design calculations for pressure shell
TRANSCRIPT
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 1440.00 psi
Inner Diameter of Shell Do 219.00 mm
Design Temperature Temp 120.00 F
Corrosion Allowance CA 3.00 mm
17115
20000.00
Radiography Type Full
Joint Efficiency E 1.00
Shell thickness per UG-27
Result:
t = 11.9131 mm
1.489 mm
to= 13.4023 mm or
16.0000 mm Recommended thickness is adequate
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 16.00 mm
Final Centre Linre Radius Rf= 117.50 mm
Original Centreline radius Ro= infinity for straight plate
6.809%
Stress Releif Required. To Avoid Stress Releif Increase The Thickness
THICKNESS OF CYLINDRICAL SHELL(Internal Pressure & Outside Dimensions)
SA-106 Gr. B
Allowable Stress S psi
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Shell
Mill Undertolerence per UG-16
Min. req'd thickness of Shell
Select shell thickness
Cylindrical Shell
)4.0(2 PSE
PDt
o
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction Material
See Section II Part D for other materials
Internal Design Pressure P 100.00 psi
Inner Diameter of Head L 2438.40 mm
Design Temperature Temp 650.00 F
Corrosion Allowance CA 3.18 mm
Knuckle radius r 152.40 mm
0
15000.00 To be entered by user
Radiography Type Full
Joint Efficiency E 1.00
Ratio L/r 16.00
Case 1: when L/r= 16
Thickness per UG-32
This Formula Is Valid
Result:
t = 17.5762 mm
0.300 mm
to= 17.8762 mm or
14.2875 mm
9/16 in Recommend a higher thickness
Case 2: when L/r < 16
Thickness per UG-32
This Formula Is Not Valid
Min. Req. Design Thickness of Head
Mill Undertolerence per UG-16
Min. req'd thickness of Head
Select Head thickness
THICKNESS OF TORISPHERICAL HEAD(Internal Pressure & Inside Dimensions)
As Desired
Allowable Stress S psi
Torispherical Head
)1.0(
885.0
PSE
PLt
PLMt
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Result:
M= 1.75 mmt = 17.41 mm
0.300 mm
to= 17.71 mm or14.2875 mm
SA-516 Gr. 70 9/16 in Recommend a higher thickness
SA-106 Gr. B
Case 3: SA-285 Gr. Cwhen L/r > 16 SA-240 Gr. 304
Thickness per UG-32As Desired
This Formula Is Not Valid
Result:
Factor M M= 1.75 mmt = 17.41 mm
0.300 mm
to= 17.71 mm or
14.2875 mm
9/16 in Recommend a higher thickness
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 17.88 mm
Final Centre Linre Radius Rf= 170.28 mm
Original Centreline radius Ro= infinity for straight plate
7.87%
Stress Releif Required. To Avoid Stress Releif Increase The Thickness
Mill Undertolerence per UG-16
Min. req'd thickness of Head
Select Head thickness
Percent Extreme fiber Elongation
Factor M
Min. Req. Design Thickness of Head
Mill Undertolerence per UG-16
Min. req'd thickness of HeadSelect Head thickness
Min. Req. Design Thickness of Head
PSE 2.02
)3(4
1
rLM
PSE
PLMt
2.02
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Do not print this sheet, it contains only information
as how to design elements of pressure vessel
INPUT CELLS (UNLOCKED) Drop down selection
CALCULATIONS BY PROGRAM
RESULTS
STEPS
1 Select sheet what you need to design (e-g: For shell design select shell
2 Input values in yellow cells -----> or thru cells
3 Results are shown for every item at end of the sheet
Histroy:
0 Reviewed with ARC USA 05.11.07
INPUTS
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heet)
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 107.00 psi
Inner Diameter of Shell Di 4580.00 mm
