Fixed tube sheet heat exchanger

Where am I not good enough? Post the result

Stress check: Passable. Allowable pressure: 6.57. Hydrostatic test value: 2.7820. Stress on the elliptical head: 56.33. 0.9*ReL: 292.50. Pressure test passed. Note: Reference thickness: 7.00. Calculation for the shell section **********Internal pressure cylinder check********** Calculation conditions: Calculation pressure: 0.30. Design temperature: 95.00. Inner diameter of the cylinder: 600.00. Corrosion allowance: 1.00. Negative deviation: 0.30. Weld joint coefficient: 0.85. Material: Q345R. Input thickness: 10.00. Calculation results: Stress check: Passable. Allowable pressure: 4.59. σt = 10.49. t*Φ = 160.65. Hydrostatic test value: 0.3750. Cylinder stress: 15.43. 0.9*ReL: 310.50. Pressure test passed. Note: Reference thickness: 4.50. The nominal thickness of the cylinder is greater than or equal to the minimum thickness specified in GB/T151-2014, which is 6.00 mm; therefore, it is acceptable. Opening reinforcement calculation * * * * * * * * * * Opening reinforcement calculation results * * * * * * * * * * Nozzle a: Calculation method for the opening on the oval head: HG/T20582-2011 pressure area method to calculate pressure 1.6 MPa Shell material Q345R, nominal thickness 18 mm Nozzle material 20 (GB8163), specification φ325×8 Pressure-bearing area = 83589 mm2 Shell metal area = 1903 mm2 Nozzle metal area = 364 mm2 Weld metal area = 22 mm2 Reinforcement ring metal area = 0 mm2 Required pressure area = 133742 N Actual reinforcement area = 289836 N Please note that the material yield ratio, structure, manufacturing and usage conditions and other restrictions are qualified (+117%) Nozzle b: Calculation method for the opening on the elliptical head: HG/T20582-2011 Pressure area method to calculate pressure 1.6 MPa Shell material Q345R, nominal thickness 18 mm Nozzle material 20 (GB8163), specification φ325×8 Pressure-bearing area = 83589 mm2 Shell metal area = 1903 mm2 Nozzle metal area = 364 mm2 Weld metal area = 22 mm2 Reinforcement ring metal area = 0 mm2 Required pressure area = 133742 N Actual reinforcement area = 289836 N Please note that the material yield ratio, structure, manufacturing and usage conditions are qualified (+117%). Nozzle c: Calculation method for the opening on the circular cylinder: GB150-2011 equal area method to calculate pressure 0.3 MPa. Shell material Q345R, nominal thickness 10 mm. Nozzle material 20 (GB8163), specification φ57×4 A1=419, A2=55, A3=10, A4=0 A1+A2+A3+A4=484 >= A=25.307 Passed (+1811%) Nozzle d: Calculation method for opening on circular cylinder: GB150-2011 equal area method to calculate pressure 0.3 MPa Shell material Q345R, nominal thickness 10 mm Nozzle material 20 (GB8163), specification φ57×4 A1=419, A2=55, A3=10, A4=0 A1+A2+A3+A4=484 >= A=25.307 Passed (+1811%) Tubesheet calculation calculation basis * * Extensions double as flange-mounted tubesheet calculations * * * * Calculation of tubesheet after corrosion * * 1. Design parameters: Shell inner diameter Di=600 mm Shell side design pressure ps=0.3 MPa Tube side design pressure Pt=1.6 MPa Shell side design temperature Ts=95 ℃ Tube side design temperature Tt=350 ℃ Assembly temperature T0=20 ℃ Shell material: Q345R Shell average temperature θs=95 ℃ Nominal shell thickness δsn=10 mm Effective thickness of the shell δse=8.7 mm Elastic modulus at the average temperature of the shell Es=197250 MPa Thermal expansion coefficient at the average temperature of the shell αs=1.1489e-05 1/℃ Allowable stress at the design temperature of the shell s=189 MPa Pipe