Sample3_PVElite.pdf

PVE Sample Vessel 3 Horizontal Retention Tank DESIGN CALCULATION In Accordance with ASME Section VIII Division 1 ASME Code Version : 2007 Analysis Performed by : PRESSURE VESSEL ENGINEERING Date of Analysis : Oct 27,2008 PV Elite 2008, May 2008

1 REVISED 10/22/2008 ART0 RELEASE 5/23/2002 LB

REV DESCRIPTION DATE INITIALS

Table of Contents

Cover Sheet ..............................................................................................................................................1 Input Echo.................................................................................................................................................3 XY Coordinate Calculations ..........................................................................................................8 Internal Pressure Calculations.................................................................................................9 External Pressure Calculations...............................................................................................12 Element and Detail Weights ........................................................................................................14 Nozzle Flange MAWP ...........................................................................................................................16 Center of Gravity Calculation .................................................................................................17 Horizontal Vessel Analysis (Ope.) .......................................................................................18 Horizontal Vessel Analysis (Test) .......................................................................................25 Nozzle Calcs. A - 3/4 in. 3000# ............................................................................................32 Nozzle Calcs. B - 6 in. Pipe ...................................................................................................34 Nozzle Calcs. C - 6 in. Pipe ...................................................................................................39 Nozzle Calcs. D - 12x16 MWY......................................................................................................44 Nozzle Calcs. E - 12x16 MWY......................................................................................................47 Nozzle Calcs. F - 12x16 MWY......................................................................................................50 Nozzle Calcs. G - 1.5 in. 3000# ............................................................................................53 Nozzle Schedule...................................................................................................................................55 Nozzle Summary .....................................................................................................................................56 Vessel Design Summary ....................................................................................................................57

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Input Echo Step: 1 10:53a Oct 27,2008

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PV Elite Vessel Analysis Program: Input Data PVE Sample Vessel 3 Horizontal Retention Tank Design Internal Pressure (for Hydrotest) 75.000 psig Design Internal Temperature 150 F Type of Hydrotest UG99-b Hydrotest Position Horizontal Projection of Nozzle from Vessel Top 0.0000 in Projection of Nozzle from Vessel Bottom 0.0000 in Minimum Design Metal Temperature -20 F Type of Construction Welded Special Service None Degree of Radiography None Miscellaneous Weight Percent 15. Use Higher Longitudinal Stresses (Flag) Y Select t for Internal Pressure (Flag) N Select t for External Pressure (Flag) N Select t for Axial Stress (Flag) N Select Location for Stiff. Rings (Flag) N Use Hydrotest Allowable Unmodified Y Consider Vortex Shedding N Perform a Corroded Hydrotest N Is this a Heat Exchanger No User Defined Hydro. Press. (Used if > 0) 98.000 psig User defined MAWP 0.0000 psig User defined MAPnc 0.0000 psig Load Case 1 NP+EW+WI+FW+BW Load Case 2 NP+EW+EE+FS+BS Load Case 3 NP+OW+WI+FW+BW Load Case 4 NP+OW+EQ+FS+BS Load Case 5 NP+HW+HI Load Case 6 NP+HW+HE Load Case 7 IP+OW+WI+FW+BW Load Case 8 IP+OW+EQ+FS+BS Load Case 9 EP+OW+WI+FW+BW Load Case 10 EP+OW+EQ+FS+BS Load Case 11 HP+HW+HI Load Case 12 HP+HW+HE Load Case 13 IP+WE+EW Load Case 14 IP+WF+CW Load Case 15 IP+VO+OW Load Case 16 IP+VE+EW Load Case 17 NP+VO+OW Load Case 18 FS+BS+IP+OW Load Case 19 FS+BS+EP+OW Wind Design Code No Wind Loads Design Wind Speed 70.000 mile/hr Exposure Constant C Importance Factor Roughness Factor Base Elevation 0.0000 in Percent Wind for Hydrotest 33. Use Wind Profile (Y/N) N Damping Factor (Beta) for Wind (Ope) 0.0100 Damping Factor (Beta) for Wind (Empty) 0.0000 Damping Factor (Beta) for Wind (Filled) 0.0000 Seismic Design Code No Seismic


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Design Nozzle for Des. Press. + St. Head Y Consider MAP New and Cold in Noz. Design N Consider External Loads for Nozzle Des. Y Consider Code Case 2168 for Nozzle Des. N Material Database Year Current w/Addenda or Code Year Complete Listing of Vessel Elements and Details: Element From Node 10 Element To Node 20 Element Type Elliptical Description Semi Elliptical Head - Left Distance "FROM" to "TO" 1.5000 in Inside Diameter 95.436 in Element Thickness 0.2820 in Internal Corrosion Allowance 0.0000 in Nominal Thickness 0.3125 in External Corrosion Allowance 0.0000 in Design Internal Pressure 75.000 psig Design Temperature Internal Pressure 150 F Design External Pressure 0.0000 psig Design Temperature External Pressure 150 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Allowable Stress, Ambient 20000. psi Allowable Stress, Operating 20000. psi Allowable Stress, Hydrotest 26000. psi Material Density 0.2830 lbm/in³ P Number Thickness 1.2500 in Yield Stress, Operating 35700. psi UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K02700 Product Form Plate Efficiency, Longitudinal Seam 0.85 Efficiency, Circumferential Seam 0.7 Elliptical Head Factor 2. Element From Node 10 Detail Type Liquid Detail ID LIQUID 10 Dist. from "FROM" Node / Offset dist 0.0000 in Height/Length of Liquid 96.000 in Density of Liquid 62.400 lbm/ft³ Element From Node 10 Detail Type Nozzle Detail ID B - 6" Pipe Dist. from "FROM" Node / Offset dist 34.500 in Nozzle Diameter 6. in. Nozzle Schedule 80 Nozzle Class 150 Layout Angle 0. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 27.295 lbf Grade of Attached Flange GR 1.1 Nozzle Matl SA-106 B Element From Node 10 Detail Type Nozzle Detail ID D - 12x16 MWY


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Dist. from "FROM" Node / Offset dist 31.000 in Nozzle Diameter 17.5 in. Nozzle Schedule None Nozzle Class 0 Layout Angle 180. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 40.675 lbf Grade of Attached Flange None Nozzle Matl SA-106 B Element From Node 20 Element To Node 30 Element Type Cylinder Description 96" OD Shell Distance "FROM" to "TO" 120.00 in Inside Diameter 95.375 in Element Thickness 0.3125 in Internal Corrosion Allowance 0.0000 in Nominal Thickness 0.3125 in External Corrosion Allowance 0.0000 in Design Internal Pressure 75.000 psig Design Temperature Internal Pressure 150 F Design External Pressure 0.0000 psig Design Temperature External Pressure 150 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Efficiency, Longitudinal Seam 0.7 Efficiency, Circumferential Seam 0.7 Element From Node 20 Detail Type Saddle Detail ID Left Saddle Dist. from "FROM" Node / Offset dist 12.000 in Width of Saddle 10.000 in Height of Saddle at Bottom 66.000 in Saddle Contact Angle 150. Height of Composite Ring Stiffener 0.0000 in Width of Wear Plate 12.000 in Thickness of Wear Plate 0.3750 in Contact Angle, Wear Plate (degrees) 150. Element From Node 20 Detail Type Saddle Detail ID Right Saddle Dist. from "FROM" Node / Offset dist 108.00 in Width of Saddle 10.000 in Height of Saddle at Bottom 66.000 in Saddle Contact Angle 150. Height of Composite Ring Stiffener 0.0000 in Width of Wear Plate 12.000 in Thickness of Wear Plate 0.3750 in Contact Angle, Wear Plate (degrees) 150. Element From Node 20 Detail Type Liquid Detail ID Liquid 20 Dist. from "FROM" Node / Offset dist 0.0000 in Height/Length of Liquid 96.000 in Density of Liquid 62.400 lbm/ft³ Element From Node 20 Detail Type Nozzle Detail ID A - 3/4" 3000#


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Dist. from "FROM" Node / Offset dist 60.000 in Nozzle Diameter 1.375 in. Nozzle Schedule None Nozzle Class 0 Layout Angle 0. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lbf Grade of Attached Flange None Nozzle Matl SA-105 Element From Node 20 Detail Type Nozzle Detail ID F - 12x16 MWY Dist. from "FROM" Node / Offset dist 60.000 in Nozzle Diameter 17.5 in. Nozzle Schedule None Nozzle Class 0 Layout Angle 135. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 40.675 lbf Grade of Attached Flange None Nozzle Matl SA-106 B Element From Node 20 Detail Type Nozzle Detail ID G - 1.5" 3000# Dist. from "FROM" Node / Offset dist 60.000 in Nozzle Diameter 2.5 in. Nozzle Schedule None Nozzle Class 0 Layout Angle 180. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 40.675 lbf Grade of Attached Flange None Nozzle Matl SA-105 Element From Node 30 Element To Node 40 Element Type Elliptical Description Semi Elliptical Head - Right Distance "FROM" to "TO" 1.5000 in Inside Diameter 95.436 in Element Thickness 0.2820 in Internal Corrosion Allowance 0.0000 in Nominal Thickness 0.3125 in External Corrosion Allowance 0.0000 in Design Internal Pressure 75.000 psig Design Temperature Internal Pressure 150 F Design External Pressure 0.0000 psig Design Temperature External Pressure 150 F Effective Diameter Multiplier 1.2 Material Name SA-516 70 Efficiency, Longitudinal Seam 0.85 Efficiency, Circumferential Seam 0.7 Elliptical Head Factor 2. Element From Node 30 Detail Type Liquid Detail ID Liquid 30 Dist. from "FROM" Node / Offset dist 0.0000 in Height/Length of Liquid 95.436 in Density of Liquid 62.400 lbm/ft³


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Element From Node 30 Detail Type Nozzle Detail ID C - 6" Pipe Dist. from "FROM" Node / Offset dist 45.000 in Nozzle Diameter 6. in. Nozzle Schedule 80 Nozzle Class 150 Layout Angle 180. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 38.245 lbf Grade of Attached Flange GR 1.1 Nozzle Matl SA-106 B Element From Node 30 Detail Type Nozzle Detail ID E - 12x16 MWY Dist. from "FROM" Node / Offset dist 31.000 in Nozzle Diameter 17.5 in. Nozzle Schedule None Nozzle Class 0 Layout Angle 0. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 40.675 lbf Grade of Attached Flange None Nozzle Matl SA-106 B PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- XY Coordinate Calculations Step: 2 10:53a Oct 27,2008

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XY Coordinate Calculations | | | | | | From| To | X (Horiz.)| Y (Vert.) |DX (Horiz.)| DY (Vert.) | | | in | in | in | in | Semi Ellip| 1.50000 | 0.00000 | 1.50000 | 0.00000 | 96" OD She| 121.500 | 0.00000 | 120.000 | 0.00000 | Semi Ellip| 123.000 | 0.00000 | 1.50000 | 0.00000 | PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Internal Pressure Calculations Step: 3 10:53a Oct 27,2008

