11522 - tank horizontale 29 000l
DESCRIPTION
horizTRANSCRIPT
Falco Technologies Inc.
1245, rue Industrielle
La Prairie (Québec) J5R 2E4
CANADA
COMPRESS Pressure Vessel Design Calculations
Item: Tank 29 000L Horizontal
Vessel No: -
Customer: Laporte
Contract: 11522
Designer: Ryadh Dahli ing. Jr. (#OIQ = 5053176)
Date: 03-12-2015
Table of ContentsGeneral Arrangement Drawing................................................................................................................................1/81
Deficiencies Summary..............................................................................................................................................2/81
Pressure Summary...................................................................................................................................................3/81
Revision History........................................................................................................................................................4/81
Settings Summary.....................................................................................................................................................5/81
Radiography Summary.............................................................................................................................................7/81
Thickness Summary.................................................................................................................................................8/81
Weight Summary.......................................................................................................................................................9/81
Long Seam Summary.............................................................................................................................................10/81
Hydrostatic Test......................................................................................................................................................12/81
Vacuum Summary...................................................................................................................................................13/81
Engineering Notes..................................................................................................................................................14/81
Liquid Level bounded by F&D Head #1.................................................................................................................15/81
F&D Head #2............................................................................................................................................................16/81
Straight Flange on F&D Head #2............................................................................................................................23/81
Cylinder #1...............................................................................................................................................................27/81
Cylinder #2...............................................................................................................................................................31/81
Cylinder #3...............................................................................................................................................................35/81
Cylinder #4...............................................................................................................................................................39/81
Rings #1...................................................................................................................................................................43/81
Cylinder #5...............................................................................................................................................................46/81
Cylinder #6...............................................................................................................................................................50/81
Straight Flange on F&D Head #1............................................................................................................................54/81
F&D Head #1............................................................................................................................................................58/81
Saddle #1.................................................................................................................................................................65/81
Seismic Code...........................................................................................................................................................81/81
i
General Arrangement Drawing
1/81
Deficiencies Summary
Deficiencies for Saddle #1Circumferential stress at the wear plate horns is excessive.
2/81
Pressure Summary
Component Summary
IdentifierP
Design(psi)
T
Design(°F)
MAWP(psi)
MAP(psi)
MAEP(psi)
Te
external(°F)
MDMT(°F)
MDMTExemption
ImpactTested
F&D Head #2 14,7 176 14,79 18,18 2,23 176 -320 Note 1 No
Straight Flange on F&D Head #2 14,7 176 35,92 39,31 1,34 176 -320 Note 1 No
Cylinder #1 14,7 176 51,17 54,56 2,96 176 -320 Note 2 No
Cylinder #2 14,7 176 35,92 39,31 1,34 176 -320 Note 1 No
Cylinder #3 14,7 176 35,92 39,31 1,34 176 -320 Note 1 No
Cylinder #4 14,7 176 35,92 39,31 1,34 176 -320 Note 1 No
Cylinder #5 14,7 176 35,92 39,31 1,34 176 -320 Note 1 No
Cylinder #6 14,7 176 51,17 54,56 2,96 176 -320 Note 2 No
Straight Flange on F&D Head #1 14,7 176 35,92 39,31 1,34 176 -320 Note 1 No
F&D Head #1 14,7 176 14,79 18,18 2,23 176 -320 Note 1 No
Rings #1 N/A N/A N/A N/A 1,33 176 N/A N/A No
Saddle #1 14,7 176 14,79 N/A N/A N/A N/A N/A N/A
Chamber Summary
Design MDMT -20 °F
Rated MDMT -320 °F @ 14,79 psi
MAWP hot & corroded 14,79 psi @ 176 °F
MAP cold & new 18,18 psi @ 70 °F
MAEP 1,33 psi @ 176 °F
Notes for MDMT Rating
Note # Exemption Details
1. Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
2. Impact test exempt per UHA-51(g) (coincident ratio = 0,2662)
3/81
Revision History
Revisions
No. Date Operator Notes
0 12/ 2/2015 rdahli New vessel created ASME Section VIII Division 1 [COMPRESS 2015 Build 7500]
4/81
Settings Summary
COMPRESS 2015 Build 7500
ASME Section VIII Division 1, 2013 Edition
Units U.S. Customary
Datum Line Location 0,00" from right 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 No
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
5/81
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 Yes
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.
6/81
Radiography Summary
UG-116 Radiography
ComponentLongitudinal Seam Left Circumferential Seam Right 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 #2 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
Cylinder #2 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B None UW-11(c) / Type 1 None
Cylinder #3 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B None UW-11(c) / Type 1 None
Cylinder #4 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B None UW-11(c) / Type 1 None
Cylinder #5 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B None UW-11(c) / Type 1 None
Cylinder #6 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 B None UW-11(c) / Type 1 None
F&D Head #1 A None UW-11(c) / Type 1 B None UW-11(c) / Type 1 N/A N/A None
UG-116(e) Required Marking: None
7/81
Thickness Summary
Component Data
ComponentIdentifier
Material Diameter(in)
Length(in)
Nominal t(in)
Design t(in)
Total Corrosion(in)
JointE
Load
F&D Head #2 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 16,5101 0,1091* 0,1087 0 0,70 Internal
Straight Flange on F&D Head #2 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 1 0,135 0,1216 0 0,70 External
Cylinder #1 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 48 0,1875 0,1216 0 0,70 External
Cylinder #2 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 12 0,135 0,1216 0 0,70 External
Cylinder #3 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 48 0,135 0,1216 0 0,70 External
Cylinder #4 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 48 0,135 0,1216 0 0,70 External
Cylinder #5 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 48 0,135 0,1216 0 0,70 External
Cylinder #6 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 48 0,1875 0,1216 0 0,70 External
Straight Flange on F&D Head #1 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 1 0,135 0,1216 0 0,70 External
F&D Head #1 304L- Buffed - Ryadh Dahli (Full User Defined) 96 ID 16,5101 0,1091* 0,1087 0 0,70 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
8/81
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 #2 285,1 285,1 0 0 0 0 2 879,1 2 879,1 2 884,1 2 884,1 64
Cylinder #1 788,7 788,7 0 0 0 0 12 477,8 12 477,8 12 541,4 12 541,4 101
Cylinder #2 141,9 141,9 0 0 0 0 3 119,4 3 119,4 3 135,3 3 135,3 25
Cylinder #3 567,6 567,6 0 0 0 0 12 477,8 12 477,8 12 541,4 12 541,4 101
Cylinder #4 567,6 567,6 0 0 0 0 12 477,8 12 477,8 12 541,4 12 541,4 101
Cylinder #5 567,6 567,6 0 0 0 0 12 477,8 12 477,8 12 541,4 12 541,4 101
Cylinder #6 788,7 788,7 0 0 0 0 12 477,8 12 477,8 12 541,4 12 541,4 101
F&D Head #1 285,1 285,1 0 0 0 0 2 879,1 2 879,1 2 884,1 2 884,1 64
Saddle #1 1 412 1 412 0 0 0 0 0 0 0 0 141
TOTAL: 5 404,1 5 404,1 0 0 0 0 71 266,5 71 266,5 71 610,5 71 610,5 799
*Shells with attached nozzles have weight reduced by material cut out for opening.
Weight (lb) Contributed by Attachments
Component Body Flanges Nozzles &Flanges Packed
Beds Trays TraySupports
Rings &Clips
VerticalLoads
Surface Areaft2
New Corroded New Corroded
F&D Head #2 0 0 0 0 0 0 0 0 0 0
Cylinder #1 0 0 0 0 0 0 0 0 0 0
Cylinder #2 0 0 0 0 0 0 0 0 0 0
Cylinder #3 0 0 0 0 0 0 0 0 0 0
Cylinder #4 0 0 0 0 0 0 0 43,7 0 9
Cylinder #5 0 0 0 0 0 0 0 0 0 0
Cylinder #6 0 0 0 0 0 0 0 0 0 0
F&D Head #1 0 0 0 0 0 0 0 0 0 0
TOTAL: 0 0 0 0 0 0 0 43,7 0 9
Vessel Totals
New Corroded
Operating Weight (lb) 76 714 76 714
Empty Weight (lb) 5 448 5 448
Test Weight (lb) 77 058 77 058
Surface Area (ft2) 808 -
Capacity** (US gal) 8 588 8 588
**The vessel capacity does not includevolume of nozzle, piping or otherattachments.
Vessel Lift Condition
Vessel Lift Weight, New (lb) 5 448
Center of Gravity from Datum (in) 126
9/81
Long Seam Summary
Shell Long Seam Angles
Component Seam 1 Seam 2
Cylinder #1 0° 285,9205°
Cylinder #2 30° 315,9205°
Cylinder #3 0° 285,9205°
Cylinder #4 30° 315,9205°
Cylinder #5 0° 285,9205°
Cylinder #6 30° 315,9205°
Shell Plate Lengths
Component StartingAngle Plate 1 Plate 2
Cylinder #1 0° 240" 62,1819"
Cylinder #2 30° 239,869" 62,148"
Cylinder #3 0° 239,869" 62,148"
Cylinder #4 30° 239,869" 62,148"
Cylinder #5 0° 239,869" 62,148"
Cylinder #6 30° 240" 62,1819"
Note
1) Plate Lengths use the circumference of the vessel based on the mid diameter of the components.
