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Pressure Vessel Engineering, Ltd.120 Randall Dr. Waterloo,
Ontario N2V 1C6
Date Printed: 11/12/2009
CUSTOMERPressure Vessel Engineering Ltd
120 Randall Drive, Suite BWaterloo, Ontario N2V 1C6
VESSEL LOCATIONPressure Vessel Engineering Ltd
120 Randall Drive, Suite BWaterloo, Ontario N2V 1C6
VESSEL DESCRIPTIONSample Tower
Vessel designed per the ASME Boiler & Pressure Vessel Code,
Section VIII, Division 1,2007 Edition, 2008 Addenda
with Advanced Pressure Vessel, Version: 10.1.5Vessel is ASME
Code Stamped
Wind Analysis performed in accordance with IBC 2006Seismic
Analysis performed in accordance with IBC 2006
Job No: PVE-3602 Sample 13Vessel Number: Sample 13
NAMEPLATE INFORMATIONVessel MAWP: 250.00 PSI and Full Vacuum at
550 F
M D M T : -20 F at 250.00 PSI
Serial Number(s): __________________________________
National Board Number(s): __________________________________Year
Built: 2009
R a d i o g r a p h y : RT 2Postweld Heat Treated: PHT
Construction Type: W
Signatures
_______________________________________________________________
Date: ____/____/____
P.Eng:_______________________________________________________________
Date: ____/____/____ Laurence Brundret
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Pressure Vessel Engineering, Ltd.120 Randall Dr. Waterloo,
Ontario N2V 1C6
Date Printed: 11/12/2009
Project Description
Sample Tower for website posting - stored under sample jobs in
Engineering directory
-
Pressure Vessel Engineering, Ltd.120 Randall Dr. Waterloo,
Ontario N2V 1C6
Date Printed: 11/12/2009
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Pressure Vessel Design Summary
CustomerVesselJob & RevCalculations byReviewed by
UG-22 Loadings ConsideredYes (a) Internal pressureNo (a)
External pressureNo (b) Vessel weight full, empty and at hydro
testNo (c) Weight of attached equipment and pipingNo (d)(1)
Attachment of internalsNo (d)(2) Attachment of vessel supportsNo
(d) Cyclic or dynamic reactionsYes (f) WindNo (f) SnowYes (f)
SeismicNo (g) Fluid impact shock reactionsNo (h) Temperature
gradientsNo (h) Differential thermal expansionNo (i) Abnormal
pressures like deflagrationNO (j) Hydrotest Loads
Sample 13Sample 13
Brian MunnLaurence Brundrett P. Eng.
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Pressure Vessel Engineering, Ltd.Shell 1
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 1 Mark Number: S1
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 34.00 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 98.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 11431 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
16286 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 7976 PSI
Outside Diameter (new): 86.0000 in.Outside Diameter (corroded):
86.0000 in. Specific Gravity: 1.00
Shell Surface Area: 183.87 Sq. Ft. Weight of Fluid: 19643.09
lb.Shell Estimated Volume: 2351.32 Gal. Total Flooded Shell Weight:
26970.54 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 7327.45 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -30 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.5830 in. Ext. Nominal t: 1.0000 in.Minimum
L/Do: 3.4186 Nominal L/Do: 3.4186Minimum Do/t: 187.7730 Nominal
Do/t: 98.2857
Minimum Factor A:0.0001627 Nominal Factor A:0.0004162Minimum
Factor B: 2112 PSI Nominal Factor B: 5414 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
284.00 * 42.1250
2 * 19700 * 0.85 + 0.4 * 284.00 = 0.3560 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.4810 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
284.00 * 43.0000
19700 * 0.85 + 0.4 * 284.00 = 0.7244 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 0.8494 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 5414
3 * ( 86.0000 / 0.8750 ) = maximum external pressure of 73.45 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.0000
42.5000 = elongation of 1.18 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 1 of
95
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Pressure Vessel Engineering, Ltd.Shell 1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 1 Mark Number: S1
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.0000 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 2 of
95
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Pressure Vessel Engineering, Ltd.Shell 2
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 2 Mark Number: S2
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 17.00 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 88.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 10819 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
19075 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 9380 PSI
Outside Diameter (new): 122.2500 in.Outside Diameter (corroded):
122.2500 in. Specific Gravity: 1.00
Shell Surface Area: 234.70 Sq. Ft. Weight of Fluid: 35997.33
lb.Shell Estimated Volume: 4308.96 Gal. Total Flooded Shell Weight:
46545.50 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 10548.16 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -26 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.6939 in. Ext. Nominal t: 1.1250 in.Minimum
L/Do: 2.4049 Nominal L/Do: 2.4049Minimum Do/t: 214.8880 Nominal
Do/t: 122.2500
Minimum Factor A:0.0001862 Nominal Factor A:0.0004285Minimum
Factor B: 2418 PSI Nominal Factor B: 5573 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
267.00 * 60.1250
2 * 19700 * 0.85 + 0.4 * 267.00 = 0.4778 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.6028 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
267.00 * 61.1250
19700 * 0.85 + 0.4 * 267.00 = 0.9685 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 1.0935 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 5573
3 * ( 122.2500 / 1.0000 ) = maximum external pressure of 60.78 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.1250
60.5625 = elongation of 0.93 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 3 of
95
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Pressure Vessel Engineering, Ltd.Shell 2
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 2 Mark Number: S2
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.1250 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 4 of
95
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Pressure Vessel Engineering, Ltd.Shell 3
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 3 Mark Number: S3
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 17.00 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 144.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 10819 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
19075 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 9380 PSI
Outside Diameter (new): 122.2500 in.Outside Diameter (corroded):
122.2500 in. Specific Gravity: 1.00
Shell Surface Area: 384.06 Sq. Ft. Weight of Fluid: 58904.73
lb.Shell Estimated Volume: 7051.03 Gal. Total Flooded Shell Weight:
76165.36 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 17260.63 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -26 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.6939 in. Ext. Nominal t: 1.1250 in.Minimum
L/Do: 2.4049 Nominal L/Do: 2.4049Minimum Do/t: 214.8880 Nominal
Do/t: 122.2500
Minimum Factor A:0.0001862 Nominal Factor A:0.0004285Minimum
Factor B: 2418 PSI Nominal Factor B: 5573 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
267.00 * 60.1250
2 * 19700 * 0.85 + 0.4 * 267.00 = 0.4778 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.6028 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
267.00 * 61.1250
19700 * 0.85 + 0.4 * 267.00 = 0.9685 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 1.0935 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 5573
3 * ( 122.2500 / 1.0000 ) = maximum external pressure of 60.78 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.1250
60.5625 = elongation of 0.93 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 5 of
95
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Pressure Vessel Engineering, Ltd.Shell 3
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 3 Mark Number: S3
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.1250 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 6 of
95
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Pressure Vessel Engineering, Ltd.Shell 4
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 4 Mark Number: S4
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 34.00 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 98.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 11431 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
16286 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 7976 PSI
Outside Diameter (new): 86.0000 in.Outside Diameter (corroded):
86.0000 in. Specific Gravity: 1.00
Shell Surface Area: 183.87 Sq. Ft. Weight of Fluid: 19643.09
lb.Shell Estimated Volume: 2351.32 Gal. Total Flooded Shell Weight:
26970.54 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 7327.45 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -30 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.5830 in. Ext. Nominal t: 1.0000 in.Minimum
L/Do: 3.4186 Nominal L/Do: 3.4186Minimum Do/t: 187.7730 Nominal
Do/t: 98.2857
Minimum Factor A:0.0001627 Nominal Factor A:0.0004162Minimum
Factor B: 2112 PSI Nominal Factor B: 5414 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
284.00 * 42.1250
2 * 19700 * 0.85 + 0.4 * 284.00 = 0.3560 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.4810 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
284.00 * 43.0000
19700 * 0.85 + 0.4 * 284.00 = 0.7244 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 0.8494 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 5414
3 * ( 86.0000 / 0.8750 ) = maximum external pressure of 73.45 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.0000
42.5000 = elongation of 1.18 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 7 of
95
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Pressure Vessel Engineering, Ltd.Shell 4
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 4 Mark Number: S4
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.0000 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 8 of
95
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Pressure Vessel Engineering, Ltd.Shell 5
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 5 Mark Number: S5
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 34.00 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 98.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 11431 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
16286 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 7976 PSI
Outside Diameter (new): 86.0000 in.Outside Diameter (corroded):
86.0000 in. Specific Gravity: 1.00
Shell Surface Area: 183.87 Sq. Ft. Weight of Fluid: 19643.09
lb.Shell Estimated Volume: 2351.32 Gal. Total Flooded Shell Weight:
26970.54 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 7327.45 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -30 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.5830 in. Ext. Nominal t: 1.0000 in.Minimum
L/Do: 3.4186 Nominal L/Do: 3.4186Minimum Do/t: 187.7730 Nominal
Do/t: 98.2857
Minimum Factor A:0.0001627 Nominal Factor A:0.0004162Minimum
Factor B: 2112 PSI Nominal Factor B: 5414 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
284.00 * 42.1250
2 * 19700 * 0.85 + 0.4 * 284.00 = 0.3560 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.4810 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
284.00 * 43.0000
19700 * 0.85 + 0.4 * 284.00 = 0.7244 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 0.8494 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 5414
3 * ( 86.0000 / 0.8750 ) = maximum external pressure of 73.45 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.0000
42.5000 = elongation of 1.18 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 9 of
95
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Pressure Vessel Engineering, Ltd.Shell 5
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 5 Mark Number: S5
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.0000 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 10 of
95
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Pressure Vessel Engineering, Ltd.Shell 6
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 6 Mark Number: S6
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 17.00 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 72.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 10819 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
19075 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 9380 PSI
Outside Diameter (new): 122.2500 in.Outside Diameter (corroded):
122.2500 in. Specific Gravity: 1.00
Shell Surface Area: 192.03 Sq. Ft. Weight of Fluid: 29452.36
lb.Shell Estimated Volume: 3525.52 Gal. Total Flooded Shell Weight:
38082.68 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 8630.32 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -26 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.6939 in. Ext. Nominal t: 1.1250 in.Minimum
L/Do: 2.4049 Nominal L/Do: 2.4049Minimum Do/t: 214.8880 Nominal
Do/t: 122.2500
Minimum Factor A:0.0001862 Nominal Factor A:0.0004285Minimum
Factor B: 2418 PSI Nominal Factor B: 5573 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
267.00 * 60.1250
2 * 19700 * 0.85 + 0.4 * 267.00 = 0.4778 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.6028 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
267.00 * 61.1250
19700 * 0.85 + 0.4 * 267.00 = 0.9685 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 1.0935 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 5573
3 * ( 122.2500 / 1.0000 ) = maximum external pressure of 60.78 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.1250
60.5625 = elongation of 0.93 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 11 of
95
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Pressure Vessel Engineering, Ltd.Shell 6
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 6 Mark Number: S6
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.1250 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 12 of
95
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Pressure Vessel Engineering, Ltd.Shell 7
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 7 Mark Number: S7
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 3.50 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 12.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 12806 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
6229 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 2965 PSI
Outside Diameter (new): 37.2500 in.Outside Diameter (corroded):
37.2500 in. Specific Gravity: 1.00
Shell Surface Area: 9.75 Sq. Ft. Weight of Fluid: 423.57
lb.Shell Estimated Volume: 50.70 Gal. Total Flooded Shell Weight:
806.22 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 382.65 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -30 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.4224 in. Ext. Nominal t: 1.0000 in.Minimum
L/Do: 7.8926 Nominal L/Do: 7.8926Minimum Do/t: 125.2520 Nominal
Do/t: 42.5714
Minimum Factor A:0.0001088 Nominal Factor A:0.0006686Minimum
Factor B: 1409 PSI Nominal Factor B: 8458 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
253.50 * 17.7500
2 * 19700 * 0.85 + 0.4 * 253.50 = 0.1340 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.2590 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
253.50 * 18.6250
19700 * 0.85 + 0.4 * 253.50 = 0.2803 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 0.4053 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 8458
3 * ( 37.2500 / 0.8750 ) = maximum external pressure of 264.90 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 1.0000
18.1250 = elongation of 2.76 %
External loads do not control design.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 13 of
95
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Pressure Vessel Engineering, Ltd.Shell 7
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 7 Mark Number: S7
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 1.0000 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 14 of
95
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Pressure Vessel Engineering, Ltd.Shell 8
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 8 Mark Number: S8
Date Printed: 11/12/2009
Cylindrical Shell Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 3.50 PSI Long. Joint Efficiency: 85 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Shell Length: 104.0000 in. Material Stress (cold): 20000
PSICompressive Stress: 11946 PSI
Corrosion Allowance: 0.1250 in. Actual Circumferential Stress:
10990 PSIExternal Corrosion Allowance: 0.0000 in. Actual
Longitudinal Stress: 5346 PSI
Outside Diameter (new): 37.2500 in.Outside Diameter (corroded):
37.2500 in. Specific Gravity: 1.00
Shell Surface Area: 84.52 Sq. Ft. Weight of Fluid: 3828.81
lb.Shell Estimated Volume: 458.32 Gal. Total Flooded Shell Weight:
5922.91 lb.