Design Temperature Temp 315.00 F
Corrosion Allowance CA 3.00 mm
20000
20000.00
Radiography Type Full
Joint Efficiency E 1.00
Shell thickness per UG-27
Result:
t = 15.2910 mm
0.300 mm
to= 15.5910 mm or16.0000 mm Recommended thickness is adequate
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 16.00 mm
Final Centre Linre Radius Rf= 2298.00 mm
Original Centreline radius Ro= infinity for straight plate
0.348% Stress Releif Not Required
SA-516 Gr. 70
Mill Undertolerence per UG-16
Allowable Stress S psi
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Shell
Min. req'd thickness of ShellSelect shell thickness
(Internal Pressure & Inside Dimensions)
THICKNESS OF CYLINDRICAL SHELL
Cylindrical Shell
)6.0(2 PSE
PDt
i
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 1440.00 psi
Inner Diameter of Shell Do 219.00 mm
Design Temperature Temp 120.00 F
Corrosion Allowance CA 3.00 mm
17115
20000.00
Radiography Type Full
Joint Efficiency E 1.00
Shell thickness per UG-27
Result:
t = 11.9131 mm
1.489 mm
to= 13.4023 mm or
16.0000 mm Recommended thickness is adequate
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 16.00 mm
Final Centre Linre Radius Rf= 117.50 mm
Original Centreline radius Ro= infinity for straight plate
6.809%
Stress Releif Required. To Avoid Stress Releif Increase The Thickness
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Shell
Min. req'd thickness of Shell
Select shell thickness
Mill Undertolerence per UG-16
SA-106 Gr. B
(Internal Pressure & Outside Dimensions)
THICKNESS OF CYLINDRICAL SHELL
Allowable Stress S psi
Cylindrical Shell
)4.0(2 PSE
PDt
o
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 350.00 psi
Inner Diameter of Shell Di 1524.00 mm
Height of Liquid Level in Boot H 3.00 ft
Design Temperature Temp 100.00 F
Corrosion Allowance CA 3.00 mm
Total Internal Pressure in Boot Pi 351.30 psi
0
20000.00 To be entered by user
Radiography Type Full
Joint Efficiency E 1.00
Thickness per UG-27
Result:
t = 16.5271 mm
0.300 mm
to= 16.8271 mm or
17.0000 mm Recommended thickness is adequate
Stress Releif per UCS-79
Nominal thickness of Boot tnom= 17.00 mm
Final Centre Linre Radius Rf= 770.50 mm
Original Centreline radius Ro= infinity for straight plate
1.10% Stress Releif Not Required
As Desired
(Internal Pressure & Inside Dimensions)
THICKNESS OF BOOT
Mill Undertolerence per UG-16
Allowable Stress S psi
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Boot
Min. req'd thickness of Boot
Select Boot thickness
Boot
)6.0(2 PSE
DPt
ii
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 1440.00 psi
Inner Diameter of Head Di 3300.00 mm
Design Temperature Temp 170.00 F
Corrosion Allowance CA 3.00 mm
20000
20000.00
Radiography Type Spot
Joint Efficiency E 0.85
Thickness per UG-32
Result:
t = 145.1705 mm
0.300 mm
to= 145.4705 mm or
14.0000 mm
Recommend a higher thickness
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 14.00 mm
Final Centre Linre Radius Rf= 563.38 mm
Original Centreline radius Ro= infinity for straight plate
1.86% Stress Releif Not RequiredPercent Extreme fiber Elongation
Min. Req. Design Thickness of Head
Min. req'd thickness of Head
Select Head thickness
Mill Undertolerence per UG-16
SA-516 Gr. 70
(Internal Pressure & Inside Dimensions)
THICKNESS OF ELLIPSOIDAL HEAD
Allowable Stress S psi
Ellipsoidal
Head
Ellipsoidal
Head
PSE
PDt
i
2.02
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 1440.00 psi
