS 1 Sch 80 (XS) SA-106 A Smls
pipe No No No N/A N/A N/A N/A WN A105 Class150
N11 Nozzle#11 NPS 1 Sch 80 (XS) SA-106 B Smls
pipe No No No N/A N/A N/A N/A WN A105 Class150
N12 Nozzle#12
NPS 0,75 Class 6000 -threaded SA-105 No No No N/A N/A N/A N/A N/A
N13 Nozzle#13 NPS 2 Sch 80 (XS) SA-106 B Smls
pipe No No No N/A N/A N/A N/A WN A105 Class150
N14 Nozzle#14 NPS 8 Sch 80 (XS) SA-106 B Smls
pipe No No No N/A N/A N/A N/A WN A105 Class150
N2 Nozzle #2 NPS 6 Sch 80 (XS) SA-106 B Smlspipe No No No N/A N/A N/A N/A WN A105 Class
150
N3 Nozzle #3 NPS 4 Sch 80 (XS) SA-106 B Smlspipe No No No N/A N/A N/A N/A WN A105 Class
150
N4 Nozzle #4 NPS 2 Sch 80 (XS) SA-106 B Smlspipe No No No N/A N/A N/A N/A WN A105 Class
150
N5 Nozzle #5 NPS 18 Sch 1,000 SA-106 B Smlspipe No No No N/A N/A N/A N/A WN A105 Class
150
N6 Nozzle #6 NPS 0,375 Class 6000 -threaded SA-105 No No No N/A N/A N/A N/A N/A
N7 Nozzle #7 NPS 0,5 Class 6000 -threaded
SA-106 B Smlspipe No No No N/A N/A N/A N/A N/A
N8 Nozzle #8 NPS 0,75 Class 6000 -threaded
SA-106 B Smlspipe No No No N/A N/A N/A N/A N/A
N9 Nozzle #9 NPS 0,75 Class 6000 -threaded
SA-106 B Smlspipe No No No N/A N/A N/A N/A N/A
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Nozzle Summary
Nozzlemark
OD(in)
tn
(in)Req t
n(in)
A1? A2?Shell Reinforcement
Pad Corr(in)
Aa/A
r(%)
Nom t(in)
Design t(in)
User t(in)
Width(in)
tpad(in)
N1 8,625 0,5 0,322 Yes Yes 0,487* 0,3905 N/A N/A 0 100,0
N10 1,315 0,179 0,133 Yes Yes 0,5 N/A N/A N/A 0 Exempt
N11 1,315 0,179 0,133 Yes Yes 0,5 N/A N/A N/A 0 Exempt
N12 1,75 0,35 0,0625 Yes Yes 0,487* N/A N/A N/A 0 Exempt
N13 2,375 0,218 0,154 Yes Yes 0,487* N/A N/A N/A 0 Exempt
N14 8,625 0,5 0,322 Yes Yes 0,5 0,3666 N/A N/A 0 100,0
N2 6,625 0,432 0,28 Yes Yes 0,5 0,3198 N/A N/A 0 100,0
N3 4,5 0,337 0,237 Yes Yes 0,5 0,3193 N/A N/A 0 100,0
N4 2,375 0,218 0,154 Yes Yes 0,5 N/A N/A N/A 0 Exempt
N5 18 1 0,1206 Yes Yes 0,487* 0,3928 N/A N/A 0 100,0
N6 1,25 0,2875 0,0625 Yes Yes 0,5 N/A N/A N/A 0 Exempt
N7 1,5 0,33 0,0714 Yes Yes 0,5 N/A N/A N/A 0 Exempt
N8 1,75 0,35 0,0714 Yes Yes 0,5 N/A N/A N/A 0 Exempt
N9 1,75 0,35 0,0714 Yes Yes 0,5 N/A N/A N/A 0 Exempt
tn: Nozzle thicknessReq tn: Nozzle thickness required per UG-45/UG-16Nom t: Vessel wall thicknessDesign t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37User t: Local vessel wall thickness (near opening)Aa: Area available per UG-37, governing conditionAr: Area required per UG-37, governing conditionCorr: Corrosion allowance on nozzle wall* Head minimum thickness after forming
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Pressure Summary
Pressure Summary for Chamber bounded by Ellipsoidal Head #1 and Ellipsoidal Head #2
IdentifierP
Design( psi)
T
Design( °F)
MAWP( psi)
MAP( psi)
MDMT( °F)
MDMTExemption
ImpactTested
Ellipsoidal Head #2 150 300 252,58 252,58 -20 Note 1 No
Straight Flange on Ellipsoidal Head #2 150 300 160,77 160,77 -20 Note 2 No
Cylinder #1 150 300 257,73 257,73 -44,5 Note 3 No
Straight Flange on Ellipsoidal Head #1 150 300 160,77 160,77 -20 Note 2 No
Ellipsoidal Head #1 150 300 252,58 252,58 -20 Note 4 No
Saddle #2 150 300 160,77 N/A N/A N/A N/A
Nozzle #1 (N1) 150 300 222,47 222,47 -55 Note 5 No
Nozzle #10 (N10) 150 300 230 257,73 -55 Note 5 No
Nozzle #11 (N11) 150 300 230 257,73 -55 Note 5 No
Nozzle #12 (N12) 150 300 252,58 252,58 -155 Note 6 No
Nozzle #13 (N13) 150 300 193,98 193,98 -55 Note 5 No
Nozzle #14 (N14) 150 300 188,68 188,68 -55 Note 5 No
Nozzle #2 (N2) 150 300 164,51 164,51 -55 Note 5 No
Nozzle #3 (N3) 150 300 164,27 164,27 -55 Note 5 No
Nozzle #4 (N4) 150 300 230 257,73 -55 Note 5 No
Nozzle #5 (N5) 150 300 223,83 223,83 -51,05 Note 7 No
Nozzle #6 (N6) 150 300 257,73 257,73 -155 Note 8 No
Nozzle #7 (N7) 150 300 257,73 257,73 -155 Note 9 No
Nozzle #8 (N8) 150 300 257,73 257,73 -155 Note 10 No
Nozzle #9 (N9) 150 300 257,73 257,73 -155 Note 10 No
Chamber design MDMT is -20 °FChamber rated MDMT is -20 °F @ 160,77 psi
Chamber MAWP hot & corroded is 160,77 psi @ 300 °F
Chamber MAP cold & new is 160,77 psi @ 70 °F
This pressure chamber is not designed for external pressure.
Notes for MDMT Rating:
Note # Exemption Details
1. Straight Flange governs MDMT
2. Material is impact test exempt per UG-20(f) UCS-66 governing thickness = 0,3125 in
3. Material impact test exemption temperature from Fig UCS-66 Curve B = -7 °FFig UCS-66.1 MDMT reduction = 37,5 °F, (coincident ratio = 0,625) UCS-66 governing thickness = 0,5 in
4. Straight Flange governs MDMT
5. Flange rating governs: UCS-66(b)(1)(b)
6. Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,01212).
7. Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -8,25 °FFig UCS-66.1 MDMT reduction = 42,8 °F, (coincident ratio = 0,5801) UCS-66 governing thickness = 0,487 in.
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8. Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,00948).
9. Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,01375).
10. Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,01621).
Design notes are available on the Settings Summary page.
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Revision History
No. Date Operator Notes
0 2/12/2013 carlosalvarez New vessel created ASME Section VIII Division 1 [COMPRESS Build 7110]
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Settings Summary
COMPRESS Build 7110
Units: U.S. Customary
Datum Line Location: 0,00" from right seam
Design
ASME Section VIII Division 1, 2010 Edition
Design or Rating: Get Thickness from PressureMinimum thickness: 0,0625" per UG-16(b)Design for cold shut down only: NoDesign for lethal service (full radiography required): NoDesign nozzles for: Design P, find nozzle MAWP and MAPCorrosion weight loss: 100% of theoretical lossUG-23 Stress Increase: 1,20Skirt/legs stress increase: 1,0Minimum nozzle projection: 6"Juncture calculations for α > 30 only: YesPreheat P-No 1 Materials > 1,25" and <= 1,50" thick: NoUG-37(a) shell tr calculation considers longitudinal stress: NoButt welds are tapered per Figure UCS-66.3(a).
Hydro/Pneumatic Test
Shop Hydrotest Pressure: 1,3 times vesselMAWP
Test liquid specific gravity: 1,00Maximum stress during test: 90% of yield
Required Marking - UG-116
UG-116(e) Radiography: RT1UG-116(f) Postweld heat treatment: None
Code Cases\Interpretations
Use Code Case 2547: NoApply interpretation VIII-1-83-66: YesApply interpretation VIII-1-86-175: YesApply interpretation VIII-1-83-115: YesApply interpretation VIII-1-01-37: YesNo UCS-66.1 MDMT reduction: NoNo UCS-68(c) MDMT reduction: NoDisallow UG-20(f) exemptions: No
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UG-22 Loadings
UG-22(a) Internal or External Design Pressure : YesUG-22(b) Weight of the vessel and normal contents under operating or test conditions: YesUG-22(c) Superimposed static reactions from weight of attached equipment (external loads): NoUG-22(d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: YesUG-22(f) Wind reactions: NoUG-22(f) Seismic reactions: NoUG-22(j) Test pressure and coincident static head acting during the test: NoNote: UG-22(b),(c) and (f) loads only considered when supports are present.
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Thickness Summary
ComponentIdentifier
Material Diameter(in)
Length(in)
Nominal t(in)
Design t(in)
Total Corrosion(in)
JointE
Load
Ellipsoidal Head #2 SA-516 70 78 OD 19,7435 0,487* 0,2906 0 1,00 Internal
Straight Flange on Ellipsoidal Head #2 SA-516 70 78 OD 2 0,3125 0,2917 0 1,00 Internal
Cylinder #1 SA-516 70 78 OD 240 0,5 0,2917 0 1,00 Internal
Straight Flange on Ellipsoidal Head #1 SA-516 70 78 OD 2 0,3125 0,2917 0 1,00 Internal
Ellipsoidal Head #1 SA-516 70 78 OD 19,7435 0,487* 0,2906 0 1,00 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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Weight Summary
ComponentWeight ( lb) Contributed by Vessel Elements
MetalNew*
Metal
Corroded*Insulation &
Supports Lining Piping+ Liquid
OperatingLiquid
TestLiquid
Ellipsoidal Head #2 964 964 0 0 0 0 2.505,1
Cylinder #1 8.250,8 8.250,8 0 0 0 0 40.353,7
Ellipsoidal Head #1 992 992 0 0 0 0 2.505,3
Saddle #2 1.052 1.052 0 0 0 0 0
TOTAL: 11.258,9 11.258,9 0 0 0 0 45.364,1
* Shells with attached nozzles have weight reduced by material cut out for opening.
Component
Weight ( lb) Contributed by Attachments
Body Flanges Nozzles &Flanges Packed
BedsTrays &
SupportsRings &
ClipsVerticalLoads
New Corroded New Corroded
Ellipsoidal Head #2 0 0 483,3 483,3 0 0 0 0
Cylinder #1 0 0 188,2 188,2 0 0 0 0
Ellipsoidal Head #1 0 0 62,6 62,6 0 0 0 0
TOTAL: 0 0 734,2 734,2 0 0 0 0
Vessel operating weight, Corroded: 11.993 lbVessel operating weight, New: 11.993 lbVessel empty weight, Corroded: 11.993 lbVessel empty weight, New: 11.993 lbVessel test weight, New: 57.357 lb
Vessel center of gravity location - from datum - lift condition
Vessel Lift Weight, New: 11.993 lbCenter of Gravity: 124,242"
Vessel Capacity
Vessel Capacity** (New): 5.437 US galVessel Capacity** (Corroded): 5.437 US gal**The vessel capacity does not include volume of nozzle, piping or other attachments.
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Hydrostatic Test
Shop test pressure determination for Chamber bounded by Ellipsoidal Head #1 and Ellipsoidal Head #2 basedon MAWP per UG-99(b)
Shop hydrostatic test gauge pressure is 209,003 psi at 70 °F (the chamber MAWP = 160,772 psi)
The shop test is performed with the vessel in the horizontal position.
