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Victor
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Comments
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It's actually in the right-click menu of the Solution branch of the outline tree. That's a mistake in the manual so thanks for pointing it out.
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Though Sergio's idea is probably easiest, an alternative which works with either solver is to create a New formula under Solution to convert reaction forces into moments, then use Tools -> Sum to sum them over the constrained nodes. Here's an exa…
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Hello 28kevinf and Welcome to Mecway **1) The displacement for the first few modes shows rigid body rotation which looks like radial expansion/contraction with the large automatic deformation scaling factor. To prevent these modes appearing, constr…
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WARNING for anyone else using this. SandpointDave discovered that the SECTION FORCES results are wrong. This seems to be a bug in CCX 2.10-2.13 for circular tubes. It looks like you can do further calculation on the results to correct for that thoug…
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I see. I misread your 37000 as the total number of nodes. I've reproduced it with your model. This appears to be caused by memory fragmentation and I've now fixed it for the next version so thanks for bringing it up. It's the combination of a large…
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There's no hard limit and I'm surprised it failed with such a small model. I'm having trouble replicating your results. I tried with both fixed support and frictionless support on 36 000 nodes of a 116 000 node model (attached) and it used about 1-…
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This is probably because two or more bonded contacts are sharing slave nodes where all 3 parts meet. It's a common problem without a simple solution. Some suggestions: A) Make a small chamfer on those edges so there are no common nodes. B ) Manual…
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There's a tutorial on frictionless contact in the manual called PipeClip.liml For friction, you set it up the same way but add a friction coefficient and stick slope. Stick slope is another parameter you usually have to choose by trial and error. …
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Oh yes, that looks like a bug showing the wrong error message sorry. You can just ignore it since it'll go away.
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Thanks for pointing this out. It's sort of a bug. The beam rotation in the display is done using the Twist angle field variable instead of the 3 rotation components. However, Twist angle is no longer generated automatically in version 8 so it doesn'…
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That probably means you're using shell edges as master faces which isn't allowed, but they can be slaves. So where an edge meets another surface perpendicularly, set the edge as slave and the 2D surface as master. If that's not your intention, mayb…
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You can use the SECTION FORCES parameter on the *EL FILE card. To do this in Mecway, under CCX in the outline tree, add a custom step contents containing: *EL FILE,OUTPUT=2D,SECTION FORCES S Then the stress components in the solution have differen…
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The main problem is that the two SSteel materials have Youngs modulus = 200 Pa. I changed them to 200 GPa and it converges. I also turned off quasi-static since there aren't any time dependent loads to make use of it.
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3-point bending with contact is a bit difficult because the bar and the loading cylinder can fly away if they're not constrained. But you can do it with both the free objects having all 6 of their degrees of freedom each constrained by soft springs …
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I forgot about this, but you can use normal pressure and enter a formula to make it a linear function of position. That's the same as hydrostatic pressure when the edge of the selected faces is along the free surface.
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I might add it for linear analysis by exporting it as node forces. It won't work for non-linear though because they won't follow the moving mesh, and from what I can tell, CCX doesn't support non-uniform pressure loads without writing a user subrout…
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Yes, all configurations get all of them unsuppressed at first.
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I see the convenience of having analysis type settable per configuration but I don't expect to make that change. If you have several configurations with different thermal solutions, you can still transfer all their temperature fields into static co…
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I'm not sure about CCX specifically but for most FEA solvers, memory use isn't proportional to the number of equations. It goes up a bit faster than that since the equations are stored in a 2D matrix not a 1D list of values. But it's a sparse matrix…
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That's an omission from the manual sorry. The table is only for the internal solver. So yes, you can use line3 tube elements with nonlinear 3D and CCX.
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With *DLOAD, you can also write a user subroutine which could probably read the data from a file but I don't know anything about how to do that. If you need to recompile CCX, there are instructions in the file included in Mecway as well as various o…
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Looking at *DLOAD, it seems like if you have a fluid model with node pressures, you can use PxNP to apply them to element faces. So maybe you could make a fake fluid model with all the pressures specified by your data, then use *DLOAD to map them on…
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Just in case it helps, if you have smallish displacements, a simpler way to apply external moments to solids is with the moment load on a face selection. Mecway converts it to distributed forces for CCX.
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Thanks. This seems to be a bug in Netgen which is generating a corrupt surface preview. I don't know why it's happening but for the next version it'll show an error message and continue to read what it can so you can see the area of the model that h…
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Thanks for reporting this. When did the error appear? Immediately after opening the file, after meshing, at the start of meshing, or something else? Can you post more details that are shown with it, or better, the STEP file itself?
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I guess that pretty much anything bought in the past 5-10 years will be OK. Mecway is not very GPU heavy - it uses it for simple rendering of triangles which isn't the bottleneck in the graphics.
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The cutting plane slider on the right of the toolbar hides foreground elements. That's OK if your surface is flat but would need several adjustments to see all over a curved surface. If you use Mecway as the preprocessor then it carries components …
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That's the nature of these problems - there are so many ways for it to go wrong, you can't be sure until you isolate it.
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file for previous post
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No, I only changed E for the Cplate material. I left K at 5e10. Here are the files I used if you want to run it again. I agree your results seem wrong. The plate's deflection strangely increases when its stiffness increases from E=1 GPa to E=10 GPa…