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Element Thickness, Pressure, Diameter and Allowable Stress : | | Int. Press | Nominal | Total Corr| Element | Allowable | From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)| | | psig | in | in | in | psi | Semi Ellip| 78.4667 | 0.31250 | 0.00000 | 95.4360 | 17000.0 | 96" OD She| 78.4667 | 0.31250 | 0.00000 | 95.3750 | 14000.0 | Semi Ellip| 78.4463 | 0.31250 | 0.00000 | 95.4360 | 17000.0 | Element Required Thickness and MAWP : | | Design | M.A.W.P. | M.A.P. | Actual | Required | From| To | Pressure | Corroded | New & Cold | Thickness | Thickness | | | psig | psig | psig | in | in | Semi Ellip| 75.0000 | 96.9392 | 100.406 | 0.28200 | 0.22035 | 96" OD She| 75.0000 | 87.9171 | 91.3838 | 0.31250 | 0.26818 | Semi Ellip| 75.0000 | 96.9596 | 100.406 | 0.28200 | 0.22030 | Minimum 87.917 91.384 MAWP: 80.598 psig, limited by: Nozzle Reinforcment. Internal Pressure Calculation Results : ASME Code, Section VIII, Division 1, 2007 Elliptical Head From 10 To 20 SA-516 70 , UCS-66 Crv. B at 150 F Semi Elliptical Head - Left Thickness Due to Internal Pressure [Tr]: = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (78.467*95.4360*0.00)/(2*20000.00*0.85-0.2*78.467) = 0.2204 + 0.0000 = 0.2204 in Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: Less Operating Hydrostatic Head Pressure of 3.467 psig = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*20000.00*0.85*0.2820)/(1.00*95.4360+0.2*0.2820) = 100.406 - 3.467 = 96.939 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*20000.00*0.85*0.2820)/(1.00*95.4360+0.2*0.2820) = 100.406 psig Actual stress at given pressure and thickness, corroded [Sact]: = (P*(K*D+0.2*t))/(2*E*t) = (78.467*(1.00*95.4360+0.2*0.2820))/(2*0.85*0.2820) = 15629.891 psi Required Thickness of Straight Flange = 0.221 in Percent Elongation per UCS-79 (75*tnom/Rf)*(1-Rf/Ro) 1.440 % Min Metal Temp. w/o impact per UCS-66 -20 F Min Metal Temp. at Rqd thickness (UCS 66.1)[rat 0.66] -54 F Cylindrical Shell From 20 To 30 SA-516 70 , UCS-66 Crv. B at 150 F 96" OD Shell


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Thickness Due to Internal Pressure [Tr]: = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (78.467*47.6875)/(20000.00*0.70-0.6*78.467) = 0.2682 + 0.0000 = 0.2682 in Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: Less Operating Hydrostatic Head Pressure of 3.467 psig = (S*E*t)/(R+0.6*t) per UG-27 (c)(1) = (20000.00*0.70*0.3125)/(47.6875+0.6*0.3125) = 91.384 - 3.467 = 87.917 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1) = (20000.00*0.70*0.3125)/(47.6875+0.6*0.3125) = 91.384 psig Actual stress at given pressure and thickness, corroded [Sact]: = (P*(R+0.6*t))/(E*t) = (78.467*(47.6875+0.6*0.3125))/(0.70*0.3125) = 17172.990 psi Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 0.327 % Min Metal Temp. w/o impact per UCS-66 -20 F Min Metal Temp. at Rqd thickness (UCS 66.1)[rat 0.69] -51 F Elliptical Head From 30 To 40 SA-516 70 , UCS-66 Crv. B at 150 F Semi Elliptical Head - Right Thickness Due to Internal Pressure [Tr]: = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (78.446*95.4360*0.00)/(2*20000.00*0.85-0.2*78.446) = 0.2203 + 0.0000 = 0.2203 in Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: Less Operating Hydrostatic Head Pressure of 3.446 psig = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*20000.00*0.85*0.2820)/(1.00*95.4360+0.2*0.2820) = 100.406 - 3.446 = 96.960 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c) = (2*20000.00*0.85*0.2820)/(1.00*95.4360+0.2*0.2820) = 100.406 psig Actual stress at given pressure and thickness, corroded [Sact]: = (P*(K*D+0.2*t))/(2*E*t) = (78.446*(1.00*95.4360+0.2*0.2820))/(2*0.85*0.2820) = 15625.833 psi Required Thickness of Straight Flange = 0.221 in Percent Elongation per UCS-79 (75*tnom/Rf)*(1-Rf/Ro) 1.440 % Min Metal Temp. w/o impact per UCS-66 -20 F Min Metal Temp. at Rqd thickness (UCS 66.1)[rat 0.66] -54 F MINIMUM METAL DESIGN TEMPERATURE RESULTS : Minimum Metal Temp. w/o impact per UCS-66 -20. F Minimum Metal Temp. at Required thickness -51. F


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Note: Heads and Shells Exempted to -20F (-29C) by paragraph UG-20F Minimum Design Metal Temperature ( Entered by User ) -20. F Hydrostatic Test Pressure Results: Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 104.777 psig Pressure per UG99b[34] = 1.3 * Design Pres * Sa/S 97.500 psig Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 115.353 psig Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 88.657 psig User Defined Hydrostatic Test Pressure at High Point 98.000 psig Horizontal Hydrotest performed in accordance with: UG-99b Stresses on Elements due to Hydrostatic Test Pressure: From To Stress Allowable Ratio Pressure Semi Elliptical Head 20207.2 26000.0 0.777 101.45 96" OD Shell 22201.8 26000.0 0.854 101.44 Semi Elliptical Head 20207.2 26000.0 0.777 101.45 Elements Suitable for Internal Pressure. PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- External Pressure Calculations Step: 4 10:53a Oct 27,2008

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External Pressure Calculation Results : ASME Code, Section VIII, Division 1, 2007 Elliptical Head From 10 to 20 Ext. Chart: CS-2 at 150 F Semi Elliptical Head - Left Elastic Modulus from Chart: CS-2 at 300 F : 0.29000E+08 psi Results for Maximum Allowable External Pressure (MAEP): Tca OD D/t Factor A B 0.282 96.00 340.43 0.0004080 5915.80 EMAP = B/(K0*D/t) = 5915.7988 /(0.9000 *340.4255 ) = 19.3085 psig Cylindrical Shell From 20 to 30 Ext. Chart: CS-2 at 150 F 96" OD Shell Elastic Modulus from Chart: CS-2 at 300 F : 0.29000E+08 psi Results for Maximum Allowable External Pressure (MAEP): Tca OD SLEN D/t L/D Factor A B 0.312 96.00 138.91 307.20 1.4469 0.0001699 2463.23 EMAP = (4*B)/(3*(D/t)) = (4*2463.2302 )/(3*307.2000 ) = 10.6911 psig Results for Maximum Stiffened Length (Slen): Tca OD SLEN D/t L/D Factor A B 0.312 96.00 0.35E+33 307.20 .5000E+02 0.0000117 169.01 EMAP = (4*B)/(3*(D/t)) = (4*169.0123 )/(3*307.2000 ) = 0.7336 psig Elliptical Head From 30 to 40 Ext. Chart: CS-2 at 150 F Semi Elliptical Head - Right Elastic Modulus from Chart: CS-2 at 300 F : 0.29000E+08 psi Results for Maximum Allowable External Pressure (MAEP): Tca OD D/t Factor A B 0.282 96.00 340.43 0.0004080 5915.80 EMAP = B/(K0*D/t) = 5915.7988 /(0.9000 *340.4255 ) = 19.3085 psig External Pressure Calculations | | Section | Outside | Corroded | Factor | Factor | From| To | Length | Diameter | Thickness | A | B | | | in | in | in | | psi | 10| 20| No Calc | 96.0000 | 0.28200 | 0.00040799 | 5915.80 | 20| 30| 138.906 | 96.0000 | 0.31250 | 0.00016988 | 2463.23 | 30| 40| No Calc | 96.0000 | 0.28200 | 0.00040799 | 5915.80 | External Pressure Calculations | | External | External | External | External | From| To | Actual T. | Required T.|Des. Press. | M.A.W.P. | | | in | in | psig | psig | 10| 20| 0.28200 | No Calc | 0.00000 | 19.3085 | 20| 30| 0.31250 | No Calc | 0.00000 | 10.6911 | 30| 40| 0.28200 | No Calc | 0.00000 | 19.3085 | Minimum 10.691 External Pressure Calculations

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- External Pressure Calculations Step: 4 10:53a Oct 27,2008

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| | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia | From| To | Bet. Stiff.| Bet. Stiff.| Required | Available | | | in | in | in**4 | in**4 | 10| 20| No Calc | No Calc | No Calc | No Calc | 20| 30| 138.906 | 352.2E+30 | No Calc | No Calc | 30| 40| No Calc | No Calc | No Calc | No Calc | Elements Suitable for External Pressure. PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Element and Detail Weights Step: 5 10:53a Oct 27,2008

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Element and Detail Weights | | Element | Element | Corroded | Corroded | Extra due | From| To | Metal Wgt. | ID Volume |Metal Wgt. | ID Volume | Misc % | | | lbf | ft³ | lbf | ft³ | lbf | 10| 20| 1010.28 | 72.0554 | 1010.28 | 72.0554 | 151.542 | 20| 30| 3190.24 | 496.128 | 3190.24 | 496.128 | 478.536 | 30| 40| 1010.28 | 72.0554 | 1010.28 | 72.0554 | 151.542 | --------------------------------------------------------------------------- Total 5210 640 5210 640 1563 Weight of Details | | Weight of | X Offset, | Y Offset, | From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description | | lbf | in | in | 10|Liqd| 4495.81 | -7.95300 | -0.28200 | LIQUID 10 10|Nozl| 31.3890 | -1.98825 | 34.5000 | B - 6" Pipe 10|Nozl| 46.7762 | -1.98825 | 31.0000 | D - 12x16 MWY 20|Sadl| 1065.29 | 12.0000 | 56.5000 | Left Saddle 20|Sadl| 1065.29 | 108.000 | 56.5000 | Right Saddle 20|Liqd| 30958.6 | 60.0000 | -0.31250 | Liquid 20 20|Nozl| 0.33995 | 60.0000 | 48.3750 | A - 3/4" 3000# 20|Nozl| 46.7762 | 60.0000 | 56.4375 | F - 12x16 MWY 20|Nozl| 46.7762 | 60.0000 | 48.9375 | G - 1.5" 3000# 30|Liqd| 4496.29 | 9.45300 | 0.00000 | Liquid 30 30|Nozl| 43.9823 | 3.48825 | 45.0000 | C - 6" Pipe 30|Nozl| 46.7762 | 3.48825 | 31.0000 | E - 12x16 MWY Total Weight of Each Detail Type Total Weight of Saddles 2130.6 Total Weight of Liquid 39950.7 Total Weight of Nozzles 262.8 --------------------------------------------------------------- Sum of the Detail Weights 42344.1 lbf Weight Summary Fabricated Wt. - Bare Weight W/O Removable Internals 8385.8 lbf Shop Test Wt. - Fabricated Weight + Water ( Full ) 48337.0 lbf Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 8385.8 lbf Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 8385.8 lbf Ope. Wt. no Liq - Fab. Wt + Intls. + Details + Wghts. 8385.8 lbf Operating Wt. - Empty Wt. + Operating Liquid (No CA) 48336.5 lbf Oper. Wt. + CA - Corr Wt. + Operating Liquid 48336.5 lbf Field Test Wt. - Empty Weight + Water (Full) 48337.0 lbf Note: The Corroded Weight and thickness are used in the Horizontal Vessel Analysis (Ope Case) and Earthquake Load Calculations. Outside Surface Areas of Elements | | Surface | From| To | Area | | | in² | 10| 20| 10455.4 | 20| 30| 36191.1 | 30| 40| 10455.4 | ----------------------------------------------------- Total 57101.914 in² [396.5 Square Feet ]

