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Found 123 results

  1. Hi, I am doing spur gear to spur gear transmission analysis on motionview (gears have module 1 & teeth of the gears are 28 and 82). I used the rigid to rigid type gear contact and used poisson model with parameters as ,penalty = 1000, COR = 1, Normal transition velocity = 1mm/s to define the contact. I gave uniform rotational speed to the gear with 28 teeth and i requested for the output of rotational speed of the gear with 82 teeth. Theoretically i should be getting output plot to be a straight line with slope 0 & 1.024 rad/s (marker velocity) above x axis (time), but i am getting a curve which is not throughout straight line, plot shows a max peak of 7 rad/s velocity as well. What could be the issue for this?
  2. Hello everybody, I'm a Student and have to do a thesis. The thesis is about a FEA about an large bearing. But I'm a beginner in Hypermesh. Does someboby has some tips for modeling of the isssues "initial bolt prestress", "hertzian stress" and general Information which is important to consider?
  3. Hi everybody. I am designing a rapid attach system for the bucket of a skid steer loader (see picture below), taking inspiration from the commercial systems. In the second picture you can see how this system work: there a contact surface between the bucket and the tach. So there is a contact zone and of sure I should do a non-linear quasi static analysis; however since I would not do a non linear analysis I ask you if there is another way to get a solution. I've already done a non linear analysis but I can't validate the results since this kind of analysis should be quite instable. So I'd like to find another way (with linear analysis) just to compare the results. Thanks in advance for your help Best Regards Stefano
  4. Good morning, I am modeling a rotor composed by three components: shaft, magnet and surrounding fiber. I would like to evaluate the effect of thermal expansion, simulating the contact between the three components. I have some difficulties with contacts (the contact force is not constant, as expected). Differences are quite small, but I would like to ask you if there are any errors in my model or if there are any possibilities to obtain better results (I have already tried with s2s option in contact definition and with expertnl param). Thank you so much for your kindness Enrico
  5. I want to know what this error mean when i used comp in interface definition of contact: ERROR id : 475 ** ERROR SURFACE BUILD FROM SOLIDS PART NON AVAILABLE OPTION /SURF/PART/Surf_ID FOR CREATING SURFACE 6 FROM A PART OF SOLIDS ;
  6. Hello, i am simulating a contact (slide) between a pin and a lug. At the beginning of the motion everything is fine, but at the end the pin is penetrating the lug. The pins displacement is implemented with a constraint. I already tried to change master and slave, but it didn't work. I have no idea what to do next, do someone have some hints maybe? I attached a screenshot of my card settings and the movement of the pin.
  7. Hi All How do we assure a mesh continuity on the border between two spherical parts, one inside the other one, in contact with each other?
  8. Hi all, I am looking for some assistance in impact testing within Radioss. I have been working on the pre-processing part where I have set up the material for the composite using LAW25, and as a result, used P10 as the property card. Also, I have defined type 7 contact between the steel indentor and the composite specimen (the whole components were chosen rather than inidividual nodes). I am finding it difficult to define the output control cards properly. Specifically, the following control cards: ENG_ANIM_DT ENG_OUTP_DT ENG_OUTP_DT ENG_RUN ENG_TFILE How do I determine these values? I believe, the values I am inputting are wrong, and running my simulation seems to take minimum of 45 minutes. . Also, how do I obtain physical data from the simulation, which I can then use to plot parameters with respect to time? Thanks.