10/81
Shell Rollout
11/81
Hydrostatic Test
Horizontal shop hydrostatic test based on MAWP per UG-99(b)
Gauge pressure at 70°F =1,3*MAWP*LSR= 1,3*14,79*1= 19,22 psi
Horizontal shop hydrostatic test
IdentifierLocal testpressure
(psi)
Test liquidstatic head
(psi)
UG-99(b)stressratio
UG-99(b)pressure
factor
F&D Head #2 (1) 22,69 3,465 1 1,30
Straight Flange on F&D Head #2 22,69 3,465 1 1,30
Cylinder #1 22,69 3,465 1 1,30
Cylinder #2 22,69 3,465 1 1,30
Cylinder #3 22,69 3,465 1 1,30
Cylinder #4 22,69 3,465 1 1,30
Cylinder #5 22,69 3,465 1 1,30
Cylinder #6 22,69 3,465 1 1,30
Straight Flange on F&D Head #1 22,69 3,465 1 1,30
F&D Head #1 22,69 3,465 1 1,30
(1) F&D Head #2 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.
12/81
Vacuum Summary
Largest Unsupported Length Le
Component Line of SupportElevation
above Datum(in)
Length Le(in)
F&D Head #2 - 269,5101 N/A
- 1/3 depth of F&D Head #2 258,467 N/A
Straight Flange on F&D Head #2 Left - 253 132,467
Straight Flange on F&D Head #2 Right - 252 132,467
Cylinder #1 Left - 252 132,467
Cylinder #1 Right - 204 132,467
Cylinder #2 Left - 204 132,467
Cylinder #2 Right - 192 132,467
Cylinder #3 Left - 192 132,467
Cylinder #3 Right - 144 132,467
Cylinder #4 Left - 144 132,467
- Rings #1 126 132,467
Cylinder #4 Right - 96 132,467
Cylinder #5 Left - 96 132,467
Cylinder #5 Right - 48 132,467
Cylinder #6 Left - 48 132,467
Cylinder #6 Right - 0 132,467
Straight Flange on F&D Head #1 Left - 0 132,467
Straight Flange on F&D Head #1 Right - -1 132,467
- 1/3 depth of F&D Head #1 -6,467 N/A
F&D Head #1 - -17,5101 N/A
For Rings, the listed value of 'Le' is Ls per UG-29.
13/81
Engineering Notes
Les depassement des contraintes dans les support ( 35000 psi vs allowable 30000 psi) est jugé acceptable.
Ryadh Dahli ing. jr.#OIQ :505317604-12-2015
14/81
Liquid Level bounded by F&D Head #1
ASME Section VIII Division 1, 2013 Edition
Location from Center Line (in) 46
Operating Liquid Specific Gravity 1
15/81
F&D Head #2
ASME Section VIII Division 1, 2013 Edition
Component F&D Head
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
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 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Crown Radius L 96"
Knuckle Radius r 6"
Minimum Thickness 0,1091"
Corrosion Inner 0"
Outer 0"
Length Lsf 1"
Nominal Thickness tsf 0,135"
Weight and Capacity
Weight (lb)1 Capacity (US gal)1
New 285,1 345,88
Corroded 285,1 345,88
Radiography
Category A joints None UW-11(c) Type 1
Head to shell seam None UW-11(c) Type 11includes straight flange
16/81
Results Summary
Governing condition internal pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,1087"
Design thickness due to external pressure (te) 0,0731"
Maximum allowable working pressure (MAWP) 14,79 psi
Maximum allowable pressure (MAP) 18,18 psi
Maximum allowable external pressure (MAEP) 2,23 psi
Rated MDMT -320°F
Note: Endnote 90 used to determine allowable stress.
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -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 + (96 / 6)1/2] 1,75
New M = 1/4*[3 + (96 / 6)1/2] 1,75
Design thickness for internal pressure, (Corroded at 176 °F) Appendix 1-4(d)
t = P*L*M / (2*S*E - 0,2*P) + Corrosion= 18,09*96*1,75 / (2*20 000*0,7 - 0,2*18,09) + 0= 0,1086"
Design thickness for internal pressure, (Corroded at 176 °F) Appendix 1-4(f)(1)
0,0005 ≤ (tmin head - Corrosion) / L = 0,1091 / 96 = 0,0011 < 0,002
r / D = 0,0625 ≤ 0,08
C1 = 9,31*r / D - 0,086= 9,31*0,0625 - 0,086= 0,4959
Se = C1*ET*(t / r)= 0,4959*27,65E+06*(0,1087 / 6)= 248 336 psi
C2 = 1,25
φ = (L*t)0,5 / r= (96*0,1087)0,5 / 6
17/81
= 0,53835 radians
a = 0,5*D - r= 0,5*96 -6= 42"
b = L - r= 96 - 6= 90"
β = arc cos(a / b)= arc cos(42 / 90)= 1,085278 radians
φ = 0,5383 < β = 1,0853
c = a / (cos(β - φ))= 42 / (cos(1,0853 - 0,5383))= 49,173083"
Re = c + r= 49,1731 + 6= 55,173083"
Pe = Se*t / (C2*Re*[(0,5*Re / r) - 1])= 248 336*0,1087 / (1,25*55,1731*[(0,5*55,1731 / 6) - 1])= 108,78 psi
Py = Sy*t / (C2*Re*[(0,5*Re / r) - 1])= 35 000*0,1087 / (1,25*55,1731*[(0,5*55,1731 / 6) - 1])= 15,33 psi
1 ≤ Pe / Py = 108,78 / 15,33 = 7,1 ≤ 8,29
Pck = 0,408*Py + 0,192*Pe= 0,408*15,33 + 0,192*108,78= 27,14 psi
Pck / 1,5 = 18,09 psi ≥ Internal design pressure P = 18,09 psi
t = tr + Corrosion= 0,108683 + 0= 0,108683"
Design thickness is acceptable per Appendix 1-4(f) for a design pressure of 14,7 psi.
The head internal pressure design thickness is 0,1087".
Maximum allowable working pressure, (Corroded at 176 °F) Appendix 1-4(d)
P = 2*S*E*t / (L*M + 0,2*t) - Ps= 2*20 000*0,7*0,1091 / (96*1,75 + 0,2*0,1091) - 3,39= 14,79 psi
18/81
Maximum allowable working pressure, (Corroded at 176 °F) Appendix 1-4(f)(1)
0,0005 ≤ (tmin head - Corrosion) / L = 0,1091 / 96 = 0,0011 < 0,002
r / D = 0,0625 ≤ 0,08
C1 = 9,31*r / D - 0,086= 9,31*0,0625 - 0,086= 0,4959
Se = C1*ET*(t / r)= 0,4959*27,65E+06*(0,1091 / 6)= 249 290 psi
C2 = 1,25
φ = (L*t)0,5 / r= (96*0,1091)0,5 / 6= 0,539382 radians
a = 0,5*D - r= 0,5*96 -6= 42"
b = L - r= 96 - 6= 90"
β = arc cos(a / b)= arc cos(42 / 90)= 1,085278 radians
φ = 0,5394 < β = 1,0853
c = a / (cos(β - φ))= 42 / (cos(1,0853 - 0,5394))= 49,142204"
Re = c + r= 49,1422 + 6= 55,142204"
Pe = Se*t / (C2*Re*[(0,5*Re / r) - 1])= 249 290*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 109,75 psi
Py = Sy*t / (C2*Re*[(0,5*Re / r) - 1])= 35 000*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 15,41 psi
1 ≤ Pe / Py = 109,75 / 15,41 = 7,12 ≤ 8,29
Pck = 0,408*Py + 0,192*Pe= 0,408*15,41 + 0,192*109,75= 27,36 psi
19/81
Pck / 1,5 = 18,24 psi
P = Pck / 1,5 - Ps= 27,36 / 1,5 - 3,39= 14,85 psi
The maximum allowable working pressure (MAWP) is 14,79 psi.