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Element and Detail Weights Step: 5 10:53a Oct 27,2008

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PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Flange MAWP Step: 6 10:53a Oct 27,2008

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Nozzle Flange MAWP Results : Flange Rating Operating Ambient Temperature Class Grade|Group psig psig F ---------------------------------------------------------------------------- 272.500 285.000 150 150 GR 1.1 ---------------------------------------------------------------------------- Minimum Rating 272.500 285.000 psig Note: ANSI Ratings are per ANSI/ASME B16.5 2003 Edition PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Center of Gravity Calculation Step: 7 10:53a Oct 27,2008

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Shop/Field Installation Options : Note : The CG is computed from the first Element From Node Center of Gravity of Saddles 61.5 in Center of Gravity of Liquid 61.5 in Center of Gravity of Nozzles 64.5 in Center of Gravity of Bare Shell New and Cold 61.5 in Center of Gravity of Bare Shell Corroded 61.5 in Vessel CG in the Operating Condition 61.5 in Vessel CG in the Fabricated (Shop/Empty) Condition 61.6 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Horizontal Vessel Analysis (Ope.) Step: 8 10:53a Oct 27,2008

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Zick Analysis: Stresses for the Left Saddle Horizontal Vessel Stress Calculations : Operating Case Shell Allowable Stress used in Calculation 20000.00 psi Shell Comp. Yield Stress used in Calculation 35700.00 psi Head Allowable Stress used in Calculation 20000.00 psi Saddle Force Q, Operating Case 34208.43 lbf Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 5855.78 14000.00 psi Long. Stress at Bottom of Saddles 5823.04 14000.00 psi Long. Stress at Top of Midspan 5455.64 14000.00 psi Long. Stress at Bottom of Midspan 6223.17 14000.00 psi Tangential Shear in Shell 1113.63 16000.00 psi Tangential Shear in Head 1234.08 16000.00 psi Circ. Stress at Horn of Saddle -14745.84 -30000.00 psi Addl. Stress in Head as Stiffener 751.03 5000.00 psi Circ. Compressive Stress in Shell -2791.77 -17850.00 psi Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Intermediate Results: Saddle Reaction Q due to Wind or Seismic Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls = Max( 0.00 , 16166.01 , 0 ) * 66.0000 / 96.0000 = 11114.1 lbf Saddle Reaction Force due to Earthquake Fl or Friction [Fsl]: = Max( Fl, Friction Force, Sum of X Forces ) * B / Ls = Max( 0.00 , 16166.01 , 0 ) * 66.0000 / 96.0000 = 11114.1 lbf Saddle Reaction Force due to Earthquake Ft [Fst]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E = 3.00 * ( 0 /2 + 0 ) * 66.0000 / 92.7289 = 0.0 lbf Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 23094 + Max( 11114 , 0 , 11114 , 0 ) = 34208.4 lbf Summary of Loads on this Saddle Support: Vertical Load on this Saddle 34208.43 lbf Transverse Shear Load on this Saddle 0.00 lbf Longitudinal Shear Load on this Saddle 16166.01 lbf Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 0.25 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 34208 * 123.00 * 0.5346 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = 251.86 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) -


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(Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.614 ) / 1.614 - Cos(1.614 )) / ( 1.614 + Sin(1.614 ) * Cos(1.614 ) - 2 * Sin(1.614 ) * Sin(1.614 )/ 1.614 ) = 6.2238 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 13.500 /123.000 + (47.688² - 23.859²)/( 2 * 13.500 * 123.000 (1 + (4 * 1.988 )/(3 * 123.000 ) ) = -0.1152 Intermediate Product [K.1]: = K * X * 4 * A / L = 6.224 * -0.115 * 4 * 13.500 / 123.000 = -0.3147 Longitudinal Bending (+-) at Saddle = ( 0.25 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 34208 * 123.00 * -0.3147 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = -148.28 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 34208 * 0.4851 / ( 47.6875 * ( 0.3125 - 0.0000 ) = 1113.63 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 34208 * 0.4851 / ( 47.69 * ( 0.2820 - 0.0000 ) = 1234.08 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -34208 /( 4 * 0.3125 * (10.00 + 1.56 * sqrt(47.6875 *0.3125 ))) -12.0 * 34208 * 3.97 * 0.0080 / ( 10.2500 * 0.0977 ) = -14745.84 psi Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (34208 / ( 47.6875 * ( 0.2820 - 0.0000 )))*(3/8)*( sin( 99.75 )²)/ ( pi - 99.75 + sin( 99.75 ) * cos( 99.75 ))) = 751.03 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9 * WPDWTH ) ) ) = ( 34208 *( 0.6733 /( 0.6875 * 12.000 ) ) ) = -2791.77 psi Free Un-Restrained Thermal Expansion between the Saddles [Exp]: = Alpha * Ls * ( Design Temperature - Ambient Temperature ) = 0.571E-05 * 96.000 * ( 150.0 - 70.0 ) = 0.044 in Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 70.0000 in Baseplate Thickness Bpthk 0.7500 in Baseplate Width Bpwid 12.0000 in Number of Ribs ( inc. outside ribs ) Nribs 5 Rib Thickness Ribtk 0.5000 in Web Thickness Webtk 0.5000 in Web Location Webloc Center Moment of Inertia of Saddle - Lateral Direction


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Y A AY Ay² Io Shell 0. 6. 1. 0. 0. Wearplate 0. 4. 2. 1. 0. Web 8. 8. 65. 546. 153. BasePlate 17. 9. 149. 2452. 0. Totals 26. 27. 217. 2999. 154. Value C1 = Sumof(Ay)/Sumof(A) = 8. in Value I = Sumof(Ay² ) + Sumof(Io) - C1*Sumof(Ay) = 1406. in**4 Value As = Sumof(A) - Ashell = 21. in² K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2594 Fh = ( K1 * Q ) = 8872.7207 lbf Tension Stress, St = ( Fh/As ) = 418.1055 psi Allowed Stress, Sa = 0.6 * Yield Str = 21600.0000 psi d = B - R*Sin(theta) / theta = 29.3783 in Bending Moment, M = Fh * d = 260665.2188 in-lb Bending Stress, Sb = ( M * C1 / I ) = 1495.6577 psi Allowed Stress, Sa = 2/3 * Yield Str = 24000.0000 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 4 * BasePlateLength * AllStress ))½ = ( 3 * 34208 * 12.00 / ( 4 * 70.000 * 24000.000 ))½ = 0.43 in Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 70.0000 - 1.0 ) / ( 5 - 1 ) = 17.2500 in Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 17.2500 * 12.0000 / 2 = 103.5000 in² Axial Load [P]: = Ap * Bp = 103.5 * 40.72 = 4215.0 lbf Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 12.000 - 1.0 - 0.500 ) * 0.500 + 17.2500 /2 * 0.500 = 9.562 in² Compressive Stress [Sc]: = P/Ar = 4215.0 / 9.5625 = 440.7809 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 5.0 5.0 25.0 0.0 48.2 Web 5.0 4.3 21.6 0.0 0.2 Values 5.0 9.3 46.6 0.0 48.4 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 16166.0 /( 2 * 70.00 ) * 17.250 * 52.14 / 2


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= 51932.559 in-lb KL/R < Cc ( 23.1743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 23.17 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(23.17 )/(8* 126.10 )-( 23.17³)/(8*126.10³) Sca = 20401.15 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 440.78 / 20401.15 + (51932.56 /8.069 ) / 24000.00 Check = 0.29 Check of Inside Ribs Inertia of Saddle, Inner Ribs - Axial Direction Y A AY Ay² Io Rib 5.5 5.2 28.9 0.0 55.5 Web 5.5 8.6 47.4 0.0 0.2 Values 5.5 13.9 76.3 0.0 55.6 KL/R < Cc ( 9.6743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 9.67 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(9.67 )/(8* 126.10 )-( 9.67³)/(8*126.10³) Sca = 21171.69 psi AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 607.56 / 21171.69 + ( 38587.97 /10.116 ) / 24000.00 Check = 0.19 Zick Analysis: Stresses for the Right Saddle Shell Allowable Stress used in Calculation 20000.00 psi Shell Comp. Yield Stress used in Calculation 35700.00 psi Head Allowable Stress used in Calculation 20000.00 psi Saddle Force Q, Operating Case 34234.11 lbf Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 5855.89 14000.00 psi Long. Stress at Bottom of Saddles 5822.93 14000.00 psi Long. Stress at Top of Midspan 5455.45 14000.00 psi Long. Stress at Bottom of Midspan 6223.36 14000.00 psi Tangential Shear in Shell 1114.47 16000.00 psi Tangential Shear in Head 1235.00 16000.00 psi Circ. Stress at Horn of Saddle -14756.91 -30000.00 psi Addl. Stress in Head as Stiffener 751.59 5000.00 psi Circ. Compressive Stress in Shell -2793.87 -17850.00 psi Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Intermediate Results: Saddle Reaction Q due to Wind or Seismic Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls = Max( 0.00 , 16178.14 , 0 ) * 66.0000 / 96.0000 = 11122.5 lbf


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Saddle Reaction Force due to Earthquake Fl or Friction [Fsl]: = Max( Fl, Friction Force, Sum of X Forces ) * B / Ls = Max( 0.00 , 16178.14 , 0 ) * 66.0000 / 96.0000 = 11122.5 lbf Saddle Reaction Force due to Earthquake Ft [Fst]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E = 3.00 * ( 0 /2 + 0 ) * 66.0000 / 92.7289 = 0.0 lbf Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 23111 + Max( 11122 , 0 , 11122 , 0 ) = 34234.1 lbf Summary of Loads on this Saddle Support: Vertical Load on this Saddle 34234.11 lbf Transverse Shear Load on this Saddle 0.00 lbf Longitudinal Shear Load on this Saddle 16178.14 lbf Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 0.25 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 34234 * 123.00 * 0.5346 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = 252.05 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.614 ) / 1.614 - Cos(1.614 )) / ( 1.614 + Sin(1.614 ) * Cos(1.614 ) - 2 * Sin(1.614 ) * Sin(1.614 )/ 1.614 ) = 6.2238 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 13.500 /123.000 + (47.688² - 23.859²)/( 2 * 13.500 * 123.000 (1 + (4 * 1.988 )/(3 * 123.000 ) ) = -0.1152 Intermediate Product [K.1]: = K * X * 4 * A / L = 6.224 * -0.115 * 4 * 13.500 / 123.000 = -0.3147 Longitudinal Bending (+-) at Saddle = ( 0.25 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 34234 * 123.00 * -0.3147 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = -148.39 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 34234 * 0.4851 / ( 47.6875 * ( 0.3125 - 0.0000 ) = 1114.47 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 34234 * 0.4851 / ( 47.69 * ( 0.2820 - 0.0000 ) = 1235.00 psi Circumferential Stress at Horn of Saddle


