asme tubesheet (heater 10m2)

Equipment : Heater 10m2ASME TS Calc : ASME Tubesheet 1

Input Echo, Tubesheet Number 1, Description: ASME TubesheetShell Data:Shell Design Pressure Ps 3.00 kgf/cm^2Shell Operating Pressure Psox 1.00 kgf/cm^2Shell Thickness ts 10.0000 mmShell Corrosion Allowance cas 1.6000 mmInside Diameter of Shell Ds 324.000 mmShell Circumferential Joint Efficiency Esw 0.700Shell Temperature for Internal Pressure Ts 100.00 CShell Material SA-516 70

Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-516 70

Shell Material UNS Number K02700Shell Allowable Stress at Temperature Ss 1406.14 kgf/cm^2Shell Allowable Stress at Ambient 1406.14 kgf/cm^2

Channel Type: CylinderChannel Design Pressure Pt 1.00 kgf/cm^2Channel Operating Pressure Ptox 0.50 kgf/cm^2Channel Thickness tc 10.0000 mmChannel Corrosion Allowance cac 1.6000 mmInside Diameter of Channel Dc 304.000 mmChannel Design Temperature TEMPC 50.00 CChannel Material SA-516 70


Channel Material UNS Number K02700Channel Allowable Stress at Temperature Sc 1406.14 kgf/cm^2Channel Allowable Stress at Ambient 1406.14 kgf/cm^2

Tube Data:Number of Tube Holes Nt 15Tube Wall Thickness et 1.4500 mmTube Outside Diameter D 30.0000 mmTotal Straight Tube Length Lt 3006.00 mmStraight Tube Length (bet. inner tubsht faces) L 2936.00 mmDesign Temperature of the Tubes 100.00 CTube Material SA-249 TP304Tube Material UNS Number S30400Is this a Welded Tube YesTube Material Specification used Wld. tube

Note: Welded Tube Material Spec. already includes a Joint Eff. of 0.85. SinceUHX checks Long. Tube stress, Jt. Eff. of long. seam is not applicable.Increasing the Tube allowables by dividing by 0.85 for ASME UHX check.

Tube Allowable Stress at Temperature 1187.64 kgf/cm^2Tube Allowable Stress At Ambient 1195.22 kgf/cm^2Tube Allowable Stress at Temper.(for Pressure) 1187.64 kgf/cm^2Tube Allowable Stress at Temper. (for UHX) St 1397.22 kgf/cm^2


Tube Yield Stress At design Temperature Syt 1734.09 kgf/cm^2Tube Pitch (Center to Center Spacing) P 52.0000 mmTube Layout Pattern Triangular

Fillet Weld Leg af 2.0000 mmGroove Weld Leg ag 2.0000 mmTube-Tubesheet Joint Weld Type Full StrengthMethod for Tube-Tubesheet Jt. Allow. UW-20Tube-Tubesheet Joint Classification c

Radius to Outermost Tube Hole Center ro 119.000 mmLargest Center-to-Center Tube Distance Ul 0.0000 mmLength of Expanded Portion of Tube ltx 0.0000 mmTube-side pass partition groove depth hg 0.0000 mm

Tubesheet Data:

Tubesheet TYPE: Fixed Tubesheet Exchanger, Conf B

Tubesheet Design Metal Temperature T 100.00 CTubesheet Material SA-266 2


Tubesheet Material UNS Number K03506Tubesheet Allowable Stress at Temperature S 1406.14 kgf/cm^2Tubesheet Allowable Stress at Ambient Tt 1406.14 kgf/cm^2Thickness of Tubesheet h 35.0000 mmTubesheet Corr. Allowance (Shell side) Cats 1.6000 mmTubesheet Corr. Allowance (Channel side) Catc 1.6000 mmTubesheet Outside Diameter A 483.000 mm

Additional Data for Stepped Tubesheets:Is the Tubesheet Stepped? NO

Area of the Untubed Lanes AL 0.0 cm^2

Additional Data for Fixed/Floating Tubesheet Exchangers:Unsupported Tube Span under consideration l 1460.000 mmTube End condition corresponding to Span (l) k 0.80Tubesheet Metal Temp. at Rim T' 100.00 CShell Metal Temp. at Tubesheet T'S 100.00 CChannel Metal Temp. at Tubesheet T'C 50.00 CPerform Differential Pressure Design NRun Multiple Load Cases YESShell Side Vacuum Pressure Pexts 3.0000 kgf/cm^2Channel Side Vacuum Pressure Pextc 1.0550 kgf/cm^2

Mean Shell Metal Temp. along Shell len. Tsm 49.75 CMean Tube Metal Temp. along Tube length Ttm 37.50 CJunction Stress Reduction option Perform Plastic Calculation

Additional Data for Gasketed Tubesheets:Tubesheet Gasket on which Side ChannelFlange Outside Diameter A 483.000 mmFlange Inside Diameter B 304.000 mm


Flange Face Outside Diameter Fod 380.000 mmFlange Face Inside Diameter Fid 325.000 mmGasket Outside Diameter Go 379.000 mmGasket Inside Diameter Gi 329.000 mmGasket Factor, m 2.00Gasket Design Seating Stress y 112.49 kgf/cm^2Flange Facing Sketch Code Sketch 1bColumn for Gasket Seating Code Column IIGasket Thickness tg 3.0000 mmFull face Gasket Flange Option Program Selects

Bolting Information:Diameter of Bolt Circle C 431.800 mmNominal Bolt Diameter dB 24.0000 mmType of Thread Series TEMA Metric ThreadNumber of Bolts n 12Bolt Material SA-193 B7Bolt Material UNS Number G41400Bolt Allowable Stress At Temperature Sb 1757.68 kgf/cm^2Bolt Allowable Stress At Ambient Sa 1757.68 kgf/cm^2Weld between Flange and Shell/Channel 0.0000 mm

Tubesheet Integral with ShellTubesheet Extended as Flange YesThickness of Extended Portion of Tubesheet Tf 27.0000 mmIs Bolt Load Transferred to the Tubesheet Yes

Is Exchanger in Creep range (skip EP, Use 3S for Sps) NO

ASME TubeSheet Results per Part UHX, 2010

Elasticity/Expansion Material Properties:

Shell - TE-1 Carbon & Low Alloy Steels, Group 1Shell - TM-1 Carbon Steels with C


TubeSheet - TE-1 Carbon & Low Alloy Steels, Group 1TubeSheet - TM-1 Carbon Steels with C


ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:= 2a + 6t/(m + 0.5)= 2 * 24.000 + 6 * 27.000 /(2.00 + 0.5)= 112.800 mm

