The equations for stresses in thin- and thick-wall cylinders can be found in many mechanics of materials references, and are summarized here, with a = inner radius, b = outer radius, r = radial position where stress is to be found, and t = wall thickness.
Notice that in thick-wall theory, the hoop stress varies with the radial position, while the stress is assumed to be constant in thin-wall theory. Comparing the substitution of a and b for r in the hoop stress thick-wall equation will convince you that stress is greater on the inner surface. The hoop stress variation in thick-walled vessels can be depicted as follows (the view shown corresponds to looking from above the pressure vessel):
By using the parameters given in the problem statement and the above formulae for hoop stress, we find that the maximum hoop stresses using the thin-wall and thick-wall approximations yield 3000 psi and 3571 psi, respectively. This corresponds to a 16% difference which tells us that the thin wall theory might not be adequate for this geometry. Thin-wall theory actually gives good results when b/a ratio is less than 1.10, and that is not the case here.
Notice that the axial stresses are constant for both theories since they do not depend on radius. For this example, the thin-wall and thick-wall approximations yield 1500 psi and 1285 psi, respectively.
The radial stresses at the inner and outer surfaces can be deduced from the boundary conditions:
The following tables display the results of these approximations:
We will fill in the missing information by performing an axisymmetric analysis using Ansys simulations. We will then compare the numerical results from the Ansys simulation to the analytical results.
Launch Ansys Workbench and start a "Static Structural" analysis on the project page as shown in the video below.