cover page deficiencies summary - custom eng · cylinder #1 sa-516 70 36.00 od 44.00 0.1875 0.1368...
TRANSCRIPT
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Concast
Index
Cover Page
Deficiencies SummaryNozzle ScheduleNozzle SummaryPressure SummaryRevision HistorySettings SummaryThickness SummaryWeight SummaryHydrostatic TestVacuum Summary
Cylinder #1
Top HeadStraight Flange on Top HeadStraight Flange on Bottom HeadBottom Head
Nozzle #1 (N1)Nozzle #2 (N2)Nozzle #3 (N3)Nozzle #4 (N4)
Legs
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Cover Page
Cover Page
Custom Engineering2800 McClelland Ave
Erie, PA 16510
COMPRESS Pressure Vessel Design Calculations
Item: Pressure Vessel Vessel No: Customer: Customer #2 Contract: WO# 7220
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Cover Page
Designer: George Clark Date: 1/14/04
Location: New Castle Purchaser: Concast America, Inc.
Vessel Name: Comp2
You can edit this page by selecting Cover Page settings... in the report menu.
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Deficiencies Summary
Deficiencies Summary
Warnings Summary
Warnings for Nozzle #2 (N2)A full penetration groove weld would qualify this nozzle as integral reinforcment likely reducing the reinforcement required. (warning)
Warnings for Nozzle #3 (N3)A full penetration groove weld would qualify this nozzle as integral reinforcment likely reducing the reinforcement required. (warning)
ASME B16.5 / B16.47 Flange Warnings Summary
ASME B16.5 / 16.47 Flanges with Warnings
Flange Applicable Warnings
Nozzle #1 (N1) 1
Nozzle #2 (N2) 1
Nozzle #3 (N3) 1
Nozzle #4 (N4) 1
ASME B16.5 / 16.47 Flange Warnings
No. Warning
1 For Class 150 flanges, ASME B16.5 para. 5.4.2 recommends gaskets to be in accordance with Fig. E1, Group No. I.
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Nozzle Schedule
Nozzle Schedule
Nozzlemark Service Size
Materials
Nozzle Impact Norm Fine Grain Pad Impact Norm
Fine Grain Flange
N1 Nozzle #1
1.500" Sch 40 (Std)
SA-106 B Smls pipe
No No No N/A N/A N/A N/AWN A105 150#
N2 Nozzle #2
1.500" Sch 40 (Std)
SA-106 B Smls pipe
No No No N/A N/A N/A N/AWN A105 150#
N3 Nozzle #3
1.500" Sch 40 (Std)
SA-106 B Smls pipe
No No No N/A N/A N/A N/AWN A105 150#
N4 Nozzle #4
6" Sch 40 (Std)
SA-106 B Smls pipe
No No No N/A N/A N/A N/AWN A105 150#
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Nozzle Summary
Nozzle Summary
Nozzlemark
OD(in)
tn(in)
Req tn(in)
A1? A2? Shell
ReinforcementPad Corr
(in) Aa/Ar(%)Nom t
(in) Design t(in)
User t(in)
Width(in)
tpad(in)
N1 1.90 0.1450 0.1450 Yes Yes 0.1875 N/A N/A N/A 0.0000 Exempt
N2 1.90 0.1450 0.1450 Yes Yes 0.1875 N/A N/A N/A 0.0000 Exempt
N3 1.90 0.1450 0.1450 Yes Yes 0.1875 N/A N/A N/A 0.0000 Exempt
N4 6.63 0.2800 0.1279 Yes Yes 0.1875 0.1500 N/A N/A 0.0000 100.0
tn: Nozzle thickness
Req tn: Nozzle thickness required per UG-45/UG-16
Nom t: Vessel wall thickness
Design t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37
User t: Local vessel wall thickness (near opening)
Aa: Area available per UG-37, governing condition
Ar: Area required per UG-37, governing condition
Corr: Corrosion allowance on nozzle wall
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Pressure Summary
Pressure Summary
Pressure Summary for Chamber bounded by Bottom Head and Top Head
Identifier P
Design( psi)
TDesign
(°F)
MAWP( psi)
MAP( psi)
MAEP( psi)
Teexternal
(°F)
MDMT Rating Total CorrosionAllowance
(in)
ImpactTestMDMT
(°F) Exemption
Top Head 100.0 150.0 178.28 178.28 61.33 150.0 -55.0 Note 1 0.000 No
Straight Flange on Top Head
100.0 150.0 177.35 177.35 33.07 150.0 -55.0 Note 2 0.000 No
Cylinder #1 100.0 150.0 146.44 146.44 33.33 150.0 -55.0 Note 3 0.000 No
Straight Flange on Bottom Head
100.0 150.0 177.35 177.35 33.07 150.0 -55.0 Note 2 0.000 No
Bottom Head
100.0 150.0 178.28 178.28 61.33 150.0 -55.0 Note 4 0.000 No
Legs 100.0 150.0 100.00 N/A N/A N/A N/A N/A N/A N/A
Nozzle #1 (N1)
100.0 150.0 209.14 209.14 33.33 150.0 -55.0 Note 5 0.000 No
Nozzle #2 (N2)
100.0 150.0 209.14 209.14 33.33 150.0 -55.0 Note 5 0.000 No
Nozzle #3 (N3)
100.0 150.0 209.14 209.14 33.33 150.0 -55.0 Note 5 0.000 No
Nozzle #4 (N4)
100.0 150.0 124.70 124.70 18.93 150.0 -55.0 Note 6 0.000 No
Chamber design MDMT is -20.00°FChamber rated MDMT is -55.00°F @ 100.00 psi
Chamber MAWP hot & corroded is 100.00 psi @ 150.0°F
Chamber MAP cold & new is 124.70 psi @ 70.0°F
Chamber MAEP is 18.93 psi @ 150.0°F
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Pressure Summary
Vacuum rings did not govern the external pressure rating.
Notes for MDMT Rating:
Note # Exemption Details
1. Straight Flange governs MDMT
2.
Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 65.5 °F, (coincident ratio = 0.4801537)Rated MDMT is governed by UCS-66(b)(2)
UCS-66 governing thickness = 0.187 in
3.
Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 48.7 °F, (coincident ratio = 0.5470086)Rated MDMT is governed by UCS-66(b)(2)
UCS-66 governing thickness = 0.1875 in
4. Straight Flange governs MDMT
5. Flange rating governs: UCS-66(b)(1)(b)
6.
Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 65.7 °F, (coincident ratio = 0.47904)Rated MDMT is governed by UCS-66(b)(2)
UCS-66 governing thickness = 0.1875 in.
Design notes are available on the Settings Summary page.
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Revision History
Revision History
No. Date Operator Notes
0 3/12/2004 george New vessel created with Vessel Wizard, ASME Division 1 [Build 6229]
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Settings Summary
Settings Summary
COMPRESS Build 6242
Units: English
Datum Line Location: 0.00" from bottom seam
Design
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
Design or Rating: Get Thickness from Pressure
Minimum thickness: 1/16" per UG-16(b)
Design for cold shut down only: No
Design for lethal service (full radiography required): No
Design nozzles for: Design P, find nozzle MAWP and MAP
Corrosion weight loss: 100% of theoretical loss
UG-23 Stress Increase: 1.20
Skirt/legs stress increase: 1.3
Minimum nozzle projection: 4.0000"
Juncture calculations for α > 30 only: Yes Preheat P-No 1 Materials > 1.25" and
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Settings Summary
Apply interpretation VIII-1-01-37: Yes
Disallow UG-20(f) exemptions: No
UG-22 Loadings
UG-22 (a) Internal or External Design Pressure : Yes
UG-22 (b) Weight of the vessel and normal contents under operating or test conditions: Yes
UG-22 (c) Superimposed static reactions from weight of attached equipment (external loads): No
UG-22 (d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: Yes
UG-22 (f) Wind reactions: No
UG-22 (f) Seismic reactions: No
Note: UG-22 (b),(c) and (f) loads only considered when supports are present.