Inner Diameter of Head D0 273.00 mm
Design Temperature Temp 120.00 F
Corrosion Allowance CA 3.00 mm
20000
20000.00
Radiography Type Full
Joint Efficiency E 1.00
Thickness per UG-32
Result:
t = 12.2271 mm
0.300 mm
to= 12.5271 mm or
14.0000 mm Recommended thickness is adequate
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 14.00 mm
Final Centre Linre Radius Rf= 48.79 mm
Original Centreline radius Ro= infinity for straight plate
21.52%
Stress Releif Required. To Avoid Stress Releif Increase The Thick
SA-516 Gr. 70
(Internal Pressure & Inside Dimensions)
THICKNESS OF ELLIPSOIDAL HEAD
Allowable Stress S psi
Mill Undertolerence per UG-16
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Head
Min. req'd thickness of Head
Select Head thickness
Ellipsoidal
Head
Ellipsoidal
Head
PSE
PDt
o
8.12
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction Material Add SA 105 as Boot capSee Section II Part D for other materials
Internal Design Pressure P 386.30 psi
Inner Diameter of Head Di 457.20 mm
Design Temperature Temp 150.00 F
Corrosion Allowance CA 3.00 mm
0
20000.00 To be entered by user
Radiography Type Full
Joint Efficiency E 1.00
Thickness per UG-32
Result:
t = 7.4297 mm
0.300 mm
to= 7.7297 mm or
7.9375 mm Recommended thickness is adequate
5/16 in
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 7.94 mm
Final Centre Linre Radius Rf= 79.07 mm
Original Centreline radius Ro= infinity for straight plate
7.53%
Stress Releif Required. To Avoid Stress Releif Increase The Thickness
As Desired
Mill Undertolerence per UG-16
Allowable Stress S psi
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Head
Min. req'd thickness of Head
Select Head thickness
(Internal Pressure & Inside Dimensions)
THICKNESS OF ELLIPSOIDAL HEAD
Boot
PSE
PDt
i
2.02
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 100.00 psi
Inner Diameter of Head Di 2438.40 mm
Design Temperature Temp 650.00 F
Corrosion Allowance CA 0.00 mm
0
20000.00 To be entered by user
Radiography Type Full
Joint Efficiency E 1.00
Thickness per UG-32
Result:
t = 3.0495 mm
0.300 mm
to= 3.3495 mm or
4.0000 mm Recommended thickness is adequate
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 4.00 mm
Final Centre Linre Radius Rf= 1221.20 mm
Original Centreline radius Ro= infinity for straight plate
0.25% Stress Releif Not RequiredPercent Extreme fiber Elongation
Min. Req. Design Thickness of Head
Min. req'd thickness of Head
Select Head thickness
Mill Undertolerence per UG-16
As Desired
(Internal Pressure & Inside Dimensions)
THICKNESS OF HEMISPHERICAL HEAD
Allowable Stress S psi
Spheric
al
Head
Spher
ical
Hea
d
)2.02(2 PSE
PDt
i
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Inputs
Note: to be less than 30 degree
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 100.00 psi
Inner Diameter of Conical section Di 2438.40 mm
Design Temperature Temp 650.00 F
Corrosion Allowance CA 0.00 mm
Cone Half Apex Angle 35.00 Degree
17115
20000.00
Radiography Type Full
Joint Efficiency E 1.00
Thickness per UG-32
Result:
t = 8.7270 mm
1.091 mm
to= 9.8179 mm or
7.9375 mm
5/16 in Recommend a higher thickness
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 7.94 mm
Final Centre Linre Radius Rf= 1223.17 mm
Original Centreline radius Ro= infinity for straight plate
0.49% Stress Releif Not Required
SA-106 Gr. B
(Internal Pressure & Inside Dimensions)
