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Victor
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Comments
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That's strange. I don't understand either. He's my one that solves.
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No stress usually means it didn't converge. The stiffener comes away because the stiffness of the bonded contact joint is too low. I changed it to 1000 GPa/m and it stays pretty close. I also changed the pressure load from constant to ramped by re…
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A common way to get things to mesh is to set the max. element size. Here I used 0.5m and it worked.
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Don't use the internal solver for nonlinear. It's inferior to CCX in just about every way. *INFO and *WARNING messages are often normal and harmless. These ones look OK. *ERROR is what makes it fail. This one looks like it might be the same proble…
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That's correct. Both the elastic and *TIE options close up the gap in a strain-free way. EDIT: By leaving a gap, you're specifying something physically impossible so the software has some liberty in deciding what to do with it. The default option f…
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It's the dot product of displacement with the unit radial vector.
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Signed radial displacement is (x*u.x + z*u.z) / sqrt(x^2+z^2)
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It turns out the Y displacement constraint on the adjacent nodes is what's causing it. That error message was really misleading, sorry. I replaced it with a 10 000 GPa/m elastic support on the whole bottom surface of the 50rsa2 component. I've also…
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Thanks for reporting this bug. It's a known one that will be fixed in version 10. It happens with the Gradient contour plot option (not the Banded one) and a formula that has a divide by zero or similar problem.
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You can track it down using Edit -> Select nodes by number and enter 3498. Then see if either: * There are conflicting constraints which aren't physically possible, such as displacement by two different distances in the same direction or * T…
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Here are some tests. Connectivity of the mesh has a huge effect on memory requirements so I used two models at opposite extremes - a cube and a 1-element-thick plate. Real models would usually be somewhere between the two. Your 250000 nodes sounds …
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Oh. That does sound wrong, unless you have ~30 GB or more of RAM, in which case it's reasonable to have 10 GB unused by both CCX and the internal solver. I'm running some benchmarks and will post graphs tomorrow showing my observations of memory us…
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This number of nodes looks like about the limit for default CCX which I think is restricted to 16 GB so you might be over the limit with only 10 GB. I can't reproduce your model because the STEP file isn't included in the .liml file but I tried it …
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There's no direct CoG readout, so you might have to do it by supporting it at a couple of points and using the reaction forces to calculate the location of the line of action for the weight load.
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1. That's an artifact of the display. It displays the offset shell with the same shape as a non-offset shell but different position. Since the surface becomes curved with Open cracks, that causes gaps between them. 2. Yes except except for stress a…
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Yes, you can use imperfections to cause buckling in FEA, but with nonlinear analysis, not with linear. Perhaps you're looking for wrinkling like this? - No, this isn't buckling because linear static analysis can't do that. Displacements are prop…
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The number one rule in FEA is that it's wrong until you estimate the size of the error. The basic reliable way to that is with a mesh convergence study. Here, you only have a single element in the thickness direction which is probably not enough for…
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Yes. 3-node beam elements are only for the CCX solver. There are also line3 thermal fin elements for the internal solver.
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Sorry for the frustrating experience. Ever increasing stress there is normal behavior and with that fine mesh, you probably have good results elsewhere. It's at a sharp re-entrant corner which is a stress singularity so it's theoretically infinite. …
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Most of what Mecway does runs in only one thread so it will only use a fraction of the CPU resources on typical CPU. Two main exceptions are the matrix solving stage of the internal solver which should use multiple cores, and the CCX solver if you o…
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I didn't notice the title, sorry. No, Mecway doesn't support lines in STEP files. It supports some types of lines in DXF, as you can see, but not all of them, which might be why it's not showing up. Your file might use POLYLINE which is not supporte…
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The files might be using features that aren't supported. Try some of the STEP files in the Samples folder and the DXF attached here which should all appear.
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It isn't a special feature - just apply the load that causes the prestress as well as the other loads with the Nonlinear Static 3D analysis type. To show the difference between prestress on and off, you can suppress/unsuppress that load, or define i…
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If you made the 2D section with Automesh 2D, you can add a local refinement in there which is located at a specified node number. If it's from a flat STEP or IGES file, that's a bit easier. Right click a node and choose New local refinement which m…
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At mesh convergence, the node and element stresses will be the same. Any difference is error in one or both. Usually, the node stresses are more accurate because they're a smoothed version of the element stresses, which eliminates discontinuities th…
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It depends what you want. If you're trying to find the maximum stress anywhere simply by using FEA, then you'll need to model the joints with their details like weld fillets, fasteners, and internal corner radius on angle sections since those detail…
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It looks like CCX crashed. I think that can happen with a too big model but also for other reasons. You might need to reduce the number of nodes or at least eliminate parts to identify what causes the failure.
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Being only 15 values and new to Mecway, it might be easiest to make the mesh by hand and enter all those values by clicking nodes. However, if you're going to do this multiple times, you could make the mesh definition in the spreadsheet and export a…
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Ever increasing stress with refinement indicates an infinite stress concentration. For stress at the connections between shell elements, you could use a solid mesh with the correct details of the geometry and radii, or some other technique like a co…
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Separate surfaces is a problem that happens with IGES files. It's better to use STEP format instead. To set the element axes so U is the radial direction, make another element orientation in Loads & Constraints with these values: X: x Y: 0 Z: z