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Thickness Summary
Thickness Summary
ComponentIdentifier Material
Diameter(in)
Length(in)
Nominal t(in)
Design t(in)
JointE Load
Top Head SA-516 70 36.00 OD 9.09 0.1870* 0.1054 0.8500 Internal
Straight Flange on Top Head SA-516 70 36.00 OD 2.00 0.1870 0.1368 0.8500 External
Cylinder #1 SA-516 70 36.00 OD 44.00 0.1875 0.1368 0.7000 External
Straight Flange on Bottom Head SA-516 70 36.00 OD 2.00 0.1870 0.1368 0.8500 External
Bottom Head SA-516 70 36.00 OD 9.09 0.1870* 0.1054 0.8500 Internal
Nominal t: Vessel wall nominal thickness
Design t: Required vessel thickness due to governing loading + corrosion
Joint E: Longitudinal seam joint efficiency
* Head minimum thickness after forming
Load
internal: Circumferential stress due to internal pressure governs
external: External pressure governs
Wind: Combined longitudinal stress of pressure + weight + wind governs
Seismic: Combined longitudinal stress of pressure + weight + seismic governs
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Weight Summary
Weight Summary
Component
Weight ( lb) Contributed by Vessel Elements
MetalNew*
MetalCorroded*
Insulation &Supports
Lining Piping
+ Liquid Operating
Liquid Test
Liquid
Top Head 90.30 90.30 0.00 0.00 0.00 0.00 285.62
Cylinder #1 260.40 260.40 0.00 0.00 0.00 0.00 1,586.39
Bottom Head 90.30 90.30 0.00 0.00 0.00 0.00 285.62
Legs 37.36 37.36 0.00 0.00 0.00 0.00 0.00
TOTAL: 478.36 478.36 0.00 0.00 0.00 0.00 2,157.63
* Shells with attached nozzles have weight reduced by material cut out for opening.
Component
Weight ( lb) Contributed by Attachments
Body Flanges Nozzles &
Flanges PackedBeds
Ladders &Platforms
Trays &Supports
Rings &
Clips
VerticalLoads
New Corroded New Corroded
Top Head 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00
Cylinder #1 0.00 0.00 43.00 43.00 0.00 0.00 0.00 0.00 0.00
Bottom Head 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00
Legs 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00
TOTAL: 0.00 0.00 43.00 43.00 0.00 0.00 0.00 0.00 0.00
Vessel operating weight, Corroded: 521 lbVessel operating weight, New: 521 lbVessel empty weight, Corroded: 521 lbVessel empty weight, New: 521 lbVessel test weight, New: 2,679 lb
Vessel center of gravity location (from datum)
Vessel Lift Weight, New: 521 lbCenter of Gravity: 20.19"
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Weight Summary
Vessel Capacity
Vessel Capacity** (New): 258 US galVessel Capacity** (Corroded): 258 US gal**The vessel capacity does not include volume of nozzle, piping or other attachments.
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Hydrostatic Test
Hydrostatic Test
Shop test pressure determination for Chamber bounded by Bottom Head and Top Head based on MAWP per UG-99(b)
Shop hydrostatic test gauge pressure is 130.000 psi at 70.00 °F (the chamber MAWP = 100.000 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
Stressduring test
psi
Allowabletest stress
psi
Stressexcessive?
Top Head (1) 131.509 1.509 1.0000 1.30 11,274 34,200 No
Straight Flange on Top Head
131.509 1.509 1.0000 1.30 12,593 34,200 No
Cylinder #1 131.509 1.509 1.0000 1.30 12,559 34,200 No
Straight Flange on Bottom Head
131.509 1.509 1.0000 1.30 12,593 34,200 No
Bottom Head 131.509 1.509 1.0000 1.30 11,274 34,200 No
Nozzle #1 (N1) 130.217 0.217 1.0000 1.30 17,887 47,250 No
Nozzle #2 (N2) 130.284 0.284 1.0000 1.30 17,896 47,250 No
Nozzle #3 (N3) 130.284 0.284 1.0000 1.30 17,896 47,250 No
Nozzle #4 (N4) 130.217 0.217 1.0000 1.30 27,307 47,250 No
Notes:(1) Top Head limits the UG-99 stress ratio.(2) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399,
pages 77-82.(3) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress.(4) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange.
The field test condition has not been investigated for the Chamber bounded by Bottom Head and Top Head.
The test temperature of 70.00 °F is warmer than the minimum recommended temperature of -25.00 °F so the brittle fracture provision of UG-99(h) has been met.
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Hydrostatic Test
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Vacuum Summary
Vacuum Summary
Component Line of Support Elevationabove Datum(in)
Length Le(in)
Top Head - 55.09 N/A
- 1/3 depth of Top Head 48.97 N/A
Straight Flange on Top Head Top - 46.00 53.94
Straight Flange on Top Head Bottom - 44.00 53.94
Cylinder #1 Top - 44.00 53.94
Cylinder #1 Bottom - 0.00 53.94
Straight Flange on Bottom Head Top - 0.00 53.94
Straight Flange on Bottom Head Bottom - -2.00 53.94
- 1/3 depth of Bottom Head -4.97 N/A
Bottom Head - -11.09 N/A
Note
For main components, the listed value of 'Le' is the largest unsupported length for the component.
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Cylinder #1
Cylinder #1
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
Component: CylinderMaterial specification: SA-516 70 (ASME II-D p. 14, ln. 31)Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 48.7 °F, (coincident ratio = 0.5470086)Rated MDMT is governed by UCS-66(b)(2)UCS-66 governing thickness = 0.1875 in
Internal design pressure: P = 100 psi @ 150°FExternal design pressure: Pe = 15 psi @ 150°F
Static liquid head:
Pth=1.5093 psi(SG=1.0000, Hs=41.8125", Horizontal test head)
Corrosion allowance: Inner C = 0.0000" Outer C = 0.0000"
Design MDMT = -20.00°F No impact test performedRated MDMT = -55.00°F Material is not normalized
Material is not produced to Fine Grain PracticePWHT is not performed
Radiography: Longitudinal joint - None UW-11(c) Type 1Top circumferential joint - None UW-11(c) Type 1Bottom circumferential joint - None UW-11(c) Type 1
Estimated weight: New = 262.6787 lb corr = 262.6787 lbCapacity: New = 189.8630 gal corr = 189.8630 gal
OD = 36.0000"Length Lc = 44.0000"
t = 0.1875"
Design thickness, (at 150.00°F) Appendix 1-1
t = P*Ro/(S*E + 0.40*P) + Corrosion
= 100.0000*18.0000/(20000.0000*0.70 + 0.40*100.0000) + 0.0000
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Cylinder #1
= 0.1283"
Maximum allowable working pressure, (at 150.00°F) Appendix 1-1
P = S*E*t/(Ro - 0.40*t) - Ps= 20000.0000*0.70*0.1875 / (18.0000 - 0.40*0.1875) - 0.0000= 146.4435 psi
Maximum allowable pressure, (at 70.00°F) Appendix 1-1
P = S*E*t/(Ro - 0.40*t)
= 20000.0000*0.70*0.1875 / (18.0000 - 0.40*0.1875)= 146.4435 psi
External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 53.9377/36.0000 = 1.4983
Do/t = 36.0000/0.136839 = 263.0834
From table G: A = 0.000206
From table CS-2: B = 2959.6812
Pa = 4*B/(3*(Do/t))
= 4*2959.6812/(3*(36.0000/0.136839))
= 15.0000 psi
Design thickness for external pressure Pa = 15.0000 psi
= t + Corrosion = 0.136839 + 0.0000 = 0.1368"
Maximum Allowable External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 53.9377/36.0000 = 1.4983
Do/t = 36.0000/0.1875 = 192.0000
From table G: A = 0.000334
From table CS-2: B = 4799.8105
Pa = 4*B/(3*(Do/t))
= 4*4799.8105/(3*(36.0000/0.1875))
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Cylinder #1
= 33.3320 psi
% Extreme fiber elongation - UCS-79(d)
= (50 * t / Rf) * (1 - Rf / Ro)
= (50 * 0.1875 / 17.9063) * (1 - 17.9063 / ∞)= 0.5236 %
External Pressure + Weight Check (Bergman, ASME paper 54-A-104)
Pv = W / (2*π*Rm) + M / (π*Rm2)
= 390.01 / (2*π*17.9063) + 1003.47 / (π*17.90632)= 4.4627 lb/in
α = Pv / (Pe*Do)
= 4.462692 / (15.0000*36.0000)
= 0.0083
n = 5
m = 1.23 / (L/Do)2
= 1.23 / (53.937668/36.0000)2
= 0.5479
Ratio Pe = (n2 - 1 + m + m*α) / (n2 - 1 + m)= (52 - 1 + 0.547931 + 0.547931*0.008264) / (52 - 1 + 0.547931)
= 1.0002
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight Check at Bottom Seam (Bergman, ASME paper 54-A-104)
Pv = W / (2*π*Rm) + M / (π*Rm2)
= 390.01 / (2*π*17.9063) + 0.00 / (π*17.90632)= 3.4665 lb/in
α = Pv / (Pe*Do)
= 3.466493 / (15.0000*36.0000)
= 0.0064
n = 5
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Cylinder #1
m = 1.23 / (L/Do)2
= 1.23 / (53.937668/36.0000)2
= 0.5479
Ratio Pe = (n2 - 1 + m + m*α) / (n2 - 1 + m)= (52 - 1 + 0.547931 + 0.547931*0.006419) / (52 - 1 + 0.547931)
= 1.0001
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
Design thickness = 0.1368"
The governing condition is due to external pressure.