box material: Q345R Nominal thickness of the pipe box δhn=16 mm Effective thickness of the pipe box δhe=15 mm Elastic modulus at the design temperature of the tube box Eh=178000 MPa Number of triangular pipes n=109 Tube sheet material name: Q345R Elastic modulus Ep=178000 MPa Center distance of heat exchange tubes S=50 mm Area of partition groove (including tie rods and dummy tubes) Ad=0 mm * mm Tubesheet corrosion margin c2p=2 mm Tubesheet shell side partition groove depth Hs=0 mm Tubesheet tube side partition groove depth Hh=0 mm Tubesheet input thickness δp=100 mm Stiffness weakening coefficient η=0.4 Strength weakening coefficient μ=0.4 Pipe material name: 20 (GB9948) Pipe outer diameter d=25 mm Pipe wall thickness δt=2 mm Nominal length of the pipe L=500 mm Pipe instability equivalent length lcr=247.5 mm Average pipe temperature θt=221 ℃ Allowable stress at design temperature tt=98 MPa Yield stress at design temperature σst=147 MPa Elastic modulus at design temperature Ett=178000 MPa Elastic modulus at average temperature Et=189740 MPa Thermal expansion coefficient at average temperature αt=1.23802e-05 1/℃ Thickness difference between tube sheet and tube sheet flange dt=0 mm Minimum ratio of thickness between tube sheet and pipe box flange xt=0.6 mm Flange outer diameter Do=760 mm Pipe box flange thickness δf2=50 mm Basic flange moment Mm=2.89022e+07 N * mm Flange moment Mp=2.74436e+07 N under pipe side pressure operating conditions * mm 2. Design process: Shell inner diameter area A=282743 mm * mm Shell metal cross-sectional area As=16636.9 mm * mm Pipe metal cross-sectional area a=144.513 mm * mm Total metal cross-sectional area of ​​the pipe na=15751.9 mm * mm Pipe equivalent axial elastic modulus Et * =189740 MPa Tube bundle modulus Kt=16604.3 Tube radius of gyration i=8.16241 Coefficient Cr=154.602 Stable allowable compressive stress of heat exchange tube cr=88.3897 MPa Tube plate area after opening Al=229238 mm * mm Tube plate layout area At=235992 mm * mm Equivalent diameter of pipe layout Dt=548.155 mm Ratio Dt/Di=ρt=0.913592 Coefficient λ=0.810764 Coefficient β=0.0687143 Stiffness ratio of tube bundle and shell Q=0.910759 Difference in expansion deformation of pipe and shell γ=0.00162675 Effective thickness of tube sheet δ=97.7 mm Effective length of heat exchange tube L=300 mm Pipe reinforcement coefficient K=3.11469 Coefficient Σs=1.81404 Coefficient Σt=2.29086 Ratio of flange outer diameter to inner diameter K=1.26667 Coefficient Y=8.34882 Difference in expansion deformation between tube and shell γ=0.00162675 jp=6 mm=1.58117 0.348276 -0.945091 0.326835 -1.28609 0.369538 xmm=1.58117 0.348276 -0.945091 0.326835 -1.28609 0.369538 G1e=0.609567 0.134266 0.364348 0.126 0.495809 0.142463 G1i=1.35483 0.359908 1.20479 0.364655 1.50101 0.355328 zG1i=1.35483 0.352584 1.31253 0.358412 1.60662 0.348567 ksib=0.859376 0.4 1.21326 0.4 1.15454 0.425292 frb=1.30962 0.134266 -1.10513 0.126 -1.43107 0.151471 fri=0 -0.358899 -1.2067 -0.365085 -1.50342 -0.353031 fr=1.30962 -0.358899 -1.2067 -0.365085 -1.51246 -0.366229 G1=1.30962 -0.358899 -1.2067 -0.365085 -1.51246 -0.366229 Center heat exchange tube stress -9.42135 3.37065 -41.3948 -23.4171 -36.5676 -23.7249 Peripheral heat exchange tube stress 5.33229 -206.415 18.1922 -195.906 17.0415 -194.705 17.0646 -197.033 Pipe compressive stress-σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * cr should add expansion joints or reduce the baffle spacing welding leg height (expansion joint length) l=2 pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * Change the minimum welding