THICKNESS OF CONICAL SECTION
Mill Undertolerence per UG-16
Formula is not valid. See Div I for
special analysis
Allowable Stress S psi
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Conical section
Min. req'd thickness of Conical section
Select Conical section thickness
ConicalSection
)6.0(2 PSECos
PDt
i
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction Material
See Section II Part D for other materials
Internal Design Pressure P 100.00 psi
Inner Diameter of Head L 2438.40 mm
Design Temperature Temp 650.00 F
Corrosion Allowance CA 3.18 mm
Knuckle radius r 152.40 mm
0
15000.00 To be entered by user
Radiography Type Full
Joint Efficiency E 1.00
Ratio L/r 16.00
Case 1: when L/r= 16
Thickness per UG-32
This Formula Is Valid
Result:
t = 17.5762 mm
0.300 mm
to= 17.8762 mm or
14.2875 mm
9/16 in Recommend a higher thickness
Case 2: when L/r < 16
Thickness per UG-32
This Formula Is Not Valid
(Internal Pressure & Inside Dimensions)
THICKNESS OF TORISPHERICAL HEAD
Min. Req. Design Thickness of Head
As Desired
Mill Undertolerence per UG-16
Allowable Stress S psi
Min. req'd thickness of Head
Select Head thickness
Torispherical Head
)1.0(
885.0
PSE
PLt
PLMt
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Result:
M= 1.75 mmt = 17.41 mm
0.300 mm
to= 17.71 mm or14.2875 mm
SA-516 Gr. 70 9/16 in Recommend a higher thickness
SA-106 Gr. B
Case 3: SA-285 Gr. Cwhen L/r > 16 SA-240 Gr. 304
Thickness per UG-32As Desired
This Formula Is Not Valid
Result:
Factor M M= 1.75 mmt = 17.41 mm
0.300 mm
to= 17.71 mm or
14.2875 mm
9/16 in Recommend a higher thickness
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 17.88 mm
Final Centre Linre Radius Rf= 170.28 mm
Original Centreline radius Ro= infinity for straight plate
7.87%
Stress Releif Required. To Avoid Stress Releif Increase The Thickness
Select Head thickness
Factor M
Min. req'd thickness of Head
Select Head thickness
Percent Extreme fiber Elongation
Min. Req. Design Thickness of Head
Mill Undertolerence per UG-16
Min. Req. Design Thickness of Head
Mill Undertolerence per UG-16
Min. req'd thickness of Head
PSE 2.02
)3(4
1
rLM
PSE
PLMt
2.02
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Inputs
Dsign Code: ASME Sec VIII, Div.1, 2004
Cylinder Construction MaterialSee Section II Part D for other materials
Internal Design Pressure P 300.00 psi
Inner Diameter of Head Di 609.60 mm
Design Temperature Temp 450.00 F
Corrosion Allowance CA 3.00 mm
FALSE
20000.00 To be entered by user
Radiography Type Full
Joint Efficiency E 1.00
Required thickness of Shell tr -505.00 mm
Actual thickness of Shell ts -505.00 mm
Thickness per UG-34
Result:
C= 0.33 mm
t = 45.8892 mm
0.300 mm
to= 46.1892 mm or
46.0000 mm
Recommend a higher thickness
Stress Releif per UCS-79
Nominal thickness of Vessel tnom= 46.19 mm
As Desired
(Internal Pressure & Inside Dimensions)
THICKNESS OF HEMISPHERICAL HEAD
Mill Undertolerence per UG-16
C Factor
Allowable Stress S psi
Min. Req. Design Thickness of Head
Min. req'd thickness of Head
Select Head thickness
Circular FlatHead
SE
CPDt
s
r
t
tC 33.0
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Final Centre Linre Radius Rf= 327.89 mm
Original Centreline radius Ro= infinity for straight plate
10.56%
Stress Releif Required. To Avoid Stress Releif Increase The Thickness
Percent Extreme fiber Elongation
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Dia of Max.Weight Dist. Of centr