The cylinder thickness of 0.1875" is adequate.
Thickness Required Due to Pressure + External Loads
ConditionPressure P ( psi)
Allowable Stress Before UG-23 Stress Increase
( psi)Temperature
(°F)Corrosion
C (in)Location Load
Req'd Thk
Due to Tension
(in)
Req'd Thk Due to
Compression (in)
St Sc
Operating, Hot & Corroded
100.00 20000.00 13265.59 150.00 0.0000top Weight 0.0444 0.0443
Bottom Weight 0.0443 0.0443
Operating, Hot & New
100.00 20000.00 13265.59 150.00 0.0000top Weight 0.0444 0.0443
Bottom Weight 0.0443 0.0443
Hot Shut Down, Corroded
0.00 20000.00 13265.59 150.00 0.0000top Weight 0.0002 0.0003
Bottom Weight 0.0003 0.0003
Hot Shut Down, New
0.00 20000.00 13265.59 150.00 0.0000top Weight 0.0002 0.0003
Bottom Weight 0.0003 0.0003
Empty, Corroded
0.00 20000.00 13265.59 0.00 0.0000top Weight 0.0002 0.0003
Bottom Weight 0.0003 0.0003
Empty, top Weight 0.0002 0.0003
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Cylinder #1
New 0.00 20000.00 13265.59 0.00 0.0000 Bottom Weight 0.0003 0.0003
Vacuum -15.00 20000.00 13265.59 150.00 0.0000top Weight 0.0103 0.0104
Bottom Weight 0.0103 0.0103
Hot Shut Down, Corroded, Weight & Eccentric Moments Only
0.00 20000.00 13265.59 150.00 0.0000
top Weight 0.0000 0.0001
Bottom Weight 0.0000 0.0000
Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1875)
= 0.001302
B = 13265.5928 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScHC = 13265.5928 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 13265.5928 psi
Allowable Compressive Stress, Cold and New- ScCN, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1875)
= 0.001302
B = 13265.5928 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
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Cylinder #1
ScCN = 13265.5928 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 13265.5928 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1875)
= 0.001302
B = 13265.5928 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScVC = 13265.5928 psi
Operating, Hot & Corroded, Above Support Point
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|)
= 0.0445"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 1003.47/(π*17.90632*20000.0000*1.0000*1.00)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 390.01/(2*π*17.9063*20000.0000*1.0000*1.00)= 0.0002"
tt = tp + tm - tw (total required, tensile)
= 0.044487 + 0.000050 - (0.000173)
= 0.0444"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000050 + (0.000173) - (0.044487)|
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Cylinder #1
= 0.0443"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*1.00*(0.1875-0.000050+(0.000173)) / (17.8125 - 0.40*(0.1875-0.000050+(0.000173)))
= 423.1127 psi
Operating, Hot & New, Above Support Point
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|)
= 0.0445"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 1003.47/(π*17.90632*20000.0000*1.0000*1.00)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 390.01/(2*π*17.9063*20000.0000*1.0000*1.00)= 0.0002"
tt = tp + tm - tw (total required, tensile)
= 0.044487 + 0.000050 - (0.000173)
= 0.0444"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000050 + (0.000173) - (0.044487)|
= 0.0443"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*1.00*(0.1875-0.000050+(0.000173)) / (17.8125 - 0.40*(0.1875-0.000050+(0.000173)))
= 423.1127 psi
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Cylinder #1
Hot Shut Down, Corroded, Above Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 1003.47/(π*17.90632*13265.5928*1.0000)= 0.0001"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000075 - (0.000261)|
= 0.0002"
tc = tmc + twc - tpc (total required, compressive)
= 0.000075 + (0.000261) - (0.000000)
= 0.0003"
Hot Shut Down, New, Above Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 1003.47/(π*17.90632*13265.5928*1.0000)= 0.0001"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000075 - (0.000261)|
= 0.0002"
tc = tmc + twc - tpc (total required, compressive)
= 0.000075 + (0.000261) - (0.000000)
= 0.0003"
Empty, Corroded, Above Support Point
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Cylinder #1
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 1003.47/(π*17.90632*13265.5928*1.0000)= 0.0001"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000075 - (0.000261)|
= 0.0002"
tc = tmc + twc - tpc (total required, compressive)
= 0.000075 + (0.000261) - (0.000000)
= 0.0003"
Empty, New, Above Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 1003.47/(π*17.90632*13265.5928*1.0000)= 0.0001"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000075 - (0.000261)|
= 0.0002"
tc = tmc + twc - tpc (total required, compressive)
= 0.000075 + (0.000261) - (0.000000)
= 0.0003"
Vacuum, Above Support Point
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Cylinder #1
tp = P*R/(2*Sc*Ks + 0.40*|P|) (Pressure)
= -15.0000*17.8125/(2*13265.5928*1.0000 + 0.40*|15.0000|)
= -0.0101"
tm = M/(π*Rm2*Sc*Ks) (bending)
= 1003.47/(π*17.90632*13265.5928*1.0000)= 0.0001"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |-0.010068 + 0.000075 - (0.000261)|
= 0.0103"
tc = tmc + twc - tpc (total required, compressive)
= 0.000075 + (0.000261) - (-0.010068)
= 0.0104"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Above Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 1003.47/(π*17.90632*20000.0000*1.0000*1.00)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 0.00/(2*π*17.9063*20000.0000*1.0000*1.00)= 0.0000"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000050 - (0.000000)
= 0.0000"
tmc = M/(π*Rm2*Sc*Ks) (bending)
= 1003.47/(π*17.90632*13265.5928*1.0000)= 0.0001"
tc = tmc + twc - tpc (total required, compressive)
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Cylinder #1
= 0.000075 + (0.000000) - (0.000000)
= 0.0001"
Operating, Hot & Corroded, Below Support Point
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|)
= 0.0445"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90632*20000.0000*1.0000*1.00)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 390.01/(2*π*17.9063*20000.0000*1.0000*1.00)= 0.0002"
tt = tp + tm - tw (total required, tensile)
= 0.044487 + 0.000000 - (0.000173)
= 0.0443"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (0.000173) - (0.044487)|
= 0.0443"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*1.00*(0.1875-0.000000+(0.000173)) / (17.8125 - 0.40*(0.1875-0.000000+(0.000173)))
= 423.2255 psi
Operating, Hot & New, Below Support Point
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|)
= 0.0445"
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Cylinder #1
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90632*20000.0000*1.0000*1.00)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 390.01/(2*π*17.9063*20000.0000*1.0000*1.00)= 0.0002"
tt = tp + tm - tw (total required, tensile)
= 0.044487 + 0.000000 - (0.000173)
= 0.0443"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (0.000173) - (0.044487)|
= 0.0443"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*1.00*(0.1875-0.000000+(0.000173)) / (17.8125 - 0.40*(0.1875-0.000000+(0.000173)))
= 423.2255 psi
Hot Shut Down, Corroded, Below Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90632*13265.5928*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000261)|
= 0.0003"
tc = tmc + twc - tpc (total required, compressive)
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Cylinder #1
= 0.000000 + (0.000261) - (0.000000)
= 0.0003"
Hot Shut Down, New, Below Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90632*13265.5928*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000261)|
= 0.0003"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000261) - (0.000000)
= 0.0003"
Empty, Corroded, Below Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90632*13265.5928*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000261)|