IdentifierLocal testpressure
psi
Test liquidstatic head
psi
UG-99stressratio
UG-99pressure
factor
Ellipsoidal Head #2 (1) 212,09 3,087 1 1,30
Straight Flange on Ellipsoidal Head #2 212,096 3,093 1 1,30
Cylinder #1 212,09 3,086 1 1,30
Straight Flange on Ellipsoidal Head #1 212,096 3,093 1 1,30
Ellipsoidal Head #1 212,09 3,087 1 1,30
Nozzle #1 (N1) 210,837 1,834 1 1,30
Nozzle #10 (N10) 209,292 0,289 1 1,30
Nozzle #11 (N11) 212,324 3,321 1 1,30
Nozzle #12 (N12) 209,455 0,452 1 1,30
Nozzle #13 (N13) 211,998 2,995 1 1,30
Nozzle #14 (N14) 210,837 1,834 1 1,30
Nozzle #2 (N2) 212,324 3,321 1 1,30
Nozzle #3 (N3) 209,292 0,289 1 1,30
Nozzle #4 (N4) 209,292 0,289 1 1,30
Nozzle #5 (N5) 210,989 1,985 1 1,30
Nozzle #6 (N6) 210,712 1,709 1 1,30
Nozzle #7 (N7) 209,292 0,289 1 1,30
Nozzle #8 (N8) 209,292 0,289 1 1,30
Nozzle #9 (N9) 212,324 3,321 1 1,30
Notes:(1) Ellipsoidal Head #2 limits the UG-99 stress ratio.(2) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-mostflange.
The field test condition has not been investigated for the Chamber bounded by Ellipsoidal Head #1 and EllipsoidalHead #2.
The test temperature of 70 °F is warmer than the minimum recommended temperature of 10 °F so the brittle fractureprovision of UG-99(h) has been met.
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Cylinder #1
ASME Section VIII Division 1, 2010 Edition
Component: CylinderMaterial specification: SA-516 70 (II-D p. 18, ln. 19)Material impact test exemption temperature from Fig UCS-66 Curve B = -7 °FFig UCS-66.1 MDMT reduction = 37,5 °F, (coincident ratio = 0,625)UCS-66 governing thickness = 0,5 in
Internal design pressure: P = 150 psi @ 300 °F
Static liquid head:
Pth = 3,09 psi (SG = 1, Hs = 85,5", Horizontal testhead)
Corrosion allowance Inner C = 0" Outer C = 0"
Design MDMT = -20 °F No impact test performedRated MDMT = -44,5 °F Material is not normalized
Material is not produced to Fine Grain PracticePWHT is not performed
Radiography: Longitudinal joint - Full UW-11(a) Type 1Left circumferential joint - Full UW-11(a) Type 1Right circumferential joint - Full UW-11(a) Type 1
Estimated weight New = 8.250,8 lb corr = 8.250,8 lbCapacity New = 4.838,05 US gal corr = 4.838,05 US gal
OD = 78"LengthLc
= 240"
t = 0,5"
Design thickness, (at 300 °F) Appendix 1-1
t = P*Ro / (S*E + 0,40*P) + Corrosion= 150*39 / (20.000*1,00 + 0,40*150) + 0= 0,2917"
Maximum allowable working pressure, (at 300 °F) Appendix 1-1
P = S*E*t / (Ro - 0,40*t) - Ps= 20.000*1,00*0,5 / (39 - 0,40*0,5) - 0= 257,73 psi
Maximum allowable pressure, (at 70 °F) Appendix 1-1
P = S*E*t / (Ro - 0,40*t)= 20.000*1,00*0,5 / (39 - 0,40*0,5)= 257,73 psi
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% Extreme fiber elongation - UCS-79(d)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,5 / 38,75)*(1 - 38,75 / ∞)= 0,6452%
The extreme fiber elongation does not exceed 5%.
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Ellipsoidal Head #2
ASME Section VIII, Division 1, 2010 Edition
Component: Ellipsoidal HeadMaterial Specification: SA-516 70 (II-D p.18, ln. 19)Straight Flange governs MDMT
Internal design pressure: P = 150 psi @ 300 °F
Static liquid head:
Ps= 0 psi (SG=1, Hs=0" Operating head)Pth= 3,0868 psi (SG=1, Hs=85,513" Horizontal test head)
Corrosion allowance: Inner C = 0" Outer C = 0"
Design MDMT = -20°F No impact test performedRated MDMT = -20°F Material is not normalized
Material is not produced to fine grain practicePWHT is not performedDo not Optimize MDMT / Find MAWP
Radiography: Category A joints - Seamless No RT Head to shell seam - Full UW-11(a) Type 1
Estimated weight*: new = 964 lb corr = 964 lbCapacity*: new = 299,7 US gal corr = 299,7 US gal* includes straight flange
Outer diameter = 78"Minimum head thickness = 0,487"Head ratio D/2h = 2 (new)Head ratio D/2h = 2 (corroded)Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0,3125"Results Summary
The governing condition is internal pressure.Minimum thickness per UG-16 = 0,0625" + 0" = 0,0625"Design thickness due to internal pressure (t) = 0,2906"Maximum allowable working pressure (MAWP) = 252,58 psiMaximum allowable pressure (MAP) = 252,58 psi
K (Corroded)
K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (77,026 / (2*19,2565))2]=1
K (New)
K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (77,026 / (2*19,2565))2]=1
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Design thickness for internal pressure, (Corroded at 300 °F) Appendix 1-4(c)
t = P*Do*K / (2*S*E + 2*P*(K - 0,1)) + Corrosion= 150*78*1 / (2*20.000*1 + 2*150*(1 - 0,1)) + 0= 0,2905"
The head internal pressure design thickness is 0,2906".
Maximum allowable working pressure, (Corroded at 300 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0,1)) - Ps= 2*20.000*1*0,487 / (1*78 - 2*0,487*(1 - 0,1)) - 0= 252,58 psi
The maximum allowable working pressure (MAWP) is 252,58 psi.
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0,1)) - Ps= 2*20.000*1*0,487 / (1*78 - 2*0,487*(1 - 0,1)) - 0= 252,58 psi
The maximum allowable pressure (MAP) is 252,58 psi.
% Extreme fiber elongation - UCS-79(d)
EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*0,3125 / 13,2507)*(1 - 13,2507 / ∞)= 1,7688%
The extreme fiber elongation does not exceed 5%.
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Straight Flange on Ellipsoidal Head #2
ASME Section VIII Division 1, 2010 Edition
Component: Straight FlangeMaterial specification: SA-516 70 (II-D p. 18, ln. 19)Material is impact test exempt per UG-20(f)UCS-66 governing thickness = 0,3125 in
Internal design pressure: P = 150 psi @ 300 °F
Static liquid head:
Pth = 3,09 psi (SG = 1, Hs = 85,6875", Horizontal testhead)
Corrosion allowance Inner C = 0" Outer C = 0"
Design MDMT = -20 °F No impact test performedRated MDMT = -20 °F Material is not normalized
Material is not produced to Fine Grain PracticePWHT is not performed
Radiography: Longitudinal joint - Seamless No RTCircumferential joint - Full UW-11(a) Type 1
Estimated weight New = 43,2 lb corr = 43,2 lbCapacity New = 40,71 US gal corr = 40,71 US gal
OD = 78"LengthLc
= 2"
t = 0,3125"
Design thickness, (at 300 °F) Appendix 1-1
t = P*Ro / (S*E + 0,40*P) + Corrosion= 150*39 / (20.000*1,00 + 0,40*150) + 0= 0,2917"
Maximum allowable working pressure, (at 300 °F) Appendix 1-1
P = S*E*t / (Ro - 0,40*t) - Ps= 20.000*1,00*0,3125 / (39 - 0,40*0,3125) - 0= 160,77 psi
Maximum allowable pressure, (at 70 °F) Appendix 1-1
P = S*E*t / (Ro - 0,40*t)= 20.000*1,00*0,3125 / (39 - 0,40*0,3125)= 160,77 psi
% Extreme fiber elongation - UCS-79(d)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,3125 / 38,8438)*(1 - 38,8438 / ∞)
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= 0,4023%
The extreme fiber elongation does not exceed 5%.
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Straight Flange on Ellipsoidal Head #1
ASME Section VIII Division 1, 2010 Edition
Component: Straight FlangeMaterial specification: SA-516 70 (II-D p. 18, ln. 19)Material is impact test exempt per UG-20(f)UCS-66 governing thickness = 0,3125 in
Internal design pressure: P = 150 psi @ 300 °F
Static liquid head:
Pth = 3,09 psi (SG = 1, Hs = 85,6875", Horizontal testhead)
Corrosion allowance Inner C = 0" Outer C = 0"
Design MDMT = -20 °F No impact test performedRated MDMT = -20 °F Material is not normalized
Material is not produced to Fine Grain PracticePWHT is not performed
Radiography: Longitudinal joint - Seamless No RTCircumferential joint - Full UW-11(a) Type 1
Estimated weight New = 43,2 lb corr = 43,2 lbCapacity New = 40,71 US gal corr = 40,71 US gal
OD = 78"LengthLc
= 2"
t = 0,3125"
Design thickness, (at 300 °F) Appendix 1-1
t = P*Ro / (S*E + 0,40*P) + Corrosion= 150*39 / (20.000*1,00 + 0,40*150) + 0= 0,2917"
Maximum allowable working pressure, (at 300 °F) Appendix 1-1
P = S*E*t / (Ro - 0,40*t) - Ps= 20.000*1,00*0,3125 / (39 - 0,40*0,3125) - 0= 160,77 psi
Maximum allowable pressure, (at 70 °F) Appendix 1-1
P = S*E*t / (Ro - 0,40*t)= 20.000*1,00*0,3125 / (39 - 0,40*0,3125)= 160,77 psi
% Extreme fiber elongation - UCS-79(d)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,3125 / 38,8438)*(1 - 38,8438 / ∞)
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= 0,4023%
The extreme fiber elongation does not exceed 5%.
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Ellipsoidal Head #1
ASME Section VIII, Division 1, 2010 Edition
Component: Ellipsoidal HeadMaterial Specification: SA-516 70 (II-D p.18, ln. 19)Straight Flange governs MDMT
Internal design pressure: P = 150 psi @ 300 °F
Static liquid head:
Ps= 0 psi (SG=1, Hs=0" Operating head)Pth= 3,0868 psi (SG=1, Hs=85,513" Horizontal test head)
Corrosion allowance: Inner C = 0" Outer C = 0"
Design MDMT = -20°F No impact test performedRated MDMT = -20°F Material is not normalized
Material is not produced to fine grain practicePWHT is not performedDo not Optimize MDMT / Find MAWP
Radiography: Category A joints - Seamless No RT Head to shell seam - Full UW-11(a) Type 1
Estimated weight*: new = 992 lb corr = 992 lbCapacity*: new = 299,7 US gal corr = 299,7 US gal* includes straight flange
Outer diameter = 78"Minimum head thickness = 0,487"Head ratio D/2h = 2 (new)Head ratio D/2h = 2 (corroded)Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0,3125"Results Summary
The governing condition is internal pressure.Minimum thickness per UG-16 = 0,0625" + 0" = 0,0625"Design thickness due to internal pressure (t) = 0,2906"Maximum allowable working pressure (MAWP) = 252,58 psiMaximum allowable pressure (MAP) = 252,58 psi
K (Corroded)
K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (77,026 / (2*19,2565))2]=1
K (New)
K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (77,026 / (2*19,2565))2]=1
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Design thickness for internal pressure, (Corroded at 300 °F) Appendix 1-4(c)
t = P*Do*K / (2*S*E + 2*P*(K - 0,1)) + Corrosion= 150*78*1 / (2*20.000*1 + 2*150*(1 - 0,1)) + 0= 0,2905"
The head internal pressure design thickness is 0,2906".
Maximum allowable working pressure, (Corroded at 300 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0,1)) - Ps= 2*20.000*1*0,487 / (1*78 - 2*0,487*(1 - 0,1)) - 0= 252,58 psi
The maximum allowable working pressure (MAWP) is 252,58 psi.
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0,1)) - Ps= 2*20.000*1*0,487 / (1*78 - 2*0,487*(1 - 0,1)) - 0= 252,58 psi
The maximum allowable pressure (MAP) is 252,58 psi.
% Extreme fiber elongation - UCS-79(d)
EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*0,3125 / 13,2507)*(1 - 13,2507 / ∞)= 1,7688%
The extreme fiber elongation does not exceed 5%.
