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Victor
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Writing *TRANSFORM directly, you have to be careful about other constraints on the same nodes that it might conflict with. A safer way and simpler way is to specify the displacements as formulas. Radial displacement would have the direction vector …
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1. Select the fixed elements and right click one then Add elements to new named selection. 2. Solve. 3. Solution -> Sum external forces on the element selection: a) Choose an external force component b) Select only the element selection for the…
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The stress in that corner may well be high but not as high as at the fixed support so it isn't visible without scaling the contour plot range. Don't forget to refine the mesh since there's likely to be high error near these regions too. I don't thi…
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Just a follow up after investigating. I think Mecway is behaving correctly here and the problem is caused by the shape of the tri6 element at the axis of symmetry. Its surface normal is not quite parallel to the axis of symmetry so the frictionless …
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I'd say bonded contact for the pins is non-conservative since it distributes the force around the entire hole instead of concentrating it on one side. You could replace the lower pin with compression only support, or replace bonded contact with cont…
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That delay before solving turns out to be the solver itself running completely, so it shouldn't be any slower than doing one configuration at a time. The problem is that it locks up the UI and doesn't report progress, so maybe OK if it's unattended …
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Thanks for reporting that delay and different solution. It must be a bug. I'm still investigating but avoid using Solve all configurations for now. I notice the material's 100 MPa Young's modulus is in the circumferential direction (V) rather than …
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Poisson's ratio failing is a concern - maybe something else is wrong and that just reveals the problem. Could you attach the file? I'd be skeptical of any results from linear analysis since the displacements when it's collapsed will be much larger …
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Hello amasha. This is probably not a good forum for such a non-FEA question. I recommend you try eng-tips.com which has a whole sub-forum for ASME codes.
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Sorry for all the frustrations. Here's a 1 quadrant model that solves with hydrostatic pressure and non-linear. You can use them together for small displacements, it's just that the pressures aren't follower loads which is an issue for large displac…
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The CCX manual says it has an explicit option (*DYNAMIC,EXPLICIT) but I haven't been able to get it to solve properly.
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Here you go. Initial velocity (*INITIAL CONDITIONS) doesn't seem to work for shells - only solids from what I can tell. So I used a force to accelerate the object then released the force before impact so it would have a predictable initial velocity.
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Though it looks similar, this new displacement is about double what it was before. The maximum is now 1.3e-8 m compared to 6.7e-9 m without the midside nodes included. That's because without temperatures on the midside nodes, half the nodes of each …
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The change is that version 8 and earlier calculated thermal stress using a single average temperature over the whole element but version 9 interpolates the temperature at each integration point which is more accurate. That means non-uniform temperat…
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Yes, it can do that. You need to make these settings for plastic material options to be enabled: Analysis type: Nonlinear Static 3D or Nonlinear Dynamic Response 3D Solver: CCX
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Thanks for the suggestions. a) Somebody has asked for this before but it's become low priority. For now, you might find it a little easier to click it and press F2 instead of using the menu. b) Again, yes, especially surfaces, but I haven't done i…
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This appears to be the "gradient error estimator" (see CCX manual). If it's this, then it's an estimate of the error in the maximum principal stress and is obtained using a heuristic based on the difference between values at the integration points i…
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That's even more mysterious. It almost sounds like two issues that might be somehow interacting. Would you mind doing these things to help isolate it a bit? 1) Clear all Mecway's settings: 1a) Make a backup of it from %localappdata%/mecway_limit…
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This error message indicates a new bug in version 9 to do with element orientation but I'm also not able to reproduce it. It may depend on what was already present before you imported the DXF file. Could you post that too? A workaround might be to …
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In principle, it can, but it may not be very convenient for more complex models. Some people report failure of the solver for severe deformations like drawing. They might need careful workarounds. In case of non-uniform temperatures, you can write…
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If you find the center, you could use Mesh tools -> Fit to curved surface with the Cylinder option. This link should edit the first post. The discussion ID 605 is shown in the URL of the current thread. I don't know why there isn't a button for …
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If you change line2 elements to line3, then these extra section shapes become available with CCX: * circle * cylinder * rectangular tube With the internal solver, you could use dynamic response with strong Rayleigh damping so that it's eff…
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Sorry for the extra problems. You can email it confidentially to support@mecway.com if you want. Here's an example showing shell elements connected to tet solids using elastic bonded contact without any problems. It even has a large gap between the…
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1. As far as I know about CCX, there's no tolerance for contact (elastic option in Mecway), either default or able to be changed. I also didn't think it generated any MPCs, so I'm surprised by this warning message. 2. No. Only if you open the .inp …
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Tools -> Labs -> Shell shear force per length If there's no Labs menu, then Tools -> Options -> General -> Labs. Beware that it's inaccurate. However, often the problem is having alternating values on adjacent nodes but if you averag…
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Yes: STEP format: Turn on the Surface mesh option in Meshing parameters. DXF or STL format: Use Mesh tools -> Automesh 2D to mesh the imported shape.
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*TIE with shells sometimes causes wrong results which might be obvious or not, so it's best to never use that. It looks like you're using version 8. In version 9, there's a new option, Elastic, which has more compatibility with shells and works in …
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View -> Open cracks is useful for spotting disconnected nodes and elements.
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I think it's too big. It says 3 000 000 nodes which must be after expanding the shells into solids. That looks like too much for CCX with the free matrix solver it comes with.
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I think the Fit to window problem is triggered by a faulty solution that leaves the display in a broken state. You may need to restart Mecway to correct it then see if the solution has extreme values or NaN using Solution -> Table. There's no si…