Vessel of Vessel Length Width Thickness Height Thickness Width Thickness Width Thickness from Base Plate
(mm) (Kg) A (mm) C (mm) G (mm) (mm) H (mm) D (mm) K (mm) (mm) H (mm) (B)
304.8 19,051 266.7 101.6 6.35 6.35 101.6 6.35 304.8
355.6 22,680 317.5 101.6 6.35 6.35 101.6 6.35 330.2
406.4 25,402 355.6 101.6 6.35 6.35 101.6 6.35 355.6
457.2 28,123 393.7 101.6 6.35 6.35 101.6 6.35 381
508 31,752 444.5 101.6 6.35 6.35 101.6 6.35 406.4
558.8 34,474 482.6 101.6 6.35 6.35 152.4 6.35 431.8
609.6 38,102 533.4 101.6 6.35 6.35 152.4 6.35 457.2
660.4 40,824 571.5 101.6 6.35 6.35 152.4 6.35 6.35 482.6
711.2 44,453 622.3 101.6 12.7 6.35 152.4 6.35 6.35 508
762 47,174 660.4 101.6 12.7 6.35 152.4 6.35 6.35 533.4
812.8 50,803 711.2 101.6 12.7 6.35 152.4 6.35 6.35 558.8
863.6 58,061 736.6 152.4 12.7 6.35 279.4 6.35 6.35 584.2
914.4 60,782 774.7 152.4 12.7 6.35 279.4 6.35 6.35 609.6
965.2 65,318 838.2 152.4 12.7 6.35 279.4 6.35 6.35 635
1016 95,256 889 152.4 12.7 9.525 279.4 9.525 9.525 660.4
1066.8 99,792 927.1 152.4 12.7 9.525 279.4 9.525 9.525 685.8
1219.2 114,307 1066.8 152.4 19.05 9.525 279.4 9.525 9.525 762
1371.6 127,915 1193.8 152.4 19.05 9.525 279.4 9.525 9.525 914.4
1524 141,523 1320.8 152.4 19.05 9.525 279.4 9.525 9.525 990.6
Ribs
SADDLE DIMENSIONS
Base Plate Web Plate Wear Plate
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1676.4 156,038 1460.5 152.4 19.05 9.525 279.4 9.525 9.525 1066.8
1828.8 182,347 1587.5 228.6 19.05 9.525 457.2 9.525 9.525 1143
1981.2 197,770 1727.2 228.6 19.05 12.7 457.2 9.525 12.7 1219.2
2133.6 213,192 1854.2 228.6 19.05 12.7 457.2 9.525 12.7 1295.4
2286 227,707 1981.2 228.6 19.05 12.7 457.2 9.525 12.7 1371.62438.4 243,130 2120.9 228.6 25.4 12.7 457.2 9.525 12.7 1447.8
2590.8 344,736 2247.9 228.6 25.4 12.7 457.2 12.7 12.7 1524
2743.2 365,602 2374.9 228.6 25.4 12.7 457.2 12.7 12.7 1600.2
2895.6 386,467 2527.3 228.6 25.4 19.05 609.6 12.7 19.05 1676.4
3048 406,426 2641.6 228.6 25.4 19.05 609.6 12.7 19.05 1752.6
3200.4 426,384 2781.3 228.6 25.4 19.05 609.6 12.7 19.05 1828.8
3352.8 447,250 2908.3 228.6 25.4 19.05 609.6 12.7 19.05 1905
3505.2 467,208 3048 228.6 25.4 19.05 609.6 12.7 19.05 1981.2
3657.6 488,074 3175 228.6 25.4 19.05 609.6 12.7 19.05 2057.4
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LATERInputs
* Wind Load (From PVElite) P 8500.00 lbs
* Height of Vessel H 58.00 ft* Moment MT 493,000.00 lbs-ft
* Outside Radius of Skirt R 28.00 in
* Joint Efficiency E 0.70
* Stress Value of Head or Skirt 20000.00 psi
Mat. Whichever is smaller
* Weight of Tower above Skirt W 78000.00 lbs
Temp(F) S (psi)
(-20) 20,000
Formula used : 50 20,000
100 20,000
200 20,000
Resuslt: 300 20,000400 20,000
Required Thickness of Skirt 0.30 in 500 20,000600 19,400
650 18,800
Required Thickness of Skirt 7.58 mm 700 18,100750 14,800
800 12,000
850 9,300
516 Gr-70
THICKNESS OF SKIRT
Skirt
RSE
W
SER
Mt
T
2
12
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900 6,700
950 4,000
1000 2,500
Note: For other materials
see section 2 part D
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Nozzle Size : NB 3/4" (DN 20) Nozzle on Sump of PV-221 ( R22 Receiver ) LATER
Inputs Inputs
UG-45 b(1) for Internal Pressure UG-45 b(2) for External Pressure
Internal Design Pressure P 300.00 psi External Design Pressure P 15.0
Diameter of Shell/Head D 3000.00 mm Diameter of Shell/Head D 3000.