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= -Q/(4*TEM*(SADWTH+1.56*sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -34234 /( 4 * 0.3125 * (10.00 + 1.56 * sqrt(47.6875 *0.3125 ))) -12.0 * 34234 * 3.97 * 0.0080 / ( 10.2500 * 0.0977 ) = -14756.91 psi Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (34234 / ( 47.6875 * ( 0.2820 - 0.0000 )))*(3/8)*( sin( 99.75 )²)/ ( pi - 99.75 + sin( 99.75 ) * cos( 99.75 ))) = 751.59 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9 * WPDWTH ) ) ) = ( 34234 *( 0.6733 /( 0.6875 * 12.000 ) ) ) = -2793.87 psi Results for Vessel Ribs, Web and Base Baseplate Length Bplen 70.0000 in Baseplate Thickness Bpthk 0.7500 in Baseplate Width Bpwid 12.0000 in Number of Ribs ( inc. outside ribs ) Nribs 5 Rib Thickness Ribtk 0.5000 in Web Thickness Webtk 0.5000 in Web Location Webloc Center Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0. 6. 1. 0. 0. Wearplate 0. 4. 2. 1. 0. Web 8. 8. 65. 546. 153. BasePlate 17. 9. 149. 2452. 0. Totals 26. 27. 217. 2999. 154. Value C1 = Sumof(Ay)/Sumof(A) = 8. in Value I = Sumof(Ay² ) + Sumof(Io) - C1*Sumof(Ay) = 1406. in**4 Value As = Sumof(A) - Ashell = 21. in² K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2594 Fh = ( K1 * Q ) = 8879.3809 lbf Tension Stress, St = ( Fh/As ) = 418.4193 psi Allowed Stress, Sa = 0.6 * Yield Str = 21600.0000 psi d = B - R*Sin(theta) / theta = 29.3783 in Bending Moment, M = Fh * d = 260860.8750 in-lb Bending Stress, Sb = ( M * C1 / I ) = 1496.7803 psi Allowed Stress, Sa = 2/3 * Yield Str = 24000.0000 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 4 * BasePlateLength * AllStress ))½ = ( 3 * 34234 * 12.00 / ( 4 * 70.000 * 24000.000 ))½ = 0.43 in Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 70.0000 - 1.0 ) / ( 5 - 1 ) = 17.2500 in


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Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 17.2500 * 12.0000 / 2 = 103.5000 in² Axial Load [P]: = Ap * Bp = 103.5 * 40.75 = 4218.1 lbf Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 12.000 - 1.0 - 0.500 ) * 0.500 + 17.2500 /2 * 0.500 = 9.562 in² Compressive Stress [Sc]: = P/Ar = 4218.1 / 9.5625 = 441.1117 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 5.0 5.0 25.0 0.0 48.2 Web 5.0 4.3 21.6 0.0 0.2 Values 5.0 9.3 46.6 0.0 48.4 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 16178.1 /( 2 * 70.00 ) * 17.250 * 52.14 / 2 = 51971.539 in-lb KL/R < Cc ( 23.1743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 23.17 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(23.17 )/(8* 126.10 )-( 23.17³)/(8*126.10³) Sca = 20401.15 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 441.11 / 20401.15 + (51971.54 /8.069 ) / 24000.00 Check = 0.29 Check of Inside Ribs Inertia of Saddle, Inner Ribs - Axial Direction Y A AY Ay² Io Rib 5.5 5.2 28.9 0.0 55.5 Web 5.5 8.6 47.4 0.0 0.2 Values 5.5 13.9 76.3 0.0 55.6 KL/R < Cc ( 9.6743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 9.67 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(9.67 )/(8* 126.10 )-( 9.67³)/(8*126.10³) Sca = 21171.69 psi AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 608.02 / 21171.69 + ( 38616.94 /10.116 ) / 24000.00 Check = 0.19 PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Horizontal Vessel Analysis (Test) Step: 9 10:53a Oct 27,2008

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Zick Analysis: Stresses for the Left Saddle Horizontal Vessel Stress Calculations : Test Case Shell Allowable Stress used in Calculation 20000.00 psi Shell Comp. Yield Stress used in Calculation 38000.00 psi Head Allowable Stress used in Calculation 20000.00 psi Saddle Force Q, Test Case, no Ext. Forces 23094.86 lbf Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 7557.90 14000.00 psi Long. Stress at Bottom of Saddles 7357.69 14000.00 psi Long. Stress at Top of Midspan 7287.76 14000.00 psi Long. Stress at Bottom of Midspan 7627.84 14000.00 psi Tangential Shear in Shell 751.84 16000.00 psi Tangential Shear in Head 833.15 16000.00 psi Circ. Stress at Horn of Saddle -9955.24 -30000.00 psi Addl. Stress in Head as Stiffener 507.03 5000.00 psi Circ. Compressive Stress in Shell -1884.79 -19000.00 psi Hydrostatic Test Pressure at top of Vessel 98.000 psig Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 23094 + Max( 0 , 0 , 0 , 0 ) = 23094.9 lbf Summary of Loads on this Saddle Support: Vertical Load on this Saddle 23094.86 lbf Transverse Shear Load on this Saddle 0.00 lbf Longitudinal Shear Load on this Saddle 0.00 lbf Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 0.25 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 23094 * 123.00 * 0.5346 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = 170.04 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.614 ) / 1.614 - Cos(1.614 )) / ( 1.614 + Sin(1.614 ) * Cos(1.614 ) - 2 * Sin(1.614 ) * Sin(1.614 )/ 1.614 ) = 6.2238 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 13.500 /123.000 + (47.688² - 23.859²)/( 2 * 13.500 * 123.000 (1 + (4 * 1.988 )/(3 * 123.000 ) ) = -0.1152 Intermediate Product [K.1]: = K * X * 4 * A / L = 6.224 * -0.115 * 4 * 13.500 / 123.000 = -0.3147


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Longitudinal Bending (+-) at Saddle = ( 0.25 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 23094 * 123.00 * -0.3147 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = -100.10 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 23094 * 0.4851 / ( 47.6875 * ( 0.3125 - 0.0000 ) = 751.84 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 23094 * 0.4851 / ( 47.69 * ( 0.2820 - 0.0000 ) = 833.15 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -23094 /( 4 * 0.3125 * (10.00 + 1.56 * sqrt(47.6875 *0.3125 ))) -12.0 * 23094 * 3.97 * 0.0080 / ( 10.2500 * 0.0977 ) = -9955.24 psi Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (23094 / ( 47.6875 * ( 0.2820 - 0.0000 )))*(3/8)*( sin( 99.75 )²)/ ( pi - 99.75 + sin( 99.75 ) * cos( 99.75 ))) = 507.03 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9 * WPDWTH ) ) ) = ( 23094 *( 0.6733 /( 0.6875 * 12.000 ) ) ) = -1884.79 psi Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 70.0000 in Baseplate Thickness Bpthk 0.7500 in Baseplate Width Bpwid 12.0000 in Number of Ribs ( inc. outside ribs ) Nribs 5 Rib Thickness Ribtk 0.5000 in Web Thickness Webtk 0.5000 in Web Location Webloc Center Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0. 6. 1. 0. 0. Wearplate 0. 4. 2. 1. 0. Web 8. 8. 65. 546. 153. BasePlate 17. 9. 149. 2452. 0. Totals 26. 27. 217. 2999. 154. Value C1 = Sumof(Ay)/Sumof(A) = 8. in Value I = Sumof(Ay² ) + Sumof(Io) - C1*Sumof(Ay) = 1406. in**4 Value As = Sumof(A) - Ashell = 21. in² K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2594 Fh = ( K1 * Q ) = 5990.1689 lbf Tension Stress, St = ( Fh/As ) = 282.2722 psi Allowed Stress, Sa = 0.6 * Yield Str = 21600.0000 psi d = B - R*Sin(theta) / theta = 29.3783 in


27

Bending Moment, M = Fh * d = 175980.8125 in-lb Bending Stress, Sb = ( M * C1 / I ) = 1009.7513 psi Allowed Stress, Sa = 2/3 * Yield Str = 24000.0000 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 4 * BasePlateLength * AllStress ))½ = ( 3 * 23094 * 12.00 / ( 4 * 70.000 * 24000.000 ))½ = 0.35 in Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 70.0000 - 1.0 ) / ( 5 - 1 ) = 17.2500 in Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 17.2500 * 12.0000 / 2 = 103.5000 in² Axial Load [P]: = Ap * Bp = 103.5 * 27.49 = 2845.6 lbf Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 12.000 - 1.0 - 0.500 ) * 0.500 + 17.2500 /2 * 0.500 = 9.562 in² Compressive Stress [Sc]: = P/Ar = 2845.6 / 9.5625 = 297.5809 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 5.0 5.0 25.0 0.0 48.2 Web 5.0 4.3 21.6 0.0 0.2 Values 5.0 9.3 46.6 0.0 48.4 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 0.0 /( 2 * 70.00 ) * 17.250 * 52.14 / 2 = 0.000 in-lb KL/R < Cc ( 23.1743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 23.17 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(23.17 )/(8* 126.10 )-( 23.17³)/(8*126.10³) Sca = 20401.15 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 297.58 / 20401.15 + (0.00 /8.069 ) / 24000.00 Check = 0.01 Check of Inside Ribs Inertia of Saddle, Inner Ribs - Axial Direction Y A AY Ay² Io Rib 5.5 5.2 28.9 0.0 55.5 Web 5.5 8.6 47.4 0.0 0.2 Values 5.5 13.9 76.3 0.0 55.6


28

KL/R < Cc ( 9.6743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 9.67 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(9.67 )/(8* 126.10 )-( 9.67³)/(8*126.10³) Sca = 21171.69 psi AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 410.18 / 21171.69 + ( 0.00 /10.116 ) / 24000.00 Check = 0.02 Zick Analysis: Stresses for the Right Saddle Shell Allowable Stress used in Calculation 20000.00 psi Shell Comp. Yield Stress used in Calculation 38000.00 psi Head Allowable Stress used in Calculation 20000.00 psi Saddle Force Q, Test Case, no Ext. Forces 23111.52 lbf Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 7557.98 14000.00 psi Long. Stress at Bottom of Saddles 7357.62 14000.00 psi Long. Stress at Top of Midspan 7287.64 14000.00 psi Long. Stress at Bottom of Midspan 7627.96 14000.00 psi Tangential Shear in Shell 752.38 16000.00 psi Tangential Shear in Head 833.75 16000.00 psi Circ. Stress at Horn of Saddle -9962.42 -30000.00 psi Addl. Stress in Head as Stiffener 507.40 5000.00 psi Circ. Compressive Stress in Shell -1886.15 -19000.00 psi Hydrostatic Test Pressure at top of Vessel 98.000 psig Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 23111 + Max( 0 , 0 , 0 , 0 ) = 23111.5 lbf Summary of Loads on this Saddle Support: Vertical Load on this Saddle 23111.52 lbf Transverse Shear Load on this Saddle 0.00 lbf Longitudinal Shear Load on this Saddle 0.00 lbf Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 0.25 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 23111 * 123.00 * 0.5346 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = 170.16 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.614 ) / 1.614 - Cos(1.614 )) / ( 1.614 + Sin(1.614 ) * Cos(1.614 ) - 2 * Sin(1.614 ) * Sin(1.614 )/ 1.614 ) = 6.2238