leg height (expansion length) l=2 mm required by the standard for connecting the tube sheet and pipe. 3. Design calculation results: allowable stress rt=117MPa at design temperature. Check the tube sheet thickness δd=100 mm. The tube sheet check fails to pass the setting or choose an expansion joint with a smaller stiffness. * * * * * * Heat exchange tube strength calculation * * * * * * The calculation of the internal pressure of the heat exchange tube is qualified. The calculation of the external pressure of the heat exchange tube is qualified. The calculation of the external pressure of the heat exchange tube shell side pressure test is qualified. * * Tubesheet calculation before corrosion * * 1. Design parameters: Shell inner diameter Di=600 mm Shell side design pressure ps=0.3 MPa Tube side design pressure Pt=1.6 MPa Shell side design temperature Ts=95 ℃ Tube side design temperature Tt=350 ℃ Assembly temperature T0=20 ℃ Shell material: Q345R Shell average temperature θs=95 ℃ Nominal shell thickness δsn=10 mm Effective thickness of the shell δse=9.7 mm Elastic modulus at the average temperature of the shell Es=197250 MPa Coefficient of thermal expansion at the average temperature of the shell αs=1.1489e-05 1/℃ Allowable stress at the design temperature of the shell s=189 MPa Pipe box material: Q345R Nominal thickness of the pipe box δhn=16 mm Effective thickness of the pipe box δhe=16 mm Elastic modulus at the design temperature of the tube box Eh=178000 MPa Number of triangular pipes n=109 Tube sheet material name: Q345R Elastic modulus Ep=178000 MPa Center distance of heat exchange tubes S=50 mm Area of partition groove (including tie rods and dummy tubes) Ad=0 mm * mm Tubesheet corrosion margin c2p=0 mm Tubesheet shell side partition groove depth Hs=0 mm Tubesheet tube side partition groove depth Hh=0 mm Tubesheet input thickness δp=100 mm Stiffness weakening coefficient η=0.4 Strength weakening coefficient μ=0.4 Pipe material name: 20 (GB9948) Pipe outer diameter d=25 mm Pipe wall thickness δt=2 mm Nominal length of the pipe L=500 mm Pipe instability equivalent length lcr=247.5 mm Average pipe temperature θt=221 ℃ Allowable stress at design temperature tt=98 MPa Yield stress at design temperature σst=147 MPa Elastic modulus at design temperature Ett=178000 MPa Elastic modulus at average temperature Et=189740 MPa Thermal expansion coefficient at average temperature αt=1.23802e-05 1/℃ Thickness difference between tube sheet and tube sheet flange dt=0 mm Minimum ratio of thickness between tube sheet and pipe box flange xt=0.6 mm Flange outer diameter Do=760 mm Pipe box flange thickness δf2=50 mm Basic flange moment Mm=2.89022e+07 N * mm Flange moment Mp=2.74436e+07 N under pipe side pressure operating conditions * mm 2. Design process: Shell inner diameter area A=282743 mm * mm Shell metal cross-sectional area As=18579.6 mm * mm Pipe metal cross-sectional area a=144.513 mm * mm Total metal cross-sectional area of ​​the pipe na=15751.9 mm * mm Pipe equivalent axial elastic modulus Et * =189740 MPa Tube bundle modulus Kt=16604.3 Tube radius of gyration i=8.16241 Coefficient Cr=154.602 Stable allowable compressive stress of heat exchange tube cr=88.3897 MPa Tube plate area after opening Al=229238 mm * mm Tube plate layout area At=235992 mm * mm Equivalent diameter of pipe distribution area Dt=548.155 mm Ratio Dt/Di=ρt=0.913592 Coefficient λ=0.810764 Coefficient β=0.0687143 Pipe bundle to shell stiffness ratio Q=0.815527 Pipe and shell expansion deformation difference γ=0.00162675 Tube sheet meter effective thickness