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Nozzle #1 (N1)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0 inLeg41 = 0,375 inLeg43 = 0,5 inhnew = 2 in
Note: round inside edges per UG-76(c)
Located on: Ellipsoidal Head #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 8 Sch 80 (XS)Flange description: 8 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 0°Calculated as hillside: NoLocal vessel minimum thickness: 0,487 inEnd of nozzle to datum line: -29,6722 inNozzle inside diameter, new: 7,625 inNozzle nominal wall thickness: 0,5 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 4,0498 inInternal projection, hnew: 2 inProjection available outside vessel to flange face, Lf: 8,0498 inDistance to head center, R: 0 in
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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 = 222,47 psi @ 300 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
3,0338 3,0341 0,7222 0,9369 1,041 -- 0,334 0,2818 0,4375
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
47.882,94 21.142 118.954,77 54.564,95 99.329,73
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,3462 0,35(corroded)
weld size is adequate
Reinforcement Calculations for MAP
Available reinforcement per UG-37 governs the MAP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 222,47 psi @ 70 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
3,0338 3,0341 0,7222 0,9369 1,041 -- 0,334 0,2818 0,4375
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
47.882,94 21.142 118.954,77 54.564,95 99.329,73
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
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Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,3462 0,35(corroded)
weld size is adequate
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:24:31 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : Elliptical Head
Parent Outside Diameter : 78.000 in.Thickness : 0.487 in.Ellipse Ratio : 2.000Straight Flange Length : 2.000 in.Attached Shell Length : 240.000 in.Attached Shell Thick : 0.487 in.Shell Transition Length: 0.039 in.Shell Transition SCF : 0.000 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 8.625 in.Thickness : 0.438 in.
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Length : 8.172 in.Nozzle Weld Length : 0.375 in.Insert Length : 2.365 in.Insert Thickness : 0.438 in.Location perpendicularto the head centerline : 0.000 in.
Nozzle Tilt Angle : 0.000 deg.
Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector: 0.000 0.000 -1.000Nozzle Centerline Vector: 0.000 0.000 -1.000Zero Degree Orientation Vector: 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
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THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1Loads from (Thermal Only)
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
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8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 1392Number of Nodes = 3853Number of Elements = 1296Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -9051. 0.2 0. -9051. -707930.3 0. 0. 0.4 0. -9051. -707930.5 0. 0. -225059.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 0. -707930.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
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5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Shell Next to Nozzle 1
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.
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Stress Concentration ..... 1.350
Nozzle 1 Next to Shell
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
Shell Next to Nozzle 1 Pad
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
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NOT USED
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
Nozzle 1 Pad Weld Area
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
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Shell In Nozzle 1 Vicinity
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.000
Nozzle 1 Transition Area
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
Barrel Section of Nozzle 1
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.000
Nozzle 1
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.000
Pad at Nozzle 1
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Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Shell Next to Nozzle 1
Pl 1.5(k)Smh Primary Membrane Load Case 214,903 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:49% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Nozzle 1 Next to Shell
Pl 1.5(k)Smh Primary Membrane Load Case 214,339 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:55% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Shell In Nozzle 1 Vicinity
Pl 1.5(k)Smh Primary Membrane Load Case 213,385 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:44% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Nozzle 1
Pl 1.5(k)Smh Primary Membrane Load Case 215,434 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:60% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Shell Next to Nozzle 1
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 416,358 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:27% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Nozzle 1 Next to Shell
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 419,238 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:37% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Shell In Nozzle 1 Vicinity
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 414,703 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:24% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Nozzle 1
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 431,828 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:62% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Table of Contents
Highest Fatigue Stress Ratios
Shell Next to Nozzle 1
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 511,027 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 7,658,056.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3,526,298.WRC 474 99% Probability Cycles = 819,207.WRC 474 95% Probability Cycles = 1,137,381.BS5500 Allowed Cycles(Curve F) = 484,888.Membrane-to-Bending Ratio = 3.204Bending-to-PL+PB+Q Ratio = 0.238Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Nozzle 1 Next to Shell
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 512,977 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 595,108.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1,223,304.WRC 474 99% Probability Cycles = 284,190.WRC 474 95% Probability Cycles = 394,568.BS5500 Allowed Cycles(Curve F) = 252,600.Membrane-to-Bending Ratio = 2.502Bending-to-PL+PB+Q Ratio = 0.286Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Shell In Nozzle 1 Vicinity
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 57,345 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 2.7222E100% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 4,850,926.WRC 474 99% Probability Cycles = 1,126,936.
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WRC 474 95% Probability Cycles = 1,564,630.BS5500 Allowed Cycles(Curve F) = 666,839.Membrane-to-Bending Ratio = 7.066Bending-to-PL+PB+Q Ratio = 0.124Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Nozzle 1
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 515,912 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 215,241.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 518,449.WRC 474 99% Probability Cycles = 120,443.WRC 474 95% Probability Cycles = 167,222.BS5500 Allowed Cycles(Curve F) = 65,595.Membrane-to-Bending Ratio = 0.680Bending-to-PL+PB+Q Ratio = 0.595Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 10.129 5.383 15.006Inplane : 7.162 2.868 10.611Outplane: 7.162 2.867 10.611Torsion : 0.716 0.997 1.061Pressure: 1.325 1.285 2.649
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 8.625 in.Pipe Thk: 0.438 in.Z approx: 23.034 cu.in.Z exact : 21.928 cu.in.
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B31.3Peak Stress Sif .... 0.000 Axial11.444 Inplane14.959 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial7.692 Inplane7.692 Outplane7.692 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial5.192 Inplane5.192 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 44994. 10914. 16372.Inplane Moment (in. lb.) 123992. 21268. 45116.Outplane Moment (in. lb.) 123996. 21268. 45117.Torsional Moment (in. lb.) 1060540. 150028. 225041.Pressure (psi ) 241.81 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 53621. 7886. 11829.Inplane Moment (in. lb.) 196140. 20398. 43271.Outplane Moment (in. lb.) 196166. 20401. 43276.Torsional Moment (in. lb.) 564023. 74901. 112351.Pressure (psi ) 249.33 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. A
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more realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 8.625 in.Wall Thickness = 0.438 in.
Axial Translational Stiffness = 566269. lb./in.Inplane Rotational Stiffness = 256645. in.lb./degOutplane Rotational Stiffness = 256645. in.lb./degTorsional Rotational Stiffness = 8064298. in.lb./deg
Table of Contents
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Finite Element Model
Finite Element Model•
Discontinuity at Center Nozzle
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #10 (N10)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 inLeg43 = 0,375 inhnew = 1 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 A Smls pipe (II-D p. 6, ln. 22)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 1 Sch 80 (XS)Flange description: 1 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 0°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 237 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 0,957 inNozzle nominal wall thickness: 0,179 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 3,81 inInternal projection, hnew: 1 inProjection available outside vessel to flange face, Lf: 6 in
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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 = 230 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1164 0,1566
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,1253 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,1253 0,2625(corroded)
weld size is adequate
Nozzle to shell groove (Lower) 0,1253 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1164 0,1566
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
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UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,1253 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,1253 0,2625(corroded)
weld size is adequate
Nozzle to shell groove (Lower) 0,1253 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:22:53 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 1.315 in.Thickness : 0.157 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Insert Length : 1.256 in.Insert Thickness : 0.157 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 3.000 in.
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Distance from Bottom : 237.000 in.
Nozzle PropertiesCold Allowable : 13700.0 psiHot Allowable : 13700.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 48000.0 psiYield Strength (Amb) : 30000.0 psiYield Strength (Hot) : 26500.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
The cylinder length or nozzle/branch location was adjustedso that a better mesh could be generated at each end of thecylinder. The nozzle is now located 5.43 in.down the length of the cylinder and the total cylinder lengthis 240.00 in.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratcheting
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calculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7
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Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 960Number of Nodes = 3612Number of Elements = 1164Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -441. 0.2 0. 462874. 37097.3 0. 0. 0.4 0. 462874. 37097.5 0. 2127. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 463315. 37097.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
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4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psi
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Case 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
Cold Allowable ........... 13700. psiHot Allowable @ 300 deg .. 13700. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 13700. psiHot Allowable @ 300 deg .. 13700. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8
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Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 13700. psiHot Allowable @ 300 deg .. 13700. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psi
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Pressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 212,147 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:40% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 210,515 20,550 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:51% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 2670 20,550 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:3% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 211,670 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:38% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 2697 20,550 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:3% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 514,270 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:23% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 518,067 41,100 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:43% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 5744 41,100 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:1% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 511,880 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:
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19% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 5830 41,100 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:2% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 59,632 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.1514E80% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3,076,001.WRC 474 99% Probability Cycles = 714,597.WRC 474 95% Probability Cycles = 992,142.BS5500 Allowed Cycles(Curve F) = 610,744.Membrane-to-Bending Ratio = 2.307Bending-to-PL+PB+Q Ratio = 0.302Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 512,195 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1,100,396.0% "B31" Fatigue Stress Allowable = 34250.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 5,830,184.WRC 474 99% Probability Cycles = 1,354,430.WRC 474 95% Probability Cycles = 1,880,483.BS5500 Allowed Cycles(Curve F) = 358,496.Membrane-to-Bending Ratio = 1.086Bending-to-PL+PB+Q Ratio = 0.479Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
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Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 5502 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 34250.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1.2006E11WRC 474 99% Probability Cycles = 2.7891E10WRC 474 95% Probability Cycles = 3.8724E10BS5500 Allowed Cycles(Curve F) = 3.3400E11Membrane-to-Bending Ratio = 3.498Bending-to-PL+PB+Q Ratio = 0.222Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 55,940 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 9,203,925.WRC 474 99% Probability Cycles = 2,138,196.WRC 474 95% Probability Cycles = 2,968,658.BS5500 Allowed Cycles(Curve F) = 1,260,782.Membrane-to-Bending Ratio = 28.753Bending-to-PL+PB+Q Ratio = 0.034Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5415 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 34250.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 9.1929E10WRC 474 99% Probability Cycles = 2.1356E10WRC 474 95% Probability Cycles = 2.9651E10BS5500 Allowed Cycles(Curve F) = 1.9357E11Membrane-to-Bending Ratio = 1.089Bending-to-PL+PB+Q Ratio = 0.479Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
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Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 1.848 1.046 2.738Inplane : 0.919 0.892 1.362Outplane: 0.914 0.892 1.354Torsion : 0.678 0.889 1.004Pressure: 1.042 1.039 1.544
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 1.315 in.Pipe Thk: 0.157 in.Z approx: 0.165 cu.in.Z exact : 0.148 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial3.921 Inplane5.124 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.000 Inplane1.000 Outplane1.000 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 11736. 2311. 3466.Inplane Moment (in. lb.) 4467. 622. 1319.Outplane Moment (in. lb.) 4495. 626. 1328.Torsional Moment (in. lb.) 6059. 1193. 1789.Pressure (psi ) 341.23 150.00 150.00
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PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 11195. 1820. 2731.Inplane Moment (in. lb.) 3411. 396. 839.Outplane Moment (in. lb.) 3411. 397. 841.Torsional Moment (in. lb.) 3422. 556. 835.Pressure (psi ) 292.86 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 1.315 in.Wall Thickness = 0.157 in.
Axial Translational Stiffness = 533075. lb./in.Inplane Rotational Stiffness = 153135. in.lb./degOutplane Rotational Stiffness = 61138. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element model
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is stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #11 (N11)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 inLeg43 = 0,375 inhnew = 1 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 1 Sch 80 (XS)Flange description: 2 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 180°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 237 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 0,957 inNozzle nominal wall thickness: 0,179 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 3,5 inInternal projection, hnew: 1 inProjection available outside vessel to flange face, Lf: 6 in
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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 = 230 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1164 0,1566
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,1253 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,1253 0,2625(corroded)
weld size is adequate
Nozzle to shell groove (Lower) 0,1253 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1164 0,1566
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
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UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,1253 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,1253 0,2625(corroded)
weld size is adequate
Nozzle to shell groove (Lower) 0,1253 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:23:23 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 1.315 in.Thickness : 0.157 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Insert Length : 1.256 in.Insert Thickness : 0.157 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 3.000 in.
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Distance from Bottom : 237.000 in.
Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
The cylinder length or nozzle/branch location was adjustedso that a better mesh could be generated at each end of thecylinder. The nozzle is now located 5.43 in.down the length of the cylinder and the total cylinder lengthis 240.00 in.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 -1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratcheting
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calculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7
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Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 960Number of Nodes = 3612Number of Elements = 1164Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -441. 0.2 -1. -463755. 37097.3 0. 0. 0.4 -1. -463755. 37097.5 0. -2127. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 -1. -463315. 37097.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
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4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psi
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Case 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8
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Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 3732. psi
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Pressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 14366. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.157 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 212,174 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:40% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 210,536 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:41% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 2668 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 211,695 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:38% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 2695 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 414,279 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:23% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 418,090 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:35% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 4744 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:1% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 411,891 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:
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19% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 4832 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:1% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 59,632 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.1514E80% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3,076,007.WRC 474 99% Probability Cycles = 714,598.WRC 474 95% Probability Cycles = 992,144.BS5500 Allowed Cycles(Curve F) = 610,743.Membrane-to-Bending Ratio = 2.306Bending-to-PL+PB+Q Ratio = 0.302Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 512,195 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1,100,447.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 5,830,221.WRC 474 99% Probability Cycles = 1,354,439.WRC 474 95% Probability Cycles = 1,880,495.BS5500 Allowed Cycles(Curve F) = 358,498.Membrane-to-Bending Ratio = 1.086Bending-to-PL+PB+Q Ratio = 0.479Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
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Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 5502 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1.2006E11WRC 474 99% Probability Cycles = 2.7892E10WRC 474 95% Probability Cycles = 3.8726E10BS5500 Allowed Cycles(Curve F) = 3.3402E11Membrane-to-Bending Ratio = 3.498Bending-to-PL+PB+Q Ratio = 0.222Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 55,940 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 9,202,534.WRC 474 99% Probability Cycles = 2,137,873.WRC 474 95% Probability Cycles = 2,968,209.BS5500 Allowed Cycles(Curve F) = 1,260,600.Membrane-to-Bending Ratio = 28.752Bending-to-PL+PB+Q Ratio = 0.034Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5415 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 9.1944E10WRC 474 99% Probability Cycles = 2.1360E10WRC 474 95% Probability Cycles = 2.9656E10BS5500 Allowed Cycles(Curve F) = 1.9362E11Membrane-to-Bending Ratio = 1.088Bending-to-PL+PB+Q Ratio = 0.479Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
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Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 1.849 1.046 2.740Inplane : 0.920 0.892 1.362Outplane: 0.914 0.892 1.354Torsion : 0.678 0.889 1.004Pressure: 1.042 1.039 1.544
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 1.315 in.Pipe Thk: 0.157 in.Z approx: 0.165 cu.in.Z exact : 0.148 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial3.921 Inplane5.124 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.000 Inplane1.000 Outplane1.000 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 12481. 3276. 4914.Inplane Moment (in. lb.) 5575. 883. 1873.Outplane Moment (in. lb.) 5611. 889. 1885.Torsional Moment (in. lb.) 7562. 1694. 2541.Pressure (psi ) 425.92 150.00 150.00
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PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 13973. 2746. 4120.Inplane Moment (in. lb.) 4258. 597. 1266.Outplane Moment (in. lb.) 4258. 598. 1269.Torsional Moment (in. lb.) 4272. 840. 1259.Pressure (psi ) 365.55 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 1.315 in.Wall Thickness = 0.157 in.
Axial Translational Stiffness = 533070. lb./in.Inplane Rotational Stiffness = 152688. in.lb./degOutplane Rotational Stiffness = 61130. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element model
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is stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #12 (N12)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Ellipsoidal Head #2Liquid static head included: 0 psiNozzle material specification: SA-105 (II-D p. 18, ln. 5)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 0,75 Class 6000 - threadedNozzle orientation: 0°Calculated as hillside: YesLocal vessel minimum thickness: 0,487 inEnd of nozzle to datum line: 258,0562 inNozzle inside diameter, new: 1,05 inNozzle nominal wall thickness: 0,35 inNozzle corrosion allowance: 0 inOpening chord length: 1,5075 inProjection available outside vessel, Lpr: 6,4979 inDistance to head center, R: 35 inReinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 252,58 psi @ 300 °F
UG-45Nozzle WallThicknessSummary
(in)The nozzle
passes UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
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This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,35
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,245 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,245 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 252,58 psi @ 70 °F
UG-45Nozzle WallThicknessSummary
(in)The nozzle
passes UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,35
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,245 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,245 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Nozzle #13 (N13)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0 inLeg41 = 0,375 inLeg43 = 0,375 inhnew = 1 in
Note: round inside edges per UG-76(c)
Located on: Ellipsoidal Head #2Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 2 Sch 80 (XS)Flange description: 2 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 180°Calculated as hillside: YesLocal vessel minimum thickness: 0,487 inEnd of nozzle to datum line: 258,3231 inNozzle inside diameter, new: 1,939 inNozzle nominal wall thickness: 0,218 inNozzle corrosion allowance: 0 inOpening chord length: 2,7926 inProjection available outside vessel, Lpr: 3,9843 inInternal projection, hnew: 1 inProjection available outside vessel to flange face, Lf: 6,4843 inDistance to head center, R: 35 in
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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 = 193,98 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1348 0,1908
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,1526 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,1526 0,2625(corroded)
weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
Available reinforcement per UG-37 governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 193,98 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1348 0,1908
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
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Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,1526 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,1526 0,2625(corroded)
weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Nozzle #14 (N14)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0 inLeg41 = 0,375 inLeg43 = 0,5625 inhnew = 0,5625 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 8 Sch 80 (XS)Flange description: 8 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 90°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 12 inEnd of nozzle to shell center: 47 inNozzle inside diameter, new: 7,625 inNozzle nominal wall thickness: 0,5 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 4 inInternal projection, hnew: 0,5625 inProjection available outside vessel to flange face, Lf: 8 in
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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 = 188,68 psi @ 300 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
2,8481 2,8481 0,9982 0,9783 0,4809 -- 0,3907 0,2818 0,4375
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
39.279,87 21.970 118.954,77 45.548,75 106.424,7
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,3625 0,3938(corroded)
weld size is adequate
Reinforcement Calculations for MAP
Available reinforcement per UG-37 governs the MAP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 188,68 psi @ 70 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
2,8481 2,8481 0,9982 0,9783 0,4809 -- 0,3907 0,2818 0,4375
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
39.279,87 21.970 118.954,77 45.548,75 106.424,7
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
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Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,3625 0,3938(corroded)
weld size is adequate
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:23:04 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 8.625 in.Thickness : 0.438 in.Length : 8.250 in.Nozzle Weld Length : 0.375 in.Insert Length : 1.055 in.Insert Thickness : 0.438 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 228.000 in.
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Distance from Bottom : 12.000 in.
Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 1.000 0.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
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Weight ONLY case run to get the stress rangebetween the installed and the operating states.
/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8
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Loads from (Outplane)
9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 1032Number of Nodes = 4063Number of Elements = 1328Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -8295. 0.2 -890. -8295. 698509.3 0. 0. 0.4 -890. -8295. 698509.5 255615. 0. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 -890. 0. 698509.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
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7) Bending < User (OPE,Bending) Case 4
8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 22715. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
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Branch Next to Header Weld
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 22715. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 22715. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 10
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Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 22715. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 22715. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11657. psi
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Pressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11657. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.438 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 215,983 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:53% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 217,378 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:67% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
S1+S2+S3 4S Part 5 (5.3.2) Load Case 29,197 68,400 Plot Reference:psi psi 3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
13%
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 214,193 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1
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Plot Reference:47% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 416,991 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:28% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 434,184 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:66% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 45,285 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:10% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 414,443 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:24% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 511,463 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 3,683,533.0% "B31" Fatigue Stress Allowable = 50000.0
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Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1,759,287.WRC 474 99% Probability Cycles = 408,706.WRC 474 95% Probability Cycles = 567,445.BS5500 Allowed Cycles(Curve F) = 362,392.Membrane-to-Bending Ratio = 6.808Bending-to-PL+PB+Q Ratio = 0.128Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 523,050 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 46,679.1% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 405,383.WRC 474 99% Probability Cycles = 94,176.WRC 474 95% Probability Cycles = 130,753.BS5500 Allowed Cycles(Curve F) = 53,089.Membrane-to-Bending Ratio = 0.801Bending-to-PL+PB+Q Ratio = 0.555Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 53,565 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1.3575E8WRC 474 99% Probability Cycles = 31,535,548.WRC 474 95% Probability Cycles = 43,783,760.BS5500 Allowed Cycles(Curve F) = 18,520,082.Membrane-to-Bending Ratio = 0.778Bending-to-PL+PB+Q Ratio = 0.562Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 57,209 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 3.8872E100% "B31" Fatigue Stress Allowable = 50000.0
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Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 5,027,957.WRC 474 99% Probability Cycles = 1,168,062.WRC 474 95% Probability Cycles = 1,621,730.BS5500 Allowed Cycles(Curve F) = 705,345.Membrane-to-Bending Ratio = 22.854Bending-to-PL+PB+Q Ratio = 0.042Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 13.585 6.630 20.125Inplane : 6.090 2.653 9.023Outplane: 8.816 3.409 13.061Torsion : 0.717 1.001 1.062Pressure: 1.970 1.485 2.919
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 8.625 in.Pipe Thk: 0.438 in.Z approx: 23.034 cu.in.Z exact : 21.928 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial10.955 Inplane14.315 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial7.361 Inplane7.361 Outplane7.361 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial4.969 Inplane4.969 Outplane1.000 Torsional
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Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 33550. 4406. 6609.Inplane Moment (in. lb.) 145817. 14517. 30796.Outplane Moment (in. lb.) 100736. 9825. 20842.Torsional Moment (in. lb.) 1058975. 118522. 177783.Pressure (psi ) 225.34 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 50924. 5770. 8655.Inplane Moment (in. lb.) 212045. 16136. 34230.Outplane Moment (in. lb.) 191008. 14535. 30834.Torsional Moment (in. lb.) 562106. 60825. 91238.Pressure (psi ) 221.52 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,
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"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 8.625 in.Wall Thickness = 0.438 in.
Axial Translational Stiffness = 525314. lb./in.Inplane Rotational Stiffness = 351803. in.lb./degOutplane Rotational Stiffness = 176913. in.lb./degTorsional Rotational Stiffness = 472092864. in.lb./deg
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #2 (N2)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,5 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 6 Sch 80 (XS)Flange description: 6 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 180°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 226 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 5,761 inNozzle nominal wall thickness: 0,432 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 2,5 inProjection available outside vessel to flange face, Lf: 6 in
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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 = 164,51 psi @ 300 °F
The opening is adequately reinforced
UG-45Nozzle WallThicknessSummary
(in)The nozzle
passes UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
1,8821 1,8823 1,0158 0,7463 -- -- 0,1202 0,245 0,378
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(1)
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Reinforcement Calculations for MAP
Available reinforcement per UG-37 governs the MAP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 164,51 psi @ 70 °F
The opening is adequately reinforced
UG-45Nozzle WallThicknessSummary
(in)The nozzle
passes UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
1,8821 1,8823 1,0158 0,7463 -- -- 0,1202 0,245 0,378
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(1)
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:21:30 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 6.625 in.Thickness : 0.378 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 14.000 in.Distance from Bottom : 226.000 in.
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Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 -1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 828Number of Nodes = 2638Number of Elements = 840Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -1773. 0.2 -4. -1732054. 148790.3 0. 0. 0.4 -4. -1732054. 148790.5 0. -130303. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 -4. -1730281. 148790.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 17565. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.378 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 17565. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.378 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 17565. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.378 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 17565. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.378 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 17565. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 11884. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.378 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 218,698 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:62% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 218,425 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:71% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 23,067 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:11% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 214,527 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:48% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 423,504 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:39% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 425,447 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:49% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 44,528 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:8% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 514,998 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:24% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 515,853 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 218,896.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 649,388.
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WRC 474 99% Probability Cycles = 150,862.WRC 474 95% Probability Cycles = 209,455.BS5500 Allowed Cycles(Curve F) = 136,986.Membrane-to-Bending Ratio = 2.469Bending-to-PL+PB+Q Ratio = 0.288Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 517,154 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 161,648.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1,058,903.WRC 474 99% Probability Cycles = 245,997.WRC 474 95% Probability Cycles = 341,541.BS5500 Allowed Cycles(Curve F) = 128,805.Membrane-to-Bending Ratio = 2.402Bending-to-PL+PB+Q Ratio = 0.294Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 53,052 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2.4356E8WRC 474 99% Probability Cycles = 56,582,940.WRC 474 95% Probability Cycles = 78,559,416.BS5500 Allowed Cycles(Curve F) = 40,288,588.Membrane-to-Bending Ratio = 0.857Bending-to-PL+PB+Q Ratio = 0.538Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 57,499 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.8346E100% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 4,460,972.