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(d)
P = 2*S*E*t / (L*M + 0,2*t) - Ps= 2*20 000*0,7*0,1091 / (96*1,75 + 0,2*0,1091) - 0= 18,18 psi
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(f)(1)
0,0005 ≤ (tmin head - Corrosion) / L = 0,1091 / 96 = 0,0011 < 0,002
r / D = 0,0625 ≤ 0,08
C1 = 9,31*r / D - 0,086= 9,31*0,0625 - 0,086= 0,4959
Se = C1*ET*(t / r)= 0,4959*28,3E+06*(0,1091 / 6)= 255 171 psi
C2 = 1,25
φ = (L*t)0,5 / r= (96*0,1091)0,5 / 6= 0,539382 radians
a = 0,5*D - r= 0,5*96 -6= 42"
b = L - r= 96 - 6= 90"
β = arc cos(a / b)= arc cos(42 / 90)= 1,085278 radians
φ = 0,5394 < β = 1,0853
c = a / (cos(β - φ))= 42 / (cos(1,0853 - 0,5394))= 49,142204"
Re = c + r= 49,1422 + 6= 55,142204"
20/81
Pe = Se*t / (C2*Re*[(0,5*Re / r) - 1])= 255 171*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 112,34 psi
Py = Sy*t / (C2*Re*[(0,5*Re / r) - 1])= 35 000*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 15,41 psi
1 ≤ Pe / Py = 112,34 / 15,41 = 7,29 ≤ 8,29
Pck = 0,408*Py + 0,192*Pe= 0,408*15,41 + 0,192*112,34= 27,86 psi
Pck / 1,5 = 18,57 psi
P = Pck / 1,5 - Ps= 27,86 / 1,5 - 0= 18,57 psi
The maximum allowable pressure (MAP) is 18,18 psi.
Design thickness for external pressure, (Corroded at 176 °F) UG-33(e)
Equivalent outside spherical radius (Ro)= Outside crown radius= 96,1091 in
A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,073045)= 0,000095
From TableHA-3: B = 1 315,7465
psi
Pa = B / (Ro / t)= 1 315,7465 / (96,1091 / 0,073)= 1 psi
t = 0,073" + Corrosion = 0,073" + 0" = 0,073"Check the external pressure per UG-33(a)(1) Appendix 1-4(d)
t = 1,67*Pe*L*M / (2*S*E - 0,2*1,67*Pe) + Corrosion= 1,67*1*96*1,75 / (2*20 000*1 - 0,2*1,67*1) + 0= 0,007"
The head external pressure design thickness (te) is 0,073".
Maximum Allowable External Pressure, (Corroded at 176 °F) UG-33(e)
Equivalent outside spherical radius (Ro)= Outside crown radius= 96,1091 in
21/81
A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,1091)= 0,000142
From TableHA-3: B = 1 962,9103
psi
Pa = B / (Ro / t)= 1 962,9103 / (96,1091 / 0,1091)= 2,2282 psi
Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(d)
P = 2*S*E*t / ((L*M + 0,2*t)*1,67)= 2*20 000*1*0,1091 / ((96*1,75 + 0,2*0,1091)*1,67)= 15,55 psi
The maximum allowable external pressure (MAEP) is 2,23 psi.
% Forming strain - UHA-44(a)(2)
EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*0,135 / 6,0675)*(1 - 6,0675 / infinity)= 1,6687%
22/81
Straight Flange on F&D Head #2
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 1"
Nominal Thickness 0,135"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 11,82 31,33
Corroded 11,82 31,33
Radiography
Longitudinal seam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
23/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 35,92 psi
Maximum allowable pressure (MAP) 39,31 psi
Maximum allowable external pressure (MAEP) 1,34 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,135 / (48 + 0,60*0,135) - 3,39= 35,92 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,1216 = 791,9654From table G: A = 0,000043From tableHA-3: B = 593,9766 psi
Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"
24/81
Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,135 = 713,1111From table G: A = 0,000052From tableHA-3: B = 717,0059 psi
Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,135 / 48,0675)*(1 - 48,0675 / infinity)= 0,1404%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 4 837 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 4 837 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 959 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 4 959 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 4 959 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
25/81
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 4 837 psi
26/81
Cylinder #1
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 48"
Nominal Thickness 0,1875"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 788,69 1 504,05
Corroded 788,69 1 504,05
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
27/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 51,17 psi
Maximum allowable pressure (MAP) 54,56 psi
Maximum allowable external pressure (MAEP) 2,96 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
tr = 18,18*48 / (20 000*0,7 - 0.6*18,18) = 0,0624"
Stress ratio = tr*E* / (tn - c) = 0,0624*0,8 / (0,1875 - 0) = 0,2662
Impact test exempt per UHA-51(g) (coincident ratio = 0,2662)
Rated MDMT = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,1875 / (48 + 0,60*0,1875) - 3,39= 51,17 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,1875 / (48 + 0,60*0,1875)= 54,56 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,375 = 1,3745Do / t = 96,375 / 0,1216 = 792,2514From table G: A = 0,000043From tableHA-3: B = 594,1889 psi
Pa = 4*B / (3*(Do / t))= 4*594,19 / (3*(96,375 / 0,1216))= 1 psi
28/81
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,375 = 1,3745Do / t = 96,375 / 0,1875 = 514,0000From table G: A = 0,000082From tableHA-3: B = 1 139,2798 psi
Pa = 4*B / (3*(Do / t))= 4*1 139,28 / (3*(96,375 / 0,1875))= 2,96 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,1875 / 48,0938)*(1 - 48,0938 / infinity)= 0,1949%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,1875 / 0,1875)= 0,000486
B = 6 294 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 6 294 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 6 294 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,1875 / 0,1875)= 0,000486
B = 6 867 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 6 867 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 6 867 psi
29/81
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,1875 / 0,1875)= 0,000486
B = 6 294 psi
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 6 294 psi
30/81
Cylinder #2
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 12"
Nominal Thickness 0,135"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 141,89 376,01
Corroded 141,89 376,01
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
31/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 35,92 psi
Maximum allowable pressure (MAP) 39,31 psi
Maximum allowable external pressure (MAEP) 1,34 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,135 / (48 + 0,60*0,135) - 3,39= 35,92 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,1216 = 791,9654From table G: A = 0,000043From tableHA-3: B = 593,9766 psi
Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"
32/81
Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,135 = 713,1111From table G: A = 0,000052From tableHA-3: B = 717,0059 psi
Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,135 / 48,0675)*(1 - 48,0675 / infinity)= 0,1404%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 4 837 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 4 837 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 959 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 4 959 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 4 959 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
33/81
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 4 837 psi
34/81
Cylinder #3
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 48"
Nominal Thickness 0,135"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 567,55 1 504,05
Corroded 567,55 1 504,05
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
35/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 35,92 psi
Maximum allowable pressure (MAP) 39,31 psi
Maximum allowable external pressure (MAEP) 1,34 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,135 / (48 + 0,60*0,135) - 3,39= 35,92 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,1216 = 791,9654From table G: A = 0,000043From tableHA-3: B = 593,9766 psi
Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"
36/81
Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,135 = 713,1111From table G: A = 0,000052From tableHA-3: B = 717,0059 psi
Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,135 / 48,0675)*(1 - 48,0675 / infinity)= 0,1404%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 4 837 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 4 837 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 959 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 4 959 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 4 959 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
37/81
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 4 837 psi
38/81
Cylinder #4
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 48"
Nominal Thickness 0,135"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 567,55 1 504,05
Corroded 567,55 1 504,05
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
39/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 35,92 psi
Maximum allowable pressure (MAP) 39,31 psi
Maximum allowable external pressure (MAEP) 1,34 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,135 / (48 + 0,60*0,135) - 3,39= 35,92 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,1216 = 791,9654From table G: A = 0,000043From tableHA-3: B = 593,9766 psi
Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"
40/81
Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,135 = 713,1111From table G: A = 0,000052From tableHA-3: B = 717,0059 psi
Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,135 / 48,0675)*(1 - 48,0675 / infinity)= 0,1404%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 4 837 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 4 837 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 959 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 4 959 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 4 959 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
41/81
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 4 837 psi
42/81
Rings #1
ASME Section VIII Division 1, 2013 Edition
Attached to Cylinder #4
Ring type Equal leg angle rolled the hard way
Description 2x2x1/8 Equal Angle
Material SA-240 304L (II-D p. 86, ln. 43)
External design pressure 1 psi
External design temperature 176°F
Corrosion allowance 0"
Distance from ring neutral axis to datum 126"
Distance to previous support 132,467"
Distance to next support 132,467"
Internal ring No
Welds
Weld configuration Staggered intermittent
Fillet weld leg size 0,375"
Length of individual weld segments 3"
Spacing between toes of weld segments 1,08"
Vessel thickness at weld location, new 0,135"
Vessel corrosion allowance at weld location 0"
Stiffener thickness at weld location 0,125"
Ring Properties
Max depth to thickness ratio 36
Ring distance to centroid 1,454"
Ring area 0,484 in2
Ring inertia 0,19 in4
External Pressure, (Corroded & at 176°F) UG-29(a)
L / Do = 132,467 / 96,27 = 1,376Do / t = 96,27 / 0,1216 = 791,7852From Table G: A = 4,2809E-05From Table HA-3: B = 594,25 psi
Pa = 4*B / (3*(Do / t))= 4*594,25 / (3*(96,27 / 0,121586))= 1 psi
B = 0,75*P*Do / (t + As / Ls)= 0,75*1*96,27 / (0,1216 + 0,484 / 132,467)
43/81
= 576 psi
From Table HA-3: A = 0,000041 (ring, 176°F)
Is' = [Do2*Ls*(t + As / Ls)*A] / 10,9
= [96,272*132,467*(0,1216 + 0,484 / 132,467)*0,000041] / 10,9= 0,585 in4
I' for the composite corroded shell-ring cross section is 0,7793 in4
As I' >= Is' a 2x2x1/8 Equal Angle stiffener is adequate for an external pressure of 1 psi.