Actual Circumferential Bolt Spacing [Bs]:= C * sin( pi / n )= 431.800 * sin( 3.142 / 12 )= 111.758 mm

ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:= max( sqrt( Bs/( 2a + t )), 1 )= max( sqrt( 111.758 /( 2 * 24.000 + 27.000 )), 1 )= 1.2207

Bolting Information for TEMA Metric Thread Series (Non Mandatory):Distance Across Corners for Nuts 47.340 mmCircular Wrench End Diameter a 0.000 mm-----------------------------------------------------------------------------

Minimum Actual Maximum-----------------------------------------------------------------------------Bolt Area, cm^2 6.468 37.530Radial distance bet. hub and bolts 28.580 43.900Radial distance bet. bolts and the edge 28.580 25.600Circumferential spacing between bolts 58.740 111.758 112.800-----------------------------------------------------------------------------

Flange Design Bolt Load, Seating Condition W : 38666.46 kgfFlange Design Bolt Load, Operating Condition Wm1: 1428.83 kgf

Results for ASME Fixed Tubesheet Calculations for Configuration b,

Results for Tubesheet Calculations Original Thickness :

UHX-13.5.1 Step 1:

Compute the Tube Expansion Depth Ratio [rho]:= ltx / h ( modified for corrosion if present )= 0.0000 / 35.0000 = 0.0000 ( must be 0


Compute the Effective Tube Pitch [p*]:= p / sqrt( 1 - 4 * min( AL * CNV_factor, 4*Do*p)/(Pi * Do^2) )= 52.0000 / sqrt( 1 - 4 * min( 0.00 *100.000 , 4*268.000 *52.000 )/ ( 3.141 * 268.000^2) )

= 52.0000 mm

Compute the Effective Ligament Efficiency for Bending [mu*]:= (p* - d*) / p* = (52.0000 - 30.0000 ) / 52.0000 = 0.4231

Compute the Ratio [Rhos]:= as / ao = 162.0000 / 134.0000 = 1.208955

Compute the Ratio [Rhoc]:= ac / ao = 180.5940 / 134.0000 = 1.347716

Compute Parameter [xt]:= 1 - Nt * (( dt - 2 * tt )/( 2 * ao ))2= 1 - 15 * ((30.0000 - 2 * 1.4500 )/(2 * 134.0000 ))2 = 0.8466

Determine Parameter [xs]:= 1 - Nt*( dt/(2*ao) )2= 1 - 15 *( 30.0000 /(2*134.0000 ) )2 = 0.8120

Determine the Value [h'g]:= Max(( hg - CATC ), 0 ) (For pressure only cases)= Max(( 0.000 - 0.000 ), 0 ) = 0.000 mm

UHX-13.5.2 Step 2:Determine the Axial Shell Stiffness [Ks]:= pi * ts( Ds + ts )Es/L= 3.1416 * 10.0000 ( 324.0000 + 10.0000 )2020629 /2936.000= 7221491.5000 kgf/c * mm

Determine the Axial Tube Stiffness [Kt]:= pi * tt( Dt - tt )Et/L= 3.1416 * 1.4500 ( 30.0000 - 1.4500 )1929230 /2936.000= 85457.8516 kgf/c * mm

Compute the Stiffness Factor [Kst]:= Ks / ( Nt * Kt ) = 7221491 / ( 15 * 85457.852 ) = 5.63357

Compute Factor [J]:= 1 / ( 1 + Ks/Kj )= 1/(1 + 7221491 /0.000 ) = 1.0000000 (= 1 if No Exp. Jt.)

Compute Shell Coefficient [betas]:= (( 12 * (1-nus^2))0.25 )/((Ds + ts) * ts )0.5= (( 12 * (1 - 0.30^2) )0.25 ) / (( 324.0000 + 10.0000 ) * 10.0000 )0.5= 0.0315 1/mm

Determine Shell Coefficient [ks]:= betas * Es * ts^3/ ( 6 * (1 - nus^2) )= 0.031 * 2020629 * 10.0003 / ( 6 * (1 - 0.300^2) )= 11640625.0000 kgf/cm^2*mm^2

Determine Shell Coefficient [Lambdas]:= (6*Ds*ks)/(h^3) * (1 + h*betas + 0.5*(h*betas)^2)


= 6*324.000 *11640625 /(35.000^3) * ( 1 + 35.000 *0.031 + 0.606 )= 1428700.8750 kgf/cm^2

Determine Shell Coefficient [deltaS]:= Ds2/(4 * Es * Ts) * ( 1 - nus/2 )= 324.0002/( 4 * 2020629 * 10.000 ) * ( 1 - 0.3 /2 )= 0.0011039830 mm/kgf/cm^2

Intermediate parameters for Tubesheet Gasketed on the Channel Side:betac, kc, deltaC, Lambdac = 0

UHX-13.5.3 Step 3:E*/E and nu* for Triangular pattern from Fig. UHX-11.3.

h/p = 0.673077 ; mu* = 0.423077E*/E = 0.498500 ; nu* = 0.260352 ; E* = 1007284. kgf/cm^2

Compute the Tube Bundle Stiffness Factor [Xa]:= ((24 *(1 - nu*2)*Nt * Et* tt* (dt - tt)* ao^2) /( E* * L * H3 ) )0.25

= ((24 *(1 - 0.2602)*15 *1929230 *1.4500 *(30.0000 - 1.4500 )*134.00002)/( 1007283 *2936.00 * 35.0003 ))0.25

= 1.3958

Values from Table UHX-13.1Zd = 0.584360 ; Zv = 0.190545 ; Zm = 0.769660Za = 0.462357E+00 ; Zw = 0.190545

UHX-13.5.4 Step 4:Compute the Diameter Ratio [K]:= A / Do = 483.0000 / 268.0000 = 1.8022

Compute Coefficient [F]:= (1 - nu*) / (E*) * ( Lambdas + Lambdac + E * ln(K) )= (1 - 0.26 ) / (1007283 ) * ( 1428700 + 0.00 +2020629 * ln(1.80 ) )

= 1.9231

Compute Parameter [Phi]:= (1 + nu*) * F = (1 + 0.2604 ) * 1.9231 = 2.4237

Compute Parameter [Q1]:= (Rhos - 1 - Phi * Zv)/(1 + Phi * Zm)= (1.2090 - 1 - 2.4237 *0.1905 )/(1 + 2.4237 *0.7697 )= -0.088250116

Compute Parameter [Qz1]:= (Zd + Q1*Zw)/2 *Xa4= (0.58436 + -0.08825 *0.19055 )/2 *1.395794 = 1.0771

