Despite being a subject that is not applied as a subject, its expression and application has been quite understandable. It was a good practice in terms of not having a lot of resources in this regard.I am waiting for the continuation of the videos.
Dear meric büyükkoyuncu, Thank you very very much for the tutorial. It helped me to validate my work. I am eagerly waiting for your next video. I hope you will arrange some time to help others from your busy schedule. May Almighty reward you for your good deeds. Please keep up the works... I would also like to ask you if you can elaborate damage analysis of composite stiffened panel with skin stiffener debonding/delamination using the Cohesive Zone Element method.... Best wishes...Rayhan S.B.
Thanks for the great video. Also I have a doubt, does the final result (F vs disp) depend on the scale factor of 0.004, will the chart be very different if the scale factor was different?
Elinize sağlık çok güzel bir çalışma, başta girdiğiniz nonlinear özellikleri için bende plasticity nin içinde nonlinear komutu yok multilinear ve bilinear var sadece 2019 kullanıyorum sürümden dolayı mıdır acaba ?
Merhaba, öncelikle güzel yorumlarınız için teşekkür ederim. Bu plastik özellikler 2020 ile geldi. Ansys 19 ile ilgili diğer videomu izlerseniz orada sizin işinize yarayabilecek multilinear isotropic hardening ile kullanabileceğiniz bir excel hazırlama örneği var. Aşağıya linkini bırakıyorum. th-cam.com/video/SHqUajOzEMg/w-d-xo.html
Hello! First of all thanks for your tutorial - it was very helpful and you should make some more! I would like to ask, how did you find the specific parameters for the power law for aluminium? I couldn't find any similar values on the internet.
Thank you for your nice comments. I find these parameters by searching. In the video, I showed the related article. If you are lucky enough, you can find these parameters for different materials
Hi, thanks for your video. I am curious about the setting of the auto time step. Why you chose these values? Do you have any suggestions for the similar simulations with other structures?
@@mericbuyukkoyuncu385 Hi, thanks for your reply. Another inquiry: The "share Topology" was used in Designmode without forming the four faces as a new part, which would be a redundant step. None of edges or face will be merged in this way unless employing "form new part" for the four faces.
This video is very helpful .. i need to work on all combinations of local and global eigenmode (buckling of subpanel and stiffeners) and sin/ cos functions also with half waves. could you please guide me
perçinli bir model yapıyorum fakat çökme yükü için structural bloğunu eigenvalue bloğuna bağlarken solution kısmı update olmuyor ve "Update failed for the Solution component in Eigenvalue Buckling. Error updating cell Solution in system Eigenvalue Buckling." hatası geliyor. scale factor 0.004 olarak girdim.
Thank you for your comments. I don't know another method to find ultimate load. Because this is iterative solution (It has to be), so you need to have this graph to see the ultimate load. This graph is the conclusion of the reaction of the plate to the given displacement . This reaction is a outcome of displacement on the plate. Therefore I don't know another method whether another method is exist or not.
@@mericbuyukkoyuncu385 oh ok.. thanks for your time and reply... I really appreciate the way you try to answer all most all queries... Keep going sir.. thank you
4:24 de yazdığınız initial yield stress ve exponentin JC teoremindeki A ve n parametreleri olduğuna emin misiniz başka nonlinear analizlerde testle benzer sonuçlar alamıyorum da
Sir, in the paper they have taken 'Shell element S4R' for FEA (It is mentioned in the section 4.2 ). but in your video it is said which element you have considered. please show us how to select elements(like SOLID 181, SHELL81 etc) in ANSYS workbench.
When you apply "Surface From Skecth" Shell elements are automatically created. There are 2 options as Shell 181 and Shell 281. In the video probably Shell 181 is used.
@@hlulanirikhotso729 Okay I got it. In 21:58 we applied this little process. I carried solution of eigen-value buckling analysis into the new static structural's model. Therefore initial imperfection goes to the new static structural anaylsis.
How do I contact the surfaces in case of T stiffeners? Is it okay if I select the web edge as a target and the flange face as the contact body by making another contact in ANSYS? I would be glad to get an answer.
Ilk burkulma yükünü nasıl bulabiliriz, (N_critical=N_applied*load factor ) denklemi makale sonucundan çok uzak bir burkulma yükü veriyor bu değeri bulmanın bir yolu var mıdır?
@@mericbuyukkoyuncu385 örneğin bu model için Load factor 1343 civarı cikiyor sizde de 1343.8 , N appliad 100 N/m kritik buckling yükü 134 KN çıkıyor makalele göre ise specimen A karşısında initial plate buckling olarak 74,5 KN yazıyor.
@@hakansezen2019 İşlem yaparken birimlere çok dikkat etmemiz lazım, bazen gözden kaçabiliyor. 1348,8 ile 100N/m çarpıldığı zaman 134 kN/m çıkmaktadır. Makaledeki birime çevirmek için yapılması gereken bir işlem daha var. Kritik buckling yükü hesabını aşağıdaki yorumlarda başka bir izleyici yapmıştı. İsterseniz onun hesabından kendinizinkini kontrol edebilirsiniz. Onun hesabı doğru gözüküyordu baktığımda.
In the non linear analysis, you have applied a displacement of 2.5mm to the bottom edge. Should it not be 1.25mm to the bottom edge and 1.25mm to the top?
@@bhagyahb2811 just give a meaningful value and draw load vs displacement graph until you see the "peak" point like 34:47. Also you can see the graph here : hizliresim.com/OwAtQH If displacement is getting too much, go back and make smaller. If graph could not reach "peak" point, increase the displacement value. By the way, If displacement is too much you are gonna see the error, but you can check the chart and see the meaningful values.