Check the stiffener ring attachment welds per UG-30Per UG-30(f)(3) the minimum attachment weld size is 0,125 in
The fillet weld size of 0,375 in is adequate per UG-30(f)(3).
Radial pressure load, P*Ls = 1*132,467 = 132,47 lbf/inRadial shear load, V = 0,01*P*Ls*Do = 0,01*1*132,467*96,27 = 127,53 lbfFirst moment of area, Q = 0,54*0,7224 = 0,3868 in3
Weld shear flow, q = V*Q / I' = 63,2923 lbf/inCombined weld load, fw = Sqr(132,4672 + 63,29232) = 146,81 lbf/in
Allowable weld stress per UW-18(d) Sw = 0,55*S = 0,55*16 700 = 9 185 psi
Fillet weld size required to resist radial pressure and shear
tw = fw*(dweld segment
+ dtoe
) / (Sw*dweld total
) + corrosion= 146,81*(3 + 1,08) / (9 185*6) + 0= 0,0109 in
The fillet weld size of 0,375 in is adequate to resist radial pressure and shear.
Maximum Allowable External Pressure, (Corroded & at 176°F) UG-29(a)
L / Do = 132,467 / 96,27 = 1,376Do / t = 96,27 / 0,1346 = 715,0338From Table G: A = 5,1463E-05From Table HA-3: B = 714,01 psi
Pa = 4*B / (3*(Do / t))= 4*714,01 / (3*(96,27 / 0,134637))= 1,33 psi
B = 0,75*P*Do / (t + As / Ls)= 0,75*1,33*96,27 / (0,1346 + 0,484 / 132,467)= 695 psi
From Table HA-3: A = 0,00005 (ring, 176°F)
Is' = [Do2*Ls*(t + As / Ls)*A] / 10,9
= [96,272*132,467*(0,1346 + 0,484 / 132,467)*0,00005] / 10,9= 0,7792 in4
I' for the composite corroded shell-ring cross section is 0,7793 in4
44/81
As I' >= Is' a 2x2x1/8 Equal Angle stiffener is adequate for an external pressure of 1,33 psi.
Check the stiffener ring attachment welds per UG-30Per UG-30(f)(3) the minimum attachment weld size is 0,125 in
The fillet weld size of 0,375 in is adequate per UG-30(f)(3).
Radial pressure load, P*Ls = 1,33*132,467 = 176,34 lbf/inRadial shear load, V = 0,01*P*Ls*Do = 0,01*1,33*132,467*96,27 = 169,76 lbfFirst moment of area, Q = 0,54*0,7224 = 0,3868 in3
Weld shear flow, q = V*Q / I' = 84,2551 lbf/inCombined weld load, fw = Sqr(176,34082 + 84,25512) = 195,44 lbf/in
Allowable weld stress per UW-18(d) Sw = 0,55*S = 0,55*16 700 = 9 185 psi
Fillet weld size required to resist radial pressure and shear
tw = fw*(dweld segment
+ dtoe
) / (Sw*dweld total
) + corrosion= 195,44*(3 + 1,08) / (9 185*6) + 0= 0,0145 in
The fillet weld size of 0,375 in is adequate to resist radial pressure and shear.
45/81
Cylinder #5
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 48"
Nominal Thickness 0,135"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 567,55 1 504,05
Corroded 567,55 1 504,05
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
46/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 35,92 psi
Maximum allowable pressure (MAP) 39,31 psi
Maximum allowable external pressure (MAEP) 1,34 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,135 / (48 + 0,60*0,135) - 3,39= 35,92 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,1216 = 791,9654From table G: A = 0,000043From tableHA-3: B = 593,9766 psi
Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"
47/81
Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,135 = 713,1111From table G: A = 0,000052From tableHA-3: B = 717,0059 psi
Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,135 / 48,0675)*(1 - 48,0675 / infinity)= 0,1404%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 4 837 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 4 837 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 959 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 4 959 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 4 959 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
48/81
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 4 837 psi
49/81
Cylinder #6
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 48"
Nominal Thickness 0,1875"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 788,69 1 504,05
Corroded 788,69 1 504,05
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
Right Circumferentialseam None UW-11(c) Type 1
50/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 51,17 psi
Maximum allowable pressure (MAP) 54,56 psi
Maximum allowable external pressure (MAEP) 2,96 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
tr = 18,18*48 / (20 000*0,7 - 0.6*18,18) = 0,0624"
Stress ratio = tr*E* / (tn - c) = 0,0624*0,8 / (0,1875 - 0) = 0,2662
Impact test exempt per UHA-51(g) (coincident ratio = 0,2662)
Rated MDMT = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,1875 / (48 + 0,60*0,1875) - 3,39= 51,17 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,1875 / (48 + 0,60*0,1875)= 54,56 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,375 = 1,3745Do / t = 96,375 / 0,1216 = 792,2514From table G: A = 0,000043From tableHA-3: B = 594,1889 psi
Pa = 4*B / (3*(Do / t))= 4*594,19 / (3*(96,375 / 0,1216))= 1 psi
51/81
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,375 = 1,3745Do / t = 96,375 / 0,1875 = 514,0000From table G: A = 0,000082From tableHA-3: B = 1 139,2798 psi
Pa = 4*B / (3*(Do / t))= 4*1 139,28 / (3*(96,375 / 0,1875))= 2,96 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,1875 / 48,0938)*(1 - 48,0938 / infinity)= 0,1949%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,1875 / 0,1875)= 0,000486
B = 6 294 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 6 294 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 6 294 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,1875 / 0,1875)= 0,000486
B = 6 867 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 6 867 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 6 867 psi
52/81
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,1875 / 0,1875)= 0,000486
B = 6 294 psi
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 6 294 psi
53/81
Straight Flange on F&D Head #1
ASME Section VIII Division 1, 2013 Edition
Component Cylinder
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Length 1"
Nominal Thickness 0,135"
Corrosion Inner 0"
Outer 0"
Weight and Capacity
Weight (lb) Capacity (US gal)
New 11,82 31,33
Corroded 11,82 31,33
Radiography
Longitudinal seam None UW-11(c) Type 1
Left Circumferentialseam None UW-11(c) Type 1
54/81
Results Summary
Governing condition External pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,0621"
Design thickness due to external pressure (te) 0,1216"
Maximum allowable working pressure (MAWP) 35,92 psi
Maximum allowable pressure (MAP) 39,31 psi
Maximum allowable external pressure (MAEP) 1,34 psi
Rated MDMT -320 °F
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -320°F
Material is exempt from impact testing at the Design MDMT of -20°F.
Design thickness, (at 176 °F) UG-27(c)(1)
t = P*R / (S*E - 0,60*P) + Corrosion= 18,09*48 / (20 000*0,70 - 0,60*18,09) + 0= 0,0621"
Maximum allowable working pressure, (at 176 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t) - Ps= 20 000*0,70*0,135 / (48 + 0,60*0,135) - 3,39= 35,92 psi
Maximum allowable pressure, (at 70 °F) UG-27(c)(1)
P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi
External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,1216 = 791,9654From table G: A = 0,000043From tableHA-3: B = 593,9766 psi
Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi
Design thickness for external pressure Pa = 1 psi
ta = t + Corrosion = 0,1216 + 0 = 0,1216"
55/81
Maximum Allowable External Pressure, (Corroded & at 176 °F) UG-28(c)
L / Do = 132,467 / 96,27 = 1,3760Do / t = 96,27 / 0,135 = 713,1111From table G: A = 0,000052From tableHA-3: B = 717,0059 psi
Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi
% Forming strain - UHA-44(a)(2)
EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0,135 / 48,0675)*(1 - 48,0675 / infinity)= 0,1404%
Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
S = 20 000 / 1,00 = 20 000 psi
ScHC = min(B, S) = 4 837 psi
Allowable Compressive Stress, Hot and New- ScHN
ScHN = ScHC
= 4 837 psi
Allowable Compressive Stress, Cold and New- ScCN, (table HA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 959 psi
S = 20 000 / 1,00 = 20 000 psi
ScCN = min(B, S) = 4 959 psi
Allowable Compressive Stress, Cold and Corroded- ScCC
ScCC = ScCN
= 4 959 psi
Allowable Compressive Stress, Vacuum and Corroded- ScVC, (tableHA-3)A = 0,125 / (Ro / t)
= 0,125 / (48,135 / 0,135)= 0,000351
B = 4 837 psi
56/81
S = 20 000 / 1,00 = 20 000 psi
ScVC = min(B, S) = 4 837 psi
57/81
F&D Head #1
ASME Section VIII Division 1, 2013 Edition
Component F&D Head
Material 304L- Buffed - Ryadh Dahli (Full User Defined)
Attached To Cylinder #6
ImpactTested Normalized Fine Grain
Practice PWHT Optimize MDMT/Find MAWP
No No No No No
DesignPressure (psi)
DesignTemperature (°F)
DesignMDMT (°F)
Internal 14,7 176 -20External 1 176
Static Liquid Head
Condition Ps (psi) Hs (in) SG
Operating 3,39 94 1
Test horizontal 3,47 96 1
Dimensions
Inner Diameter 96"
Crown Radius L 96"
Knuckle Radius r 6"
Minimum Thickness 0,1091"
Corrosion Inner 0"
Outer 0"
Length Lsf 1"
Nominal Thickness tsf 0,135"
Weight and Capacity
Weight (lb)1 Capacity (US gal)1
New 285,1 345,88
Corroded 285,1 345,88
Radiography
Category A joints None UW-11(c) Type 1
Head to shell seam None UW-11(c) Type 11includes straight flange
58/81
Results Summary
Governing condition internal pressure
Minimum thickness per UG-16 0,0625" + 0" = 0,0625"
Design thickness due to internal pressure (t) 0,1087"
Design thickness due to external pressure (te) 0,0731"
Maximum allowable working pressure (MAWP) 14,79 psi
Maximum allowable pressure (MAP) 18,18 psi
Maximum allowable external pressure (MAEP) 2,23 psi
Rated MDMT -320°F
Note: Endnote 90 used to determine allowable stress.