Compute Parameter [Qz2]:= (Zv + Q1*Zm)/2 *Xa4= (0.19055 + -0.08825 *0.76966 )/2 *1.395794 = 0.2327

Compute Parameter [U]:= (Zw + (Rhos - 1)*Zm)*Xa4 / (1 + Phi*Zm)


= (0.1905 + (1.2090 - 1)*0.7697 )*1.395794/ (1 + 2.4237 *0.7697 )= 0.4654

UHX-13.5.5 Step 5:

Determine factor [gamab]:= ( Gc - C ) / Do (config b)= (361.1880 - 431.8000 ) / 268.0000 = -0.26348

Compute Parameter [gamma]:= 0.000 mm (For Pressure only cases)

Calculate Parameter [OmegaS]:= rhos * ks * Betas * deltaS( 1 + h * Betas )= 1.2090 * 11640625 * 0.0315 * 0.001104 ( 1 + 35.0000 * 0.0315 )= 1026.6869 mm ^2

Calculate Parameter [Omega*S]:= Ao^2* ( Rhos^2- 1 ) * ( Rhos - 1 ) / 4 - OmegaS= 134.000^2* ( 1.209^2- 1 ) * ( 1.209 - 1 ) / 4 - 1026.687= -593.7319 mm ^2

Calculate Parameter [OmegaC]:= rhoc * kc * Betac * deltaC( 1 + h * Betac )= 1.3477 * 0.00 * 0.0000 * 0.000000 ( 1 + 35.0000 * 0.0000 )= 0.0000 mm ^2

Calculate Parameter [Omega*C]:= ao^2[( Rhoc^2+1 )*( Rhoc-1 )/4 -(Rhos-1)/2]- OmegaC= 134.00000^2[( 1.34772^2+1 )*( 1.34772 -1 )/4 -(1.20896 -1)/2]- 0.00000= 2520.0190 mm ^2

Compute the Pressure [P*S]:= 0 For Pressure only cases or Configurations d,e,f,A,B,C,D

Compute the Pressure [P*C]:= 0 For Pressure only cases or Configurations b,c,d,B,C,D

UHX-13.5.6 Step 6:Compute the Pressure [P's]:= Ps * {xs + 2( 1 - xs )nut + [2/Kst(Ds/Do)^2]nus -[(rhos^2-1)/(J*Kst)]-[(1-J)/(2J*Kst)][(Dj^2-(Ds)^2)/Do^2]}

= 3.000 * {0.812 + 2( 1 - 0.812 ) 0.300 +[2/5.634 (324.000 /268.000 )^2]0.300 -[(1.209^2-1)/( 1.000 * 5.634 )] -[(1 - 1.000 )/(2 * 1.000 * 5.634 )][(0.000^2-(324.000 )^2)/268.000^2]}

= 2.9956 kgf/cm^2

Compute the Pressure [P't]:= [ xt + 2(1 - xt)nut + 1/(J * Kst) ]*Pt= [ 0.847 + 2(1 - 0.847 )0.300 +1/(1.00000 * 5.634 ) ]* 1.000

= 1.1162 kgf/cm^2

Compute the Pressure [Pgama]:= Nt * Kt * gama / ( pi * ao^2)= 15 * 85457.852 * 0.000 / (3.142 * 134.000^2) = 0.000 kgf/cm^2


Compute the Pressure [Pw]:= -gamab * U * W* / (2 * pi * ao^2)= --0.263 * 0.465 * 1428.83 / (2 * 3.142 * 134.000^2)= 0.1553 kgf/cm^2

Calculate the Pressure [Prim]:= -( U/ao^2)(Omega*S * Ps - Omega*C * Pt )= -( 0.465 / 134.000^2)(-0.920 * 3.000 - 3.906 * 1.000 )= 0.1115 kgf/cm^2

Calculate the Pressure [POmega]:= U/ao^2(OmegaS * P*s - OmegaC * P*c )= 0.465 /134.0000^2( 1.5914 * 0.0000 - 0.0000 * 0.0000 )= 0.0000 kgf/cm^2

Determine the Effective Pressure [Pe]:= J * Kst / (1 + J * Kst *(Qz1 + (Rhos - 1) * Qz2)) *(P's - P't + Pgama + Pw + Prim )

= 0.1000E+01 * 5.634 / (1 + 1.000 * 5.634 *(1.077 + (1.209 -1) * 0.233 )) * (2.996 - 1.116 + 0.000 + 0.155 + 0.111 )

= 1.6469 kgf/cm^2

UHX-13.5.7 Step 7:Determine Factor [Q2]:= [((Omega*S*Ps - Omega*C*Pt) - (Omegas*P*s - Omegac P*c))CNV_FAC +W* * gamab/(2*pi)]/(1 + Phi*Zm)

= [ ( ( -593.732 * 3.000 - 2520.019 * 1.000 ) -( 1026.687 * 0.000 - 0.000 * 0.000 ) ) * 0.010 +1428.8 * -0.263 /(2*3.141)]/(1 + 2.42374 * 0.76966 )

= -35.920410156 kgf

Calculate Factor [Q3]:= Q1 + 2 * Q2 / ( Pe * ao2 )= -0.088 + 2 * -35.920 / ( 1.647 * 134.0002 )= -0.331185

Fm Value from Table UHX-13.1 = 0.165592

The Tubesheet Bending Stress - Original Thickness [Sigma]:= (1.5 * Fm / mu* ) * (2 * ao/(H - h'g)2 * Pe= (1.5 * 0.1656 /0.4231 ) * (2 * 134.0000 /(35.000 - 0.000 ))2 * 1.65= 56.6916 kgf/cm^2

The Allowable Tubesheet Bending Stress [Sigma allowed]:= 1.5 * S = 1.5 * 1406.14 = 2109.21 kgf/cm^2

Note: Tubesheet Bending Stress is probably low, use the following req. thk:Tubesheet thickness (Incl. Corr.)= 3.8100 mmTubesheet Bending Stress = 818.1468 kgf/cm^2

UHX-13.5.8 Step 8:Shear Stress check [Tau_limit]:= 1.6 * S * MU * h / ao= 1.6 * 1406.14 * 0.423 * 35.000 / 134.00 = 248.62 kgf/cm^2


The Tubesheet Average Shear Stress - Original Thickness [Tau]:= ( 1 / ( 2*mu ) ) * ( ao/h ) * Pe= ( 1 / (2*0.423 ) ) * ( 134.0000 /35.000 ) * 1.647= 7.4518 kgf/cm^2