Circ. Joint Efficiency: 85 % Shell Weight: 2094.11 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: Yes Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -55 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550
FDimension L: 294.0000 in.
Ext. Minimum t: 0.4224 in. Ext. Nominal t: 0.6250 in.Minimum
L/Do: 7.8926 Nominal L/Do: 7.8926Minimum Do/t: 125.2520 Nominal
Do/t: 74.5000
Minimum Factor A:0.0001088 Nominal Factor A:0.0002451Minimum
Factor B: 1409 PSI Nominal Factor B: 3184 PSI
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
253.50 * 18.1250
2 * 19700 * 0.85 + 0.4 * 253.50 = 0.1368 + 0.1250 ( c o r r o s
i o n ) + 0.0000 (ext. corrosion) = minimum of 0.2618 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
253.50 * 18.6250
19700 * 0.85 + 0.4 * 253.50 = 0.2803 + 0.1250 ( c o r r o s i o
n ) + 0.0000 (ext. corrosion) = minimum of 0.4053 i n .
Maximum External Pressure Calculation per Paragraph UG-28
Pa ( u s i n g nominal t ) = 4B
3(Do / t) =
4 * 3184
3 * ( 37.2500 / 0.5000 ) = maximum external pressure of 56.98 P
S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 0.6250
18.3125 = elongation of 1.71 %
External loads do not control design.
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Pressure Vessel Engineering, Ltd.Shell 8
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 8 Mark Number: S8
Date Printed: 11/12/2009
Nominal Shell Thickness Selected = 0.6250 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Ring Stiffener 1
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 1 Mark Number: RS1
Date Printed: 11/12/2009
Stiffener Design Information
D e s c r i p t i o n : Ring 1Q u a n t i t y : 1
Stiffener Is: Outside Design Temperature: 550 FMaterial: SA-36
Factor B Chart: CS-2
S t r e s s ( h o t ) : 16600 PSI S t r e s s ( c o l d ) :
16600 PSIA s : 5.0000 sq. in. L s : 294.0000 in.d 1 : 5.0000 in. d
2 : 1.0000 in.
Corrosion Allowance: 0.0000 in.
Cylindrical Shell Design InformationShell 5
External Pressure: 15.00 PSI Shell Factor B Chart: CS-2Shell
Thickness: 1.0000 in. Shell Outside Diameter: 86.0000 in.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Ring Stiffener 1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 1 Mark Number: RS1
Date Printed: 11/12/2009
FLATBAR Stiffener CalculationsAvailable Moments of Intertia
Available Stiffening Ring Moment of Inertia (I)
y = d12
= 5.0000
2= 2.5000 i n .
I = d2 * d1
12 =
1.0000 * 5.0000
12= 10.4167 i n . ^4
Lsh = 1.1 * Do * t = 1.1 * 86.0000 * 0.8750 = 9.5421 i n .
Ash(Shell Area) = Lsht = 9.5421 * 0.8750 = 8.3493 sq. in.
Ish(Shell Moment of Inertia) = Lsht
12 =
9.5421 * 0.8750
12 = 0.5327 i n . ^4
X(Neutral Axis) = As(t + y) + (Ash * t)
As + Ash =
5.0000 * (0.8750 + 2.5000) + (8.3493 * * 0.8750)
5.0000 + 8.3493 = 1.5377 i n .
I' = I + Ish + As * ((t + y) - X) + Ash * (X - t) = 10.4167 +
0.5327 + 5.0000 * ((0.8750 + 2.5000) - 1.5377) + 8.3493 * (1.5377 -
( * 0.8750)) = 37.9341 i n . ^4
Required Moments of Inertia
Factor B = PDo
t + AsLs
= 15.00 * 86.0000
0.8750 + 5.0000
294.0000
= 1085 P S I
From Factor B Table Factor A = 0.0000840
Ring Moment(Is) =
Do * Ls t +
AsLs
* A
14 =
86.0000 * 294.00000.8750 + 5.0000
294.0000 * 0.0000840
14 = 11.6376 i n . ^4
Combined Moment(Is') =
Do * Ls t +
AsLs
* A
10.9 =
86.0000 * 294.00000.8750 + 5.0000
294.0000 * 0.0000840
10.9 = 14.9474 i n . ^4
I' greater than or equal to Is'Stiffener Ring PASSES the
requirements of UG-29
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Ring Stiffener 2
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 2 Mark Number: RS2
Date Printed: 11/12/2009
Stiffener Design Information
D e s c r i p t i o n : Ring 2Q u a n t i t y : 1
Stiffener Is: Outside Design Temperature: 550 FMaterial: SA-36
Factor B Chart: CS-2
S t r e s s ( h o t ) : 16600 PSI S t r e s s ( c o l d ) :
16600 PSIA s : 5.0000 sq. in. L s : 294.0000 in.d 1 : 5.0000 in. d
2 : 1.0000 in.
Corrosion Allowance: 0.0000 in.
Cylindrical Shell Design InformationShell 2
External Pressure: 15.00 PSI Shell Factor B Chart: CS-2Shell
Thickness: 1.1250 in. Shell Outside Diameter: 122.2500 in.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Ring Stiffener 2
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 2 Mark Number: RS2
Date Printed: 11/12/2009
FLATBAR Stiffener CalculationsAvailable Moments of Intertia
Available Stiffening Ring Moment of Inertia (I)
y = d12
= 5.0000
2= 2.5000 i n .
I = d2 * d1
12 =
1.0000 * 5.0000
12= 10.4167 i n . ^4
Lsh = 1.1 * Do * t = 1.1 * 122.2500 * 1.0000 = 12.1623 i n .
Ash(Shell Area) = Lsht = 12.1623 * 1.0000 = 12.1623 sq. in.
Ish(Shell Moment of Inertia) = Lsht
12 =
12.1623 * 1.0000
12 = 1.0135 i n . ^4
X(Neutral Axis) = As(t + y) + (Ash * t)
As + Ash =
5.0000 * (1.0000 + 2.5000) + (12.1623 * * 1.0000)
5.0000 + 12.1623 = 1.3740 i n .
I' = I + Ish + As * ((t + y) - X) + Ash * (X - t) = 10.4167 +
1.0135 + 5.0000 * ((1.0000 + 2.5000) - 1.3740) + 12.1623 * (1.3740
- ( * 1.0000)) = 43.3201 i n . ^4
Required Moments of Inertia
Factor B = PDo
t + AsLs
= 15.00 * 122.2500
1.0000 + 5.0000
294.0000
= 1352 P S I
From Factor B Table Factor A = 0.0001050
Ring Moment(Is) =
Do * Ls t +
AsLs
* A
14 =
122.2500 * 294.00001.0000 + 5.0000
294.0000 * 0.0001050
14 = 33.5143 i n . ^4
Combined Moment(Is') =
Do * Ls t +
AsLs
* A
10.9 =
122.2500 * 294.00001.0000 + 5.0000
294.0000 * 0.0001050
10.9 = 43.0459 i n . ^4
I' greater than or equal to Is'Stiffener Ring PASSES the
requirements of UG-29
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 20 of
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Pressure Vessel Engineering, Ltd.Ring Stiffener 3
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 3 Mark Number: RS3
Date Printed: 11/12/2009
Stiffener Design Information
D e s c r i p t i o n : Q u a n t i t y : 1
Stiffener Is: Outside Design Temperature: 550 FMaterial: SA-36
Factor B Chart: CS-2
S t r e s s ( h o t ) : 16600 PSI S t r e s s ( c o l d ) :
16600 PSIA s : 5.0000 sq. in. L s : 294.0000 in.d 1 : 5.0000 in. d
2 : 1.0000 in.
