| $ $
| material | $\mathrm{ }$
|
| $ $
| testing group | $\mathrm{ }$
|
| $ $
| production according to temperature | $\mathrm{ }$
|
| $ $
| seamless product | $\mathrm{ }$
|
| $ $
| material of bolt | $\mathrm{ }$
|
| $ $
| material of the shell | $\mathrm{ }$
|
| $ $
| type of material | $\mathrm{ }$
|
| $ $
| class | $\mathrm{ }$
|
| $ $
| type of material | $\mathrm{ }$
|
| $ $
| min. elongation after fracture | $\mathrm{ }$
|
| $ $
| type of material of the shell | $\mathrm{ }$
|
| $ $
| min. elongation after fracture of the shell | $\mathrm{ }$
|
| $ $
| type of material of bolt | $\mathrm{ }$
|
| $ $
| material of the nozzle | $\mathrm{ }$
|
| $ $
| type of material of the nozzle | $\mathrm{ }$
|
| $ $
| min. elongation after fracture of the nozzle | $\mathrm{ }$
|
| $ $
| material of nut | $\mathrm{ }$
|
| $ $
| material group | $\mathrm{ }$
|
| $2b''$
| effective gasket pressure width | $\mathrm{mm}$
|
| $A$
| outside diameter of the flange | $\mathrm{mm}$
|
| $A$
| factor $ A $ | $\mathrm{ }$
|
| $A$
| parameter $ A $ | $\mathrm{ }$
|
| $A$
| factor $ A $ | $\mathrm{ }$
|
| $A$
| total area of the reinforcement | $\mathrm{mm^2}$
|
| $A$
| inside diameter of flange | $\mathrm{mm}$
|
| $A'$
| nozzle reiforcement area | $\mathrm{mm^2}$
|
| $A_1$
| factor $ A_1 $ | $\mathrm{ }$
|
| $A_1$
| inside diameter of gasket contact face | $\mathrm{mm}$
|
| $A_B$
| total cross-sectional area of bolts at the section of least bolt diameter | $\mathrm{mm^2}$
|
| $A_{1_{test}}$
| factor $ A_{1_{test}} $ | $\mathrm{ }$
|
| $A_{B,min}$
| total required cross-sectional area of bolts | $\mathrm{mm^2}$
|
| $A_{test}$
| parameter $ A_{test} $ | $\mathrm{ }$
|
| $B$
| inside diameter of flange | $\mathrm{mm}$
|
| $B$
| parameter $ B $ | $\mathrm{ }$
|
| $B$
| factor $ B $ | $\mathrm{ }$
|
| $B$
| outside diameter of the flange | $\mathrm{mm}$
|
| $B_1$
| factor $ B_1 $ | $\mathrm{ }$
|
| $B_{1_{test}}$
| factor $ B_{1_{test}} $ | $\mathrm{ }$
|
| $B_{test}$
| parameter $ B_{test} $ | $\mathrm{ }$
|
| $C$
| bolt pitch circle diameter | $\mathrm{mm}$
|
| $C$
| factor $ C $ | $\mathrm{ }$
|
| $C_1$
| factor $ C_1 $ | $\mathrm{ }$
|
| $C_1$
| shape factor for calculation of circular flat ends | $\mathrm{ }$
|
| $C_1$
| constant $ C_1 $ | $\mathrm{ }$
|
| $C_2$
| factor $ C_2 $ | $\mathrm{ }$
|
| $C_2$
| shape factor for calculation of circular flat ends | $\mathrm{ }$
|
| $C_2$
| constant $ C_2 $ | $\mathrm{ }$
|
| $C_3$
| factor $ C_3 $ | $\mathrm{ }$
|
| $C_3$
| shape factors for calculation of flat ends of non-circular shape | $\mathrm{ }$
|
| $C_4$
| factor $ C_4 $ | $\mathrm{ }$
|
| $C_4$
| shape factors for calculation of flat ends of non-circular shape | $\mathrm{ }$
|
| $C_5$
| factor $ C_5 $ | $\mathrm{ }$
|
| $C_6$
| factor $ C_6 $ | $\mathrm{ }$
|
| $C_7$
| factor $ C_7 $ | $\mathrm{ }$
|
| $C_8$
| factor $ C_8 $ | $\mathrm{ }$
|
| $C_9$
| factor $ C_9 $ | $\mathrm{ }$
|
| $C_F$
| bolt pitch correction factor | $\mathrm{ }$
|
| $C_{10}$
| factor $ C_{10} $ | $\mathrm{ }$
|
| $C_{11}$
| factor $ C_{11} $ | $\mathrm{ }$
|
| $C_{12}$
| factor $ C_{12} $ | $\mathrm{ }$
|
| $C_{13}$
| factor $ C_{13} $ | $\mathrm{ }$
|
| $C_{14}$
| factor $ C_{14} $ | $\mathrm{ }$
|
| $C_{15}$
| factor $ C_{15} $ | $\mathrm{ }$
|
| $C_{16}$