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WRC 474 99% Probability Cycles = 1,036,344.WRC 474 95% Probability Cycles = 1,438,854.BS5500 Allowed Cycles(Curve F) = 626,634.Membrane-to-Bending Ratio = 8.298Bending-to-PL+PB+Q Ratio = 0.108Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 13.304 6.875 19.710Inplane : 4.277 2.393 6.336Outplane: 6.165 2.824 9.133Torsion : 0.717 0.993 1.062Pressure: 1.466 1.596 2.172
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 6.625 in.Pipe Thk: 0.378 in.Z approx: 11.586 cu.in.Z exact : 10.965 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial9.465 Inplane12.368 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial5.518 Inplane5.518 Outplane5.518 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial3.725 Inplane3.725 Outplane1.000 Torsional
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Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 22583. 4062. 6094.Inplane Moment (in. lb.) 96365. 12330. 26155.Outplane Moment (in. lb.) 65979. 8899. 18878.Torsional Moment (in. lb.) 529817. 99878. 149817.Pressure (psi ) 302.79 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 27676. 2606. 3910.Inplane Moment (in. lb.) 117521. 7826. 16602.Outplane Moment (in. lb.) 99574. 6631. 14066.Torsional Moment (in. lb.) 283263. 26695. 40043.Pressure (psi ) 209.07 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of the
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branch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 6.625 in.Wall Thickness = 0.378 in.
Axial Translational Stiffness = 290833. lb./in.Inplane Rotational Stiffness = 208029. in.lb./degOutplane Rotational Stiffness = 105345. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #3 (N3)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 4 Sch 80 (XS)Flange description: 4 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 0°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 226 inEnd of nozzle to shell center: 46 inNozzle inside diameter, new: 3,826 inNozzle nominal wall thickness: 0,337 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 4 inProjection available outside vessel to flange face, Lf: 7 in
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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 = 164,27 psi @ 300 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
1,2528 1,2529 0,6738 0,4589 -- -- 0,1202 0,2074 0,2949
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
13.662,24 11.582 48.588,89 17.344,7 61.441,01
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,2359 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,2359 0,375 weld size is adequate
Reinforcement Calculations for MAP
Available reinforcement per UG-37 governs the MAP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 164,27 psi @ 70 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
1,2528 1,2529 0,6738 0,4589 -- -- 0,1202 0,2074 0,2949
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
13.662,24 11.582 48.588,89 17.344,7 61.441,01
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,2359 0,2625 weld size is adequate
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Nozzle to shell groove (Lower) 0,2359 0,375 weld size is adequate
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:21:35 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 4.500 in.Thickness : 0.295 in.Length : 7.250 in.Nozzle Weld Length : 0.375 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 14.000 in.Distance from Bottom : 226.000 in.
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Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 828Number of Nodes = 2782Number of Elements = 888Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -1372. 0.2 0. 1380492. 115234.3 0. 0. 0.4 0. 1380492. 115234.5 0. 46902. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 1381864. 115234.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 12039. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.295 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 12039. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.295 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 12039. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.295 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 12039. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.295 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 12039. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 12195. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.295 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 216,788 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:55% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 216,220 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:63% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 21,865 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:7% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 213,193 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:43% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 22,078 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:8% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 523,033 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:38% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 524,656 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:48% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 52,607 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:5% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 413,987 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:23% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 53,089 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:6% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 515,547 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 239,282.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 692,947.WRC 474 99% Probability Cycles = 160,981.WRC 474 95% Probability Cycles = 223,505.BS5500 Allowed Cycles(Curve F) = 145,239.Membrane-to-Bending Ratio = 2.069Bending-to-PL+PB+Q Ratio = 0.326Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 516,643 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 180,261.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1,392,213.WRC 474 99% Probability Cycles = 323,430.WRC 474 95% Probability Cycles = 449,048.BS5500 Allowed Cycles(Curve F) = 141,039.Membrane-to-Bending Ratio = 1.855Bending-to-PL+PB+Q Ratio = 0.350Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 51,760 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1.5503E9WRC 474 99% Probability Cycles = 3.6016E8
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WRC 474 95% Probability Cycles = 5.0004E8BS5500 Allowed Cycles(Curve F) = 6.3162E8Membrane-to-Bending Ratio = 2.286Bending-to-PL+PB+Q Ratio = 0.304Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 56,993 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 6.9466E100% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 5,548,528.WRC 474 99% Probability Cycles = 1,288,998.WRC 474 95% Probability Cycles = 1,789,637.BS5500 Allowed Cycles(Curve F) = 772,922.Membrane-to-Bending Ratio = 8.579Bending-to-PL+PB+Q Ratio = 0.104Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 51,545 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 9.3176E8WRC 474 99% Probability Cycles = 2.1646E8WRC 474 95% Probability Cycles = 3.0053E8BS5500 Allowed Cycles(Curve F) = 2.7062E8Membrane-to-Bending Ratio = 1.228Bending-to-PL+PB+Q Ratio = 0.449Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 9.197 5.481 13.626Inplane : 2.799 1.721 4.146
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Outplane: 3.395 1.909 5.030Torsion : 0.718 0.962 1.064Pressure: 1.422 1.436 2.107
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 4.500 in.Pipe Thk: 0.295 in.Z approx: 4.096 cu.in.Z exact : 3.846 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial7.384 Inplane9.649 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial3.501 Inplane3.501 Outplane3.501 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial2.363 Inplane2.363 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 15932. 3120. 4680.Inplane Moment (in. lb.) 47586. 7163. 15194.Outplane Moment (in. lb.) 39223. 6015. 12759.Torsional Moment (in. lb.) 185471. 37675. 56512.Pressure (psi ) 312.09 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 18233. 2230. 3344.Inplane Moment (in. lb.) 57324. 4957. 10515.Outplane Moment (in. lb.) 51667. 4467. 9477.Torsional Moment (in. lb.) 102501. 12534. 18801.
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Pressure (psi ) 236.91 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 4.500 in.Wall Thickness = 0.295 in.
Axial Translational Stiffness = 239701. lb./in.Inplane Rotational Stiffness = 122811. in.lb./degOutplane Rotational Stiffness = 73369. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #4 (N4)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,1875 inLeg41 = 0,25 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 2 Sch 80 (XS)Flange description: 2 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 0°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 12 inEnd of nozzle to shell center: 47 inNozzle inside diameter, new: 1,939 inNozzle nominal wall thickness: 0,218 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 5,5 inProjection available outside vessel to flange face, Lf: 8 in
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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 = 230 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1348 0,1908
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,1526 0,175 weld size is adequate
Nozzle to shell groove (Lower) 0,1526 0,1875 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,1348 0,1908
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
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Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,1526 0,175 weld size is adequate
Nozzle to shell groove (Lower) 0,1526 0,1875 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:21:36 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.250 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 2.375 in.Thickness : 0.191 in.Length : 8.250 in.Nozzle Weld Length : 0.250 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 228.000 in.Distance from Bottom : 12.000 in.
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Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 888Number of Nodes = 3218Number of Elements = 1032Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -731. 0.2 0. 760927. 61485.3 0. 0. 0.4 0. 760927. 61485.5 0. 8448. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 761658. 61485.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 6456. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.191 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 6456. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.191 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 6456. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.191 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 6456. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.191 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 6456. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 12757. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.191 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 215,859 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:52% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 215,225 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:59% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 21,311 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:5% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 212,303 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:41% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 21,397 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:5% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 522,939 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:38% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 525,621 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:49% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 51,907 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:3% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 513,182 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:21% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 52,500 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:4% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 515,484 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 243,813.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 782,793.WRC 474 99% Probability Cycles = 181,853.WRC 474 95% Probability Cycles = 252,484.BS5500 Allowed Cycles(Curve F) = 165,062.Membrane-to-Bending Ratio = 1.884Bending-to-PL+PB+Q Ratio = 0.347Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 517,294 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 156,975.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1,687,447.WRC 474 99% Probability Cycles = 392,017.WRC 474 95% Probability Cycles = 544,274.BS5500 Allowed Cycles(Curve F) = 125,697.Membrane-to-Bending Ratio = 1.407Bending-to-PL+PB+Q Ratio = 0.416Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 51,287 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 5.5935E9WRC 474 99% Probability Cycles = 1.2994E9
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WRC 474 95% Probability Cycles = 1.8041E9BS5500 Allowed Cycles(Curve F) = 3.0187E9Membrane-to-Bending Ratio = 2.061Bending-to-PL+PB+Q Ratio = 0.327Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 56,591 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 6,669,916.WRC 474 99% Probability Cycles = 1,549,512.WRC 474 95% Probability Cycles = 2,151,332.BS5500 Allowed Cycles(Curve F) = 922,894.Membrane-to-Bending Ratio = 9.541Bending-to-PL+PB+Q Ratio = 0.095Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 51,250 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2.4896E9WRC 474 99% Probability Cycles = 5.7836E8WRC 474 95% Probability Cycles = 8.0300E8BS5500 Allowed Cycles(Curve F) = 7.7868E8Membrane-to-Bending Ratio = 0.840Bending-to-PL+PB+Q Ratio = 0.543Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 4.754 3.106 7.043Inplane : 1.718 0.973 2.546
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Outplane: 1.780 0.991 2.637Torsion : 0.705 0.932 1.044Pressure: 1.478 1.357 2.190
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 2.375 in.Pipe Thk: 0.191 in.Z approx: 0.715 cu.in.Z exact : 0.662 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial4.775 Inplane6.240 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.606 Inplane1.606 Outplane1.606 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 9531. 1942. 2913.Inplane Moment (in. lb.) 13346. 2605. 5526.Outplane Moment (in. lb.) 12885. 2515. 5335.Torsional Moment (in. lb.) 32536. 6574. 9862.Pressure (psi ) 300.33 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 10807. 1461. 2192.Inplane Moment (in. lb.) 17459. 1669. 3541.Outplane Moment (in. lb.) 17140. 1639. 3477.Torsional Moment (in. lb.) 18218. 2464. 3695.
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Pressure (psi ) 252.39 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 2.375 in.Wall Thickness = 0.191 in.
Axial Translational Stiffness = 350358. lb./in.Inplane Rotational Stiffness = 64192. in.lb./degOutplane Rotational Stiffness = 46954. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #5 (N5)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0 inLeg41 = 0,375 inLeg43 = 1 inhnew = 3 in
Note: round inside edges per UG-76(c)
Located on: Ellipsoidal Head #2Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 18 Sch 1,000Flange description: 18 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 230 psi @ 300°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FPWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 0°Calculated as hillside: NoLocal vessel minimum thickness: 0,487 inEnd of nozzle to datum line: 268 inNozzle inside diameter, new: 16 inNozzle nominal wall thickness: 1 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 1,2894 inInternal projection, hnew: 3 inProjection available outside vessel to flange face, Lf: 6,7894 inDistance to head center, R: 0 in
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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 = 223,83 psi @ 300 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
6,3989 6,3991 1,4797 1,8623 2,0819 -- 0,9752 0,1055 0,875
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
101.604,8 39.650 408.482,84 115.043,9 325.752,13
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,3462 0,7(corroded)
weld size is adequate
Reinforcement Calculations for MAP
Available reinforcement per UG-37 governs the MAP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 223,83 psi @ 70 °F
The opening is adequately reinforced
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
6,3989 6,3991 1,4797 1,8623 2,0819 -- 0,9752 0,1055 0,875
UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads
Weld loadW
Weld loadW1-1
Path 1-1strength
Weld loadW2-2
Path 2-2strength
101.604,8 39.650 408.482,84 115.043,9 325.752,13
UW-16 Weld Sizing Summary
Weld description Required weldthroat size (in)
Actual weldthroat size (in) Status
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Nozzle to shell fillet (Leg41) 0,25 0,2625 weld size is adequate
Nozzle to inside shell fillet (Leg43) 0,3462 0,7(corroded)
weld size is adequate
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:21:09 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : Elliptical Head
Parent Outside Diameter : 78.000 in.Thickness : 0.487 in.Ellipse Ratio : 2.000Straight Flange Length : 2.000 in.Attached Shell Length : 240.000 in.Attached Shell Thick : 0.487 in.Shell Transition Length: 0.039 in.Shell Transition SCF : 0.000 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 18.000 in.Thickness : 0.875 in.