Corrosion Allowance: 0.0000 in.
Cylindrical Shell Design InformationShell 6
External Pressure: 15.00 PSI Shell Factor B Chart: CS-2Shell
Thickness: 1.1250 in. Shell Outside Diameter: 122.2500 in.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Ring Stiffener 3
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 3 Mark Number: RS3
Date Printed: 11/12/2009
FLATBAR Stiffener CalculationsAvailable Moments of Intertia
Available Stiffening Ring Moment of Inertia (I)
y = d12
= 5.0000
2= 2.5000 i n .
I = d2 * d1
12 =
1.0000 * 5.0000
12= 10.4167 i n . ^4
Lsh = 1.1 * Do * t = 1.1 * 122.2500 * 1.0000 = 12.1623 i n .
Ash(Shell Area) = Lsht = 12.1623 * 1.0000 = 12.1623 sq. in.
Ish(Shell Moment of Inertia) = Lsht
12 =
12.1623 * 1.0000
12 = 1.0135 i n . ^4
X(Neutral Axis) = As(t + y) + (Ash * t)
As + Ash =
5.0000 * (1.0000 + 2.5000) + (12.1623 * * 1.0000)
5.0000 + 12.1623 = 1.3740 i n .
I' = I + Ish + As * ((t + y) - X) + Ash * (X - t) = 10.4167 +
1.0135 + 5.0000 * ((1.0000 + 2.5000) - 1.3740) + 12.1623 * (1.3740
- ( * 1.0000)) = 43.3201 i n . ^4
Required Moments of Inertia
Factor B = PDo
t + AsLs
= 15.00 * 122.2500
1.0000 + 5.0000
294.0000
= 1352 P S I
From Factor B Table Factor A = 0.0001050
Ring Moment(Is) =
Do * Ls t +
AsLs
* A
14 =
122.2500 * 294.00001.0000 + 5.0000
294.0000 * 0.0001050
14 = 33.5143 i n . ^4
Combined Moment(Is') =
Do * Ls t +
AsLs
* A
10.9 =
122.2500 * 294.00001.0000 + 5.0000
294.0000 * 0.0001050
10.9 = 43.0459 i n . ^4
I' greater than or equal to Is'Stiffener Ring PASSES the
requirements of UG-29
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Conical Reducer 1
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 1 Mark Number: R1
Date Printed: 11/12/2009
Conical Reducer Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 34.00 PSI Joint Efficiency: 85 %
Conical Reducer Material: SA-516 Gr. 70 Factor B Chart:
CS-2Material Condition: Normalized Material Stress (hot): 19700
PSI
Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000
PSIExternal Corrosion Allowance: 0.0000 in. Actual Conical Reducer
Stress: 18226 PSISmall End of Cone Located at: Bottom Outside Ds :
86.0000 in.
Outside Diameter : 122.2500 in. Cone Height (h) : 120.0000
in.angle a (): 8.59
Conical Reducer Surface Area: 275.69 Sq. Ft. Specific Gravity:
1.00Conical Reducer Estimated Volume: 4256.50 Gal. Weight of Fluid:
35499.18 lb.
Conical Reducer Weight: 13726.15 lb. Total Flooded Conical
Reducer Weight: 49225.33 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -21 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550 FExt.
Minimum t: 0.5053 in. Ext. Nominal t: 1.2500 in.
Minimum te: 0.3760 in. Nominal te: 1.1124 in.Minimum Factor
A:0.0002814 Nominal Factor A:0.0014486Minimum Factor B: 3657 PSI
Nominal Factor B: 10066 PSI
Design Thickness Calculations
Design Thickness Calculations per Appendix 1-4(e)
t = PDo
2 cos (SE + 0.4P) =
284.00 * 122.2500
2 * 0.9888 * (19700 * 0.85 + 0.4 * 284.00 ) = 1.0414 + 0.1250 (
c o r r o s i o n ) + 0.0000 (ext. corrosion)
= minimum of 1.1664 i n .
Maximum External Pressure Calculation per Paragraph UG-33
Pa ( u s i n g nominal t) = 4B
3Dlte
= 4 * 10066
3122.2500
1.1124
= = maximum external pressure of 122.13 P S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
elongation = 50t
Rf =
50 * 1.2500
42.3750 = elongation of 1.47 %
Nominal Conical Reducer Thickness Selected = 1.2500 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Conical Reducer 2
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 2 Mark Number: R2
Date Printed: 11/12/2009
Conical Reducer Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 3.50 PSI Joint Efficiency: 85 %
Conical Reducer Material: SA-516 Gr. 70 Factor B Chart:
CS-2Material Condition: Normalized Material Stress (hot): 19700
PSI
Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000
PSIExternal Corrosion Allowance: 0.0000 in. Actual Conical Reducer
Stress: 19688 PSISmall End of Cone Located at: Top Outside Ds :
37.2500 in.
Outside Diameter : 122.2500 in. Cone Height (h) : 100.0000
in.angle a (): 23.03
Conical Reducer Surface Area: 189.05 Sq. Ft. Specific Gravity:
1.00Conical Reducer Estimated Volume: 2236.83 Gal. Weight of Fluid:
18655.18 lb.
Conical Reducer Weight: 8443.82 lb. Total Flooded Conical
Reducer Weight: 27099.00 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 224.75 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -26 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550 FExt.
Minimum t: 0.4624 in. Ext. Nominal t: 1.1250 in.
Minimum te: 0.3105 in. Nominal te: 0.9203 in.Minimum Factor
A:0.0003408 Nominal Factor A:0.0018060Minimum Factor B: 4431 PSI
Nominal Factor B: 10518 PSI
Design Thickness Calculations
Design Thickness Calculations per Appendix 1-4(e)
t = PDo
2 cos (SE + 0.4P) =
253.50 * 122.2500
2 * 0.9203 * (19700 * 0.85 + 0.4 * 253.50 ) = 0.9995 + 0.1250 (
c o r r o s i o n ) + 0.0000 (ext. corrosion)
= minimum of 1.1245 i n .
Maximum External Pressure Calculation per Paragraph UG-33
Pa ( u s i n g nominal t) = 4B
3Dlte
= 4 * 10518
3122.2500
0.9203
= = maximum external pressure of 105.57 P S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
elongation = 50t
Rf =
50 * 1.1250
18.0625 = elongation of 3.11 %
Nominal Conical Reducer Thickness Selected = 1.1250 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 24 of
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Pressure Vessel Engineering, Ltd.Head 1
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 1 Mark Number: H1
Date Printed: 11/12/2009
Ellipsoidal Head Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 34.00 PSI Joint Efficiency: 100 %
Head Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000
PSIExternal Corrosion Allowance: 0.0000 in. Actual Head Stress:
13701 PSI
Head Location: Bottom Straight Flange : 1.5000 in.Outside
Diameter : 86.0000 in. Head Depth (ho) : 22.1250 in.
Thin Out : 0.2500 in.
K = 1
6 [2 + (D/2h) ] : 1.00
Head Surface Area: 57.14 Sq. Ft. Specific Gravity: 1.00Head
Estimated Volume: 365.50 Gal. Weight of Fluid: 3048.30 lb.
Head Weight: 2879.93 lb. Total Flooded Head Weight: 5928.22
lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -30 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550 FExt.
Minimum t: 0.6023 in. Ext. Nominal t: 1.2500 in.
Minimum t - Ca - ext. Ca - Thin Out: 0.2273 in. Nominal t - Ca -
ext. Ca. - Thin Out: 0.8750 in.Minimum Factor A:0.0003797 Nominal
Factor A:0.0014618Minimum Factor B: 4939 PSI Nominal Factor B:
10083 PSI
Design Thickness Calculations
Design Thickness Calculations per Appendix 1-4(c)
t = PDoK
2SE + 2P(K - 0.1) =
284.00 * 86.0000 * 1.00
2 * 19700 * 1.00 + 2 * 284.00 * (1.00 - 0.1)
= 0.6120 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext.
corrosion) + 0.2500(thin out) = minimum of 0.9870 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 25 of
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Pressure Vessel Engineering, Ltd.Head 1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 1 Mark Number: H1
Date Printed: 11/12/2009
Maximum External Pressure Calculation per Paragraph UG-33
Pa ( u s i n g nominal t) = B
Rot
= 10083
74.82000.8750
= maximum external pressure of 117.92 P S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
elongation = 75tRf
= 75 * 1.2500
14.4075 = elongation of 6.51 %
tmin(external) = 1.67PDo K
2SE + 2(1.67P)(K - 0.1) =
1.67 * 15.00 * 86.0000 * 1.00 2 * 19700 * 1.0 + 2(1.67 * 15.00)
* (1.00 - 0.1 )
= Greater of(0.0546(Calc),0.0938(MinT)) + 0.1250 ( c o r r o s i
o n ) + 0.0000 (ext. corrosion) + 0.2500 ( T h i n o u t )= minimum
of 0.4688 in.
Nominal Head Thickness Selected = 1.2500 i n .Minimum Thickness
after forming, ts (uncorroded) = 1.0000 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
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Pressure Vessel Engineering, Ltd.Head 2
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 2 Mark Number: H2
Date Printed: 11/12/2009
Ellipsoidal Head Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 0.00 PSI Joint Efficiency: 100 %
Head Material: SA-516 Gr. 70 Factor B Chart: CS-2Material
Condition: Normalized Material Stress (hot): 19700 PSI
Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000
PSIExternal Corrosion Allowance: 0.0000 in. Actual Head Stress:
12070 PSI
Head Location: Top Straight Flange : 1.5000 in.Outside Diameter
: 37.2500 in. Head Depth (ho) : 9.5938 in.
Thin Out : 0.0625 in.
K = 1
6 [2 + (D/2h) ] : 0.99
Head Surface Area: 11.39 Sq. Ft. Specific Gravity: 1.00Head
Estimated Volume: 33.37 Gal. Weight of Fluid: 278.34 lb.