| factor $ C_{16} $ | $\mathrm{ }$
|
| $C_{17}$
| factor $ C_{17} $ | $\mathrm{ }$
|
| $C_{18}$
| factor $ C_{18} $ | $\mathrm{ }$
|
| $C_{19}$
| factor $ C_{19} $ | $\mathrm{ }$
|
| $C_{1_{test}}$
| shape factor for calculation of circular flat ends for testing load cases | $\mathrm{ }$
|
| $C_{20}$
| factor $ C_{20} $ | $\mathrm{ }$
|
| $C_{21}$
| factor $ C_{21} $ | $\mathrm{ }$
|
| $C_{22}$
| factor $ C_{22} $ | $\mathrm{ }$
|
| $C_{23}$
| factor $ C_{23} $ | $\mathrm{ }$
|
| $C_{24}$
| factor $ C_{24} $ | $\mathrm{ }$
|
| $C_{25}$
| factor $ C_{25} $ | $\mathrm{ }$
|
| $C_{26}$
| factor $ C_{26} $ | $\mathrm{ }$
|
| $C_{27}$
| factor $ C_{27} $ | $\mathrm{ }$
|
| $C_{28}$
| factor $ C_{28} $ | $\mathrm{ }$
|
| $C_{29}$
| factor $ C_{29} $ | $\mathrm{ }$
|
| $C_{30}$
| factor $ C_{30} $ | $\mathrm{ }$
|
| $C_{31}$
| factor $ C_{31} $ | $\mathrm{ }$
|
| $C_{32}$
| factor $ C_{32} $ | $\mathrm{ }$
|
| $C_{33}$
| factor $ C_{33} $ | $\mathrm{ }$
|
| $C_{34}$
| factor $ C_{34} $ | $\mathrm{ }$
|
| $C_{35}$
| factor $ C_{35} $ | $\mathrm{ }$
|
| $C_{36}$
| factor $ C_{36} $ | $\mathrm{ }$
|
| $C_{37}$
| factor $ C_{37} $ | $\mathrm{ }$
|
| $D_F$
| diameter of the flat part of an end with a tapered hub | $\mathrm{mm}$
|
| $D_L$
| inside diameter of seal weld lip | $\mathrm{mm}$
|
| $D_c$
| mean diameter of the cylinder at the junction with the cone | $\mathrm{mm}$
|
| $D_e$
| outside diameter of the cylindrical flange | $\mathrm{mm}$
|
| $D_i$
| inside diameter of shell | $\mathrm{mm}$
|
| $D_i$
| inside diameter of the cylindrical flange | $\mathrm{mm}$
|
| $D_i$
| inside diameter of the cone | $\mathrm{mm}$
|
| $D_i$
| inside diameter of the cylindrical shell welded to a flat end | $\mathrm{mm}$
|
| $D_{eq}$
| equivalent diameter of an end with a hub | $\mathrm{mm}$
|
| $E_1$
| factor $ E_1 $ | $\mathrm{ }$
|
| $E_2$
| factor $ E_2 $ | $\mathrm{ }$
|
| $E_3$
| factor $ E_3 $ | $\mathrm{ }$
|
| $E_4$
| factor $ E_4 $ | $\mathrm{ }$
|
| $E_5$
| factor $ E_5 $ | $\mathrm{ }$
|
| $E_6$
| factor $ E_6 $ | $\mathrm{ }$
|
| $E_T$
| modulus of elasticity for normal operating load cases | $\mathrm{MPa}$
|
| $E_{T_{test}}$
| modulus of elasticity for testing load cases | $\mathrm{MPa}$
|
| $F$
| factor $ F $ | $\mathrm{ }$
|
| $F_e$
| coefficient $ F_e $ | $\mathrm{ }$
|
| $F_s$
| coefficient $ F_s $ | $\mathrm{ }$
|
| $G$
| diameter of gasket load reaction | $\mathrm{mm}$
|
| $G$
| factor $ G $ | $\mathrm{ }$
|
| $G$
| diameter at location of gasket load reaction | $\mathrm{mm}$
|
| $G_0$
| outside diameter of gasket or outside diameter of flange, whichever is less | $\mathrm{mm}$
|
| $H$
| total hydrostatic end force | $\mathrm{N}$
|
| $H$
| factor $ H $ | $\mathrm{ }$
|
| $H_D$
| hydrostatic end force applied via shell to flange | $\mathrm{N}$
|
| $H_G$
| compression load on gasket to ensure tight joint | $\mathrm{N}$
|
| $H_R$
| balancing reaction force outside bolt circle in opposition to moments due to loads inside bolt circle | $\mathrm{N}$
|
| $H_T$
| hydrostatic end force due to pressure on flange face | $\mathrm{N}$
|
| $H_T$
| net pressure load on the flange faces | $\mathrm{N}$
|
| $H_{D_{test}}$
| hydrostatic end force applied via shell to flange for testing load cases | $\mathrm{N}$
|
| $H_{G_{test}}$