  9. Hi, I've previously had help from one of your colleagues with my model for which they suggested I do a Mesh-->Check--> Elements-->Penetration as I had a problem with my slide contact surfaces. I fixed the majority of these penetrations with the auto manager (not all were fixed) and tried to relaunch the calculation. However, now my model does not manage to converge and I don't fully understand why, even after reading up on all of the input fields in the contact menu. Any help would be greatly appreciated (model is attached)! Thanks in advance. 151207_MD_01_A-42.hm
  10. Hello, I would like to calculate a contact between a sphere and flat solid block, pressed together under certain load. I am interested in the contact stress and precise contact area (I would like to compare the results with the analytical solution of Hertzian contact theory). Is it feasible to get the desired results with a non-linear quasi static analysis in Optistruct or shall I do it with Radioss? Additionally, what is the best way to obtain the final nodes in contact or even to fix them together and perform an additional analysis? Thank you for you help, Matej
  11. Hi, I've been trying to find the force required to create an interference fit between two parts. I'm fully constraining one of them, and placing an SPCD upon the other. The contact between the parts is a sliding one (I've tried different values of friction, but nothing seems to help). I'm using a non-linear implicit analysis. The solver gets quite far down the line, but then crashes at some point because it cannot converge. One of the parts begins to deform (as it is supposed to), but then the solver doesn't get any further. Chamfering the goemetry to avoid sharp edges helped some, but not enough. Any thoughts, or a location where I can share a large .fem file? Thanks, Jai
  12. Hi, I am doing a simple contact simulation in Radioss Bulk Data between 2 2D surfaces meshed with shell elements. The first surface is similar to an S-shaped extruded plate and the second one is just a rectangular surface near the s-shaped. Distance between surfaces is 0.1 compared to 0.5 el. size. Contact surfaces (near the gap) were created with the SURF card and it was ensured that their normals were pointing to each other. I want to do two consecutive subcases. In both of them the top of the S-shaped sheet is fixed. 1) The rectangular plate is constrained with some predefined distance (in my case, SPC with dof1=4 and all other dof=0), so it pushes the S-shape. 2) The plate goes back to zero and the S-shape should go back to the origin (or a bit less if there is plastic deformation). To do this I modified the constrained of the rectangular plate to have 0 for all dof for the SPC constrained. I also turned the CNTLSUB option on and put it to YES. However, it seems like the unloading does not start from the loading case and the plate just stays at zero. I have tried different contacts (initially SLIDE and then STICK and FREEZE) but the result was the same. Attached is also a sample file. Any help would be appreciated. Georgi Shell_Contact.zip
  13. Hi, I am wondering if somebody could help me defining contact between to surfaces so that I can easily update the contact definition in the input file. The problem is stated as follows: I am pressing two beams together and would like to perform FRF modal analysis on the beams. With an optimization routine, I would like to update the contact definition between single nodes and surfaces to be either stuck, slipping, or not in contact, and match an experimentally obtained FRF. In order to solve this problem, I need to define the contact in a way that I can easily update the contact definition between single nodes and surfaces in the input file. In this initial analysis, I define the contacting interfaces to be stuck and am hoping to understand the input (.fem) file, hoping to be able to figure out how tho change the contact definition from stuck to slide within the .fem file. Attached are the .fem file and the .hm file. Could you explain to me the entries in the .fem file in: Line 61 (+ 21603 13616 13929 1) Line 1762 to 1778: How is contact defined here? Is it between the sets of nodes? Can I change that to single nodes? Is grid data the nodal position? Is CHexa Data the element definition? I hope this description is sufficient to help me solve my problem. Thank you, Kevin 170706_FRF_HZBeam_FullyStuck.fem 170706_FRF_HZBeam_FullyStuck.hm
  14. Hi together, i try to visualize the contact forces (normal and tangential) of a type 2 interface in radioss. Is there a engine keyword to visualize the contact force as Animation, so that one can see it in hyperview ? I use Interface type 2 with spotflag 20. This means, that a contact force is calculated in order to compare the result to the rupture criterium. I would like to visualize this contact force. Thanks in advance! Greetings, Sebastian
  15. Hi all I was watching a video on youtube , where the contact creation brings the user to choose among the Contact Type 7 or Type 11, but what I see in lower versions is just CONTACT, GROUND, CONVECTION ,...etc I would like to know how to choose the Contact type in versions 13 and lower
  16. Datta1234

    Contact

    Hi, I am trying to simulate contact for performing frontal crash analysis of a chassis having a tank. I have a tank which is wrapped by two brackets and supported by rubber. This bracket is welded to a chassis. I need to create contact for the following- 1) Between tank and bracket. 2) Between rubber and bracket. 3) Between rubber and tank. It is attached to chassis as follows- I know that I need to create Interface. Please tell me for each case which Type interface should be used and which should be selected as master and slave? Thank you, Datta
