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TWI Oilfield Fabrication1560 River Road Fruita, Colorado 81521
Date Printed: 11/27/2012
CUSTOMERTAQA North LTD
1106 West 2nd Street Suite 2Williston, ND 58801
VESSEL LOCATIONTAQA North LTD
1106 West 2nd Street Suite 2Williston, ND 58801
VESSEL DESCRIPTION30"x96" 300 MAWP VT Sand Seperator
Vessel designed with DesignCalcs, Version: 2013.0Vessel is ASME Code Stamped
Wind Analysis performed in accordance with IBC 2006Seismic Analysis performed in accordance with IBC 2006
T.M. No: C W 1 5 0 1 1Vessel Number: C W 1 5 0 1 1 . 1
NAMEPLATE INFORMATIONVessel MAWP: 300.00 PSI at 100 °F
M D M T : -20 °F at 300.00 PSISerial Number(s): CW15011.1
National Board Number(s): __________________________________Year Built: 2012
R a d i o g r a p h y : NONEPostweld Heat Treated: NONE
Construction Type: W
Signatures
Authorized Inspector:_______________________________________________________________ Date: ____/____/____ Jim Radigan
Detailing Supervisor:_______________________________________________________________ Date: ____/____/____ Kelly Chamberlain
Quality Control Manager:_______________________________________________________________ Date: ____/____/____ Kelly Chamberlain
Fabrication Supervisor:_______________________________________________________________ Date: ____/____/____ Kelly Chamberlain
TWI Oilfield Fabrication1560 River Road Fruita, Colorado 81521
Date Printed: 11/27/2012
TWI Oilfield FabricationShell 1
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1 N u m b e r : 1 Mark Number: S1
Date Printed: 11/27/2012
Cylindrical Shell Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °FStatic Head: 0.00 PSI Long. Joint Efficiency: 70 %
Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material Stress (hot): 20000 PSI
Shell Length: 96.0000 in. Material Stress (cold): 20000 PSICompressive Stress: 16588 PSI
Corrosion Allowance: 0.0625 in. Actual Circumferential Stress: 14522 PSIExternal Corrosion Allowance: 0.0000 in. Actual Longitudinal Stress: 7047 PSI
Outside Diameter (new): 30.0000 in.Outside Diameter (corroded): 30.0000 in. Specific Gravity: 1.00
Shell Surface Area: 62.83 Sq. Ft. Weight of Fluid: 2293.47 lb.Shell Estimated Volume: 274.53 Gal. Total Flooded Shell Weight: 3539.05 lb.
Circ. Joint Efficiency: 70 % Shell Weight: 1245.58 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: B Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -50 °F
Design Thickness Calculations
Longitudinal Stress Calculations per Paragraph UG-27(c)(2)
t = PR
2SE + 0.4P =
300.00 * 14.5625
2 * 20000 * 0.70 + 0.4 * 300.00 = 0.1554 + 0.0625 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = minimum of 0.2179 i n .
Circumferential Stress Calculations per Appendix 1-1(a)(1)
t = PRo
SE + 0.4P=
300.00 * 15.0000
20000 * 0.70 + 0.4 * 300.00 = 0.3187 + 0.0625 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = minimum of 0.3812 i n .
Extreme Fiber Elongation Calculation per Paragraph UCS-79
Elongation = 50t
Rf=
50 * 0.5000
14.7500 = elongation of 1.69 %
External loads do not control design.
Nominal Shell Thickness Selected = 0.5000 i n .
DesignCalcs version: 2013.0 ©CEI 2013Page 1 of 48
TWI Oilfield FabricationHead 1
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1 N u m b e r : 1 Mark Number: H1
Date Printed: 11/27/2012
Ellipsoidal Head Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °FStatic Head: 0.00 PSI Joint Efficiency: 70 %
Head Material: SA-516 Gr. 70 Factor B Chart: CS-2Material Stress (hot): 20000 PSI
Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000 PSIExternal Corrosion Allowance: 0.0000 in. Actual Head Stress: 19984 PSI
Head Location: Left Straight Flange : 0.0000 in.Outside Diameter : 30.0000 in. Head Depth (ho) : 7.7500 in.
Thin Out : 0.0625 in.
K = 1
6 [2 + (D/2h)² ] : 0.99
Head Surface Area: 6.59 Sq. Ft. Specific Gravity: 1.00Head Estimated Volume: 13.82 Gal. Weight of Fluid: 115.28 lb.
Head Weight: 132.80 lb. Total Flooded Head Weight: 248.08 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: C Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -55 °F
Design Thickness Calculations
Design Thickness Calculations per Appendix 1-4(c)
t = PDoK
2SE + 2P(K - 0.1) =
300.00 * 30.0000 * 0.99
2 * 20000 * 0.70 + 2 * 300.00 * (0.99 - 0.1)
= 0.3123 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) + 0.0625(thin out) = minimum of 0.4998 i n .
Extreme Fiber Elongation Calculation per Paragraph UCS-79
elongation = 75t
Rf =
75 * 0.5000
5.0150 = elongation of 7.48 %
Nominal Head Thickness Selected = 0.5000 i n .Minimum Thickness after forming, ts (uncorroded) = 0.4375 i n .
DesignCalcs version: 2013.0 ©CEI 2013Page 2 of 48
TWI Oilfield FabricationHead 2
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1 N u m b e r : 2 Mark Number: H2
Date Printed: 11/27/2012
Ellipsoidal Head Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °FStatic Head: 0.00 PSI Joint Efficiency: 70 %
Head Material: SA-516 Gr. 70 Factor B Chart: CS-2Material Stress (hot): 20000 PSI
Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000 PSIExternal Corrosion Allowance: 0.0000 in. Actual Head Stress: 19984 PSI
Head Location: Right Straight Flange : 0.0000 in.Outside Diameter : 30.0000 in. Head Depth (ho) : 7.7500 in.
Thin Out : 0.0625 in.
K = 1
6 [2 + (D/2h)² ] : 0.99
Head Surface Area: 6.59 Sq. Ft. Specific Gravity: 1.00Head Estimated Volume: 13.82 Gal. Weight of Fluid: 115.28 lb.
Head Weight: 132.80 lb. Total Flooded Head Weight: 248.08 lb.
Minimum Design Metal Temperature Data
Min. Temperature Curve: C Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -55 °F
Design Thickness Calculations
Design Thickness Calculations per Appendix 1-4(c)
t = PDoK
2SE + 2P(K - 0.1) =
300.00 * 30.0000 * 0.99
2 * 20000 * 0.70 + 2 * 300.00 * (0.99 - 0.1)
= 0.3123 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) + 0.0625(thin out) = minimum of 0.4998 i n .
Extreme Fiber Elongation Calculation per Paragraph UCS-79
elongation = 75t
Rf =
75 * 0.5000
5.0150 = elongation of 7.48 %
Nominal Head Thickness Selected = 0.5000 i n .Minimum Thickness after forming, ts (uncorroded) = 0.4375 i n .
DesignCalcs version: 2013.0 ©CEI 2013Page 3 of 48
TWI Oilfield FabricationNozzle 1
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 1 Mark Number: N1
ID Number: 1
Date Printed: 11/27/2012
Nozzle Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °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: 5.0000 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: 3 Nozzle Pipe Schedule: 160Nozzle ID (new): 2.6240 in. Nozzle Wall Thickness(new): 0.4380 in.
Nozzle ID (corroded): 2.8740 in. Nozzle Wall Thickness(corroded): 0.3130 in.External Limit of Reinforcement: 0.7825 in. Upper Weld Leg Size(Weld 41): 0.3130 in.Internal Limit of Reinforcement: 0.4700 in. Internal Weld Leg Size(Weld 43): 0.0000 in.
Parallel Limit of Reinf (2Lpar): 5.7480 in. Outside Groove Weld Depth: 0.5000 in.Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -147 °F
Host Component: Shell 1 - Shell 1
Material: SA-516 Gr. 70 Shell wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Shell wall thickness(corroded): 0.4375 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3130 in.
Nozzle Wall Thickness(tn): 0.4380 in.
Outside Groove Weld Depth: 0.5000 in.
Nozzle passes through the vessel, attached by a groove weld.Pipe Size: 3 Schedule: 160
Nozzle is adequate for UG-45 requirements.Opening is adequately reinforced for Internal Pressure.
Reinforcement calculations are not required per UG-36(c)(3)(a)See Uw-14 for exceptions.Weld Strength Paths are adequate.