δ=99.7 mm Effective length of heat exchange tube L=300 mm Pipe reinforcement coefficient K=3.06771 Coefficient Σs=1.74357 Coefficient Σt=2.1734 Ratio of flange outer diameter to inner diameter K=1.26667 Coefficient Y=8.34882 Difference in expansion deformation between tube and shell γ=0.00162675 jp=6 mm=1.54846 0.343244 -0.944482 0.317195 -1.28649 0.362085 xmm=1.54846 0.343244 -0.944482 0.317195 -1.28649 0.362085 G1e=0.606098 0.134353 0.36969 0.124157 0.503558 0.141727 G1i=1.34643 0.374931 1.22371 0.381152 1.52462 0.370432 zG1i=1.34643 0.366964 1.33187 0.374476 1.63062 0.363028 ksib=0.858946 0.4 1.21066 0.4 1.15258 0.422351 frb=1.30151 0.134353 -1.11892 0.124157 -1.45098 0.149647 fri=0 -0.373648 -1.22539 -0.381184 -1.52753 -0.368384 fr=1.30151 -0.373648 -1.22539 -0.381184 -1.54478 -0.382202 G1=1.30151 -0.373648 -1.22539 -0.381184 -1.54478 -0.382202 Center heat exchange tube stress -9.41793 0.157878 -40.7103 -25.3831 -35.9664 -26.297 Peripheral heat exchange tube stress 4.76792 -212.937 16.6778 -203.394 15.5777 -202.127 15.6162 -204.456 Pipe compressive stress-σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * cr should add expansion joints or reduce the baffle spacing welding leg height (expansion joint length) l=2 pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * The minimum welding leg height (expansion length) required by the standard for changing the tube sheet and pipe connection form is l=2 mm 3. Design calculation results: allowable stress rt=117MPa at the design temperature. Check the tube sheet thickness δd=100 mm. The tube sheet check is not calculated by setting or changing the expansion joint pipe box flange with smaller stiffness. * * * * * * * * * * Narrow face flange calculation * * * * * * * * * * Calculated pressure (MPa): 1.600000 Design temperature (degrees C): 350.000000 t=50.000000mm: Stress calculation: axial stress σH=149.44MPa tangential stress σT=34.91MPa radial stress σR=30.22MPa The larger of (σH+σT)/2 or (σH+σR)/2=92.18Pa J=0.503545 The shear stress under pre-tightening condition τ1 (MPa): 10.796474 The shear stress under operating condition τ2 (MPa): 5.394146 The shear stress after verification is passed like this

This post was last edited by sdwfsgyykai on 2018-7-27 08:07. 1. Do not enter the wall temperature; what you entered is incorrect as well – that value is determined through process calculations； 2. The flange also serves as the tube sheet; as stated in the report, the tube sheet thickness is insufficient – at least 100 mm is required. Try using 47023. The tube sheets for this type of heat exchanger are already quite thick; if there are any issues, contact me privately

Required pressure area = 133742 N Actual reinforcement area = 289836 N Please note that the material yield ratio, structure, manufacturing and usage conditions are qualified (+117%) Nozzle c: Calculation method for openings in circular cylinders: GB150-2011 equal area method to calculate pressure 0.3 MPa Shell material Q345R, nominal thickness 16 mm Nozzle material 20 (GB8163), Specification φ57×4 A1=724, A2=55, A3=16, A4=0 A1+A2+A3+A4=795 >= A=25.307 Passed (+3041%) Nozzle d: Calculation method of opening on circular cylinder: GB150-2011 equal area method to calculate pressure 0.3 MPa Shell material Q345R, nominal thickness 16 mm Nozzle material 20 (GB8163), specification φ57×4 A1=724, A2=55, A3=16, A4=0 A1+A2+A3+A4=795 >= A=25.307 Qualified (+3041%) Tubesheet calculation calculation basis * * Extensions double as flange-mounted tubesheet calculations * * * * Calculation of tubesheet after corrosion * * 1. Design