The Allowable Tubesheet Shear Stress [Tau allowed]:= 0.8 * S = 0.8 * 1406.14 = 1124.91 kgf/cm^2

Note: Tubesheet Shear Stress is probably low, use the following req. thk:Tubesheet thickness (Incl. Corr.)= 3.8100 mmTubesheet Shear Stress = 36.2712 kgf/cm^2

Reqd Tubesheet Thickness for Given Loadings (Including CA) [Hreqd] := Max( HreqB, HreqS ) = Max( 3.8100 , 3.8100 ) = 3.8100 mm

UHX-13.5.9 Step 9:The Ftmin and Ftmax Coefficients from Table UHX-13.2:Ftmin = 0.9892 , Ftmax = 1.0049

First Extreme Tube Axial Stress from among all the tubes [Sigmat1]:= ( (Ps * xs - Pt * xt) - Pe * Ftmin ) / ( Xt - Xs )= ( (3.00 * 0.8120 - 1.00 * 0.8466 ) - (1.647 ) * 0.989 ) /(0.8466 - 0.8120 ) )

= -1.1473 kgf/cm^2

Second Extreme value of Tube Axial Stress from among all the tubes [Sigmat2]:= ( (Ps * xs - Pt * xt) - Pe * Ftmax ) / ( Xt - Xs )= ( (3.00 * 0.8120 - 1.00 * 0.8466 ) - (1.647 ) * 1.005 ) /(0.8466 - 0.8120 ) )

= -1.8955 kgf/cm^2

Maximum Tube Axial Stress [Sigmat,max]:= MAX( |Sigmat1|, |Sigmat2| ) = 1.895 kgf/cm2

The Allowable Tube Stress, [SigmatA]= Sot = 1397.2194 kgf/cm^2

Check for Buckling as some of the Tubes are in Compression

Determine the Factor of Safety [Fs]:= Max( (3.25 - 0.25*(Zd + Q3*Zw)*Xa^4 ), 1.25 )= Max((3.25 - 0.25*(0.584 + -0.331 *0.191 )*1.396^4), 1.25 )= 2.0000 (Should be


The Buckling Allowable Stress [Stb]:= Sy,t/Fs*( 1 - Ft/(2*Ct) )= 1734 /2.00 *( 1 - 115.564 /(2*148.191 ) )= 528.969 kgf/cm^2 (Never greater than Sot)

Note: The Axial Compressive stress in Tubes is within limits.

The Largest tube-to-tubesheet Joint Load [Wt]:= Sigmat,max * Tube Area = 1.90 * 1.3005 = 2.47 kgf

Tube Weld Size Results per UW-20:Tube Strength [Ft]:= 3.1415 * t * ( do - t ) * Sa= 3.1415 * 1.450 * ( 30.000 - 1.450 ) * 1397.22 = 1817.139 kgf

Fillet Weld Strength [Ff]:= .55 * 3.1415 * af * (do + 0.67*af) * Sw (but not > Ft)= .55 * 3.1415 * 2.000 * (30.000 + 0.67*2.000 ) * 1397.22= 1513.2323 kgf

Groove Weld Strength [Fg]:= .85 * 3.1415 * ag * (do + 0.67*ag) * Sw (but not > Ft)= .85 * 3.1415 * 2.000 * (30.000 + 0.67*2.000 ) * 1397.22= 1817.1385 kgf

Max. Allow. Tube-Tubesheet Joint load, Lmax= Ft = 1817.1385 kgf

Design Strength Ratio [fd]:= 1.0000

Weld Strength Factor [fw]:= Sot / ( Min(Sot, S) ) = 1.0000

Min Weld Length [ar]:= 2 *( ( (0.75 * do)^2+ 1.07*t*(do - t)* fw * fd ) )^1/2 - .75 * do)= 1.9274 mm

Minimum Required Fillet Weld Leg afr 0.9637 mmMinimum Required Groove Weld Leg agr 0.9637 mm

Tube-Tubesheet Jt allowable, 1817.14 is >= tube strength 1817.14 kgfNote: This tube-tubesheet joint is a Full Strength joint

UHX-13.5.10 Step 10:Shell Axial Membrane Allowable Stress:= Ss * Esw = 1406.14 * 0.70 = 984.30 kgf/cm^2

Axial Membrane Stress in Shell [Sigmasm_ax]:= ao^2/((Ds+ts)*ts)* [Pe + (Rhos^2-1)(Ps-Pt)]+ as^2*Pt/((Ds+ts)*ts)= 134.000^2/((324.000 +10.0000 )*10.0000 )* [1.65 + (1.209^2-1)(3.00 -1.00 )] + 162.000^2*1.00 /((324.00 +10.0000 )* 10.00 )

= 21.6743 kgf/cm^2


UHX-13.5.11 Step 11:Note: For a given Shell thickness of 10.000 mm, the minimum Shell

length adjacent to the tubesheet should be 102.458 mm

The Shell Membrane Stress due to Joint Interaction [Sigmasm]:= ao^2/((Ds+ts)*ts)[Pe + (Rhos^2-1)(Ps-Pt)]+ as^2*Pt/((Ds+ts)*ts)= 134.000^2/((324.000 +10.0000 )*10.0000 )[1.65 + (1.209^2-1)(3.00 -1.00 )] + 162.000^2*1.00 /((324.00 +10.0000 )* 10.00 )

= 21.6743 kgf/cm^2

The Shell Bending Stress due to Joint Interaction [Sigmasb]= 6*ks/ts^2{betas[deltaS*Ps + as^2*PstarS/(Es*ts)] +6(1 - nu*^2)/(E*)(ao/h)^3(1 + h*betas/2)[Pe(Zv + Zm*Q1) +2/ao^2* Zm * Q2 ]}

= 6 * 11640625 /10.0000^2{0.031 [ 0.001 * 3.000 + 162.0000^2* 0.0000 /(20206290 ) ] +6(1 - 0.26^2)/(1007283 )(134.00 /35.00 )^3(1 + 35.00 *0.03 /2)[ 1.6 ( 0.191 + 0.770 * -0.088 ) +2/134.00^2* 0.770 * -35.920 ] }

= 36.9946 kgf/cm^2

Shell Stress Summation vs. Allowable|Sigmasm| + |Sigmasb|


ASME Code, Section VIII, Division 1, 2010

Gasket Contact Width, N = (Goc-Gic) / 2 25.000 mmBasic Gasket Width, b0 = N / 2.0 12.500 mmEffective Gasket Width, b = SQRT(b0) * 2.5 8.906 mmGasket Reaction Diameter, G = Go-2.0*b 361.188 mm

ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:= 2a + 6t/(m + 0.5)= 2 * 24.000 + 6 * 27.000 /(2.00 + 0.5)= 112.800 mm

Actual Circumferential Bolt Spacing [Bs]:= C * sin( pi / n )= 431.800 * sin( 3.142 / 12 )= 111.758 mm

ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:= max( sqrt( Bs/( 2a + t )), 1 )= max( sqrt( 111.758 /( 2 * 24.000 + 27.000 )), 1 )= 1.2207

Bolting Information for TEMA Metric Thread Series (Non Mandatory):Distance Across Corners for Nuts 47.340 mmCircular Wrench End Diameter a 0.000 mm-----------------------------------------------------------------------------

Minimum Actual Maximum-----------------------------------------------------------------------------Bolt Area, cm^2 6.468 37.530Radial distance bet. hub and bolts 28.580 43.900Radial distance bet. bolts and the edge 28.580 25.600Circumferential spacing between bolts 58.740 111.758 112.800-----------------------------------------------------------------------------

Flange Design Bolt Load, Seating Condition W : 38666.46 kgfFlange Design Bolt Load, Operating Condition Wm1: 1428.83 kgf

Results for ASME Fixed Tubesheet Calculations for Configuration b,

Results for Tubesheet Calculations Original Thickness :

UHX-13.5.1 Step 1:

Compute the Tube Expansion Depth Ratio [rho]:= ltx / h ( modified for corrosion if present )= 0.0000 / 31.8000 = 0.0000 ( must be 0


Determine the Basic Ligament Efficiency for Shear [mu]:= (p - dt)/p = (52.0000 - 30.0000 )/52.0000 = 0.4231

Compute the Equivalent Outer Tube Limit Radius [ao]:= Do / 2 = 268.0000 / 2 = 134.0000 mm

Compute the Effective Tube Pitch [p*]:= p / sqrt( 1 - 4 * min( AL * CNV_factor, 4*Do*p)/(Pi * Do^2) )= 52.0000 / sqrt( 1 - 4 * min( 0.00 *100.000 , 4*268.000 *52.000 )/ ( 3.141 * 268.000^2) )

= 52.0000 mm

Compute the Effective Ligament Efficiency for Bending [mu*]:= (p* - d*) / p* = (52.0000 - 30.0000 ) / 52.0000 = 0.4231

Compute the Ratio [Rhos]:= as / ao = 163.6000 / 134.0000 = 1.220896

Compute the Ratio [Rhoc]:= ac / ao = 180.5940 / 134.0000 = 1.347716

Compute Parameter [xt]:= 1 - Nt * (( dt - 2 * tt )/( 2 * ao ))2= 1 - 15 * ((30.0000 - 2 * 1.4500 )/(2 * 134.0000 ))2 = 0.8466

Determine Parameter [xs]:= 1 - Nt*( dt/(2*ao) )2= 1 - 15 *( 30.0000 /(2*134.0000 ) )2 = 0.8120

Determine the Value [h'g]:= 0 (For pressure plus thermal and thermal only cases )

UHX-13.5.2 Step 2:Determine the Axial Shell Stiffness [Ks]:= pi * ts( Ds + ts )Es/L= 3.1416 * 8.4000 ( 327.2000 + 8.4000 )2020629 /2939.200= 6088474.0000 kgf/c * mm

Determine the Axial Tube Stiffness [Kt]:= pi * tt( Dt - tt )Et/L= 3.1416 * 1.4500 ( 30.0000 - 1.4500 )1929230 /2939.200= 85364.8125 kgf/c * mm

Compute the Stiffness Factor [Kst]:= Ks / ( Nt * Kt ) = 6088474 / ( 15 * 85364.812 ) = 4.75487

Compute Factor [J]:= 1 / ( 1 + Ks/Kj )= 1/(1 + 6088474 /0.000 ) = 1.0000000 (= 1 if No Exp. Jt.)

Compute Shell Coefficient [betas]:= (( 12 * (1-nus^2))0.25 )/((Ds + ts) * ts )0.5= (( 12 * (1 - 0.30^2) )0.25 ) / (( 327.2000 + 8.4000 ) * 8.4000 )0.5= 0.0342 1/mm

Determine Shell Coefficient [ks]:


= betas * Es * ts^3/ ( 6 * (1 - nus^2) )= 0.034 * 2020629 * 8.4003 / ( 6 * (1 - 0.300^2) )= 7509945.5000 kgf/cm^2*mm^2

Determine Shell Coefficient [Lambdas]:= (6*Ds*ks)/(h^3) * (1 + h*betas + 0.5*(h*betas)^2)= 6*327.200 *7509945 /(31.800^3) * ( 1 + 31.800 *0.034 + 0.593 )= 1229394.0000 kgf/cm^2

Determine Shell Coefficient [deltaS]:= Ds2/(4 * Es * Ts) * ( 1 - nus/2 )= 327.2002/( 4 * 2020629 * 8.400 ) * ( 1 - 0.3 /2 )= 0.0013403546 mm/kgf/cm^2

Intermediate parameters for Tubesheet Gasketed on the Channel Side:betac, kc, deltaC, Lambdac = 0

UHX-13.5.3 Step 3:E*/E and nu* for Triangular pattern from Fig. UHX-11.3.

h/p = 0.611539 ; mu* = 0.423077E*/E = 0.501038 ; nu* = 0.255368 ; E* = 1012411. kgf/cm^2

Compute the Tube Bundle Stiffness Factor [Xa]:= ((24 *(1 - nu*2)*Nt * Et* tt* (dt - tt)* ao^2) /( E* * L * H3 ) )0.25

= ((24 *(1 - 0.2552)*15 *1929230 *1.4500 *(30.0000 - 1.4500 )*134.00002)/( 1012411 *2939.20 * 31.8003 ))0.25

= 1.4986

Values from Table UHX-13.1Zd = 0.453373 ; Zv = 0.188847 ; Zm = 0.765214Za = 0.502488E+00 ; Zw = 0.188847

UHX-13.5.4 Step 4:Compute the Diameter Ratio [K]:= A / Do = 483.0000 / 268.0000 = 1.8022

Compute Coefficient [F]:= (1 - nu*) / (E*) * ( Lambdas + Lambdac + E * ln(K) )= (1 - 0.26 ) / (1012411 ) * ( 1229394 + 0.00 +2020629 * ln(1.80 ) )

= 1.7796

Compute Parameter [Phi]:= (1 + nu*) * F = (1 + 0.2554 ) * 1.7796 = 2.2341

Compute Parameter [Q1]:= (Rhos - 1 - Phi * Zv)/(1 + Phi * Zm)= (1.2209 - 1 - 2.2341 *0.1888 )/(1 + 2.2341 *0.7652 )= -0.074183717