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Length : 6.500 in.Nozzle Weld Length : 0.375 in.Insert Length : 3.776 in.Insert Thickness : 0.875 in.Location perpendicularto the head centerline : 0.000 in.
Nozzle Tilt Angle : 0.000 deg.
Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector: 0.000 0.000 1.000Nozzle Centerline Vector: 0.000 0.000 1.000Zero Degree Orientation Vector: 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
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THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1Loads from (Thermal Only)
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
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8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 1392Number of Nodes = 3853Number of Elements = 1296Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -9139. 0.2 0. -9139. 707902.3 0. 0. 0.4 0. -9139. 707902.5 0. 0. 941468.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 0. 707902.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
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5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Shell Next to Nozzle 1
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.
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Stress Concentration ..... 1.350
Nozzle 1 Next to Shell
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.350
Shell Next to Nozzle 1 Pad
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.350
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NOT USED
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.350
Nozzle 1 Pad Weld Area
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.350
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Shell In Nozzle 1 Vicinity
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.000
Nozzle 1 Transition Area
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.350
Barrel Section of Nozzle 1
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.000
Nozzle 1
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.000
Pad at Nozzle 1
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Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 12012. psiCase 6Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20000. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 12012. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.875 in.Stress Concentration ..... 1.350
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Shell Next to Nozzle 1
Pl 1.5(k)Smh Primary Membrane Load Case 213,207 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:44% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Nozzle 1 Next to Shell
Pl 1.5(k)Smh Primary Membrane Load Case 211,511 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:44% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Shell In Nozzle 1 Vicinity
Pl 1.5(k)Smh Primary Membrane Load Case 212,311 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:41% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Nozzle 1
Pl 1.5(k)Smh Primary Membrane Load Case 211,912 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:46% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Shell Next to Nozzle 1
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 415,441 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:25% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Nozzle 1 Next to Shell
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 417,615 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:34% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Shell In Nozzle 1 Vicinity
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 413,507 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:22% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Nozzle 1
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 423,959 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:46% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Table of Contents
Highest Fatigue Stress Ratios
Shell Next to Nozzle 1
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 510,409 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 23,030,240.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 4,232,365.WRC 474 99% Probability Cycles = 983,235.WRC 474 95% Probability Cycles = 1,365,118.BS5500 Allowed Cycles(Curve F) = 576,520.Membrane-to-Bending Ratio = 2.815Bending-to-PL+PB+Q Ratio = 0.262Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Nozzle 1 Next to Shell
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 511,887 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1,899,477.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1,952,002.WRC 474 99% Probability Cycles = 453,476.WRC 474 95% Probability Cycles = 629,604.BS5500 Allowed Cycles(Curve F) = 384,187.Membrane-to-Bending Ratio = 1.079Bending-to-PL+PB+Q Ratio = 0.481Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Shell In Nozzle 1 Vicinity
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 56,753 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 6,315,883.WRC 474 99% Probability Cycles = 1,467,265.
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WRC 474 95% Probability Cycles = 2,037,142.BS5500 Allowed Cycles(Curve F) = 857,999.Membrane-to-Bending Ratio = 6.068Bending-to-PL+PB+Q Ratio = 0.141Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Nozzle 1
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 511,978 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1,614,597.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 774,155.WRC 474 99% Probability Cycles = 179,847.WRC 474 95% Probability Cycles = 249,698.BS5500 Allowed Cycles(Curve F) = 152,619.Membrane-to-Bending Ratio = 0.712Bending-to-PL+PB+Q Ratio = 0.584Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 18.810 6.539 27.866Inplane : 17.765 6.847 26.319Outplane: 17.765 6.851 26.318Torsion : 0.969 1.435 1.435Pressure: 0.997 1.099 1.994
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 18.000 in.Pipe Thk: 0.875 in.Z approx: 201.539 cu.in.Z exact : 192.242 cu.in.
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B31.3Peak Stress Sif .... 0.000 Axial22.888 Inplane29.918 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial22.298 Inplane22.298 Outplane22.298 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial15.051 Inplane15.051 Outplane3.325 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 101359. 25103. 37654.Inplane Moment (in. lb.) 438261. 76750. 162811.Outplane Moment (in. lb.) 438274. 76752. 162816.Torsional Moment (in. lb.) 8036165. 1832154. 2748232.Pressure (psi ) 321.22 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 196558. 36119. 54179.Inplane Moment (in. lb.) 842261. 111131. 235745.Outplane Moment (in. lb.) 841783. 111068. 235611.Torsional Moment (in. lb.) 4018774. 749890. 1124836.Pressure (psi ) 323.03 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. A
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more realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 18.000 in.Wall Thickness = 0.875 in.
Axial Translational Stiffness = 1275837. lb./in.Inplane Rotational Stiffness = 1517246. in.lb./degOutplane Rotational Stiffness = 1517247. in.lb./degTorsional Rotational Stiffness = 48777128. in.lb./deg
Table of Contents
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Finite Element Model
Finite Element Model•
Discontinuity at Center Nozzle
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #6 (N6)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-105 (II-D p. 18, ln. 5)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 0,375 Class 6000 - threadedNozzle orientation: 270°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 144 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 0,675 inNozzle nominal wall thickness: 0,2875 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 6 inReinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,2875
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UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,2012 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,2013 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,2875
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,2012 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,2013 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:22:49 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 1.250 in.Thickness : 0.287 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 96.000 in.Distance from Bottom : 144.000 in.
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Nozzle PropertiesCold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 36000.0 psiYield Strength (Hot) : 31800.0 psiElastic Modulus (Amb) : 29200000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : -1.000 0.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 900Number of Nodes = 4240Number of Elements = 1356Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -422. 0.2 -443556. -422. 35502.3 0. 0. 0.4 -443556. -422. 35502.5 -3528. 0. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 -443556. 0. 35502.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4058. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.287 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4058. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.287 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4058. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.287 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4058. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.287 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4058. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 20110. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.287 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 212,197 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:40% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 29,050 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:30% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 2352 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:1% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 211,760 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:39% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 2419 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:1% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 413,535 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:22% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 517,987 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:29% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 4486 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:0% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 411,799 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:19% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 4491 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:0% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 59,136 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 3.2381E80% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3,624,190.WRC 474 99% Probability Cycles = 841,948.WRC 474 95% Probability Cycles = 1,168,956.BS5500 Allowed Cycles(Curve F) = 715,768.Membrane-to-Bending Ratio = 2.418Bending-to-PL+PB+Q Ratio = 0.293Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 512,141 1,786,975 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1,046,077.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3,810,786.WRC 474 99% Probability Cycles = 885,297.WRC 474 95% Probability Cycles = 1,229,141.BS5500 Allowed Cycles(Curve F) = 370,831.Membrane-to-Bending Ratio = 1.002Bending-to-PL+PB+Q Ratio = 0.499Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 5325 1,786,975 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3.0434E11WRC 474 99% Probability Cycles = 7.0702E10
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WRC 474 95% Probability Cycles = 9.8162E10BS5500 Allowed Cycles(Curve F) = 3.0617E12Membrane-to-Bending Ratio = 2.237Bending-to-PL+PB+Q Ratio = 0.309Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 55,900 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 9,403,123.WRC 474 99% Probability Cycles = 2,184,472.WRC 474 95% Probability Cycles = 3,032,908.BS5500 Allowed Cycles(Curve F) = 1,287,048.Membrane-to-Bending Ratio = 30.241Bending-to-PL+PB+Q Ratio = 0.032Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 5240 1,786,975 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3.0383E11WRC 474 99% Probability Cycles = 7.0585E10WRC 474 95% Probability Cycles = 9.8000E10BS5500 Allowed Cycles(Curve F) = 3.0762E12Membrane-to-Bending Ratio = 2.886Bending-to-PL+PB+Q Ratio = 0.257Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 2.791 1.178 4.135Inplane : 0.862 0.779 1.277
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Outplane: 0.860 0.779 1.274Torsion : 0.691 0.790 1.024Pressure: 1.038 1.042 1.537
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 1.250 in.Pipe Thk: 0.287 in.Z approx: 0.209 cu.in.Z exact : 0.175 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial7.199 Inplane9.407 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.345 Inplane1.345 Outplane1.345 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 12613. 3302. 4953.Inplane Moment (in. lb.) 8244. 1788. 3794.Outplane Moment (in. lb.) 8265. 1793. 3803.Torsional Moment (in. lb.) 10275. 3152. 4729.Pressure (psi ) 500.37 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 22135. 4379. 6568.Inplane Moment (in. lb.) 6755. 1131. 2399.Outplane Moment (in. lb.) 6756. 1131. 2400.Torsional Moment (in. lb.) 6665. 1564. 2346.
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Pressure (psi ) 369.00 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 1.250 in.Wall Thickness = 0.287 in.
Axial Translational Stiffness = 580188. lb./in.Inplane Rotational Stiffness = 120031. in.lb./degOutplane Rotational Stiffness = 39951. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #7 (N7)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 0,5 Class 6000 - threadedNozzle orientation: 0°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 132 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 0,84 inNozzle nominal wall thickness: 0,33 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 6 inReinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,2888
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UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,231 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,231 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,2888
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,231 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,231 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:22:31 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 1.500 in.Thickness : 0.289 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 108.000 in.Distance from Bottom : 132.000 in.
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Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 900Number of Nodes = 4096Number of Elements = 1308Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -495. 0.2 0. 518840. 41635.3 0. 0. 0.4 0. 518840. 41635.5 0. 5102. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 519335. 41635.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4644. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.289 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4644. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.289 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4644. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.289 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4644. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.289 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 4644. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 17969. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.289 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 212,098 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:40% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 29,976 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:38% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 2497 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:1% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 211,652 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:38% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 2530 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 515,136 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:25% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 518,752 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:36% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 4548 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:1% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 511,978 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:19% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 5740 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:1% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 510,217 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 32,921,626.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2,562,633.WRC 474 99% Probability Cycles = 595,334.WRC 474 95% Probability Cycles = 826,559.BS5500 Allowed Cycles(Curve F) = 511,837.Membrane-to-Bending Ratio = 2.168Bending-to-PL+PB+Q Ratio = 0.316Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 512,658 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 744,660.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 3,387,799.WRC 474 99% Probability Cycles = 787,031.WRC 474 95% Probability Cycles = 1,092,709.BS5500 Allowed Cycles(Curve F) = 320,616.Membrane-to-Bending Ratio = 1.127Bending-to-PL+PB+Q Ratio = 0.470Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 5369 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2.0518E11WRC 474 99% Probability Cycles = 4.7666E10
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WRC 474 95% Probability Cycles = 6.6179E10BS5500 Allowed Cycles(Curve F) = 1.5564E12Membrane-to-Bending Ratio = 4.350Bending-to-PL+PB+Q Ratio = 0.187Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 55,989 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 8,975,190.WRC 474 99% Probability Cycles = 2,085,058.WRC 474 95% Probability Cycles = 2,894,881.BS5500 Allowed Cycles(Curve F) = 1,230,195.Membrane-to-Bending Ratio = 21.870Bending-to-PL+PB+Q Ratio = 0.044Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5370 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 8.3280E10WRC 474 99% Probability Cycles = 1.9347E10WRC 474 95% Probability Cycles = 2.6861E10BS5500 Allowed Cycles(Curve F) = 3.4257E11Membrane-to-Bending Ratio = 1.163Bending-to-PL+PB+Q Ratio = 0.462Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 3.510 1.320 5.200Inplane : 0.931 0.817 1.379
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Outplane: 0.931 0.817 1.379Torsion : 0.697 0.818 1.033Pressure: 1.082 1.035 1.603
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 1.500 in.Pipe Thk: 0.289 in.Z approx: 0.333 cu.in.Z exact : 0.284 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial7.229 Inplane9.446 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.589 Inplane1.589 Outplane1.589 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 12678. 3337. 5005.Inplane Moment (in. lb.) 10562. 2250. 4773.Outplane Moment (in. lb.) 10560. 2250. 4773.Torsional Moment (in. lb.) 14099. 4248. 6372.Pressure (psi ) 410.35 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 21354. 4346. 6520.Inplane Moment (in. lb.) 8910. 1299. 2756.Outplane Moment (in. lb.) 8911. 1300. 2759.Torsional Moment (in. lb.) 8900. 1816. 2724.