29

Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 13.500 /123.000 + (47.688² - 23.859²)/( 2 * 13.500 * 123.000 (1 + (4 * 1.988 )/(3 * 123.000 ) ) = -0.1152 Intermediate Product [K.1]: = K * X * 4 * A / L = 6.224 * -0.115 * 4 * 13.500 / 123.000 = -0.3147 Longitudinal Bending (+-) at Saddle = ( 0.25 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 0.25 * 23111 * 123.00 * -0.3147 ) / ( 3.141 * 47.6875 * 47.6875 * ( 0.3125 - 0.0000 ))) = -100.18 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 23111 * 0.4851 / ( 47.6875 * ( 0.3125 - 0.0000 ) = 752.38 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 23111 * 0.4851 / ( 47.69 * ( 0.2820 - 0.0000 ) = 833.75 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -23111 /( 4 * 0.3125 * (10.00 + 1.56 * sqrt(47.6875 *0.3125 ))) -12.0 * 23111 * 3.97 * 0.0080 / ( 10.2500 * 0.0977 ) = -9962.42 psi Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (23111 / ( 47.6875 * ( 0.2820 - 0.0000 )))*(3/8)*( sin( 99.75 )²)/ ( pi - 99.75 + sin( 99.75 ) * cos( 99.75 ))) = 507.40 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9 * WPDWTH ) ) ) = ( 23111 *( 0.6733 /( 0.6875 * 12.000 ) ) ) = -1886.15 psi Results for Vessel Ribs, Web and Base Baseplate Length Bplen 70.0000 in Baseplate Thickness Bpthk 0.7500 in Baseplate Width Bpwid 12.0000 in Number of Ribs ( inc. outside ribs ) Nribs 5 Rib Thickness Ribtk 0.5000 in Web Thickness Webtk 0.5000 in Web Location Webloc Center Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0. 6. 1. 0. 0. Wearplate 0. 4. 2. 1. 0. Web 8. 8. 65. 546. 153. BasePlate 17. 9. 149. 2452. 0. Totals 26. 27. 217. 2999. 154.


30

Value C1 = Sumof(Ay)/Sumof(A) = 8. in Value I = Sumof(Ay² ) + Sumof(Io) - C1*Sumof(Ay) = 1406. in**4 Value As = Sumof(A) - Ashell = 21. in² K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2594 Fh = ( K1 * Q ) = 5994.4902 lbf Tension Stress, St = ( Fh/As ) = 282.4759 psi Allowed Stress, Sa = 0.6 * Yield Str = 21600.0000 psi d = B - R*Sin(theta) / theta = 29.3783 in Bending Moment, M = Fh * d = 176107.7656 in-lb Bending Stress, Sb = ( M * C1 / I ) = 1010.4798 psi Allowed Stress, Sa = 2/3 * Yield Str = 24000.0000 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 4 * BasePlateLength * AllStress ))½ = ( 3 * 23111 * 12.00 / ( 4 * 70.000 * 24000.000 ))½ = 0.35 in Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 70.0000 - 1.0 ) / ( 5 - 1 ) = 17.2500 in Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 17.2500 * 12.0000 / 2 = 103.5000 in² Axial Load [P]: = Ap * Bp = 103.5 * 27.51 = 2847.7 lbf Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 12.000 - 1.0 - 0.500 ) * 0.500 + 17.2500 /2 * 0.500 = 9.562 in² Compressive Stress [Sc]: = P/Ar = 2847.7 / 9.5625 = 297.7955 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 5.0 5.0 25.0 0.0 48.2 Web 5.0 4.3 21.6 0.0 0.2 Values 5.0 9.3 46.6 0.0 48.4 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 0.0 /( 2 * 70.00 ) * 17.250 * 52.14 / 2 = 0.000 in-lb KL/R < Cc ( 23.1743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 23.17 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(23.17 )/(8* 126.10 )-( 23.17³)/(8*126.10³) Sca = 20401.15 psi


31

AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 297.80 / 20401.15 + (0.00 /8.069 ) / 24000.00 Check = 0.01 Check of Inside Ribs Inertia of Saddle, Inner Ribs - Axial Direction Y A AY Ay² Io Rib 5.5 5.2 28.9 0.0 55.5 Web 5.5 8.6 47.4 0.0 0.2 Values 5.5 13.9 76.3 0.0 55.6 KL/R < Cc ( 9.6743 < 126.0993 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 9.67 )²/(2 * 126.10² )) * 36000 / ( 5/3+3*(9.67 )/(8* 126.10 )-( 9.67³)/(8*126.10³) Sca = 21171.69 psi AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 410.47 / 21171.69 + ( 0.00 /10.116 ) / 24000.00 Check = 0.02 PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. A - 3/4" 3000# Nozl: 10 10:53a Oct 27,2008

32

INPUT VALUES, Nozzle Description: A - 3/4" 3000# From : 20 Pressure for Nozzle Reinforcement Calculations P 75.023 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Cylindrical Shell D 95.3750 in Shell Actual Thickness T 0.3125 in Shell Internal Corrosion Allowance Cas 0.0000 in Shell External Corrosion Allowance Caext 0.0000 in Distance from Bottom/Left Tangent 61.5000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-105 Nozzle Allowable Stress at Temperature Sn 20000.00 psi Nozzle Allowable Stress At Ambient Sna 20000.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 0.00 deg Nozzle Diameter Dia 1.3750 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.1625 in Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 1.6875 in Weld leg size between Nozzle and Pad/Shell Wo 0.2500 in Groove weld depth between Nozzle and Vessel Wgnv 0.3125 in Nozzle Inside Projection H 0.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.0000 in ASME Code Weld Type per UW-16 Z-1 The Pressure Design option was Design Pressure + static head Nozzle Sketch | | | | | | | | ____________/| | | \ | | | \ | | |____________\|__| Insert Nozzle No Pad, no Inside projection NOZZLE CALCULATION, Description: A - 3/4" 3000# ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 1.375 in. Actual Nozzle Thickness Used in Calculation 0.162 in.

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. A - 3/4" 3000# Nozl: 10 10:53a Oct 27,2008

33

Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (75.02*47.6875)/(20000*1.00-0.6*75.02) = 0.1793 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (75.02*0.6875)/(20000*1.00+0.4*75.02) = 0.0026 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 2.1000 in Effective material thickness limit, no pad Tlnp 0.4062 in Note: Taking a UG-36(c)(3)(a) exemption for A - 3/4" 3000# . This calculation is valid for nozzles that meet all the requirements of paragraph UG-36. Please check the Code carefully, especially for nozzles that are not isolated or do not meet Code spacing requirements. It may be necessary to force the program to print the areas per UG-37. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness per UG45(a), tra = 0.0026 in Wall Thickness per UG16(b), tr16b = 0.0625 in Wall Thickness per UG45(b)(1), trb1 = 0.1793 in Check UG16(b) Min. Thickness, trb1 = Max(trb1, tr16b) = 0.1793 in Std. Wall Pipe per UG45(b)(4), trb4 = 0.1225 in Wall Thickness per UG45(b), trb = Min(trb1, trb4) = 0.1225 in Final Required Thickness, tr45 = Max(tra, trb) = 0.1225 in Available Nozzle Neck Thickness = 0.1625 in --> OK Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 75.02 / 285.00 = 0.263 Weld Size Calculations, Description: A - 3/4" 3000# Intermediate Calc. for nozzle/shell Welds Tmin 0.1625 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.1137 = 0.7 * TMIN 0.1768 = 0.7 * Wo in The Drop for this Nozzle is : 0.0050 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 2.0050 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. B - 6" Pipe Nozl: 8 10:53a Oct 27,2008

34

INPUT VALUES, Nozzle Description: B - 6" Pipe From : 10 Pressure for Nozzle Reinforcement Calculations P 75.498 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Elliptical Head D 95.4360 in Aspect Ratio of Elliptical Head Ar 2.00 Head Actual Thickness T 0.2820 in Head Internal Corrosion Allowance Cas 0.0000 in Head External Corrosion Allowance Caext 0.0000 in Distance from Head Centerline L1 34.5000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-106 B Nozzle Allowable Stress at Temperature Sn 17100.00 psi Nozzle Allowable Stress At Ambient Sna 17100.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 0.00 deg Nozzle Diameter Dia 6.0000 in. Nozzle Size and Thickness Basis Idbn Nominal Nominal Thickness of Nozzle Thknom 80 Nozzle Flange Material SA-105 Nozzle Flange Type Slip on Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 4.0000 in Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in Groove weld depth between Nozzle and Vessel Wgnv 0.2820 in Nozzle Inside Projection H 1.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.3125 in ASME Code Weld Type per UW-16 C Class of attached Flange 150 Grade of attached Flange GR 1.1 The Pressure Design option was Design Pressure + static head Nozzle Sketch | | | | | | | | ____________/| | | \ | | | \ | | |____________\| | \| | |__|


35

Insert Nozzle No Pad, with Inside projection NOZZLE CALCULATION, Description: B - 6" Pipe ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 6.625 in. Actual Nozzle Thickness Used in Calculation 0.432 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (75.50*95.4360*1.00)/( 2*20000.00*1.00-0.2*75.50) = 0.1802 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (75.50*3.3125)/(17100*1.00+0.4*75.50) = 0.0146 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 13.0400 in Effective material thickness limit, no pad Tlnp 0.7050 in Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 1.197 NA NA in² Area in Shell A1 0.651 NA NA in² Area in Nozzle Wall A2 0.503 NA NA in² Area in Inward Nozzle A3 0.521 NA NA in² Area in Welds A4 0.167 NA NA in² Area in Pad A5 0.000 NA NA in² TOTAL AREA AVAILABLE Atot 1.842 NA NA in² The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 62.08 Degs. The area available without a pad is Sufficient. Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (6.5200*0.1802+2*(0.4320-0.0000)*0.1802*(1-0.8550)) = 1.197 in² Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (13.040-6.520)*(1.00*(0.2820-0.000)-0.180)-2*(0.432-0.000) *(1.00*(0.2820-0.0000)-0.1802)*(1-0.8550) = 0.651 in² Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.705 ,4.000 ) ) * ( 0.4320 - 0.0000 - 0.0146 ) * 0.8550 ) = 0.503 in² Area Available in Nozzle Penetration [A3]: = 2*(Tn-Can-Can)*(min(H-Can,Tl, 2.5*Tn-Can-Can))*fr2 = 2 * ( 0.4320 ) * ( 0.7050 ) * 0.8550 = 0.521 in²


36

Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.3125² * 0.8550 + ( 0.3125 )² * 0.8550 = 0.167 in² M.A.W.P. Results for this Nozzle (Based on Areas and UG-45) at this Location Approximate M.A.W.P. for given geometry 96.052 psig Note: The MAWP of this junction was limited by the Areas. Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 75.50 / 285.00 = 0.265 Weld Size Calculations, Description: B - 6" Pipe Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in Note : Checking Nozzle in the Latitudinal direction. NOZZLE CALCULATION, Description: B - 6" Pipe ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 6.625 in. Actual Nozzle Thickness Used in Calculation 0.432 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (75.50*95.4360*1.00)/( 2*20000.00*1.00-0.2*75.50) = 0.1802 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (75.50*3.3125)/(17100*1.00+0.4*75.50) = 0.0146 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 11.5220 in Effective material thickness limit, no pad Tlnp 0.7050 in Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 1.061 NA NA in²