UHA-51 Material Toughness Requirements
Rated MDMT per UHA-51(d)(1)(a), (carbon content does not exceed 0,10%) = -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 + (96 / 6)1/2] 1,75
New M = 1/4*[3 + (96 / 6)1/2] 1,75
Design thickness for internal pressure, (Corroded at 176 °F) Appendix 1-4(d)
t = P*L*M / (2*S*E - 0,2*P) + Corrosion= 18,09*96*1,75 / (2*20 000*0,7 - 0,2*18,09) + 0= 0,1086"
Design thickness for internal pressure, (Corroded at 176 °F) Appendix 1-4(f)(1)
0,0005 ≤ (tmin head - Corrosion) / L = 0,1091 / 96 = 0,0011 < 0,002
r / D = 0,0625 ≤ 0,08
C1 = 9,31*r / D - 0,086= 9,31*0,0625 - 0,086= 0,4959
Se = C1*ET*(t / r)= 0,4959*27,65E+06*(0,1087 / 6)= 248 336 psi
C2 = 1,25
φ = (L*t)0,5 / r= (96*0,1087)0,5 / 6
59/81
= 0,53835 radians
a = 0,5*D - r= 0,5*96 -6= 42"
b = L - r= 96 - 6= 90"
β = arc cos(a / b)= arc cos(42 / 90)= 1,085278 radians
φ = 0,5383 < β = 1,0853
c = a / (cos(β - φ))= 42 / (cos(1,0853 - 0,5383))= 49,173083"
Re = c + r= 49,1731 + 6= 55,173083"
Pe = Se*t / (C2*Re*[(0,5*Re / r) - 1])= 248 336*0,1087 / (1,25*55,1731*[(0,5*55,1731 / 6) - 1])= 108,78 psi
Py = Sy*t / (C2*Re*[(0,5*Re / r) - 1])= 35 000*0,1087 / (1,25*55,1731*[(0,5*55,1731 / 6) - 1])= 15,33 psi
1 ≤ Pe / Py = 108,78 / 15,33 = 7,1 ≤ 8,29
Pck = 0,408*Py + 0,192*Pe= 0,408*15,33 + 0,192*108,78= 27,14 psi
Pck / 1,5 = 18,09 psi ≥ Internal design pressure P = 18,09 psi
t = tr + Corrosion= 0,108683 + 0= 0,108683"
Design thickness is acceptable per Appendix 1-4(f) for a design pressure of 14,7 psi.
The head internal pressure design thickness is 0,1087".
Maximum allowable working pressure, (Corroded at 176 °F) Appendix 1-4(d)
P = 2*S*E*t / (L*M + 0,2*t) - Ps= 2*20 000*0,7*0,1091 / (96*1,75 + 0,2*0,1091) - 3,39= 14,79 psi
60/81
Maximum allowable working pressure, (Corroded at 176 °F) Appendix 1-4(f)(1)
0,0005 ≤ (tmin head - Corrosion) / L = 0,1091 / 96 = 0,0011 < 0,002
r / D = 0,0625 ≤ 0,08
C1 = 9,31*r / D - 0,086= 9,31*0,0625 - 0,086= 0,4959
Se = C1*ET*(t / r)= 0,4959*27,65E+06*(0,1091 / 6)= 249 290 psi
C2 = 1,25
φ = (L*t)0,5 / r= (96*0,1091)0,5 / 6= 0,539382 radians
a = 0,5*D - r= 0,5*96 -6= 42"
b = L - r= 96 - 6= 90"
β = arc cos(a / b)= arc cos(42 / 90)= 1,085278 radians
φ = 0,5394 < β = 1,0853
c = a / (cos(β - φ))= 42 / (cos(1,0853 - 0,5394))= 49,142204"
Re = c + r= 49,1422 + 6= 55,142204"
Pe = Se*t / (C2*Re*[(0,5*Re / r) - 1])= 249 290*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 109,75 psi
Py = Sy*t / (C2*Re*[(0,5*Re / r) - 1])= 35 000*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 15,41 psi
1 ≤ Pe / Py = 109,75 / 15,41 = 7,12 ≤ 8,29
Pck = 0,408*Py + 0,192*Pe= 0,408*15,41 + 0,192*109,75= 27,36 psi
61/81
Pck / 1,5 = 18,24 psi
P = Pck / 1,5 - Ps= 27,36 / 1,5 - 3,39= 14,85 psi
The maximum allowable working pressure (MAWP) is 14,79 psi.
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(d)
P = 2*S*E*t / (L*M + 0,2*t) - Ps= 2*20 000*0,7*0,1091 / (96*1,75 + 0,2*0,1091) - 0= 18,18 psi
Maximum allowable pressure, (New at 70 °F) Appendix 1-4(f)(1)
0,0005 ≤ (tmin head - Corrosion) / L = 0,1091 / 96 = 0,0011 < 0,002
r / D = 0,0625 ≤ 0,08
C1 = 9,31*r / D - 0,086= 9,31*0,0625 - 0,086= 0,4959
Se = C1*ET*(t / r)= 0,4959*28,3E+06*(0,1091 / 6)= 255 171 psi
C2 = 1,25
φ = (L*t)0,5 / r= (96*0,1091)0,5 / 6= 0,539382 radians
a = 0,5*D - r= 0,5*96 -6= 42"
b = L - r= 96 - 6= 90"
β = arc cos(a / b)= arc cos(42 / 90)= 1,085278 radians
φ = 0,5394 < β = 1,0853
c = a / (cos(β - φ))= 42 / (cos(1,0853 - 0,5394))= 49,142204"
Re = c + r= 49,1422 + 6= 55,142204"
62/81
Pe = Se*t / (C2*Re*[(0,5*Re / r) - 1])= 255 171*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 112,34 psi
Py = Sy*t / (C2*Re*[(0,5*Re / r) - 1])= 35 000*0,1091 / (1,25*55,1422*[(0,5*55,1422 / 6) - 1])= 15,41 psi
1 ≤ Pe / Py = 112,34 / 15,41 = 7,29 ≤ 8,29
Pck = 0,408*Py + 0,192*Pe= 0,408*15,41 + 0,192*112,34= 27,86 psi
Pck / 1,5 = 18,57 psi
P = Pck / 1,5 - Ps= 27,86 / 1,5 - 0= 18,57 psi
The maximum allowable pressure (MAP) is 18,18 psi.
Design thickness for external pressure, (Corroded at 176 °F) UG-33(e)
Equivalent outside spherical radius (Ro)= Outside crown radius= 96,1091 in
A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,073045)= 0,000095
From TableHA-3: B = 1 315,7465
psi
Pa = B / (Ro / t)= 1 315,7465 / (96,1091 / 0,073)= 1 psi
t = 0,073" + Corrosion = 0,073" + 0" = 0,073"Check the external pressure per UG-33(a)(1) Appendix 1-4(d)
t = 1,67*Pe*L*M / (2*S*E - 0,2*1,67*Pe) + Corrosion= 1,67*1*96*1,75 / (2*20 000*1 - 0,2*1,67*1) + 0= 0,007"
The head external pressure design thickness (te) is 0,073".
Maximum Allowable External Pressure, (Corroded at 176 °F) UG-33(e)
Equivalent outside spherical radius (Ro)= Outside crown radius= 96,1091 in
63/81
A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,1091)= 0,000142
From TableHA-3: B = 1 962,9103
psi
Pa = B / (Ro / t)= 1 962,9103 / (96,1091 / 0,1091)= 2,2282 psi
Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(d)
P = 2*S*E*t / ((L*M + 0,2*t)*1,67)= 2*20 000*1*0,1091 / ((96*1,75 + 0,2*0,1091)*1,67)= 15,55 psi
The maximum allowable external pressure (MAEP) is 2,23 psi.
