11488 VALIDAPRO 400L
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Transcript of 11488 VALIDAPRO 400L
Codeware, Inc.
Sarasota, FL, USA
www.codeware.com
COMPRESS Pressure Vessel Design Calculations
Item: Split Stream Dearator
Vessel No: V-1234
Customer: Magaladon Oil Venture
Contract: C-45490-R56
Designer: John Doe
Date: April 1, 2001
You can edit this page by selecting Cover Page settings... in the report menu.
Table of ContentsGeneral Arrangement Drawing................................................................................................................................1/46
Deficiencies Summary..............................................................................................................................................2/46
Pressure Summary...................................................................................................................................................3/46
Revision History........................................................................................................................................................4/46
Settings Summary.....................................................................................................................................................5/46
Radiography Summary.............................................................................................................................................7/46
Thickness Summary.................................................................................................................................................8/46
Weight Summary.......................................................................................................................................................9/46
Long Seam Summary.............................................................................................................................................10/46
Hydrostatic Test......................................................................................................................................................12/46
Liquid Level bounded by Bottom of vessel..........................................................................................................13/46
F&D Head #1............................................................................................................................................................14/46
Straight Flange on F&D Head #1............................................................................................................................16/46
Cylinder #1...............................................................................................................................................................22/46
Legs #1.....................................................................................................................................................................31/46
Transition #1............................................................................................................................................................37/46
i
General Arrangement Drawing
1/46
Deficiencies Summary
Deficiencies for Transition #1Transition calculations cannot be completed until a component is attached to the small end of the cone (or thediscontinuity is eliminated).The half apex angle is greater than 30 degrees. This results in UW-3 Category B weld joints being UW-12 type 8. Auser defined joint efficiency should be used.
Warnings Summary
Warnings for VesselThe vessel does not have a bottom closure (head or cover). (warning)
2/46
Pressure Summary
Component Summary
IdentifierP
Design(psi)
T
Design(°F)
MAWP(psi)
MAP(psi)
MDMT(°F)
MDMTExemption
ImpactTested
F&D Head #1 0,01 120 29,4 29,57 -320 Note 1 No
Straight Flange on F&D Head #1 0,01 120 51,86 52,05 -320 Note 2 No
Cylinder #1 0,01 120 50,35 52,05 -320 Note 3 No
Transition #1 0,01 120 23,83 25,6 -320 Note 4 No
Legs #1 0,01 120 0,01 N/A N/A N/A N/A
Chamber Summary
Design MDMT -20 °F
Rated MDMT -320 °F @ 0,01 psi
MAWP hot & corroded 0,01 psi @ 120 °F
MAP cold & new 25,6 psi @ 70 °F
(1) This pressure chamber is not designed forexternal pressure.
Notes for MDMT Rating
Note # Exemption Details
1. Impact test exempt per UHA-51(g) (coincident ratio = 0,0028)
2. Impact test exempt per UHA-51(g) (coincident ratio = 0,0031)
3. Impact test exempt per UHA-51(g) (coincident ratio = 0,0262)
4. Impact test exempt per UHA-51(g) (coincident ratio = 0,0582)
3/46
Revision History
Revisions
No. Date Operator Notes
0 10/29/2015 mnmeil New vessel created ASME Section VIII Division 1 [COMPRESS 2015 Build 7500]
4/46
Settings Summary
COMPRESS 2015 Build 7500
ASME Section VIII Division 1, 2013 Edition
Units U.S. Customary
Datum Line Location 0,00" from bottom seam
Vessel Design Mode Get Thickness from Pressure
Minimum thickness 0,0625" 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 andMAP
Corrosion weight loss 100% of theoretical loss
UG-23 Stress Increase 1,20
Skirt/legs stress increase 1,0
Minimum nozzle projection 6"
Juncture calculations for α > 30 only Yes
Preheat P-No 1 Materials > 1,25" and <= 1,50" thick No
UG-37(a) shell tr calculation considers longitudinal stress No
Cylindrical shells made from pipe are entered as minimum thickness No
Nozzles made from pipe are entered as minimum thickness No
Pipe caps are entered as minimum thickness No
Butt welds Tapered per Figure UCS-66.3(a)
Disallow Appendix 1-5, 1-8 calculations under 15 psi No
Hydro/Pneumatic Test
Shop Hydrotest Pressure 1,3 times vessel MAWP
Test liquid specific gravity 1,00
Maximum stress during test 90% of yield
Required Marking - UG-116
UG-116(e) Radiography None
UG-116(f) Postweld heat treatment None
Code Cases\Interpretations
Use Code Case 2547 No
Use Code Case 2695 No
Apply interpretation VIII-1-83-66 Yes
Apply interpretation VIII-1-86-175 Yes
5/46
Apply interpretation VIII-1-01-37 Yes
Apply interpretation VIII-1-01-150 Yes
Apply interpretation VIII-1-07-50 Yes
No UCS-66.1 MDMT reduction No
No UCS-68(c) MDMT reduction No
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 testconditions 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
UG-22(j) Test pressure and coincident static head acting during the test: No
Note: UG-22(b),(c) and (f) loads only considered when supports are present.
