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Hello justhumm The density is very high. 150 lb.s^2/ft^4 is 4820 lb/ft^3. Mecway doesn't currently have a lb/ft^3 unit so you would need to convert to one of the available units. The displacements are excessive because there are insufficient const…
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It seems to be working correctly as a tension-only member. Is the problem that you want to apply a balanced tension to it instead of the external force that you currently have? If you have a known tensile force that remains constant even as the fra…
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You can't really do that with Mecway, at least not without a lot of hackery. Calculix has it though, called Steady state dynamics. So you can still use Mecway to generate most of the model and manually set up the *STEADY STATE DYNAMICS card and othe…
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Good to hear. Yes, CCX can have trouble with very tiny elements and may be a little stricter on element quality.
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By the way, the CCX solver can calculate effective modal mass. Change to the CCX solver and add a CCX -> custom step contents containing the line: *NODE PRINT and it generates a .dat file in the working directory (configure that in Tools -> …
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Hello tdool Constrained DOFs are condensed out of the matrices so it looks like you have: 2488 nodes 2488 nodes * 3 DOFs per node = 7464 DOFs in total 7299 unconstrained DOFs 7476-7299 = 165 constrained DOFs (equivalent to 55 fully constrained node…
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Just some guesses - Could it be "tested" doesn't mean "load tested"? Or that it's a different version of the standard? The site has a to link what looks like B30.20 2013 but ends up at a page for 2018.
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@cwharpe I see your suggestion of increasing the beam stiffness addresses the underlying problem - it was already qualitatively correct but for very flexible beams! By refining the beams, you can see why the lip bends backwards and why the beams rot…
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I don't know why it seems to be bending the opposite way there. Another way is to apply the moment load to a ring of faces around the top and it'll be distributed as equivalent forces. It doesn't work reliably with shell elements and CCX but you ca…
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You can normally use a single bonded contact for many parts so you could perhaps select all the nodes of the ends of the cables, change to Select faces mode, then use that face selection in the bonded contact. And similar for the faces on the struct…
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Oh. Can you confirm that it's the thermal transient analysis type, not steady state? If so, it would be great to see an example of it being missing. Radiation doesn't seem to work reliably with steady state with CCX. It might be something to do wit…
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Fantastic bug report, ehoule! This has been a very elusive problem before but hopefully I'll be able to get it solved using this reproducible example.
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I don't think it's possible to do that in Mecway. If it were static with hydrostatic pressure, you could use a low Young's modulus (hence low shear modulus) and a Poisson's ratio near 0.5 such as 0.4999 but that doesn't sound like it would work corr…
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Hello JL82. You can do it using *RIGID BODY like this: * Change Analysis settings -> Solver to CCX. * Add a node on the axis of the pin. * Create 2 node selections for the 3 hole surfaces. * Add a CCX -> custom model definition contai…
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There's no complete API. But there is: Python API for scripts run from Mecway that currently covers: * Simple operations on nodes and elements * Read data from the solution * Measurement tools that integrate over elements or faces * Read t…
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Thanks. I don't want to study it too much but that adds a little clarity to something that I never quite understood - how materials with different mechanisms for storing thermal energy can manage to completely transfer it between each other and reac…
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Oh, that's interesting about the cause of thermal resistance. Thanks for confirming the name is OK. It looks like "thermal conductance" would have been alright instead of "thermal conductance per unit area", but hopefully the extra words add more cl…
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There isn't yet an easy way to modify the loads but you can write an external script that generates a .liml file with the loads, runs Mecway using the command line parameters to solve and exit, then reads the solution, possibly from a .csv file. Do…
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Yes, that's fine. If the response is independent of load history, then it's equivalent to many separate solves, otherwise, time just determines the sequence of loading so it's probably still suitable.
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These large deformations with contact can be finicky. It sometimes helps to turn off automatic time stepping and use a small time step. Also, make sure the pipe is fully constrained, perhaps at its other end, so that when the contacts let go, it's…
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No plans for integrating *STEP into the GUI.
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Hello pschwenn. Best to try the CCX group https://calculix.discourse.group/ But since you're here, a couple of general ideas to bear in mind: A solution that looks continuous is consistent with a discontinuous one for small enough discontinuities…
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Thanks for sharing. To be honest, I'm never quite clear on the definitions of all those TCCs and CTCs and all that. I named the parameter using what I hoped was the more obvious term "thermal conductance" (=1/thermal resistance). But it turns out t…
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Works fine in CCX 2.16 but not 2.17. I'm not sure what's wrong but it seems like a bug so it might be better to isolate it post on the CCX forum.
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That scrolling back to the top is a bug, sorry. It can help if you collapse parts of the tree to keep it within the window.
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Oh, yes. Maybe my 3 replies were lost on the way. I'll resend from alternative account.
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I've never seen that before except the situation JohnM described where the bad elements have nodes moved by the *TIE or elastic bonded contact. Perhaps you can send me the model privately to investigate?
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Turn off View -> Show element edges and Show element surfaces so only the selected element is visible.
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Named loads - yes Multiplicative constants - probably but it might be in the form of constants you can include in load formulas and not quite as visual as what's shown on your screenshot. Load groups - maybe Country specific input format - It's a…
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Some possible reasons: A ) If stress is listed in the outline tree but has no data, it may have failed to converge. In that case, it sometimes shows the final displacement without stress. B ) If stress isn't shown in the outline tree, add it throu…
