Analysis

Hi, I am looking for help regarding Wear Analysis in Creo.   I have got 2 parts, one static, one rotating - as on the picture:     How to simulate a Fatigue - Wear - Contact analysis?   Would you please explain me? thank you,   Arek

Hello everyoneI am not good at English, so I'm sorry if it was a funny translation.   I asked a question on how to check the gear mechanism with MDO and it was able to run.However, since MDO can not confirm the stress analysis (contact analysis?) Of the gear, I think that we will check the stress of the gear with Simulate by diverting MDO data, but since it is not detailed in the analysis, the definition method is well understood not.I will attach a reference file.Could you tell me the definition method to check the force generated during gear drive?Thank you.

Hello all,   We combined the two gears (spur) with MDO and confirmed that it can be rotated by servo motor.However, I do not know how to check the forces that occur on teeth.Is there a way to check how to apply force to parts when making movements with MDO?   Please tell me if you know it.  

We are moving from Windchill 9.1 to Windchill 11 and at the same time we upgrading from WF 5  to CREO 4. With our new instance of Windchill, there are many restricted parameters which we will need to add to our legacy components.  I know ModelCHECK can check for missing param and allow the user to add it to the model.  However, this is what I want to accomplish with Modelcheck: 1. Check for missing restricted parameters. 2. Allow the user to add the restricted using the same pulldown menu using the Interactive mode 3. Designate the parameters    Advance function, using the same scheme above  except instead of interactive the user can run it in batch mode and select a default value for each restricted parameter.  

My current experience with Creo simulation is primarily random vibration and dynamic time analyses, but have recently been required to perform sinusoidal content, in particular, a swept sine on random vibration profile.  How would this type of analysis be performed with Creo?  I would guess that one would have to either convert one into the realm of the other (sine into random or vice versa) or to apply them as separate analyses and somehow evaluate a combination of results?  If anyone has done such analysis or can point me in a direction your help would be greatly appreciated. 

info, in german

I have a mismatch in temperatures during the postprocessing of a flow analysis problem coupled with conjugate heat transfer. My problem has a cylindrical shape, with almost axial symmetry. To visualize the temperatures, I have made two cuts along X and Y planes. I also want to know the temperature in the inner part of the vessel, which is a cylinder. I expected to see exactly the same temperatures on the intersection region of the cylinder with the two planes, but this is not the case. This issue may be due to the high temperature gradient in the direction normal to the cylinder, but I am not sure.   The pictures below illustrate the problem.  Help please. Axial view of planes X Y and the cylinderArea affected by temperatures mismatchDetail of temperatures mismatch

Hello, I should create in my assembly the movement illustrated in the image that I have attached. Each phase is sequential, there are no combined rotation and translation at the same time, in each passage it occurs, or only rotation of the pin, or only the translation of the slider  I would like to ask you a tip on how to get started. I've set up a Pin  and a slider constraint, now I suppose I'll be applying some motor  and setting the correct sequence of each movement in Creo Mechanism, but I have no idea how to do it. Use I create parametric 5, I also attached the assembly files . thanks

Hi, I want to be able to create P&ID diagrams within Creo. Really, all I need is a library of the symbols so I can insert via custom symbol function within drawings. Does anyone have a library of P&ID .sym? Thanks

Hello everyone, I am trying to perform a fea on a shaft with 2 inputs (10000 lb*ft), supported by 2 bearings. Instead of putting a constraint at the output gear I thought it would be better to apply a torque opposite to the input torque, in this case -20000 lb*ft. The stress and deflection I obtain don't seem correct. The shaft rotates in the direction of the input torque (more than one full rotation, the output torque doesn't seem to have any effect), it shrinks and on the output gear it is showed a high localized stressed area, which I cannot justify. If I substitute the output torque with a constraint that fix rotations the result seems to be correct, but I would like to investigate the reason why applying opposite torques doesn't work. I add that if I run the model with only input torques the fea still runs, even if I should get an error because the system is not isostatic and the shaft can rotate on its axis. I hope someone can help me on this.   Thank you Daniele

This article describes  a solution to use when it is desired to have 2 "concentric" pin joints but that causes redundancies and improper load transfer. Some application examples are a door with two "hinges" or a loader/excavator with two arms out to the bucket. The attached example includes static analysis showing the amount of load on the individual pin joints.   It also includes the ability to model joint stiffness via springs. The ability of the joint to "flex" is what removes the redundancies. This model has both hinges modeled with cylindrical joints and springs to allow shared UP/DOWN load bearing, However, a simpler version would be to change one to a PIN, then that one would bear the full UP/DOWN load alone. (remove the springs on the cylinder translation as well)  That simpler model would work with Force Balance whereas the attached example uses Static analysis due to the additional degrees of freedom UP/DOWN that are absorbed by th