6/46
Radiography Summary
UG-116 Radiography
ComponentLongitudinal Seam Top Circumferential Seam Bottom Circumferential Seam
MarkCategory
(Fig UW-3) Radiography / Joint Type Category(Fig UW-3) Radiography / Joint Type Category
(Fig UW-3) Radiography / Joint Type
F&D Head #1 A None UW-11(c) / Type 1 N/A N/A B None UW-11(c) / Type 1 None
Cylinder #1 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B None UW-11(c) / Type 1 None
Transition #1 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B N/A / Type 8 None
UG-116(e) Required Marking: None
7/46
Thickness Summary
Component Data
ComponentIdentifier
Material Diameter(in)
Length(in)
Nominal t(in)
Design t(in)
Total Corrosion(in)
JointE
Load
F&D Head #1 SA-240 316L 28 ID 4,816 0,0625* 0,0004 0 0,70 Internal
Straight Flange on F&D Head #1 SA-240 316L 28 ID 0,5 0,0625 0,0003 0 0,70 Internal
Cylinder #1 SA-240 316L 28 ID 41,75 0,0625 0,0021 0 0,70 Internal
Transition #1 SA-240 316L 1,5 / 28 ID 8 0,0625 0,0043 0 0,70 Internal
Knuckle of Transition #1 SA-240 316L 28 -- 0,0625 0,0036 0 -- Internal
*Head minimum thickness after forming
Definitions
Nominal t Vessel wall nominal thickness
Design t Required vessel thickness due to governing loading + corrosion
Joint E Longitudinal seam joint efficiency
Load
Internal Circumferential stress due to internal pressure governs
External External pressure governs
Wind Combined longitudinal stress of pressure + weight + windgoverns
Seismic Combined longitudinal stress of pressure + weight + seismicgoverns
8/46
Weight Summary
Weight (lb) Contributed by Vessel Elements
Component MetalNew*
MetalCorroded Insulation Insulation
Supports Lining Piping+ Liquid
Operating Liquid Test Liquid Surface Areaft2New Corroded New Corroded
F&D Head #1 14,1 14,1 0 0 0 0 75,6 75,6 75,6 75,6 6
Cylinder #1 66,7 66,7 0 0 0 0 928 928 928 928 26
Transition #1 14,2 14,2 0 0 0 0 80,9 80,9 80,9 80,9 5
Legs #1 97,7 97,7 0 0 0 0 0 0 0 0 12
TOTAL: 192,7 192,7 0 0 0 0 1 084,4 1 084,4 1 084,4 1 084,4 48
*Shells with attached nozzles have weight reduced by material cut out for opening.
Weight (lb) Contributed by Attachments
Component Body Flanges Nozzles &Flanges Packed
BedsLadders &Platforms
Trays TraySupports
Rings &Clips
VerticalLoads
Surface Areaft2
New Corroded New Corroded
F&D Head #1 0 0 0 0 0 0 0 0 0 0 0
Cylinder #1 0 0 0 0 0 0 0 0 0 0 0
Transition #1 0 0 0 0 0 0 0 0 0 0 0
Legs #1 0 0 0 0 0 0 0 0 0 0 0
TOTAL: 0 0 0 0 0 0 0 0 0 0 0
Vessel Totals
New Corroded
Operating Weight (lb) 1 277 1 277
Empty Weight (lb) 193 193
Test Weight (lb) 1 277 1 277
Surface Area (ft2) 48 -
Capacity** (US gal) 130 130
**The vessel capacity does not includevolume of nozzle, piping or otherattachments.
Vessel Lift Condition
Vessel Lift Weight, New (lb) 193
Center of Gravity from Datum (in) 10,1934
9/46
Long Seam Summary
Shell Long SeamAngles
Component Seam 1
Cylinder #1 0°
Transition #1 30°
Shell Plate Lengths
Component StartingAngle Plate 1
Cylinder #1 0° 88,1609"
Transition #1 30° 88,1609"
Notes
1) Plate Lengths use the circumference of the vessel based on the mid diameter of the components.2) North is located at 0°
10/46
Shell Rollout
11/46
Hydrostatic Test
Horizontal shop hydrostatic test based on MAWP per UG-99(b)
Gauge pressure at 70°F =1,3*MAWP*LSR= 1,3*0,01*1= 0,01 psi
Horizontal shop hydrostatic test
IdentifierLocal testpressure
(psi)
Test liquidstatic head
(psi)
UG-99(b)stressratio
UG-99(b)pressure
factor
F&D Head #1 (1) 1,024 1,011 1 1,30
Straight Flange on F&D Head #1 1,024 1,011 1 1,30
Cylinder #1 1,024 1,011 1 1,30
Transition #1 1,024 1,011 1 1,30
(1) F&D Head #1 limits the UG-99(b) stress ratio.(2) The zero degree angular position is assumed to be up, and the testliquid height is assumed to the top-most flange.
The field test condition has not been investigated.
12/46
Liquid Level bounded by Bottom of vessel
ASME Section VIII Division 1, 2013 Edition
Location from Datum (in) 55,0035
Operating Liquid Specific Gravity 1
13/46
F&D Head #1
ASME Section VIII Division 1, 2013 Edition
Component F&D Head
Material SA-240 316L (II-D p. 74, ln. 9)
Attached To Cylinder #1
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 0,01 120 -20
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 0,17 4,7535 1
Test horizontal 1,01 28 1
Dimensions
Inner Diameter 28"
Crown Radius L 28"
Knuckle Radius r 1,7"
Minimum Thickness 0,0625"
Corrosion Inner 0"
Outer 0"
Length Lsf 0,5"
Nominal Thickness tsf 0,0625"
Weight and Capacity
Weight (lb)1 Capacity (US gal)1
New 14,12 9,06
Corroded 14,12 9,06
Radiography
Category A joints None UW-11(c) Type 1
Head to shell seam None UW-11(c) Type 11includes straight flange
14/46
Results Summary
Governing condition UG-16
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0004"
Maximum allowable working pressure (MAWP) 29,4 psi
Maximum allowable pressure (MAP) 29,57 psi
Rated MDMT -320°F
UHA-51 Material Toughness Requirements
tr = 0,18*28*1 / (2*16 700*0,7 - 0,2*0,18) = 0,0002"
Stress ratio = tr*E* / (tn - c) = 0,0002*0,8 / (0,0625 - 0) = 0,0028
Impact test exempt per UHA-51(g) (coincident ratio = 0,0028)
Rated MDMT = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Factor M
M = 1/4*[3 + (L / r)1/2]
Corroded M = 1/4*[3 + (28 / 1,7)1/2] 1,7646
New M = 1/4*[3 + (28 / 1,7)1/2] 1,7646
Design thickness for internal pressure, (Corroded at 120 °F) Appendix 1-4(d)
t = P*L*M / (2*S*E - 0,2*P) + Corrosion= 0,18*28*1,7646 / (2*16 700*0,7 - 0,2*0,18) + 0= 0,0004"
