Difference between coupling and constrain equations in ansys

  • #1
What is the difference between coupling and constrain equations in ansys
 

Answers and Replies

  • #2
minger
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IIRC one is on a nodal basis, while the other is on an element basis.
 
  • #3


Thanks

Can u explain be with a example or in detail and wt does iirc means
 
  • #4
minger
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IIRC == If I Remember Correctly

As far as an example, I typically preferred to do coupling on a nodal basis, via CP, CPINT, or CPCYC commands.

CP is used when typically when you're manually joining together two groups of nodes that may not necessarily be coincident.

CPINT is used when you have two adjacent surfaces that you'd like to connect. Often times I would use these instead of contact regions. Contact regions make the problem nonlinear and increase solution time drastically. Aside from that, they are picky and can often ruin a solution if not defined well.

So, as an example, let's say that you're doing a 2D axisymmetric analysis of two tubes, one which fits inside the other. You could take the nodes at the interface and couple them via CPINT only in the UX direction (radial). This would allow the parts to slip both tangentially (if doing 3D) and axially.

CPCYC is cyclic coupling. I've typically used it when doing a 3D sector analysis. The other option is the CYCLIC command which like coupling commands, increases solution drastically. If you were doing a slice of a part, you would select the outer slice nodes, issue the CPCYC command in all directions (ensuring you were in the correct coordinate system).

All of the CP commands assume that you either have matched nodes, or at least close. There is typically a tolerance on the commands, but aside from that they assume matched nodes. In fact, if you increase the tolerance too much, you'll get nodes being coupled to more than 1 node on the adjacent side, and the solution will bomb.

CE commands are very similar except they operate on an elemental basis, meaning they doing require matched nodes. Because of this, however, I find that they don't quite work as well.
 
  • #5


thanks for the info.


i am doing a chassie static analysis how can i best transfer the mass of a structure sitting on the chassie. i know that creat a mass element and it can transfer the load but connect it throug CP or RBEs confused pls help me
 
  • #6
minger
Science Advisor
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I would use CPs. I know of RBEs, know that they have their uses, but haven't found myself using them very often. Create a mass and CP it to the applicable position(s) on the chassie...do you mean chassis?
 
  • #7


I am doing a G load analysis,Can any suggest the correct value to GRAVITY

Model Units in MM, Density in Tonne/mm3, Youngs Modulus in MPa

I am confused weather to take 9810 or 9.810

Please Suggest
 
  • #8
minger
Science Advisor
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What are the units of acceleration? What unit are you using for length? What about time? You're using metric, it should be pretty straightforward.

Be lucky you doing have to worry about gc.
 
  • #9


If Length in mm g is mm/s2 is the value of g will be 9810 mm/s2 or 9.810 mm/s2 confused little bit please help me out.
 
  • #10


Try solving the following equation using [kg] and [m/s²] to get [N]:

F = m.a

Now try again combining [kg] or [tonne] and [m/s²] or [mm/s²].

Which mass and acceleration units can be combined to give the same numerical result as [kg] and [m/s²] ?

Which combination returns consistent units ?
 
  • #11


Thanks Boss I got your answer
 
  • #12


Hi Boss

I am doing modal analysis free-free on a structure on which a huge mass is sitting i have created a point mass element and connected using CERIG to transfer mass. Does the analysis will consider the huge mass and give the results or there is any other option.

Also how to cross check in ANSYS weather the mass is transfered to the structure or not.

Please help me
 
  • #13
minger
Science Advisor
1,496
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Check your output file. It lists total mass of each defined element type.
 
  • #15


hi,

i am doing static analysis of compressor housing. i am considering shell 91 element for generating FE model as it has the option of taking thickness in one direction, wereas other elements take thickness from center and divide it equally either sides.

but my problem is that shell 91 is giving a message

ELEMENT 1 HAS A RADIUS/THICKNESS RATION OF 0.1085(MIN RADIUS OF CURVATURE OF 0.32 AND A MAX THICKNESS OF 3). THIS VOILATES THE ASSUMPTION OF A SHELL ELEMENT.

whenusing shell 181 the problem is solving with out any errors.

please help me in solving the problem using shell 91 or any other element having option of taking thickness in one direction
 

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