Compute Parameter [Qz1]:= (Zd + Q1*Zw)/2 *Xa4= (0.45337 + -0.07418 *0.18885 )/2 *1.498584 = 1.1079


Compute Parameter [Qz2]:= (Zv + Q1*Zm)/2 *Xa4= (0.18885 + -0.07418 *0.76521 )/2 *1.498584 = 0.3331

Compute Parameter [U]:= (Zw + (Rhos - 1)*Zm)*Xa4 / (1 + Phi*Zm)= (0.1888 + (1.2209 - 1)*0.7652 )*1.498584/ (1 + 2.2341 *0.7652 )= 0.6661

UHX-13.5.5 Step 5:

Determine factor [gamab]:= ( Gc - C ) / Do (config b)= (361.1880 - 431.8000 ) / 268.0000 = -0.26348

Compute Parameter [gamma]:= (alphatm*( Ttm - AMB_TEMP ) - alphasm*( Tsm - AMB_TEMP ))* L= ( 0.155E-04*(37.5 - 21.1 ) - 0.118E-04*(49.8 - 21.1 ))*2939.20= -0.2459 mm

Calculate Parameter [OmegaS]:= rhos * ks * Betas * deltaS( 1 + h * Betas )= 1.2209 * 7509945 * 0.0342 * 0.001340 ( 1 + 31.8000 * 0.0342 )= 878.8779 mm ^2

Calculate Parameter [Omega*S]:= Ao^2* ( Rhos^2- 1 ) * ( Rhos - 1 ) / 4 - OmegaS= 134.000^2* ( 1.221^2- 1 ) * ( 1.221 - 1 ) / 4 - 878.878= -392.4129 mm ^2

Calculate Parameter [OmegaC]:= rhoc * kc * Betac * deltaC( 1 + h * Betac )= 1.3477 * 0.00 * 0.0000 * 0.000000 ( 1 + 31.8000 * 0.0000 )= 0.0000 mm ^2

Calculate Parameter [Omega*C]:= ao^2[( Rhoc^2+1 )*( Rhoc-1 )/4 -(Rhos-1)/2]- OmegaC= 134.00000^2[( 1.34772^2+1 )*( 1.34772 -1 )/4 -(1.22090 -1)/2]- 0.00000= 2412.8184 mm ^2

Compute the average Temperature of the Unperforated Rim [Tr]:= (T' + T's )/2 = (100.0 + 100.0 )/ 2 = 100.0 C

Average Temperature of the Shell at the Tubesheet [T*s]:= (T's + Tr)/2 = (100.0 + 100.0 )/ 2 = 100.0 C

Average Temperature of the Channel at the Tubesheet [T*c]:= (T'c + Tr)/2 = (50.0 + 100.0 )/ 2 = 75.0 C

Compute the Pressure [P*S]:= Es*ts/as * ( alphas' * (T*s - AMB_TEMP) - alpha' * (Tr - AMB_TEMP) )= 2020629 *8.4000 /163.6000 * [ 0.121E-04 * (100.0 - 21.1 ) -0.121E-04 * (100.0 - 21.1 ) ]

= 0.0000 kgf/cm^2

Compute the Pressure [P*C]:= 0 For Pressure only cases or Configurations b,c,d,B,C,D


UHX-13.5.6 Step 6:Compute the Pressure [P's]:= Ps * {xs + 2( 1 - xs )nut + [2/Kst(Ds/Do)^2]nus -[(rhos^2-1)/(J*Kst)]-[(1-J)/(2J*Kst)][(Dj^2-(Ds)^2)/Do^2]}

= 1.000 * {0.812 + 2( 1 - 0.812 ) 0.300 +[2/4.755 (327.200 /268.000 )^2]0.300 -[(1.221^2-1)/( 1.000 * 4.755 )] -[(1 - 1.000 )/(2 * 1.000 * 4.755 )][(0.000^2-(327.200 )^2)/268.000^2]}

= 1.0097 kgf/cm^2

Compute the Pressure [P't]:= [ xt + 2(1 - xt)nut + 1/(J * Kst) ]*Pt= [ 0.847 + 2(1 - 0.847 )0.300 +1/(1.00000 * 4.755 ) ]* 0.500

= 0.5745 kgf/cm^2

Compute the Pressure [Pgama]:= Nt * Kt * gama / ( pi * ao^2)= 15 * 85364.812 * -0.246 / (3.142 * 134.000^2) = -5.581 kgf/cm^2

Compute the Pressure [Pw]:= -gamab * U * W* / (2 * pi * ao^2)= --0.263 * 0.666 * 38666.46 / (2 * 3.142 * 134.000^2)= 6.0151 kgf/cm^2

Calculate the Pressure [Prim]:= -( U/ao^2)(Omega*S * Ps - Omega*C * Pt )= -( 0.666 / 134.000^2)(-0.608 * 1.000 - 3.740 * 0.500 )= 0.0593 kgf/cm^2

Calculate the Pressure [POmega]:= U/ao^2(OmegaS * P*s - OmegaC * P*c )= 0.666 /134.0000^2( 1.3623 * 0.0000 - 0.0000 * 0.0000 )= 0.0000 kgf/cm^2

Determine the Effective Pressure [Pe]:= J * Kst / (1 + J * Kst *(Qz1 + (Rhos - 1) * Qz2)) *(P's - P't + Pgama + Pw + Prim )

= 0.1000E+01 * 4.755 / (1 + 1.000 * 4.755 *(1.108 + (1.221 -1) * 0.333 )) * (1.010 - 0.574 + -5.581 + 6.015 + 0.059 )

= 0.6673 kgf/cm^2

UHX-13.5.7 Step 7:Determine Factor [Q2]:= [((Omega*S*Ps - Omega*C*Pt) - (Omegas*P*s - Omegac P*c))CNV_FAC +W* * gamab/(2*pi)]/(1 + Phi*Zm)

= [ ( ( -392.413 * 1.000 - 2412.818 * 0.500 ) -( 878.878 * 0.000 - 0.000 * 0.000 ) ) * 0.010 +38666.5 * -0.263 /(2*3.141)]/(1 + 2.23409 * 0.76521 )

= -604.312805176 kgf

Calculate Factor [Q3]:= Q1 + 2 * Q2 / ( Pe * ao2 )= -0.074 + 2 * -604.313 / ( 0.667 * 134.0002 )= -10.161596