Design Temperature Temp 200.00 F Design Temperature Temp 200.0Allowable Stress of Shell S 20000.00 psi Allowable Stress of Shell S 20000
Joint Efficiency E 1.00 Joint Efficiency E 1.00
Corrosion Allowance CA 3.00 mm Corrosion Allowance CA 3.00
Formula used Formula used
Result Result
Thickness t 25.7043 mm Thickness t 4.125
Inputs Inputs
UG-16(b) UG-45 b(4)
Minimum thickness t 1/16 in Standard Wall Thk of pipe t 2.87
Minimum thickness t 1.59 mm Minimum thickness t 2.511
Corrosion Allowance CA 3.00 mm Corrosion Allowance CA 3.00
Result Result
Thickness t 4.5875 mm Thickness t 5.511
Final Result Inputs
UG-45 a for Internal PressureStep 1: Max ( UG 45b(1) , UG 16b) t 25.7043 mm
Internal Design Pressure P 300.0
Step 2: Max ( UG 45b(2) , UG 16b) t 4.5875 mm Diameter of Pipe D 20.0
Design Temperature Temp 200.0
Step 3: Max ( Step1 , Step 2) t 25.7043 mm Allowable Stress S 17100
Joint Efficiency E 1.00
Step 4: Min ( Step3 , UG-45 b(4)) t 5.5113 mm Corrosion Allowance CA 3.00
Step 5: Max ( Step4 , UG-45 (a)) t 5.5113 mm Formula used
Result
t 5.5113 mm Thickness t 3.177
THICKNESS OF NOZZLE AS PER UG-45
Sch
Min Required thickness of
Nozzle
)6.0(2 PSE
PDt
)6.0(2 PSE
PDt
)6.0(2 PSE
PDt
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Nozzle Size : 11.75 in ASME Section VIII Index L-7.2 Example 2 LATER
Inputs Inputs
UG-45 b(1) for Internal Pressure UG-45 b(2) for External Pressure
Internal Design Pressure P 400.00 psi External Design Pressure P
Diameter of Shell/Head D 60.00 in Diameter of Shell/Head D
Design Temperature Temp 250.00 F Design Temperature Tem
Allowable Stress of Shell S 14300.00 psi Allowable Stress of Shell S
Joint Efficiency E 1.00 Joint Efficiency E
Corrosion Allowance CA 0.00 in Corrosion Allowance CA
Formula used Formula used
Result Result
Thickness t 0.8535 in Thickness t
Inputs Inputs
UG-16(b) UG-45 b(4)
Minimum thickness t 1/16 in Standard Wall Thk of pipe t
Minimum thickness t 1.59 mm Minimum thickness t
Corrosion Allowance CA 3.00 mm Corrosion Allowance CA
Result Thickness t 4.5875 mm Result Thickness t
Thickness t 0.1806 in Thickness t
Final Result Inputs
UG-45 a for Internal PressureStep 1: Max ( UG 45b(1) , UG 16b) t 0.8535 mm
Internal Design Pressure P
Step 2: Max ( UG 45b(2) , UG 16b) t 0.1806 mm Diameter of Pipe D
Design Temperature Tem
Step 3: Max ( Step1 , Step 2) t 0.8535 mm Allowable Stress S
Joint Efficiency E
Step 4: Min ( Step3 , UG-45 b(4)) t 0.3297 mm Corrosion Allowance CA
Step 5: Max ( Step4 , UG-45 (a)) t 0.3297 mm Formula used
Result
t 0.3297 mm Thickness t
Actual Thickness of Pipe = Pipe Schedule Thickness x 0.875 (12.5% Undertolerance )
Actual Thickness of Pipe should be greater than Minimum Required Thickness
THICKNESS OF NOZZLE AS PER UG-45
Min Required thickness of
NozzleSch
)6.0(2 PSE
PDt
6.0(2 PSE
PDt
0(2 SE
PDt
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ND OD Sch Sch. Sch. Std. Sch. Sch. Extra Sch. Sch. Sch. Sch. Sch XX
