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#AUTODESK INVENTOR 2010 STRESS ANALYSIS SOFTWARE#
Images of the software are attached, thank you in advance. If anyone knows of anything I may be doing wrong I would appreciate the help.
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To reiterate, when the analysis is set to actual, so that the movement is what it would be without exaggerating it, I do not see the same amount as with the real thing. However, in the software I do not see the same level of displacement as on the actual chassis. I can see with the physical chassis that there is definitely torsional flex. I have performed a similar test where I took the front of the chassis and rotated it in one direction while the other laid flat, so essentially one end was fixed and the other was being torqued like in the software. I have actually had this assembly created and have it sitting in the lab. Some of the contacts may be incorrect, but my knowledge in this environment is limited so I used what the software spat out. I have also used the automatic contact tool to apply contacts between parts. I now have fixed one end of the assembly and applied a moment to the other of 1000 in-lbs, which I think is rather high but I wanted to see what would happen with a moment that could exaggerate the displacement. I have made an assembly of the parts using strictly mates, both face to face and flush mates. With the help of the software my final model ended up being 3/8 steel plate and i used 4 locating holes.I have been using the stress analysis environment in Autodesk Inventor to find the torsional displacement of a chassis I have been constructing. Search or browse from the navigational panel on the left or simply start with the essentials below. The more the plate was allowed to flex(max deformation) the lower the stress concentration was but in this case designing the bracket to handle the stresses rather than allow deflection was key. Here you can acquire essential skills through video tutorials and much more. For instance in this case, the more rigid the plate was, the higher the stress concentration at fillets was. Not only for the part you are designing but the hardware you use, what its connected to etc. Understanding why this is so and what the effects are is cruicial. You can see that changing the constraints makes a huge difference in stress distribution of the model. Same material leaving out the small hole as a bolt location. That was 3/8" steel only using the small hole where MAX is and the original caliper bracket holes on the left to hold the plate
#AUTODESK INVENTOR 2010 STRESS ANALYSIS UPGRADE#
Here are a few screen shots of a big brake upgrade i designed and i used inventor to help narrow down how i wanted to restrain the plate and also material and thickness. 2.1 Finite element stress analysis above of a solid modeled Inventor part is very fast and convenient. The software will help optimize your design by pointing out theoretical weak spots. Also these results are only to help "focus" your design and should not actually replace hand calculations and common sense. If the part isnt correctly restrained or loaded the data will tell you nothing. Inventor should have a help file that will walk you through the basic procedure, but like i said without an understanding of the physical relations you are attempting to simulate the results are junk. A mesh is applied to your part and the resolution of this mesh will determine how accurate the distribution is. The accuracey of the distribution also is dependant on mesh size. This is based on the geometry obviously and also the material( atomic structure and all its physical properties). When you perform FEA(finite element analysis) the software(ansys in this case) is actually looking how the load is distributed throughout the part. Having an understanding of constraints and loads is cruicial before attempting any sort of FEA. Without understanding the context of what you are doing, the results will not be useful. The amount of deflection in the spring sheet as a result of exposure to this mounting model force was examined.