DesignCalcs version: 2013.0 ©CEI 2013Page 4 of 48
TWI Oilfield FabricationNozzle 1
T.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 1 Mark Number: N1
ID Number: 1
Date Printed: 11/27/2012
Required Shell Thickness per Paragraph UG-37(a)
tr = PRo
SE + 0.4P =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 = 0.2237 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)
trn = PRn
SE - 0.6P =
300.00 * 1.4370
17100 * 1 - 0.6 * 300.00 = 0.0255 i n .
Strength Reduction Factors
fr1 = min ¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550 fr2 = min
¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion)
ta = PRn
SE - 0.6P + Ca + ext. Ca =
300.00 * 1.4370
17100 * 1.00 - 0.6 * 300.00 + 0.1250 + 0.0000 = 0.1505 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) Based on Host
tb1 = PRo
SE + 0.4P + Ca + ext. Ca =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 + 0.1250 + 0.0000 = 0.3487 i n .
Minimum Thickness (plus corrosion) per Table UG-45tb3 = minimum thickness (Table UG-45) + Ca + ext. Ca = 0.3140 i n .
Nozzle Minimum Thickness Based on Host and Table UG-45tb = min[tb3, max(tb1, tb2)] = 0.3140 i n .
tUG-45 = max( ta, tb ) = 0.3140 i n .
Wall thickness = tn * 0.875(pipe) = 0.3832 is greater than or equal to UG-45 value of 0.3140
DesignCalcs version: 2013.0 ©CEI 2013Page 5 of 48
TWI Oilfield FabricationNozzle 2
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 2 Mark Number: N2
ID Number: 2
Date Printed: 11/27/2012
Nozzle Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °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: 5.0000 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: 3 Nozzle Pipe Schedule: 160Nozzle ID (new): 2.6240 in. Nozzle Wall Thickness(new): 0.4380 in.
Nozzle ID (corroded): 2.8740 in. Nozzle Wall Thickness(corroded): 0.3130 in.External Limit of Reinforcement: 0.7813 in. Upper Weld Leg Size(Weld 41): 0.3125 in.Internal Limit of Reinforcement: 0.4700 in. Internal Weld Leg Size(Weld 43): 0.0000 in.
Parallel Limit of Reinf (2Lpar): 5.7480 in. Outside Groove Weld Depth: 0.5000 in.Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -155 °F
Host Component: Head 2 - Head 2
Material: SA-516 Gr. 70 Head wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Head wall thickness - thin out (corroded): 0.3125 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3125 in.
Internal Weld Leg Size(Weld 43): 0.0000 in.
Nozzle Wall Thickness(tn): 0.4380 in.
Outside Groove Weld Depth: 0.5000 in.
Nozzle passes through the vessel, attached by a groove weld.Pipe Size: 3 Schedule: 160
Nozzle is adequate for UG-45 requirements.Opening is adequately reinforced for Internal Pressure.
Reinforcement calculations are not required per UG-36(c)(3)(a)See Uw-14 for exceptions.Weld Strength Paths are adequate.
DesignCalcs version: 2013.0 ©CEI 2013Page 6 of 48
TWI Oilfield FabricationNozzle 2
T.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 2 Mark Number: N2
ID Number: 2
Date Printed: 11/27/2012
Required Head Thickness per Paragraph UG-37(a)
tr = P K1 Do
(2SE + 0.8P) =
300.00 * 0.8900 * 30.0000
(2 * 20000 * 1 + 0.8 * 300.00) = 0.1991 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)
trn = PRn
SE - 0.6P =
300.00 * 1.4370
17100 * 1 - 0.6 * 300.00 = 0.0255 i n .
Strength Reduction Factors
fr1 = min ¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550 fr2 = min
¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion)
ta = PRn
SE - 0.6P + Ca + ext. Ca =
300.00 * 1.4370
17100 * 1.00 - 0.6 * 300.00 + 0.1250 + 0.0000 = 0.1505 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) Based on Host
tb1 = P K Do
(2SE + 2P(K - 0.1)) + Ca + ext. Ca =
300.00 * 0.9900 * 30.0000
(2 * 20000 * 1 + 2 * 300.00 * (0.9900 - 0.1)) + 0.1250 + 0.0000 = 0.3448 i n .
Minimum Thickness (plus corrosion) per Table UG-45tb3 = minimum thickness (Table UG-45) + Ca + ext. Ca = 0.3140 i n .
Nozzle Minimum Thickness Based on Host and Table UG-45tb = min[tb3, max(tb1, tb2)] = 0.3140 i n .
tUG-45 = max( ta, tb ) = 0.3140 i n .
Wall thickness = tn * 0.875(pipe) = 0.3832 is greater than or equal to UG-45 value of 0.3140
DesignCalcs version: 2013.0 ©CEI 2013Page 7 of 48
TWI Oilfield FabricationNozzle 3
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 3 Mark Number: N3
ID Number: 3
Date Printed: 11/27/2012
Nozzle Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °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): 20000 PSIInternal Projection: 0.0000 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): 8.0000 in. Nozzle Wall Thickness(new): 0.8800 in.Nozzle ID (corroded): 8.2500 in. Nozzle Wall Thickness(corroded): 0.7550 in.
External Limit of Reinforcement: 1.0938 in. Upper Weld Leg Size(Weld 41): 0.3125 in.Internal Limit of Reinforcement: 1.0938 in. Internal Weld Leg Size(Weld 43): 0.0000 in.
Parallel Limit of Reinf (2Lpar): 16.5000 in. Outside Groove Weld Depth: 0.5000 in.Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -117 °F
Host Component: Shell 1 - Shell 1
Material: SA-516 Gr. 70 Shell wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Shell wall thickness(corroded): 0.4375 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3125 in.
Internal Weld Leg Size(Weld 43): 0.0000 in.
Nozzle Wall Thickness(tn): 0.8800 in.
Outside Groove Weld Depth: 0.5000 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.Weld Strength Paths are adequate.
DesignCalcs version: 2013.0 ©CEI 2013Page 8 of 48
TWI Oilfield FabricationNozzle 3
T.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 3 Mark Number: N3
ID Number: 3
Date Printed: 11/27/2012
Required Shell Thickness per Paragraph UG-37(a)
tr = PRo
SE + 0.4P =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 = 0.2237 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)
trn = PRn
SE - 0.6P =
300.00 * 4.1250
20000 * 1 - 0.6 * 300.00 = 0.0624 i n .
Strength Reduction Factors
fr1 = min ¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
20000
20000, 1.0000
§¨ = 1.0000 fr2 = min
¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
20000
20000, 1.0000
§¨ = 1.0000
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion)
ta = PRn
SE - 0.6P + Ca + ext. Ca =
300.00 * 4.1250
20000 * 1.00 - 0.6 * 300.00 + 0.1250 + 0.0000 = 0.1874 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) Based on Host
tb1 = PRo
SE + 0.4P + Ca + ext. Ca =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 + 0.1250 + 0.0000 = 0.3487 i n .
Minimum Thickness (plus corrosion) per Table UG-45tb3 = minimum thickness (Table UG-45) + Ca + ext. Ca = 0.4440 i n .
Nozzle Minimum Thickness Based on Host and Table UG-45tb = min[tb3, max(tb1, tb2)] = 0.3487 i n .
tUG-45 = max( ta, tb ) = 0.3487 i n .
Wall thickness = tn = 0.8800 is greater than or equal to UG-45 value of 0.3487
DesignCalcs version: 2013.0 ©CEI 2013Page 9 of 48
TWI Oilfield FabricationNozzle 3
T.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 3 Mark Number: N3
ID Number: 3
Date Printed: 11/27/2012
Limits of Reinforcement (UG-40)
Lpar = max(d, Rn + t + tn) = max(8.2500, 4.0000 + 0.4375 + 0.7550) = 8.2500 i n .Lnoro = min(2.5 t, 2.5 tn + te) = min(2.5 * 0.4375, 2.5 * 0.7550 + 0.0000) = 1.0938 i n .Lnori = min(2.5 t, 2.5 ti) = min(2.5 * 0.4375, 2.5 * 0.6300) = 1.0938 i n .
Nozzle Reinforcement Calculations (Internal Pressure)
A = max{C [d tr F + 2 tn tr F (1 - fr1)], 0} = max{1.0000 * [8.2500 * 0.2237 * 1.00 + 2 * 0.7550 * 0.2237 * 1.00 * (1 - 1.0000)], 0} = 1.8455 sq. in.