Hello,   In a transient thermal analysis, for a boundary convection condition, give the possibilty to users to combine temperature dependent convection coefficient and bulk temperature dependent to time. Actually, when we try to define in Creo Simulate a such boundary condition, "Creo Simulate" give us the following message (see please the JPG file)   Thank you in advance   Sidi MOUATADIRI    

Hello,   my task is simple. I have 2 metal part with 1 interface between them. The first body temperature is T1, the second body temp. is T2. Goal is to see the modified temperature after certain time. My question is, how can I initialize the different temperatures? Based on creo simulate: 1.) I can define 1 temperature in full field, this solution of course is not ok 2.) I can define temp. distribution from previous steady simulation result but it seems, the result is total wrong with this solution. Any idea? I can't believe that it is a complicated task for simulate...   Thanks Roland

Hello,I'm starting to use the mechanisms with Creo and would like to play a kinematics with a bevel gear (or conical pair ,  I do not know the translation of "coppia conica" in italian),   similar to the one in the video I've linked (they're only 3mb).  The assembly is very simple, it is composed of: A)a fixed body (the vertical shaft to which the first gear is fixed , they do not rotate and does not move) B) the moving bodies: the horizontal shaft (motor), which being free to turn both on its axis and on the vertical one, will turn the box into  which it is inserted (with tho radial spherical bearings ). I should also understand how to set the ratio so that 90 degrees of rotation on the vertical axis correspond to 90 degrees of rotation of the horizontal shaft axis, in practice 1: 1. Reading the guide I understand that to use the mechanisms in Creo Parametric  you must use the constraints defined by the user instead of the automatic co

I don't understand the problem...  

I am trying to determine the best method for simulating an assembly with pinned joints and hydraulic cylinders that will give reasonable results with minimal run time. I have seen 4 different methods used and I wanted to get some advice and pros/cons for each one:   The method I have used in the past is to setup contact interfaces. This gives very good results that correlate well with measured data but it can take hours to run in some cases. When you have 6-12 loading conditions to check this is very time consuming. The second method I have seen used is to define weighted links and springs. My understanding is that this won't necessarily give an accurate result for the pins stresses, but it will give good results for the assembly stresses. If anyone has a link to a tutorial on this method I would love to see it. The third method was something I saw in documentation for an older program (I-DEAS). This method used beam elements to represent the pins an

Hi ,   I have problem in my Creo where i am unable to view entire options in pop-up windows and unable to click the OK or Cancel button at the bottom. Please guide me on how to fix this. Thanks.

I usually think that more users complain about the "traffic" light indicator in Creo that shows the yellow or red status but they're unable to easily trace the cause of the issue.I stumbled on the reverse case - I have an assembly that shows a green light, yet the components in it are not located properly.  I am wondering if anyone else came across this issue.Here was my situation (Creo 2.0, M210, btw).  I noticed that the patterned components in two of my assemblies were not lined up quite right; this was not a graphics artifact - as the measurement tool was reporting a small but significant misalignment.  The green light indicator was not showing anything wrong, and I didn't see any warnings in the message log.So, after double-checking all the dimensions, I started to look at the definition of the pattern (axis-type).In the first assembly, when I initiated the edit-definition of the pattern, the clue to the problem presented itself, as the selection box which contained

I need to analysis the stick and boom models.I have tried to do the boom but stress is high in boom mounting point because i fixed a pin as X:00 Y:00 and Z:00 displacement.  

I have an assembly with a gusset bolted to a vertical beam. When I start the analysis, I get an error: "Cannot process highlighted contacting surfaces. Surface: Vert_Beam, Surface: Bolt"   I have attached an image of the highlighted surface. Any suggestions to a solution?   Thanks

Hello,   I try to push down the top part (see pict.). The inside of ring part should contact with outside faces of lower part but the result doesnt show this:     Before they go into contact the distance between faces of interfaces starts to increase. Why?   Thanks Roland

results in creo 2 fatigue advisor: OK   creo 3: wrong   creo 4: wrong   creo 5: wrong

Hello everybody,I wonder how can I make a function (for torque motors and others) like this:f(theta) = g(theta) * thetawhere theta = an input from the analysis (in my case the angle of a shaft) that I take from a measure, g() = a points/graph with theta for x-coordinate. I have the file with points but I don't know how to insert the datas )points from file) in the function f(x).   Thanks Bye

Hi Everyone,    I am looking for a way to essentially generate a graph of force balance (i.e. input and output force) of a linkage, for it's entire range of motion (360 degrees).  For example, see the attached snap.     I can do a Force Balance analysis to achieve the result I want at discrete linkage positions, but to generate that even at 10 degree intervals is somewhat tedious.  I do this by setting the input force to 1, and the load cell is at the output on the linkage.     If I do a dynamic analysis, every body must have mass and inertia, which skews the result.  If I could disable inertia like gravity can be disabled, than this would not be an issue.     Is there an easy way to do this?  I feel like this is an overly simple problem.  I could do this with pencil and paper, but also don't want to generate tables that way with each design iteration.     This is something that has stum

(view in My Videos)