Maximum allowable working pressure, (Corroded at 120 °F) Appendix 1-4(d)
P = 2*S*E*t / (L*M + 0,2*t) - Ps= 2*16 700*0,7*0,0625 / (28*1,7646 + 0,2*0,0625) - 0,17= 29,4 psi
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(d)
P = 2*S*E*t / (L*M + 0,2*t) - Ps= 2*16 700*0,7*0,0625 / (28*1,7646 + 0,2*0,0625) - 0= 29,57 psi
% Forming strain - UHA-44(a)(2)
EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*0,0625 / 1,7313)*(1 - 1,7313 / infinity)= 2,7076%
15/46
Straight Flange on F&D Head #1
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material SA-240 316L (II-D p. 74, ln. 9)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 0,01 120 -20
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 0,19 5,2535 1
Test horizontal 1,01 28 1
Dimensions
Inner Diameter 28"
Length 0,5"
Nominal Thickness 0,0625"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 0,8 1,33
Corroded 0,8 1,33
Radiography
Longitudinal seam None UW-11(c) Type 1
Bottom Circumferentialseam None UW-11(c) Type 1
16/46
Results Summary
Governing condition UG-16
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0003"
Design thickness due to combined loadings + corrosion 0"
Maximum allowable working pressure (MAWP) 51,86 psi
Maximum allowable pressure (MAP) 52,05 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
tr = 0,2*14 / (16 700*0,7 - 0.6*0,2) = 0,0002"
Stress ratio = tr*E* / (tn - c) = 0,0002*0,8 / (0,0625 - 0) = 0,0031
Impact test exempt per UHA-51(g) (coincident ratio = 0,0031)
Rated MDMT = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 120 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 0,2*14 / (16 700*0,70 - 0,60*0,2) + 0= 0,0003"
Maximum allowable working pressure, (at 120 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 16 700*0,70*0,0625 / (14 + 0,60*0,0625) - 0,19= 51,86 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 16 700*0,70*0,0625 / (14 + 0,60*0,0625)= 52,05 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,0625 / 14,0313)*(1 - 14,0313 / infinity)= 0,2227%
17/46
Thickness Required Due to Pressure + External Loads
Condition Pressure P (psi)
AllowableStress BeforeUG-23 StressIncrease ( psi)
Temperature (°F)
Corrosion C(in) Load Req'd Thk Due to
Tension (in)
Req'd Thk Dueto
Compression(in)
St Sc
Operating, Hot & Corroded 0,01 16 700 7 633 120 0 Weight 0 0
Operating, Hot & New 0,01 16 700 7 633 120 0 Weight 0 0
Hot Shut Down, Corroded 0 16 700 7 633 120 0 Weight 0 0
Hot Shut Down, New 0 16 700 7 633 120 0 Weight 0 0
Empty, Corroded 0 16 700 7 778 70 0 Weight 0 0
Empty, New 0 16 700 7 778 70 0 Weight 0 0
Hot Shut Down, Corroded, Weight &Eccentric Moments Only 0 16 700 7 633 120 0 Weight 0 0
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-4)A = 0,125 / (Ro / t)
= 0,125 / (14,0625 / 0,0625)= 0,000556
B = 7 633 psi
S = 16 700 / 1,00 = 16 700 psi
ScHC = min(B, S) = 7 633 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 7 633 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-4)A = 0,125 / (Ro / t)
= 0,125 / (14,0625 / 0,0625)= 0,000556
B = 7 778 psi
S = 16 700 / 1,00 = 16 700 psi
ScCN = min(B, S) = 7 778 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 7 778 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-4)A = 0,125 / (Ro / t)
= 0,125 / (14,0625 / 0,0625)= 0,000556
B = 7 633 psi
S = 16 700 / 1,00 = 16 700 psi
ScVC = min(B, S) = 7 633 psi
18/46
Operating, Hot & Corroded, Bottom Seam
tp = P*R / (2*Sc*Ks + 0,40*|P|) (Pressure)= 0,01*14 / (2*7 632,98*1,00 + 0,40*|0,01|)= 0"
tm = M / (π*Rm2*Sc*Ks) (bending)
= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 632,98*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0,40*(t - tm + tw))= 2*16 700*1,00*0,70*(0,0625 - 0 + (0)) / (14 - 0,40*(0,0625 - 0 + (0)))= 104,58 psi
Operating, Hot & New, Bottom Seam
tp = P*R / (2*Sc*Ks + 0,40*|P|) (Pressure)= 0,01*14 / (2*7 632,98*1,00 + 0,40*|0,01|)= 0"
tm = M / (π*Rm2*Sc*Ks) (bending)
= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 632,98*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0,40*(t - tm + tw))= 2*16 700*1,00*0,70*(0,0625 - 0 + (0)) / (14 - 0,40*(0,0625 - 0 + (0)))= 104,58 psi
19/46
Hot Shut Down, Corroded, Bottom Seam
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 632,98*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
Hot Shut Down, New, Bottom Seam
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 632,98*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
Empty, Corroded, Bottom Seam
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 777,62*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 777,62*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
20/46
Empty, New, Bottom Seam
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 777,62*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 777,62*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Bottom Seam
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 14,1 / (2*π*14,0313*7 632,98*1,00)= 0"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0)|= 0"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (0)= 0"
21/46
Cylinder #1
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material SA-240 316L (II-D p. 74, ln. 9)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 0,01 120 -20
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 1,7 47,0035 1
Test horizontal 1,01 28 1
Dimensions
Inner Diameter 28"
Length 41,75"
