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Found 102 results

  1. Sunilshanmugam

    Initial Penetrations In Interface

    Hi Guys, Im doing frontal collision using radioss, spot weld and adhesives were provided using connectors. Since there were interferences between spot weld and adhesives as shown in the figure. Both spot and adhesives will be there in model, is it advisable to continue with this. Since my major interferences and penetrations is between spot and adhesives. Can you provide me a better solution. Also while providing type7 contact, Case1 In my model both shell and solid part persists i have directly selected those parts in Master Entity and Case2 In my model , i have created skin for all solid parts with a thickness of 0.01mm and updated those in Master entity along with shell parts in this which one is advisable, how to establish contact for those solid components.
  2. Hi everyone, I have problem obtaining the TCL command of auto contact pair finding. My model contains 6 components, I use the Abaqus contact manager to automatically find contact pairs for me. Manually, I can successfully find contact pairs. Since I want to run this process automatically by TCL script, I do the process manually and check out the code added in the command.cmf file. Unfortunately, the code are very long, approximately 50000 lines. Also, the code are about nodes' data and surface set, which is not I am looking for. I am looking for the command that represents the buttons "auto", "components: all", "find", "create". I will show these buttons in the figures attached. By the way, the file: raw.hm is my model. Again, my goal is to get the TCL code for finding contact pairs. Please help me, thanks! raw.hm
  3. mvass

    Advice needed

    Hello, I would like to have your expert opinion in one of the problems I am currently working on. Part of the simplified geometry is shown in the attached picture. As seen I have two cylindrical parts in contact with an interference fit of 0.001 inches. In addition to that a pin is installed and goes through (with a size to size connection) both cylindrical parts. I decided to perform a quasi static non-linear analysis, firstly by solving the interference fit and pin connection load case and then continuing with the load on the structure as a second load case. When I solved the press fit problem (without the pins), I had no problems, both the displacements and the stresses looked reasonable. But when the pins are included into the solution I am having a band of peak stresses (well beyond the material's yield point) where the pin contacts both cylinders (see red oval in the attached pic). This happened with almost every type of contact connection I tried between the pins and the cylinders (freeze, slide, friction etc). Same results when I replaced the 3D pins with 1D elements with RBE2 connections (to connect them with the cylinders). One solution is to ignore the pins and continue with my solution and then perform a detail stress analysis of the pins based on my results, but before doing so, I would like to know that I have tried all possible scenarios with the pins' contact. Any suggestions? Thank you in advance. pin.bmp
  4. Ganesh Munge

    Friction force estimation

    Dear All, @Prakash Pagadala in attached image green- housing yellow - shaft blue- ball ball makes a contact with shaft at 2 points and with housing at 2 points. at every contact there is an interference of 3 microns. housing is fixed and shaft is allowed to translate axially. i tried contact with static coefficient of friction and and clearance value but still groove surface of shaft and housing is penetrating the ball and vice versa. can anyone suggest how can i work on this??
  5. semih balci

    Contact

    Hi, What is the best contact type generally? if the answer is type7, what is the best properties of type7 contact?
  6. 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?
  7. Hi all, I was running a model in Optistruct 13.0 dealing with a two step non linear quasi-static analysis of two plates coming into contact. In the first step my goal is to make sure the two plates don't come into contact; let's say my initial gap is 5 mm, one plate is pushed down by a force of 100 N, the other one is fixed at the base. At the end of this step the two plates should have minimum gap between them, in other words no load should be transferred from one to another. After the second step in which I apply a force of 1000 N, the two plates obviously come into contact, resulting in a load transfer to the spcf applied at the base of the fixed plate, since friction between the plates is activated. I tried using a gap element in order to simulate the problem but no matter how I change the values into the pgap card (for example I first put a value of Kb equal to 25 N/mm to make sure the pushed plate didn't reach 5 mm of displacement with a force of 100 N.... didn't work, then I put it equal to 0 and I obtained the same result ), at the end of the first step the gap of 5 mm is always reached, resulting in load transfer. How can I avoid this situation in order to make it work properly? I'll attach the .hm file so you can check it. Thanks for any replies, hope someone will help me with this matter! model_with_gap.hm
  8. Dawnblade

    Contact in composites

    Dear Sir, I want to do a three point bending test of carbon fiber laminate in Hypermesh with Radioss. I found something puzzle when i create the contact between components after i had defined materials, properties (CFK using M25_COMPSH and property with it using P17_STACK), plies, laminate and some of boundary conditions. I chose TYPE 7 as the card image to let laminate be a slave entity and impactor be a mater entity but i found i cannot select my laminate component in the option(i can only see other component) Is there any mistake in my operation? Here are some pics under. I am exactly green hand in radioss, my apology... and I hope someone can help me on this.
  9. Sp108

