Ingenieria Strycon Cra 13 # 35 - 43 COMPRESS Pressure Vessel Design Calculations Item: Separador Primario Vessel No: V-90 Customer: Plant process Equipment INC. Contract: - Designer: Carlos Alvarez Date: 13/02/2013 Location: Servicios Auxiliares y varios - Proyecto Star Purchaser: PACIFIC RUBIALES Vessel Name: Comp1.CW7 Service: Separador Primario Tag Number: 341-V-90 You can edit this page by selecting Cover Page settings... in the report menu.
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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
You can edit this page by selecting Cover Page settings... in the report menu.
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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
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
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
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
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
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
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
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
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.
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.
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
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.
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.
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.
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.
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.
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.
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.
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.
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.
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.
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)
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.
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.
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.
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.
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.
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.
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
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.
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.
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.
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.
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
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.
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.
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.
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.
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
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.
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.
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.
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.
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
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.
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.
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.
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.
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
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.
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.
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)
267/345
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.
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.
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
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.
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.
279/345
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.
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.
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.
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
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.
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.
304/345
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.
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
305/345
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
316/345
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)
317/345
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.
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.
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
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.
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.
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.
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)