(in) 10 20 30 Wall 40 60 Strong 80 100 120 140 160 Strong
0.50 21.30 2.77 2.77 3.73 3.73 4.75 7.47
0.75 26.70 2.11 2.87 2.87 3.91 3.91 5.54 7.82
1.00 33.4 2.77 3.38 3.38 4.55 4.55 6.35 9.09
1.25 42.2 2.77 3.56 3.56 4.85 4.85 6.35 9.7
1 1/2 48.3 2.77 3.69 3.69 5.08 5.08 7.14 10.16
2.00 60.3 2.77 3.91 3.91 5.54 5.54 8.71 11.07
2 1/2 73 3.05 5.16 5.16 7.01 7.01 9.52 14.02
3.00 88.9 3.05 5.49 5.49 7.62 7.62 11.13 15.24
3 1/2 101.6 3.05 5.74 5.74 8.08 8.08 16.15
4.00 114.3 3.05 6.02 6.02 8.56 8.56 11.3 13.49 17.12
5.00 141.3 3.4 6.55 6.55 9.52 9.52 12.7 15.87 19.05
6.00 168.3 7.11 7.11 10.97 10.97 14.27 18.24 21.95
8.00 219.1 6.35 7.04 8.18 8.18 10.34 12.7 12.7 15.06 18.24 20.62 23.01 22.22
10.00 273.1 6.35 7.8 9.27 9.27 12.7 12.7 15.06 18.24 21.41 25.4 28.57
12.00 323.9 6.35 8.38 9.57 10.31 14.27 12.7 17.45 21.41 23.8 28.57 33.3214.00 355.6 6.35 7.92 9.52 9.52 11.12 15.06 12.7 19.05 23.8 27.76 31.75 35.71
16.00 406.4 6.35 7.92 9.52 9.52 12.7 16.66 12.7 21.41 26.19 30.94 36.53 40.46
18.00 457.2 6.35 7.92 11.12 9.52 14.27 19.05 12.7 23.8 29.36 34.92 39.67 45.24
20.00 508 6.35 9.52 12.7 9.52 15.06 20.62 12.7 26.19 32.54 38.1 44.45 49.99
22.00 558.8 6.35 9.52 12.7 9.52 15.87 22.22 12.7 28.57 34.92 41.27 47.64 53.97
24.00 609.6 6.35 9.52 14.27 9.52 17.48 24.59 12.7 30.94 38.89
26.00 660.4 7.92 12.7 9.52 12.7
28.00 711.2 7.92 12.7 15.87 9.52 12.7
30.00 762 7.92 12.7 15.87 9.52 12.7
32.00 812.8 7.92 12.7 15.87 9.52 17.48 12.7
34.00 863.6 7.92 12.7 15.87 9.52 17.48 12.7
36.00 914.4 7.92 12.7 15.87 9.52 19.05 12.7
PIPE SCHEDULE CHART
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LIFTING LUG DIMENSIONS
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Vessel Weight Dia of Hole Thickness of Lug Radius of Outer Height of Lug Length of Lug Weld
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(Kg) D (mm) T (mm) arc R (mm) H (mm) L (mm) (Min)
5,443 25.4 12.7 38.1 127 254
9,072 28.702 19.05 50.8 152.4 254
13,608 35.052 25.4 54.102 152.4 254
22,680 41.402 31.75 63.5 177.8 304.8
31,752 54.102 31.75 88.9 203.2 304.8
45,360 63.5 38.1 114.3 228.6 406.468,040 76.2 44.45 127 254 406.4
90,720 101.6 50.8 152.4 304.8 457.2
113,400 107.95 50.8 165.1 330.2 457.2
136,080 114.3 63.5 177.8 355.6 508
12.7 mm Full Penetration Fillet
19.05 mm Full Penetration Fillet
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LATER
Butt Weld Input Pressure Conditions
Thickness of the Plate t 16.00 mm Design Pressure P 400.00 psi
Bevel Angle Theta 56.00 degree Diameter D 1375 mm
Diameter to be Weld D 1375.00 mm Area for Pressure A 1484140.63 mm2
Total Area of Weld A 539867.88 mm2
Area for Pressure A 2300.42 in2
Total Area of Weld A 836.80 in2
Load induced F 920169 lbs
Allowable Stress of Material S 20000.00 psi
Bearable Load for Butt Weld F 16735938 lbs
Strength of Weld 1718.79 %
Result Weld is O.K.