% Forming strain - UHA-44(a)(2)
EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*0,135 / 6,0675)*(1 - 6,0675 / infinity)= 1,6687%
64/81
Saddle #1
ASME Section VIII Division 1, 2013 Edition
Saddle Material
Saddle Construction Web at edge of rib
Welded to Vessel Yes
Saddle Allowable Stress, Ss 26 000 psi
Saddle Yield Stress, Sy 38 000 psi
Foundation Allowable Stress 1 658 psi
DesignPressure Left Saddle Right Saddle
Operating 18,18 psi
Test 22,69 psi
Vacuum 1 psi
Dimensions
Right saddle distance to datum 25"
Tangent To Tangent Length, L 254"
Saddle separation, Ls 202"
Vessel Radius, R 48,1875"
Tangent Distance Left, Al 26"
Tangent Distance Right, Ar 26"
Saddle Height, Hs 60,1563"
Saddle Contact Angle, θ 140°
Web Plate Thickness, ts 0,5"
Base Plate Length, E 84,4"
Base Plate Width, F 16"
Base Plate Thickness, tb 0,4375"
Number of Stiffening Ribs, n 6
Largest Stiffening Rib Spacing, di 16,705"
Stiffening Rib Thickness, tw 0,25"
Saddle Width, b 14"
Reinforcing Plate
Thickness, tp 0,1875"
Width, Wp 24"
Contact Angle, θw 160°
Bolting
65/81
Material
Bolt Allowable Shear 15 000 psi
Description 1,125" series 8 threaded
Corrosion on root 0"
Anchor Bolts per Saddle 2
Base coefficient of friction, µ 0,45
Weight
Operating,Corroded Hydrotest
Weight on Left Saddle 37 651 lb 37 823 lb
Weight on Right Saddle 37 651 lb 37 823 lb
Weight of Saddle Pair 1 456 lb
Notes
(1) Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels onTwo Saddle Supports" by L.P. Zick.
66/81
Stress Summary
Load Condition Saddle
Bending + pressure between saddles(psi)
Bending + pressure at the saddle(psi)
S1(+)
allow(+)
S1(-)
allow(-)
S2(+)
allow(+)
S2(-)
allow(-)
Seismic Operating Right Saddle 4 888 16 800 1 655 5 804 2 496 24 000 169 7 553
Left Saddle 2 496 24 000 169 7 553
Seismic Vacuum Right Saddle 1 655 16 800 1 833 5 804 169 24 000 297 7 553
Left Saddle 169 24 000 297 7 553
Weight Test Right Saddle 5 429 22 050 1 395 4 959 3 064 31 500 159 6 867
Left Saddle 3 064 31 500 159 6 867
Stress Summary
Load Condition Saddle
Tangentialshear (psi)
Circumferentialstress (psi)
Stress oversaddle (psi) Splitting (psi)
S3 allow S4(horns)
S4(Wearplate)
allow(+/-) S5 allow S6 allow
Seismic Operating Right Saddle 3 408 16 000 -18 567 -30 463 30 000 11 697 17 500 1 061 17 333
Left Saddle 3 408 16 000 -18 567 -30 463 30 000 11 697 17 500 1 061 17 333
Seismic Vacuum Right Saddle 3 408 16 000 -18 567 -30 463 30 000 11 697 17 500 1 061 17 333
Left Saddle 3 408 16 000 -18 567 -30 463 30 000 11 697 17 500 1 061 17 333
Weight Test Right Saddle 2 764 25 200 -15 650 -25 677 31 500 9 859 31 500 894 34 200
Left Saddle 2 764 25 200 -15 650 -25 677 31 500 9 859 31 500 894 34 200
67/81
Seismic base shear on vessel
Vessel is assumed to be a rigid structure.
Method of seismic analysis ASCE 7-10 ground supported
Vertical seismic accelerations considered Yes
Importance factor, Ie 1
Site Class C
Short period spectral response acceleration as percent of g, Ss 59
From Table 11.4-1, Fa 1,164
Risk Category (Table 1.5-1) II
Equations
SMS = Fa*Ss
SDS = (2 / 3)*SMS
Fp = 0,3*SDS*W*Ie*0,7
Results
SMS = 1,164*0,59 0,6868
SDS = (2 / 3)*0,6868 0,4578
Seismic Design Category (Section 11.6) C
Fp = 0,3*0,4578*75 302*1*0,7 7 240,02 lbf
68/81
Saddle reactions due to weight + seismic
Vv = vertical seismic force acting on the saddle
V = horizontal seismic shear acting on the saddle (worst case if not slotted)
Seismic longitudinal reaction, Ql
Seismic transverse reaction, Qt
Equations
Ql = V*Hs / Ls + Vv
Qt = V*Hs / (Ro*Sin( θ / 2 )) + Vv
Q = W + max[ Qt , Ql ]
Results
Operating
Right SaddleQl = 7 240,02*60,1563 / 202 + 0,14*0,4578*37 651 4 569,44 lbf
Qt = 3 620,01*60,1563 / (48,1875*Sin( 140 / 2 )) + 0,14*0,4578*37 651 7 222,51 lbf
Q = 37 651 + max[ 7 222,51 , 4 569,44 ] 44 873,51 lbf
Left SaddleQl = 7 240,02*60,1563 / 202 + 0,14*0,4578*37 651 4 569,44 lbf
Qt = 3 620,01*60,1563 / (48,1875*Sin( 140 / 2 )) + 0,14*0,4578*37 651 7 222,51 lbf
Q = 37 651 + max[ 7 222,51 , 4 569,44 ] 44 873,51 lbf
Load Case 1: Seismic, Operating
Longitudinal stress between saddles (Seismic, Operating, right saddle loading and geometry govern)
S1 = ± 3*K1*Q*(L / 12) / (π*R2*t)= 3*0,5693*44 873,51*(254 / 12) / (π*48,06752*0,135)= 1 655 psi
Sp = P*R / (2*t)= 18,18*48 / (2*0,135)= 3 232 psi
Maximum tensile stress S1t = S1 + Sp = 4 888 psiMaximum compressive stress (shut down) S1c = S1 = 1 655 psi
Tensile stress is acceptable (<=1,2*S*E = 16 800 psi)Compressive stress is acceptable (<=1,2*Sc = 5 804 psi)
Longitudinal stress at the right saddle (Seismic, Operating)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*16,5101 / 3 + 254 + 2*16,5101 / 3= 276,0135 in
Seismic vertical acceleration coefficient m = 0,6667*0,0961 = 0,0641
w = Wt*(1 + m) / Le = 75 302*(1 + 0,0641) / 276,0135 = 290,31 lbf/in
Bending moment at the right saddle:
69/81
Mq = w*(2*H*Ar / 3 + Ar2 / 2 - (R2 - H2) / 4)
= 290,31*(2*16,5101*26 / 3 + 262 / 2 - (48,18752 - 16,51012) / 4)= 32 459,9 lbf-in
S2 = ± Mq*K1' / (π*R2*t)= 32 459,9*7,0845 / (π*48,09382*0,1875)= 169 psi
Sp = P*R / (2*t)= 18,18*48 / (2*0,1875)= 2 327 psi
Maximum tensile stress S2t = S2 + Sp = 2 496 psiMaximum compressive stress (shut down) S2c = S2 = 169 psi
Tensile stress is acceptable (<=1,2*S = 24 000 psi)Compressive stress is acceptable (<=1,2*Sc = 7 553 psi)
Tangential shear stress in the shell (right saddle, Seismic, Operating)
Qshear = Q - w*(a + 2*H / 3)= 44 873,51 - 290,31*(26 + 2*16,5101 / 3)= 34 130,19 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*34 130,19 / (48,0938*0,1875)= 3 408 psi
Tangential shear stress is acceptable (<= 0.8*S = 16 000 psi)
Circumferential stress at the right saddle horns (Seismic, Operating)
S4 = -Q / (4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*(t2+tp2))= -44 873,51 / (4*(0,1875+0,1875)*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0117*44 873,51*48,0938 /(254*(0,18752+0,18752))= -18 567 psi
Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 30 000 psi)
Circumferential stress at the right saddle wear plate horns (Seismic, Operating)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -44 873,51 / (4*0,1875*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0094*44 873,51*48,0938 / (254*0,18752)= -30 463 psi
** WARNING Circumferential stress at the wear plate horns is excessive (> 30 000 psi)**
Ring compression in shell over right saddle (Seismic, Operating)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,6971*44 873,51 / ((0,1875 + 0,1875)*(0,5 + 1,56*Sqr(48,1875*0,375)))= 11 697 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 17 500 psi)
70/81
Saddle splitting load (right, Seismic, Operating)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 11,3438*0,5 + 0,1875*24= 10,1719 in2
S6 = K8*Q / Ae= 0,2404*44 873,51 / 10,1719= 1 061 psi
Stress in saddle is acceptable (<= (2 / 3)*Ss = 17 333 psi)
Longitudinal stress at the left saddle (Seismic, Operating)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*16,5101 / 3 + 254 + 2*16,5101 / 3= 276,0135 in
Seismic vertical acceleration coefficient m = 0,6667*0,0961 = 0,0641
w = Wt*(1 + m) / Le = 75 302*(1 + 0,0641) / 276,0135 = 290,31 lbf/in