    Bearing Analysis

    Hey! I am trying to perform a structural and transient analysis on a Roller Element Bearing model. I am able to perform simple static analysis but I would like to utilize Hyperworks to simulate the following conditions: Inner race to be rotating with a constant velocity and a fixed radial load is applied. Outer race is fixed. The balls should also be rotating. I wish to know: 1. How I can give a constant velocity to the inner race of the bearing while also allowing the balls to rotate? Which card am I supposed to use? 2. What kind of contact constraint should I apply. Right now I am working with slide contact only. 3. Is quasi static analysis adviced or implicit non linear? There is one video but in a different solver which does what I have been trying to do. I wish to do it in Hyperworks. Here is the link: Also please suggest whether optistruct's non linear can be used or whether I should switch over to a different solver module! Cheers
  10. Model description: A set of gears Load:Torque Non-linear analysis conditions (NLSTAT) There have contact between the gears (Slide) Problem Description: The ideal result should be that the largest stress is at the root of the tooth, but the analysis result is that the largest stress is at one point of the tooth surface. This maybe stress concentration. Is it a model problem? Or, if not, how to solve the stress concentration problem caused by this analysis. When I look at the results at different times, stress is still relatively uniform even at t=0.9, but stress concentration occurs at t=1.0. Is the load equally divided? The following pictures show the stress results On the left is t=0.9. On the right is t=1.0.
  11. 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
  12. 3D model with solid elements, there are two surfaces in contact and friction interaction were set in Hypermesh. When .inp file was imported to ABAQUS and check data, there is a warning "the slave assembly has 1200 nodes in common with master surface". Should I separate the nodes on the interface and how to do it?
  13. For Modal and Stiffness(torsional and bending) of ladder frame chassis, is there any significant difference in results when I use stick contact between frame and cross-members or when I use shell/rigid weld elements to connect cross-members and long members?
  14. Hi everybody, I was running a test with optistruct using two simple cubes. They are both fixed at opposite ends. Their faces are separated by 0.1 mm and can, if pushed, become engaged in a contact (type SLIDE). Type of analysis: nonlinear quasistatic. Issue: Even if I fixed both cubes at their bases and there is no applied force and no contact is engaged (shcdist=0.001 and the solver warns me that no contact elements have been defined during the analysis), the cubes translate of 2 mm as if they are moving like rigid bodies. I have already tried to constrain some more nodes, to no avail. Any explanation for this thing by anyone? Thank you in advance. Find attached my .fem file to check SHRCTOL001.fem
  15. Hi all, 1、For a problem with large deformation, the contact status between two objects will change. Some location will come into contact while some other location will separate. What's more, relative sliding may also exist. How to choose the proper parameter values in contact property card for this problem? 2、If a linear static analysis is chosen, could the contact status change during deformation process? Roy
  16. Is it possible to create contact between two surfaces edges in Optistruct? does it require a special interface type? I tried creating a contact interface with an element set for master and a node set for slave, but it doesn't work. The solver outputs this error: *** ERROR # 1762 *** Incorrect SET type for MSID This video explains how to do what I'm trying to do in the Ansys profile. I would like to know how to do it in Bulk data format. https://www.youtube.com/watch?v=Bx6JFiqeCmM Thanks in advance!
  17. Hello Sir, I'm working on bullet penetration into steel plate. At first contact works beetwen bullet and plate, but next it doens't work so good (picture 1). Finally, contact again work (picture 2) and I don't know where is a problem. On top of that, the speed of the projectile doesn't decrease (picture 3). Contact settings: Type 7 Istf: 4 Igap: 2 Fric: 0.2 Gapmin: 0.1 Inacti: 6 I tried a lot of contact setting, among others: Type 7 Istf: 4 Igap: 2 Idel: 2 Fpenmax: 0,8 Stmin: 1000 Fric: 0,1 Gapmin: 0,04 Inacti: 6 Iform: 2 but still doesn't work. Thanks for helping me. test21.hm
  18. Hello, Since the contact surface is deformed in the current analyses, I would like to use tracking system to obtain the projection of the contact forces on the element surfaces. I could manage to use tracking system for displacement but I could not find a way to use for vectors of contact forces. the toggle A picture of the issue I mentioned, is attached to this message. The swicthed that is written "use tracking system" cannot be activated as shown in the second picture, Thank you for your help in advance.
  19. Hello to all, I'm trying to model a wheel that rotates on a plane without slipping, but that can lift off the floor when it's needed. I used the contact command and Poissoin's algorithm, but I wonder if there is another way to do it. Is it necessary to write a subroutine? thank you
  20. Ganesh Munge

    enforced displacement

    Dear All, can you please help me with, How to apply enforced displacement on shaft and fixed constraints on hub as shown in figure. i'm confused in load collectors, where to assign spc and where to assign spcd and in which collector. also want to know about search distance option what it means actually. is it a gap between contacting bodies? regards, Ganesh
  21. 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!
  22. Ganesh Munge

    error id 55

    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. Dear All, Please help me out with mentioned errors.
  24. Oli

    LGDISP

    Hello, I have a Model with 2 Load Steps. I applied a force just in one direction with differnet magnitude . For load step 1 =4000N and for load step 2= 10000N. (I do not use CNTNLSUB) I wonder, why the force vs. displacement curve is not equal for both load steps until 4000N. So the stresse are actually also not equal at the same force magnitude. Do somebody has an idea? Attached a Diagram of the 2 curves (force vs displacement), and the model files .fem and .h3d kleines_Loch__plastisch.h3d
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