AD2000-薄管板换热器强度计算示例

AD2000-薄管板换热器强度计算示例 Component: Front Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 6.7.1 Circular Flat Plates Mutually Stayed by the Tubes and the Shell Tubesheet Material: 1.4404 X 2 CrNiMo 17 13 2 Blech Tube Material: 1.4404 X 2 CrNiMo 17 13 2 Shell Material: 1.4301 X 5 CrNi 8 10 Blech Condition: Operating Testing Temperature T = 30 20 C Strenth Value, Tubesheet K = 220.2 221.8 N/mm2 Strength Value, Tubes K = 222.3 225 N/mm2 Safety Factor S = 1.5 1.1 Modulus of Elasticity, Shell E = 198725 - N/mm2 Modulus of Elasticity, Tubes E = 198200 - N/mm2 Geometric Data Actual Thickness of Tubesheet se = 23.8 mm Shell Outside Diam. Da = 1404 mm Shell Wall Thickness se = 2 mm Tube Outside Diam. da = 25 mm Tube Wall Thickness se = 2 mm Tube Inside Diam. di = 21 mm Tube Pitch t = 32 mm Design Diameter D1 = 1408 mm Design Diameter d2 = 281.6 mm Number of Tubes n = 1526 Component: Front Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 Boundry Tubes (approx. the two outermost tube rows) nt = 2*PI(Da-2*se-2*t)/t = 263 Cross-sectional Area, Shell AM = PI*(Da**2-(Da-2*se)**2)/4 = 8809 mm2 Cross-sectional Area, nt AR = nt*PI*(da**2-(da-2*st)**2)/4 = 38007.1 mm2 AD S 3/7 - Allowing For Thermal Stresses in Heat Exchangers - October 1991 Shell Tubes Thermal Expansion Coef. (*10**6 1/deg. C) alpha = 16 16.5 Temperature, C theta = 30 20 Thermal Expansion Difference, xd xd = |(alphaM*(thetaM-20)-alphaR*(thetaR-20))/10**6| = 0.00016 Thermal Stress in Shell sM = -xd /((1/EM)+AM/(AR*ER))*F = -258 bar Thermal Stress in Tubes sR = xd /((1/ER)+AR/(AM*EM))*F = 59.8 bar F, % = 100 Component: Front Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 6.7.1.4 - Tube Forces Des. Pressure, Shell pu = 1 bar Tensile Stress, Tubes sR = 59.8 bar Des. Pressure, Tubes pi = 2 bar Comp. Stress, Tubes sR = - Pressure p1 = pu+sR = 60.8 bar Test Pressure, Shell p1'= 1 bar Pressure p2 = pi-sR = 2 bar Test Pressure, Tubes p2'= 1 bar Maximum Pressure p = 60.8 bar Expanded Length lw = 0 mm 6.7.1.1 - Required Wall Thickness, mm Operating Testing s = 0,4*d2*SQRT(p*S/(10*K) = 22.9 2.5 (12) Loaded Area AR = PI/4*((Da-2*se)**2-n*da**2)/n = 517.9 mm2 Bild 12 Effective Area AW = (da-di)*lw = 0 mm2 (13) AW <= 0.1*da*lw = 0 mm2 (14) Tube Forces, N Operating Testing Tensile Force FR = AR*p1/10 = 3149 52 (21) Compressive Force FR = AR*p2/10 = 104 52 (21) Maximum Force FR = 3149 52 N Allowable Loading of the Expanded Joint FR/AW = 0 0 N/mm2 Component: Front Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 B5 - 6.5.3 - Calculation of the Buckling Loads and Wall Thickness Buckling Length lk = 1400 mm Design Factor C = 0.4 J = 0,049*(da**4-di**4) = 9611 Weakening Factor v = 0.219 v = (t-da)/t Slenderness Ratio La = 4*lk/SQRT(da**2-di**2) = 171.5 (9a) Slenderness Ratio Range La0 = PI*SQRT(E/K) = 93.8 (9b) Allowable Buckling Load, N Operating Testing Fk = PI**2*E*J/(lk**2*3.0) or (8a) Fk = (K/S)*PI*((da**2-di**2)/4)*(1-(La/La0)*(1-S/3)) = 3197 3207 (8b) Maximum Buckling Load FRcmax = 104 52 Smallest Weld Thickness g = 0,4*FR*S/(da*K) = 0.3 0 mm (15) 6.7.1.5 - Required Tubesheet Thickness (FRcmax > Fk) s = C*SQRT(((D1**2-n*di**2)/v)*(pi*S/(10*K))) = 36.1 21.8 mm (16) Component: Front Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 6.7.5 - Circular, Flat Tubesheets on Heat Exchangers with Expansion Joints Exp. Joint Diameter Dk = 1964 mm Outer Tube Limit l = 656.5 mm Design Diameter D3 = (Dk+Da)/2 = 1684 mm Design Pressure p = pi+pu*(D3**2-4*l**2)/D1**2 = 2.6 bar (26) Fig. 16 Ratio l/D1 = 0.47 Ratio dt/dD = 1.03 Design Factor C5 = 0.19 Table 1 Type = - Required Tubesheet Thickness s = C5*D1*SQRT(p*S/(10*K*v)) = 23.8 