Nominal Thickness 0,0625"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 66,71 111,29
Corroded 66,71 111,29
Radiography
Longitudinal seam None UW-11(c) Type 1
Top Circumferentialseam None UW-11(c) Type 1
Bottom Circumferentialseam None UW-11(c) Type 1
22/46
Results Summary
Governing condition UG-16
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0021"
Design thickness due to combined loadings + corrosion 0,0007"
Maximum allowable working pressure (MAWP) 50,35 psi
Maximum allowable pressure (MAP) 52,05 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
tr = 1,71*14 / (16 700*0,7 - 0.6*1,71) = 0,002"
Stress ratio = tr*E* / (tn - c) = 0,002*0,8 / (0,0625 - 0) = 0,0262
Impact test exempt per UHA-51(g) (coincident ratio = 0,0262)
Rated MDMT = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 120 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 1,71*14 / (16 700*0,70 - 0,60*1,71) + 0= 0,0021"
Maximum allowable working pressure, (at 120 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 16 700*0,70*0,0625 / (14 + 0,60*0,0625) - 1,7= 50,35 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 16 700*0,70*0,0625 / (14 + 0,60*0,0625)= 52,05 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,0625 / 14,0313)*(1 - 14,0313 / infinity)= 0,2227%
23/46
Thickness Required Due to Pressure + External Loads
Condition Pressure P (psi)
AllowableStress BeforeUG-23 StressIncrease ( psi)
Temperature (°F)
Corrosion C(in) Location Load Req'd Thk Due to
Tension (in)
Req'd Thk Dueto
Compression(in)
St Sc
Operating, Hot & Corroded 0,01 16 700 7 633 120 0 Top Weight 0,0001 0,0001
Bottom Weight 0,0007 0,0007
Operating, Hot & New 0,01 16 700 7 633 120 0 Top Weight 0,0001 0,0001
Bottom Weight 0,0007 0,0007
Hot Shut Down, Corroded 0 16 700 7 633 120 0 Top Weight 0,0001 0,0001
Bottom Weight 0,0007 0,0007
Hot Shut Down, New 0 16 700 7 633 120 0 Top Weight 0,0001 0,0001
Bottom Weight 0,0007 0,0007
Empty, Corroded 0 16 700 7 778 70 0 Top Weight 0,0001 0,0001
Bottom Weight 0 0
Empty, New 0 16 700 7 778 70 0 Top Weight 0,0001 0,0001
Bottom Weight 0 0
Hot Shut Down, Corroded,Weight & Eccentric MomentsOnly 0 16 700 7 633 120 0
Top Weight 0,0001 0,0001
Bottom Weight 0,0007 0,0007
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-4)A = 0,125 / (Ro / t)
= 0,125 / (14,0625 / 0,0625)= 0,000556
B = 7 633 psi
S = 16 700 / 1,00 = 16 700 psi
ScHC = min(B, S) = 7 633 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 7 633 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-4)A = 0,125 / (Ro / t)
= 0,125 / (14,0625 / 0,0625)= 0,000556
B = 7 778 psi
S = 16 700 / 1,00 = 16 700 psi
ScCN = min(B, S) = 7 778 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 7 778 psi
24/46
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-4)A = 0,125 / (Ro / t)
= 0,125 / (14,0625 / 0,0625)= 0,000556
B = 7 633 psi
S = 16 700 / 1,00 = 16 700 psi
ScVC = min(B, S) = 7 633 psi
Operating, Hot & Corroded, Above Support Point
tp = P*R / (2*Sc*Ks + 0,40*|P|) (Pressure)= 0,01*14 / (2*7 632,98*1,00 + 0,40*|0,01|)= 0"
tm = M / (π*Rm2*Sc*Ks) (bending)
= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 632,98*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0,40*(t - tm + tw))= 2*16 700*1,00*1,00*(0,0625 - 0 + (0,0001)) / (14 - 0,40*(0,0625 - 0 + (0,0001)))= 149,5 psi
Operating, Hot & New, Above Support Point
tp = P*R / (2*Sc*Ks + 0,40*|P|) (Pressure)= 0,01*14 / (2*7 632,98*1,00 + 0,40*|0,01|)= 0"
tm = M / (π*Rm2*Sc*Ks) (bending)
= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 632,98*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
25/46
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0,40*(t - tm + tw))= 2*16 700*1,00*1,00*(0,0625 - 0 + (0,0001)) / (14 - 0,40*(0,0625 - 0 + (0,0001)))= 149,5 psi
Hot Shut Down, Corroded, Above Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 632,98*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Hot Shut Down, New, Above Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 632,98*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Empty, Corroded, Above Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 777,62*1,00)= 0"
26/46
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 777,62*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Empty, New, Above Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 777,62*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 777,62*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Above Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*Sc*Ks) (bending)= 0 / (π*14,03132*7 632,98*1,00)= 0"
tw = W / (2*π*Rm*Sc*Ks) (Weight)= 79,2 / (2*π*14,0313*7 632,98*1,00)= 0,0001"
tt = |tp + tm - tw| (total, net compressive)= |0 + 0 - (0,0001)|= 0,0001"
tc = tmc + twc - tpc (total required, compressive)= 0 + (0,0001) - (0)= 0,0001"
Operating, Hot & Corroded, Below Support Point
tp = P*R / (2*St*Ks*Ec + 0,40*|P|) (Pressure)= 0,01*14 / (2*16 700*1,00*1,00 + 0,40*|0,01|)= 0"
27/46
tm = M / (π*Rm2*St*Ks*Ec) (bending)
= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -1 081,9 / (2*π*14,0313*16 700*1,00*1,00)= -0,0007"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0007)= 0,0007"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0007) - (0)|= 0,0007"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0,40*(t - tm + tw))= 2*16 700*1,00*1,00*(0,0625 - 0 + (-0,0007)) / (14 - 0,40*(0,0625 - 0 + (-0,0007)))= 147,61 psi
Operating, Hot & New, Below Support Point