Head Weight: 258.30 lb. Total Flooded Head Weight: 536.64
lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: D Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: No Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -55 F
External Pressure Data
Design Pressure (Pa): 15.00 PSI Design Temperature: 550 FExt.
Minimum t: 0.2860 in. Ext. Nominal t: 0.5625 in.
Minimum t - Ca - ext. Ca - Thin Out: 0.0985 in. Nominal t - Ca -
ext. Ca. - Thin Out: 0.3750 in.Minimum Factor A:0.0003799 Nominal
Factor A:0.0014464Minimum Factor B: 4941 PSI Nominal Factor B:
10064 PSI
Design Thickness Calculations
Design Thickness Calculations per Appendix 1-4(c)
t = PDoK
2SE + 2P(K - 0.1) =
250.00 * 37.2500 * 0.99
2 * 19700 * 1.00 + 2 * 250.00 * (0.99 - 0.1)
= 0.2314 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext.
corrosion) + 0.0625(thin out) = minimum of 0.4189 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 27 of
95
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Pressure Vessel Engineering, Ltd.Head 2
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13 N u m b e r
: 2 Mark Number: H2
Date Printed: 11/12/2009
Maximum External Pressure Calculation per Paragraph UG-33
Pa ( u s i n g nominal t) = B
Rot
= 10064
32.40750.3750
= maximum external pressure of 116.45 P S I
Extreme Fiber Elongation Calculation per Paragraph UCS-79
elongation = 75tRf
= 75 * 0.5625
6.2369 = elongation of 6.76 %
tmin(external) = 1.67PDo K
2SE + 2(1.67P)(K - 0.1) =
1.67 * 15.00 * 37.2500 * 0.99 2 * 19700 * 1.0 + 2(1.67 * 15.00)
* (0.99 - 0.1 )
= Greater of(0.0234(Calc),0.0938(MinT)) + 0.1250 ( c o r r o s i
o n ) + 0.0000 (ext. corrosion) + 0.0625 ( T h i n o u t )= minimum
of 0.2813 in.
Nominal Head Thickness Selected = 0.5625 i n .Minimum Thickness
after forming, ts (uncorroded) = 0.5000 i n .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 28 of
95
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Pressure Vessel Engineering, Ltd.N1
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 1 Mark Number: N1ID Number: N1
Date Printed: 11/12/2009
Nozzle Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 0.00 PSI Nozzle Efficiency (E): 100 %
Nozzle Material: SA-106 Gr. B Joint Efficiency (E1): 1.00Factor
B Chart: CS-2
External Projection: 2.0000 in. Allowable Stress at Design
Temperature (Sn): 17100 PSIInternal Projection: 0.0000 in.
Allowable Stress at Ambient Temperature: 17100 PSI
Inside Corrosion Allowance: 0.1250 in. Correction Factor (F):
1.00External Corrosion Allowance: 0.0000 in. Nozzle Path: None
Nozzle Pipe Size: 8 Nozzle Pipe Schedule: 80Nozzle ID (new):
7.6250 in. Nozzle Wall Thickness(new): 0.5000 in.
Nozzle ID (corroded): 7.8750 in. Nozzle Wall
Thickness(corroded): 0.3750 in.Outer "h" Limit: 1.6875 in. Upper
Weld Leg Size(Weld 41): 0.3750 in.
Internal "h" Limit: 0.6250 in. Internal Weld Leg Size(Weld 43):
0.0000 in.OD, Limit of Reinforcement: 15.7500 in. Outside Groove
Weld Depth: 1.2500 in.
Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: Yes Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -125 F
Reinforcing Pad Information
Reinforcing Material: SA-516 Gr. 70 Allowable Stress at Design
Temperature(Sp): 19700 PSIAllowable Stress at Ambient Temperature:
20000 PSI
Reinforcing Plate Thickness(te): 0.7500 in. Repad to Vessel Weld
Leg Size(Weld 42): 0.6250 in.OD, Reinforcing Plate(Dp): 10.0000 in.
Repad to Nozzle Groove Weld Depth: 0.7500 in.
Host Component: Head 1 - Head 1
Material: SA-516 Gr. 70 Head wall thickness(new): 1.2500
in.Material Stress(Sv): 19700 PSI Head wall thickness - thin out
(corroded): 0.8750 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3750 in.
Nozzle Wall Thickness(tn): 0.5000 in.
Outside Groove Weld Depth: 1.2500 in.
Repad to Vessel Weld Leg Size(Weld 42): 0.6250 in.
Repad Thickness(te): 0.7500 in.
Nozzle passes through the vessel, attached by a groove weld.Pipe
Size: 8 Schedule: 80
Nozzle is adequate for UG-45 requirements.Opening is adequately
reinforced for Internal Pressure.Opening is adequately reinforced
for External Pressure.
Weld Strength Paths are adequate.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 29 of
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Pressure Vessel Engineering, Ltd.N1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
1 Mark Number: N1
ID Number: N1
Date Printed: 11/12/2009
Required Head Thickness per Paragraph UG-37(a)
tr = P K1 Do
(2SE + 0.8P) =
250.00 * 0.9000 * 86.0000
(2 * 19700 * 1 + 0.8 * 250.00) = 0.4886 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph
UG-37(a)
trn = PRn
SE - 0.6P =
250.00 * 3.9375
17100 * 1 - 0.6 * 250.00 = 0.0581 i n .
Required Nozzle Thickness for External Pressure per Paragraph
UG-37(a)
trn = 3 * Do * Pa
4B =
3 * 8.6250 * 15.00
4 * 6410 = 0.0152 i n .
Strength Reduction Factors
fr1 = min Sn
Sv, 1.0000 = min
17100
19700, 1.0000 = 0.8680 fr2 = min
Sn
Sv, 1.0000 = min
17100
19700, 1.0000 = 0.8680
fr3 = min Sn
Sv, 1.0000 = min
17100
19700, 1.0000 = 0.8680 fr4 = min
Sp
Sv, 1.0000 = min
19700
19700, 1.0000 = 1.0000
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion) per
Paragraph UG-45(a)
t = PRn
SE - 0.6P + Ca + ext. Ca =
250.00 * 3.9375
17100 * 1.00 - 0.6 * 250.00 + 0.1250 + 0.0000 = 0.1831 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) per
Paragraph UG-45(b)(1)
t = P K Do
(2SE + 2P(K - 0.1)) + Ca + ext. Ca =
250.00 * 1.0000 * 86.0000
(2 * 19700 * 1 + 2 * 250.00 * (1.0000 - 0.1)) + 0.1250 + 0.0000
= 0.6645 i n .
Nozzle Thickness for External Pressure (plus corrosion) per
Paragraph UG-45(b)(2)
t = P K Do
(2SE + 2P(K - 0.1)) + Ca + ext. Ca =
15.00 * 1.0000 * 86.0000
(2 * 19700 * 1 + 2 * 15.00 * (1.0000 - 0.1)) + 0.1250 +
0.0000
= Greater Of (0.0327(Calculated), 0.0938(Minimum Allowed)) +
0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = 0.2188 i n
.Minimum Thickness for Internal and External Pressure per Paragraph
UG-45(b)(3)
t = Greater of the thicknesses determined by UG-45(b)(1) or
UG-45(b)(2) = 0.6645 i n .
Minimum Thickness of Standard Wall Pipe (plus corrosion) per
Paragraph UG-45(b)(4)t = minimum thickness of standard wall pipe +
Ca + ext. Ca = 0.4067 i n .
Nozzle Minimum Thickness per Paragraph UG-45(b)t = Smallest of
UG-45(b)(3) or UG-45(b)(4) = 0.4067 i n .
Wall thickness = tn * 0.875(pipe) = 0.4375 is greater than or
equal to UG-45 value of 0.4067
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 30 of
95
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Pressure Vessel Engineering, Ltd.N1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
1 Mark Number: N1
ID Number: N1
Date Printed: 11/12/2009
Nozzle Reinforcement Calculations
Area Required for Internal PressureA = d tr F + 2 tn tr F (1 -
fr1) = (7.8750 * 0.4886 * 1.00) + (2 * 0.3750 * 0.4886 * 1.00 * (1
- 0.8680)) = 3.8961 sq. in.
Area Available - Internal PressureA1 Formula 1 = d(E1 t - F tr)
- 2tn(E1 t - F tr)(1 - fr1) = 7.8750 * (1.00 * 0.8750 - 1.00 *
0.4886) - 2 * 0.3750 * (1.00 * 0.8750 - 1.00 * 0.4886) * (1 -
0.8680) = 3.0047 sq. in.A1 Formula 2 = 2(t + tn)(E1 t - F tr) -
2tn(E1 t - F tr)(1 - fr1) = 2 * (0.8750 + 0.3750)(1.00 * 0.8750 -
1.00 * 0.4886) - 2 * 0.3750 * (1.00 * 0.8750 - 1.00 * 0.4886) * (1
- 0.8680) = 0.9278 sq. in.A1 = Larger value of A1 Formula 1 a n d
A1 Formula 2 = 3.0047 sq. in.
A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.3750 - 0.0581) * 0.8680 *
0.8750 = 1.2035 sq. in.A2 Formula 2 = 2(tn - trn) fr2 (2.5 tn + te
) = 2(0.3750 - 0.0581) * 0.8680 * (2.5 * 0.3750 + 0.7500) = 0.9284
sq. in.A2 = Smaller value of A2 Formula 1 a n d A2 Formula 2 =
0.9284 sq. in.
A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 *
0.8750 * 0.2500 * 0.8680 = 0.9494 sq. in.5 * ti * ti * fr2 = 5 *
0.2500 * 0.2500 * 0.8680 = 0.2713 sq. in.2 * h * ti * fr2 = 2 *
0.0000 * 0.2500 * 0.8680= 0.0000 sq. in.
= 0.0000 sq. in.
A41 = (leg) * fr3 = (0.3750) * 0.8680 = 0.1221 sq. in.
A42 = (leg) * fr4 = (0.6250) * 1.0000 = 0.3906 sq. in.
A43 = (leg) * fr2 = 0 * 0.8680 = 0.0000 sq. in.
A5 = (Dp - d - 2tn) te fr4 = (10.0000 - 7.8750 - 2 * 0.3750) *
0.7500 * 1.0000 = 1.0313 sq. in.
