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10:00 If this example were tension (uniform surface load, applied to the free end) instead of transverse load, then would a single Quad4 element give the perfect answer? Again, assuming a Poisson's ratio of 0.

Your enthusiasm in the live demo made it even more interesting... I loved watching two PhDs, trying to interpret the 'rebellious' results coz of one element

48:13 What a cruel act, to use such vocabulary with a Pole. I've heard "spurious" fewer than 5 times in my life.

Hi, Lukasz, this is one great explanation. I have one question with regardless to plastic theory. I am reading your enterfea blog, and I know that you are using Rfem software, and I want to compare Von Misses plasticity implemented in Rfem and for example Adina or Abaqus . I am not talking about large strain plasticity (probably this is not implemented in rfem). In Abaqus or Adina Von Misses plasticity is followed by FLOW RULE and YIELD FUNCTION, but, what about rfem is it the same math or something else, maybe simpler?

I think you should also compare the displacements. The quad4 presents a locking behavior that you are not looking in your examples.

Hello! :) Please, could you tell me, how to make this example in SolidWorks ? I need help with the fixtures, connections. I mean, what is the contact interaction between the components and which degrees of freedom are removed to be model stable.

As an Economics Graduate i say YES. I am nowv studying Mechanical Engineering so if one gets this Joke, place a thumbs up 😂. Economist abuse Math 😂

thanks for this incredible video i have a question , why there is second mode and third mode of buckling while it's supposed to collapse at first mode of buckling ?

Hej Łukasz. Could you start your videos with a brief description of boundary conditions applied? As for this example - when there are nonlinear contacts involved and there's seemingly nothing that stabilises the model (model is not fully constrained, contacts are not 'bonded') is it 100% reqquired to explicitly use "soft springs" / "rigid body motion" or whatever this may be called in other software? Or based on contact types do some packages like ANSYS or FEMAP somehow resolve it in a different way or automatically? I'm asking since an analyst in my company (ansys) said he doesn't have to apply soft springs, ansys just moves on on its way and frictional contacts stabilise the model. In theory empty places on stiffness diagonal are disallowed numerically...

Hello, thanks a lot for this video. Very clear explanations! 😊 One question I have is what are the various methods for obtaining the averaged value? Also which is the "best" method? Thank you.

Waste of time

Thank you so much for the post. It is going to help many engineers. One suggestion to use screen pointer to indicate the exact location that you are referring to during your explanations.

unbelievable !!! this is the stuff i was looking for .....fantastic !!!

wow wow wow..... great stuff

This was a very good explanation. Thank you.

Hello! I like a lot the way how you explain everything! :) May I ask what is the name of the software you used for the FEA ?

I NEED TO FIND DISPLACEMNT VALUE CAN YOU HELP ME FROM MY RESULTS OF BUCKLING ANALYSIS OF HELICAL SPRING.

Really amazing topic to go with. Can we get the Power point presentation slides.....

👋

Thank you for your talks

thank you for sharing with your experience

Thank you, Lukasz. What material behavior model did you use? (Bilinear or multilinear)

interesting.

Superb explanation. Would love to have had this kind of professors at my university. Everybody just grasps ober the topic, like not even knowing it that deep. Sad.

Do you do CFD as well or just fea

Thank you again Sir Lukasz for the result of your non linear analysis. It clearly shows 2 shear plane occurs per each Lug. This is very useful since there is no code gives clear guidelines whether 2 plane shear or single plane shear will be applied on pin-connected member. Therefore for this configuration where there is axial uniform load is applied 2 plane shear will be applicable..But what about if the load is not uniform when there is a out of plane load, especially occurs in Lifting Lugs where the sling with angle attached to the shackle, then pin shackle connected to the pin hole.. In this case load is not uniform, then single plane shear maybe more applicable for shearing stress?

Good pronunciation, escpecially RRRR

Hi I'm looking for an FEA software which has user friendly pre and post processing And ability to handle and mesh complex gemoetries which curvatures. Can you please suggest one

in minutes 8.10 ; what material model do you use to achieve negative slope like that? Why is there no strain hardening phase indicated in the graph?

Great 🎉 You got a new follower

Great video

Thank you so much Sir Lukasz for sharing. This part of structure plays important role especially for heavy equipment and module lifting. Please allow me to ask my query. 1. What is the maximum von mises stress for Case-1 and Case-2. 2. Do we need to perform mesh convergence in this type. Since there is a changes in geometry like hole, there may be need to check mesh convergence? 3. Is plastic strain contour map you show for shear check can display from FEMAP, in addition to maximum von mises stress contour map? Just curious since I try to find out using STAAD, but i afraid there is no such thing plastic strain contour map. Thank you again for your sharing. Actually I almost near and close to decide to take masterclass but my remaining issue is if my software that I use is not capable to perform good output Non Linear Analysis, then it will be hard for me to follow all things. I am checking now the capability of STAAD in non linear analysis.

Thanks for great session

Thank you for the valuable tips.

Great FEA session and insights into Non-Linear analysis using equilibrium paths and indicative failure modes. I just have a question: Where did you query the equilibrium paths for all the 3 cases ? Since you divide the max load capacity by the no. of shear planes (2 in pin shear case, 4 in plates' shear failure) and the no. of parts involved (2 in case of plates' contact failure), it's unclear to me how you select the query part/geometry/node/element/surface of interest or if you just selected the entire model (2 plates + pin) and then compare equivalently with the codes? Thanks for your time and answers!

Tension failure also for lugs with small widths

Thank you for this very informative video. Which material behaviour did you use ( Bilinear,elastic-plastic or other) ?

We often neglect how powerful plastic strain plots can be.

I think not

VERY GOOD!

In Mechanical Engineering, specialty in dynamics, a bolt without pre load is unthinkable. Talking about shear loads in bolts are not common either, they are supposed to make other parts transfer the load by friction. Very nice video, keep up with the good work

Great video! Thank you :)

We helpful thanks a lot

sensivity analysis is the answer for all these questions

Very good, I was looking for how to mix plate with solid elements!

My key concern with singularities is as following: if the stress result provided by my FEA in an inside sharp corner is wrong due to a singularity and this is confirmed by the results diverging as the mesh is refined, how do I find out what the real stress is?

thank you!!!

Excellent video presentation. I wanted to ask you how I can develop that example manually since I have problems when performing the material nonlinear matrix and geometric nonlinear matrix. If you could explain with a video I would be infinitely grateful. Regards

Thumb Rule of 15% is something I am going to remember till death