Bending moment at the left saddle:
Mq = w*(2*H*Al / 3 + Al2 / 2 - (R2 - H2) / 4)
= 290,31*(2*16,5101*26 / 3 + 262 / 2 - (48,18752 - 16,51012) / 4)= 32 459,9 lbf-in
S2 = ± Mq*K1' / (π*R2*t)= 32 459,9*7,0845 / (π*48,09382*0,1875)= 169 psi
Sp = P*R / (2*t)= 18,18*48 / (2*0,1875)= 2 327 psi
Maximum tensile stress S2t = S2 + Sp = 2 496 psiMaximum compressive stress (shut down) S2c = S2 = 169 psi
Tensile stress is acceptable (<=1,2*S = 24 000 psi)Compressive stress is acceptable (<=1,2*Sc = 7 553 psi)
Tangential shear stress in the shell (left saddle, Seismic, Operating)
Qshear = Q - w*(a + 2*H / 3)= 44 873,51 - 290,31*(26 + 2*16,5101 / 3)= 34 130,19 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*34 130,19 / (48,0938*0,1875)= 3 408 psi
Tangential shear stress is acceptable (<= 0.8*S = 16 000 psi)
Circumferential stress at the left saddle horns (Seismic, Operating)
71/81
S4 = -Q / (4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*(t2+tp2))= -44 873,51 / (4*(0,1875+0,1875)*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0117*44 873,51*48,0938 /(254*(0,18752+0,18752))= -18 567 psi
Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 30 000 psi)
Circumferential stress at the left saddle wear plate horns (Seismic, Operating)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -44 873,51 / (4*0,1875*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0094*44 873,51*48,0938 / (254*0,18752)= -30 463 psi
** WARNING Circumferential stress at the wear plate horns is excessive (> 30 000 psi)**
Ring compression in shell over left saddle (Seismic, Operating)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,6971*44 873,51 / ((0,1875 + 0,1875)*(0,5 + 1,56*Sqr(48,1875*0,375)))= 11 697 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 17 500 psi)
Saddle splitting load (left, Seismic, Operating)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 11,3438*0,5 + 0,1875*24= 10,1719 in2
S6 = K8*Q / Ae= 0,2404*44 873,51 / 10,1719= 1 061 psi
Stress in saddle is acceptable (<= (2 / 3)*Ss = 17 333 psi)
Load Case 2: Seismic, Vacuum
Longitudinal stress between saddles (Seismic, Vacuum, right saddle loading and geometry govern)
S1 = ± 3*K1*Q*(L / 12) / (π*R2*t)= 3*0,5693*44 873,51*(254 / 12) / (π*48,06752*0,135)= 1 655 psi
Sp = P*R / (2*t)= 1*48 / (2*0,135)= 178 psi
Maximum tensile stress (shut down) S1t = S1 = 1 655 psiMaximum compressive stress S1c = S1 + Sp = 1 833 psi
Tensile stress is acceptable (<=1,2*S*E = 16 800 psi)Compressive stress is acceptable (<=1,2*Sc = 5 804 psi)
72/81
Longitudinal stress at the right saddle (Seismic, Vacuum)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*16,5101 / 3 + 254 + 2*16,5101 / 3= 276,0135 in
Seismic vertical acceleration coefficient m = 0,6667*0,0961 = 0,0641
w = Wt*(1 + m) / Le = 75 302*(1 + 0,0641) / 276,0135 = 290,31 lbf/in
Bending moment at the right saddle:
Mq = w*(2*H*Ar / 3 + Ar2 / 2 - (R2 - H2) / 4)
= 290,31*(2*16,5101*26 / 3 + 262 / 2 - (48,18752 - 16,51012) / 4)= 32 459,9 lbf-in
S2 = ± Mq*K1' / (π*R2*t)= 32 459,9*7,0845 / (π*48,09382*0,1875)= 169 psi
Sp = P*R / (2*t)= 1*48 / (2*0,1875)= 128 psi
Maximum tensile stress (shut down) S2t = S2 = 169 psiMaximum compressive stress S2c = S2 + Sp = 297 psi
Tensile stress is acceptable (<=1,2*S = 24 000 psi)Compressive stress is acceptable (<=1,2*Sc = 7 553 psi)
Tangential shear stress in the shell (right saddle, Seismic, Vacuum)
Qshear = Q - w*(a + 2*H / 3)= 44 873,51 - 290,31*(26 + 2*16,5101 / 3)= 34 130,19 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*34 130,19 / (48,0938*0,1875)= 3 408 psi
Tangential shear stress is acceptable (<= 0.8*S = 16 000 psi)
Circumferential stress at the right saddle horns (Seismic, Vacuum)
S4 = -Q / (4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*(t2+tp2))= -44 873,51 / (4*(0,1875+0,1875)*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0117*44 873,51*48,0938 /(254*(0,18752+0,18752))= -18 567 psi
Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 30 000 psi)
Circumferential stress at the right saddle wear plate horns (Seismic, Vacuum)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -44 873,51 / (4*0,1875*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0094*44 873,51*48,0938 / (254*0,18752)= -30 463 psi
73/81
** WARNING Circumferential stress at the wear plate horns is excessive (> 30 000 psi)**
Ring compression in shell over right saddle (Seismic, Vacuum)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,6971*44 873,51 / ((0,1875 + 0,1875)*(0,5 + 1,56*Sqr(48,1875*0,375)))= 11 697 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 17 500 psi)
Saddle splitting load (right, Seismic, Vacuum)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 11,3438*0,5 + 0,1875*24= 10,1719 in2
S6 = K8*Q / Ae= 0,2404*44 873,51 / 10,1719= 1 061 psi
Stress in saddle is acceptable (<= (2 / 3)*Ss = 17 333 psi)
Longitudinal stress at the left saddle (Seismic, Vacuum)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*16,5101 / 3 + 254 + 2*16,5101 / 3= 276,0135 in
Seismic vertical acceleration coefficient m = 0,6667*0,0961 = 0,0641
w = Wt*(1 + m) / Le = 75 302*(1 + 0,0641) / 276,0135 = 290,31 lbf/in
Bending moment at the left saddle:
Mq = w*(2*H*Al / 3 + Al2 / 2 - (R2 - H2) / 4)
= 290,31*(2*16,5101*26 / 3 + 262 / 2 - (48,18752 - 16,51012) / 4)= 32 459,9 lbf-in
S2 = ± Mq*K1' / (π*R2*t)= 32 459,9*7,0845 / (π*48,09382*0,1875)= 169 psi
Sp = P*R / (2*t)= 1*48 / (2*0,1875)= 128 psi
Maximum tensile stress (shut down) S2t = S2 = 169 psiMaximum compressive stress S2c = S2 + Sp = 297 psi
Tensile stress is acceptable (<=1,2*S = 24 000 psi)Compressive stress is acceptable (<=1,2*Sc = 7 553 psi)
Tangential shear stress in the shell (left saddle, Seismic, Vacuum)
74/81
Qshear = Q - w*(a + 2*H / 3)= 44 873,51 - 290,31*(26 + 2*16,5101 / 3)= 34 130,19 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*34 130,19 / (48,0938*0,1875)= 3 408 psi
Tangential shear stress is acceptable (<= 0.8*S = 16 000 psi)
Circumferential stress at the left saddle horns (Seismic, Vacuum)
S4 = -Q / (4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*(t2+tp2))= -44 873,51 / (4*(0,1875+0,1875)*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0117*44 873,51*48,0938 /(254*(0,18752+0,18752))= -18 567 psi
Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 30 000 psi)
Circumferential stress at the left saddle wear plate horns (Seismic, Vacuum)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -44 873,51 / (4*0,1875*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0094*44 873,51*48,0938 / (254*0,18752)= -30 463 psi
** WARNING Circumferential stress at the wear plate horns is excessive (> 30 000 psi)**
Ring compression in shell over left saddle (Seismic, Vacuum)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,6971*44 873,51 / ((0,1875 + 0,1875)*(0,5 + 1,56*Sqr(48,1875*0,375)))= 11 697 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 17 500 psi)
Saddle splitting load (left, Seismic, Vacuum)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 11,3438*0,5 + 0,1875*24= 10,1719 in2