Area Available (Internal Pressure) = A1 + A2 + A3 + A41 + A42 +
A43 + A5 = 5.4771 sq. in., which is greater than A (3.8961)
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 31 of
95
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Pressure Vessel Engineering, Ltd.N1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
1 Mark Number: N1
ID Number: N1
Date Printed: 11/12/2009
Nozzle Reinforcement Calculations
Area Required for External Pressure
A = * (d tr F + 2 tn tr F (1 - fr1)) = * ((7.8750 * 0.2273 *
1.0) + (2 * 0.3750 * 0.2273 * 1.0 * (1 - 0.8680))) = 0.9062 sq.
in.Area Available - External Pressure
A1 Formula 1 = d(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) =
7.8750 * (1.00 * 0.8750 - 1.00 * 0.2273) - 2 * 0.3750 * (1.00 *
0.8750 - 1.00 * 0.2273) * (1 - 0.8680) = 5.0365 sq. in.A1 Formula 2
= 2(t + tn)(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 2 * (0.8750
+ 0.3750)(1.00 * 0.8750 - 1.00 * 0.2273) - 2 * 0.3750 * (1.00 *
0.8750 - 1.00 * 0.2273) * (1 - 0.8680) = 1.5551 sq. in.A1 = Larger
value of A1 Formula 1 a n d A1 Formula 2 = 5.0365 sq. in.
A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.3750 - 0.0152) * 0.8680 *
0.8750 = 1.3664 sq. in.A2 Formula 2 = 2(tn - trn) fr2 (2.5 tn + te
) = 2(0.3750 - 0.0152) * 0.8680 * (2.5 * 0.3750 + 0.7500) = 1.0541
sq. in.A2 = Smaller value of A2 Formula 1 a n d A2 Formula 2 =
1.0541 sq. in.
A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 *
0.8750 * 0.2500 * 0.8680 = 0.9494 sq. in.5 * ti * ti * fr2 = 5 *
0.2500 * 0.2500 * 0.8680 = 0.2713 sq. in.2 * h * ti * fr2 = 2 *
0.0000 * 0.2500 * 0.8680= 0.0000 sq. in.
= 0.0000 sq. in.
A41 = (leg) * fr3 = (0.3750) * 0.8680 = 0.1221 sq. in.
A42 = (leg) * fr4 = (0.6250) * 1.0000 = 0.3906 sq. in.
A43 = (leg) * fr2 = 0 * 0.8680 = 0.0000 sq. in.
A5 = (Dp - d - 2tn) te fr4 = (10.0000 - 7.8750 - 2 * 0.3750) *
0.7500 * 1.0000 = 1.0313 sq. in.
Area Available (External Pressure) = A1 + A2 + A3 + A41 + A42 +
A43 + A5 = 7.6346 sq. in., which is greater than A (0.9062)
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 32 of
95
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Pressure Vessel Engineering, Ltd.N1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
1 Mark Number: N1
ID Number: N1
Date Printed: 11/12/2009
Nozzle Weld Strength Calculations
Attachment Weld Strength per Paragraph UW-16 (Corroded
Condition)
Weld 41 tmin = smaller of 0.75, te, or tn = smaller of 0.75,
0.7500, or 0.3750 = 0.3750 i n .
Weld 41 Leg min. = (smaller of 0.25 or (tmin * 0.7)) + ext.
CA
0.7 =
0.2500
0.7 = 0.3571 i n .
Weld 41, actual weld leg = 0.3750 i n .
Weld 42 tmin = smaller of 0.75, t, or te = smaller of 0.75,
0.8750, or 0.7500 = 0.7500 i n .
Weld 42 Leg min. = 0.5 * tmin + ext. CA
0.7 =
0.5 * 0.7500 + 0.0000
0.7 = 0.5357 i n .
Weld 42, actual weld leg = 0.6250 i n .
Unit Stresses per Paragraphs UG-45(c) and UW-15Nozzle wall in
shear = 0.70 * Sn = 0.70 * 17100 = 11970 P S IUpper fillet, Weld
41, in shear = 0.49 * Material Stress = 0.49 * 17100 = 8379 P S
IVessel groove weld, in tension = 0.74 * Material Stress = 0.74 *
17100 = 12654 P S IOuter fillet, Weld 42, in shear = 0.49 *
Material Stress = 0.49 * 19700 = 9653 P S IRepad groove weld, in
tension = 0.74 * Material Stress = 0.74 * 17100 = 12654 P S I
Strength of Connection ElementsNozzle wall in shear = * * mean
nozzle diameter * tn * Nozzle wall in shear unit stress = * *
8.2500 * 0.3750 * 11970 = 58100 l b .Upper fillet in shear = * *
Nozzle OD * weld leg * upper fillet in shear unit stress = * *
8.6250 * 0.3750 * 8379 = 42500 l b .Groove Weld in Tension = * *
Nozzle OD * groove depth * groove weld tension unit stress = * *
8.6250 * 0.8750 * 12654 = 149900 l b .Outer fillet in shear = * *
Plate OD * weld leg * outer fillet in shear unit stress = * *
10.0000 * 0.6250 * 9653 = 94700 l b .Repad groove weld = * * Nozzle
OD * Groove Depth * repad groove weld in tension unit stress = * *
8.6250 * 0.7500 * 12654 = 128500 l b .
Load to be carried by welds, per UG-41(b)(1) and Fig. UG-41.1
sketch (a)W = [A - A1 + 2 tn fr1(E1t - Ftr)] Sv = [3.8961 - 3.0047
+ 2 * 0.3750 * 0.8680 * (1.00 * 0.8750 - 1.0000 * 0.4886)] * 19700
= 22500 l b .W1-1 = (A2 + A5 + A41 + A42) * Sv = (0.9284 + 1.0313 +
0.1221 + 0.3906) * 19700 = 48700 l b .W2-2 = (A2 + A3 + A41 + A43 +
2 tn t fr1) Sv = (0.9284 + 0.0000 + 0.1221 + 0.0000 + 2 * 0.3750 *
0.8750 * 0.8680) * 19700 = 31900 l b .W3-3 = (A2 + A3 + A5 + A41 +
A42 + A43 + 2 tn t fr1) * Sv = (0.9284 + 0.0000 + 1.0313 + 0.1221 +
0.3906 + 0.0000 + 2 * 0.3750 * 0.8750 * 0.8680) * 19700 = 59900 l b
.
Check Strength PathsPath 1-1 = Outer fillet in shear + Nozzle
wall in shear = 94700 + 58100 = 152800 l b .Path 2-2 = Upper fillet
in shear + Repad groove weld + Groove weld in tension + Inner
fillet in shear = 42500 + 128500 + 149900 + 0 = 320900 l b .Path
3-3 = Outer fillet in shear + Inner fillet in shear + Groove weld
in tension = 94700 + 0 + 149900 = 244600 l b .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 33 of
95
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Pressure Vessel Engineering, Ltd.N1
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
1 Mark Number: N1
ID Number: N1
Date Printed: 11/12/2009
Plate Strength = A5 * Sp = 1.0313 * 19700 = 20317 l b .
Outer fillet weld strength(94700) is greater than plate
strength(20317).
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 34 of
95
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Pressure Vessel Engineering, Ltd.N2
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 2 Mark Number: N2ID Number: 2
Date Printed: 11/12/2009
Nozzle Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 0.00 PSI Nozzle Efficiency (E): 100 %
Nozzle Material: SA-106 Gr. B Joint Efficiency (E1): 1.00Factor
B Chart: CS-2
External Projection: 6.0000 in. Allowable Stress at Design
Temperature (Sn): 17100 PSIInternal Projection: 0.0000 in.
Allowable Stress at Ambient Temperature: 17100 PSI
Inside Corrosion Allowance: 0.1250 in. Correction Factor (F):
1.00External Corrosion Allowance: 0.0000 in. Nozzle Path: None
Nozzle Pipe Size: 6 Nozzle Pipe Schedule: 160Nozzle ID (new):
5.1890 in. Nozzle Wall Thickness(new): 0.7180 in.
Nozzle ID (corroded): 5.4390 in. Nozzle Wall
Thickness(corroded): 0.5930 in.Outer "h" Limit: 1.4825 in. Upper
Weld Leg Size(Weld 41): 0.3750 in.
Internal "h" Limit: 1.1700 in. Internal Weld Leg Size(Weld 43):
0.0000 in.OD, Limit of Reinforcement: 10.8780 in. Outside Groove
Weld Depth: 1.0000 in.
Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: Yes Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -135 F
Host Component: Shell 1 - Shell 1
Material: SA-516 Gr. 70 Shell wall thickness(new): 1.0000
in.Material Stress(Sv): 19700 PSI Shell wall thickness(corroded):
0.8750 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3750 in.
Nozzle Wall Thickness(tn): 0.7180 in.
Outside Groove Weld Depth: 1.0000 in.
Nozzle passes through the vessel, attached by a groove weld.Pipe
Size: 6 Schedule: 160
Nozzle is adequate for UG-45 requirements.Opening is adequately
reinforced for Internal Pressure.Opening is adequately reinforced
for External Pressure.
Weld Strength Paths are adequate.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 35 of
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Pressure Vessel Engineering, Ltd.N2
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
2 Mark Number: N2
ID Number: 2
Date Printed: 11/12/2009
Required Shell Thickness per Paragraph UG-37(a)
tr = PRo
SE + 0.4P =
250.00 * 43.0000
19700 * 1 + 0.4 * 250.00 = 0.5429 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph
UG-37(a)
trn = PRn
SE - 0.6P =
250.00 * 2.7195
17100 * 1 - 0.6 * 250.00 = 0.0401 i n .
Required Nozzle Thickness for External Pressure per Paragraph
UG-37(a)
trn = 3 * Do * Pa
4B =
3 * 6.6250 * 15.00
4 * 3548 = 0.0212 i n .
Strength Reduction Factors
fr1 = min Sn
Sv, 1.0000 = min
17100
19700, 1.0000 = 0.8680 fr2 = min
Sn
Sv, 1.0000 = min
17100
19700, 1.0000 = 0.8680
fr3 = min Sn
Sv, 1.0000 = min
17100
19700, 1.0000 = 0.8680
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion) per
Paragraph UG-45(a)
t = PRn
SE - 0.6P + Ca + ext. Ca =
250.00 * 2.7195
17100 * 1.00 - 0.6 * 250.00 + 0.1250 + 0.0000 = 0.1651 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) per
Paragraph UG-45(b)(1)
t = PRo
SE + 0.4P + Ca + ext. Ca =
250.00 * 43.0000
19700 * 1 + 0.4 * 250.00 + 0.1250 + 0.0000 = 0.6679 i n .
