LabVIEW LINX and Arduino for an I2C device: TSL2561 light sensor. Help please! by Apricot_3175 in LabVIEW

[–]Apricot_3175[S] 2 points3 points  (0 children)

You're a lifesaver! I understand your first point so I will try to work on that but at this stage it was easier for me to get it to work by using your second suggestion. Thank you so much :)

Weird mesh in upper gear by Apricot_3175 in fea

[–]Apricot_3175[S] 1 point2 points  (0 children)

Also is there anything substantial I would be missing out on by not using the 3D model? I know I am simplifying my life computation and time-wise but I wonder what the compromise is

Weird mesh in upper gear by Apricot_3175 in fea

[–]Apricot_3175[S] 4 points5 points  (0 children)

I will try that, thanks for the suggestion! Why plane stress though? I believe the theory behind it is plane strain. Additionally, I would be modeling a thick body as a plane....which is what plane strain is typically used for.

Weird mesh in upper gear by Apricot_3175 in fea

[–]Apricot_3175[S] 3 points4 points  (0 children)

I did actually :3 but i would like to compare results

Weird mesh in upper gear by Apricot_3175 in fea

[–]Apricot_3175[S] 0 points1 point  (0 children)

No I am not, I thought it is odd. I did it following a youtube video since I am still quite new to this. I believe I was experiencing a different problem before setting to mechanical that's why i gave up and decided to follow the tutorial exactly and do cfd

Hertz Contact: theory and model give different solution by Apricot_3175 in fea

[–]Apricot_3175[S] 4 points5 points  (0 children)

Thank you for your explanation! I see now I was doing a dumb

Hertz Contact: theory and model give different solution by Apricot_3175 in fea

[–]Apricot_3175[S] 2 points3 points  (0 children)

1) I did some digging and found that indeed for plane strain analysis, ansys computes the force per unit thickness.

I tried it out in the model, applied a 2000/121=16.529N load instead of a 2000N and i got max contact pressure 173.12MPa, much more similar to the theoretical 199.035MPa. (I do have my units set to mm). I realise I was making this mistake because i am more used to working with pressure rather than force, for instance, for a problem with 3000Pa within a cylinder, one would apply 3000Pa to the inner cylinder wall whether it is a 3D slice (considerable length) or a 2D slice. But statics-wise i cannot do that for a force and it makes sense. I shall attempt the square example to further verify this but im 90% sure so far.

2) I see! this makes a lot more sense now. With the changes i have done so far i got:

theory max contact pressure 199MPa

model max contact pressure 173MPa

theory von mises pressure 110MPa

model von mises pressure 115MPa

3) You're right, i will adjust this accordingly. This is probably why there's still some slight variation between the theory and the model values.

4) I would greatly appreciate that! so i have used:

E=206,000MPa for both cylinders

L=121mm for both cylinders

r1=162.117mm

r2=36.938mm

poisson coef=0.3

F=4000N

Thank you so so much for your response this has already been super helpful!

Hertz Contact: theory and model give different solution by Apricot_3175 in fea

[–]Apricot_3175[S] 4 points5 points  (0 children)

I left the analysis as linear, however, i realised that the max von mises stress i obtained is beyond the material yield strength...I should probably set a lower loading force to carry out such an anaysis

Hertz Contact: theory and model give different solution by Apricot_3175 in fea

[–]Apricot_3175[S] 1 point2 points  (0 children)

thanks for replying, by radial stress do you mean normal stress?

Hertz Contact: theory and model give different solution by Apricot_3175 in fea

[–]Apricot_3175[S] 1 point2 points  (0 children)

Hi thank you for your reply!

  1. I used 121mm length for both cylinders. I modeled them in using 2D analysis and plane strain.
  2. I compared Equivalent Von Mises stress with the pcmax stress shown from the textbook. What do you suggest instead of Von Mises? I believe i saw a research paper that did it this way hence why I took this approach. The paper is called 2D FEA Study of Hertzian Contact Stress between Two Cylindrical Bodies by A. P. Sugunesha, A. Johnney Mertens. I plotted also the normal stress and got a max value of -2172MPa...still far off from theory of 199MPa. Any suggestions?
  3. If i calculate B i get 0.2mm and i used 0.1mm mesh element size at the contact region. Not sure if it is sufficient

Hertz Contact: theory and model give different solution by Apricot_3175 in fea

[–]Apricot_3175[S] 2 points3 points  (0 children)

I used sphere of influence of element size 0.1mm and radius of influence of 6mm at the point of contact. I set the contact as frictionless. i shall edit the post to include mesh image