= 0.0003"
tc = tmc + twc - tpc (total required, compressive)
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Cylinder #1
= 0.000000 + (0.000261) - (0.000000)
= 0.0003"
Empty, New, Below Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90632*13265.5928*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000261)|
= 0.0003"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000261) - (0.000000)
= 0.0003"
Vacuum, Below Support Point
tp = P*R/(2*Sc*Ks + 0.40*|P|) (Pressure)
= -15.0000*17.8125/(2*13265.5928*1.0000 + 0.40*|15.0000|)
= -0.0101"
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90632*13265.5928*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 390.01/(2*π*17.9063*13265.5928*1.0000)= 0.0003"
tt = |tp + tm - tw| (total, net compressive)
= |-0.010068 + 0.000000 - (0.000261)|
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Cylinder #1
= 0.0103"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000261) - (-0.010068)
= 0.0103"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Below Support Point
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90632*20000.0000*1.0000*1.00)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 0.00/(2*π*17.9063*20000.0000*1.0000*1.00)= 0.0000"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000000 - (0.000000)
= 0.0000"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000000) - (0.000000)
= 0.0000"
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Top Head
Top Head
ASME Section VIII, Division 1, 2001 Edition, A03 Addenda
Component: Ellipsoidal Head Material Specification: SA-516 70 (ASME II-D p.14, ln. 31)Straight Flange governs MDMT
Internal design pressure: P = 100 psi @ 150 °FExternal design pressure: Pe = 15 psi @ 150 °F
Static liquid head:
Ps= 0 psi (SG=1, Hs=0" Operating head)
Pth= 1.5093 psi (SG=1, Hs=41.813" Horizontal test head)
Corrosion allowance: Inner C = 0" Outer C = 0"
Design MDMT = -20°F No impact test performed Rated MDMT = -55°F Material is not normalized
Material is not produced to fine grain practice PWHT is not performed Do not Optimize MDMT / Find MAWP
Radiography: Category A joints - Seamless No RT Head to shell seam - None UW-11(c) Type 1
Estimated weight*: new = 90.3 lb corr = 90.3 lb Capacity*: new = 34.3 US gal corr = 34.3 US gal* includes straight flange
Outer diameter = 36"Minimum head thickness = 0.187"Head ratio D/2h = 2 (new)Head ratio D/2h = 2 (corroded)Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0.187"
Insulation thk*: 0" density: 0 lb/ft3 weight: 0 lb
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Top Head
Insulation support ring spacing:
0" individual weight: 0 lb total weight: 0 lb
Lining/ref thk*: 0" density: 0 lb/ft3 weight: 0 lb
* includes straight flange if applicable
Results Summary
The governing condition is internal pressure.Minimum thickness per UG-16 = 0.0625" + 0" = 0.0625"Design thickness due to internal pressure (t) = 0.1054"Design thickness due to external pressure (te) = 0.0927"
Maximum allowable working pressure (MAWP) = 178.278 psi
Maximum allowable pressure (MAP) = 178.278 psi
Maximum allowable external pressure (MAEP) = 61.3292 psi
K (Corroded)
K = (1/6)*[2 + (D / (2*h))2]= (1/6)*[2 + (35.626 / (2*8.9065))2]= 1
K (New)
K = (1/6)*[2 + (D / (2*h))2]= (1/6)*[2 + (35.626 / (2*8.9065))2]= 1
Design thickness for internal pressure, (Corroded at 150 °F) Appendix 1-4(c)
t = P*Do*K / (2*S*E + 2*P*(K - 0.1)) + Corrosion
= 100*36*1 / (2*20000*0.85 + 2*100*(1 - 0.1)) + 0= 0.1053"
The head internal pressure design thickness is 0.1054".
Maximum allowable working pressure, (Corroded at 150 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0
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Top Head
= 178.278 psi
The maximum allowable working pressure (MAWP) is 178.278 psi.
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0= 178.278 psi
The maximum allowable pressure (MAP) is 178.278 psi.
Design thickness for external pressure, (Corroded at 150 °F) UG-33(d)
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8907 * 36 = 32.0669 in
A = 0.125 / (Ro/t)
= 0.125 / (32.0669/0.092617) = 0.000361
From Table CS-2: B=5,193.4531 psi
Pa = B/(Ro/t)
= 5,193.453/(32.0669/0.092617) = 15 psi
t = 0.0926" + Corrosion = 0.0926" + 0" = 0.0926"
Check the external pressure per UG-33(a)(1) Appendix 1-4(c)
t = 1.67*Pe*Do*K / (2*S*E + 2*1.67*Pe*(K - 0.1)) + Corrosion
= 1.67*15*36*1 / (2*20000*1 + 2*1.67*15*(1 - 0.1)) + 0= 0.0225"
The head external pressure design thickness (te) is 0.092617".
Maximum Allowable External Pressure, (Corroded at 150 °F) UG-33(d)
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Top Head
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8907 * 36 = 32.0669 in
A = 0.125 / (Ro/t)
= 0.125 / (32.0669/0.187) = 0.000729
From Table CS-2: B=10,516.7607 psi
Pa = B/(Ro/t)
= 10,516.76/(32.0669/0.187) = 61.3292 psi
Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(c)
P = 2*S*E*t / ((K*Do - 2*t*(K - 0.1))*1.67) - Ps2= 2*20000*1*0.187 / ((1*36 - 2*0.187*(1 - 0.1))*1.67) - 0= 125.5921 psi
The maximum allowable external pressure (MAEP) is 61.3292 psi.
% Extreme fiber elongation - UCS-79(d)
= (75*t / Rf)*(1 - Rf / Ro)
= (75*0.187 / 6.1499)*(1 - 6.1499 / ∞)= 2.2805%
The extreme fiber elongation does not exceed 5%.
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Straight Flange on Top Head
Straight Flange on Top Head
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
Component: Straight FlangeMaterial specification: SA-516 70 (ASME II-D p. 14, ln. 31)Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 65.5 °F, (coincident ratio = 0.4801537)Rated MDMT is governed by UCS-66(b)(2)UCS-66 governing thickness = 0.187 in
Internal design pressure: P = 100 psi @ 150°FExternal design pressure: Pe = 15 psi @ 150°F
Static liquid head:
Pth=1.5093 psi(SG=1.0000, Hs=41.8130", Horizontal test head)
Corrosion allowance: Inner C = 0.0000" Outer C = 0.0000"
Design MDMT = -20.00°F No impact test performedRated MDMT = -55.00°F Material is not normalized
Material is not produced to Fine Grain PracticePWHT is not performed
Radiography: Longitudinal joint - Seamless No RTCircumferential joint - None UW-11(c) Type 1
Estimated weight: New = 11.9083 lb corr = 11.9083 lbCapacity: New = 8.6306 gal corr = 8.6306 gal
OD = 36.0000"Length Lc = 2.0000"
t = 0.1870"
Design thickness, (at 150.00°F) Appendix 1-1
t = P*Ro/(S*E + 0.40*P) + Corrosion
= 100.0000*18.0000/(20000.0000*0.85 + 0.40*100.0000) + 0.0000= 0.1057"
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Straight Flange on Top Head
Maximum allowable working pressure, (at 150.00°F) Appendix 1-1
P = S*E*t/(Ro - 0.40*t) - Ps= 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870) - 0.0000= 177.3481 psi
Maximum allowable pressure, (at 70.00°F) Appendix 1-1
P = S*E*t/(Ro - 0.40*t)
= 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870)= 177.3481 psi
External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 53.9377/36.0000 = 1.4983
Do/t = 36.0000/0.136839 = 263.0834
From table G: A = 0.000206
From table CS-2: B = 2959.6812
Pa = 4*B/(3*(Do/t))
= 4*2959.6812/(3*(36.0000/0.136839))
= 15.0000 psi
Design thickness for external pressure Pa = 15.0000 psi
= t + Corrosion = 0.136839 + 0.0000 = 0.1368"
Maximum Allowable External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 53.9377/36.0000 = 1.4983
Do/t = 36.0000/0.1870 = 192.5134
From table G: A = 0.000332
From table CS-2: B = 4775.1362
Pa = 4*B/(3*(Do/t))
= 4*4775.1362/(3*(36.0000/0.1870))
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Straight Flange on Top Head
= 33.0722 psi
% Extreme fiber elongation - UCS-79(d)
= (50 * t / Rf) * (1 - Rf / Ro)
= (50 * 0.1870 / 17.9065) * (1 - 17.9065 / ∞)= 0.5222 %
Design thickness = 0.1368"
The governing condition is due to external pressure.