mm (27) Component: Rear Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 6.7.1 Circular Flat Plates Mutually Stayed by the Tubes and the Shell Tubesheet Material: 1.4404 X 2 CrNiMo 17 13 2 Blech Tube Material: 1.4404 X 2 CrNiMo 17 13 2 Shell Material: 1.4301 X 5 CrNi 8 10 Blech Condition: Operating Testing Temperature T = 30 20 C Strenth Value, Tubesheet K = 220.2 221.8 N/mm2 Strength Value, Tubes K = 222.3 225 N/mm2 Safety Factor S = 1.5 1.1 Modulus of Elasticity, Shell E = 198725 - N/mm2 Modulus of Elasticity, Tubes E = 198200 - N/mm2 Geometric Data Actual Thickness of Tubesheet se = 23.9 mm Shell Outside Diam. Da = 1404 mm Shell Wall Thickness se = 2 mm Tube Outside Diam. da = 25 mm Tube Wall Thickness se = 2 mm Tube Inside Diam. di = 21 mm Tube Pitch t = 32 mm Design Diameter D1 = 1400 mm Design Diameter d2 = 280 mm Number of Tubes n = 1526 Component: Rear Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 Boundry Tubes (approx. the two outermost tube rows) nt = 2*PI(Da-2*se-2*t)/t = 263 Cross-sectional Area, Shell AM = PI*(Da**2-(Da-2*se)**2)/4 = 8809 mm2 Cross-sectional Area, nt AR = nt*PI*(da**2-(da-2*st)**2)/4 = 38007.1 mm2 AD S 3/7 - Allowing For Thermal Stresses in Heat Exchangers - October 1991 Shell Tubes Thermal Expansion Coef. (*10**6 1/deg. C) alpha = 16 16.5 Temperature, C theta = 30 20 Thermal Expansion Difference, xd xd = |(alphaM*(thetaM-20)-alphaR*(thetaR-20))/10**6| = 0.00016 Thermal Stress in Shell sM = -xd /((1/EM)+AM/(AR*ER))*F = -258 bar Thermal Stress in Tubes sR = xd /((1/ER)+AR/(AM*EM))*F = 59.8 bar F, % = 100 Component: Rear Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 6.7.1.4 - Tube Forces Des. Pressure, Shell pu = 1 bar Tensile Stress, Tubes sR = 59.8 bar Des. Pressure, Tubes pi = 2 bar Comp. Stress, Tubes sR = - Pressure p1 = pu+sR = 60.8 bar Test Pressure, Shell p1'= 1 bar Pressure p2 = pi-sR = 2 bar Test Pressure, Tubes p2'= 1 bar Maximum Pressure p = 60.8 bar Expanded Length lw = 0 mm 6.7.1.1 - Required Wall Thickness, mm Operating Testing s = 0,4*d2*SQRT(p*S/(10*K) = 22.8 2.5 (12) Loaded Area AR = PI/4*((Da-2*se)**2-n*da**2)/n = 517.9 mm2 Bild 12 Effective Area AW = (da-di)*lw = 0 mm2 (13) AW <= 0.1*da*lw = 0 mm2 (14) Tube Forces, N Operating Testing Tensile Force FR = AR*p1/10 = 3149 52 (21) Compressive Force FR = AR*p2/10 = 104 52 (21) Maximum Force FR = 3149 52 N Allowable Loading of the Expanded Joint FR/AW = 0 0 N/mm2 Component: Rear Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 B5 - 6.5.3 - Calculation of the Buckling Loads and Wall Thickness Buckling Length lk = 1400 mm Design Factor C = 0.3 J = 0,049*(da**4-di**4) = 9611 Weakening Factor v = 0.219 v = (t-da)/t Slenderness Ratio La = 4*lk/SQRT(da**2-di**2) = 171.5 (9a) Slenderness Ratio Range La0 = PI*SQRT(E/K) = 93.8 (9b) Allowable Buckling Load, N Operating Testing Fk = PI**2*E*J/(lk**2*3.0) or (8a) Fk = (K/S)*PI*((da**2-di**2)/4)*(1-(La/La0)*(1-S/3)) = 3197 3207 (8b) Maximum Buckling Load FRcmax = 104 52 Smallest Weld Thickness g = 0,4*FR*S/(da*K) = 0.3 0 mm (15) 6.7.1.5 - Required Tubesheet Thickness (FRcmax > Fk) s = C*SQRT(((D1**2-n*di**2)/v)*(pi*S/(10*K))) = 31.3 18.9 mm (16) Component: Rear Tubesheet AD-Merkblatt B 5 - Unstayed and Stayed Flat Ends and Plates - January 1995 6.7.5 - Circular, Flat Tubesheets on Heat Exchangers with Expansion Joints Exp. Joint Diameter Dk = 1964 mm Outer Tube Limit l = 656.5 mm Design Diameter D3 = (Dk+Da)/2 = 1684 mm Design Pressure p = pi+pu*(D3**2-4*l**2)/D1**2 = 2.6 bar (26) Fig. 16 Ratio l/D1 = 0.47 Ratio dt/dD = 1.04 Design Factor C5 = 0.19 Table 1 Type = - Required Tubesheet Thickness s = C5*D1*SQRT(p*S/(10*K*v)) = 23.9 mm (27)