Recent content by cspkumar

A detailed description of the solid model (plate?, rod?) and the applied load will be helpful here. You can display the stress vectors using "plvect" to gain further insight. I don't know how to attach pictures either.

I am using the Augmented Lagrangian method & tried normal contact stiffnes, FKN of 0.1 (default is 1, I think) & the model did not run past 2% of total load. I have not run the model with penalty method yet. Thanks

Thanks for your reply. I tried nsubst,100,1000,20 but the model converges only until 10% of load. I get a warning saying that 2 contact points have too much penetration. Also tried standard contact instead of no separation and I get the same message. Currently I am running the model by slowly...

Hello, I have a convergence problem with my contact model. I have a Ubolt (Solid185) which is wrapped around a tube (Shell 181) (modeled such as the bottom inner node of the Ubolt has almost no penetration/gap with the bottom node on the tube). No separation contact is used because the bolt...

The slenderness ratio is well above the minimum. Increasing the mesh density did not change the frequencies in beam188 elements.

The moment of inertia's are exactly the same for Beam4, Beam44 and Beam188 elements. Also, modeled with shell elements and the frequencies are different. If E, I and m are the same then, frequencies should be the same I thought, correct? Thanks.

I knew about the theories behind the beam elements. I thought shear deformation does not play any role in modal analysis. But the results contradict this. Why? Thanks.

Hi, I ran a modal analysis of a hollow rectangular section cantilever beam with beam4, beam8 and beam188 elements. Beam4 and Beam44 produced the same frequencies for bending modes and match closely to hand calculations. But results with Beam188 differ by ~30%. Can anyone explain the reason for...

Hi, I ran a modal analysis of a hollow rectangular section cantilever beam with beam4, beam8 and beam188 elements. Beam4 and Beam44 produced the same frequencies for bending modes and match closely to hand calculations. But results with Beam188 differ by ~30%. Can anyone explain the reason for...

I have a spherical thin film supported by a ring at film's circumference. When I cool the system to an uniform temperature, intuitively it seems to me that both the ring & film should shrink together if CTE of film is same as that of the ring. In other words, it would be a sphere of smaller...

Hello, Sorry if my question was not clear. The problem what I have is how to obtain the orthotropic material properties of helical windings so that I can model them as shell elements instead of windings? Thanks

We are building a rigid elliptical torus with helically wound pre-preg carbon fibers at -/+ 30 degrees. There are 15 windings each in the clockwise and counter clockwise direction. Since its difficult to model the helical windings, I was wondering if there is a way to model it with shell...

Since the model in question is a membrane or a thin film where membrane stresses are predominant than the bending stresses, I think it's quite reasonable to model varying modulus instead of varying thickness.

Hi all, I am trying to model a circular membrane (thin film) with a variable thickness coating in Algor (thickness increases from zero at the center to a finite height at the edge). The way I have been modeling the variable thickness distribution is by having many elements to approximate the...

Hi all, It was a software glitch. Somehow it got corrupt and I had to delete and load it again. Now, the first real mode for an unloaded ring is out-of-plane flexure mode with a frequency of 11.75 Hz. The first in-plane flexure mode frequency is 12.1 Hz, which agrees with Englishmuffin's...