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FEA
Andrea
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Spring is in extension not in compression. In compression, with 5lbf, there will be a contact and the classic study is not applicable. Try to solve with classical theory of spring. I found a nominal shear stress about 90 ksi which is very near to th…
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I tried to apply 5lbf to the model and, without convergence study, I found a peak stress of 349.8 Ksi (first principal stress - NL analysis). The problem is to know the right conditions of work. Due to the geometry the spring loaded with a distrib…
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To trasmit bending moment is possible using a trick: strechting the beam inside the plate. This kind of joint is close to the real situation because beams are welded or bolted so is necessary to have an overlap Regards
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Use shell instead brick and creates a node where the beam encounters the plate Regards
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disla: Andrea I remember you posting some similar problem that was not with the linux version... the problem was different because runing the solver the solution was completely wrong (wrong eigenvalue and wrong deformed shape). This case is differe…
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The error found on buckling factor is not due to CCX version. Same error you will find using CCX under linux. Spurious mode were present also on previous version of CCX by MT Try with reduced integration elements
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OK... For Mecway user: definition of spring elements is not compatible with CCX from version 2.12. Regards
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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