The cylinder thickness of 0.1870" is adequate.
Thickness Required Due to Pressure + External Loads
ConditionPressure P ( psi)
Allowable Stress Before UG-23 Stress Increase
( psi)Temperature
(°F)Corrosion
C (in)Load
Req'd Thk
Due to Tension
(in)
Req'd Thk Due to
Compression (in)St Sc
Operating, Hot & Corroded
100.00 20000.00 13255.46 150.00 0.0000 Weight 0.0635 0.0635
Operating, Hot & New
100.00 20000.00 13255.46 150.00 0.0000 Weight 0.0635 0.0635
Hot Shut Down, Corroded
0.00 20000.00 13255.46 150.00 0.0000 Weight 0.0001 0.0001
Hot Shut Down, New
0.00 20000.00 13255.46 150.00 0.0000 Weight 0.0001 0.0001
Empty, Corroded 0.00 20000.00 13255.46 0.00 0.0000 Weight 0.0001 0.0001
Empty, New 0.00 20000.00 13255.46 0.00 0.0000 Weight 0.0001 0.0001
Vacuum -15.00 20000.00 13255.46 150.00 0.0000 Weight 0.0101 0.0101
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Straight Flange on Top Head
Hot Shut Down, Corroded, Weight & Eccentric Moments Only
0.00 20000.00 13255.46 150.00 0.0000 Weight 0.0001 0.0001
Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1870)
= 0.001299
B = 13255.4551 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScHC = 13255.4551 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 13255.4551 psi
Allowable Compressive Stress, Cold and New- ScCN, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1870)
= 0.001299
B = 13255.4551 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScCN = 13255.4551 psi
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Straight Flange on Top Head
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 13255.4551 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1870)
= 0.001299
B = 13255.4551 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScVC = 13255.4551 psi
Operating, Hot & Corroded, Bottom Seam
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|)
= 0.0635"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= 0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.063527 + 0.000000 - (0.000057)
= 0.0635"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (0.000057) - (0.063527)|
= 0.0635"
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Straight Flange on Top Head
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*0.70*(0.1870-0.000000+(0.000057)) / (17.8130 - 0.40*(0.1870-0.000000+(0.000057)))
= 295.2730 psi
Operating, Hot & New, Bottom Seam
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|)
= 0.0635"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= 90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= 0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.063527 + 0.000000 - (0.000057)
= 0.0635"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (0.000057) - (0.063527)|
= 0.0635"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*0.70*(0.1870-0.000000+(0.000057)) / (17.8130 - 0.40*(0.1870-0.000000+(0.000057)))
= 295.2730 psi
Hot Shut Down, Corroded, Bottom Seam
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Straight Flange on Top Head
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 90.30/(2*π*17.9065*13255.4551*1.0000)= 0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000061)|
= 0.0001"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000061) - (0.000000)
= 0.0001"
Hot Shut Down, New, Bottom Seam
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 90.30/(2*π*17.9065*13255.4551*1.0000)= 0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000061)|
= 0.0001"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000061) - (0.000000)
= 0.0001"
Empty, Corroded, Bottom Seam
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Straight Flange on Top Head
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 90.30/(2*π*17.9065*13255.4551*1.0000)= 0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000061)|
= 0.0001"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000061) - (0.000000)
= 0.0001"
Empty, New, Bottom Seam
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 90.30/(2*π*17.9065*13255.4551*1.0000)= 0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000061)|
= 0.0001"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000061) - (0.000000)
= 0.0001"
Vacuum, Bottom Seam
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Straight Flange on Top Head
tp = P*R/(2*Sc*Ks + 0.40*|P|) (Pressure)
= -15.0000*17.8130/(2*13255.4551*1.0000 + 0.40*|15.0000|)
= -0.0101"
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 90.30/(2*π*17.9065*13255.4551*1.0000)= 0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |-0.010076 + 0.000000 - (0.000061)|
= 0.0101"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000061) - (-0.010076)
= 0.0101"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Bottom Seam
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= 90.30/(2*π*17.9065*13255.4551*1.0000)= 0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |0.000000 + 0.000000 - (0.000061)|
= 0.0001"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (0.000061) - (0.000000)
= 0.0001"
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Straight Flange on Bottom Head
Straight Flange on Bottom Head
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
Component: Straight FlangeMaterial specification: SA-516 70 (ASME II-D p. 14, ln. 31)Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 65.5 °F, (coincident ratio = 0.4801537)Rated MDMT is governed by UCS-66(b)(2)UCS-66 governing thickness = 0.187 in
Internal design pressure: P = 100 psi @ 150°FExternal design pressure: Pe = 15 psi @ 150°F
Static liquid head:
Pth=1.5093 psi(SG=1.0000, Hs=41.8130", Horizontal test head)
Corrosion allowance: Inner C = 0.0000" Outer C = 0.0000"
Design MDMT = -20.00°F No impact test performedRated MDMT = -55.00°F Material is not normalized
Material is not produced to Fine Grain PracticePWHT is not performed
Radiography: Longitudinal joint - Seamless No RTCircumferential joint - None UW-11(c) Type 1
Estimated weight: New = 11.9083 lb corr = 11.9083 lbCapacity: New = 8.6306 gal corr = 8.6306 gal
OD = 36.0000"Length Lc = 2.0000"
t = 0.1870"
Design thickness, (at 150.00°F) Appendix 1-1
t = P*Ro/(S*E + 0.40*P) + Corrosion
= 100.0000*18.0000/(20000.0000*0.85 + 0.40*100.0000) + 0.0000= 0.1057"
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Straight Flange on Bottom Head
Maximum allowable working pressure, (at 150.00°F) Appendix 1-1
P = S*E*t/(Ro - 0.40*t) - Ps= 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870) - 0.0000= 177.3481 psi
Maximum allowable pressure, (at 70.00°F) Appendix 1-1
P = S*E*t/(Ro - 0.40*t)
= 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870)= 177.3481 psi
External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 53.9377/36.0000 = 1.4983
Do/t = 36.0000/0.136839 = 263.0834
From table G: A = 0.000206
From table CS-2: B = 2959.6812
Pa = 4*B/(3*(Do/t))
= 4*2959.6812/(3*(36.0000/0.136839))
= 15.0000 psi
Design thickness for external pressure Pa = 15.0000 psi
= t + Corrosion = 0.136839 + 0.0000 = 0.1368"
Maximum Allowable External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 53.9377/36.0000 = 1.4983
Do/t = 36.0000/0.1870 = 192.5134
From table G: A = 0.000332
From table CS-2: B = 4775.1362
Pa = 4*B/(3*(Do/t))
= 4*4775.1362/(3*(36.0000/0.1870))
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Straight Flange on Bottom Head
= 33.0722 psi
% Extreme fiber elongation - UCS-79(d)
= (50 * t / Rf) * (1 - Rf / Ro)
= (50 * 0.1870 / 17.9065) * (1 - 17.9065 / ∞)= 0.5222 %
Design thickness = 0.1368"
The governing condition is due to external pressure.
The cylinder thickness of 0.1870" is adequate.