parameters: Shell inner diameter Di=600 mm Shell side design pressure ps=0.3 MPa Tube side design pressure Pt=1.6 MPa Shell side design temperature Ts=95 ℃ Tube side design temperature Tt=350 ℃ Assembly temperature T0=20 ℃ Shell material: Q345R Shell average temperature θs=95 ℃ Nominal shell thickness δsn=16 mm Effective thickness of the shell δse=14.7 mm Elastic modulus at the average temperature of the shell Es=197250 MPa Coefficient of thermal expansion at the average temperature of the shell αs=1.1489e-05 1/℃ Allowable stress at the design temperature of the shell s=189 MPa Pipe box material: Q345R Nominal thickness of the pipe box δhn=16 mm Effective thickness of the pipe box δhe=15 mm Elastic modulus at the design temperature of the tube box Eh=178000 MPa Number of triangular pipes n=109 Tube sheet material name: Q345R Elastic modulus Ep=178000 MPa Center distance of heat exchange tubes S=50 mm Area of partition groove (including tie rods and dummy tubes) Ad=0 mm * mm Tubesheet corrosion margin c2p=2 mm Tubesheet shell side partition groove depth Hs=0 mm Tubesheet tube side partition groove depth Hh=0 mm Tubesheet input thickness δp=100 mm Stiffness weakening coefficient η=0.4 Strength weakening coefficient μ=0.4 Pipe material name: 20 (GB9948) Pipe outer diameter d=25 mm Pipe wall thickness δt=2 mm Nominal length of the pipe L=500 mm Pipe instability equivalent length lcr=247.5 mm Average pipe temperature θt=221 ℃ Allowable stress at design temperature tt=98 MPa Yield stress at design temperature σst=147 MPa Elastic modulus at design temperature Ett=178000 MPa Elastic modulus at average temperature Et=189740 MPa Thermal expansion coefficient at average temperature αt=1.23802e-05 1/℃ Thickness difference between tube sheet and tube sheet flange dt=0 mm Minimum ratio of thickness between tube sheet and pipe box flange xt=0.6 mm Flange outer diameter Do=760 mm Pipe box flange thickness δf2=50 mm Basic flange moment Mm=2.89022e+07 N * mm Flange moment Mp=2.74436e+07 N under pipe side pressure operating conditions * mm 2. Design process: Shell inner diameter area A=282743 mm * mm Shell metal cross-sectional area As=28387.7 mm * mm Pipe metal cross-sectional area a=144.513 mm * mm Total metal cross-sectional area of ​​the pipe na=15751.9 mm * mm Pipe equivalent axial elastic modulus Et * =189740 MPa Tube bundle modulus Kt=16604.3 Tube radius of gyration i=8.16241 Coefficient Cr=154.602 Stable allowable compressive stress of heat exchange tube cr=88.3897 MPa Tube plate area after opening Al=229238 mm * mm Tube plate layout area At=235992 mm * mm Equivalent diameter of pipe layout Dt=548.155 mm Ratio Dt/Di=ρt=0.913592 Coefficient λ=0.810764 Coefficient β=0.0687143 Stiffness ratio of tube bundle and shell Q=0.53376 Difference in expansion deformation of pipe and shell γ=0.00162675 Effective thickness of tube sheet δ=97.7 mm Effective length of heat exchange tube L=300 mm Pipe reinforcement coefficient K=3.11469 Coefficient Σs=1.53505 Coefficient Σt=1.82587 Ratio of flange outer diameter to inner diameter K=1.26667 Coefficient Y=8.34882 Difference in expansion deformation between tube and shell γ=0.00162675 jp=6 mm=1.43546 0.36078 -0.931516 0.337812 -1.38218 0.373485 0.359115 0.130232 0.532853 0.143985 G1i=1.21475 0.357214 1.19327 0.362167 1.58628 0.354478 zG1i=1.21475 0.350189 1.30083 0.3553 1.68949 0.347829 ksib=0.845938 0.411542 1.21649 0.4 1.14322 0.431279 frb=1.17035 0.1431 -1.09215 0.130232 -1.52292 0.155244 fri=0 -0.355416 -1.19552 -0.361885 -1.58764 -0.351971 fr=1.17035 -0.355416 -1.19552 -0.361885 -1.58764 -0.362563 