A1 = max[(2 Lpar - d) (E1 t - F tr) - 2 tn ( E1 t - F tr) (1 - fr1), 0] =max[(2 * 8.2500 - 8.2500) * (1.0000 * 0.4375 - 1.00 * 0.2237) - 2 * 0.7550 * (1.0000 * 0.4375 - 1.00 * 0.2237) * (1 - 1.0000), 0]
= 1.7639 sq. in.
A2 = max{2 min(ho, Lnoro) [min(tn, Lpar - 0.5 d) - trn] fr2, 0} = max{2 * min(6.0000, 1.0938) * [min(0.7550, 8.2500 - 0.5 * 8.2500) - 0.0624] * 1.0000, 0} = 1.5151 sq. in.
A3 = max{2 min(h, Lnori) min(ti, Lpar - 0.5 d) fr2, 0} = max{2 * min(0.0000, 1.0938) * min(0.6300, 8.2500 - 0.5 * 8.2500) * 1.0000, 0} = 0.0000 sq. in.
A41 = fr2 [ L412 - (L41 - L41pareff)2 - (L41 - L41noreff)2] =
1.0000 * [0.31252 - (0.3125 - 0.3125)2 - (0.3125 - 0.3125)2] = 0.0977 sq. in.
A42 = fr4 L42pareff L42noreff = 0.0000 * 0.0000 * 0.0000 = 0.0000 sq. in.
A43 = fr2 L43pareff L43noreff = 1.0000 * 0.0000 * 0.0000 = 0.0000 sq. in.
A5 = 0.0000 sq. in.
Area Available (Internal Pressure) = A1 + A2 + A3 + A41 + A42 + A43 + A5 = 3.3766 sq. in., which is >= A (1.8455)
DesignCalcs version: 2013.0 ©CEI 2013Page 10 of 48
TWI Oilfield FabricationNozzle 4
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 4 Mark Number: N4
ID Number: 4
Date Printed: 11/27/2012
Nozzle Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °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: 8.0000 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: 3 Nozzle Pipe Schedule: 160Nozzle ID (new): 2.6240 in. Nozzle Wall Thickness(new): 0.4380 in.
Nozzle ID (corroded): 2.8740 in. Nozzle Wall Thickness(corroded): 0.3130 in.Developed Opening: 3.0355 in. Tangential Dimension L: 7.3059 in.
External Limit of Reinforcement: 0.7825 in. Upper Weld Leg Size(Weld 41): 0.3125 in.Internal Limit of Reinforcement: 0.4700 in. Internal Weld Leg Size(Weld 43): 0.0000 in.
Parallel Limit of Reinf (2Lpar): 6.6420 in. Outside Groove Weld Depth: 0.5000 in.Minimum Design Metal Temperature
Min. Temp. Curve: B Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -147 °F
Host Component: Shell 1 - Shell 1
Material: SA-516 Gr. 70 Shell wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Shell wall thickness(corroded): 0.4375 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3125 in.
Internal Weld Leg Size(Weld 43): 0.0000 in.
Nozzle Wall Thickness(tn): 0.4380 in.
Outside Groove Weld Depth: 0.5000 in.
tangential to the vessel wall, attached by a groove weld.Pipe Size: 3 Schedule: 160
Nozzle is adequate for UG-45 requirements.Opening is adequately reinforced for Internal Pressure.
Reinforcement calculations are not required per UG-36(c)(3)(a)See Uw-14 for exceptions.Weld Strength Paths are adequate.
DesignCalcs version: 2013.0 ©CEI 2013Page 11 of 48
TWI Oilfield FabricationNozzle 4
T.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 4 Mark Number: N4
ID Number: 4
Date Printed: 11/27/2012
Required Shell Thickness per Paragraph UG-37(a)
tr = PRo
SE + 0.4P =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 = 0.2237 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)
trn = PRn
SE - 0.6P =
300.00 * 1.4370
17100 * 1 - 0.6 * 300.00 = 0.0255 i n .
Strength Reduction Factors
fr1 = min ¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550 fr2 = min
¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion)
ta = PRn
SE - 0.6P + Ca + ext. Ca =
300.00 * 1.4370
17100 * 1.00 - 0.6 * 300.00 + 0.1250 + 0.0000 = 0.1505 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) Based on Host
tb1 = PRo
SE + 0.4P + Ca + ext. Ca =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 + 0.1250 + 0.0000 = 0.3487 i n .
Minimum Thickness (plus corrosion) per Table UG-45tb3 = minimum thickness (Table UG-45) + Ca + ext. Ca = 0.3140 i n .
Nozzle Minimum Thickness Based on Host and Table UG-45tb = min[tb3, max(tb1, tb2)] = 0.3140 i n .
tUG-45 = max( ta, tb ) = 0.3140 i n .
Wall thickness = tn * 0.875(pipe) = 0.3832 is greater than or equal to UG-45 value of 0.3140
DesignCalcs version: 2013.0 ©CEI 2013Page 12 of 48
TWI Oilfield FabricationNozzle 5
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 5 Mark Number: N5
ID Number: 5
Date Printed: 11/27/2012
Nozzle Design Information
Design Pressure: 300.00 PSI Design Temperature: 100 °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: 5.0000 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: 3 Nozzle Pipe Schedule: 160Nozzle ID (new): 2.6240 in. Nozzle Wall Thickness(new): 0.4380 in.
Nozzle ID (corroded): 2.8740 in. Nozzle Wall Thickness(corroded): 0.3130 in.External Limit of Reinforcement: 0.7825 in. Upper Weld Leg Size(Weld 41): 0.3130 in.Internal Limit of Reinforcement: 0.4700 in. Internal Weld Leg Size(Weld 43): 0.0000 in.
Parallel Limit of Reinf (2Lpar): 5.7480 in. Outside Groove Weld Depth: 0.5000 in.Minimum Design Metal Temperature
Min. Temp. Curve: Pressure at MDMT: 300.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -155 °F
Host Component: Shell 1 - Shell 1
Material: SA-516 Gr. 70 Shell wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Shell wall thickness(corroded): 0.4375 in.
Nozzle Detail Information
Upper Weld Leg Size(Weld 41): 0.3130 in.
Nozzle Wall Thickness(tn): 0.4380 in.
Outside Groove Weld Depth: 0.5000 in.
Nozzle passes through the vessel, attached by a groove weld.Pipe Size: 3 Schedule: 160
Nozzle is adequate for UG-45 requirements.Opening is adequately reinforced for Internal Pressure.
Reinforcement calculations are not required per UG-36(c)(3)(a)See Uw-14 for exceptions.Weld Strength Paths are adequate.
DesignCalcs version: 2013.0 ©CEI 2013Page 13 of 48
TWI Oilfield FabricationNozzle 5
T.M. No: CW15011 Vessel Number: CW15011.1N u m b e r : 5 Mark Number: N5
ID Number: 5
Date Printed: 11/27/2012
Required Shell Thickness per Paragraph UG-37(a)
tr = PRo
SE + 0.4P =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 = 0.2237 i n .
Nozzle Required Thickness Calculations
Required Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)
trn = PRn
SE - 0.6P =
300.00 * 1.4370
17100 * 1 - 0.6 * 300.00 = 0.0255 i n .
Strength Reduction Factors
fr1 = min ¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550 fr2 = min
¥¦
Sn
Sv, 1.0000
§¨ = min
¥¦
17100
20000, 1.0000
§¨ = 0.8550
UG-45 Thickness Calculations
Nozzle Thickness for Pressure Loading (plus corrosion)
ta = PRn
SE - 0.6P + Ca + ext. Ca =
300.00 * 1.4370
17100 * 1.00 - 0.6 * 300.00 + 0.1250 + 0.0000 = 0.1505 i n .
Nozzle Thickness for Internal Pressure (plus corrosion) Based on Host
tb1 = PRo
SE + 0.4P + Ca + ext. Ca =
300.00 * 15.0000
20000 * 1 + 0.4 * 300.00 + 0.1250 + 0.0000 = 0.3487 i n .
Minimum Thickness (plus corrosion) per Table UG-45tb3 = minimum thickness (Table UG-45) + Ca + ext. Ca = 0.3140 i n .
Nozzle Minimum Thickness Based on Host and Table UG-45tb = min[tb3, max(tb1, tb2)] = 0.3140 i n .
tUG-45 = max( ta, tb ) = 0.3140 i n .