Thickness Required Due to Pressure + External Loads
ConditionPressure P ( psi)
Allowable Stress Before UG-23 Stress Increase
( psi)Temperature
(°F)Corrosion
C (in)Load
Req'd Thk
Due to Tension
(in)
Req'd Thk Due to
Compression (in)St Sc
Operating, Hot & Corroded
100.00 20000.00 13255.46 150.00 0.0000 Weight 0.0636 0.0636
Operating, Hot & New
100.00 20000.00 13255.46 150.00 0.0000 Weight 0.0636 0.0636
Hot Shut Down, Corroded
0.00 20000.00 13255.46 150.00 0.0000 Weight 0.0001 0.0001
Hot Shut Down, New
0.00 20000.00 13255.46 150.00 0.0000 Weight 0.0001 0.0001
Empty, Corroded 0.00 20000.00 13255.46 0.00 0.0000 Weight 0.0001 0.0001
Empty, New 0.00 20000.00 13255.46 0.00 0.0000 Weight 0.0001 0.0001
Vacuum -15.00 20000.00 13255.46 150.00 0.0000 Weight 0.0100 0.0100
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Straight Flange on Bottom Head
Hot Shut Down, Corroded, Weight & Eccentric Moments Only
0.00 20000.00 13255.46 150.00 0.0000 Weight 0.0001 0.0001
Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1870)
= 0.001299
B = 13255.4551 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScHC = 13255.4551 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 13255.4551 psi
Allowable Compressive Stress, Cold and New- ScCN, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1870)
= 0.001299
B = 13255.4551 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScCN = 13255.4551 psi
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Straight Flange on Bottom Head
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 13255.4551 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2)
A = 0.125 / (Ro / t)
= 0.125 / (18.0000 / 0.1870)
= 0.001299
B = 13255.4551 psi
S = 20000.0000 / 1.0000
= 20000.0000 psi
ScVC = 13255.4551 psi
Operating, Hot & Corroded, Top Seam
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|)
= 0.0635"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.063527 + 0.000000 - (-0.000057)
= 0.0636"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.063527)|
= 0.0636"
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Straight Flange on Bottom Head
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*0.70*(0.1870-0.000000+(-0.000057)) / (17.8130 - 0.40*(0.1870-0.000000+(-0.000057)))
= 295.0913 psi
Operating, Hot & New, Top Seam
tp = P*R/(2*St*Ks*Ec + 0.40*|P|) (Pressure)
= 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|)
= 0.0635"
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.063527 + 0.000000 - (-0.000057)
= 0.0636"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.063527)|
= 0.0636"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))
=2*20000.0000*1.0000*0.70*(0.1870-0.000000+(-0.000057)) / (17.8130 - 0.40*(0.1870-0.000000+(-0.000057)))
= 295.0913 psi
Hot Shut Down, Corroded, Top Seam
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Straight Flange on Bottom Head
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000000 - (-0.000057)
= 0.0001"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.000000)|
= 0.0001"
Hot Shut Down, New, Top Seam
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000000 - (-0.000057)
= 0.0001"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.000000)|
= 0.0001"
Empty, Corroded, Top Seam
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Straight Flange on Bottom Head
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000000 - (-0.000057)
= 0.0001"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.000000)|
= 0.0001"
Empty, New, Top Seam
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000000 - (-0.000057)
= 0.0001"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.000000)|
= 0.0001"
Vacuum, Top Seam
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Straight Flange on Bottom Head
tp = P*R/(2*Sc*Ks + 0.40*|P|) (Pressure)
= -15.0000*17.8130/(2*13255.4551*1.0000 + 0.40*|15.0000|)
= -0.0101"
tm = M/(π*Rm2*Sc*Ks) (bending)
= 0.00/(π*17.90652*13255.4551*1.0000)= 0.0000"
tw = W/(2*π*Rm*Sc*Ks) (Weight)
= -90.30/(2*π*17.9065*13255.4551*1.0000)= -0.0001"
tt = |tp + tm - tw| (total, net compressive)
= |-0.010076 + 0.000000 - (-0.000061)|
= 0.0100"
tc = tmc + twc - tpc (total required, compressive)
= 0.000000 + (-0.000061) - (-0.010076)
= 0.0100"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Top Seam
tp = 0.0000" (Pressure)
tm = M/(π*Rm2*St*Ks*Ec) (bending)
= 0.00/(π*17.90652*20000.0000*1.0000*0.70)= 0.0000"
tw = W/(2*π*Rm*St*Ks*Ec) (Weight)
= -90.30/(2*π*17.9065*20000.0000*1.0000*0.70)= -0.0001"
tt = tp + tm - tw (total required, tensile)
= 0.000000 + 0.000000 - (-0.000057)
= 0.0001"
tc = |tmc + twc - tpc| (total, net tensile)
= |0.000000 + (-0.000057) - (0.000000)|
= 0.0001"
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Bottom Head
Bottom Head
ASME Section VIII, Division 1, 2001 Edition, A03 Addenda
Component: Ellipsoidal Head Material Specification: SA-516 70 (ASME II-D p.14, ln. 31)Straight Flange governs MDMT
Internal design pressure: P = 100 psi @ 150 °FExternal design pressure: Pe = 15 psi @ 150 °F
Static liquid head:
Ps= 0 psi (SG=1, Hs=0" Operating head)
Pth= 1.5093 psi (SG=1, Hs=41.813" Horizontal test head)
Corrosion allowance: Inner C = 0" Outer C = 0"
Design MDMT = -20°F No impact test performed Rated MDMT = -55°F Material is not normalized
Material is not produced to fine grain practice PWHT is not performed Do not Optimize MDMT / Find MAWP
Radiography: Category A joints - Seamless No RT Head to shell seam - None UW-11(c) Type 1
Estimated weight*: new = 90.3 lb corr = 90.3 lb Capacity*: new = 34.3 US gal corr = 34.3 US gal* includes straight flange
Outer diameter = 36"Minimum head thickness = 0.187"Head ratio D/2h = 2 (new)Head ratio D/2h = 2 (corroded)Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0.187"
Insulation thk*: 0" density: 0 lb/ft3 weight: 0 lb
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Bottom Head
Insulation support ring spacing:
0" individual weight: 0 lb total weight: 0 lb
Lining/ref thk*: 0" density: 0 lb/ft3 weight: 0 lb
* includes straight flange if applicable
Results Summary
The governing condition is internal pressure.Minimum thickness per UG-16 = 0.0625" + 0" = 0.0625"Design thickness due to internal pressure (t) = 0.1054"Design thickness due to external pressure (te) = 0.0927"
Maximum allowable working pressure (MAWP) = 178.278 psi
Maximum allowable pressure (MAP) = 178.278 psi
Maximum allowable external pressure (MAEP) = 61.3292 psi
K (Corroded)
K = (1/6)*[2 + (D / (2*h))2]= (1/6)*[2 + (35.626 / (2*8.9065))2]= 1
K (New)
K = (1/6)*[2 + (D / (2*h))2]= (1/6)*[2 + (35.626 / (2*8.9065))2]= 1
Design thickness for internal pressure, (Corroded at 150 °F) Appendix 1-4(c)
t = P*Do*K / (2*S*E + 2*P*(K - 0.1)) + Corrosion
= 100*36*1 / (2*20000*0.85 + 2*100*(1 - 0.1)) + 0= 0.1053"
The head internal pressure design thickness is 0.1054".
Maximum allowable working pressure, (Corroded at 150 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0
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Bottom Head
= 178.278 psi
The maximum allowable working pressure (MAWP) is 178.278 psi.
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)
P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0= 178.278 psi
The maximum allowable pressure (MAP) is 178.278 psi.
Design thickness for external pressure, (Corroded at 150 °F) UG-33(d)
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8907 * 36 = 32.0669 in
A = 0.125 / (Ro/t)
= 0.125 / (32.0669/0.092617) = 0.000361
From Table CS-2: B=5,193.4531 psi
Pa = B/(Ro/t)
= 5,193.453/(32.0669/0.092617) = 15 psi
t = 0.0926" + Corrosion = 0.0926" + 0" = 0.0926"
Check the external pressure per UG-33(a)(1) Appendix 1-4(c)
t = 1.67*Pe*Do*K / (2*S*E + 2*1.67*Pe*(K - 0.1)) + Corrosion
= 1.67*15*36*1 / (2*20000*1 + 2*1.67*15*(1 - 0.1)) + 0= 0.0225"
The head external pressure design thickness (te) is 0.092617".
Maximum Allowable External Pressure, (Corroded at 150 °F) UG-33(d)
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Bottom Head
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8907 * 36 = 32.0669 in
A = 0.125 / (Ro/t)
= 0.125 / (32.0669/0.187) = 0.000729
From Table CS-2: B=10,516.7607 psi
Pa = B/(Ro/t)
= 10,516.76/(32.0669/0.187) = 61.3292 psi
Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(c)
P = 2*S*E*t / ((K*Do - 2*t*(K - 0.1))*1.67) - Ps2= 2*20000*1*0.187 / ((1*36 - 2*0.187*(1 - 0.1))*1.67) - 0= 125.5921 psi
The maximum allowable external pressure (MAEP) is 61.3292 psi.
