Job No: Example Vessels Vessel Number: Fixed Tube

1 PAGET EQUIPMENT EAST 29TH STREET MARSHFIELD, WI 54449 Date Printed: 2/27/2006 Vessel designed per the ASME Boiler & Pressure Vessel Code, Section VIII, Division 1,2004 Edition, 2005 Addendawith Advanced Pressure Vessel , Version: is ASME Code StampedJob No: Example VesselsVessel number : Fixed TubeNAMEPLATE INFORMATIONS hell MAWP: PSI and Full Vacuum at 650 FChannel MAWP: PSI at 350 FMDMT: -20 F at PSIS erial number (s): _____National Board number (s): _____Year Built: 2004 Radiography: RT 1-S, RT 1-TPostweld Heat Treated: NONE-S, NONE-TSignaturesDesigned by:_____ Date: ____/____/____ Jason DiercksPAGET EQUIPMENT 1 Job No: Example VesselsVessel number : Fixed Tube number : 1 Mark number : S1 Date Printed: 2/27/2006 Cylindrical Shell Design Information Design Temperature:650 FStatic Efficiency:100%Shell Material:SA-516 Gr 70 Factor B Chart:CS-2 Material Stress (hot):18800 PSIS hell Stress (cold):20000 PSIC orrosion Circumferential Stress:16970 PSIE xternal Corrosion Longitudinal Stress:8385 PSII nside Diameter (new) Diameter (corroded) Surface of Estimated Flooded Shell Design Metal Temperature DataMin.

2 Temperature Curve:BPressure at (b) reduction:YesMinimum Design Metal Temperature:-20 FUCS-68(c) reduction:NoComputed Minimum Temperature:-35 FExternal Pressure DataDesign Pressure (Pa) Temperature:650 FDimension Minimum Nominal L/ L/ Do/ Do/ Factor Factor Factor B:2224 PSIN ominal Factor B:2849 PSID esign Thickness CalculationsLongitudinal Stress Calculations per Paragraph UG-27(c)(2)t = PR2SE + = * * 18800 * + * = + (corrosion) + (ext. corrosion) = minimum of Stress Calculations per UG-27(c)(1)t = PRSE - * * - * = + (corrosion) + (ext. corrosion) = minimum of External Pressure Calculation per Paragraph UG-28Pa (using nominal t) = 4B3(Do / t) = 4 * 28493 * ( / ) = maximum external pressure of PSIE xtreme Fiber Elongation Calculation per Paragraph UCS-79 Elongation = 50tRf= 50 * = elongation of %Nominal Shell Thickness Selected = Pressure Vessel version: Computer Engineering, VIII, Division 1, 2004 Edition, 2005 AddendaPage 1 of 76 PAGET EQUIPMENT " InletJob No: Example VesselsVessel number : Fixed TubeNumber: 1 Mark number : N2ID number : 1 Date Printed: 2/27/2006 Nozzle Design InformationDesign Temperature:650 FStatic Efficiency (E):100%Nozzle Material:SA-106 Gr BJoint Efficiency (E1) B Chart:CS-2 External Stress at Design Temperature (Sn):17100 PSII nternal Stress at Ambient Temperature.

3 17100 PSII nside Corrosion Factor (F) Corrosion through a Category A Joint:NoNozzle Pipe Size:5 Nozzle Pipe Schedule:80 Nozzle ID (new) Wall Thickness(new) ID (corroded) Wall Thickness(corroded) "h" Weld Leg Size(Weld 41) "h" Weld Leg Size(Weld 43) , Limit of Groove Weld Design Metal TemperatureMin. Temp. Curve:BPressure at (b) reduction:YesMinimum Design Metal Temperature:-20 FUCS-68(c) reduction:NoComputed Minimum Temperature:-155 FReinforcing Pad InformationReinforcing Material:SA-516 Gr 70 Allowable Stress at Design Temperature(Sp):18800 PSIA llowable Stress at Ambient Temperature:20000 PSIR einforcing Plate Thickness(te) to Vessel Weld Leg Size(Weld 42) , Reinforcing Plate(Dp) to Nozzle Groove Weld Component: Shell 1 - Shell 1 Material:SA-516 Gr 70 Shell wall thickness(new) Stress(Sv):18800 PSIS hell wall thickness(corroded) Detail InformationUpper Weld Leg Size(Weld 41): Wall Thickness(tn): Groove Weld Depth: to Vessel Weld Leg Size(Weld 42): Thickness(te): passes through the Vessel , attached by a groove Size: 5 Schedule.

