Godo work. Few minor comments: (1) Forth the classical mesh sensetivity study, the new refined mesh must contain all of the previous coarse meshes; a simple way to achieve this is to reduce the element size by 1/2 with each refinement. Many times it is hard to achieve, so atleast try to get closer to previous mesh. (2) Convergence check should not be done on arbitrary point, especially when it is integration point variable. With mesh refinement, the integration point keep on shifting. In such case, convergence check should be done at the point closest to the previous one (or even better a cloud of points). (3) For displacement based elements, the higher order derivatives converge relatively slowly than displacements. So higher order quantities are better check for convergence, unless the interest quantity is displacement only. Additionally, it is also advised to use individual components than resultants as it also gives hint regarding which direction mesh refinement is better.
Thanks for the really good response to the video. The one thing you mentioned that has been on my mind is the recording of the new stress from an arbitrary point. Since making the video, I realised that I should have been taking the measurement from the exact same location, and this is what I have been teaching in my labs, but unfortunately it's not included in this video.
+landoflemon hi, i would like to contact u directly, if u wouldn't mind drop your email, or whatsapp, or facebook contact for me chinobright1@gmail.com cheers
@@landoflemon But, upon refinement of the mesh the geometry of element at a particular location is gonna change, so does the elemental stress. How to tackle this issue?
That's an interesting point, I'll have to look into that. If it is introducing artifacts, at least they will be consistently distributed as you go closer to the centre, not randomly, as would be seen with the default meshing.
Very nice Job - I liked the mesh partitioning part in the beginning ... it would be interesting to see, though, how different the results to the Abaqus "default" meshing would really be, since your mesh elements were getting smaller and smaller around the center, wouldn't that introduce artifacts as well?
Thank you for the explanation for mesh of cylinder. I tried this method, and it gives high percentage of warning elements after verifying the mesh. My question is if these warning elements will affect the results. Thank you :)
Excuse me, I have a circular pin and I want to test it under four point bending load. Can you tell me please how can I divide the pin into four non equal parts in order to apply a four point bending load on the pin.
Hello my friend. Congratulations, this tutorial has been really good. I have a doubt, when you did the graphic on excel how u did it? i mean did u use any formula? i would like u helpe out.. thanks a lot...
How did you bold the element like that on the first mesh? mine is just on the surface even though i assigned the material but still the mesh inside is empty when i cut-view inside
Hello Please I need help regarding the mesh of a cylindrical tool (shoulder and pin) modeled by a 3D solid analytical rigid type in Job there is an error that is displayed (Error in job Job-1: ELEMENT TYPE C3D10 IS NOT AVAILABLE IN Abaqus/Explicit) Thank you.
Hi, great video My only question is why did you apply a load (7e5) to one part of the circle quadrants? (7:55) P.s I'm looking to use this pin as part a four point bending test.
+blazedouble07 You're welcome, it's been a while since I made the video, but I think was just demonstrating very quickly how to apply a load. I know it would be strange to just load one quadrant, it was simply just an example, because I don't think I ended up running any kind of analysis on that model!
Hello I am trying to model a 3D cylinder with a constant rotation of 45 rad/s. I have meshed the cylinder similar to this tutorial with a much finer mesh. I have applied the angular velocity using a predefined field but am getting a varying stress field for the hoop and radial stresses over time. If you could give me any thoughts or suggestions it would be very much appreciated.
Hi Cian, if it's a 3D cylinder rotating in space with a constant velocity, I don't understand where the stress would be coming from? Is it purely a result of the rotational velocity (approx 430 rpm)? Or is there some other load/displacement/contact applied?
Just pure constant rotational velocity.There is a boundary condition on the central axis such that U1 = U2 = U3 = 0. Other than that nothing else is applied to the disc other than the predefined angular velocity field. I have tried running the simulation in double precision and also with second order accuracy wedge elements but still get an unrealistically high and steadily increasing stress field.
I am trying to do a simple fixed beam analysis with a concentrated load in the middle. The problem is my solution is not converging as I refined the mesh. The maximum stress just keep increasing, Any help please?
I there. One thing I forgot to mention in the video is to pick the same location to measure your stress value from. It's no good if your max stress keeps moving around to different locations in your model. The stress really should be converging, are you sure you're refining the mesh to a high enough density to achieve convergence? Have you tried locally seeding around your location of highest stress and just increasing the mesh density in this location?
Thanks for the help. But I think that I figured out what was happening. Since it is a point load, i.e a load over an infinitely small area. Therefore as i was refining the mesh the stress was just getting bigger and bigger which was in a way converging to infinite stress. btw do you know how to overlay different plot (graphs)? I want to plot different meshing results on the same graph. Thanks in advance
Very pedagogic, explained at the perfect speed for me. Thanks!
thanks Dan brah. Project due Monday watching this Saturday has helped a lot.
Evan Kelly No problem brah! I see you mirin my FEA skills!
Thanks a lot for this video, it has been so much helpful!!!!
I needed a video simulation of the pieces for anything to see orders Entry to the program
abaqus
Very necessary
Thanks for the help in this Alvedioa
Thank you! This video helped me a lot to improve the mesh of my model of indentation testing.
Godo work. Few minor comments:
(1) Forth the classical mesh sensetivity study, the new refined mesh must contain all of the previous coarse meshes; a simple way to achieve this is to reduce the element size by 1/2 with each refinement. Many times it is hard to achieve, so atleast try to get closer to previous mesh.
(2) Convergence check should not be done on arbitrary point, especially when it is integration point variable. With mesh refinement, the integration point keep on shifting. In such case, convergence check should be done at the point closest to the previous one (or even better a cloud of points).