Wall thickness = tn * 0.875(pipe) = 0.3832 is greater than or equal to UG-45 value of 0.3140
DesignCalcs version: 2013.0 ©CEI 2013Page 14 of 48
TWI Oilfield FabricationLifting Lug 1
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1
Mark Number: LL1
Date Printed: 11/27/2012
Lifting Lug Information
M a t e r i a l : SA-36 Design Temperature: 0 °FC o n d i t i o n : Material Stress (Hot): 16600 PSI
T y p e : Type 1 Material Stress (Cold): 16600 PSILength (L): 10.0000 in. Yield Strength: 36000 PSIT h i c k n e s s : 1.0000 in. R a d i u s : 2.0000 in.
Weld Joint Efficiency: 45 % Weld Leg: 10.0000 in.Shackle Hole Diameter: 1.1250 in. Shackle Hole Centerline Height: 2.0000 in.
Vessel Information
M a t e r i a l : SA-516 Gr. 70 Design Temperature: 100 °FC o n d i t i o n : Material Stress (Hot): 20000 PSI
R a d i u s : 15.0000 in. Material Stress (Cold): 20000 PSIT h i c k n e s s : 0.5000 in. Yield Strength: 38000 PSI
Vertical Lift Angle: 45 ° Impact Factor: 1.50W e i g h t : 1667.79 lb.
Design Calculations
Wi = W * I = 1667.79 * 1.50 = 2502Vertical Lift Force, Fv = Wi = 2502 = 2502 l b .Horizontal Lift Force, Fh = Wi * tan(n) = 2502 * tan(45) = 2502 l b .
Total Lift Force, Ft = Fv² + Fh² = 2502² + 2502² = 3538 l b .
Lug Stress Calculation
Sl = Ft
T * (2 * r' - d) =
3538
1.0000 * ( 2 * 2.0000 - 1.1250) = 1231 P S I
Shear Stress Ratio, Srl = Sl
0.4 * Sly =
1231
0.4 * 36000 = 0.0855
DesignCalcs version: 2013.0 ©CEI 2013Page 15 of 48
TWI Oilfield FabricationLifting Lug 1
T.M. No: CW15011 Vessel Number: CW15011.1Mark Number: LL1
Date Printed: 11/27/2012
Lug Weld CalculationsLwl = 2 * (L + T) = 2 * (10.0000 + 1.0000) = 22.0000 i n .
Zwl = (T * L) + L²
3 = (1.0000 * 10.0000) +
10.0000²
3 = 43.3333 sq. in.
f1 = Ml
Zwl =
6411
43.3333 = 147.9 l b . / i n .
f2 = Fh
Lwl =
2502
22.0000 = 113.7 l b . / i n .
f3 = Fv
Lwl =
2502
22.0000 = 113.7 l b . / i n .
f = ((f1 + f3)² + f2²) = ((147.9 + 113.7)² + 113.7²) = 285.2 l b . / i n .fw = E * min(Sla, Sva) = 0.45 * min(16600, 20000) = 7470 P S I
WLa = f
fw =
285.2
7470 = 0.0382 i n .
Lug Weld Leg Ratio, WLRl = WLa
WL =
0.0382
10.0000 = 0.0038
DesignCalcs version: 2013.0 ©CEI 2013Page 16 of 48
TWI Oilfield FabricationSaddle 1
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1 N u m b e r : 1 Mark Number: SDL1
Date Printed: 11/27/2012
Saddle Design Information
Design Temperature: 100 °F Support Type: Type IMaterial: SA-36 Stiffener Quantity: 2
Condition: Material Stress (hot): 16600 PSILength (d): 26.8468 in. Material Stress (cold): 16600 PSI
Top Width (b'): 10.0000 in. Yield Strength: 36000 PSIBottom Width (bb'): 1.0000 in. Density: 0.2800 lb/in.^3
Outside Stiffener Thickness (tso): 0.5000 in. Web Plate Thickness (tw): 0.5000 in.Inside Stiffener Thickness (tsi): 0.2500 in. Vessel Centerline Height (h): 20.5000 in.
Saddle Angle of contact (n): 120.0 ° Elevation above grade (g): 0.0000 in.Dist. from saddle centerline to tang. line (A): 19.2000 in.
Support Design Condition: Shell unstiffened (A/R > 1/2)
Wear Plate Information
Design Temperature: 100 °FMaterial: SA-36 Material Stress (hot): 16600 PSI
Condition: Material Stress (cold): 16600 PSIExtension (jw): 2.0000 in. Use for S2: Yes
Width (bw): 15.0000 in. Use for S3: YesThickness (twp): 0.5000 in. Use for S5: Yes
Base Plate Information
Design Temperature: 100 °F Ultimate 28 Day Concrete Strength: 3000.00 PSIMaterial: SA-36 Yield Strength: 36000 PSI
Condition: Length (m): 29.0000 in.Width (bb): 1.0000 in. Thickness (tb): 0.3750 in.
Anchor Bolt Information
Material: SA-36 Material Stress (hot): 16600 PSICondition: Material Stress (cold): 16600 PSI
Size: 1" Number of Threads per in. : 8.0000Quantity: 2 Root Area: 0.5510 sq. in.
DesignCalcs version: 2013.0 ©CEI 2013Page 17 of 48
TWI Oilfield Fabrication30"x96" 300 MAWP VT Sand Seperator
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
ASME Flange Design Information
Host Description Type Size M a t e r i a l ASME Material MAP(in.) Class Group (PSI)
Nozzle 1 ASME Flange 1 Slip On 3 S A - 1 0 5 300 1.1 740.00Nozzle 2 ASME Flange 2 Slip On 3 S A - 1 0 5 300 1.1 740.00Nozzle 3 ASME Flange 3 Slip On 8 S A - 1 0 5 300 1.1 740.00Nozzle 4 ASME Flange 4 Slip On 3 S A - 1 0 5 300 1.1 740.00Nozzle 5 ASME Flange 5 Slip On 3 S A - 1 0 5 300 1.1 740.00
DesignCalcs version: 2013.0 ©CEI 2013Page 18 of 48
TWI Oilfield FabricationC u s t o m e r : TAQA North LTD
T.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Loading SummaryType Starting Point Ending Point Depth Density Wind Diameter
(in.) (in.) (in.) (lb./Ft^3) (in.)Liquid - - 12.0000 40.0000 -Liquid - - 30.0000 62.4000 -
DesignCalcs version: 2013.0 ©CEI 2013Page 19 of 48
TWI Oilfield FabricationC u s t o m e r : TAQA North LTD
T.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Zick Analysis
IBC 2006 Wind Design Information
Basic Wind Speed (V): 100 MPH
IBC 2006 Seismic Design Information
Spectral Resp. Accel at short periods (Ss): 0.000 Spectral Resp. Accel. at a period of 1 s (S1): 0.000Response Modification Factor (R): 2.000
Occupancy Category: IV Site Class: DSeismic Design Category: A
Operating Pressurized Condition - Sustained Loads
Saddle Support Loads
QL = FLh
L - 2A =
0 * 20.5000
96.0000 - 2 * 19.2000 = 0 l b .
QT = 1.5 FT h
d =
1.5 * 0 * 20.5000
26.8468 = 0 l b .
QW = W
2 =
4032
2 = 2016 l b .
QN = QW = 2016 = 2016 l b .
Saddle Load for Vessel Stress Analysis
Q = QN = 2016 = 2016 l b .
Saddle Load for Support Stress Analysis
QS = QN = 2016 = 2016 l b .
DesignCalcs version: 2013.0 ©CEI 2013Page 20 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Zick Calculations
Longitudinal Stress Due to Internal Pressure
Sp = P R
2 t =
300.00 * 14.7813
2 * 0.4375= 5068 P S I
Longitudinal Compressive Stress Due to External Pressure
Spe = -Pe R
2 t =
-0.00 * 14.7813
2 * 0.4375= 0 P S I
Longitudinal Bending Stress in the Shell at the MidpointZ1 = m R² t = 3.1416 * 14.7813² * 0.4375 = 300 i n . ³
S1 = K1 Q L
4 Z1 =
0.13386 * 2016 * 96.0000
4 * 300= 22 P S I
Longitudinal Bending Stress in the Shell in the Plane of the Saddle
S1' = K1' Q L
4 Z1 =
1.79288 * 2016 * 96.0000
4 * 300= 289 P S I
Saddle Plane Tangential Shear Stress
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S2 = ¡¢
K2 Q
R te
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
1.17074 * 2016
14.7813 * 0.9375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 92 P S I
S2w = ¡¢
K2w Q
R t
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
0.99596 * 2016
14.7813 * 0.4375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 168 P S I
Circumferential Stress at the Horn of the Saddlete² = t² + twp² = 0.4375² + 0.5000² = 0.4414 sq. in.