tp = P*R / (2*St*Ks*Ec + 0,40*|P|) (Pressure)= 0,01*14 / (2*16 700*1,00*1,00 + 0,40*|0,01|)= 0"
tm = M / (π*Rm2*St*Ks*Ec) (bending)
= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -1 081,9 / (2*π*14,0313*16 700*1,00*1,00)= -0,0007"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0007)= 0,0007"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0007) - (0)|= 0,0007"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0,40*(t - tm + tw))= 2*16 700*1,00*1,00*(0,0625 - 0 + (-0,0007)) / (14 - 0,40*(0,0625 - 0 + (-0,0007)))= 147,61 psi
28/46
Hot Shut Down, Corroded, Below Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*St*Ks*Ec) (bending)= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -1 081,9 / (2*π*14,0313*16 700*1,00*1,00)= -0,0007"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0007)= 0,0007"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0007) - (0)|= 0,0007"
Hot Shut Down, New, Below Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*St*Ks*Ec) (bending)= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -1 081,9 / (2*π*14,0313*16 700*1,00*1,00)= -0,0007"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0007)= 0,0007"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0007) - (0)|= 0,0007"
Empty, Corroded, Below Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*St*Ks*Ec) (bending)= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -15,8 / (2*π*14,0313*16 700*1,00*1,00)= 0"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (0)
29/46
= 0"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (0) - (0)|= 0"
Empty, New, Below Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*St*Ks*Ec) (bending)= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -15,8 / (2*π*14,0313*16 700*1,00*1,00)= 0"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (0)= 0"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (0) - (0)|= 0"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Below Support Point
tp = 0" (Pressure)tm = M / (π*Rm
2*St*Ks*Ec) (bending)= 0 / (π*14,03132*16 700*1,00*1,00)= 0"
tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -1 081,9 / (2*π*14,0313*16 700*1,00*1,00)= -0,0007"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0007)= 0,0007"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0007) - (0)|= 0,0007"
30/46
Legs #1
Inputs
Leg material
Leg description 3 inch sch 40 pipe
Number of legs, N 4
Overall length 36"
Base to girth seam length 34"
Bolt circle 30,125"
Foundation allowable bearing stress 1 658 psi
User defined leg eccentricity 0
Effective length coefficient, K 1,2
Coefficient, Cm 0,85
Leg yield stress, Fy 36 000 psi
Leg elastic modulus, E 29 000 000 psi
Anchor Bolts
Anchor bolt size 0,375" series 8 threaded
Anchor bolt material
Anchor bolts/leg 1
Anchor bolt allowable stress, Sb 20 000 psi
Anchor bolt corrosion allowance 0"
Anchor bolt hole clearance 0,375"
Welds
Leg to shell fillet weld 0,0625" (0,0089" required)
Legs braced No
Note: The support attachment point is assumed to be 1 in up from the cylinder circumferential seam.
31/46
Governing Condition : Weight operating corroded, Moment = 0,0 lbf-ft
Forceattack
angle °
Legposition °
Axialend load
lbf
Shearresisted
lbf
Axialfa
psi
Bendingfbxpsi
Bendingfbypsi
RatioH1-1
RatioH1-2
0
0 319,3 0,0 143 0 0 0,0073 0,0066
90 319,3 0,0 143 0 0 0,0073 0,0066
180 319,3 0,0 143 0 0 0,0073 0,0066
270 319,3 0,0 143 0 0 0,0073 0,0066
Weight empty corroded, Moment = 0,0 lbf-ft
Forceattack
angle °
Legposition °
Axialend load
lbf
Shearresisted
lbf
Axialfa
psi
Bendingfbxpsi
Bendingfbypsi
RatioH1-1
RatioH1-2
0
0 48,2 0,0 22 0 0 0,0011 0,0010
90 48,2 0,0 22 0 0 0,0011 0,0010
180 48,2 0,0 22 0 0 0,0011 0,0010
270 48,2 0,0 22 0 0 0,0011 0,0010
Leg Calculations (AISC manual ninth edition)
Axial end load, P1 (Based on vessel total bending moment acting at leg attachment elevation)
P1 = W / N + 48*Mt / (N*D)= 1 277,11 / 4 + 48*0 / ( 4*28,125)= 319,28 lbf
Allowable axial compressive stress, Fa (AISC chapter E)
Cc = Sqr(2*π2*E / Fy)= Sqr(2*π2*29 000 000 / 36 000)= 126,0993
K*l / r = 1,2*35 / 1,1637 = 36,0909
Fa = 1 * (1 - (K*l / r)2 / (2*Cc2))*Fy / (5 / 3 + 3*(K*l / r) / (8*Cc)-(K*l / r)3 / (8*Cc
3))= 1 * (1 - (36,0909)2 / (2*126,09932))*36 000 / (5 / 3 + 3*(36,0909) / (8*126,0993)-(36,0909)3 / (8*126,09933))= 19 494 psi
Allowable axial compression and bending (AISC chapter H)
F'ex = 1*12*π2*E / (23*(K*l / r)2)
= 1*12*π2*29 000 000 / (23*(36,0909)2)= 114 645 psi
F'ey = 1*12*π2*E / (23*(K*l / r)2)
= 1*12*π2*29 000 000 / (23*(36,0909)2)= 114 645 psi
Fb = 1*0,66*Fy= 1*0,66*36 000= 23 760 psi
32/46
Compressive axial stress
fa = P1 / A= 319,28 / 2,23= 143 psi
Bending stresses
fbx = F*cos(α)*L / (Ix / Cx) + P1*Ecc / (Ix / Cx)= 0*cos(0)*35 / (3,02 / 1,75) + 319,28*0 / (3,02 / 1,75)= 0 psi
fby= F*sin(α)*L / (Iy / Cy)= 0*sin(0)*35 / (3,02 / 1,75)= 0 psi
AISC equation H1-1
H1-1 = fa / Fa + Cmx*fbx / ((1 - fa / F'ex)*Fbx) + Cmy*fby / ((1 - fa / F'
ey)*Fby)= 143 / 19 494 + 0,85*0 / ((1 - 143 / 114 645)*23 760) + 0,85*0 / ((1 - 143 / 114 645)*23 760)= 0,0073
AISC equation H1-2
H1-2 = fa / (0,6*1*Fy) + fbx / Fbx + fby / Fby= 143 / (0,6*1*36 000) + 0 / 23 760 + 0 / 23 760= 0,0066
4, 3 inch sch 40 pipe legs are adequate.
Anchor bolts - Weight empty corroded condition governs
Tensile loading per leg (1 bolt per leg)
R = 48*M / (N*BC) - W / N= 48*0 / (4*30,125) - 192,66 / 4= -48,16 lbfThere is no net uplift (R is negative).