Nozzle Thickness for External Pressure (plus corrosion) per
Paragraph UG-45(b)(2)
t = PRo
SE + 0.4P + Ca + ext. Ca =
15.00 * 43.0000
19700 * 1 + 0.4 * 15.00 + 0.1250 + 0.0000
= Greater Of (0.0327(Calculated), 0.0938(Minimum Allowed)) +
0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = 0.2188 i n
.Minimum Thickness for Internal and External Pressure per Paragraph
UG-45(b)(3)
t = Greater of the thicknesses determined by UG-45(b)(1) or
UG-45(b)(2) = 0.6679 i n .
Minimum Thickness of Standard Wall Pipe (plus corrosion) per
Paragraph UG-45(b)(4)t = minimum thickness of standard wall pipe +
Ca + ext. Ca = 0.3700 i n .
Nozzle Minimum Thickness per Paragraph UG-45(b)t = Smallest of
UG-45(b)(3) or UG-45(b)(4) = 0.3700 i n .
Wall thickness = tn * 0.875(pipe) = 0.6282 is greater than or
equal to UG-45 value of 0.3700
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 36 of
95
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Pressure Vessel Engineering, Ltd.N2
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
2 Mark Number: N2
ID Number: 2
Date Printed: 11/12/2009
Nozzle Reinforcement Calculations
Area Required for Internal PressureA = d tr F + 2 tn tr F (1 -
fr1) = (5.4390 * 0.5429 * 1.00) + (2 * 0.5930 * 0.5429 * 1.00 * (1
- 0.8680)) = 3.0378 sq. in.
Area Available - Internal PressureA1 Formula 1 = d(E1 t - F tr)
- 2tn(E1 t - F tr)(1 - fr1) = 5.4390 * (1.00 * 0.8750 - 1.00 *
0.5429) - 2 * 0.5930 * (1.00 * 0.8750 - 1.00 * 0.5429) * (1 -
0.8680) = 1.7543 sq. in.A1 Formula 2 = 2(t + tn)(E1 t - F tr) -
2tn(E1 t - F tr)(1 - fr1) = 2 * (0.8750 + 0.5930)(1.00 * 0.8750 -
1.00 * 0.5429) - 2 * 0.5930 * (1.00 * 0.8750 - 1.00 * 0.5429) * (1
- 0.8680) = 0.9231 sq. in.A1 = Larger value of A1 Formula 1 a n d
A1 Formula 2 = 1.7543 sq. in.
A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.5930 - 0.0401) * 0.8680 *
0.8750 = 2.0997 sq. in.A2 Formula 2 = 5(tn - trn) fr2 tn = 5(0.5930
- 0.0401) * 0.8680 * 0.5930 = 1.4230 sq. in.A2 = Smaller value of
A2 Formula 1 a n d A2 Formula 2 = 1.4230 sq. in.
A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 *
0.8750 * 0.4680 * 0.8680 = 1.7773 sq. in.5 * ti * ti * fr2 = 5 *
0.4680 * 0.4680 * 0.8680 = 0.9506 sq. in.2 * h * ti * fr2 = 2 *
0.0000 * 0.4680 * 0.8680= 0.0000 sq. in.
= 0.0000 sq. in.
A41 = (leg) * fr2 = (0.3750) * 0.8680 = 0.1221 sq. in.
A43 = (leg) * fr2 = 0 * 0.8680 = 0.0000 sq. in.
Area Available (Internal Pressure) = A1 + A2 + A3 + A41 + A43 =
3.2994 sq. in., which is greater than A (3.0378)
Nozzle Reinforcement Calculations
Area Required for External Pressure
A = * (d tr F + 2 tn tr F (1 - fr1)) = * ((5.4390 * 0.4580 *
1.0) + (2 * 0.5930 * 0.4580 * 1.0 * (1 - 0.8680))) = 1.2814 sq.
in.Area Available - External Pressure
A1 Formula 1 = d(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) =
5.4390 * (1.00 * 0.8750 - 1.00 * 0.4580) - 2 * 0.5930 * (1.00 *
0.8750 - 1.00 * 0.4580) * (1 - 0.8680) = 2.2028 sq. in.A1 Formula 2
= 2(t + tn)(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 2 * (0.8750
+ 0.5930)(1.00 * 0.8750 - 1.00 * 0.4580) - 2 * 0.5930 * (1.00 *
0.8750 - 1.00 * 0.4580) * (1 - 0.8680) = 1.1590 sq. in.A1 = Larger
value of A1 Formula 1 a n d A1 Formula 2 = 2.2028 sq. in.
A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.5930 - 0.0212) * 0.8680 *
0.8750 = 2.1715 sq. in.A2 Formula 2 = 5(tn - trn) fr2 tn = 5(0.5930
- 0.0212) * 0.8680 * 0.5930 = 1.4716 sq. in.A2 = Smaller value of
A2 Formula 1 a n d A2 Formula 2 = 1.4716 sq. in.
A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 *
0.8750 * 0.4680 * 0.8680 = 1.7773 sq. in.5 * ti * ti * fr2 = 5 *
0.4680 * 0.4680 * 0.8680 = 0.9506 sq. in.2 * h * ti * fr2 = 2 *
0.0000 * 0.4680 * 0.8680= 0.0000 sq. in.
= 0.0000 sq. in.
A41 = (leg) * fr2 = (0.3750) * 0.8680 = 0.1221 sq. in.
A43 = (leg) * fr2 = 0 * 0.8680 = 0.0000 sq. in.
Area Available (External Pressure) = A1 + A2 + A3 + A41 + A43 =
3.7965 sq. in., which is greater than A (1.2814)
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 37 of
95
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Pressure Vessel Engineering, Ltd.N3
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 3 Mark Number: N3ID Number: 3
Date Printed: 11/12/2009
Nozzle Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 0.00 PSI Nozzle Efficiency (E): 100 %
Nozzle Material: SA-105 Joint Efficiency (E1): 1.00Factor B
Chart: CS-2
External Projection: 6.0000 in. Allowable Stress at Design
Temperature (Sn): 19000 PSIInternal Projection: 2.0000 in.
Allowable Stress at Ambient Temperature: 20000 PSI
Inside Corrosion Allowance: 0.1250 in. Correction Factor (F):
1.00External Corrosion Allowance: 0.0000 in. Nozzle Path: None
Nozzle ID (new): 2.0000 in. Nozzle Wall Thickness(new): 0.6600
in.Nozzle ID (corroded): 2.2500 in. Nozzle Wall
Thickness(corroded): 0.5350 in.
Outer "h" Limit: 1.3375 in. Upper Weld Leg Size(Weld 41): 0.3750
in.Internal "h" Limit: 1.0250 in. Internal Weld Leg Size(Weld 43):
0.5625 in.
OD, Limit of Reinforcement: 5.0700 in. Outside Groove Weld
Depth: 1.0000 in.
Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 250.00 PSIUCS-66(b)
reduction: Yes Minimum Design Metal Temperature: -20 FUCS-68(c)
reduction: No Computed Minimum Temperature: -133 F
Host Component: Shell 4 - Shell 4
Material: SA-516 Gr. 70 Shell wall thickness(new): 1.0000
in.Material Stress(Sv): 19700 PSI Shell wall thickness(corroded):
0.8750 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3750 in.
Internal Weld Leg Size(Weld 43): 0.5625 in.
Nozzle Wall Thickness(tn): 0.6600 in.
Outside Groove Weld Depth: 1.0000 in.
Nozzle passes through the vessel, attached by a groove
weld.Nozzle is adequate for UG-45 requirements.
Opening is adequately reinforced for Internal Pressure.Opening
is adequately reinforced for External Pressure.
Reinforcement calculations are not required per
UG-36(c)(3)(a)See Uw-14 for exceptions.Weld Strength Paths are
adequate.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 38 of
95
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Pressure Vessel Engineering, Ltd.N3
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
3 Mark Number: N3
ID Number: 3
Date Printed: 11/12/2009
Required Shell Thickness per Paragraph UG-37(a)
tr = PRo
SE + 0.4P =
250.00 * 43.0000
19700 * 1 + 0.4 * 250.00 = 0.5429 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph
UG-37(a)
trn = PRn
SE - 0.6P =
250.00 * 1.1250
19000 * 1 - 0.6 * 250.00 = 0.0149 i n .
Required Nozzle Thickness for External Pressure per Paragraph
UG-37(a)
trn = 3 * Do * Pa
4B =
3 * 3.3200 * 15.00
4 * 2717 = 0.0138 i n .
Strength Reduction Factors
fr1 = min Sn
Sv, 1.0000 = min
19000
19700, 1.0000 = 0.9645 fr2 = min
Sn
Sv, 1.0000 = min
19000
19700, 1.0000 = 0.9645
fr3 = min Sn
Sv, 1.0000 = min
19000
19700, 1.0000 = 0.9645
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion) per
Paragraph UG-45(a)
t = PRn
SE - 0.6P + Ca + ext. Ca =
250.00 * 1.1250
19000 * 1.00 - 0.6 * 250.00 + 0.1250 + 0.0000 = 0.1399 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) per
Paragraph UG-45(b)(1)
t = PRo
SE + 0.4P + Ca + ext. Ca =
250.00 * 43.0000
19700 * 1 + 0.4 * 250.00 + 0.1250 + 0.0000 = 0.6679 i n .
Nozzle Thickness for External Pressure (plus corrosion) per
Paragraph UG-45(b)(2)
t = PRo
SE + 0.4P + Ca + ext. Ca =
15.00 * 43.0000
19700 * 1 + 0.4 * 15.00 + 0.1250 + 0.0000
= Greater Of (0.0327(Calculated), 0.0938(Minimum Allowed)) +
0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = 0.2188 i n
.Minimum Thickness for Internal and External Pressure per Paragraph
UG-45(b)(3)
t = Greater of the thicknesses determined by UG-45(b)(1) or
UG-45(b)(2) = 0.6679 i n .
