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Hi All, Thanks for your inputs...very helpful Mike, you're reference led me to MIL-STD-480, Sections 5.1 and 5.2, which define Class I and Class II changes...just what I was looking for. Thanks again! Chip

Most companies employ change classes on their engineering change documents to indicate whether the changes are major (affecting form, fit, or function) or minor (eg, typos). My experience is that Class I indicates major changes and Class II, minor. However, I don't know of a reference that...

That sounds like what I want, however, I don't seem to have that option. I'm using WF2.0...are you using another version? Thanks, Chip

Thanks! That's a helpful tool. Too bad there's not a "lock all dimensions" button...I can't figure out how to create a mapkey that does this, yet. If I do, I'll post it. Chip

I would like to select all dimensions (only) in the sketcher in order to toggle lock the dimensions. The only way that I know how to do this is to manually control-click each dimension. If I window select the dimensions, most of the time it will also select some kind of geometry as well...

Thanks for the many replies. The best behaved solution (two different methods were suggested) that was provided: Use the following 2-sketch method: 1. In the first sketch, sketch your spline. 2. In the second sketch, use edge on the spline from the previous feature 3. Draw your desired arc...

I have created a 2D spline in Sketcher. I would like to connect a circular arc at one end of the spline, and make the two tangent to one another. However, when I apply the tangency constraint to these two, it alters the curvature of the spline. I would like the spline to be fully constrained...

Thanks, but I tried that before asking the question. As you can see from your google search, no source for the code is readily apparent from a web search. Anyone know of a source?

Does anyone know where I can buy BOSOR FE software? Thanks, CRB

I apologize...I mis-typed it... should read "...ASME B36.10, B36.19,..." Sorry for the confusion.

Thanks, Steve, for the advice. Chip

I should clarify...this project is not governed by code. I will be using the pipe for R&D work, and there is no safety concerns. I've found pipe at distributors (such as API5L B/ERW, API5L B/DSAW, and A53-B WP ERW), but the distributors do not know which documents govern the dimensional...

I need to get the appropriate specification that covers the allowable diameter and wall thickness variation, and ovality of ERW and DSAW steel and stainless steel pipes. There seems to be an abundance of specs (ASTM A53, A530, A999, A312, ASME B36.10, B39.10, API 5L)...which spec covers the...

Batman2: Thanks for the suggestions. This is an experimental program. These structures will be tested, but no production is planned. Julian: Thanks for the advice. Good points all. Now I have closed form solutions (Donnell, Timoshenko, etc.), eigenvalue solutions, and nonlinear solutions...

All, Thank you for your help. The magnitude of the initial geometric perturbation was the key. I started with a magnitude of 14% of the wall thickness. After your suggestions, I ran with various magnitudes from 14% down to .06%. The knee of resulting load-deflection curves became sharper as...

bvi, Yes, I found the same thing with an axisym model. I'm now running a 1/8 shell and solid models with better results. Thanks!

TGS4, Answers to your questions: -Largest magnitude of your initial displacements (for initial imperfrections)is 0.03 (R=5, t=.21). So largest init disp is about 14% of thickness? -Only geometric non-linearity is modelled. -Loads do not follow deformed geometry...direction and area...

I have a theory, but need more info on the configuration. I'm having a hard time visualizing how the tongue penetrates the facesheet of the vertical panel...is the tongue vertically oriented? Does the tongue insert into the edge of the vertical panel? Does the tongue penetrate the horizontal...

I am performing nonlinear buckling analysis using COSMOS/M of long thin-walled cylinders under external lateral pressure, using the eigenvalue buckling mode shape as the initial geometric imperfection. I (perhaps naively) was expecting the resulting load-deflection curve to have a nice sharp...