% Extreme fiber elongation - UCS-79(d)
= (75*t / Rf)*(1 - Rf / Ro)
= (75*0.187 / 6.1499)*(1 - 6.1499 / ∞)= 2.2805%
The extreme fiber elongation does not exceed 5%.
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Nozzle #1 (N1)
Nozzle #1 (N1)
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
tw(lower) = 0.1250 in
Leg41 = 0.1870 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 (ASME II-D p. 10, ln. 15)Nozzle longitudinal joint efficiency: 1.00Nozzle description: 1.500" Sch 40 (Std)Flange description: 1.5 inch 150# WN A105Bolt Material: SA-193 B7 Bolt
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Nozzle #1 (N1)
Reinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 209.14 psi @ 150.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 0.1269
Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for internal pressure 209.14 psi @ 150.00 °F
Fig UCS-66.2 general note (1) applies.
Nozzle is impact test exempt per UCS-66(d)(NPS 4 or smaller pipe).
Nozzle UCS-66 governing thk: 0.1269 inNozzle rated MDMT: -155.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.6100 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-27(c)(1)
trn = P*Rn/(Sn*E - 0.6*P)
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Nozzle #1 (N1)
= 209.1423*0.805/(17,100.00*1 - 0.6*209.1423)= 0.0099 in
Required thickness tr from UG-37(a)
tr = P*Ro/(S*E + 0.4*P)
= 209.1423*18/(20,000.00*1 + 0.4*209.1423)= 0.1874 in
This opening does not require reinforcement per UG-36(c)(3)(a)
Area calculations for weld failure path analysis
Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi
fr1 = lesser of 1 or Sn/Sv = 0.855
fr2 = lesser of 1 or Sn/Sv = 0.855
A = d*tr*F + 2*tn*tr*F*(1 - fr1)
= 1.61*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855)= 0.3097 in2
A1 = larger of the following= 0.0001 in2
= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 1.61*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0001 in2
= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0000 in2
A2 = smaller of the following= 0.0837 in2
= 5*(tn - trn)*fr2*t
= 5*(0.145 - 0.0099)*0.855*0.1875= 0.1083 in2
= 5*(tn - trn)*fr2*tn= 5*(0.145 - 0.0099)*0.855*0.145= 0.0837 in2
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Nozzle #1 (N1)
A41 = Leg2*fr2= 0.1872*0.855 =0.0299 in2
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in
t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in
The weld size t1 is satisfactory.
t2(actual) = 0.125 in
The weld size t2 is satisfactory.
t1 + t2 = 0.2559 >= 1.25*tmin
The combined weld sizes for t1 and t2 are satisfactory.
UG-45 Nozzle Neck Thickness Check
Wall thickness per UG-45(a): tr1 = 0.0099 in (E =1)
Wall thickness per UG-45(b)(1): tr2 = 0.1874 in
Wall thickness per UG-16(b): tr3 = 0.0625 in
Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in
The greater of tr2 or tr3: tr5 = 0.1874 in
The lesser of tr4 or tr5: tr6 = 0.1269 in
Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in
Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in
The nozzle neck thickness is adequate.
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 209.14 psi @ 70.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
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Nozzle #1 (N1)
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 0.1269
Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for internal pressure 209.14 psi @ 70.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.6100 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-27(c)(1)
trn = P*Rn/(Sn*E - 0.6*P)
= 209.1423*0.805/(17,100.00*1 - 0.6*209.1423)= 0.0099 in
Required thickness tr from UG-37(a)
tr = P*Ro/(S*E + 0.4*P)
= 209.1423*18/(20,000.00*1 + 0.4*209.1423)= 0.1874 in
This opening does not require reinforcement per UG-36(c)(3)(a)
Area calculations for weld failure path analysis
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Nozzle #1 (N1)
Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi
fr1 = lesser of 1 or Sn/Sv = 0.855
fr2 = lesser of 1 or Sn/Sv = 0.855
A = d*tr*F + 2*tn*tr*F*(1 - fr1)
= 1.61*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855)= 0.3097 in2
A1 = larger of the following= 0.0001 in2
= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 1.61*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0001 in2
= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0000 in2
A2 = smaller of the following= 0.0837 in2
= 5*(tn - trn)*fr2*t
= 5*(0.145 - 0.0099)*0.855*0.1875= 0.1083 in2
= 5*(tn - trn)*fr2*tn= 5*(0.145 - 0.0099)*0.855*0.145= 0.0837 in2
A41 = Leg2*fr2= 0.1872*0.855 =0.0299 in2
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in
t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in
The weld size t1 is satisfactory.
t2(actual) = 0.125 in
The weld size t2 is satisfactory.
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Nozzle #1 (N1)
t1 + t2 = 0.2559 >= 1.25*tmin
The combined weld sizes for t1 and t2 are satisfactory.
UG-45 Nozzle Neck Thickness Check
Wall thickness per UG-45(a): tr1 = 0.0099 in (E =1)
Wall thickness per UG-45(b)(1): tr2 = 0.1874 in
Wall thickness per UG-16(b): tr3 = 0.0625 in
Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in
The greater of tr2 or tr3: tr5 = 0.1874 in
The lesser of tr4 or tr5: tr6 = 0.1269 in
Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in
Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in
The nozzle neck thickness is adequate.
Reinforcement Calculations for External Pressure
UG-37 Area Calculation Summary (in2)For Pe = 33.33 psi @ 150.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.0625 0.1269
Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
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Nozzle #1 (N1)
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for external pressure 33.33 psi @ 150.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.6100 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-28 trn = 0.0114 in
From UG-37(d)(1) required thickness tr = 0.1875 in
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in
t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in
The weld size t1 is satisfactory.
t2(actual) = 0.125 in
The weld size t2 is satisfactory.
t1 + t2 = 0.2559 >= 1.25*tmin
The combined weld sizes for t1 and t2 are satisfactory.
UG-45 Nozzle Neck Thickness Check
Wall thickness per UG-45(a): tr1 = 0.0114 in
Wall thickness per UG-45(b)(2): tr2 = 0.0300 in
Wall thickness per UG-16(b): tr3 = 0.0625 in
Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in
The greater of tr2 or tr3: tr5 = 0.0625 in
The lesser of tr4 or tr5: tr6 = 0.0625 in
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Nozzle #1 (N1)
Required per UG-45 is the larger of tr1 or tr6 = 0.0625 in
Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in
The nozzle neck thickness is adequate.
External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 4.0251/1.9000 = 2.1185
Do/t = 1.9000/0.011395 = 166.7393
From table G: A = 0.000290
From table CS-2: B = 4168.5352
Pa = 4*B/(3*(Do/t))
= 4*4168.5352/(3*(1.9000/0.011395))
= 33.3338 psi
Design thickness for external pressure Pa = 33.3338 psi
= t + Corrosion = 0.011395 + 0.0000 = 0.0114"
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Nozzle #2 (N2)
Nozzle #2 (N2)
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
tw(lower) = 0.1250 in
Leg41 = 0.1870 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 (ASME II-D p. 10, ln. 15)Nozzle longitudinal joint efficiency: 1.00Nozzle description: 1.500" Sch 40 (Std)Flange description: 1.5 inch 150# WN A105Bolt Material: SA-193 B7 Bolt
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Nozzle #2 (N2)
Reinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 209.14 psi @ 150.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 0.1269
Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for internal pressure 209.14 psi @ 150.00 °F
Fig UCS-66.2 general note (1) applies.
Nozzle is impact test exempt per UCS-66(d)(NPS 4 or smaller pipe).