Fm Value from Table UHX-13.1 = 5.080798

The Tubesheet Bending Stress - Original Thickness [Sigma]:= (1.5 * Fm / mu* ) * (2 * ao/(H - h'g)2 * Pe= (1.5 * 5.0808 /0.4231 ) * (2 * 134.0000 /(31.800 - 0.000 ))2 * 0.67= 853.7331 kgf/cm^2

The Allowable Tubesheet Bending Stress [Sigma allowed]:SPS (ASME Sec VIII Div 1, UG-23(e)) = 4620.0425 kgf/cm^2

The Tubesheet Bending Stress - Final Thickness [Sigmaf]:= (1.5 * Fm/mu*) * (2 * ao/( h - h'g)^2* Pe= (1.5 * 0.1558 /0.4231 ) * (2 * 134.0000 /(8.929 - 0.000 ))^2* 9.28= 4619.7407 kgf/cm^2

Reqd Tubesheet Thickness, for Bending Stress (Including CA ) [HReqB]:= h + Cats + Catc = 8.9295 + 1.6000 + 1.6000 = 12.1295 mm

UHX-13.5.8 Step 8:Shear Stress check [Tau_limit]:= 1.6 * S * MU * h / ao= 1.6 * 1406.14 * 0.423 * 31.800 / 134.00 = 225.89 kgf/cm^2

The Tubesheet Average Shear Stress - Original Thickness [Tau]:= ( 1 / ( 2*mu ) ) * ( ao/h ) * Pe= ( 1 / (2*0.423 ) ) * ( 134.0000 /31.800 ) * 0.667= 3.3230 kgf/cm^2

The Allowable Tubesheet Shear Stress [Tau allowed]:= 0.8 * S = 0.8 * 1406.14 = 1124.91 kgf/cm^2

Note: Tubesheet Shear Stress is probably low, use the following req. thk:Tubesheet thickness (Incl. Corr.)= 7.0100 mmTubesheet Shear Stress = 281.4815 kgf/cm^2

Reqd Tubesheet Thickness for Given Loadings (Including CA) [Hreqd] := Max( HreqB, HreqS ) = Max( 12.1295 , 7.0100 ) = 12.1295 mm

UHX-13.5.9 Step 9:The Ftmin and Ftmax Coefficients from Table UHX-13.2:Ftmin = -3.6958 , Ftmax = 5.5882

First Extreme Tube Axial Stress from among all the tubes [Sigmat1]:= ( (Ps * xs - Pt * xt) - Pe * Ftmin ) / ( Xt - Xs )= ( (1.00 * 0.8120 - 0.50 * 0.8466 ) - (0.667 ) * -3.696 ) /(0.8466 - 0.8120 ) )

= 82.5508 kgf/cm^2

Second Extreme value of Tube Axial Stress from among all the tubes [Sigmat2]:= ( (Ps * xs - Pt * xt) - Pe * Ftmax ) / ( Xt - Xs )= ( (1.00 * 0.8120 - 0.50 * 0.8466 ) - (0.667 ) * 5.588 ) /(0.8466 - 0.8120 ) )

= -96.5836 kgf/cm^2

Maximum Tube Axial Stress [Sigmat,max]:


= MAX( |Sigmat1|, |Sigmat2| ) = 96.584 kgf/cm2

The Allowable Tube Stress, [SigmatA]= 2*Sot = 2794.4387 kgf/cm^2

Check for Buckling as some of the Tubes are in Compression

Determine the Factor of Safety [Fs]:= Max( (3.25 - 0.25*(Zd + Q3*Zw)*Xa^4 ), 1.25 )= Max((3.25 - 0.25*(0.453 + -10.162 *0.189 )*1.499^4), 1.25 )= 2.0000 (Should be Ft)= .55 * 3.1415 * 2.000 * (30.000 + 0.67*2.000 ) * 1397.22= 1513.2323 kgf

Groove Weld Strength [Fg]:= .85 * 3.1415 * ag * (do + 0.67*ag) * Sw (but not > Ft)= .85 * 3.1415 * 2.000 * (30.000 + 0.67*2.000 ) * 1397.22= 1817.1385 kgf

Max. Allow. Tube-Tubesheet Joint load, Lmax= 2 * Ft = 3634.2771 kgf

Design Strength Ratio [fd]:= 1.0000

Weld Strength Factor [fw]:= Sot / ( Min(Sot, S) ) = 1.0000


Min Weld Length [ar]:= 2 *( ( (0.75 * do)^2+ 1.07*t*(do - t)* fw * fd ) )^1/2 - .75 * do)= 1.9274 mm

Minimum Required Fillet Weld Leg afr 0.9637 mmMinimum Required Groove Weld Leg agr 0.9637 mm

Tube-Tubesheet Jt allowable, 3634.28 is >= tube strength 3634.28 kgfNote: This tube-tubesheet joint is a Full Strength joint

UHX-13.5.10 Step 10:Shell Axial Membrane Allowable Stress:= Sps,s = 4873.15 kgf/cm^2

Axial Membrane Stress in Shell [Sigmasm_ax]:= ao^2/((Ds+ts)*ts)* [Pe + (Rhos^2-1)(Ps-Pt)]+ as^2*Pt/((Ds+ts)*ts)= 134.000^2/((327.200 +8.4000 )*8.4000 )* [0.67 + (1.221^2-1)(1.00 -0.50 )] + 163.600^2*0.50 /((327.20 +8.4000 )* 8.40 )

= 10.5598 kgf/cm^2

UHX-13.5.11 Step 11:Note: For a given Shell thickness of 8.400 mm, the minimum Shell

length adjacent to the tubesheet should be 94.367 mm

The Shell Membrane Stress due to Joint Interaction [Sigmasm]:= ao^2/((Ds+ts)*ts)[Pe + (Rhos^2-1)(Ps-Pt)]+ as^2*Pt/((Ds+ts)*ts)= 134.000^2/((327.200 +8.4000 )*8.4000 )[0.67 + (1.221^2-1)(1.00 -0.50 )] + 163.600^2*0.50 /((327.20 +8.4000 )* 8.40 )

= 10.5598 kgf/cm^2

The Shell Bending Stress due to Joint Interaction [Sigmasb]= 6*ks/ts^2{betas[deltaS*Ps + as^2*PstarS/(Es*ts)] +6(1 - nu*^2)/(E*)(ao/h)^3(1 + h*betas/2)[Pe(Zv + Zm*Q1) +2/ao^2* Zm * Q2 ]}