  17. Hello, I am doing a study inflating an airbag with a particular shape and there are a lot of contacts between surfaces, that I modeled with interface type 7. I have some troubles because there are some nodes that pass through master surfaces (even if the interface is activated) but then the contact is applied and the nodes can not pass through, creating high contact forces and reducing the time step. I wanted to use the control card DT/INT/DEL to delete the interface in those nodes, I fixed Tscale to 0.9 and Tmin to 1.0 e-4. When I run radioss, time step reduces up to 5e-5, some nodes are deleted but not those that passed through surfaces and have high contact forces. Any idea about how can I deactivate interfaces in nodes where the contact force is higher than a fixed value? Thank you
  18. Hello, I am trying to build a rigid mbd model with rigid bodies engaging in 2D rigid-to-rigid contact. I have defined curves where the contacts will occur, using the Add Curve functionality. Attached images 1.png, 2.png and 3.png from my curve panel, showing the settings I am using for all three contact curves. As you can see, in the Z direction, they all have the same value as 0. So they are indeed coplanar as they all line on the XY plane. I proceed to define a 2D rigid-to-ridig contact. Attached image, contact.png, shows my settings for one of the contacts I use. I have also made sure to correctly define the contact sides; so there are no problems there either. Finally, attached image, error.png, shows two of the error messages I'm getting. All my error messages are the same so I am only showing those two. It is telling me my curve graphics are not coplanar. However, what it seems is that they actually are indeed coplanar. I would be grateful for any help to fix this problem. Best regards
  19. Hello, I have been having issues with a model containing contacts and friction. The model is relatively straight forward, a multiple mast model with wearpads and contacts between pad faces and adjacent mast sections. When the contact is set to property type slide N2S, the analysis demands around 47GB for In-Core Solution. However when the type is set to static friction coeff = 0.15, the in-core demand becomes 80GB. The model on my pc then typically fails because MUMPS demands significantly more RAM. I've tried adjusting the search distance and using a PCONT card to define friction with little impact on MUMPS demand. Any suggestions? I currently have one PARAM card... PARAM,EXPERTNL,CNTSTB
  20. I have components in the assembly and i want to find the IDs of surfaces which are really close or almost touching other component. Is there any way to find out those details?
  21. Hi, I am having a radioss bus structure file with min. element size of 5 mm used for crash simulation and now I want to use the same file for static and non-linear quasistaic analysis in optistruct If I go to optistruct will all contacts be detected as it is in radioss and is recommended this way or generate separate file for it. As the structure size is large, meshing will take more time and thus wanted to avoid making new file. Thank you
  22. Dear All, how can i resolve it. im having all solid elements in my model. gap between two part is 0.2mm friction is 0.05 what additional parameters i need to choose in type 24. i'm doing failure analysis with JC material model regards, Ganesh m
  23. I've been recently working on a Knee joint model . I need to find the contact force vector between two particular components. I have been getting a lot of errors and unable to run the model. All the contact pairs and properly defined and I am able to generate all typical outputs except for contact output. please help me out. The output blocks defined so far are node and element outputs for all 8 components defined. Thanks in advance!
  24. Hello, I would like to do some lattice optimization in Hypermesh. However, I need to know if it is possible to have a different mesh size for the lattice sections compared to the solid sections. The way I understand lattice optimization in Altair is that the element size you mesh with originally will determine the average length of the lattice struts. For example; I tetra mesh my model with a size of 2, the lattice beams have an average length of 2. However, I would like to have a mesh size of 0.5 with lattice elements of length 2 (or vice versa). My game plan is to run a minimize compliance with volume fraction on my model with a penalization of 1.8 (low porosity). Then use the results of the compliance optimization to split my part into sections for a given element density threshold. I should end up with solids for the lattice elements and solids for the non-lattice elements. The lattice solid sections will then be filled with lattice beam elements from another lattice topology optimization. I want to remesh each solid individually for different lattice strut sizes and types. Contact surfaces will then be used to connect the solids together and then run the Lattice optimization. The end goal is to use mesh refinement on the non lattice sections to check the validity of my model as well as experiment with different lattice sizes. Any advice is greatly appreciated. -Eric
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