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Pressure (psi ) 371.54 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 1.500 in.Wall Thickness = 0.289 in.
Axial Translational Stiffness = 550315. lb./in.Inplane Rotational Stiffness = 81225. in.lb./degOutplane Rotational Stiffness = 34619. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #8 (N8)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,375 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 0,75 Class 6000 - threadedNozzle orientation: 0°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 144 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 1,05 inNozzle nominal wall thickness: 0,35 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 6 inReinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,3063
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UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,245 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,245 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,3063
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,245 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,245 0,375 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:23:23 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 1.750 in.Thickness : 0.306 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 96.000 in.Distance from Bottom : 144.000 in.
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Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 900Number of Nodes = 4024Number of Elements = 1284Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -568. 0.2 0. 594145. 47767.3 0. 0. 0.4 0. 594145. 47767.5 0. 7367. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 0. 594713. 47767.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.306 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 212,158 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:40% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 210,701 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:41% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 2599 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 211,583 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:38% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 2608 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 516,249 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:27% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 519,479 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:37% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 5668 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:1% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 512,182 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:20% 13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 51,017 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:1% 14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 510,968 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 8,509,863.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2,055,679.WRC 474 99% Probability Cycles = 477,562.WRC 474 95% Probability Cycles = 663,044.BS5500 Allowed Cycles(Curve F) = 413,678.Membrane-to-Bending Ratio = 2.066Bending-to-PL+PB+Q Ratio = 0.326Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 513,149 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 528,560.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2,877,451.WRC 474 99% Probability Cycles = 668,471.WRC 474 95% Probability Cycles = 928,101.BS5500 Allowed Cycles(Curve F) = 286,022.Membrane-to-Bending Ratio = 1.209Bending-to-PL+PB+Q Ratio = 0.453Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5451 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1.0890E11WRC 474 99% Probability Cycles = 2.5299E10
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WRC 474 95% Probability Cycles = 3.5124E10BS5500 Allowed Cycles(Curve F) = 5.7063E11Membrane-to-Bending Ratio = 1.304Bending-to-PL+PB+Q Ratio = 0.434Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 56,091 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 8,519,013.WRC 474 99% Probability Cycles = 1,979,082.WRC 474 95% Probability Cycles = 2,747,745.BS5500 Allowed Cycles(Curve F) = 1,169,486.Membrane-to-Bending Ratio = 16.704Bending-to-PL+PB+Q Ratio = 0.056Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5509 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2.9781E10WRC 474 99% Probability Cycles = 6.9186E9WRC 474 95% Probability Cycles = 9.6057E9BS5500 Allowed Cycles(Curve F) = 6.9891E10Membrane-to-Bending Ratio = 1.076Bending-to-PL+PB+Q Ratio = 0.482Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 4.425 1.710 6.555Inplane : 1.018 0.834 1.509
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Outplane: 1.024 0.834 1.517Torsion : 0.703 0.834 1.042Pressure: 1.124 1.040 1.665
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 1.750 in.Pipe Thk: 0.306 in.Z approx: 0.501 cu.in.Z exact : 0.432 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial7.670 Inplane10.022 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.881 Inplane1.881 Outplane1.881 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 12716. 3362. 5042.Inplane Moment (in. lb.) 14700. 3102. 6580.Outplane Moment (in. lb.) 14615. 3084. 6541.Torsional Moment (in. lb.) 21289. 6263. 9394.Pressure (psi ) 395.03 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 20840. 4045. 6068.Inplane Moment (in. lb.) 13292. 1842. 3908.Outplane Moment (in. lb.) 13295. 1844. 3912.Torsional Moment (in. lb.) 13293. 2582. 3873.
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Pressure (psi ) 359.11 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 1.750 in.Wall Thickness = 0.306 in.
Axial Translational Stiffness = 499580. lb./in.Inplane Rotational Stiffness = 75877. in.lb./degOutplane Rotational Stiffness = 34380. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Nozzle #9 (N9)
ASME Section VIII Division 1, 2010 Edition
tw(lower) = 0,25 inLeg41 = 0,375 in
Note: round inside edges per UG-76(c)
Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 0,75 Class 6000 - threadedNozzle orientation: 180°Local vessel minimum thickness: 0,5 inNozzle center line offset to datum line: 144 inEnd of nozzle to shell center: 45 inNozzle inside diameter, new: 1,05 inNozzle nominal wall thickness: 0,35 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 6 inReinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 300 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,3063
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UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,245 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,245 0,25 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary(in2)
For P = 257,73 psi @ 70 °F
UG-45 NozzleWall
ThicknessSummary (in)The nozzle passes
UG-45
Arequired
Aavailable A1 A2 A3 A5
Awelds treq tmin
This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0,0625 0,3063
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculationsper UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld description Required weldsize (in)
Actual weldsize (in) Status
Nozzle to shell fillet (Leg41) 0,245 0,2625 weld size is adequate
Nozzle to shell groove (Lower) 0,245 0,25 weld size is adequate
This opening does not require reinforcement per UG-36(c)(3)(a)
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Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed inaccordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Wed Feb 13 13:23:33 2013.
Model Notes• Load Case Report• Solution Data• ASME Code Stress Output Plots• Region Data• 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 : 78.000 in.Thickness : 0.500 in.Fillet Along Shell : 0.375 in.
Parent Properties:Cold Allowable : 20000.0 psiHot Allowable : 20000.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 70000.0 psiYield Strength (Amb) : 38000.0 psiYield Strength (Hot) : 33600.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in.(NOT USED)
Nozzle Outside Diameter : 1.750 in.Thickness : 0.306 in.Length : 6.250 in.Nozzle Weld Length : 0.375 in.Nozzle Tilt Angle : 0.000 deg.Distance from Top : 96.000 in.Distance from Bottom : 144.000 in.
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Nozzle PropertiesCold Allowable : 17100.0 psiHot Allowable : 17100.0 psiMaterial ID #2 : Low Alloy SteelUltimate Tensile (Amb) : 60000.0 psiYield Strength (Amb) : 35000.0 psiYield Strength (Hot) : 31000.0 psiElastic Modulus (Amb) : 29400000.0 psiPoissons Ratio : 0.300Weight Density : 0.2830E+00 lb./cu.in. (NOT USED)
Design Operating Cycles : 0.Ambient Temperature (Deg.) : 70.00
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 300.00 deg.Nozzle Outside Temperature : 300.00 deg.Vessel Inside Temperature : 300.00 deg.Vessel Outside Temperature : 300.00 deg.Nozzle Pressure : 150.0 psiVessel Pressure : 150.0 psi
No external forces or bending moments were included in this analysis.
Both ends of the model are "fixed," except that one endis free axially so that longitudinal pressure stressesmay be developed in the geometry.
Stresses will be calculated in the weld elements surroundingthe junction of the nozzle with the parent shell. This istypically done to get accurate values for the pressurestresses on the inside surface of the nozzle in thelongitudinal plane. The effect of any external loads willoveremphasized (too conservative) in this run.
Stresses are NOT averaged.
Vessel Centerline Vector : 0.000 0.000 1.000Nozzle Orientation Vector : 0.000 -1.000 0.000
Table of Contents
Load Case ReportInner and outer element temperatures are the samethroughout the model. No thermal ratchetingcalculations will be performed.
THE 10 LOAD CASES ANALYZED ARE:
1 WEIGHT ONLY
Weight ONLY case run to get the stress rangebetween the installed and the operating states.
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/-------- Loads in Case 1Loads due to Weight
2 SUSTAINED
Sustained case run to satisfy local primarymembrane and bending stress limits.
/-------- Loads in Case 2Loads due to WeightPressure Case 1
3 Thermal ONLY
Thermal ONLY case run in the event expansionstresses exceed the secondary stress allowable.
/-------- Loads in Case 3Temperature Case 1
4 OPERATING
Case run to compute the operating stresses used insecondary, peak and range calculations as needed.
/-------- Loads in Case 4Pressure Case 1Temperature Case 1Loads from (Operating)
5 EXPANSION (Fatigue Calc Performed)
Expansion case run to get the RANGE of stresses.
/-------- Combinations in Expansion Case 5Plus Stress Results from CASE 4Minus Stress Results from CASE 1
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 6Loads from (Axial)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 7Loads from (Inplane)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 8Loads from (Outplane)
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9 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 9Loads from (Torsion)
10 Program Generated -- Force Only
Case run to compute sif's and flexibilities./-------- Loads in Case 10Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 900Number of Nodes = 4024Number of Elements = 1284Number of Solution Cases = 9
Summation of Loads per Case
Case # FX FY FZ
1 0. -568. 0.2 -1. -595282. 47767.3 0. 0. 0.4 -1. -595282. 47767.5 0. -7367. 0.6 0. 0. 0.7 0. 0. 0.8 0. 0. 0.9 -1. -594713. 47767.
Table of Contents
ASME Code Stress Output Plots
1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
2) Qb < 3(Smh) (SUS,Bending) Case 2
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
6) Membrane < User (OPE,Membrane) Case 4
7) Bending < User (OPE,Bending) Case 4
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8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 9
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 10
13) Pl+Pb+Q < 3(Smavg) (EXP,Inside) Case 5
14) Pl+Pb+Q < 3(Smavg) (EXP,Outside) Case 5
15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.350
Branch Next to Header Weld
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Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psi
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Smallest Thickness ....... 0.306 in.Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 20000. psiHot Allowable @ 300 deg .. 20000. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.000
Branch away from Junction
Cold Allowable ........... 17100. psiHot Allowable @ 300 deg .. 17100. psiCase 2Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 4Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 5Nominal Stress (M/Z) ... 0. psiPressure Stress (Pd/2t) .. 11700. psiCase 6Nominal Stress (M/Z) ... 5303. psiPressure Stress (Pd/2t) .. 0. psiCase 7Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 8Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 9
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Nominal Stress (M/Z) ... 17044. psiPressure Stress (Pd/2t) .. 0. psiCase 10Nominal Stress (M/Z) ... 11700. psiPressure Stress (Pd/2t) .. 0. psiSmallest Thickness ....... 0.306 in.Stress Concentration ..... 1.000
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl 1.5(k)Smh Primary Membrane Load Case 212,186 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:40% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Next to Header Weld
Pl 1.5(k)Smh Primary Membrane Load Case 210,727 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:41% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Branch Transition
Pl 1.5(k)Smh Primary Membrane Load Case 2598 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Header away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 211,607 30,000 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:38% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
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Branch away from Junction
Pl 1.5(k)Smh Primary Membrane Load Case 2607 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133,psi psi Fig. 4-130.1, Table 4-120.1Plot Reference:2% 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 2
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 416,258 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:27% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Next to Header Weld
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 419,505 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:38% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch Transition
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 4671 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:1% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Header away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 412,189 60,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)Plot Reference:20% 4) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 4
Branch away from Junction
Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 41,020 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6,psi psi Fig. 4-130.1(Note 1)
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Plot Reference:1% 5) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 4
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 510,968 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 8,511,470.0% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2,055,766.WRC 474 99% Probability Cycles = 477,582.WRC 474 95% Probability Cycles = 663,072.BS5500 Allowed Cycles(Curve F) = 413,690.Membrane-to-Bending Ratio = 2.065Bending-to-PL+PB+Q Ratio = 0.326Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Next to Header Weld
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 513,149 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 528,553.0% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2,877,438.WRC 474 99% Probability Cycles = 668,468.WRC 474 95% Probability Cycles = 928,096.BS5500 Allowed Cycles(Curve F) = 286,021.Membrane-to-Bending Ratio = 1.209Bending-to-PL+PB+Q Ratio = 0.453Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch Transition
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5451 1,799,215 Stress Concentration Factor = 1.350psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 1.0890E11WRC 474 99% Probability Cycles = 2.5299E10
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WRC 474 95% Probability Cycles = 3.5125E10BS5500 Allowed Cycles(Curve F) = 5.7063E11Membrane-to-Bending Ratio = 1.304Bending-to-PL+PB+Q Ratio = 0.434Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Header away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 56,091 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 50000.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 8,519,488.WRC 474 99% Probability Cycles = 1,979,192.WRC 474 95% Probability Cycles = 2,747,898.BS5500 Allowed Cycles(Curve F) = 1,169,552.Membrane-to-Bending Ratio = 16.722Bending-to-PL+PB+Q Ratio = 0.056Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:15) Pl+Pb+Q+F < Sa (EXP,Inside) Case 5
Branch away from Junction
Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 5509 1,799,215 Stress Concentration Factor = 1.000psi psi Strain Concentration Factor = 1.000Cycles Allowed for this Stress = 1.0000E110% "B31" Fatigue Stress Allowable = 42750.0Markl Fatigue Stress Allowable = 245000.0WRC 474 Mean Cycles to Failure = 2.9781E10WRC 474 99% Probability Cycles = 6.9184E9WRC 474 95% Probability Cycles = 9.6055E9BS5500 Allowed Cycles(Curve F) = 6.9888E10Membrane-to-Bending Ratio = 1.076Bending-to-PL+PB+Q Ratio = 0.482Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135Plot Reference:16) Pl+Pb+Q+F < Sa (EXP,Outside) Case 5
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary SecondaryAxial : 4.425 1.710 6.555Inplane : 1.018 0.834 1.509
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Outplane: 1.024 0.834 1.517Torsion : 0.703 0.834 1.042Pressure: 1.124 1.040 1.665
The above stress intensification factors are to be usedin a beam-type analysis of the piping system. Inplane,Outplane and Torsional sif's should be used with thematching branch pipe whose diameter and thickness is givenbelow. The axial sif should be used to intensify theaxial stress in the branch pipe calculated by F/A. Thepressure sif should be used to intensify the nominalpressure stress in the PARENT or HEADER, calculatedfrom PD/2T.