0,375" series 8 threaded bolts are satisfactory.
Check the leg to vessel fillet weld, Bednar 10.3, Weight operating corroded governs
Note: continuous welding is assumed for all support leg fillet welds.
Zw = (2*b*d + d2) / 3= (2*3,5*1 + 12) / 3= 2,6667 in2
Jw = (b + 2*d)3 / 12 - d2*(b + d)2 / (b + 2*d)= (3,5 + 2*1)3 / 12 - 12*(3,5 + 1)2 / (3,5 + 2*1)= 10,1828 in3
E = d2 / (b + 2*d)= 12 / (3,5 + 2*1)= 0,181818 in
33/46
Governing weld load fx = Cos(0)*0 = 0 lbfGoverning weld load fy = Sin(0)*0 = 0 lbf
f1 = P1 / Lweld= 319,28 / 5,5= 58,05 lbf/in (V
L direct shear)
f2= fy*Lleg*0,5*b / Jw= 0*35*0,5*3,5 / 10,1828= 0 lbf/in (V
L torsion shear)
f3 = fy / Lweld= 0 / 5,5= 0 lbf/in (V
c direct shear)
f4 = fy*Lleg*E / Jw= 0*35*0,1818 / 10,1828= 0 lbf/in (V
c torsion shear)
f5 = (fx*Lleg + P1*Ecc) / Zw= (0*35 + 319,28*0) / 2,6667= 0 lbf/in (M
L bending)
f6 = fx / Lweld= 0 / 5,5= 0 lbf/in (Direct outward radial shear)
f = Sqr((f1 + f2)2 + (f3 + f4)2 + (f5 + f6)2)= Sqr((58,05 + 0)2 + (0 + 0)2 + (0 + 0)2)= 58,05 lbf/in (Resultant shear load)
Required leg to vessel fillet weld leg size (welded both sides + top)
tw = f / (0,707*0,55*Sa)= 58,05 / (0,707*0,55*16 700)= 0,0089 in
The 0,0625 in leg to vessel attachment fillet weld size is adequate.
Base plate thickness check, AISC 3-106
fp = P / (B*N)= 319,28 / (4*4)= 20 psi
tb =(N - (d - tL)) / 2*Sqr(3*fp / Sb)=(4 - (3,5 - 0,216)) / 2*Sqr(3*20 / 24 000)= 0,0179 in
The base plate thickness is adequate.
34/46
Check the leg to vessel attachment stresses, WRC 107 (Weight operating corrodedgoverns)
Applied Loads
Radial load, Pr 0 lbf
Circumferential moment, Mc 0 lbf-in
Circumferential shear, Vc 0 lbf
Longitudinal moment, ML 0 lbf-in
Longitudinal shear, VL 319,28 lbf
Torsion moment, Mt 0 lbf-in
Internal pressure, P 1,71 psi
Mean shell radius, Rm 14,0313"
Local shell thickness, T 0,0625"
Design factor 3
Maximum stresses due to the applied loads at the leg edge (includes pressure)
γ = Rm / T = 14,0313 / 0,0625 = 224,5
C1 = 1,75, C2 = 0,5 in
Local circumferential pressure stress = P*Ri / T =382 psi
Local longitudinal pressure stress = P*Ri / (2*T) =191 psi
Maximum combined stress (PL+P
b+Q) = 5 112 psi
Allowable combined stress (PL+P
b+Q) = ±3*S = ±50 100 psi
Note: The allowable combined stress (PL+P
b+Q) is based on the strain hardening characteristics of this material.
The maximum combined stress (PL+P
b+Q) is within allowable limits.
Maximum local primary membrane stress (PL) = 382 psi
Allowable local primary membrane stress (PL) = ±1,5*S = ±25 050 psi
The maximum local primary membrane stress (PL) is within allowable limits.
35/46
Stresses at the leg edge per WRC Bulletin 107
Figure value β Au Al Bu Bl Cu Cl Du Dl
3C* 26,8195 0,0617 0 0 0 0 0 0 0 0
4C* 28,9335 0,1044 0 0 0 0 0 0 0 0
1C 0,0625 0,1089 0 0 0 0 0 0 0 0
2C-1 0,0282 0,1089 0 0 0 0 0 0 0 0
3A* 8,938 0,0821 0 0 0 0 0 0 0 0
1A 0,0705 0,1023 0 0 0 0 0 0 0 0
3B* 24,4987 0,0541 0 0 0 0 0 0 0 0
1B-1 0,0262 0,0812 0 0 0 0 0 0 0 0
Pressure stress* 382 382 382 382 382 382 382 382
Total circumferential stress 382 382 382 382 382 382 382 382
Primary membranecircumferential stress* 382 382 382 382 382 382 382 382
3C* 16,6213 0,1044 0 0 0 0 0 0 0 0
4C* 35,1692 0,0617 0 0 0 0 0 0 0 0
1C-1 0,0848 0,0778 0 0 0 0 0 0 0 0
2C 0,0474 0,0778 0 0 0 0 0 0 0 0
4A* 16,2045 0,0821 0 0 0 0 0 0 0 0
2A 0,0394 0,0812 0 0 0 0 0 0 0 0
4B* 7,6465 0,0541 0 0 0 0 0 0 0 0
2B-1 0,0538 0,0594 0 0 0 0 0 0 0 0
Pressure stress* 191 191 191 191 191 191 191 191
Total longitudinal stress 191 191 191 191 191 191 191 191
Primary membranelongitudinal stress* 191 191 191 191 191 191 191 191
Shear from Mt 0 0 0 0 0 0 0 0
Circ shear from Vc 0 0 0 0 0 0 0 0
Long shear from VL 0 0 0 0 -2 554 -2 554 2 554 2 554
Total Shear stress 0 0 0 0 -2 554 -2 554 2 554 2 554
Combined stress (PL+Pb+Q) 382 382 382 382 5 112 5 112 5 112 5 112
* denotes primary stress.
