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Andrea
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Look at old discussion about "Salome" on my post history Regards
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Mesh doesn't contain informations about geometry so importing separately all relations will be lost. If you prepare a inp or unv mesh file you must creates node set or element set before exporting the mesh. Inside Mecway you can select nodes or ele…
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Modify of the model is normal routine for FEA. For example think at your assembly where a plate has a line contact with C profile. Is it real or it will be filled with weld?
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Leave the command also for CCX! If component are selected under Components&Materials tree the function runs correctly for the single component and runs again for the assembly
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On my experience welded component are modelled as a multibody parts for convenience to put them into a drawing but for FEM I modified the assembly into a single part to save time and to avoid to build contacts. I sometimes model the fillet joint as …
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OK... to add the parameter "perturbation" is possible only activating "stress stiffening". I tried modifying the inp file. PS Gravity could be applied for example to calculate period of body like a physical pendulum Excuse...the right one attached
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Is possible to mesh but considering the part composed by several bodies. Is better to modify the geometry into only one solid body. Regards
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Is a FDM technolgy. Take into account that the material is not isotropic. This is due to the layer over layer fusion. I try to explain with the attached picture Regards
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What kind of technology do you utilize for 3D printing?
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Try these versions of CCX compiled by Prool: http://calculixforwin.blogspot.it/2015/05/calculix-launcher.html Inside the unzipped folder you will find some version of CCX for Windows. Regards
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Model boundary seem to be different from the real. A curiosity! Which is the aim of the frequency studies?
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CCX use generalized formula of Ramberg-Osgood equation. Another formula is: e = s/E + (s/K)^n (s: sigma; e: epsilon) For generalized law you need 3 constants: alfa, s0 and the exponent n. (plus E) Obviously there is a relations: K=(E/alfa+s0^n-1)…
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Mesh is very irregular and due to the modelization you will never reach stress convergence. So make the mesh more regular you will have a good stress field far for the pipe junction but, due to the bending, peak stress along the circunference will n…
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I will try as soon as possible... thanks. PS Now I have to read again the list of new features because they are many
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For my opinion, to understand better the displacements, you must work using cylindrical coordinates. I know that is not possible inside Mecway so you can use CGX postprocessor. See attached radial displacements plot. Other aspect is the mesh. More …
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Faces create by cutting planes must remain plane. Look at the faces without applying rotational BC. Are they plane? Obviously there is a reason PS Maybe is necessary to apply gas pressure to all inner surfaces
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Elements: you have Hex8 and Wedge6 (go to Mesh Tools -> Node/elements list) BC are correct but you can change from "Frictionless support" to Z and Y displacements because your model is a quarter of the complete model. Is not necessary to apply r…
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Today the lifting of 6,2t shaft at 830°C without problems
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About v8 I had a good impression. New functions are welcome! Good job. About CCX I found that Prool's versions for Windows are stable and without bugs found for other version (eigenvalues analysis for example)
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I'm doing test about RBE to joint the mesh. Agreement with classic theory (Saint Venant beams) is very good. I'm testing a frame modelled with two mesh block bonded with RBE (Mesh onto Salome and imported). The same frame is modelled with beam eleme…
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Creating double T-Joint there is no right solution. I think that's no possible to assign a general rule for shell/tie combination
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Hi Marco! There are many issue on your model. Hollow section is no properly modelled. In fact plotting with "OUTPUT=2D" parameter activated, is possible to see that nodes of walls are separated (see pictures). Also bottom wall nodes are separated fr…
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I'm trying to glue the plates with RBE. Seems to be efficient and doesn't build thousands of *Equation card. In the meantime I tried to apply offset to the shell and also these parameters has effect on the results
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It happens when a node in a element is at the yield and another below. Most of the time the problem is related to constrained nodes and zones where there is stress concentrations but happens also in a element which is far. If you calculate vMises st…
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I share here because is a simple model of a plate to plate joint. Look to the solution when the master/slave nodes are placed on the same plane. I tried to change tolerance but I never obtain the right solution. Last chance is to try applying shell …
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I think that's better to avoid *TIE with shell. I thought that it has no problems with 2D elements because CCX expands them to 3D elements but with shell not every nodes partecipates to *TIE, so the results is not acceptable.CCX manual about this se…
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With *TIE I have always problem on MPC! But the worst problem is the error on Jacobian which false all results I'll switch to *EQUATION but I will work on a simple model to understand if the problem is due to the type of elements. Regards
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Sincerly I know ZZS since Dhondt inserted it on CCX (from version 2.6, if I remember well). Why he decided to confine it as an error estimator and not as a standard stress I don't know and I haven't the knowledge to understand. Better thing is to …
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I use it as an error estimator. Accuracy depends from mesh convergence. If you have a good mesh ZZS stress and classic stress are very closed, so ZZS display a little difference. Where the difference is higher you can evaluate if to refine mesh. Fo…
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OK! I understand that combination of boundary with *TRANSFORM, *AMPLITUDE (similar to CLOAD, DLOAD) could lead to error or to lack of a load(constraint). I read that Guido Dhondt, under your suggestion, is going to update the manual, so the situatio…