S3 = - ¡¢
Q
4 te (b + 1.56 R t)
£¤
- ¡¢
12 K3 Q R
L te²
£¤
= - ¡¢
2016
4 * 0.9375 * (10.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.05285 * 2016 * 14.7813
96.0000 * 0.4414
£¤
= -484 P S I
Circumferential Stress at End of the Wear Plate
S3w = - ¡¢
Q
4 t (bw + 1.56 R t)
£¤
- ¡¢
12 K3w Q R
L t²
£¤
= - ¡¢
2016
4 * 0.4375 * (15.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.04345 * 2016 * 14.7813
96.0000 * 0.4375²
£¤
= -906 P S I
DesignCalcs version: 2013.0 ©CEI 2013Page 21 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Ring Compression in the Shell Over the Saddle
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S5 = K5 Q
te (b + 1.56 R t) =
0.76027 * 2016
0.9375 * (0.5000 + 1.56 * 14.7813 * 0.4375)= 366 P S I
Maximum Splitting Force
Fs = K8Qs = 0.20352 * 2016 = 410 l b .
Saddle Calculations
Base Plate Stress
SBP = 0.75 Qs bb
m tb² =
0.75 * 2016 * 1.0000
29.0000 * 0.3750²= 371 P S I
Concrete Bearing Stress
SC = Qs
bb m =
2016
1.0000 * 29.0000= 70 P S I
Saddle Splitting Force
ST Splitting = FS
ASaddle =
410
2.6875= 153 P S I
M Splitting = FS ¡¢
h - C2 - RW ¥¦
sin(n/2)
n/2
§¨£¤
= 410 * ¡¢
20.5000 - 4.4820 - 15.5000 * ¥¦
sin(1.0472)
1.0472
§¨£¤
= 1312 i n . - l b .
SB Splitting = M C1
I =
1312 * 0.5180
23.0695= 29 P S I
Bolting Shear Stress
Sb = FBolt
Nb Ab =
0
2 * 0.5510= 0 P S I
Saddle Support Stiffener Stresses
Location Length Compressive Stress Bending Stress Allowable Stress Stress Ratio in. PSI PSI PSI RST
Outside 12.3750 146 0 21600 0.0068
DesignCalcs version: 2013.0 ©CEI 2013Page 22 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Vessel Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
R1t = S1 + Sp
SShell E =
22 + 5068
20000 * 0.70= 0.3636
R1C = -S1
- Min(SShell, BShell) =
-22
-Min(20000,16588)= 0.0013
R1t' = S1' + Sp
SShell E =
289 + 5068
20000 * 0.70= 0.3826
R1C' = -S1'
- Min(SShell, BShell) =
-289
-Min(20000,16588)= 0.0174
R2 = S2
0.8 SShell =
92
0.8 * 20000= 0.0058
R2W = S2W
0.8 SShell =
168
0.8 * 20000= 0.0105
R3 = S3
- ( 1.25 SShell) =
-484
- (1.25 * 20000)= 0.0194
R3w = S3W
- ( 1.25 SShell) =
-906
- (1.25 * 20000)= 0.0362
R5 = S5
0.5 YShell =
366
0.5 * 38000= 0.0193
DesignCalcs version: 2013.0 ©CEI 2013Page 23 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Saddle Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
RBase Plate = SBP
0.6 YBase Plate =
371
0.6 * 36000= 0.0172
RConcrete = SC
0.25 SConcrete =
70
0.25 * 3000= 0.0933
RWeb = ST Splitting
0.6 YSaddle +
SB Splitting
0.66 YSaddle =
153
0.6 * 36000 +
29
0.66 * 36000= 0.0083
RST = Sstc + Sstb
0.6 YSaddle =
146 + 0
0.6 * 36000= 0.0068
RBolt = SB
0.8 SBa =
0
0.8 * 16600= 0.0000
DesignCalcs version: 2013.0 ©CEI 2013Page 24 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Operating Unpressurized Condition - Sustained Loads
Saddle Support Loads
QL = FLh
L - 2A =
0 * 20.5000
96.0000 - 2 * 19.2000 = 0 l b .
QT = 1.5 FT h
d =
1.5 * 0 * 20.5000
26.8468 = 0 l b .
QW = W
2 =
4032
2 = 2016 l b .
QN = QW = 2016 = 2016 l b .
Saddle Load for Vessel Stress Analysis
Q = QN = 2016 = 2016 l b .
Saddle Load for Support Stress Analysis
QS = QN = 2016 = 2016 l b .
DesignCalcs version: 2013.0 ©CEI 2013Page 25 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Zick Calculations
Longitudinal Stress Due to Internal Pressure
Sp = P R
2 t =
0.00 * 14.7813
2 * 0.4375= 0 P S I
Longitudinal Compressive Stress Due to External Pressure
Spe = = 0 P S I
Longitudinal Bending Stress in the Shell at the MidpointZ1 = m R² t = 3.1416 * 14.7813² * 0.4375 = 300 i n . ³
S1 = K1 Q L
4 Z1 =
0.13386 * 2016 * 96.0000
4 * 300= 22 P S I
Longitudinal Bending Stress in the Shell in the Plane of the Saddle
S1' = K1' Q L
4 Z1 =
1.79288 * 2016 * 96.0000
4 * 300= 289 P S I
Saddle Plane Tangential Shear Stress
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S2 = ¡¢
K2 Q
R te
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
1.17074 * 2016
14.7813 * 0.9375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 92 P S I
S2w = ¡¢
K2w Q
R t
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
0.99596 * 2016
14.7813 * 0.4375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 168 P S I
Circumferential Stress at the Horn of the Saddlete² = t² + twp² = 0.4375² + 0.5000² = 0.4414 sq. in.
S3 = - ¡¢
Q
4 te (b + 1.56 R t)
£¤
- ¡¢
12 K3 Q R
L te²
£¤
= - ¡¢
2016
4 * 0.9375 * (10.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.05285 * 2016 * 14.7813
96.0000 * 0.4414
£¤
= -484 P S I
Circumferential Stress at End of the Wear Plate
S3w = - ¡¢
Q
4 t (bw + 1.56 R t)
£¤
- ¡¢
12 K3w Q R
L t²
£¤
= - ¡¢
2016
4 * 0.4375 * (15.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.04345 * 2016 * 14.7813
96.0000 * 0.4375²
£¤
= -906 P S I
DesignCalcs version: 2013.0 ©CEI 2013Page 26 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Ring Compression in the Shell Over the Saddle
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S5 = K5 Q
te (b + 1.56 R t) =
0.76027 * 2016
0.9375 * (0.5000 + 1.56 * 14.7813 * 0.4375)= 366 P S I
Maximum Splitting Force
Fs = K8Qs = 0.20352 * 2016 = 410 l b .
Saddle Calculations
Base Plate Stress
SBP = 0.75 Qs bb
m tb² =
0.75 * 2016 * 1.0000
29.0000 * 0.3750²= 371 P S I
Concrete Bearing Stress
SC = Qs
bb m =
2016
1.0000 * 29.0000= 70 P S I
Saddle Splitting Force
ST Splitting = FS
ASaddle =
410
2.6875= 153 P S I
M Splitting = FS ¡¢
h - C2 - RW ¥¦
sin(n/2)
n/2
§¨£¤
= 410 * ¡¢
20.5000 - 4.4820 - 15.5000 * ¥¦
sin(1.0472)
1.0472
§¨£¤
= 1312 i n . - l b .
SB Splitting = M C1
I =
1312 * 0.5180
23.0695= 29 P S I
Bolting Shear Stress
Sb = FBolt
Nb Ab =
0
2 * 0.5510= 0 P S I
Saddle Support Stiffener Stresses
Location Length Compressive Stress Bending Stress Allowable Stress Stress Ratio in. PSI PSI PSI RST
Outside 12.3750 146 0 21600 0.0068
DesignCalcs version: 2013.0 ©CEI 2013Page 27 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Vessel Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
R1t = S1 + Sp
SShell E =
22 + 0
20000 * 0.70= 0.0016
R1C = -S1
- Min(SShell, BShell) =
-22
-Min(20000,16588)= 0.0013
R1t' = S1' + Sp
SShell E =
289 + 0
20000 * 0.70= 0.0206
R1C' = -S1'
- Min(SShell, BShell) =
-289
-Min(20000,16588)= 0.0174
R2 = S2
0.8 SShell =
92
0.8 * 20000= 0.0058
R2W = S2W
0.8 SShell =
168
0.8 * 20000= 0.0105
R3 = S3
- ( 1.25 SShell) =
-484
- (1.25 * 20000)= 0.0194
R3w = S3W
- ( 1.25 SShell) =
-906
- (1.25 * 20000)= 0.0362
R5 = S5
0.5 YShell =
366
0.5 * 38000= 0.0193
DesignCalcs version: 2013.0 ©CEI 2013Page 28 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Saddle Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
RBase Plate = SBP
0.6 YBase Plate =
371
0.6 * 36000= 0.0172
RConcrete = SC
0.25 SConcrete =
70
0.25 * 3000= 0.0933
RWeb = ST Splitting
0.6 YSaddle +
SB Splitting
0.66 YSaddle =
153
0.6 * 36000 +
29
0.66 * 36000= 0.0083
RST = Sstc + Sstb
0.6 YSaddle =
146 + 0
0.6 * 36000= 0.0068
RBolt = SB
0.8 SBa =
0
0.8 * 16600= 0.0000
DesignCalcs version: 2013.0 ©CEI 2013Page 29 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Empty Pressurized Condition - Sustained Loads
Saddle Support Loads
QL = FLh
L - 2A =
0 * 20.5000
96.0000 - 2 * 19.2000 = 0 l b .
QT = 1.5 FT h
d =
1.5 * 0 * 20.5000
26.8468 = 0 l b .
QW = W
2 =
1512
2 = 756 l b .
QN = QW = 756 = 756 l b .
Saddle Load for Vessel Stress Analysis
Q = QN = 756 = 756 l b .
Saddle Load for Support Stress Analysis
QS = QN = 756 = 756 l b .
DesignCalcs version: 2013.0 ©CEI 2013Page 30 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Zick Calculations
Longitudinal Stress Due to Internal Pressure
Sp = P R
2 t =
300.00 * 14.7813
2 * 0.4375= 5068 P S I
Longitudinal Compressive Stress Due to External Pressure
Spe = -Pe R
2 t =
-0.00 * 14.7813
2 * 0.4375= 0 P S I
Longitudinal Bending Stress in the Shell at the MidpointZ1 = m R² t = 3.1416 * 14.7813² * 0.4375 = 300 i n . ³
S1 = K1 Q L
4 Z1 =
0.13386 * 756 * 96.0000
4 * 300= 8 P S I
Longitudinal Bending Stress in the Shell in the Plane of the Saddle
S1' = K1' Q L
4 Z1 =
1.79288 * 756 * 96.0000
4 * 300= 108 P S I
Saddle Plane Tangential Shear Stress
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S2 = ¡¢
K2 Q
R te
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
1.17074 * 756
14.7813 * 0.9375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 35 P S I
S2w = ¡¢
K2w Q
R t
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
0.99596 * 756
14.7813 * 0.4375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 63 P S I
Circumferential Stress at the Horn of the Saddlete² = t² + twp² = 0.4375² + 0.5000² = 0.4414 sq. in.
S3 = - ¡¢
Q
4 te (b + 1.56 R t)
£¤
- ¡¢
12 K3 Q R
L te²
£¤
= - ¡¢
756
4 * 0.9375 * (10.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.05285 * 756 * 14.7813
96.0000 * 0.4414
£¤
= -182 P S I
Circumferential Stress at End of the Wear Plate
S3w = - ¡¢
Q
4 t (bw + 1.56 R t)
£¤
- ¡¢
12 K3w Q R
L t²
£¤
= - ¡¢
756
4 * 0.4375 * (15.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.04345 * 756 * 14.7813
96.0000 * 0.4375²
£¤
= -340 P S I
DesignCalcs version: 2013.0 ©CEI 2013Page 31 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Ring Compression in the Shell Over the Saddle
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S5 = K5 Q
te (b + 1.56 R t) =
0.76027 * 756
0.9375 * (0.5000 + 1.56 * 14.7813 * 0.4375)= 137 P S I
Maximum Splitting Force
Fs = K8Qs = 0.20352 * 756 = 154 l b .
Saddle Calculations
Base Plate Stress
SBP = 0.75 Qs bb
m tb² =
0.75 * 756 * 1.0000
29.0000 * 0.3750²= 139 P S I
Concrete Bearing Stress
SC = Qs
bb m =
756
1.0000 * 29.0000= 26 P S I
Saddle Splitting Force
ST Splitting = FS
ASaddle =
154
2.6875= 57 P S I
M Splitting = FS ¡¢
h - C2 - RW ¥¦
sin(n/2)
n/2
§¨£¤
= 154 * ¡¢
20.5000 - 4.4820 - 15.5000 * ¥¦
sin(1.0472)
1.0472
§¨£¤
= 493 i n . - l b .
SB Splitting = M C1
I =
493 * 0.5180
23.0695= 11 P S I
Bolting Shear Stress
Sb = FBolt
Nb Ab =
0
2 * 0.5510= 0 P S I
Saddle Support Stiffener Stresses
Location Length Compressive Stress Bending Stress Allowable Stress Stress Ratio in. PSI PSI PSI RST
Outside 12.3750 54 0 21600 0.0025
DesignCalcs version: 2013.0 ©CEI 2013Page 32 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Vessel Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
R1t = S1 + Sp
SShell E =
8 + 5068
20000 * 0.70= 0.3626
R1C = -S1
- Min(SShell, BShell) =
-8
-Min(20000,16588)= 0.0005
R1t' = S1' + Sp
SShell E =
108 + 5068
20000 * 0.70= 0.3697
R1C' = -S1'
- Min(SShell, BShell) =
-108
-Min(20000,16588)= 0.0065
R2 = S2
0.8 SShell =
35
0.8 * 20000= 0.0022
R2W = S2W
0.8 SShell =
63
0.8 * 20000= 0.0039
R3 = S3
- ( 1.25 SShell) =
-182
- (1.25 * 20000)= 0.0073
R3w = S3W
- ( 1.25 SShell) =
-340
- (1.25 * 20000)= 0.0136
R5 = S5
0.5 YShell =
137
0.5 * 38000= 0.0072
DesignCalcs version: 2013.0 ©CEI 2013Page 33 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Saddle Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
RBase Plate = SBP
0.6 YBase Plate =
139
0.6 * 36000= 0.0064
RConcrete = SC
0.25 SConcrete =
26
0.25 * 3000= 0.0347
RWeb = ST Splitting
0.6 YSaddle +
SB Splitting
0.66 YSaddle =
57
0.6 * 36000 +
11
0.66 * 36000= 0.0031
RST = Sstc + Sstb
0.6 YSaddle =
54 + 0
0.6 * 36000= 0.0025
RBolt = SB
0.8 SBa =
0
0.8 * 16600= 0.0000
DesignCalcs version: 2013.0 ©CEI 2013Page 34 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Empty Unpressurized Condition - Sustained Loads
Saddle Support Loads
QL = FLh
L - 2A =
0 * 20.5000
96.0000 - 2 * 19.2000 = 0 l b .
QT = 1.5 FT h
d =
1.5 * 0 * 20.5000
26.8468 = 0 l b .
QW = W
2 =
1512
2 = 756 l b .
QN = QW = 756 = 756 l b .
Saddle Load for Vessel Stress Analysis
Q = QN = 756 = 756 l b .
Saddle Load for Support Stress Analysis
QS = QN = 756 = 756 l b .
DesignCalcs version: 2013.0 ©CEI 2013Page 35 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Zick Calculations
Longitudinal Stress Due to Internal Pressure
Sp = = 0 P S I
Longitudinal Compressive Stress Due to External Pressure
Spe = = 0 P S I
Longitudinal Bending Stress in the Shell at the MidpointZ1 = m R² t = 3.1416 * 14.7813² * 0.4375 = 300 i n . ³
S1 = K1 Q L
4 Z1 =
0.13386 * 756 * 96.0000
4 * 300= 8 P S I
Longitudinal Bending Stress in the Shell in the Plane of the Saddle
S1' = K1' Q L
4 Z1 =
1.79288 * 756 * 96.0000
4 * 300= 108 P S I
Saddle Plane Tangential Shear Stress
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S2 = ¡¢
K2 Q
R te
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
1.17074 * 756
14.7813 * 0.9375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 35 P S I
S2w = ¡¢
K2w Q
R t
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
0.99596 * 756
14.7813 * 0.4375
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 63 P S I
Circumferential Stress at the Horn of the Saddlete² = t² + twp² = 0.4375² + 0.5000² = 0.4414 sq. in.
S3 = - ¡¢
Q
4 te (b + 1.56 R t)
£¤
- ¡¢
12 K3 Q R
L te²
£¤
= - ¡¢
756
4 * 0.9375 * (10.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.05285 * 756 * 14.7813
96.0000 * 0.4414
£¤
= -182 P S I
Circumferential Stress at End of the Wear Plate
S3w = - ¡¢
Q
4 t (bw + 1.56 R t)
£¤
- ¡¢
12 K3w Q R
L t²
£¤
= - ¡¢
756
4 * 0.4375 * (15.0000 + 1.56 * 14.7813 * 0.4375)
£¤
- ¡¢
12 * 0.04345 * 756 * 14.7813
96.0000 * 0.4375²
£¤
= -340 P S I
DesignCalcs version: 2013.0 ©CEI 2013Page 36 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Ring Compression in the Shell Over the Saddle
te = t + twp = 0.4375 + 0.5000 = 0.9375 i n .
S5 = K5 Q
te (b + 1.56 R t) =
0.76027 * 756
0.9375 * (0.5000 + 1.56 * 14.7813 * 0.4375)= 137 P S I
Maximum Splitting Force
Fs = K8Qs = 0.20352 * 756 = 154 l b .
Saddle Calculations
Base Plate Stress
SBP = 0.75 Qs bb
m tb² =
0.75 * 756 * 1.0000
29.0000 * 0.3750²= 139 P S I
Concrete Bearing Stress
SC = Qs
bb m =
756
1.0000 * 29.0000= 26 P S I
Saddle Splitting Force
ST Splitting = FS
ASaddle =
154
2.6875= 57 P S I
M Splitting = FS ¡¢
h - C2 - RW ¥¦
sin(n/2)
n/2
§¨£¤
= 154 * ¡¢
20.5000 - 4.4820 - 15.5000 * ¥¦
sin(1.0472)
1.0472
§¨£¤
= 493 i n . - l b .
SB Splitting = M C1
I =
493 * 0.5180
23.0695= 11 P S I
Bolting Shear Stress
Sb = FBolt
Nb Ab =
0
2 * 0.5510= 0 P S I
Saddle Support Stiffener Stresses
Location Length Compressive Stress Bending Stress Allowable Stress Stress Ratio in. PSI PSI PSI RST
Outside 12.3750 54 0 21600 0.0025
DesignCalcs version: 2013.0 ©CEI 2013Page 37 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Vessel Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
R1t = S1 + Sp
SShell E =
8 + 0
20000 * 0.70= 0.0006
R1C = -S1
- Min(SShell, BShell) =
-8
-Min(20000,16588)= 0.0005
R1t' = S1' + Sp
SShell E =
108 + 0
20000 * 0.70= 0.0077
R1C' = -S1'
- Min(SShell, BShell) =
-108
-Min(20000,16588)= 0.0065
R2 = S2
0.8 SShell =
35
0.8 * 20000= 0.0022
R2W = S2W
0.8 SShell =
63
0.8 * 20000= 0.0039
R3 = S3
- ( 1.25 SShell) =
-182
- (1.25 * 20000)= 0.0073
R3w = S3W
- ( 1.25 SShell) =
-340
- (1.25 * 20000)= 0.0136
R5 = S5
0.5 YShell =
137
0.5 * 38000= 0.0072
DesignCalcs version: 2013.0 ©CEI 2013Page 38 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Saddle Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
RBase Plate = SBP
0.6 YBase Plate =
139
0.6 * 36000= 0.0064
RConcrete = SC
0.25 SConcrete =
26
0.25 * 3000= 0.0347
RWeb = ST Splitting
0.6 YSaddle +
SB Splitting
0.66 YSaddle =
57
0.6 * 36000 +
11
0.66 * 36000= 0.0031
RST = Sstc + Sstb
0.6 YSaddle =
54 + 0
0.6 * 36000= 0.0025
RBolt = SB
0.8 SBa =
0
0.8 * 16600= 0.0000
DesignCalcs version: 2013.0 ©CEI 2013Page 39 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Test Condition
Saddle Support Loads
QL = FLh
L - 2A =
0 * 20.5000
96.0000 - 2 * 19.2000 = 0 l b .
QT = 1.5 FT h
d =
1.5 * 0 * 20.5000
26.8468 = 0 l b .
QW = W
2 =
4032
2 = 2016 l b .
QN = QW = 2016 = 2016 l b .
Saddle Load for Vessel Stress Analysis
Q = QN = 2016 = 2016 l b .
Saddle Load for Support Stress Analysis
QS = QN = 2016 = 2016 l b .
DesignCalcs version: 2013.0 ©CEI 2013Page 40 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Zick Calculations
Longitudinal Stress Due to Internal Pressure
Sp = P R
2 t =
300.00 * 14.7500
2 * 0.5000= 4425 P S I
Longitudinal Compressive Stress Due to External Pressure
Spe = = 0 P S I
Longitudinal Bending Stress in the Shell at the MidpointZ1 = m R² t = 3.1416 * 14.7500² * 0.5000 = 342 i n . ³
S1 = K1 Q L
4 Z1 =
0.13368 * 2016 * 96.0000
4 * 342= 19 P S I
Longitudinal Bending Stress in the Shell in the Plane of the Saddle
S1' = K1' Q L
4 Z1 =
1.79458 * 2016 * 96.0000
4 * 342= 254 P S I
Saddle Plane Tangential Shear Stress
te = t + twp = 0.5000 + 0.5000 = 1.0000 i n .
S2 = ¡¢
K2 Q
R te
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
1.17074 * 2016
14.7500 * 1.0000
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 87 P S I
S2w = ¡¢
K2w Q
R t
£¤
¡¢
L - 2 A
L + 4
3 H
£¤
= ¡¢
0.99596 * 2016
14.7500 * 0.5000
£¤
¡¢
96.0000 - 2 * 19.2000
96.0000 + 4
3 * 7.7500
£¤
= 147 P S I
Circumferential Stress at the Horn of the Saddlete² = t² + twp² = 0.5000² + 0.5000² = 0.5000 sq. in.
S3 = - ¡¢
Q
4 te (b + 1.56 R t)
£¤
- ¡¢
12 K3 Q R
L te²
£¤
= - ¡¢
2016
4 * 1.0000 * (10.0000 + 1.56 * 14.7500 * 0.5000)
£¤
- ¡¢
12 * 0.05285 * 2016 * 14.7500
96.0000 * 0.5000
£¤
= -428 P S I
Circumferential Stress at End of the Wear Plate
S3w = - ¡¢
Q
4 t (bw + 1.56 R t)
£¤
- ¡¢
12 K3w Q R
L t²
£¤
= - ¡¢
2016
4 * 0.5000 * (15.0000 + 1.56 * 14.7500 * 0.5000)
£¤
- ¡¢
12 * 0.04345 * 2016 * 14.7500
96.0000 * 0.5000²
£¤
= -698 P S I
DesignCalcs version: 2013.0 ©CEI 2013Page 41 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Ring Compression in the Shell Over the Saddle
te = t + twp = 0.5000 + 0.5000 = 1.0000 i n .
S5 = K5 Q
te (b + 1.56 R t) =
0.76027 * 2016
1.0000 * (0.5000 + 1.56 * 14.7500 * 0.5000)= 324 P S I
Maximum Splitting Force
Fs = K8Qs = 0.20352 * 2016 = 410 l b .
Saddle Calculations
Base Plate Stress
SBP = 0.75 Qs bb
m tb² =
0.75 * 2016 * 1.0000
29.0000 * 0.3750²= 371 P S I
Concrete Bearing Stress
SC = Qs
bb m =
2016
1.0000 * 29.0000= 70 P S I
Saddle Splitting Force
ST Splitting = FS
ASaddle =
410
2.6875= 153 P S I
M Splitting = FS ¡¢
h - C2 - RW ¥¦
sin(n/2)
n/2
§¨£¤
= 410 * ¡¢
20.5000 - 4.4820 - 15.5000 * ¥¦
sin(1.0472)
1.0472
§¨£¤
= 1312 i n . - l b .
SB Splitting = M C1
I =
1312 * 0.5180
23.0695= 29 P S I
Bolting Shear Stress
Sb = FBolt
Nb Ab =
0
2 * 0.5510= 0 P S I
Saddle Support Stiffener Stresses
Location Length Compressive Stress Bending Stress Allowable Stress Stress Ratio in. PSI PSI PSI RST
Outside 12.3750 146 0 21600 0.0068
DesignCalcs version: 2013.0 ©CEI 2013Page 42 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Vessel Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
R1t = S1 + Sp
SShell E =
19 + 4425
20000 * 0.70= 0.3174
R1C = -S1
- Min(SShell, BShell) =
-19
-Min(20000,16588)= 0.0011
R1t' = S1' + Sp
SShell E =
254 + 4425
20000 * 0.70= 0.3342
R1C' = -S1'
- Min(SShell, BShell) =
-254
-Min(20000,16588)= 0.0153
R2 = S2
0.8 SShell =
87
0.8 * 20000= 0.0054
R2W = S2W
0.8 SShell =
147
0.8 * 20000= 0.0092
R3 = S3
- ( 1.25 SShell) =
-428
- (1.25 * 20000)= 0.0171
R3w = S3W
- ( 1.25 SShell) =
-698
- (1.25 * 20000)= 0.0279
R5 = S5
0.5 YShell =
324
0.5 * 38000= 0.0171
DesignCalcs version: 2013.0 ©CEI 2013Page 43 of 48
TWI Oilfield FabricationT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Saddle Stress Ratio Calculations
Any ratio greater than 1 represents an overstressed condition
RBase Plate = SBP
0.6 YBase Plate =
371
0.6 * 36000= 0.0172
RConcrete = SC
0.25 SConcrete =
70
0.25 * 3000= 0.0933
RWeb = ST Splitting
0.6 YSaddle +
SB Splitting
0.66 YSaddle =
153
0.6 * 36000 +
29
0.66 * 36000= 0.0083
RST = Sstc + Sstb
0.6 YSaddle =
146 + 0
0.6 * 36000= 0.0068
RBolt = SB
0.8 SBa =
0
0.8 * 16600= 0.0000
DesignCalcs version: 2013.0 ©CEI 2013Page 44 of 48
TWI Oilfield FabricationC u s t o m e r : TAQA North LTD
T.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
MDMT Report by ComponentsDesign MDMT is -20 °F
Component Material Curve Pressure MDMT
Shell 1 SA-516 Gr. 70 B 300.00 PSI -50 °F Nozzle 3 SA-105 B 300.00 PSI -117 °F Nozzle 1 SA-106 Gr. B B 300.00 PSI -147 °F Nozzle 5 SA-106 Gr. B 300.00 PSI -155 °F Nozzle 4 SA-106 Gr. B B 300.00 PSI -147 °FHead 1 SA-516 Gr. 70 C 300.00 PSI -55 °FHead 2 SA-516 Gr. 70 C 300.00 PSI -55 °F Nozzle 2 SA-106 Gr. B B 300.00 PSI -155 °F
Component with highest MDMT: Shell 1.
Computed MDMT = -50 °F
The required design MDMT of -20 °F has been met or exceeded for the calculated MDMT values.
ASME Flanges Are Not Included in MDMT Calculations.
DesignCalcs version: 2013.0 ©CEI 2013Page 45 of 48
TWI Oilfield Fabrication30"x96" 300 MAWP VT Sand Seperator
C u s t o m e r : TAQA North LTDT.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
MAWP Report by Components
Vessel Component VesselMAWP MAWP MAWP
Design Static New & Cold Hot & Corroded Hot & Corroded Component Pressure Head UG-98(a) UG-98(b) UG-98(a)Shell 1 300.00 PSI 0.00 PSI 472.97 PSI 378.66 PSI 378.66 PSI Nozzle 1 300.00 PSI 0.00 PSI 532.61 PSI 391.77 PSI 391.77 PSI ASME Flange Class: 300 Gr:1.1 300.00 PSI 0.00 PSI 740.00 PSI 740.00 PSI 740.00 PSI Nozzle 3 300.00 PSI 0.00 PSI 508.38 PSI 421.03 PSI 421.03 PSI ASME Flange Class: 300 Gr:1.1 300.00 PSI 0.00 PSI 740.00 PSI 740.00 PSI 740.00 PSI Nozzle 4 300.00 PSI 0.00 PSI 506.61 PSI 378.66 PSI 378.66 PSI ASME Flange Class: 300 Gr:1.1 300.00 PSI 0.00 PSI 740.00 PSI 740.00 PSI 740.00 PSI Nozzle 5 300.00 PSI 0.00 PSI 532.61 PSI 391.77 PSI 391.77 PSI ASME Flange Class: 300 Gr:1.1 300.00 PSI 0.00 PSI 740.00 PSI 740.00 PSI 740.00 PSIHead 1 300.00 PSI 0.00 PSI 419.34 PSI 300.24 PSI 300.24 PSIHead 2 300.00 PSI 0.00 PSI 419.34 PSI 300.24 PSI 300.24 PSI Nozzle 2 300.00 PSI 0.00 PSI 546.57 PSI 397.78 PSI 397.78 PSI ASME Flange Class: 300 Gr:1.1 300.00 PSI 0.00 PSI 740.00 PSI 740.00 PSI 740.00 PSI
NC = Not Calculated Inc = Incomplete
Summary
Component with the lowest vessel MAWP(New & Cold) : Head 1The lowest vessel MAWP(New & Cold) : 419.34 P S I
Component with the lowest vessel MAWP(Hot & Corroded) : Head 1The lowest vessel MAWP(Hot & Corroded) : 300.24 P S I
Pressures are exclusive of any external loads.
Flange pressures listed here do not consider external loadings
DesignCalcs version: 2013.0 ©CEI 2013Page 46 of 48
TWI Oilfield FabricationC u s t o m e r : TAQA North LTD
T.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Summary Information
Dry Weight Flooded WeightShell 1245.58 lb. 3539.05 lb.Head 265.60 lb. 496.15 lb.Nozzle 156.61 lb. 156.61 lb.ASME Flange 110.00 lb. 110.00 lb.
_________________ _________________T o t a l s 1777.79 lb. 4301.80 lb.
Volume Shell 274.53 Gal.Head 27.64 Gal.Nozzle 2.67 Gal.
_________________T o t a l s 304.85 Gal.
Area Shell 62.83 Sq. Ft.Head 13.17 Sq. Ft.Nozzle 4.32 Sq. Ft.
_________________T o t a l s 80.33 Sq. Ft.
DesignCalcs version: 2013.0 ©CEI 2013Page 47 of 48
TWI Oilfield FabricationC u s t o m e r : TAQA North LTD
T.M. No: CW15011 Vessel Number: CW15011.1
Date Printed: 11/27/2012
Hydrostatic Test Information Par. UG-99(b)Gauge at Top
Component Const. x STest / SDesign x Pressure = Component Hydro Test Pressure
Head 1 1.3 x 20000 / 20000 x 300.00 = 390.00Head 2 1.3 x 20000 / 20000 x 300.00 = 390.00Nozzle 1 1.3 x 17100 / 17100 x 300.00 = 390.00Nozzle 2 1.3 x 17100 / 17100 x 300.00 = 390.00Nozzle 3 1.3 x 20000 / 20000 x 300.00 = 390.00Nozzle 4 1.3 x 17100 / 17100 x 300.00 = 390.00Nozzle 5 1.3 x 17100 / 17100 x 300.00 = 390.00Shell 1 1.3 x 20000 / 20000 x 300.00 = 390.00
Calculated Test Pressure: 390.00 PSI
Special Notes:
This calculation assumes one chamber.
This calculation is limited by the lowest component pressure per chamber.
DesignCalcs version: 2013.0 ©CEI 2013Page 48 of 48
Table of Contents
Shell 1 1
Head 1 2
Head 2 3
Nozzle 1 4
Nozzle 2 6
Nozzle 3 8
Nozzle 4 11
Nozzle 5 13
LiftLug Information 15
Saddle Information 17
ASME Flanges 18
Attachment/Loading Information 19
Zick Information - Saddle: Saddle 1 20
MDMT Summary 45
MAWP Summary 46
Summary Information 47
Hydrostatic Test Information Par. UG-99(b) 48
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