4 80 Nozzle is adequate for UG-45 is adequately reinforced for Internal is adequately reinforced for External Strength Paths are Pressure Vessel version: Computer Engineering, VIII, Division 1, 2004 Edition, 2005 AddendaPage 2 of 76 PAGET EQUIPMENT " InletJob No: Example VesselsVessel number : Fixed TubeNumber: 1 Mark number : N2ID number : 1 Date Printed: 2/27/2006 Required Shell Thickness per Paragraph UG-37(a)tr = PRSE - = * * 1 - * = Required Thickness CalculationsRequired Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)trn = PRnSE - = * * 1 - * = Nozzle Thickness for External Pressure per Paragraph UG-37(a)trn = 3 * Do * Pa4B = 3 * * * 3283 = Reduction Factorsfr1 = SnSv = 1710018800 = = SnSv = 1710018800 = = SnSv = 1710018800 = = SpSv = 1880018800 = Thickness Calculations Nozzle Thickness for Pressure Loading (plus corrosion) per Paragraph UG-45(a)t = PRnSE - + Ca + ext.

5 Ca = * * - * + + = in. Nozzle Thickness for Internal Pressure (plus corrosion) per Paragraph UG-45(b)(1)t = PRSE - + Ca + ext. Ca = * * 1 - * + + = in. Nozzle Thickness for External Pressure (plus corrosion) per Paragraph UG-45(b)(2)t = PRSE - + Ca + ext. Ca = * * 1 - * + + = Thickness for Internal and External Pressure per Paragraph UG-45(b)(3)t = Greater of the thicknesses determined by UG-45(b)(1) or UG-45(b)(2) = Thickness of Standard Wall Pipe (plus corrosion) per Paragraph UG-45(b)(4)t = minimum thickness of standard wall pipe + Ca + ext. Ca= in. Nozzle Minimum Thickness per Paragraph UG-45(b)t = Smallest of UG-45(b)(3) or UG-45(b)(4) = thickness = tn * (pipe) = is greater than or equal to UG-45 value of Pressure Vessel version: Computer Engineering, VIII, Division 1, 2004 Edition, 2005 AddendaPage 3 of 76 PAGET EQUIPMENT " InletJob No: Example VesselsVessel number : Fixed TubeNumber: 1 Mark number : N2ID number : 1 Date Printed: 2/27/2006 Nozzle Reinforcement CalculationsArea Required for Internal PressureA = d tr F + 2 tn tr F (1 - fr1) = ( * * ) + (2 * * * * (1 - )) = sq.

6 Available - Internal PressureA1 Formula 1 = d(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = * ( * - * ) - 2 * * ( * - * ) * (1 - ) = sq. Formula 2 = 2(t + tn)(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 2 * ( + )( * - * ) - 2 * * ( * - * ) * (1 - ) = sq. = Larger value of A1 Formula 1 and A1 Formula 2 = sq. Formula 1 = 5(tn - trn) fr2 t = 5( - ) * * = sq. Formula 2 = 2(tn - trn) fr2 ( tn + te ) = 2( - ) * * ( * + ) = sq. = Smaller value of A2 Formula 1 and A2 Formula 2 = sq. = Smaller value of the following : 5 * t * ti * fr2 = 5 * * * = sq. * ti * ti * fr2 = 5 * * * = sq. * h * ti * fr2 = 2 * * * sq. sq. = (leg) * fr3 = ( ) * sq. = (leg) * fr4 = ( ) * sq.

7 = (leg) * fr2 = 0 * sq. = (Dp - d - 2tn) te fr4 = ( - - 2 * ) * * sq. Available (Internal Pressure) = A1 + A2 + A3 + A41 + A42 + A43 + A5 = sq. in., which is greater than A ( )Advanced Pressure Vessel version: Computer Engineering, VIII, Division 1, 2004 Edition, 2005 AddendaPage 4 of 76 PAGET EQUIPMENT " InletJob No: Example VesselsVessel number : Fixed TubeNumber: 1 Mark number : N2ID number : 1 Date Printed: 2/27/2006 Nozzle Reinforcement CalculationsArea Required for External PressureA = * (d tr F + 2 tn tr F (1 - fr1)) = * (( * * ) + (2 * * * * (1 - ))) = sq. Available - External PressureA1 Formula 1 = d(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = * ( * - * ) - 2 * * ( * - * ) * (1 - ) = sq. Formula 2 = 2(t + tn)(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 2 * ( + )( * - * ) - 2 * * ( * - * ) * (1 - ) = sq.