| compression load on gasket to ensure tight joint for testing load cases | $\mathrm{N}$
|
| $H_{R_{test}}$
| balancing reaction force outside bolt circle in opposition to moments due to loads inside bolt circle for testing load cases | $\mathrm{N}$
|
| $H_{T_{test}}$
| hydrostatic end force due to pressure on flange face for testing load cases | $\mathrm{N}$
|
| $H_{T_{test}}$
| net pressure load on the flange faces for testing load cases | $\mathrm{N}$
|
| $H_{test}$
| total hydrostatic end force for testing load cases | $\mathrm{N}$
|
| $J$
| factor $ J $ | $\mathrm{ }$
|
| $K$
| shape factor for an ellipsoidal end | $\mathrm{ }$
|
| $K$
| ratio of the flange diameters | $\mathrm{ }$
|
| $K$
| factor $ K $ | $\mathrm{ }$
|
| $L$
| unsupported length of the shell | $\mathrm{mm}$
|
| $L_{con}$
| axial length of a cone | $\mathrm{mm}$
|
| $L_{cyl}$
| cylinder length between tangent lines | $\mathrm{mm}$
|
| $M$
| mean stress sensitivity factor | $\mathrm{ }$
|
| $M_R$
| balancing radial moment in flange along line of bolt holes | $\mathrm{Nmm}$
|
| $M_{A}$
| moment exerted on the flange per unit of length for assembly condition | $\mathrm{Nmm/mm}$
|
| $M_{R_{test}}$
| balancing radial moment in flange along line of bolt holes for testing load cases | $\mathrm{Nmm}$
|
| $M_{T-A}$
| total moment acting upon flange for assembly condition | $\mathrm{Nmm}$
|
| $M_{T-op}$
| total moment acting upon flange for operating condition | $\mathrm{Nmm}$
|
| $M_{T-test}$
| total moment acting upon flange for testing load cases | $\mathrm{Nmm}$
|
| $M_{op}$
| moment exerted on the flange per unit of length for operating condition | $\mathrm{Nmm/mm}$
|
| $M_{test}$
| moment exerted on the flange per unit of length for testing load cases | $\mathrm{Nmm/mm}$
|
| $N$
| parameter $ N $ | $\mathrm{ }$
|
| $N$
| factor $ N $ | $\mathrm{ }$
|
| $N$
| allowable number of cycles obtained from the fatigue design curves | $\mathrm{ }$
|
| $P$
| calculation pressure | $\mathrm{MPa}$
|
| $P_c$
| design pressure in a heating/cooling channel | $\mathrm{MPa}$
|
| $P_e$
| external calculation pressure | $\mathrm{MPa}$
|
| $P_m$
| theoretical elastic instability pressure for collapse of a perfect cylindrical, conical or spherical shell for normal operating load cases | $\mathrm{MPa}$
|
| $P_m/P_y$
| radio $ P_m/P_y $ | $\mathrm{ }$
|
| $P_r/P_y$
| radio $ P_r/P_y $ | $\mathrm{ }$
|
| $P_y$
| pressure at which mean circumferential stress in cylindrical or conical shell midway between stiffeners, or in a spherical shell, reaches yield point for normal operating load cases | $\mathrm{MPa}$
|
| $P_{e_{test}}$
| external test pressure | $\mathrm{MPa}$
|
| $P_{m_{test}}$
| theoretical elastic instability pressure for collapse of a perfect cylindrical, conical or spherical shell for testing load cases | $\mathrm{MPa}$
|
| $P_{m_{test}}/P_{y_{test}}$
| radio $ P_{m_{test}}/P_{y_{test}} $ | $\mathrm{ }$
|
| $P_{r_{test}}/P_{y_{test}}$
| radio $ P_{r_{test}}/P_{y_{test}} $ | $\mathrm{ }$
|
| $P_{test}$
| test pressure | $\mathrm{MPa}$
|
| $P_{y_{test}}$
| pressure at which mean circumferential stress in cylindrical or conical shell midway between stiffeners, or in a spherical shell, reaches yield point for testing load cases | $\mathrm{MPa}$
|
| $Q$
| factor $ Q $ | $\mathrm{ }$
|
| $R$
| inside spherical radius of central part of torispherical end | $\mathrm{mm}$
|
| $R$
| mean radius of a cylindrical or spherical shell, or mean crown radius of a torispherical end | $\mathrm{mm}$
|
| $R_m$
| tensile strength | $\mathrm{MPa}$
|
| $R_p$
| proof strength | $\mathrm{MPa}$
|
| $R_z$
| surface roughness (peak to valley height) | $\mathrm{μm}$
|
| $R_{m/20/bolt}$
| tensile strength of bolt | $\mathrm{MPa}$
|
| $R_{m/20/n}$
| tensile strength of the nozzle | $\mathrm{MPa}$
|
| $R_{m/20/s}$
| tensile strength of the shell | $\mathrm{MPa}$
|
| $R_{m/20}$
| tensile strength | $\mathrm{MPa}$
|
| $R_{m/T/n}$
| tensile strength at temperature $ T $ of the nozzle | $\mathrm{MPa}$
|
| $R_{m/T/s}$
| tensile strength at temperature $ T $ of the shell | $\mathrm{MPa}$
|
| $R_{m/T^*}$
| tensile strength at temperature $ T^* $ | $\mathrm{MPa}$
|
| $R_{m/T_{assembly}}$
| tensile strength at temperature $ T_{assembly} $ | $\mathrm{MPa}$
|
| $R_{m/T_{test}/n}$
| tensile strength at temperature $ T_{test} $ of the nozzle | $\mathrm{MPa}$
|
| $R_{m/T_{test}/s}$
| tensile strength at temperature $ T_{test} $ of the shell | $\mathrm{MPa}$
|
| $R_{m/T_{test}}$
| tensile strength at temperature $ T_{test} $ | $\mathrm{MPa}$
|
| $R_{m/T}$
| tensile strength at temperature $ T $ | $\mathrm{MPa}$
|
| $R_{m/bolt/T^*}$
| tensile strength of bolt at temperature $ T^* $ | $\mathrm{MPa}$
|
| $R_{m/bolt/T_{assembly}}$
| tensile strength of bolt at temperature $ T_{assembly} $ | $\mathrm{MPa}$
|
| $R_{m/bolt/T_{test}}$
| tensile strength of bolt at temperature $ T_{test} $ | $\mathrm{MPa}$
|
| $R_{m/bolt/T}$
| tensile strength of bolt at temperature $ T $ | $\mathrm{MPa}$
|
| $R_{p0.2/T/n}$
| 0.2 % proof strength at temperature $ T $ of the nozzle | $\mathrm{MPa}$
|
| $R_{p0.2/T/s}$
| 0.2 % proof strength at temperature $ T $ of the shell | $\mathrm{MPa}$
|
| $R_{p0.2/T^*}$
| 0.2 % proof strength at temperature $ T^* $ | $\mathrm{MPa}$
|
| $R_{p0.2/T_{assembly}}$
| 0.2 % proof strength at temperature $ T_{assembly} $ | $\mathrm{MPa}$
|
| $R_{p0.2/T_{test}/n}$
| 0.2 % proof strength at temperature $ T_{test} $ of the nozzle | $\mathrm{MPa}$
|
| $R_{p0.2/T_{test}/s}$
| 0.2 % proof strength at temperature $ T_{test} $ of the shell | $\mathrm{MPa}$
|
| $R_{p0.2/T_{test}}$
| 0.2 % proof strength at temperature $ T_{test} $ | $\mathrm{MPa}$
|
| $R_{p0.2/T}$
| 0.2 % proof strength at temperature $ T $ | $\mathrm{MPa}$
|
| $R_{p0.2/bolt/T_{assembly}}$
| 0.2 % proof strength of bolt at temperature $ T_{assembly} $ | $\mathrm{MPa}$
|
| $R_{p0.2/bolt/T_{test}}$
| 0.2 % proof strength of bolt at temperature $ T_{test} $ | $\mathrm{MPa}$
|
| $R_{p0.2/bolt/T}$
| 0.2 % proof strength of bolt at temperature $ T $ | $\mathrm{MPa}$
|
| $R_{p0.2/nut/T_{assembly}}$
| 0.2 % proof strength of nut at temperature $ T_{assembly} $ | $\mathrm{MPa}$
|
| $R_{p0.2/nut/T_{test}}$
| 0.2 % proof strength of nut at temperature $ T_{test} $ | $\mathrm{MPa}$
|
| $R_{p0.2/nut/T}$
| 0.2 % proof strength of nut at temperature $ T $ | $\mathrm{MPa}$
|
| $R_{p1.0/T/n}$
| 1.0 % proof strength at temperature $ T $ of the nozzle | $\mathrm{MPa}$
|
| $R_{p1.0/T/s}$
| 1.0 % proof strength at temperature $ T $ of the shell | $\mathrm{MPa}$
|
| $R_{p1.0/T^*}$
| 1.0 % proof strength at temperature $ T^* $ | $\mathrm{MPa}$
|
| $R_{p1.0/T_{assembly}}$
| 1.0 % proof strength at temperature $ T_{assembly} $ | $\mathrm{MPa}$
|
| $R_{p1.0/T_{test}/n}$
| 1.0 % proof strength at temperature $ T_{test} $ of the nozzle | $\mathrm{MPa}$
|
| $R_{p1.0/T_{test}/s}$
| 1.0 % proof strength at temperature $ T_{test} $ of the shell | $\mathrm{MPa}$
|
| $R_{p1.0/T_{test}}$
| 1.0 % proof strength at temperature $ T_{test} $ | $\mathrm{MPa}$
|
| $R_{p1.0/T}$
| 1.0 % proof strength at temperature $ T $ | $\mathrm{MPa}$
|
| $S$
| factor $ S $ | $\mathrm{ }$
|
| $T$
| calculation temperature | $\mathrm{°C}$
|
| $T^*$
| assumed mean cycle temperature | $\mathrm{°C}$
|
| $T_{assembly}$
| assembly temperature | $\mathrm{°C}$
|
| $T_{test}$
| test temperature | $\mathrm{°C}$
|
| $U$
| factor $ U $ | $\mathrm{ }$
|
| $V$
| parameter $ V $ | $\mathrm{ }$
|
| $V_{test}$
| parameter $ V_{test} $ | $\mathrm{ }$
|
| $W$
| design bolt load for assembly condition | $\mathrm{N}$
|
| $W_A$
| minimum required bolt load for assembly condition | $\mathrm{N}$
|
| $W_{op}$
| minimum required bolt load for operating condition | $\mathrm{N}$
|
| $W_{test}$
| minimum required bolt load for testing load cases | $\mathrm{N}$
|
| $X$
| ratio of knuckle inside radius to shell inside diameter | $\mathrm{ }$
|
| $Y$
| parameter $ Y $ | $\mathrm{ }$
|
| $Y_1$
| calculation coefficient $ Y_1 $ for opening reinforcement | $\mathrm{ }$
|
| $Y_2$
| calculation coefficient $ Y_2 $ for opening reinforcement | $\mathrm{ }$
|
| $Z$
| parameter $ Z $ | $\mathrm{ }$
|
| $\overline{σ}_{eq,r}$
| reduced mean equivalent stress for elastic-plastic conditions | $\mathrm{MPa}$
|
| $\overline{σ}_{eq}$
| mean equivalent stress | $\mathrm{MPa}$
|
| $a$
| factor $ a $ | $\mathrm{ }$
|
| $a$
| length of shell covered by heating/cooling coil | $\mathrm{mm}$
|
| $a'$
| smaller width dimension in a rectangular, elliptical or obround end | $\mathrm{mm}$
|
| $b$
| effective gasket or joint seating width | $\mathrm{mm}$
|
| $b$
| factor $ b $ | $\mathrm{ }$
|
| $b'$
| greater width dimension in a rectangular, elliptical or obround end | $\mathrm{mm}$
|
| $b'$
| effective assembly width | $\mathrm{mm}$
|
| $b'_0$
| basic assembly width effective under initial tightening up | $\mathrm{mm}$
|
| $c$
| factor $ c $ | $\mathrm{ }$
|
| $c$
| mean distance between the gasket reaction and the bolt pitch circle diameter | $\mathrm{mm}$
|
| $d$
| diameter of an opening or equivalent diameter of a nozzle | $\mathrm{mm}$
|
| $d$
| arithmetic mean of the diameters of the openings or the mean equivalent diameter of the nozzles | $\mathrm{mm}$
|
| $d$
| equivalent diameter of a nozzle | $\mathrm{mm}$
|
| $d_b$
| bolt outside diameter | $\mathrm{mm}$
|
| $d_e$
| nozzle outside diameter | $\mathrm{mm}$
|
| $d_h$
| diameter of bore holes | $\mathrm{mm}$
|
| $d_h$
| diameter of bolt holes | $\mathrm{mm}$
|
| $d_i$
| inside diameter of the nozzle | $\mathrm{mm}$
|
| $d_n$
| bolt nominal diameter | $\mathrm{mm}$
|
| $e$
| required thickness | $\mathrm{mm}$
|
| $e$
| minimum flange thickness, measured at the thinnest section | $\mathrm{mm}$
|
| $e$
| minimum required thickness for a flat end with a hub | $\mathrm{mm}$
|
| $e$
| minimum thickness within the gasket | $\mathrm{mm}$
|
| $e$
| the minimum thickness for a flat end with a full-face gasket | $\mathrm{mm}$
|
| $e$
| thickness of the flat end | $\mathrm{mm}$
|
| $e$
| cylinder thickness required to carry the pressure in the channels | $\mathrm{mm}$
|
| $e_1$
| minimum thickness for the flanged extension | $\mathrm{mm}$
|
| $e_1$
| required thickness of cylinder at junction | $\mathrm{mm}$
|
| $e_2$
| required thickness of cone and knuckle at junction | $\mathrm{mm}$
|
| $e_A$
| minimum thickness within the gasket for assembly cases | $\mathrm{mm}$
|
| $e_a$
| analysis thickness | $\mathrm{mm}$
|
| $e_b$
| required thickness of knuckle to avoid plastic buckling | $\mathrm{mm}$
|
| $e_j$
| required or analysis thickness at a junction at the large end of a cone | $\mathrm{mm}$
|
| $e_j$
| required or analysis thickness at a junction at the small end of a cone | $\mathrm{mm}$
|
| $e_n$
| bolt diameter | $\mathrm{mm}$
|
| $e_n$
| material thickness | $\mathrm{mm}$
|
| $e_p$
| minimum thickness within the gasket for calculation pressure | $\mathrm{mm}$
|
| $e_r$
| minimum required thickness under a relief groove | $\mathrm{mm}$
|
| $e_s$
| required thickness of end to limit membrane stress in central part | $\mathrm{mm}$
|
| $e_s$
| analysis thickness of a uniform cylindrical shell, or the equivalent thickness of a tapered cylindrical shell, adjacent to a flat end | $\mathrm{mm}$
|
| $e_y$
| required thickness of knuckle to avoid axisymmetric yielding | $\mathrm{mm}$
|
| $e_{1,a}$
| analysis thickness for the flanged extension | $\mathrm{mm}$
|
| $e_{af}$
| analysis thickness of an end with a hub | $\mathrm{mm}$
|
| $e_{af}$
| analysis thickness | $\mathrm{mm}$
|
| $e_{b_{test}}$
| required thickness of knuckle to avoid plastic buckling for testing load cases | $\mathrm{mm}$
|
| $e_{con_{test}}$
| required thickness of cone for testing load cases | $\mathrm{mm}$
|
| $e_{con}$
| required thickness of cone | $\mathrm{mm}$
|
| $e_{cyl}$
| required thickness of cylinder | $\mathrm{mm}$
|
| $e_{p1}$
| minimum thickness for the flanged extension for calculation pressure | $\mathrm{mm}$
|
| $e_{p_{test}1}$
| minimum thickness for the flanged extension for test pressure | $\mathrm{mm}$
|
| $e_{p_{test}}$
| minimum thickness within the gasket for test pressure | $\mathrm{mm}$
|
| $e_{r_{test}}$
| minimum required thickness under a relief groove for testing load cases | $\mathrm{mm}$
|
| $e_{s_{test}}$
| required thickness of end to limit membrane stress in central part for testing load cases | $\mathrm{mm}$
|
| $e_{test}$
| required thickness for testing load cases | $\mathrm{mm}$
|
| $e_{test}$
| minimum flange thickness, measured at the thinnest section for testing load cases | $\mathrm{mm}$
|
| $e_{test}$
| minimum required thickness for a flat end with a hub for testing load cases | $\mathrm{mm}$
|
| $e_{y_{test}}$
| required thickness of knuckle to avoid axisymmetric yielding for testing load cases | $\mathrm{mm}$
|
| $f_1$
| factor $ f_1 $ | $\mathrm{ }$
|
| $f_A$
| maximum allowed value of the nominal design stress for assembly cases | $\mathrm{MPa}$
|
| $f_B$
| bolt nominal design stress for normal operating load cases | $\mathrm{MPa}$
|
| $f_b$
| design stress for buckling formula for normal operating load cases | $\mathrm{MPa}$
|
| $f_b$
| overall correction factor applied to bolts | $\mathrm{ }$
|
| $f_d$
| maximum allowed value of the nominal design stress for normal operating load cases | $\mathrm{MPa}$
|
| $f_e$
| thickness correction factor in unwelded components | $\mathrm{ }$
|
| $f_m$
| mean stress correction factor | $\mathrm{ }$
|
| $f_n$
| nominal design stress at calculation temperature of the nozzle for normal operating load cases | $\mathrm{MPa}$
|
| $f_s$
| nominal design stress at calculation temperature of the shell for normal operating load cases | $\mathrm{MPa}$
|
| $f_s$
| surface finish correction factor | $\mathrm{ }$
|
| $f_u$
| overall correction factor applied to unwelded components | $\mathrm{ }$
|
| $f_w$
| overall correction factor applied to welded components | $\mathrm{ }$
|
| $f_{B,A}$
| bolt nominal design stress at assembly temperature | $\mathrm{MPa}$
|
| $f_{B_{test}}$
| bolt nominal design stress for testing load cases | $\mathrm{MPa}$
|
| $f_{b_{test}}$
| design stress for buckling formula for testing load cases | $\mathrm{MPa}$
|
| $f_{ew}$
| thickness correction factor in welded components | $\mathrm{ }$
|
| $f_{min_{test}}$
| lower of the nominal design stresses $ f_{test} $ of the end and $ f_{s_{test}} $ of the shell for testing load cases | $\mathrm{MPa}$
|
| $f_{min}$
| lower of the nominal design stresses $ f_d $ of the end and $ f_s $ of the shell for normal operating load cases | $\mathrm{MPa}$
|
| $f_{n_{test}}$
| nominal design stress at calculation temperature of the nozzle for testing load cases | $\mathrm{MPa}$
|
| $f_{s_{test}}$
| nominal design stress at calculation temperature of the shell for testing load cases | $\mathrm{MPa}$
|
| $f_{t^*}$
| temperature correction factor | $\mathrm{ }$
|
| $f_{test}$
| maximum allowed value of the nominal design stress for testing load cases | $\mathrm{MPa}$
|
| $g$
| factor $ g $ | $\mathrm{ }$
|
| $g_0$
| thickness of hub at small end | $\mathrm{mm}$
|
| $g_1$
| thickness of hub at back of flange | $\mathrm{mm}$
|
| $h$
| hub length | $\mathrm{mm}$
|
| $h$
| smallest distance between the centre of an opening and the inside of the shell | $\mathrm{mm}$
|
| $h$
| external height of dished end $ h $ | $\mathrm{mm}$
|
| $h'$
| external height of dished end $ h' $ | $\mathrm{mm}$
|
| $h''$
| external height of dished end $ h'' $ | $\mathrm{mm}$
|
| $h_D$
| radial distance from bolt circle to circle on which $ H_D $ acts | $\mathrm{mm}$
|
| $h_G$
| radial distance from gasket load reaction to bolt circle | $\mathrm{mm}$
|
| $h_R$
| radial distance from bolt circle to circle on which $ H_R $ acts | $\mathrm{mm}$
|
| $h_T$
| radial distance from bolt circle to circle on which $ H_T $ acts | $\mathrm{mm}$
|
| $h_i$
| inside height of end measured from the tangent line | $\mathrm{mm}$
|
| $h_w$
| distance between the external wall of an end with a relief groove and the weld on the shell | $\mathrm{mm}$
|
| $k$
| stress factor | $\mathrm{ }$
|
| $k$
| distance between the centres of the openings | $\mathrm{mm}$
|
| $l_0$
| length parameter | $\mathrm{ }$
|
| $l_1$
| length along cylinder | $\mathrm{mm}$
|
| $l_2$
| length along cone at large or small end | $\mathrm{mm}$
|
| $l_b$
| length of bolts in threaded holes | $\mathrm{mm}$
|
| $l_n$
| length nut | $\mathrm{mm}$
|
| $l_{cyl}$
| length of cylindrical shell | $\mathrm{mm}$
|
| $m$
| gasket factor | $\mathrm{ }$
|
| $m_1$
| exponent $ m_1 $ | $\mathrm{ }$
|
| $m_2$
| exponent $ m_2 $ | $\mathrm{ }$
|
| $n$
| number of bolts | $\mathrm{ }$
|
| $n_{EQ}$
| equivalent bolt number | $\mathrm{ }$
|
| $n_{cyl}$
| number of circumferential waves for an unstiffened part of a cylinder | $\mathrm{ }$
|
| $r$
| inside radius of curvature of a knuckle | $\mathrm{mm}$
|
| $r$
| inside radius of a hub | $\mathrm{mm}$
|
| $r$
| knuckle radius | $\mathrm{mm}$
|
| $r_d$
| inside radius of the relief groove | $\mathrm{mm}$
|
| $s$
| factor $ s $ | $\mathrm{ }$
|
| $t_B$
| mean bolt pitch in a bolted flat end | $\mathrm{mm}$
|
| $t_{Bmax}$
| maximum bolt pitch | $\mathrm{mm}$
|
| $y$
| minimum gasket or joint seating pressure | $\mathrm{MPa}$
|
| $z$
| joint coefficient | $\mathrm{ }$
|
| $Δσ$
| stress range | $\mathrm{MPa}$
|
| $Δσ_D$
| endurance limit | $\mathrm{MPa}$
|
| $Δσ_{Cut}$
| cut-off limit | $\mathrm{MPa}$
|
| $Δσ_{eq}$
| equivalent stress range | $\mathrm{MPa}$
|
| $α$
| semi angle of cone at apex | $\mathrm{°}$
|
| $β$
| factor $ β $ | $\mathrm{ }$
|
| $β_F$
| factor $ β_F $ | $\mathrm{ }$
|
| $β_H$
| factor $ β_H $ | $\mathrm{ }$
|
| $β_K$
| weakening factor due to presence of nozzle | $\mathrm{ }$
|
| $β_T$
| factor $ β_T $ | $\mathrm{ }$
|
| $β_U$
| factor $ β_U $ | $\mathrm{ }$
|
| $β_V$
| factor $ β_V $ | $\mathrm{ }$
|
| $β_Y$
| factor $ β_Y $ | $\mathrm{ }$
|
| $β_{0.06}$
| factor $ β_{0.06} $ | $\mathrm{ }$
|
| $β_{0.1}$
| factor $ β_{0.1} $ | $\mathrm{ }$
|
| $β_{0.2}$
| factor $ β_{0.2} $ | $\mathrm{ }$
|
| $β_{FL}$
| factor $ β_{FL} $ | $\mathrm{ }$
|
| $β_{K_{test}}$
| weakening factor due to presence of nozzle for testing load cases | $\mathrm{ }$
|
| $β_{VL}$
| factor $ β_{VL} $ | $\mathrm{ }$
|
| $γ$
| factor $ γ $ | $\mathrm{ }$
|
| $δ_b$
| distance between centre lines of adjacent bolts | $\mathrm{mm}$
|
| $ε$
| mean elastic circumferential strain at collapse | $\mathrm{ }$
|
| $λ$
| factor $ λ $ | $\mathrm{ }$
|
| $ν$
| Poisson's ratio | $\mathrm{ }$
|
| $ρ$
| factor $ ρ $ | $\mathrm{ }$
|
| $σ_e$
| nominal elastic limit for shell for normal operating load cases | $\mathrm{MPa}$
|
| $σ_{H_{A}}$
| longitudinal stress in hub for assembly condition | $\mathrm{MPa}$
|
| $σ_{H_{op}}$
| longitudinal stress in hub for operating condition | $\mathrm{MPa}$
|
| $σ_{H_{test}}$
| longitudinal stress in hub for testing load cases | $\mathrm{MPa}$
|
| $σ_{e_{test}}$
| nominal elastic limit for shell for testing load cases | $\mathrm{MPa}$
|
| $σ_{eq\ max}$
| maximum equivalent stress range | $\mathrm{MPa}$
|
| $σ_{r_{A}}$
| radial stress in flange for assembly condition | $\mathrm{MPa}$
|
| $σ_{r_{op}}$
| radial stress in flange for operating condition | $\mathrm{MPa}$
|
| $σ_{r_{test}}$
| radial stress in flange for testing load cases | $\mathrm{MPa}$
|
| $σ_{θ_{A}}$
| tangential stress in flange for assembly condition | $\mathrm{MPa}$
|
| $σ_{θ_{op}}$
| tangential stress in flange for operating condition | $\mathrm{MPa}$
|
| $σ_{θ_{test}}$
| tangential stress in flange for testing load cases | $\mathrm{MPa}$
|
| $τ$
| factor $ τ $ | $\mathrm{ }$
|
| $φ$
| hub stress correction factor | $\mathrm{ }$
|