Pipe OD : 1.750 in.Pipe Thk: 0.306 in.Z approx: 0.501 cu.in.Z exact : 0.432 cu.in.
B31.3Peak Stress Sif .... 0.000 Axial7.670 Inplane10.022 Outplane1.000 TorsionalB31.1Peak Stress Sif .... 0.000 Axial1.881 Inplane1.881 Outplane1.881 TorsionalWRC 330Peak Stress Sif .... 0.000 Axial1.500 Inplane1.500 Outplane1.000 Torsional
Table of Contents
Allowable Loads
SECONDARY Maximum Conservative RealisticLoad Type (Range): Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 12715. 3361. 5042.Inplane Moment (in. lb.) 14700. 3102. 6580.Outplane Moment (in. lb.) 14616. 3084. 6542.Torsional Moment (in. lb.) 21289. 6263. 9394.Pressure (psi ) 395.03 150.00 150.00
PRIMARY Maximum Conservative RealisticLoad Type: Individual Simultaneous SimultaneousOccuring Occuring OccuringAxial Force (lb. ) 20839. 4045. 6067.Inplane Moment (in. lb.) 13292. 1842. 3908.Outplane Moment (in. lb.) 13295. 1844. 3912.Torsional Moment (in. lb.) 13293. 2582. 3873.
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Pressure (psi ) 359.11 150.00 150.00
NOTES:
1) Maximum Individual Occuring Loads are the maximumallowed values of the respective loads if all otherload components are zero, i.e. the listed axial forcemay be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads arethe maximum loads that can be applied simultaneously.A conservative stress combination equation is usedthat typically produces stresses within 50-70% of theallowable stress.
3) The Realistic Allowable Simultaneous loads are themaximum loads that can be applied simultaneously. Amore realistic stress combination equation is usedbased on experience at Paulin Research. Stresses aretypically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansionand operating piping loads.
5) Primary allowable loads are limits for weight,primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,"beam-type" analysis of the intersection. The stiff-nesses should be inserted at the surface of thebranch/header or nozzle/vessel junction. The generalcharacteristics used for the branch pipe should be:
Outside Diameter = 1.750 in.Wall Thickness = 0.306 in.
Axial Translational Stiffness = 499578. lb./in.Inplane Rotational Stiffness = 75863. in.lb./degOutplane Rotational Stiffness = 34384. in.lb./deg
The following stiffness(es) were not generated becauseof errors in input or because the finite element modelis stiffer than the piping model.
Torsional Rotational Stiffness
Table of Contents
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Finite Element Model
Finite Element Model•
Elements at Discontinuity
1) Pl < 1.5(k)Smh (SUS Membrane) Case 2• 2) Qb < 3(Smh) (SUS Bending) Case 2• 3) S1+S2+S3 < 4S (SUS S1+S2+S3) Case 2• 4) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 4• 5) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 4• 6) Membrane < User (OPE Membrane) Case 4• 7) Bending < User (OPE Bending) Case 4• 13) Pl+Pb+Q < 3(Smavg) (EXP Inside) Case 5• 14) Pl+Pb+Q < 3(Smavg) (EXP Outside) Case 5• 15) Pl+Pb+Q+F < Sa (EXP Inside) Case 5• 16) Pl+Pb+Q+F < Sa (EXP Outside) Case 5• 8) Pl+Pb+Q+F < Sa (SIF Outside) Case 6• 9) Pl+Pb+Q+F < Sa (SIF Outside) Case 7• 10) Pl+Pb+Q+F < Sa (SIF Outside) Case 8• 11) Pl+Pb+Q+F < Sa (SIF Outside) Case 9• 12) Pl+Pb+Q+F < Sa (SIF Outside) Case 10•
Tabular Results
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Saddle #2
Saddle material: A-36
Saddle construction is: Web at edge ofrib
Saddle allowable stress: Ss = 20.000 psiSaddle yield stress: Sy = 38.000 psiSaddle distance to datum: 36 inTangent to tangent length: L = 244 inSaddle separation: Ls = 168 inVessel radius: R = 39 inTangent distance left: Al = 38 inTangent distance right: Ar = 38 inSaddle height: Hs = 57 inSaddle contact angle: θ = 120 °Wear plate thickness: tp = 0,375 inWear plate width: Wp = 10 inWear plate contact angle: θw = 130 °Web plate thickness: ts = 0,5 inBase plate length: E = 69 inBase plate width: F = 8 inBase plate thickness: tb = 0,5625 inNumber of stiffener ribs: n = 4Largest stiffener rib spacing: di = 22,5 inStiffener rib thickness: tw = 0,5 inSaddle width: B = 8 in
Anchor bolt size & type: 1 inch series 8threaded
Anchor bolt material:Anchor bolt allowable shear: 15.000 psiAnchor bolt corrosion allowance: 0 inAnchor bolts per saddle: 2Base coefficient of friction: µ = 0,45
Weight on left saddle: operating corr =5.768 lb, test new =28.445 lbWeight on right saddle: operating corr =5.173 lb, test new =27.861 lbWeight of saddle pair =1.052 lb
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Notes:(1) Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels onTwo Saddle Supports" by L.P. Zick.
Load Vesselcondition
Bending + pressurebetween saddles
(psi)
Bending + pressure atthe saddle
(psi)
S1(+)
allow(+)
S1(-)
allow(-)
S2(+)
allow(+)
S2(-)
allow(-)
Weight Operating 6.237 20.000 47 14.078 6.341 20.000 151 14.078
Weight Test 8.396 34.200 231 14.078 8.944 34.200 778 14.078
Load Vesselcondition
Tangentialshear (psi)
Circumferentialstress (psi)
Stressover
saddle(psi)
Splitting(psi)
S3 allow S4(horns)
allow(+/-) S5 allow S6 allow
Weight Operating 223 16.000 -2.427 30.000 521 16.800 115 13.333
Weight Test 1.075 27.360 -11.970 34.200 2.571 34.200 565 34.200
Longitudinal stress between saddles (Weight ,Operating, left saddle loading and geometry govern)
S1 = +- 3*K1*Q*(L / 12) / (π*R2*t)= 3*0,314*5.768*(244 / 12) / (π*38,752*0,5)= 47 psi
Sp = P*R / (2*t)= 160,77*38,5 / (2*0,5)= 6.190 psi
Maximum tensile stress S1t = S1 + Sp = 6.237 psiMaximum compressive stress (shut down) S1c = S1 = 47 psi
Tensile stress is acceptable (<=1*S*E = 20.000 psi)Compressive stress is acceptable (<=1*Sc = 14.078 psi)
Longitudinal stress at the left saddle (Weight ,Operating)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*19,7435 / 3 + 244 + 2*19,7435 / 3= 270,3247 in
w = Wt / Le = 10.941 / 270,3247 = 40,47 lbf/in
Bending moment at the left saddle:
Mq = w*(2*H*Al / 3 + Al2 / 2 - (R2 - H2) / 4)
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= 40,47*(2*19,7435*38 / 3 + 382 / 2 - (392 - 19,74352) / 4)= 38.019,6 lbf-in
S2 = +- Mq*K1' / (π*R2*t)= 38.019,6*9,3799 / (π*38,752*0,5)= 151 psi
Sp = P*R / (2*t)= 160,77*38,5 / (2*0,5)= 6.190 psi
Maximum tensile stress S2t = S2 + Sp = 6.341 psiMaximum compressive stress (shut down) S2c = S2 = 151 psi
Tensile stress is acceptable (<=1*S = 20.000 psi)Compressive stress is acceptable (<=1*Sc = 14.078 psi)
Tangential shear stress in the shell (left saddle, Weight ,Operating)
Qshear = Q - w*(a + 2*H / 3)= 5.768 - 40,47*(38 + 2*19,7435 / 3)= 3.697,28 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*3.697,28 / (38,75*0,5)= 223 psi
Tangential shear stress is acceptable (<= 0.8*S = 16.000 psi)
Circumferential stress at the left saddle horns (Weight ,Operating)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -5.768 / (4*0,5*(8+1,56*Sqr(39*0,5))) - 12*0,0508*5.768*38,75 / (244*0,52)= -2.427 psi
Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 30.000 psi)The wear plate was not considered in the calculation of S4 because the wear plate contact angle did not exceed thesaddle contact angle by at least 11,46° and the wear plate width is not at least {B + 1,56*(Rotc)0,5} =14,8888 in
Ring compression in shell over left saddle (Weight ,Operating)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,7603*5.768 / ((0,5 + 0,375)*(0,5 + 1,56*Sqr(39*0,875)))= 521 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 16.800 psi)
Saddle splitting load (left, Weight ,Operating)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 13*0,5 + 0,375*10= 10,25 in2
S6 = K8*Q / Ae= 0,2035*5.768 / 10,25
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= 115 psi
Stress in saddle is acceptable (<= (2 / 3)*Ss = 13.333 psi)
Shear stress in anchor bolting, one end slotted
Maximum seismic or wind base shear = 0 lbf
Thermal expansion base shear = W*µ = 6.294*0,45 = 2.832,3 lbf
Corroded root area for a 1 inch series 8 threaded bolt = 0,551 in2 ( 2 per saddle )
Bolt shear stress = 2.832,3 / (0,551*2) = 2.570 psi
Anchor bolt stress is acceptable (<= 15.000 psi)
Web plate buckling check (Escoe pg 251)
Allowable compressive stress Sc is the lesser of 20.000 or 16.568 psi: (16.568)
Sc = Ki*π2*E / (12*(1 - 0,32)*(di / ts)2)= 1,28*π2*29E+06 / (12*(1 - 0,32)*(22,5 / 0,5)2)= 16.568 psi
Allowable compressive load on the saddle
be = di*ts / (di*ts + 2*tw*(b - 1))= 22,5*0,5 / (22,5*0,5 + 2*0,5*(8 - 1))= 0,6164
Fb = n*(As + 2*be*ts)*Sc= 4*(3,75 + 2*0,6164*0,5)*16.568= 289.365,91 lbf
Saddle loading of 28.971 lbf is <= Fb; satisfactory.
Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted)σb = V*(Hs - xo)*y / I + Q / A= 0*(57 - 32,2527)*5,4423 / 172,08 + 5.768 / 48,775= 118 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 onesaddle slotted)σb = V*(Hs - xo)*y / I + Q / A= 2.832,3*(57 - 32,2527)*5,4423 / 172,08 + 5.768 / 48,775= 2.335 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 = 22,5, b = 7,5 in
tb = (β1*q*b2 / (1,5*Sa))0,5
= (2,45*52*7,52 / (1,5*20.000))0,5
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= 0,491 in
The base plate thickness of 0,5625 in is adequate.
Foundation bearing check
Sf = Qmax / (F*E)= 28.971 / (8*69)= 52 psi
Concrete bearing stress ≤ 1.658 psi ; satisfactory.
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