Minimum Thickness of Standard Wall Pipe (plus corrosion) per
Paragraph UG-45(b)(4)t = minimum thickness of standard wall pipe +
Ca + ext. Ca = 0.3140 i n .
Nozzle Minimum Thickness per Paragraph UG-45(b)t = Smallest of
UG-45(b)(3) or UG-45(b)(4) = 0.3140 i n .
Wall thickness = tn = 0.6600 is greater than or equal to UG-45
value of 0.3140
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 39 of
95
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Pressure Vessel Engineering, Ltd.N4
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 4 Mark Number: N4ID Number: 4
Date Printed: 11/12/2009
Nozzle Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 0.00 PSI Nozzle Efficiency (E): 100 %
Nozzle Material: SA-312 TP316L, High Joint Efficiency (E1):
1.00Factor B Chart: HA-4
External Projection: 6.0000 in. Allowable Stress at Design
Temperature (Sn): 14400 PSIInternal Projection: 2.0000 in.
Allowable Stress at Ambient Temperature: 16700 PSI
Inside Corrosion Allowance: 0.1250 in. Correction Factor (F):
1.00External Corrosion Allowance: 0.0000 in. Nozzle Path: None
Nozzle Pipe Size: 4 Nozzle Pipe Schedule: 120Nozzle ID (new):
3.6240 in. Nozzle Wall Thickness(new): 0.4380 in.
Nozzle ID (corroded): 3.8740 in. Nozzle Wall
Thickness(corroded): 0.3130 in.Developed Opening: 3.6240 in.
Tangential Dimension L: 4.0000 in.
Outer "h" Limit: 1.5325 in. Upper Weld Leg Size(Weld 41): 0.3750
in.Internal "h" Limit: 0.4700 in. Internal Weld Leg Size(Weld 43):
0.5000 in.
OD, Limit of Reinforcement: 7.7480 in. Outside Groove Weld
Depth: 1.1250 in.
Minimum Design Metal Temperature
Minimum Design Metal Temperature: -20 FMaterial is exempt from
impact testing per UHA-51(d)
Reinforcing Pad Information
Reinforcing Material: SA-516 Gr. 70 Allowable Stress at Design
Temperature(Sp): 19700 PSIAllowable Stress at Ambient Temperature:
20000 PSI
Reinforcing Plate Thickness(te): 0.7500 in. Repad to Vessel Weld
Leg Size(Weld 42): 0.6250 in.OD, Reinforcing Plate(Dp): 7.0000 in.
Repad to Nozzle Groove Weld Depth: 0.7500 in.
Host Component: Cone 2 - Conical Reducer 2
Material: SA-516 Gr. 70 Conical Reducer wall thickness(new):
1.1250 in.Material Stress(Sv): 19700 PSInical Reducer wall
thickness - thin out (corroded): 1.0000 in.
Distance from small end of cone: 50.0000 in. Diameter of Cone at
Nozzle: 79.7500 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3750 in.
Internal Weld Leg Size(Weld 43): 0.5000 in.
Nozzle Wall Thickness(tn): 0.4380 in.
Outside Groove Weld Depth: 1.1250 in.
Repad to Vessel Weld Leg Size(Weld 42): 0.6250 in.
Repad Thickness(te): 0.7500 in.
tangential to the vessel wall, attached by a groove weld.Pipe
Size: 4 Schedule: 120
Nozzle is adequate for UG-45 requirements.Opening is adequately
reinforced for Internal Pressure.Opening is adequately reinforced
for External Pressure.
Weld Strength Paths are adequate.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 40 of
95
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Pressure Vessel Engineering, Ltd.N4
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
4 Mark Number: N4
ID Number: 4
Date Printed: 11/12/2009
Required Conical Reducer Thickness per Paragraph UG-37(a)
tr = PDo
(2 * cos (SE + 0.4P)) =
250.00 * 79.7500
(2 * 0.9203 * (19700 * 1 + 0.4 * 250.00)) = 0.5471 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph
UG-37(a)
trn = PRn
SE - 0.6P =
250.00 * 1.9370
14400 * 1 - 0.6 * 250.00 = 0.0340 i n .
Required Nozzle Thickness for External Pressure per Paragraph
UG-37(a)
trn = 3 * Do * Pa
4B =
3 * 4.5000 * 15.00
4 * 3051 = 0.0167 i n .
Strength Reduction Factors
fr1 = min Sn
Sv, 1.0000 = min
14400
19700, 1.0000 = 0.7310 fr2 = min
Sn
Sv, 1.0000 = min
14400
19700, 1.0000 = 0.7310
fr3 = min Sn
Sv, 1.0000 = min
14400
19700, 1.0000 = 0.7310 fr4 = min
Sp
Sv, 1.0000 = min
19700
19700, 1.0000 = 1.0000
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion) per
Paragraph UG-45(a)
t = PRn
SE - 0.6P + Ca + ext. Ca =
250.00 * 1.9370
14400 * 1.00 - 0.6 * 250.00 + 0.1250 + 0.0000 = 0.1590 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) per
Paragraph UG-45(b)(1)
t = PDo
(2 * cos (SE + 0.4P)) + Ca + ext. Ca =
250.00 * 79.7500
(2 * 0.9203 * (19700 * 1 + 0.4 * 250.00)) + 0.1250 + 0.0000 =
0.6721 i n .
Nozzle Thickness for External Pressure (plus corrosion) per
Paragraph UG-45(b)(2)
t = PDo
(2 * cos (SE + 0.4P)) + Ca + ext. Ca =
15.00 * 79.7500
(2 * 0.9203 * (19700 * 1 + 0.4 * 15.00)) + 0.1250 + 0.0000
= Greater Of (0.0330(Calculated), 0.0938(Minimum Allowed)) +
0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = 0.2188 i n
.Minimum Thickness for Internal and External Pressure per Paragraph
UG-45(b)(3)
t = Greater of the thicknesses determined by UG-45(b)(1) or
UG-45(b)(2) = 0.6721 i n .
Minimum Thickness of Standard Wall Pipe (plus corrosion) per
Paragraph UG-45(b)(4)t = minimum thickness of standard wall pipe +
Ca + ext. Ca = 0.3324 i n .
Nozzle Minimum Thickness per Paragraph UG-45(b)t = Smallest of
UG-45(b)(3) or UG-45(b)(4) = 0.3324 i n .
Wall thickness = tn * 0.875(pipe) = 0.3832 is greater than or
equal to UG-45 value of 0.3324
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 41 of
95
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Pressure Vessel Engineering, Ltd.N4
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
4 Mark Number: N4
ID Number: 4
Date Printed: 11/12/2009
Nozzle Reinforcement Calculations
Area Required for Internal PressureA = d tr F + 2 tn tr F (1 -
fr1) = (3.8740 * 0.5471 * 1.00) + (2 * 0.3130 * 0.5471 * 1.00 * (1
- 0.7310)) = 2.2116 sq. in.
Area Available - Internal PressureA1 Formula 1 = d(E1 t - F tr)
- 2tn(E1 t - F tr)(1 - fr1) = 3.8740 * (1.00 * 1.0000 - 1.00 *
0.5471) - 2 * 0.3130 * (1.00 * 1.0000 - 1.00 * 0.5471) * (1 -
0.7310) = 1.6783 sq. in.A1 Formula 2 = 2(t + tn)(E1 t - F tr) -
2tn(E1 t - F tr)(1 - fr1) = 2 * (1.0000 + 0.3130)(1.00 * 1.0000 -
1.00 * 0.5471) - 2 * 0.3130 * (1.00 * 1.0000 - 1.00 * 0.5471) * (1
- 0.7310) = 1.1130 sq. in.A1 = Larger value of A1 Formula 1 a n d
A1 Formula 2 = 1.6783 sq. in.
A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.3130 - 0.0340) * 0.7310 *
1.0000 = 1.0197 sq. in.A2 Formula 2 = 2(tn - trn) fr2 (2.5 tn + te
) = 2(0.3130 - 0.0340) * 0.7310 * (2.5 * 0.3130 + 0.7500) = 0.6251
sq. in.A2 = Smaller value of A2 Formula 1 a n d A2 Formula 2 =
0.6251 sq. in.
A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 *
1.0000 * 0.1880 * 0.7310 = 0.6871 sq. in.5 * ti * ti * fr2 = 5 *
0.1880 * 0.1880 * 0.7310 = 0.1292 sq. in.2 * h * ti * fr2 = 2 *
1.8750 * 0.1880 * 0.7310= 0.5153 sq. in.
= 0.1292 sq. in.
A41 = (leg) * fr3 = (0.3750) * 0.7310 = 0.1028 sq. in.
A42 = Allowable Weld 42 area * fr4 = 0.3276 * 1.0000 = 0.3276
sq. in.
A43 = (leg) * fr2 = (0.3214) * 0.7310 = 0.0755 sq. in.
A5 = (Dp - d - 2tn) te fr4 = (7.0000 - 3.8740 - 2 * 0.3130) *
0.7500 * 1.0000 = 1.8750 sq. in.
Area Available (Internal Pressure) = A1 + A2 + A3 + A41 + A42 +
A43 + A5 = 4.8135 sq. in., which is greater than A (2.2116)
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 42 of
95
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Pressure Vessel Engineering, Ltd.N4
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
4 Mark Number: N4
ID Number: 4
Date Printed: 11/12/2009
Nozzle Reinforcement Calculations
Area Required for External Pressure
A = * (d tr F + 2 tn tr F (1 - fr1)) = * ((3.8740 * 0.3374 *
1.0) + (2 * 0.3130 * 0.3374 * 1.0 * (1 - 0.7310))) = 0.6820 sq.
in.Area Available - External Pressure
A1 Formula 1 = d(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) =
3.8740 * (1.00 * 1.0000 - 1.00 * 0.3374) - 2 * 0.3130 * (1.00 *
1.0000 - 1.00 * 0.3374) * (1 - 0.7310) = 2.4553 sq. in.A1 Formula 2
= 2(t + tn)(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 2 * (1.0000
+ 0.3130)(1.00 * 1.0000 - 1.00 * 0.3374) - 2 * 0.3130 * (1.00 *
1.0000 - 1.00 * 0.3374) * (1 - 0.7310) = 1.6284 sq. in.A1 = Larger
value of A1 Formula 1 a n d A1 Formula 2 = 2.4553 sq. in.
