Stuck? 
support@mecway.com
support@mecway.com
Mecway
FEA
disla
About
- Username
- disla
- Joined
- Visits
- 1,954
- Last Active
- Roles
- Member
Comments
-
Hi Victor, Two suggestions for improvement that I think are not very difficult to implement. When dealing with rotations, rigid bodies and Distributing Coupling the REF node is usually required to be at the centroid of the surface or at the Center…
-
1-Select one surface 2-Invert selection.(Edit menu) 3-Select the only missing surface (first selected one) Edit: Didn't see your updated responses. Select all after one surface selection is faster .Yep !!
-
Hi dculp, I'm sorry but English is not my natural language so I'm expressing poorly sometimes. When I say "the easiest way is to lock all the displacements of the bolt and...." I mean to set the displacements=0. If not, it will happen what you hav…
-
Thanks Victor, It was “hidden” in the ccx manual all this time (pag.521 v2.18). Regarding the two springs I do it because I need more parameters to completely define the coupling with two bodies. (For one body one could be fine.) One is the overa…
-
Hi, First notice that some typical BC used in bolted connections are not available in Buckling analysis like Contact and Pretension. Taking this into consideration the easiest way is to lock all the displacements of the bolt and suppress (right bu…
-
Hi Victor, Sergio, Did you find a way to keep the different bodies separated when meshing solids? Victor ¿Are you planning to implement this nice work around.? https://mecway.com/forum/profile/cashan commented some days ago that its main problem w…
-
Easter eggs.
-
Sorry Victor, I found the error. atan2 is providing angles from [0,pi] and [0,-pi] . I was supposing [0 ,2pi] in my formula. Fixed.
-
Very cool. Thanks for sharing
-
Thanks Ken.
-
Hi, I’m not able to make my 34.5 mm model converge with Ramberg-Osgood or User Curve definition. This material has such a small tangent modulus that it fails. The minimum in my model is Bilinear Isotropic and ET = 6 GPa which is actually a very lo…
-
Very close now. ¿Did you managed to include Ramberg material model?
-
Hi kennethfugate, Victor and Happy new 2022 everyone, What a nice challenge!. I have tested this nonlinear “Pseudo-Axisymmetric” problem removing just some elements from the 0-Axis in it works always for the descending run and for the full cycle at…
-
Hi, I would start with big uniform quadratic elements to check that the model runs ok and results. If they are well shaped the results will be ok. 1mm you are going too far. That is more than 2-3M nodes and the problem is probably that you run out o…
-
Thanks.
-
Hi Rino_aic, If you want to check numbers with the example problem the plate is solid as shown in the video and the piece of pipe probably too but not sure. I think the values that are making you fail the mesh are the ones related with the minimum …
-
Be aware that your stp seems it is made of shells and solids. The main beam is meshed as solid section too if you apply those meshing parameters. mesh
-
. Thanks John , Sergio.
-
Hi Cashan, All this is possible . Go to the SOLUTION menu ---> MEAN. You need to recalculate again in case you create a new element selection in order to see it
-
Impressive.!!. That's another league. I hope msy288 you are not planning to build a ship. I agree, simple problems, simple solutions, big problems, prepare your wallet.
-
Hi cashan, Your issues are probably due to the standard procedure in the industry. Meshes are built from CAD models. Have you tried to build meshes from Scratch? I mean , manually. I’m talking seriously. Extrusion is an underrated operation. This i…
-
100% pre/mesh/solved and postprocess in Mecway . This is the tricky part. I have start from the section profiles. You can download them from the forum in the post “Library of Steel Beam Sections according to EN”. Import the ones you are going to …
-
Hi msy288, I have done some testing and MECWAY & CCX seems perfectly capable. I have obtained this result and its being tricky, at least for me, but result looks pretty good and coherent. I suppose it will need some more work in case your shape…
-
Hi Victor , As I have understood, first I need to compute the failure probability of each element by means of a volumetric integral on each finite element. The field to be integrated is a complex combination of the principal stresses. I don’t see t…
-
Hi DaveStupple, Victor, I’m struggling with the computation of the POF by means of a unique Script. I already know exactly what to do but I do not have skills with the API environment to build the script yet so I’m firstly solving it in Excel, pos…
-
¿Is there a way to obtain the volume of each element in an arbitrary solid model to build a custom formula with it? I’m trying to get it indirectly from available variables but I’m not finding the way. I think there is no way to sort the need of t…
-
Hi Dave, I’m also interested in your problem, and I have tried to implement this statistical approach. I think I have got some progress but there is a point I’m not really sure if it is properly working. Heaviside function is giving me values bigge…
-
Hi. These are my results after changing the force by pressure. I have also change in both the Poisson’s Ratio to 0.4999 just in case and to remove any source of discontinuity between elastic and plastic behavior. When computing with the Bilinear h…
-
Thanks Victor, I have an smile in my face right now. That seems a very plausible explanation. I will change force by pressure to see what happens. It would be paradoxical that I come from reviewing the concept of True/Engineering Stress some lin…