37

Area in Shell A1 0.574 NA NA in² Area in Nozzle Wall A2 0.503 NA NA in² Area in Inward Nozzle A3 0.521 NA NA in² Area in Welds A4 0.167 NA NA in² Area in Pad A5 0.000 NA NA in² TOTAL AREA AVAILABLE Atot 1.765 NA NA in² The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 90.00 Degs. The area available without a pad is Sufficient. Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (5.7610*0.1802+2*(0.4320-0.0000)*0.1802*(1-0.8550)) = 1.061 in² Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (11.522-5.761)*(1.00*(0.2820-0.000)-0.180)-2*(0.432-0.000) *(1.00*(0.2820-0.0000)-0.1802)*(1-0.8550) = 0.574 in² Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.705 ,4.000 ) ) * ( 0.4320 - 0.0000 - 0.0146 ) * 0.8550 ) = 0.503 in² Area Available in Nozzle Penetration [A3]: = 2*(Tn-Can-Can)*(min(H-Can,Tl, 2.5*Tn-Can-Can))*fr2 = 2 * ( 0.4320 ) * ( 0.7050 ) * 0.8550 = 0.521 in² Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.3125² * 0.8550 + ( 0.3125 )² * 0.8550 = 0.167 in² UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness per UG45(a), tra = 0.0146 in Wall Thickness per UG16(b), tr16b = 0.0625 in Wall Thickness per UG45(b)(1), trb1 = 0.1802 in Check UG16(b) Min. Thickness, trb1 = Max(trb1, tr16b) = 0.1802 in Std. Wall Pipe per UG45(b)(4), trb4 = 0.2450 in Wall Thickness per UG45(b), trb = Min(trb1, trb4) = 0.1802 in Final Required Thickness, tr45 = Max(tra, trb) = 0.1802 in Available Nozzle Neck Thickness = .875 * 0.4320 = 0.3780 in --> OK M.A.W.P. Results for this Nozzle (Based on Areas and UG-45) at this Location Approximate M.A.W.P. for given geometry 96.939 psig Note: The MAWP of this junction was limited by the shell (minus static head). Weld Size Calculations, Description: B - 6" Pipe Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in Results Per UW-16.1: Required Thickness Actual Thickness


38

Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in The Drop for this Nozzle is : 1.5328 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 5.8404 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. C - 6" Pipe Nozl: 13 10:53a Oct 27,2008

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INPUT VALUES, Nozzle Description: C - 6" Pipe From : 30 Pressure for Nozzle Reinforcement Calculations P 78.348 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Elliptical Head D 95.4360 in Aspect Ratio of Elliptical Head Ar 2.00 Head Actual Thickness T 0.2820 in Head Internal Corrosion Allowance Cas 0.0000 in Head External Corrosion Allowance Caext 0.0000 in Physical Maximum for Nozzle Diameter Limit Dmax 10.0000 in Physical Maximum for Nozzle Thickness Limit Tmax 0.0000 in Distance from Head Centerline L1 45.0000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-106 B Nozzle Allowable Stress at Temperature Sn 17100.00 psi Nozzle Allowable Stress At Ambient Sna 17100.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 180.00 deg Nozzle Diameter Dia 6.0000 in. Nozzle Size and Thickness Basis Idbn Nominal Nominal Thickness of Nozzle Thknom 80 Nozzle Flange Material SA-105 Nozzle Flange Type Slip on Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 4.0000 in Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in Groove weld depth between Nozzle and Vessel Wgnv 0.2820 in Nozzle Inside Projection H 0.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.0000 in Pad Material SA-516 70 Pad Allowable Stress at Temperature Sp 20000.00 psi Pad Allowable Stress At Ambient Spa 20000.00 psi Diameter of Pad along vessel surface Dp 12.0000 in Thickness of Pad Tp 0.3125 in Weld leg size between Pad and Shell Wp 0.2500 in Groove weld depth between Pad and Nozzle Wgpn 0.0000 in Reinforcing Pad Width 2.6875 in ASME Code Weld Type per UW-16 None User Defined Nozzle/Shell Centerline Angle 90.0000 deg. Class of attached Flange 150 Grade of attached Flange GR 1.1 The Pressure Design option was Design Pressure + static head


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Nozzle Sketch | | | | | | | | __________/| | ____/|__________\| | | \ | | | \ | | |________________\|__| Insert Nozzle With Pad, no Inside projection NOZZLE CALCULATION, Description: C - 6" Pipe ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 6.625 in. Actual Nozzle Thickness Used in Calculation 0.432 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (78.35*95.4360*1.00)/( 2*20000.00*1.00-0.2*78.35) = 0.1870 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (78.35*3.3125)/(17100*1.00+0.4*78.35) = 0.0151 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 12.3542 in Effective material thickness limit, no pad Tlnp 0.7050 in Effective material thickness limit, pad side Tlwp 0.7050 in Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 1.354 NA NA in² Area in Shell A1 0.486 NA NA in² Area in Nozzle Wall A2 0.503 NA NA in² Area in Inward Nozzle A3 0.000 NA NA in² Area in Welds A4 0.083 NA NA in² Area in Pad A5 1.303 NA NA in² TOTAL AREA AVAILABLE Atot 2.375 NA NA in² The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 54.04 Degs. The area available without a pad is Insufficient. The area available with the given pad is Sufficient. SELECTION OF POSSIBLE REINFORCING PADS: Diameter Thickness Based on given Pad Thickness: 7.6250 0.3125 in Based on given Pad Diameter: 12.0000 0.1250 in Based on Shell or Nozzle Thickness: 9.1250 0.3125 in Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (7.1172*0.1870+2*(0.4320-0.0000)*0.1870*(1-0.8550)) = 1.354 in²


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Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (12.354-7.117)*(1.00*(0.2820-0.000)-0.187)-2*(0.432-0.000) *(1.00*(0.2820-0.0000)-0.1870)*(1-0.8550) = 0.486 in² Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.705 ,4.000 ) ) * ( 0.4320 - 0.0000 - 0.0151 ) * 0.8550 ) = 0.503 in² Area Available in Nozzle Wall, with Pad [A2wp]: = ( 2 * min(Tlwp, ho) )*( Thk - Can - Trn )* fr2 = ( 2 * min(0.705 ,4.000 ) ) * ( 0.4320 - 0.0000 - 0.0151 ) * 0.8550 ) = 0.503 in² Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.3125² * 0.8550 + ( 0.0000 )² * 0.8550 = 0.083 in² Area Available in Welds, with Pad [A4wp]: = Wo²*fr3+(Wi-Can/0.707)²*Fr2+Wp²*Fr4 = 0.3125² *0.86 + (0.0000 )² *0.86 + 0.0000² * 1.00 = 0.083 in² Area Available in Pad [A5]: = (min(Dp,DL)-(Nozzle OD))*(min(Tp,Tlwp,Te))*fr4 = ( 12.3542 - 8.1846 ) * 0.3125 * 1.0000 = 1.303 in² UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness per UG45(a), tra = 0.0151 in Wall Thickness per UG16(b), tr16b = 0.0625 in Wall Thickness per UG45(b)(1), trb1 = 0.1870 in Check UG16(b) Min. Thickness, trb1 = Max(trb1, tr16b) = 0.1870 in Std. Wall Pipe per UG45(b)(4), trb4 = 0.2450 in Wall Thickness per UG45(b), trb = Min(trb1, trb4) = 0.1870 in Final Required Thickness, tr45 = Max(tra, trb) = 0.1870 in Available Nozzle Neck Thickness = .875 * 0.4320 = 0.3780 in --> OK M.A.W.P. Results for this Nozzle (Based on Areas and UG-45) at this Location Approximate M.A.W.P. for given geometry 96.960 psig Note: The MAWP of this junction was limited by the shell (minus static head). Minimum Design Metal Temperature Results: Nozzle Pad Minimum Temp. w/o impact per UCS-66 -20 -20 F Minimum Temp. at required thickness -155 -54 F Minimum Temp. w/o impact per UG-20(f) -20 -20 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F


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Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 78.35 / 285.00 = 0.275 Weld Size Calculations, Description: C - 6" Pipe Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in Intermediate Calc. for pad/shell Welds TminPad 0.3125 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in Pad Weld 0.1562 = 0.5*TminPad 0.1768 = 0.7 * Wp in Weld Strength and Weld Loads per UG-41.1, Sketch (a) or (b) Weld Load [W]: = (Ar-A1+2*(Thk-can)*Ffr1*(E1(T-Cas)-Tr))*S = (1.3544 - 0.4856 + 2 * ( 0.4320 - 0.0000 ) * 0.8550 * (1.00 * ( 0.2820 - 0.0000 ) - 0.1870 ) ) * 20000 = 18779.39 lbf Weld Load [W1]: = (A2+A5+A4-(Wi-Can/.707)²*Ffr2)*S = ( 0.5025 + 1.3030 + 0.0835 - 0.0000 * 0.86 ) * 20000 = 37780.18 lbf Weld Load [W2]: = ((A2+A6)+A3+A4+(2*(Thk-Can)*(T-Ca)*Fr1))*S = ( 0.5025 + 0.0000 + 0.0835 + 0.2083 ) * 20000 = 15886.99 lbf Weld Load [W3]: = ((A2+A6)+A3+A4+A5+(2*(Thk-Can)*(T-Ca)*Fr1))*S = ( 0.5025 + 0.0000 + 0.0835 + 1.3030 + 0.2083 ) * 20000 = 41946.56 lbf Strength of Connection Elements for Failure Path Analysis Shear, Outward Nozzle Weld [Sonw]: = (pi/2) * Dlo * Wo * 0.49 * Snw = ( 3.1416 / 2.0 ) * 8.1846 * 0.3125 * 0.49 * 17100 = 33664. lbf Shear, Pad Element Weld [Spew]: = (pi/2) * DP * WP * 0.49 * SEW = ( 3.1416 / 2.0 ) * 12.0000 * 0.2500 * 0.49 * 20000 = 46181. lbf Shear, Nozzle Wall [Snw]: = (pi *( Dlr + Dlo )/4 ) * ( Thk - Can ) * 0.7 * Sn = (3.1416 * 3.8255 ) * ( 0.4320 - 0.0000 ) * 0.7 * 17100 = 62146. lbf Tension, Nozzle Groove Weld [Tngw]: = (PI/2) * Dlo * (Wgnvi-Cas) * 0.74 * Sng = ( 3.1416 / 2.0 ) * 8.1846 * ( 0.2820 - 0.0000 ) * 0.74 * 17100 = 45877. lbf Strength of Failure Paths: PATH11 = ( SPEW + SNW ) = ( 46181 + 62145 ) = 108327 lbf PATH22 = ( Sonw + Tpgw + Tngw + Sinw ) = ( 33663 + 0 + 45877 + 0 ) = 79540 lbf


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PATH33 = ( Spew + Tngw + Sinw ) = ( 46181 + 45877 + 0 ) = 92058 lbf Summary of Failure Path Calculations: Path 1-1 = 108327 lbf, must exceed W = 18779 lbf or W1 = 37780 lbf Path 2-2 = 79540 lbf, must exceed W = 18779 lbf or W2 = 15886 lbf Path 3-3 = 92058 lbf, must exceed W = 18779 lbf or W3 = 41946 lbf The Drop for this Nozzle is : 0.0637 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 4.3457 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. D - 12x16 MWY Nozl: 9 10:53a Oct 27,2008