36/46
Transition #1
ASME Section VIII Division 1, 2013 Edition
Component Cone
Material SA-240 316L (II-D p. 74, ln. 9)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 0,01 120 -20
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating Large 1,7 47,0035 1Small 1,99 55,0035
Test horizontal Large 1,01 28 1Small 0,53 14,75
Dimensions
Inner Diameter Large 28"
Small 1,5"
Length 8"
Nominal Thickness 0,0625"
Corrosion Inner 0"
Outer 0"
Knuckle Thickness tkl 0,0625"
Radius r1 2,1675"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 14,16 9,7
Corroded 14,16 9,7
Radiography
Longitudinal seam None UW-11(c) Type 1
Top Circumferential seam None UW-11(c) Type 1
Bottom Circumferential seam None UW-11(c) Type 1
37/46
Results Summary
Governing condition UG-16
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0043"
Maximum allowable working pressure (MAWP) 23,83 psi
Maximum allowable pressure (MAP) 25,6 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
tr = 1,71*28 / (2*0,4493*(16 700*0,7 - 0.6*1,71)) = 0,0045"
Stress ratio = tr*E* / (tn - c) = 0,0045*0,8 / (0,0625 - 0) = 0,0582
Impact test exempt per UHA-51(g) (coincident ratio = 0,0582)
Rated MDMT = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 120 °F) UG-32(h) (Large End)
Di = D - 2*r*(1 - cos(α))= 28 - 2*2,1675*(1 - cos(63,3005))= 25,6128"
t = P*Di / (2*cos(α)*(S*E - 0,60*P)) + Corrosion= 1,78*25,6128 / (2*cos(63,3005)*(16 700*0,70 - 0,60*1,78)) + 0= 0,0043"
Design thickness, (at 120 °F) Appendix 1-4(d) (Knuckle)
L = Di / (2*cos(α))= 25,6128 / (2*cos(63,3005))= 28,5022"
M = 0,25*(3 + Sqr(L / r))= 0,25*(3 + Sqr(28,5022 / 2,1675))= 1,6566
tk = P*L*M / (2*S*E - 0,20*P) + Corrosion= 1,78*28,5022*1,6566 / (2*16 700*0,70 - 0,20*1,78) + 0= 0,0036"
Small End design thickness (t = 0,0003") does not govern.
Maximum allowable working pressure, (Corroded at 120 °F) UG-32(h)
P = 2*S*E*t*cos(α) / (Di + 1,20*t*cos(α)) - Pskl
= 2*16 700*0,70*0,0625*cos(63,3005) / (25,6128 + 1,20*0,0625*cos(63,3005)) -1,77
= 23,83 psi
38/46
Maximum allowable working pressure, (Corroded at 120 °F) App 1-4(d) (Knuckle)
P = 2*S*E*tk / (L*M + 0,20*tk) - Ps
= 2*16 700*0,70*0,0625 / (28,5022*1,6566 + 0,20*0,0625) -1,77
= 29,17 psi
Small End MAWP (426,1 psi) does not govern.
Maximum allowable pressure, (New at 70 °F) UG-32(h)
P = 2*S*E*t*cos(α) / (Di + 1,20*t*cos(α))
= 2*16 700*0,70*0,0625*cos(63,3005) / (25,6128 +1,20*0,0625*cos(63,3005))
= 25,6 psi
Maximum allowable pressure, (New at 70 °F) App 1-4(d) (Knuckle)
P = 2*S*E*tk / (L*M + 0,20*tk)
= 2*16 700*0,70*0,0625 /(28,5022*1,6566 + 0,20*0,0625)
= 30,94 psi
Small End MAP (428,09 psi) does not govern.
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,1391 / 0,8196)*(1 - 0,8196 / infinity)= 8,4865%
39/46
Thickness Required Due to Pressure + External Loads
Condition Pressure P (psi)
AllowableStress BeforeUG-23 StressIncrease ( psi)
Temperature (°F)
Corrosion C(in) Location Load Req'd Thk Due to
Tension (in)
Req'd Thk Dueto
Compression(in)
St Sc
Operating, Hot & Corroded 0,01 16 700 3 472 120 0 Top Weight 0,0024 0,0024
Bottom Weight 0,0001 0,0001
Operating, Hot & New 0,01 16 700 3 472 120 0 Top Weight 0,0024 0,0024
Bottom Weight 0,0001 0,0001
Hot Shut Down, Corroded 0 16 700 3 472 120 0 Top Weight 0,0024 0,0024
Bottom Weight 0,0001 0,0001
Hot Shut Down, New 0 16 700 3 472 120 0 Top Weight 0,0024 0,0024
Bottom Weight 0,0001 0,0001
Empty, Corroded 0 16 700 3 494 70 0 Top Weight 0 0
Bottom Weight 0 0
Empty, New 0 16 700 3 494 70 0 Top Weight 0 0
Bottom Weight 0 0
Hot Shut Down, Corroded,Weight & Eccentric MomentsOnly 0 16 700 3 472 120 0
Top Weight 0,0024 0,0024
Bottom Weight 0,0001 0,0001
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-4)A = 0,125 / (Ro / te)
= 0,125 / (14,0625 / 0,0281)= 0,000250
B = 3 472 psiS = 16 700 / 1,00 = 16 700 psiScHC = min(B, S) = 3 472 psiAllowable Compressive Stress, Hot and New- ScHNScHN = ScHC
= 3471,8766 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-4)A = 0,125 / (Ro / te)
= 0,125 / (14,0625 / 0,0281)= 0,000250
B = 3 494 psiS = 16 700 / 1,00 = 16 700 psiScCN = min(B, S) = 3 494 psiAllowable Compressive Stress, Cold and Corroded- ScCCScCC = ScCN
= 3493,8286 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-4)A = 0,125 / (Ro / te)
= 0,125 / (14,0625 / 0,0281)= 0,000250
B = 3 472 psiS = 16 700 / 1,00 = 16 700 psiScVC = min(B, S) = 3 472 psi
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Operating, Hot & Corroded, Top Seam
tp = P*R / [(2*St*Ks*Ec + 0,40*|P|)*cos(α)] (Pressure)
= 0,01*14 / [(2*16 700*1,00*0,70 +0,40*|0,01|)*cos(63,3005)]
= 0"tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)
= -1 098,6 /[(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]
= -0,0024"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0024)= 0,0024"
tc = |tmc + twc - tpc| (total, net tensile)= |0 + (-0,0024) - (0)|= 0,0024"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / ((R - 0,40*(t - tm + tw))*cos(α))= 2*16 700*1,00*0,70*(0,0625 - 0 + (-0,0024)) / ((14 - 0,40*(0,0625 - 0 + (-0,0024)))*cos(63,3005))= 223,87 psi
Operating, Hot & New, Top Seam
tp = P*R / [(2*St*Ks*Ec + 0,40*|P|)*cos(α)] (Pressure)
= 0,01*14 / [(2*16 700*1,00*0,70 +0,40*|0,01|)*cos(63,3005)]
= 0"tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)
= -1 098,6 /[(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]