8 = Larger value of A1 Formula 1 and A1 Formula 2 = sq. Formula 1 = 5(tn - trn) fr2 t = 5( - ) * * = sq. Formula 2 = 2(tn - trn) fr2 ( tn + te ) = 2( - ) * * ( * + ) = sq. = Smaller value of A2 Formula 1 and A2 Formula 2 = sq. = Smaller value of the following : 5 * t * ti * fr2 = 5 * * * = sq. * ti * ti * fr2 = 5 * * * = sq. * h * ti * fr2 = 2 * * * sq. sq. = (leg) * fr3 = ( ) * sq. = (leg) * fr4 = ( ) * sq. = (leg) * fr2 = 0 * sq. = (Dp - d - 2tn) te fr4 = ( - - 2 * ) * * sq. Available (External Pressure) = A1 + A2 + A3 + A41 + A42 + A43 + A5 = sq. in., which is greater than A ( )Advanced Pressure Vessel version: Computer Engineering, VIII, Division 1, 2004 Edition, 2005 AddendaPage 5 of 76 PAGET EQUIPMENT " InletJob No: Example VesselsVessel number : Fixed TubeNumber: 1 Mark number : N2ID number : 1 Date Printed: 2/27/2006 Nozzle Weld Strength CalculationsAttachment Weld Strength per Paragraph UW-16 Weld 41 tmin = smaller of , te, or tn = smaller of , , or = 41 Leg min.

9 = (smaller of or (tmin * )) + ext. = = 41, actual weld leg = 42 tmin = smaller of , t, or te = smaller of , , or = 42 Leg min. = * tmin + ext. = * + = 42, actual weld leg = Stresses per Paragraphs UG-45(c) and UW-15 Nozzle wall in shear = * Sn = * 17100 = 11970 PSIU pper fillet, Weld 41, in shear = * Material Stress = * 17100 = 8379 PSIV essel groove weld, in tension = * Material Stress = * 17100 = 12654 PSIO uter fillet, Weld 42, in shear = * Material Stress = * 18800 = 9212 PSIR epad groove weld, in tension = * Material Stress = * 17100 = 12654 PSIS trength of Connection ElementsNozzle wall in shear = * m * mean nozzle diameter * tn * Nozzle wall in shear unit stress = * m * * * 11970 = 30800 fillet in shear = * m * Nozzle OD * weld leg * upper fillet in shear unit stress = * m * * * 8379 = 18300 Weld in Tension = * m * Nozzle OD * groove depth * groove weld tension unit stress = * m * * * 12654 = 27600 fillet in shear = * m * Plate OD * weld leg * outer fillet in shear unit stress = * m * * * 9212 = 20700 groove weld = * m * Nozzle OD * Groove Depth * repad groove weld in tension unit stress = * m * * * 12654 = 27600 to be carried by welds, per UG-41(b)(1) and Fig.

10 Sketch (a)W = [A - A1 + 2 tn fr1(E1t - Ftr)] Sv = [ - + 2 * * * ( * - * )] * 18800 = 19200 = (A2 + A5 + A41 + A42) * Sv = ( + + + ) * 18800 = 19200 = (A2 + A3 + A41 + A43 + 2 tn t fr1) Sv = ( + + + + 2 * * * ) * 18800 = 9800 = (A2 + A3 + A5 + A41 + A42 + A43 + 2 tn t fr1) * Sv = ( + + + + + + 2 * * * ) * 18800 = 21900 Strength PathsPath 1-1 = Outer fillet in shear + Nozzle wall in shear = 20700 + 30800 = 51500 2-2 = Upper fillet in shear + Repad groove weld + Groove weld in tension + Inner fillet in shear = 18300 + 27600 + 27600 + 0 = 73500 3-3 = Outer fillet in shear + Inner fillet in shear + Groove weld in tension = 20700 + 0 + 27600 = 48300 Pressure Vessel version: Computer Engineering, VIII, Division 1, 2004 Edition, 2005 AddendaPage 6 of 76 PAGET EQUIPMENT " InletJob No: Example VesselsVessel number : Fixed TubeNumber: 1 Mark number : N2ID number : 1 Date Printed: 2/27/2006 Plate Strength = A5 * Sp = * 18800 = 11455 fillet weld strength(20700) is greater than plate strength(11455).