= 6 * 7509945 /8.4000^2{0.034 [ 0.001 * 1.000 + 163.6000^2* 0.0000 /(16973284 ) ] +6(1 - 0.26^2)/(1012411 )(134.00 /31.80 )^3(1 + 31.80 *0.03 /2)[ 0.7 ( 0.189 + 0.765 * -0.074 ) +2/134.00^2* 0.765 * -604.313 ] }

= -2040.3289 kgf/cm^2

Shell Stress Summation vs. Allowable|Sigmasm| + |Sigmasb| =< SPSs|10.6 | + |-2040.3 | =< 4873.15 kgf/cm22050.89 must be < or = 4873.15 kgf/cm^2

Computations Completed for ASME Tubesheet Configuration b

Stress/Force summary for loadcase O3 corr. (Ps + Pt + Th):------------------------------------------------------------------------

Stress Description Actual Allowable Pass/Fail------------------------------------------------------------------------Tubesheet Bend. Stress 853.7


Tubesheet Shear Stress 3.3


D4uc 21 984 -21 -1251 ... ... ... ... OkO1uc 5 4873 -5 -1251 ... ... ... ... OkO2uc 1 4873 ... ... ... ... ... ... OkO3uc 1 4873 ... ... ... ... ... ... OkO4uc 6 4873 -6 -1251 ... ... ... ... OkD1c 21 984 -21 -1239 ... ... ... ... OkD2c 22 984 ... ... ... ... ... ... OkD3c 26 984 ... ... ... ... ... ... OkD4c 25 984 -25 -1239 ... ... ... ... OkO1c 3 4873 ... ... ... ... ... ... OkO2c 10 4873 ... ... ... ... ... ... OkO3c 11 4873 ... ... ... ... ... ... OkO4c 2 4873 ... ... ... ... ... ... Ok------------------------------------------------------------------------------Max RATIO 0.026 0.020 ... ...

Tube, Shell and Channel Stress Summary:--------- Tube Stresses Tube Loads Shell Stress Channel Stress Pass

Case# Ten Allwd Cmp Allwd Ld Allwd Stress Allwd Stress Allwd Fail------------------------------------------------------------------------------D1uc 19 1397 -19 -528 24 1817 284 2109 ... ... OkD2uc 13 1397 -3 -528 17 1817 232 2109 ... ... OkD3uc 2 1397 -2 -528 2 1817 59 2109 ... ... OkD4uc 4 1397 -4 -528 5 1817 110 2109 ... ... OkO1uc 100 2794 -40 -549 130 3634 1715 4873 ... ... OkO2uc 98 2794 -34 -846 128 3634 1631 4873 ... ... OkO3uc 99 2794 -37 -846 129 3634 1661 4873 ... ... OkO4uc 99 2794 -37 -647 129 3634 1686 4873 ... ... OkD1c 28 1397 -28 -528 37 1817 353 2109 ... ... OkD2c 21 1397 -1 -528 28 1817 290 2109 ... ... OkD3c 1 1397 -1 -528 1 1817 77 2109 ... ... OkD4c 7 1397 -7 -528 9 1817 141 2109 ... ... OkO1c 101 2794 -101 -846 132 3634 2107 4873 ... ... OkO2c 93 2794 -93 -528 121 3634 2014 4873 ... ... OkO3c 97 2794 -97 -528 126 3634 2051 4873 ... ... OkO4c 98 2794 -98 -528 127 3634 2070 4873 ... ... Ok------------------------------------------------------------------------------Max RATIO 0.036 0.185 0.036 0.432 ...

Summary of Thickness Comparisons for 16 Load Cases:----------------------------------------------------------------------------

Thickness (mm) Required Actual P/F----------------------------------------------------------------------------Tubesheet Thickness : 12.163 35.000 OkTubesheet Thickness Flanged Extension : 22.599 27.000 OkTube Thickness : 0.427 1.450 OkTube-Tubesheet Fillet Weld Leg : 0.964 2.000 OkTube-Tubesheet Groove Weld Leg : 0.964 2.000 Ok----------------------------------------------------------------------------

Min Shell length of thk, (10.000) adj. to tubesheet: 102.458 mm

Note: This is a full strength Tube to Tubesheet Joint.

Summary of Axial Differential Expansion bet. Shell and Tubes :Due to Thermal Expansion Exp. Jt. Compresses by : -0.246 mmDue to Pressure Exp. Jt. Compresses by : -0.013 mm


Due to Pressure + Thermal Exp. Jt. Compresses by : -0.249 mm

Tubesheet MAWP used to Compute Hydrotest Pressure:Stress / Force | Tubeside (0 shellside) | Shellside (0 tubeside) |Condition | MAWP |Stress Rat.| MAWP |Stress Rat.|

------------------------------------------------------------------------------Tubesheet Bending Stress | 31.185 | 1.000 | 78.612 | 1.000 |Tubesheet Shear Stress | 330.875 | 1.000 | 306.510 | 1.000 |Tube Tensile Stress | 99.387 | 1.000 | 291.643 | 1.000 |Tube Compressive Stress | 37.626 | 1.000 | ---- | ---- |Tube-Tubesheet Joint load | 99.387 | 1.000 | 291.643 | 1.000 |Shell Stress (Axial, Junc) | 28.411 | 1.000 | 49.039 | 0.723 |Tube Pressure Stress | 119.422 | 1.000 | 49.039 | 1.000 |Tubesheet Extension Stress | 31.088 | 0.000 | ---- | ---- |------------------------------------------------------------------------------Minimum MAWP | 28.411 | | 49.039 | |

Tubesheet MAPnc used to Compute Hydrotest Pressure:Stress / Force | Tubeside (0 shellside) | Shellside (0 tubeside) |Condition | MAPnc |Stress Rat.| MAPnc |Stress Rat.|

------------------------------------------------------------------------------Tubesheet Bending Stress | 37.119 | 1.000 | 94.941 | 0.999 |Tubesheet Shear Stress | 362.610 | 1.000 | 319.919 | 1.000 |Tube Tensile Stress | 140.508 | 1.000 | 478.959 | 1.000 |Tube Compressive Stress | 60.757 | 1.000 | 1233.69 | 1.000 |Tube-Tubesheet Joint load | 140.508 | 1.000 | 478.959 | 1.000 |Shell Stress (Axial, Junc) | 37.119 | 1.000 | 54.133 | 0.578 |Tube Pressure Stress | 120.184 | 1.000 | 54.133 | 1.000 |Tubesheet Extension Stress | 31.088 | 0.000 | ---- | ---- |------------------------------------------------------------------------------Minimum MAPnc | 31.088 | | 54.133 | |

asme tubesheet (heater 10m2)

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tube stress

tube allowable stress

tube yield stress

welded tube material

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