(3) For displacement based elements, the higher order derivatives converge relatively slowly than displacements. So higher order quantities are better check for convergence, unless the interest quantity is displacement only. Additionally, it is also advised to use individual components than resultants as it also gives hint regarding which direction mesh refinement is better.
Thanks for the really good response to the video. The one thing you mentioned that has been on my mind is the recording of the new stress from an arbitrary point. Since making the video, I realised that I should have been taking the measurement from the exact same location, and this is what I have been teaching in my labs, but unfortunately it's not included in this video.
+landoflemon
hi, i would like to contact u directly, if u wouldn't mind drop your email, or whatsapp, or facebook contact for me chinobright1@gmail.com
cheers
@@landoflemon But, upon refinement of the mesh the geometry of element at a particular location is gonna change, so does the elemental stress. How to tackle this issue?
Thank you very much !!
Thanks for the Video!
Thanks. Very important knowledge here!
That's an interesting point, I'll have to look into that. If it is introducing artifacts, at least they will be consistently distributed as you go closer to the centre, not randomly, as would be seen with the default meshing.
Just what I needed, Thank you. Paste more
Excellent Explanation, Thanks very much.
Thank you so much, this is a very nice work
Congrats, mate! Very good tutorial :)
explanation is very good..thank you
Thanks man, huge help
Very nice Job - I liked the mesh partitioning part in the beginning ... it would be interesting to see, though, how different the results to the Abaqus "default" meshing would really be, since your mesh elements were getting smaller and smaller around the center, wouldn't that introduce artifacts as well?
Thank you for the explanation for mesh of cylinder. I tried this method, and it gives high percentage of warning elements after verifying the mesh. My question is if these warning elements will affect the results. Thank you :)
Thanks for the positive feedback, I'm afraid I have never used any of the thermal features of Abaqus to induce a stress.
landoflemon hi man i need a help regarding abaqus
thanks for sharing..nice explanations
Excuse me, I have a circular pin and I want to test it under four point bending load. Can you tell me please how can I divide the pin into four non equal parts in order to apply a four point bending load on the pin.
THANKS VERY MUCH. YOU ARE GREAT
Hello my friend. Congratulations, this tutorial has been really good. I have a doubt, when you did the graphic on excel how u did it? i mean did u use any formula? i would like u helpe out.. thanks a lot...
very nice. if this column under temperature, how to create temperature in abaqus.thanks
great! solved my problem! thanks.
How did you bold the element like that on the first mesh? mine is just on the surface even though i assigned the material but still the mesh inside is empty when i cut-view inside
Hello
Please I need help regarding the mesh of a cylindrical tool (shoulder and pin) modeled by a 3D solid analytical rigid type in Job there is an error that is displayed (Error in job Job-1: ELEMENT TYPE C3D10 IS NOT AVAILABLE IN Abaqus/Explicit)
Thank you.
thank you very much
+Maryem Oudhini You're very welcome :-)
thank you very helpful video
Thank you man!
hi. can you post a video of modelling of concrete pole with reinforcements.
can you show procedure of encased stone column in abaqus
Thank you sir...
thank you
Hi, great video
My only question is why did you apply a load (7e5) to one part of the circle quadrants? (7:55)
P.s I'm looking to use this pin as part a four point bending test.
+blazedouble07 You're welcome, it's been a while since I made the video, but I think was just demonstrating very quickly how to apply a load. I know it would be strange to just load one quadrant, it was simply just an example, because I don't think I ended up running any kind of analysis on that model!
+landoflemon I see, thanks man
Hello
I am trying to model a 3D cylinder with a constant rotation of 45 rad/s. I have meshed the cylinder similar to this tutorial with a much finer mesh. I have applied the angular velocity using a predefined field but am getting a varying stress field for the hoop and radial stresses over time.
If you could give me any thoughts or suggestions it would be very much appreciated.
Hi Cian, if it's a 3D cylinder rotating in space with a constant velocity, I don't understand where the stress would be coming from? Is it purely a result of the rotational velocity (approx 430 rpm)? Or is there some other load/displacement/contact applied?
Just pure constant rotational velocity.There is a boundary condition on the central axis such that U1 = U2 = U3 = 0. Other than that nothing else is applied to the disc other than the predefined angular velocity field. I have tried running the simulation in double precision and also with second order accuracy wedge elements but still get an unrealistically high and steadily increasing stress field.
thanks a lot
GRACIAS
Do you have tutorial make element frame 2D with earthquake force
I am trying to do a simple fixed beam analysis with a concentrated load in the middle. The problem is my solution is not converging as I refined the mesh. The maximum stress just keep increasing, Any help please?
I there. One thing I forgot to mention in the video is to pick the same location to measure your stress value from. It's no good if your max stress keeps moving around to different locations in your model. The stress really should be converging, are you sure you're refining the mesh to a high enough density to achieve convergence? Have you tried locally seeding around your location of highest stress and just increasing the mesh density in this location?
Thanks for the help. But I think that I figured out what was happening. Since it is a point load, i.e a load over an infinitely small area. Therefore as i was refining the mesh the stress was just getting bigger and bigger which was in a way converging to infinite stress.
btw do you know how to overlay different plot (graphs)? I want to plot different meshing results on the same graph. Thanks in advance
Just export the separate data to excel and graph it there perhaps?
Thanks man, It helped! :)
i think its a singularity problem !
Ansys has automatic convergence its disappointing that ABAQUS and Catia are in cave men era
then go use ANSYS...
What if the location of the maximum stress changes?
Could mean that you're starting off with a mesh which is too coarse.
landoflemon thanks
I'm afraid not, in Ireland we don't have earthquakes! :-)
jajaja 6:47 until 6:57
thank you, but your voice is too low.