G1=1.17035 -0.355416 -1.19552 -0.361885 -1.58764 -0.362563 Stress of central heat exchange tube -8.28087 1.27675 -39.1005 -24.5074 -34.4821 -24.9245 Stress of peripheral heat exchange tube 3.07698 -238.716 12.3949 -230.949 11.497 -230.296 11.4771 -231.867 Pipe compressive stress-σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * cr should add expansion joints or reduce the baffle spacing welding leg height (expansion joint length) l=2 pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * Change the minimum welding leg height (expansion length) l=2 mm required by the standard for connecting the tube sheet and pipe. 3. Design calculation results: allowable stress rt=117MPa at design temperature. Check the tube sheet thickness δd=100 mm. The tube sheet check fails to pass the setting or choose an expansion joint with a smaller stiffness. * * * * * * Heat exchange tube strength calculation * * * * * * The calculation of the internal pressure of the heat exchange tube is qualified. The calculation of the external pressure of the heat exchange tube is qualified. The calculation of the external pressure of the heat exchange tube shell side pressure test is qualified. * * Tubesheet calculation before corrosion * * 1. Design parameters: Shell inner diameter Di=600 mm Shell side design pressure ps=0.3 MPa Tube side design pressure Pt=1.6 MPa Shell side design temperature Ts=95 ℃ Tube side design temperature Tt=350 ℃ Assembly temperature T0=20 ℃ Shell material: Q345R Shell average temperature θs=95 ℃ Nominal shell thickness δsn=16 mm Effective thickness of the shell δse=15.7 mm Elastic modulus at the average temperature of the shell Es=197250 MPa Coefficient of thermal expansion at the average temperature of the shell αs=1.1489e-05 1/℃ Allowable stress at the design temperature of the shell s=189 MPa Pipe box material: Q345R Nominal thickness of the pipe box δhn=16 mm Effective thickness of the pipe box δhe=16 mm Elastic modulus at the design temperature of the tube box Eh=178000 MPa Number of triangular pipes n=109 Tube sheet material name: Q345R Elastic modulus Ep=178000 MPa Center distance of heat exchange tubes S=50 mm Area of partition groove (including tie rods and dummy tubes) Ad=0 mm * mm Tubesheet corrosion margin c2p=0 mm Tubesheet shell side partition groove depth Hs=0 mm Tubesheet tube side partition groove depth Hh=0 mm Tubesheet input thickness δp=100 mm Stiffness weakening coefficient η=0.4 Strength weakening coefficient μ=0.4 Pipe material name: 20 (GB9948) Pipe outer diameter d=25 mm Pipe wall thickness δt=2 mm Nominal length of the pipe L=500 mm Pipe instability equivalent length lcr=247.5 mm Average pipe temperature θt=221 ℃ Allowable stress at design temperature tt=98 MPa Yield stress at design temperature σst=147 MPa Elastic modulus at design temperature Ett=178000 MPa Elastic modulus at average temperature Et=189740 MPa Thermal expansion coefficient at average temperature αt=1.23802e-05 1/℃ Thickness difference between tube sheet and tube sheet flange dt=0 mm Minimum ratio of thickness between tube sheet and pipe box flange xt=0.6 mm Flange outer diameter Do=760 mm Pipe box flange thickness δf2=50 mm Basic flange moment Mm=2.89022e+07 N * mm Flange moment Mp=2.74436e+07 N under pipe side pressure operating conditions * mm 2. Design process: Shell inner diameter area A=282743 mm * mm Shell metal cross-sectional area As=30368.1 mm * mm Pipe metal cross-sectional area a=144.513 mm * mm Total metal cross-sectional area of ​​the pipe na=15751.9 mm * mm Pipe equivalent axial elastic modulus Et * =189740 MPa Tube bundle modulus Kt=16604.3 Tube radius of gyration i=8.16241 Coefficient Cr=154.602 Stable allowable compressive stress of heat exchange tube cr=88.3897 MPa Tube plate area after opening Al=229238 mm * mm Tube plate layout area At=235992 mm * mm Equivalent diameter of pipe layout Dt=548.155 mm Ratio Dt/Di=ρt=0.913592 Coefficient λ=0.810764 Coefficient β=0.0687143 Stiffness ratio of tube bundle and shell Q=0.49895 Difference in expansion deformation of pipe and shell γ=0.00162675 Effective thickness of tube sheet δ=99.7 mm Effective length of heat exchange tube L=300 mm Pipe reinforcement coefficient K=3.06771 Coefficient Σs=1.50929 Coefficient Σt=1.78294 Ratio of flange outer diameter to inner diameter K=1.26667 Coefficient Y=8.34882 Difference in expansion deformation between the tube and shell γ=0.00162675 jp=6 mm=1.41972 0.358794 -0.887973 0.333442 -1.30875 0.370608 xmm=1.41972 0.358795 -0.887973 0.333442 -1.30875 0.370608 G1e=0.555709 0.140439 0.347571 0.130516 0.51227 0.145063 G1i=1.22074 0.371218 1.17482 0.377272 1.54474 0.368397 zG1i=1.22074 0.363639 1.28251 0.369614 1.65006 0.361434 ksib=0.846863 0.417125 1.22456 0.4 1.14985 0.435456 frb=1.17652 0.146452 -1.06405 0.130516 -1.47259 0.157922 fri=0 -0.369292 -1.17708 -0.376449 -1.5479 -0.366053 fr=1.17652 -0.369292 -1.17708 -0.376449 -1.5479 -0.377081 G1=1.17652 -0.369292 -1.17708 -0.376449 -1.5479 -0.377081 Center heat exchange tube stress -8.30042 -2.9138 -38.4829 -27.6147 -33.9097 -28.5231 Peripheral heat exchange tube stress 2.80617 -241.466 11.652 -234.188 10.7766 -233.496 10.7695 -235.071 Pipe compressive stress-σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * Cr should add expansion joints or reduce the baffle spacing. The pipe compressive stress -σt is greater than (1.2) * cr should add expansion joints or reduce the baffle spacing welding leg height (expansion joint length) l=2 pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * Changing the connection form between the tube sheet and the tube results in pull-off stress q>(3) * The minimum welding leg height (expansion length) required by the standard for changing the tube sheet and pipe connection form is l=2 mm 3. Design calculation results: allowable stress rt=117MPa at the design temperature. Check the tube sheet thickness δd=100 mm. The tube sheet check is not calculated by setting or changing the expansion joint pipe box flange with smaller stiffness. * * * * * * * * * * Narrow face flange calculation * * * * * * * * * * Calculated pressure (MPa): 1.600000 Design temperature (degrees C): 350.000000 t=50.000000mm: Stress calculation: axial stress σH=149.44MPa tangential stress σT=34.91MPa radial stress σR=30.22MPa The larger of (σH+σT)/2 or (σH+σR)/2=92.18Pa J=0.503545 Checked and passed the shear stress in pre-tightening condition τ1 (MPa): 10.796474 Shear stress in operating conditions τ2 (MPa): 5.394146 Passed the shear stress check

It’s definitely possible to proceed if the wall temperature isn’t entered

Don’t enter the wall temperature; the value you entered for the wall temperature is incorrect

This is a task that requires process calculation; go and learn process calculation, let your master teach you

With such a large temperature difference, expansion joints should be installed. Additionally, since the pressure in the tube side is 1.6 MPa at 350°, flanges rated for 2.5 MPa and made of 16MN forged material should be used

This post was last edited by foam_ZPTK on 2018-8-15 08:52. Hehe, I’ll also give it a try – it’s needed for heat exchangers, heat exchange units, and water treatment