S6 = K8*Q / Ae= 0,2404*44 873,51 / 10,1719= 1 061 psi
Stress in saddle is acceptable (<= (2 / 3)*Ss = 17 333 psi)
Load Case 3: Weight, Test
Longitudinal stress between saddles (Weight, Test, right saddle loading and geometry govern)
S1 = ± 3*K1*Q*(L / 12) / (π*R2*t)= 3*0,5693*37 823*(254 / 12) / (π*48,06752*0,135)= 1 395 psi
75/81
Sp = P*R / (2*t)= 22,69*48 / (2*0,135)= 4 034 psi
Maximum tensile stress S1t = S1 + Sp = 5 429 psiMaximum compressive stress (shut down) S1c = S1 = 1 395 psi
Tensile stress is acceptable (<= 0,9*Sy = 22 050 psi)Compressive stress is acceptable (<=1*Sc = 4 959 psi)
Longitudinal stress at the right saddle (Weight, Test)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*16,5101 / 3 + 254 + 2*16,5101 / 3= 276,0135 in
w = Wt / Le = 75 646 / 276,0135 = 274,07 lbf/in
Bending moment at the right saddle:
Mq = w*(2*H*Ar / 3 + Ar2 / 2 - (R2 - H2) / 4)
= 274,07*(2*16,5101*26 / 3 + 262 / 2 - (48,18752 - 16,51012) / 4)= 30 644 lbf-in
S2 = ± Mq*K1' / (π*R2*t)= 30 644*7,0845 / (π*48,09382*0,1875)= 159 psi
Sp = P*R / (2*t)= 22,69*48 / (2*0,1875)= 2 904 psi
Maximum tensile stress S2t = S2 + Sp = 3 064 psiMaximum compressive stress (shut down) S2c = S2 = 159 psi
Tensile stress is acceptable (<= 0,9*Sy = 31 500 psi)Compressive stress is acceptable (<=1*Sc = 6 867 psi)
Tangential shear stress in the shell (right saddle, Weight, Test)
Qshear = Q - w*(a + 2*H / 3)= 37 823 - 274,07*(26 + 2*16,5101 / 3)= 27 680,7 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*27 680,7 / (48,0938*0,1875)= 2 764 psi
Tangential shear stress is acceptable (<= 0.8*S = 25 200 psi)
Circumferential stress at the right saddle horns (Weight, Test)
S4 = -Q / (4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*(t2+tp2))= -37 823 / (4*(0,1875+0,1875)*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0117*37 823*48,0938 /(254*(0,18752+0,18752))= -15 650 psi
76/81
Circumferential stress at saddle horns is acceptable (<= 0,9*Sy = 31 500 psi)
Circumferential stress at the right saddle wear plate horns (Weight, Test)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -37 823 / (4*0,1875*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0094*37 823*48,0938 / (254*0,18752)= -25 677 psi
Circumferential stress at wear plate horns is acceptable (<= 0,9*Sy = 31 500 psi)
Ring compression in shell over right saddle (Weight, Test)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,6971*37 823 / ((0,1875 + 0,1875)*(0,5 + 1,56*Sqr(48,1875*0,375)))= 9 859 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 31 500 psi)
Saddle splitting load (right, Weight, Test)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 11,3438*0,5 + 0,1875*24= 10,1719 in2
S6 = K8*Q / Ae= 0,2404*37 823 / 10,1719= 894 psi
Stress in saddle is acceptable (<= 0,9*Sy = 34 200 psi)
Longitudinal stress at the left saddle (Weight, Test)
Le = 2*(Left head depth) / 3 + L + 2*(Right head depth) / 3= 2*16,5101 / 3 + 254 + 2*16,5101 / 3= 276,0135 in
w = Wt / Le = 75 646 / 276,0135 = 274,07 lbf/in
Bending moment at the left saddle:
Mq = w*(2*H*Al / 3 + Al2 / 2 - (R2 - H2) / 4)
= 274,07*(2*16,5101*26 / 3 + 262 / 2 - (48,18752 - 16,51012) / 4)= 30 644 lbf-in
S2 = ± Mq*K1' / (π*R2*t)= 30 644*7,0845 / (π*48,09382*0,1875)= 159 psi
Sp = P*R / (2*t)= 22,69*48 / (2*0,1875)= 2 904 psi
Maximum tensile stress S2t = S2 + Sp = 3 064 psiMaximum compressive stress (shut down) S2c = S2 = 159 psi
77/81
Tensile stress is acceptable (<= 0,9*Sy = 31 500 psi)Compressive stress is acceptable (<=1*Sc = 6 867 psi)
Tangential shear stress in the shell (left saddle, Weight, Test)
Qshear = Q - w*(a + 2*H / 3)= 37 823 - 274,07*(26 + 2*16,5101 / 3)= 27 680,7 lbf
S3 = K2,2*Qshear / (R*t)= K2,2*27 680,7 / (48,0938*0,1875)= 2 764 psi
Tangential shear stress is acceptable (<= 0.8*S = 25 200 psi)
Circumferential stress at the left saddle horns (Weight, Test)
S4 = -Q / (4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*(t2+tp2))= -37 823 / (4*(0,1875+0,1875)*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0117*37 823*48,0938 /(254*(0,18752+0,18752))= -15 650 psi
Circumferential stress at saddle horns is acceptable (<= 0,9*Sy = 31 500 psi)
Circumferential stress at the left saddle wear plate horns (Weight, Test)
S4 = -Q / (4*t*(b+1,56*Sqr(Ro*t))) - 12*K3*Q*R / (L*t2)= -37 823 / (4*0,1875*(14+1,56*Sqr(48,1875*0,1875))) - 12*0,0094*37 823*48,0938 / (254*0,18752)= -25 677 psi
Circumferential stress at wear plate horns is acceptable (<= 0,9*Sy = 31 500 psi)
Ring compression in shell over left saddle (Weight, Test)
S5 = K5*Q / ((t + tp)*(ts + 1,56*Sqr(Ro*tc)))= 0,6971*37 823 / ((0,1875 + 0,1875)*(0,5 + 1,56*Sqr(48,1875*0,375)))= 9 859 psi
Ring compression in shell is acceptable (<= 0,5*Sy = 31 500 psi)
Saddle splitting load (left, Weight, Test)
Area resisting splitting force = Web area + wear plate area
Ae = Heff*ts + tp*Wp= 11,3438*0,5 + 0,1875*24= 10,1719 in2
S6 = K8*Q / Ae= 0,2404*37 823 / 10,1719= 894 psi
Stress in saddle is acceptable (<= 0,9*Sy = 34 200 psi)
Shear stress in anchor bolting, one end slotted
78/81
Maximum seismic or wind base shear = 7 240,02 lbf
Thermal expansion base shear = W*µ = 38 379*0,45 = 17 270,55 lbfCorroded root area for a 1,125" series 8 threaded bolt = 0,728 in2 ( 2 per saddle )
Bolt shear stress = 17 270,55 / (0,728*1*2) = 11 862 psi
Anchor bolt stress is acceptable (<= 15 000 psi)
Shear stress in anchor bolting, transverse
Maximum seismic or wind base shear = 7 240,02 lbfCorroded root area for a 1,125" series 8 threaded bolt = 0,728 in2 ( 2 per saddle )
Bolt shear stress = 7 240,02 / (0,728*2*2) = 2 486 psi
Anchor bolt stress is acceptable (<= 15 000 psi)
Web plate buckling check (Escoe pg 251)
Allowable compressive stress Sc is the lesser of 26 000 or 30 056 psi: (26 000)
Sc = Ki*π2*E / (12*(1 - 0,32)*(di / ts)2)= 1,28*π2*29E+06 / (12*(1 - 0,32)*(16,705 / 0,5)2)= 30 056 psi
Allowable compressive load on the saddle
be = di*ts / (di*ts + 2*tw*(b - 1))= 16,705*0,5 / (16,705*0,5 + 2*0,25*(14 - 1))= 0,5624
Fb = n*(As + 2*be*ts)*Sc= 6*(3,375 + 2*0,5624*0,5)*26 000= 614 228,67 lbf
Saddle loading of 45 601,51 lbf is <= Fb; satisfactory.
Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted)σb = V*(Hs - xo)*y / I + Q / A= 7 240,02*(60,1563 - 37,0634)*9,8125 / 741,98 + 44 873,51 / 65,5314= 2 896 psi
The primary bending + axial stress in the saddle <= 26 000 psi; satisfactory.
Secondary bending + axial stress in the saddle due to end loads (includes thermal expansion, assumes onesaddle slotted)σb = V*(Hs - xo)*y / I + Q / A= 24 510,57*(60,1563 - 37,0634)*9,8125 / 741,98 + 44 873,51 / 65,5314= 8 170 psi
The secondary bending + axial stress in the saddle < 2*Sy= 76 000 psi; satisfactory.
Saddle base plate thickness check (Roark sixth edition, Table 26, case 7a)
where a = 16,705, b = 15,5 in
79/81
tb = (β1*q*b2 / (1,5*Sa))0,5
= (0,7609*34*15,52 / (1,5*26 000))0,5
= 0,3979 in
The base plate thickness of 0,4375 in is adequate.
Foundation bearing check
Sf = Qmax / (F*E)= 45 601,51 / (16*84,4)= 34 psi
Concrete bearing stress ≤ 1 658 psi ; satisfactory.
80/81
Seismic Code
Seismic calculations are reported in the saddle report.
81/81