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INPUT VALUES, Nozzle Description: D - 12x16 MWY From : 10 Pressure for Nozzle Reinforcement Calculations P 77.863 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Elliptical Head D 95.4360 in Aspect Ratio of Elliptical Head Ar 2.00 Head Actual Thickness T 0.2820 in Head Internal Corrosion Allowance Cas 0.0000 in Head External Corrosion Allowance Caext 0.0000 in Distance from Head Centerline L1 31.0000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-106 B Nozzle Allowable Stress at Temperature Sn 17100.00 psi Nozzle Allowable Stress At Ambient Sna 17100.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 180.00 deg Nozzle Diameter Dia 17.5000 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.7500 in Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 2.0000 in Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in Groove weld depth between Nozzle and Vessel Wgnv 0.2820 in Nozzle Inside Projection H 1.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.3125 in ASME Code Weld Type per UW-16 C The Pressure Design option was Design Pressure + static head Nozzle Sketch | | | | | | | | ____________/| | | \ | | | \ | | |____________\| | \| | |__| Insert Nozzle No Pad, with Inside projection NOZZLE CALCULATION, Description: D - 12x16 MWY ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45


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Actual Nozzle Outside Diameter Used in Calculation 17.500 in. Actual Nozzle Thickness Used in Calculation 0.750 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (77.86*95.4360*1.00)/( 2*20000.00*1.00-0.2*77.86) = 0.1858 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (77.86*8.7500)/(17100*1.00+0.4*77.86) = 0.0398 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 32.0000 in Effective material thickness limit, no pad Tlnp 0.7050 in Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 3.014 NA NA in² Area in Shell A1 1.518 NA NA in² Area in Nozzle Wall A2 0.856 NA NA in² Area in Inward Nozzle A3 0.904 NA NA in² Area in Welds A4 0.167 NA NA in² Area in Pad A5 0.000 NA NA in² TOTAL AREA AVAILABLE Atot 3.445 NA NA in² The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 90.00 Degs. The area available without a pad is Sufficient. Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (16.0000*0.1858+2*(0.7500-0.0000)*0.1858*(1-0.8550)) = 3.014 in² Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (32.000-16.000)*(1.00*(0.2820-0.000)-0.186)-2*(0.750-0.000) *(1.00*(0.2820-0.0000)-0.1858)*(1-0.8550) = 1.518 in² Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.705 ,2.000 ) ) * ( 0.7500 - 0.0000 - 0.0398 ) * 0.8550 ) = 0.856 in² Area Available in Nozzle Penetration [A3]: = 2*(Tn-Can-Can)*(min(H-Can,Tl, 2.5*Tn-Can-Can))*fr2 = 2 * ( 0.7500 ) * ( 0.7050 ) * 0.8550 = 0.904 in² Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.3125² * 0.8550 + ( 0.3125 )² * 0.8550 = 0.167 in²


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UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness per UG45(a), tra = 0.0398 in Wall Thickness per UG16(b), tr16b = 0.0625 in Wall Thickness per UG45(b)(1), trb1 = 0.1858 in Check UG16(b) Min. Thickness, trb1 = Max(trb1, tr16b) = 0.1858 in Std. Wall Pipe per UG45(b)(4), trb4 = 0.3281 in Wall Thickness per UG45(b), trb = Min(trb1, trb4) = 0.1858 in Final Required Thickness, tr45 = Max(tra, trb) = 0.1858 in Available Nozzle Neck Thickness = 0.7500 in --> OK M.A.W.P. Results for this Nozzle (Based on Areas and UG-45) at this Location Approximate M.A.W.P. for given geometry 83.461 psig Note: The MAWP of this junction was limited by the Areas. Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 16 F Minimum Temp. at required thickness -124 F Minimum Temp. w/o impact per UG-20(f) -20 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 77.86 / 285.00 = 0.273 Weld Size Calculations, Description: D - 12x16 MWY Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in The Drop for this Nozzle is : 0.4457 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 3.2820 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. E - 12x16 MWY Nozl: 14 10:53a Oct 27,2008

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INPUT VALUES, Nozzle Description: E - 12x16 MWY From : 30 Pressure for Nozzle Reinforcement Calculations P 75.604 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Elliptical Head D 95.4360 in Aspect Ratio of Elliptical Head Ar 2.00 Head Actual Thickness T 0.2820 in Head Internal Corrosion Allowance Cas 0.0000 in Head External Corrosion Allowance Caext 0.0000 in Distance from Head Centerline L1 31.0000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-106 B Nozzle Allowable Stress at Temperature Sn 17100.00 psi Nozzle Allowable Stress At Ambient Sna 17100.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 0.00 deg Nozzle Diameter Dia 17.5000 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.7500 in Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 2.0000 in Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in Groove weld depth between Nozzle and Vessel Wgnv 0.2820 in Nozzle Inside Projection H 1.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.3125 in ASME Code Weld Type per UW-16 C The Pressure Design option was Design Pressure + static head Nozzle Sketch | | | | | | | | ____________/| | | \ | | | \ | | |____________\| | \| | |__| Insert Nozzle No Pad, with Inside projection NOZZLE CALCULATION, Description: E - 12x16 MWY ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45


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Actual Nozzle Outside Diameter Used in Calculation 17.500 in. Actual Nozzle Thickness Used in Calculation 0.750 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*D*K)/(2*S*E-0.2*P) Appendix 1-4(c) = (75.60*95.4360*1.00)/( 2*20000.00*1.00-0.2*75.60) = 0.1805 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (75.60*8.7500)/(17100*1.00+0.4*75.60) = 0.0386 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 35.2287 in Effective material thickness limit, no pad Tlnp 0.7050 in Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 3.218 NA NA in² Area in Shell A1 1.767 NA NA in² Area in Nozzle Wall A2 0.858 NA NA in² Area in Inward Nozzle A3 0.904 NA NA in² Area in Welds A4 0.167 NA NA in² Area in Pad A5 0.000 NA NA in² TOTAL AREA AVAILABLE Atot 3.695 NA NA in² The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 65.28 Degs. The area available without a pad is Sufficient. Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (17.6144*0.1805+2*(0.7500-0.0000)*0.1805*(1-0.8550)) = 3.218 in² Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (35.229-17.614)*(1.00*(0.2820-0.000)-0.180)-2*(0.750-0.000) *(1.00*(0.2820-0.0000)-0.1805)*(1-0.8550) = 1.767 in² Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.705 ,2.000 ) ) * ( 0.7500 - 0.0000 - 0.0386 ) * 0.8550 ) = 0.858 in² Area Available in Nozzle Penetration [A3]: = 2*(Tn-Can-Can)*(min(H-Can,Tl, 2.5*Tn-Can-Can))*fr2 = 2 * ( 0.7500 ) * ( 0.7050 ) * 0.8550 = 0.904 in² Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.3125² * 0.8550 + ( 0.3125 )² * 0.8550 = 0.167 in²


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UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness per UG45(a), tra = 0.0386 in Wall Thickness per UG16(b), tr16b = 0.0625 in Wall Thickness per UG45(b)(1), trb1 = 0.1805 in Check UG16(b) Min. Thickness, trb1 = Max(trb1, tr16b) = 0.1805 in Std. Wall Pipe per UG45(b)(4), trb4 = 0.3281 in Wall Thickness per UG45(b), trb = Min(trb1, trb4) = 0.1805 in Final Required Thickness, tr45 = Max(tra, trb) = 0.1805 in Available Nozzle Neck Thickness = 0.7500 in --> OK M.A.W.P. Results for this Nozzle (Based on Areas and UG-45) at this Location Approximate M.A.W.P. for given geometry 81.243 psig Note: The MAWP of this junction was limited by the Areas. Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 16 F Minimum Temp. at required thickness -124 F Minimum Temp. w/o impact per UG-20(f) -20 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 75.60 / 285.00 = 0.265 Weld Size Calculations, Description: E - 12x16 MWY Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in The Drop for this Nozzle is : 0.4457 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 3.2820 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. F - 12x16 MWY Nozl: 11 10:53a Oct 27,2008

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INPUT VALUES, Nozzle Description: F - 12x16 MWY From : 20 Pressure for Nozzle Reinforcement Calculations P 77.962 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Cylindrical Shell D 95.3750 in Shell Actual Thickness T 0.3125 in Shell Internal Corrosion Allowance Cas 0.0000 in Shell External Corrosion Allowance Caext 0.0000 in Distance from Bottom/Left Tangent 61.5000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-106 B Nozzle Allowable Stress at Temperature Sn 17100.00 psi Nozzle Allowable Stress At Ambient Sna 17100.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 135.00 deg Nozzle Diameter Dia 17.5000 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.7500 in Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 2.0000 in Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in Groove weld depth between Nozzle and Vessel Wgnv 0.3125 in Nozzle Inside Projection H 1.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.3125 in ASME Code Weld Type per UW-16 C This is a Manway or Access Opening. The Pressure Design option was Design Pressure + static head Nozzle Sketch | | | | | | | | ____________/| | | \ | | | \ | | |____________\| | \| | |__| Insert Nozzle No Pad, with Inside projection NOZZLE CALCULATION, Description: F - 12x16 MWY ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45


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Actual Nozzle Outside Diameter Used in Calculation 17.500 in. Actual Nozzle Thickness Used in Calculation 0.750 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (77.96*47.6875)/(20000*1.00-0.6*77.96) = 0.1863 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (77.96*8.7500)/(17100*1.00+0.4*77.96) = 0.0398 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 32.0000 in Effective material thickness limit, no pad Tlnp 0.7812 in Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 3.022 NA NA in² Area in Shell A1 1.991 NA NA in² Area in Nozzle Wall A2 0.949 NA NA in² Area in Inward Nozzle A3 1.002 NA NA in² Area in Welds A4 0.167 NA NA in² Area in Pad A5 0.000 NA NA in² TOTAL AREA AVAILABLE Atot 4.109 NA NA in² The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 90.00 Degs. The area available without a pad is Sufficient. Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (16.0000*0.1863+2*(0.7500-0.0000)*0.1863*(1-0.8550)) = 3.022 in² Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (32.000-16.000)*(1.00*(0.3125-0.000)-0.186)-2*(0.750-0.000) *(1.00*(0.3125-0.0000)-0.1863)*(1-0.8550) = 1.991 in² Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.781 ,2.000 ) ) * ( 0.7500 - 0.0000 - 0.0398 ) * 0.8550 ) = 0.949 in² Area Available in Nozzle Penetration [A3]: = 2*(Tn-Can-Can)*(min(H-Can,Tl, 2.5*Tn-Can-Can))*fr2 = 2 * ( 0.7500 ) * ( 0.7812 ) * 0.8550 = 1.002 in² Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.3125² * 0.8550 + ( 0.3125 )² * 0.8550 = 0.167 in²


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M.A.W.P. Results for this Nozzle (Based on Areas and UG-45) at this Location Approximate M.A.W.P. for given geometry 87.917 psig Note: The MAWP of this junction was limited by the shell (minus static head). Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 16 F Minimum Temp. at required thickness -124 F Minimum Temp. w/o impact per UG-20(f) -20 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 77.96 / 285.00 = 0.274 Weld Size Calculations, Description: F - 12x16 MWY Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in The Drop for this Nozzle is : 0.8096 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 3.3125 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. G - 1.5" 3000# Nozl: 12 10:53a Oct 27,2008

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INPUT VALUES, Nozzle Description: G - 1.5" 3000# From : 20 Pressure for Nozzle Reinforcement Calculations P 78.467 psig Temperature for Internal Pressure Temp 150 F Shell Material SA-516 70 Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Cylindrical Shell D 95.3750 in Shell Actual Thickness T 0.3125 in Shell Internal Corrosion Allowance Cas 0.0000 in Shell External Corrosion Allowance Caext 0.0000 in Distance from Bottom/Left Tangent 61.5000 in User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-105 Nozzle Allowable Stress at Temperature Sn 20000.00 psi Nozzle Allowable Stress At Ambient Sna 20000.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 180.00 deg Nozzle Diameter Dia 2.5000 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.3000 in Nozzle Corrosion Allowance Can 0.0000 in Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 1.1875 in Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in Groove weld depth between Nozzle and Vessel Wgnv 0.3125 in Nozzle Inside Projection H 0.0000 in Weld leg size, Inside Nozzle to Shell Wi 0.0000 in ASME Code Weld Type per UW-16 Z-1 The Pressure Design option was Design Pressure + static head Nozzle Sketch | | | | | | | | ____________/| | | \ | | | \ | | |____________\|__| Insert Nozzle No Pad, no Inside projection NOZZLE CALCULATION, Description: G - 1.5" 3000# ASME Code, Section VIII, Division 1, 2007, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 2.500 in. Actual Nozzle Thickness Used in Calculation 0.300 in.