= -0,0024"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (-0,0024)= 0,0024"
tc = |tmc + twc - tpc| (total, net tensile)= |0 + (-0,0024) - (0)|= 0,0024"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / ((R - 0,40*(t - tm + tw))*cos(α))= 2*16 700*1,00*0,70*(0,0625 - 0 + (-0,0024)) / ((14 - 0,40*(0,0625 - 0 + (-0,0024)))*cos(63,3005))= 223,87 psi
Hot Shut Down, Corroded, Top Seam
tp = 0" (Pressure)
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tm = M / [(π*Rm2*St*Ks*Ec)*cos(α)] (bending)
= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -1 098,6 / [(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]= -0,0024"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0024)= 0,0024"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0024) - (0)|= 0,0024"
Hot Shut Down, New, Top Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -1 098,6 / [(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]= -0,0024"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0024)= 0,0024"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0024) - (0)|= 0,0024"
Empty, Corroded, Top Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)
= -14,2 /[(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]
= 0"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (0)= 0"
tc = |tmc + twc - tpc| (total, net tensile)= |0 + (0) - (0)|= 0"
Empty, New, Top Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)
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= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)
= -14,2 /[(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]
= 0"
tt = tp + tm - tw(total required,tensile)
= 0 + 0 - (0)= 0"
tc = |tmc + twc - tpc| (total, net tensile)= |0 + (0) - (0)|= 0"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Top Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*14,03132*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -1 098,6 / [(2*π*14,0313*16 700*1,00*0,70)*cos(63,3005)]= -0,0024"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0024)= 0,0024"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0024) - (0)|= 0,0024"
Operating, Hot & Corroded, Bottom Seam
tp = P*R / [(2*St*Ks*Ec + 0,40*|P|)*cos(α)] (Pressure)= 0,01*0,75 / [(2*16 700*1,00*0,70 + 0,40*|0,01|)*cos(63,3005)]= 0"
tm = M / [(π*Rm2*St*Ks*Ec)*cos(α)] (bending)
= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -3,5 / [(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]= -0,0001"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0001)= 0,0001"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0001) - (0)|= 0,0001"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / ((R - 0,40*(t - tm + tw))*cos(α))
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= 2*16 700*1,00*0,70*(0,0625 - 0 + (-0,0001)) / ((0,75 - 0,40*(0,0625 - 0 + (-0,0001)))*cos(63,3005))= 4 476,16 psi
Operating, Hot & New, Bottom Seam
tp = P*R / [(2*St*Ks*Ec + 0,40*|P|)*cos(α)] (Pressure)= 0,01*0,75 / [(2*16 700*1,00*0,70 + 0,40*|0,01|)*cos(63,3005)]= 0"
tm = M / [(π*Rm2*St*Ks*Ec)*cos(α)] (bending)
= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -3,5 / [(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]= -0,0001"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0001)= 0,0001"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0001) - (0)|= 0,0001"
Maximum allowable working pressure, Longitudinal Stress
P = 2*St*Ks*Ec*(t - tm + tw) / ((R - 0,40*(t - tm + tw))*cos(α))= 2*16 700*1,00*0,70*(0,0625 - 0 + (-0,0001)) / ((0,75 - 0,40*(0,0625 - 0 + (-0,0001)))*cos(63,3005))= 4 476,16 psi
Hot Shut Down, Corroded, Bottom Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -3,5 / [(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]= -0,0001"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0001)= 0,0001"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0001) - (0)|= 0,0001"
Hot Shut Down, New, Bottom Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -3,5 / [(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]
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= -0,0001"
tt = tp + tm - tw(totalrequired,tensile)
= 0 + 0 - (-0,0001)= 0,0001"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0001) - (0)|= 0,0001"
Empty, Corroded, Bottom Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)
= 0 /[(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]
= 0"tt = tp + tm - tw (total required, tensile)
= 0 + 0 - (0)= 0"
tc = tmc + twc - tpc(total required,compressive)
= 0 + (0) - (0)= 0"
Empty, New, Bottom Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)
= 0 /[(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]
= 0"tt = tp + tm - tw (total required, tensile)
= 0 + 0 - (0)= 0"
tc = tmc + twc - tpc(total required,compressive)
= 0 + (0) - (0)= 0"
Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Bottom Seam
tp = 0" (Pressure)tm = M / [(π*Rm
2*St*Ks*Ec)*cos(α)] (bending)= 0 / [(π*0,81962*16 700*1,00*0,70)*cos(63,3005)]= 0"
tw = W / [(2*π*Rm*St*Ks*Ec)*cos(α)] (Weight)= -3,5 / [(2*π*0,8196*16 700*1,00*0,70)*cos(63,3005)]= -0,0001"
tt = tp + tm - tw (total
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required,tensile)
= 0 + 0 - (-0,0001)= 0,0001"
tc = |tmc + twc - tpc|(total, nettensile)
= |0 + (-0,0001) - (0)|= 0,0001"
Appendix 1-5 calculations are not required for the transition large end as a knuckle is present.
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