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Victor
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Here's some steps to get started. From this, you can solve it and get some kind of solution but it doesn't yet have: * Holding forces * Plastic material. See manual 14.1 Custom model definition for an example. * Friction. Set it in the contac…
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Yes, that's more tricky. I would constrain the stripper with a weak spring to oppose the holding force and ramp up the holding force so that the full 50 kN is not applied until after the contact closes.
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The PipeClip.liml example in the manual and Samples folder might be a place to start. Add plastic material and more parts. The common features with deep drawing are contact and time dependent prescribed displacement. Beware though that people seem …
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OK. I'll add that.
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You might be right about configurations. I've made a note about that. It needs a (un)suppress in all configurations option too. For the new install, are you sure all the display settings were the same?: Node/face/element selection mode and all opti…
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The internal solver has always used Intel MKL's Pardiso and I've never heard any complaints of it not working on AMD CPUs. Though it might be slower.
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Graphics is mostly limited by the CPU or memory and I don't think there's much that better hardware can do about that. You can turn off some of the display options and avoid being in Select nodes mode since that spends time searching for nodes to hi…
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Here's some memory use data for solids: Internal solver: https://mecway.com/forum/discussion/comment/1139/#Comment_689 CCX: https://mecway.com/forum/discussion/comment/3166/#Comment_3141 As for recreating components, I don't think there's a short…
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disla - that's amazing! badbunny - You might have had some nodes selected using Merge the first time. Most of the meshing tools act only on selected items if there are any or the whole model if nothing is selected. I did the merge with 0 tolerance…
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It occurred to me there's a clumsy workaround for 2D/axi: 1) Extrude the whole mesh to a solid with 1 subdivision. 2) Select the edge faces of that using Edge detecting selection. If there are a lot of sharp corners that block it, select the two 2D…
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There's no automatic edge-only selection. But you can drag a rectangle or circle to select a group of edges. Do multiple selection and inversion of selection by holding CTRL while selecting.
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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.