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InputsBolt Area Bolt Size
Wind Load (From PVElite) P 3000.00 lbs in2
in
Height of Vessel with Skirt H 21.00 ft 0.126 0.500
Moment M 63,000.00 lbs-ft 0.202 0.625
Weight of Vessel W 11000.00 lbs 0.302 0.750
Bolt Circle 84.00 in 0.419 0.875Area within Bolt Circle AB 5,538.96 in
20.551 1.000
Circumference of Bolt Circle CB 264 in 0.693 1.125
Maximum Tension T 94.78 lb/in 0.89 1.250
Allow. Stress Value of Bolt Mat. SB 15,000.00 psi 1.054 1.375
No. of Anchor Bolts N 8.00 1.294 1.500
Req.Area of one Bolt BA 0.21 in2
1.515 1.625
Dia of Bolt from Table against Root Area d 0.63 in 1.744 1.750
Induced Stress in Anchor Bolts Sind 10,191.08 psi 2.049 1.875
Corrosion Allowance for Bolt CA 0.13 in 2.3 2.000
3.02 2.250
Formulas Used 3.715 2.500
4.618 2.750i Maximum Tension ( lb/in ) 5.621 3.000
ii Req. Area of One Bolt ( Sq.in )
iii Stress in Anchor Bolt ( psi )
Resuslt:
Required Diameter of Anchor Bolt 0.75 in
Required Diameter of Anchor Bolt 19.05 mm
ANCHOR BOLT DESIGN
Table
BB C
W
A
MT 12
NS
TCB
B
BA
NB
TCS
A
BB
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LATER
Nominal Thickness Nominal Thickness Temperature (F)
(in) (mm)
0.1 2.54 -55 2.54 -55
0.2 5.08 -55 5.08 -55
0.3 7.62 -55 7.62 -55
0.4 10.16 -55 10.16 -55
0.5 12.7 -55 12.7 -55
0.6 15.24 -50 15.24 -50
0.7 17.78 -45 17.78 -45
0.8 20.32 -40 20.32 -40
0.9 22.86 -35 22.86 -35
1 25.4 -30 25.4 -30
1.3 33.02 -20 33.02 -20
1.5 38.1 -15 38.1 -15
1.7 43.18 -10 43.18 -10
2.2 55.88 0 55.88 0
2.5 63.5 5 63.5 5
2.9 73.66 10 73.66 10
3.4 86.36 15 86.36 15
3.8 96.52 20 96.52 20
4.2 106.68 25 106.68 25
4.7 119.38 30 119.38 305.3 134.62 35 134.62 35
5.4 137.16 35 137.16 35
6 152.4 38 152.4 38
0
0
0
0
0
0
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Temp (F) Thickness
X1 -50 Y1 15.24
X ? Y 16
X2 -45 Y2 17.78
X -48.5
INTERPOLATION
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X1 340.57 Y1 81.35
X ? Y 85
X2 359.93 Y2 85.95
X 355.9317
INTERPOLATION