11522 - Tank Horizontale 29 000L

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


5/81




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






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






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






- Rings #1 126 132,467






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


Location from Center Line (in) 46

Operating Liquid Specific Gravity 1

15/81

F&D Head #2


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)


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"


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)


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"


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)


21/81

A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,1091)= 0,000142


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


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 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







Rated MDMT -320 °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)


Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi



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


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 48"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 788,69 1 504,05

Corroded 788,69 1 504,05

Radiography


Left Circumferentialseam None UW-11(c) Type 1


27/81

Results Summary








Rated MDMT -320 °F


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





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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,1875 / (48 + 0,60*0,1875)= 54,56 psi



Pa = 4*B / (3*(Do / t))= 4*594,19 / (3*(96,375 / 0,1216))= 1 psi

28/81


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




= 0,125 / (48,1875 / 0,1875)= 0,000486

B = 6 294 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 6 294 psi


= 0,125 / (48,1875 / 0,1875)= 0,000486

B = 6 867 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 6 867 psi

29/81


= 0,125 / (48,1875 / 0,1875)= 0,000486

B = 6 294 psi

S = 20 000 / 1,00 = 20 000 psi


30/81

Cylinder #2


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 12"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 141,89 376,01

Corroded 141,89 376,01

Radiography




31/81

Results Summary








Rated MDMT -320 °F







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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi



Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi


ta = t + Corrosion = 0,1216 + 0 = 0,1216"

32/81



Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi




= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 4 837 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 959 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 4 959 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

33/81

S = 20 000 / 1,00 = 20 000 psi


34/81

Cylinder #3


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 48"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 567,55 1 504,05

Corroded 567,55 1 504,05

Radiography




35/81

Results Summary








Rated MDMT -320 °F







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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi



Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi


ta = t + Corrosion = 0,1216 + 0 = 0,1216"

36/81



Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi




= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 4 837 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 959 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 4 959 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

37/81

S = 20 000 / 1,00 = 20 000 psi


38/81

Cylinder #4


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 48"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 567,55 1 504,05

Corroded 567,55 1 504,05

Radiography




39/81

Results Summary








Rated MDMT -320 °F







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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi



Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi


ta = t + Corrosion = 0,1216 + 0 = 0,1216"

40/81



Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi




= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 4 837 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 959 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 4 959 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

41/81

S = 20 000 / 1,00 = 20 000 psi


42/81

Rings #1


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


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 48"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 567,55 1 504,05

Corroded 567,55 1 504,05

Radiography




46/81

Results Summary








Rated MDMT -320 °F







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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi



Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi


ta = t + Corrosion = 0,1216 + 0 = 0,1216"

47/81



Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi




= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 4 837 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 959 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 4 959 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

48/81

S = 20 000 / 1,00 = 20 000 psi


49/81

Cylinder #6


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 48"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 788,69 1 504,05

Corroded 788,69 1 504,05

Radiography




50/81

Results Summary








Rated MDMT -320 °F


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





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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,1875 / (48 + 0,60*0,1875)= 54,56 psi



Pa = 4*B / (3*(Do / t))= 4*594,19 / (3*(96,375 / 0,1216))= 1 psi

51/81


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




= 0,125 / (48,1875 / 0,1875)= 0,000486

B = 6 294 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 6 294 psi


= 0,125 / (48,1875 / 0,1875)= 0,000486

B = 6 867 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 6 867 psi

52/81


= 0,125 / (48,1875 / 0,1875)= 0,000486

B = 6 294 psi

S = 20 000 / 1,00 = 20 000 psi


53/81

Straight Flange on F&D Head #1


Component Cylinder




No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 1


Dimensions

Inner Diameter 96"

Length 1"


Corrosion Inner 0"

Outer 0"

Weight and Capacity


New 11,82 31,33

Corroded 11,82 31,33

Radiography



54/81

Results Summary








Rated MDMT -320 °F







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


P = S*E*t / (R + 0,60*t)= 20 000*0,70*0,135 / (48 + 0,60*0,135)= 39,31 psi



Pa = 4*B / (3*(Do / t))= 4*593,98 / (3*(96,27 / 0,1216))= 1 psi


ta = t + Corrosion = 0,1216 + 0 = 0,1216"

55/81



Pa = 4*B / (3*(Do / t))= 4*717,01 / (3*(96,27 / 0,135))= 1,34 psi




= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

S = 20 000 / 1,00 = 20 000 psi



ScHN = ScHC

= 4 837 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 959 psi

S = 20 000 / 1,00 = 20 000 psi



ScCC = ScCN

= 4 959 psi


= 0,125 / (48,135 / 0,135)= 0,000351

B = 4 837 psi

56/81

S = 20 000 / 1,00 = 20 000 psi


57/81

F&D Head #1


Component F&D Head


Attached To Cylinder #6



No No No No No



DesignMDMT (°F)


Static Liquid Head


Operating 3,39 94 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







Rated MDMT -320°F

Note: Endnote 90 used to determine allowable stress.




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)


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"


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)


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"


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)


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"


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)


A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,073045)= 0,000095


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)


63/81

A = 0,125 / (Ro / t)= 0,125 / (96,1091 / 0,1091)= 0,000142


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.



64/81

Saddle #1


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)



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



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


Circumferential stress at the left saddle horns (Seismic, Operating)

71/81



Circumferential stress at the left saddle wear plate horns (Seismic, Operating)



Ring compression in shell over left saddle (Seismic, Operating)



Saddle splitting load (left, Seismic, Operating)


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


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)



w = Wt*(1 + m) / Le = 75 302*(1 + 0,0641) / 276,0135 = 290,31 lbf/in


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


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


Circumferential stress at the right saddle horns (Seismic, Vacuum)



Circumferential stress at the right saddle wear plate horns (Seismic, Vacuum)


73/81


Ring compression in shell over right saddle (Seismic, Vacuum)



Saddle splitting load (right, Seismic, Vacuum)


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


Longitudinal stress at the left saddle (Seismic, Vacuum)



w = Wt*(1 + m) / Le = 75 302*(1 + 0,0641) / 276,0135 = 290,31 lbf/in


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


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


Circumferential stress at the left saddle horns (Seismic, Vacuum)



Circumferential stress at the left saddle wear plate horns (Seismic, Vacuum)



Ring compression in shell over left saddle (Seismic, Vacuum)



Saddle splitting load (left, Seismic, Vacuum)


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


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)


w = Wt / Le = 75 646 / 276,0135 = 274,07 lbf/in


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



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


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


Saddle splitting load (right, Weight, Test)


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)


w = Wt / Le = 75 646 / 276,0135 = 274,07 lbf/in


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


77/81


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


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


Saddle splitting load (left, Weight, Test)


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

Documents

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