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Victor
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It's not implemented yet. You can still use a nonzero displacement in static analysis and with CCX, so that's why the option is there. I guess it would help if the entire displacement box was disabled for cases where it's not available. Be aware th…
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I'm unlikely to do that soon unless there's a lot of demand because it's a bit tricky.
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The internal dynamic response solver doesn't allow non-zero displacements. This should be showing an error message but isn't so I need to correct that. It looks like you may have to use a force instead. This could be a large force on a stiff (relat…
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I realize it's a bit inconvenient but I probably won't change it because of priorities. Really, the predefined shapes are just there because they used to be hard coded and I included them in the curve generator to avoid removing existing features.
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Google search is probably better than the forum's. This thread is near the top of the page for "mecway shell mesh edges video". I'm also collecting some of them on the Mecway YouTube channel https://youtube.com/channel/UC8tXqfFUUYNb1kv5X4GLi3w
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You can define a sandwich panel in the same way as a laminate, but with one thick layer for the core. The internal solver might not be very accurate though because the shell elements have: * No elasticity in the thickness direction. * A single …
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Oh, that's a mistake in the manual for not mentioning that limitation. They aren't shown for Tie or Elastic, sorry. That's because it's hard to get Mecway to reliably predict which points CCX will connect.
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Yes, change to tri6 and quad8. Check Quadratic elements in the meshing parameters window or use Mesh tools -> Change element shape if it's an orphan mesh. Or you can use the CCX solver which allows them, but beware that accuracy can be poor.
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Fantastic. Thanks.
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If you use Gmsh, it makes compatible meshes on adjacent edges where they have the same length. In this example, there are some patches that break up the lines so it doesn't always match, but you can see the meshes are aligned in the other places. S…
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Yes, you can use all 3 coordinates (x,y,z) in the formula for pressure.
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The lines are normal to the master faces so if the surfaces are coincident, they will have zero length and be invisible.
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Here's a simple example of an elliptic pressure distribution done with a formula in the pressure load.
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There are ways to do some of those other checks: Duplicate nodes: Merge with a tolerance of 0 and see if the total node count changes. Or use View -> Open cracks to help look for unintentional duplicate nodes. Show orphan nodes: Select all elem…
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It's on my list but not yet done, sorry. What I do is turn on Show element numbers and when you see illegible digits on top of each other, it indicates multiple elements there. Move/copy can cause this if you don't select anything first. Selecting …
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The equations mean "average displacement = 0" in the X and Y directions, so there must be no overall motion of that group of nodes in the XY plane, which you've confirmed with your spreadsheet. There can be rotation and stretching of the whole group…
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Yes, the equations are still satisfied, which might be why it took me so long to discover. If the nodes were not part of any elements, you'd be right that it would allow many combinations of displacements, but the stiffness of the elements is suppos…
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Additionally, I think you would need to use CCX and nonlinear analysis for this because it's likely to be a nonlinear problem with stress stiffening.
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Not directly because internal faces might get selected by accident which would be annoying and risk subtle errors. But perhaps it should do that if the faces are exposed by the cutting plane or hidden components.
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I don't have the file anymore. But it should fail to converge when it buckles and only show the solution up to that point. If automatic time stepping is turned on, the steps might get pretty big but I think it should be on to get the greatest time r…
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This is pretty weird. It looks like having all 3 of: * dynamic response * bilinear plastic material * contact fails that way. It works with the Ramberg-Osgood plastic material model though. So if you calculate those coefficients, there's …
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Also use CCX instead of the internal solver. It doesn't have compression-only support but you can make a big high-stiffness element to act as "ground" and use contact on it, which is often much faster than compression-only support.
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As well as the thickness difference: A ) Y and X BCs one two edges are missing in the shell model. B ) All BCs on the solid model are on the edge of the plate's face, not the midplane like in the shell model. Correcting those brings both models' …
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Not sure what you mean by W7 and W10. Also, the file doesn't have nonlinear materials ? But I got a solution by doing this: A ) Increased contact stiffness per unit area to 10000 GPa/m (~ E/thickness). B ) Increased time period to 0.05 s. It won'…
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Mecway only has a single "face" along the length of a beam, and it includes the whole surface as it appears when you select it. Pressure load on beams uses that as the surface area. So for converting line pressure to X,Y,Z "pressure", divide by the …
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Not until now. I've added it to my list, though it's fairly low priority.
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Probably not, at least not soon because of priorities. Though I agree it would be helpful. Thanks for posting the comparison. Very nice model!
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Thanks. I've added it to the list.
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Should be. Thanks for the suggestion.
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Maybe.