Nozzle UCS-66 governing thk: 0.1269 inNozzle rated MDMT: -155.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.8014 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-27(c)(1)
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Nozzle #2 (N2)
trn = P*Rn/(Sn*E - 0.6*P)
= 209.1423*0.805/(17,100.00*1 - 0.6*209.1423)= 0.0099 in
Required thickness tr from UG-37(a)
tr = P*Ro/(S*E + 0.4*P)
= 209.1423*18/(20,000.00*1 + 0.4*209.1423)= 0.1874 in
This opening does not require reinforcement per UG-36(c)(3)(a)
Area calculations for weld failure path analysis
Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi
fr1 = lesser of 1 or Sn/Sv = 0.855
fr2 = lesser of 1 or Sn/Sv = 0.855
A = d*tr*F + 2*tn*tr*F*(1 - fr1)
= 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855)= 0.3455 in2
A1 = larger of the following= 0.0001 in2
= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0001 in2
= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0000 in2
A2 = smaller of the following= 0.0837 in2
= 5*(tn - trn)*fr2*t
= 5*(0.145 - 0.0099)*0.855*0.1875= 0.1083 in2
= 5*(tn - trn)*fr2*tn
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Nozzle #2 (N2)
= 5*(0.145 - 0.0099)*0.855*0.145= 0.0837 in2
A41 = Leg2*fr2= 0.1872*0.855 =0.0299 in2
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in
t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in
The weld size t1 is satisfactory.
t2(actual) = 0.125 in
The weld size t2 is satisfactory.
t1 + t2 = 0.2559 >= 1.25*tmin
The combined weld sizes for t1 and t2 are satisfactory.
UG-45 Nozzle Neck Thickness Check
Wall thickness per UG-45(a): tr1 = 0.0099 in (E =1)
Wall thickness per UG-45(b)(1): tr2 = 0.1874 in
Wall thickness per UG-16(b): tr3 = 0.0625 in
Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in
The greater of tr2 or tr3: tr5 = 0.1874 in
The lesser of tr4 or tr5: tr6 = 0.1269 in
Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in
Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in
The nozzle neck thickness is adequate.
Reinforcement Calculations for MAP
The vessel wall thickness governs the MAP of this nozzle.
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Nozzle #2 (N2)
UG-37 Area Calculation Summary (in2)For P = 209.14 psi @ 70.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 0.1269
Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for internal pressure 209.14 psi @ 70.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.8014 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-27(c)(1)
trn = P*Rn/(Sn*E - 0.6*P)
= 209.1423*0.805/(17,100.00*1 - 0.6*209.1423)= 0.0099 in
Required thickness tr from UG-37(a)
tr = P*Ro/(S*E + 0.4*P)
= 209.1423*18/(20,000.00*1 + 0.4*209.1423)= 0.1874 in
This opening does not require reinforcement per UG-36(c)(3)(a)
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Nozzle #2 (N2)
Area calculations for weld failure path analysis
Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi
fr1 = lesser of 1 or Sn/Sv = 0.855
fr2 = lesser of 1 or Sn/Sv = 0.855
A = d*tr*F + 2*tn*tr*F*(1 - fr1)
= 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855)= 0.3455 in2
A1 = larger of the following= 0.0001 in2
= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0001 in2
= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0000 in2
A2 = smaller of the following= 0.0837 in2
= 5*(tn - trn)*fr2*t
= 5*(0.145 - 0.0099)*0.855*0.1875= 0.1083 in2
= 5*(tn - trn)*fr2*tn= 5*(0.145 - 0.0099)*0.855*0.145= 0.0837 in2
A41 = Leg2*fr2= 0.1872*0.855 =0.0299 in2
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in
t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in
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Nozzle #2 (N2)
The weld size t1 is satisfactory.
t2(actual) = 0.125 in
The weld size t2 is satisfactory.
t1 + t2 = 0.2559 >= 1.25*tmin
The combined weld sizes for t1 and t2 are satisfactory.
UG-45 Nozzle Neck Thickness Check
Wall thickness per UG-45(a): tr1 = 0.0099 in (E =1)
Wall thickness per UG-45(b)(1): tr2 = 0.1874 in
Wall thickness per UG-16(b): tr3 = 0.0625 in
Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in
The greater of tr2 or tr3: tr5 = 0.1874 in
The lesser of tr4 or tr5: tr6 = 0.1269 in
Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in
Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in
The nozzle neck thickness is adequate.
Reinforcement Calculations for External Pressure
UG-37 Area Calculation Summary (in2)For Pe = 33.33 psi @ 150.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.0625 0.1269
Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
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Nozzle #2 (N2)
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for external pressure 33.33 psi @ 150.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.8002 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-28 trn = 0.0140 in
From UG-37(d)(1) required thickness tr = 0.1875 in
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in
t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in
The weld size t1 is satisfactory.
t2(actual) = 0.125 in
The weld size t2 is satisfactory.
t1 + t2 = 0.2559 >= 1.25*tmin
The combined weld sizes for t1 and t2 are satisfactory.
UG-45 Nozzle Neck Thickness Check
Wall thickness per UG-45(a): tr1 = 0.0140 in
Wall thickness per UG-45(b)(2): tr2 = 0.0300 in
Wall thickness per UG-16(b): tr3 = 0.0625 in
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Nozzle #2 (N2)
Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in
The greater of tr2 or tr3: tr5 = 0.0625 in
The lesser of tr4 or tr5: tr6 = 0.0625 in
Required per UG-45 is the larger of tr1 or tr6 = 0.0625 in
Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in
The nozzle neck thickness is adequate.
External Pressure, (Corroded & at 150.00°F) UG-28(c)
L/Do = 6.3828/1.9000 = 3.3594
Do/t = 1.9000/0.013962 = 136.0829
From table G: A = 0.000237
From table CS-2: B = 3402.0903
Pa = 4*B/(3*(Do/t))
= 4*3402.0903/(3*(1.9000/0.013962))
= 33.3335 psi
Design thickness for external pressure Pa = 33.3335 psi
= t + Corrosion = 0.013962 + 0.0000 = 0.0140"
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Nozzle #3 (N3)
Nozzle #3 (N3)
ASME Section VIII Division 1, 2001 Edition, A03 Addenda
tw(lower) = 0.1250 in
Leg41 = 0.1870 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 (ASME II-D p. 10, ln. 15)Nozzle longitudinal joint efficiency: 1.00Nozzle description: 1.500" Sch 40 (Std)Flange description: 1.5 inch 150# WN A105Bolt Material: SA-193 B7 Bolt
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Nozzle #3 (N3)
Reinforcement Calculations for Internal Pressure
The vessel wall thickness governs the MAWP of this nozzle.
UG-37 Area Calculation Summary (in2)For P = 209.14 psi @ 150.00 °F
UG-45 Nozzle WallThickness Summary (in)The nozzle passes UG-45
Arequired
Aavailable
A1 A2 A3 A5Awelds
treq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 0.1269
Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld descriptionRequired weldthroat size (in)
Actual weldthroat size (in)
Status
Nozzle to shell fillet (Leg41) 0.1015 0.1309 weld size is adequate
Nozzle to shell groove (Lower) 0.1015 0.1250 weld size is adequate
Calculations for internal pressure 209.14 psi @ 150.00 °F
Fig UCS-66.2 general note (1) applies.
Nozzle is impact test exempt per UCS-66(d)(NPS 4 or smaller pipe).
Nozzle UCS-66 governing thk: 0.1269 inNozzle rated MDMT: -155.00 °F
Limits of reinforcement per UG-40
Parallel to the vessel wall: d = 1.8014 in
Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in
Nozzle required thickness per UG-27(c)(1)
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Nozzle #3 (N3)
trn = P*Rn/(Sn*E - 0.6*P)
= 209.1423*0.805/(17,100.00*1 - 0.6*209.1423)= 0.0099 in
Required thickness tr from UG-37(a)
tr = P*Ro/(S*E + 0.4*P)
= 209.1423*18/(20,000.00*1 + 0.4*209.1423)= 0.1874 in
This opening does not require reinforcement per UG-36(c)(3)(a)
Area calculations for weld failure path analysis
Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi
fr1 = lesser of 1 or Sn/Sv = 0.855
fr2 = lesser of 1 or Sn/Sv = 0.855
A = d*tr*F + 2*tn*tr*F*(1 - fr1)
= 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855)= 0.3455 in2
A1 = larger of the following= 0.0001 in2
= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0001 in2
= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)
= 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855)= 0.0000 in2
A2 = smaller of the following= 0.0837 in2
= 5*(tn - trn)*fr2*t
= 5*(0.145 - 0.0099)*0.855*0.1875= 0.1083 in2
= 5*(tn - trn)*fr2*tn
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Nozzle #3 (N3)
= 5*(0.145 - 0.0099)*0.855*0.145= 0.0837 in2
A41 = Leg2*fr2= 0.1872*0.855 =0.0299 in2
UW-16(d) Weld Check
tmin = lesser of 0.75 or tn or t = 0.1450 in
t1(min) or t2(mi