BSukolsky,
If you only have internal pressure, it is relatively straightforward to calculate the free displacements of the ends of the two cylinders (that is, the displacement the joined ends would experience if they didn't restrain one another). Then determine the radial force and moment...
fem.fan,
I'm late to this discussion, but I've run into this as well. I once ran a model of a lightly loaded sharp inside corner down to an absurdly fine mesh size and found that the stress and plastic strain increased slowly and steadily at an increasing rate with diminishing element edge...
You've attached plots of crack tip stress intensity and J along the crack front. I'm not sure what your question is. You should try modeling some cases that you know the answer to, such as a center or edge cracked plate in plane strain under uniform tension. That will help you develop...
ASME VIII-2 does not generally have requirements for specific environmental cracking and corrosion issues. You formal responsibilities depend on whether you are the specifier, manufacturer or owner, as well as the specifics of your contract. Regardless, it's important that the vessel is fit...
I don't understand what the question is. If you know how the thickness varies, and it is axisymmetric, I would expect it to be easy to draw. If it is not axisymmetric, the artwork might get difficult, but I agree with DriveMeNuts that that is a CAD question. Bigger picture, though, do you...
The t^m term is a time hardening term for primary creep. The Arrhenius rate function defines temperature dependence. You can use either of these or both in concert in Ansys, as they account for different things. You can also use strain hardening, which is more often than not more...
I didn't say 5.2.3.2 doesn't make sense. I said that, if taken literally, it prohibits elastic analysis of cylinders, since their stiffness decreases with deformation.
For the cone-to-skirt junction, that's between you and the AI, but I probably would have included plasticity. I almost...
Some Curious Guy,
Area replacement is more tried-and-true than rigorous, but it does take care of the pressure thrust load. If you draw a circle on the side of the vessel, there is a radial thrust load inside the circle and Pr/t takes care of that. Cutting in a nozzle adds a stress...
I don't know if it's contributing to your problem, but your physics preference is set to CFD and it looks as if you are meshing a solid structure.
-mskds545
When it comes to large displacements and elastic analysis, I've always enjoyed paragraph 5.2.3.2. It's under limit analysis, but applies "equally to... primary stress limits of 5.2.2." This paragraph seems to prohibit elastic analysis if the stiffness is reduced with deformation, a large...
So, was it that I said "you measure it" rather than "someone measures it" that bothered you? The next sentence stated that data is already available for most fluids and you can look it up. The poster asked a question and I tried to help. Other people offered alternate answers. I hope one of...
I'm not sure why you found it necessary to take a rude tone with me, but perhaps you missed where I said that there is published data available for most fluids and recommended the OP check the tables in the back of a heat transfer text. I am also an engineer, by the way, and I am quite adept at...
In addition to high stress in the weld, it looks like the pad on the shell is highly stressed in bending. If this isn't acceptable, make the pad thicker to keep the bending stress at an acceptable level.
To decide if it's acceptable, you need to elaborate on what you are trying to prevent...
Yes, the text is clear that welds machined to smooth profiles may be evaluated using 5.5.4. There isn't a prohibition against using 5.5.4 for non-machined welds either, as far as I am aware, although I'm not sure how you would analyze the weld toe accurately with no dressing at all. Even with...
DriveMeNuts -- See this article for a rundown on how to import the shape from an eigenvalue buckling analysis into a static analysis and scale the deformation in ansys: http://www.padtinc.com/blog/eigenvalue-buckling-and-post-buckling-analysis-in-ansys-mechanical/.
IdanPV -- I'll second TGS4's...
In your pdf, the next step is to substitute k1 = k0 + a/2*(T1+T2), k2 = k0 + a/2*(T2+T3), k3 = k0 + a/2*(T3+T4). Because thermal conductivity is linear with temperature, you can use the average temperature. Whether you can use this to show analytically that Q is independent of L1, or if it's...
...in the tables in the back of most introductory heat transfer textbooks. They often list the kinematic viscosity. You want the dynamic viscosity, which is (kinematic viscosity)*(density). Viscosity is a function of temperature, so it will be different in the bulk and at the wall.
-mskds545
...of a cylinder, apply a pressure. When evaluating the FAD, you could just lump this in with KIP or you could run two load cases to get KIP and phi*KISR. The latter is exactly what you're doing when you use analytical stress intensity solutions. The former would be a bit more conservative...
Not sure if you're saying I should decline to answer his questions about elastic follow-up on principle, or that I should pack up my welding gear and go fix his plant instead of answering... but we're under quarantine, so the latter isn't really an option, and nobody should want me welding on...