A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.3130 - 0.0167) * 0.7310 *
1.0000 = 1.0829 sq. in.A2 Formula 2 = 2(tn - trn) fr2 (2.5 tn + te
) = 2(0.3130 - 0.0167) * 0.7310 * (2.5 * 0.3130 + 0.7500) = 0.6638
sq. in.A2 = Smaller value of A2 Formula 1 a n d A2 Formula 2 =
0.6638 sq. in.
A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 *
1.0000 * 0.1880 * 0.7310 = 0.6871 sq. in.5 * ti * ti * fr2 = 5 *
0.1880 * 0.1880 * 0.7310 = 0.1292 sq. in.2 * h * ti * fr2 = 2 *
1.8750 * 0.1880 * 0.7310= 0.5153 sq. in.
= 0.1292 sq. in.
A41 = (leg) * fr3 = (0.3750) * 0.7310 = 0.1028 sq. in.
A42 = Allowable Weld 42 area * fr4 = 0.3276 * 1.0000 = 0.3276
sq. in.
A43 = (leg) * fr2 = (0.3214) * 0.7310 = 0.0755 sq. in.
A5 = (Dp - d - 2tn) te fr4 = (7.0000 - 3.8740 - 2 * 0.3130) *
0.7500 * 1.0000 = 1.8750 sq. in.
Area Available (External Pressure) = A1 + A2 + A3 + A41 + A42 +
A43 + A5 = 5.6292 sq. in., which is greater than A (0.6820)
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 43 of
95
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Pressure Vessel Engineering, Ltd.N4
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
4 Mark Number: N4
ID Number: 4
Date Printed: 11/12/2009
Nozzle Weld Strength Calculations
Attachment Weld Strength per Paragraph UW-16 (Corroded
Condition)
Weld 41 tmin = smaller of 0.75, te, or tn = smaller of 0.75,
0.7500, or 0.3130 = 0.3130 i n .
Weld 41 Leg min. = (smaller of 0.25 or (tmin * 0.7)) + ext.
CA
0.7 =
0.2191
0.7 = 0.3130 i n .
Weld 41, actual weld leg = 0.3750 i n .
Weld 42 tmin = smaller of 0.75, t, or te = smaller of 0.75,
1.0000, or 0.7500 = 0.7500 i n .
Weld 42 Leg min. = 0.5 * tmin + ext. CA
0.7 =
0.5 * 0.7500 + 0.0000
0.7 = 0.5357 i n .
Weld 42, actual weld leg = 0.6250 i n .
Weld 43 tmin = smaller of 0.75, t, or tn = smaller of 0.75,
1.0000, or 0.3130 = 0.3130 i n .
Weld 43 Leg min. = (smaller of 0.25 or (tmin * 0.7)) + ca
0.7 =
(smaller of 0.25 or (0.3130 * 0.7)) + 0.1250
0.7 =
0.3441
0.7 = 0.4916 i n .
Weld 43, actual weld leg = 0.5000 i n .
Unit Stresses per Paragraphs UG-45(c) and UW-15Nozzle wall in
shear = 0.70 * Sn = 0.70 * 14400 = 10080 P S IUpper fillet, Weld
41, in shear = 0.49 * Material Stress = 0.49 * 14400 = 7056 P S
IVessel groove weld, in tension = 0.74 * Material Stress = 0.74 *
14400 = 10656 P S IInner fillet, Weld 43, in shear = 0.49 *
Material Stress = 0.49 * 14400 = 7056 P S IOuter fillet, Weld 42,
in shear = 0.49 * Material Stress = 0.49 * 19700 = 9653 P S IRepad
groove weld, in tension = 0.74 * Material Stress = 0.74 * 14400 =
10656 P S I
Strength of Connection ElementsNozzle wall in shear = * * mean
nozzle diameter * tn * Nozzle wall in shear unit stress = * *
4.1870 * 0.3130 * 10080 = 20700 l b .Upper fillet in shear = * *
Nozzle OD * weld leg * upper fillet in shear unit stress = * *
4.5000 * 0.3750 * 7056 = 18700 l b .Groove Weld in Tension = * *
Nozzle OD * groove depth * groove weld tension unit stress = * *
4.5000 * 1.1250 * 10656 = 84700 l b .Inner fillet in shear = * *
Nozzle OD * weld leg * inner fillet in shear unit stress = * *
4.5000 * 0.3214 * 7056 = 16000 l b .Outer fillet in shear = * *
Plate OD * weld leg * outer fillet in shear unit stress = * *
7.0000 * 0.6250 * 9653 = 66300 l b .Repad groove weld = * * Nozzle
OD * Groove Depth * repad groove weld in tension unit stress = * *
4.5000 * 0.7500 * 10656 = 56500 l b .
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 44 of
95
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Pressure Vessel Engineering, Ltd.N4
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
4 Mark Number: N4
ID Number: 4
Date Printed: 11/12/2009
Load to be carried by welds, per UG-41(b)(1) and Fig. UG-41.1
sketch (a)W = [A - A1 + 2 tn fr1(E1t - Ftr)] Sv = [2.2116 - 1.6783
+ 2 * 0.3130 * 0.7310 * (1.00 * 1.0000 - 1.0000 * 0.5471)] * 19700
= 14600 l b .W1-1 = (A2 + A5 + A41 + A42) * Sv = (0.6251 + 1.8750 +
0.1028 + 0.3276) * 19700 = 57700 l b .W2-2 = (A2 + A3 + A41 + A43 +
2 tn t fr1) Sv = (0.6251 + 0.1292 + 0.1028 + 0.0755 + 2 * 0.3130 *
1.0000 * 0.7310) * 19700 = 27400 l b .W3-3 = (A2 + A3 + A5 + A41 +
A42 + A43 + 2 tn t fr1) * Sv = (0.6251 + 0.1292 + 1.8750 + 0.1028 +
0.3276 + 0.0755 + 2 * 0.3130 * 1.0000 * 0.7310) * 19700 = 70800 l b
.
Check Strength PathsPath 1-1 = Outer fillet in shear + Nozzle
wall in shear = 66300 + 20700 = 87000 l b .Path 2-2 = Upper fillet
in shear + Repad groove weld + Groove weld in tension + Inner
fillet in shear = 18700 + 56500 + 84700 + 16000 = 175900 l b .Path
3-3 = Outer fillet in shear + Inner fillet in shear + Groove weld
in tension = 66300 + 16000 + 84700 = 167000 l b .
Plate Strength = A5 * Sp = 1.8750 * 19700 = 36938 l b .
Outer fillet weld strength(66300) is greater than plate
strength(36938).
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 45 of
95
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Pressure Vessel Engineering, Ltd.M2
C u s t o m e r : Pressure Vessel Engineering LtdJob No:
PVE-3602 Sample 13 Vessel Number: Sample 13
N u m b e r : 5 Mark Number: M2ID Number: M2
Date Printed: 11/12/2009
Nozzle Design Information
Design Pressure: 250.00 PSI Design Temperature: 550 FStatic
Head: 0.00 PSI Nozzle Efficiency (E): 85 %
Nozzle Material: SA-240 Gr. 316L, High Joint Efficiency (E1):
1.00Factor B Chart: HA-4
External Projection: 12.0000 in. Allowable Stress at Design
Temperature (Sn): 14400 PSIInternal Projection: 0.0000 in.
Allowable Stress at Ambient Temperature: 16700 PSI
Inside Corrosion Allowance: 0.1250 in. Correction Factor (F):
1.00External Corrosion Allowance: 0.0000 in. Nozzle Path: None
Nozzle ID (new): 22.0000 in. Nozzle Wall Thickness(new): 1.0000
in.Nozzle ID (corroded): 22.2500 in. Nozzle Wall
Thickness(corroded): 0.8750 in.Developed Opening: 22.0000 in.
Tangential Dimension L: 22.0000 in.
Outer "h" Limit: 2.5000 in. Upper Weld Leg Size(Weld 41): 0.3750
in.Internal "h" Limit: 1.8750 in. Internal Weld Leg Size(Weld 43):
0.0000 in.
OD, Limit of Reinforcement: 44.5000 in. Outside Groove Weld
Depth: 1.1250 in.
Minimum Design Metal Temperature
Minimum Design Metal Temperature: -20 FMaterial is exempt from
impact testing per UHA-51(d)
Reinforcing Pad Information
Reinforcing Material: SA-516 Gr. 70 Allowable Stress at Design
Temperature(Sp): 19700 PSIAllowable Stress at Ambient Temperature:
20000 PSI
Reinforcing Plate Thickness(te): 1.1250 in. Repad to Vessel Weld
Leg Size(Weld 42): 0.5625 in.OD, Reinforcing Plate(Dp): 34.0000 in.
Repad to Nozzle Groove Weld Depth: 1.1250 in.
Host Component: Cone 2 - Conical Reducer 2
Material: SA-516 Gr. 70 Conical Reducer wall thickness(new):
1.1250 in.Material Stress(Sv): 19700 PSInical Reducer wall
thickness - thin out (corroded): 1.0000 in.
Distance from small end of cone: 50.0000 in. Diameter of Cone at
Nozzle: 79.7500 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3750 in.
Nozzle Wall Thickness(tn): 1.0000 in.
Outside Groove Weld Depth: 1.1250 in.
Repad to Vessel Weld Leg Size(Weld 42): 0.5625 in.
Repad Thickness(te): 1.1250 in.
tangential to the vessel wall, attached by a groove weld.Nozzle
is adequate for UG-45 requirements.
Opening is adequately reinforced for Internal Pressure.Opening
is adequately reinforced for External Pressure.
Weld Strength Paths are adequate.
Advanced Pressure Vessel version: 10.1.5 Computer Engineering,
Inc. Section VIII, Division 1, 2007 Edition, 2008 AddendaPage 46 of
95
-
Pressure Vessel Engineering, Ltd.M2
Job No: PVE-3602 Sample 13 Vessel Number: Sample 13N u m b e r :
5 Mark Number: M2
ID Number: M2
Date Printed: 11/12/2009
Required Conical Reducer Thickness per Paragraph UG-37(a)
tr = PDo
(2 * cos (SE + 0.4P)) =
250.00 * 79.7500
(2 * 0.9203 * (19700 * 1 + 0.4 * 250.00)) = 0.5471 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragrap