r6155 I used calculation by hand.
I verified Nozzle Pipe and Shell thickness with Pressure and bending moments "distant" from nozzle-shell intersection and there are no problems:
σ = P*D/2*t + ML*D/2*I + MC*D/2*I
where
D = external diameter (Pipe/Vessel) [mm]
t = thickness (pipe/vessel) [mm]
Mc, ML = circum./long. bending moment [N*mm]
I = moment of inertia of pipe/vessel section [mm4].
My equipment is a pressure vessel at 25 barg in SA-516 Gr.70 at 250 °C.
Nozzle is 12" self reinforced.
That I don't understand is how to consider bending moment concentration stresses close to opening by hand.
With WRC formulation I have to use k*6*M/t^2 as stresses due to bending moment and the final result is very high, much higher than FEA analysis.
M = 150 kN*m -> 150kN*m/m
t = 25 mm
σ = 6*M/t^2 = 1440 MPa