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Calcs. G - 1.5" 3000# Nozl: 12 10:53a Oct 27,2008

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Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1) = (78.47*47.6875)/(20000*1.00-0.6*78.47) = 0.1875 in Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (78.47*1.2500)/(20000*1.00+0.4*78.47) = 0.0049 in UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 3.8000 in Effective material thickness limit, no pad Tlnp 0.7500 in Note: Taking a UG-36(c)(3)(a) exemption for G - 1.5" 3000# . This calculation is valid for nozzles that meet all the requirements of paragraph UG-36. Please check the Code carefully, especially for nozzles that are not isolated or do not meet Code spacing requirements. It may be necessary to force the program to print the areas per UG-37. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness per UG45(a), tra = 0.0049 in Wall Thickness per UG16(b), tr16b = 0.0625 in Wall Thickness per UG45(b)(1), trb1 = 0.1875 in Check UG16(b) Min. Thickness, trb1 = Max(trb1, tr16b) = 0.1875 in Std. Wall Pipe per UG45(b)(4), trb4 = 0.1776 in Wall Thickness per UG45(b), trb = Min(trb1, trb4) = 0.1776 in Final Required Thickness, tr45 = Max(tra, trb) = 0.1776 in Available Nozzle Neck Thickness = 0.3000 in --> OK Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F ANSI Flange MDMT including temperature reduction per UCS-66.1: Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -20 F Flange MDMT with Temperature reduction per UCS-66(b)(1)(b) -155 F Where the Temperature Reduction per UCS-66(b)(1)(b) is: Stress ratio, P / Ambient Rating = 78.47 / 285.00 = 0.275 Weld Size Calculations, Description: G - 1.5" 3000# Intermediate Calc. for nozzle/shell Welds Tmin 0.3000 in Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2100 = 0.7 * TMIN 0.2209 = 0.7 * Wo in The Drop for this Nozzle is : 0.0164 in The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.5164 in PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Schedule Step: 17 10:53a Oct 27,2008

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Nozzle Schedule: Nominal Flange Noz. Wall Re-Pad Cut Description Size Sch/Type O/Dia Thk ODia Thick Length in. Cls in in in in in ------------------------------------------------------------------------------ A - 3/4" 3000# 1.375 - None 1.375 0.162 - - 2.00 G - 1.5" 3000# 2.500 - None 2.500 0.300 - - 1.52 B - 6" Pipe 6.000 80 SlipOn 6.625 0.432 - - 5.84 C - 6" Pipe 6.000 80 SlipOn 6.625 0.432 12.00 0.312 4.35 D - 12x16 MWY 17.500 - None 17.500 0.750 - - 3.28 F - 12x16 MWY 17.500 - None 17.500 0.750 - - 3.31 E - 12x16 MWY 17.500 - None 17.500 0.750 - - 3.28 Note on the Cut Length Calculation: The Cut Length is the Outside Projection + Inside Projection + Drop + In Plane Shell Thickness. This value does not include weld gaps, nor does it account for shrinkage. Please Note: In the case of Oblique Nozzles, the Outside Diameter must be increased. The Re-Pad WIDTH around the nozzle is calculated as follows: Width of Pad = (Pad Outside Dia. (per above) - Nozzle Outside Dia.)/2 Nozzle Material and Weld Fillet Leg Size Details: Shl Grve Noz Shl/Pad Pad OD Pad Grve Inside Nozzle Material Weld Weld Weld Weld Weld in in in in in ------------------------------------------------------------------------------ A - 3/4 SA-105 0.312 0.250 - - - G - 1.5 SA-105 0.312 0.312 - - - B - 6" SA-106 B 0.282 0.312 - - 0.312 C - 6" SA-106 B 0.282 0.312 0.250 0.000 - D - 12x SA-106 B 0.282 0.312 - - 0.312 F - 12x SA-106 B 0.312 0.312 - - 0.312 E - 12x SA-106 B 0.282 0.312 - - 0.312 Note: The Outside projections below do not include the flange thickness. Nozzle Miscellaneous Data: Elevation/Distance Layout Projection Installed In Nozzle From Datum Angle Outside Inside Component in deg. in in ---------------------------------------------------------------------------- A - 3/4" 3000# 60.000 0.00 1.69 0.00 96" OD Shell G - 1.5" 3000# 60.000 180.00 1.19 0.00 96" OD Shell B - 6" Pipe 0.00 4.00 1.00 Semi Ellipti C - 6" Pipe 180.00 4.00 0.00 Semi Ellipti D - 12x16 MWY 180.00 2.00 1.00 Semi Ellipti F - 12x16 MWY 60.000 135.00 2.00 1.00 96" OD Shell E - 12x16 MWY 0.00 2.00 1.00 Semi Ellipti PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Nozzle Summary Step: 18 10:53a Oct 27,2008

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Nozzle Calculation Summary Description Internal Ext MAPNC UG45 [tr] Weld Areas psig psig Path --------------------------------------------------------------------------- B - 6" Pipe 95.55 ... ... OK 0.180 OK Passed B - 6" Pipe 96.94 ... ... OK 0.180 OK Passed D - 12x16 MWY 80.60 ... ... OK 0.186 OK Passed A - 3/4" 3000# 5220.88 ... ... OK 0.123 OK Passed F - 12x16 MWY 87.92 ... ... ... OK Passed G - 1.5" 3000# 5309.73 ... ... OK 0.178 OK Passed C - 6" Pipe 96.96 ... ... OK 0.187 OK Passed E - 12x16 MWY 80.64 ... ... OK 0.180 OK Passed --------------------------------------------------------------------------- Min. - Nozzles 80.60 D - 12x16 Min. Shell&Flgs 87.92 20 30 91.38 Computed Vessel M.A.W.P. 80.60 psig Note: MAWPs (Internal Case) shown above are at the High Point. Warning: A Nozzle Reinforcement is governing the MAWP of this Vessel. Check the Spatial Relationship between the Nozzles From Node Nozzle Description X Coordinate, Layout Angle, Dia. Limit 10 B - 6" Pipe 0.000 0.000 11.522 10 D - 12x16 MWY 0.000 180.000 32.000 20 A - 3/4" 3000# 61.500 0.000 2.100 20 F - 12x16 MWY 61.500 135.000 32.000 20 G - 1.5" 3000# 61.500 180.000 3.800 30 C - 6" Pipe 0.000 180.000 12.354 30 E - 12x16 MWY 0.000 0.000 35.229 The nozzle spacing is computed by the following: = Sqrt( ll² + lc² ) where ll - Arc length along the inside vessel surface in the long. direction. lc - Arc length along the inside vessel surface in the circ. direction If any interferences/violations are found, they will be noted below. No interference violations have been detected ! PV Elite 2008 ©1993-2008 by COADE Engineering Software

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Vessel Design Summary Step: 19 10:53a Oct 27,2008

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Design Code: ASME Code Section VIII Division 1, 2007 Diameter Spec : 96.000 in OD Vessel Design Length, Tangent to Tangent 123.00 in Specified Datum Line Distance 1.50 in Shell/Head Matl SA-516 70 Nozzle Material SA-106 B Nozzle Material SA-105 Re-Pad Material SA-516 70 Internal Design Temperature 150 F Internal Design Pressure 75.00 psig External Design Temperature 150 F Maximum Allowable Working Pressure 80.60 psig External Max. Allowable Working Pressure 10.69 psig Hydrostatic Test Pressure 98.00 psig Required Minimum Design Metal Temperature -20 F Warmest Computed Minimum Design Metal Temperature -51 F Wind Design Code No Wind Loads Earthquake Design Code No Seismic Element Pressures and MAWP: psig Element Desc Internal External M.A.W.P Corr. All. Semi Elliptical Head - L 78.467 0.000 96.939 0.0000 96" OD Shell 78.467 0.000 87.917 0.0000 Semi Elliptical Head - R 78.446 0.000 96.960 0.0000 Liquid Level: 95.44 in Dens.: 62.400 lbm/ft³ Sp. Gr.: 1.000 Element "To" Elev Length Element Thk R e q d T h k Joint Eff Type in in in Int. Ext. Long Circ Ellipse 0.00 1.500 0.312 0.220 No Calc 0.85 0.70 Cylinder 120.00 120.000 0.312 0.268 No Calc 0.70 0.70 Ellipse 121.50 1.500 0.312 0.220 No Calc 0.85 0.70 Element thicknesses are shown as Nominal if specified, otherwise are Minimum Saddle Parameters: Saddle Width 10.000 in Saddle Bearing Angle 150.000 deg. Centerline Dimension 66.000 in Wear Pad Width 12.000 in Wear Pad Thickness 0.375 in Wear Pad Bearing Angle 150.000 deg. Distance from Saddle to Tangent 13.500 in Baseplate Length 70.000 in Baseplate Thickness 0.750 in Baseplate Width 12.000 in Number of Ribs (including outside ribs) 5 Rib Thickness 0.500 in Web Thickness 0.500 in Height of Center Web 16.880 in Summary of Maximum Saddle Loads, Operating Case : Maximum Vertical Saddle Load 34234.11 lbf

PVE Sample Vessel 3 Horizontal Retention Tank PV Elite 2008 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample Vessel 3----------------------------------- Vessel Design Summary Step: 19 10:53a Oct 27,2008

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Maximum Transverse Saddle Shear Load 0.00 lbf Maximum Longitudinal Saddle Shear Load 16178.14 lbf Summary of Maximum Saddle Loads, Hydrotest Case : Maximum Vertical Saddle Load 23111.52 lbf Maximum Transverse Saddle Shear Load 0.00 lbf Maximum Longitudinal Saddle Shear Load 0.00 lbf Weights: Fabricated - Bare W/O Removable Internals 8385.8 lbm Shop Test - Fabricated + Water ( Full ) 48337.0 lbm Shipping - Fab. + Rem. Intls.+ Shipping App. 8385.8 lbm Erected - Fab. + Rem. Intls.+ Insul. (etc) 8385.8 lbm Empty - Fab. + Intls. + Details + Wghts. 8385.8 lbm Operating - Empty + Operating Liquid (No CA) 48336.5 lbm Field Test - Empty Weight + Water (Full) 48337.0 lbm PV Elite 2008 ©1993-2008 by COADE Engineering Software

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