Hi sir. I have doubt that what if, you are getting negative load factor value, after running the non-linear buckling analysis for thin cylinder, where the pressure is applied outside and inside surface of the cylinder. While I'm using shell elements for meshing
Hi Prabhhu, Sometimes load direction can be wrong. Sometimes you may define plasticity properties in the eigen-value buckling analysis. Sometimes applied load can be too much compared to the structure. You can check these firstly.
Sir, can you please tell us how to calculate initial buckling load (74.5KN) here? I modelled same as you said and I got Loadfactor = 1.3453, Applied load = 100N/mm so, 1.3453*100 = 134.5 N/mm. our panel edge dimension is sum of plate and stiffener edge that is 440 + (28*3) = 524mm. hence buckling load is 524*134.5 = 70478N = 70.478KN. Is this correct ?? please correct me if i am wrong sir.. thanks in advance
Sir, could you please do a video on this journal as soon as possible Computational study of strengthening effects of stiffeners on regular and arbitrarily stiffened plates October 2012 Thin-Walled Structures 59(1):78-86 DOI:10.1016/j.tws.2012.05.001
Despite being a subject that is not applied as a subject, its expression and application has been quite understandable. It was a good practice in terms of not having a lot of resources in this regard.I am waiting for the continuation of the videos.
Thank you for you comment
I followed your tutorial to practise stifferd plate structural modelling in ANSYS. Many thanks for the clear instructions.
This video just saved my life thanks, was very good.
Dear meric büyükkoyuncu, Thank you very very much for the tutorial. It helped me to validate my work. I am eagerly waiting for your next video. I hope you will arrange some time to help others from your busy schedule. May Almighty reward you for your good deeds. Please keep up the works... I would also like to ask you if you can elaborate damage analysis of composite stiffened panel with skin stiffener debonding/delamination using the Cohesive Zone Element method.... Best wishes...Rayhan S.B.
Thanks for the great video. Also I have a doubt, does the final result (F vs disp) depend on the scale factor of 0.004, will the chart be very different if the scale factor was different?
Elinize sağlık çok güzel bir çalışma, başta girdiğiniz nonlinear özellikleri için bende plasticity nin içinde nonlinear komutu yok multilinear ve bilinear var sadece 2019 kullanıyorum sürümden dolayı mıdır acaba ?
Merhaba, öncelikle güzel yorumlarınız için teşekkür ederim. Bu plastik özellikler 2020 ile geldi. Ansys 19 ile ilgili diğer videomu izlerseniz orada sizin işinize yarayabilecek multilinear isotropic hardening ile kullanabileceğiniz bir excel hazırlama örneği var. Aşağıya linkini bırakıyorum.
th-cam.com/video/SHqUajOzEMg/w-d-xo.html
@@mericbuyukkoyuncu385 cevabınız için teşekkürler
Thank you for your kind movie. It is very useful for me.
Excellent analysis.
why did you stop uploading sir.. Please upload more tutorials sir. it will be really helpful for us
Hello! First of all thanks for your tutorial - it was very helpful and you should make some more! I would like to ask, how did you find the specific parameters for the power law for aluminium? I couldn't find any similar values on the internet.
Thank you for your nice comments. I find these parameters by searching. In the video, I showed the related article. If you are lucky enough, you can find these parameters for different materials
how i am going to the same as thermal buckling
Thanks you very much, the procedure is very clear!
This video is great already subscribed thank you very much.
Thank you so much
This is a very good one.
Thank you so much
Hi, thanks for your video. I am curious about the setting of the auto time step. Why you chose these values? Do you have any suggestions for the similar simulations with other structures?
Hello, These values can be changed according to the case. You can set the value which make your simulation converged
@@mericbuyukkoyuncu385 Hi, thanks for your reply. Another inquiry: The "share Topology" was used in Designmode without forming the four faces as a new part, which would be a redundant step. None of edges or face will be merged in this way unless employing "form new part" for the four faces.
@@heshenghan1385 Yeah, that was unnecessary. Forget about share topology
This video is very helpful .. i need to work on all combinations of local and global eigenmode (buckling of subpanel and stiffeners) and sin/ cos functions also with half waves. could you please guide me
perçinli bir model yapıyorum fakat çökme yükü için structural bloğunu eigenvalue bloğuna bağlarken solution kısmı update olmuyor ve "Update failed for the Solution component in Eigenvalue Buckling. Error updating cell Solution in system Eigenvalue Buckling." hatası geliyor. scale factor 0.004 olarak girdim.
Merhaba,
Bilgim yok maalesef
Thanks for the video..it is very informative.. Can you please tell us where we can get the ultimate load (other than in the graph)? Thanks in advance
Thank you for your comments. I don't know another method to find ultimate load. Because this is iterative solution (It has to be), so you need to have this graph to see the ultimate load. This graph is the conclusion of the reaction of the plate to the given displacement . This reaction is a outcome of displacement on the plate. Therefore I don't know another method whether another method is exist or not.
@@mericbuyukkoyuncu385 oh ok.. thanks for your time and reply... I really appreciate the way you try to answer all most all queries... Keep going sir.. thank you
4:24 de yazdığınız initial yield stress ve exponentin JC teoremindeki A ve n parametreleri olduğuna emin misiniz başka nonlinear analizlerde testle benzer sonuçlar alamıyorum da
Dear! can help me for doing steel girder bridge journal in this ansys workbench?
Sir, in the paper they have taken 'Shell element S4R' for FEA (It is mentioned in the section 4.2 ). but in your video it is said which element you have considered. please show us how to select elements(like SOLID 181, SHELL81 etc) in ANSYS workbench.
When you apply "Surface From Skecth" Shell elements are automatically created. There are 2 options as Shell 181 and Shell 281. In the video probably Shell 181 is used.
@@mericbuyukkoyuncu385 oh ok. thank you sir
how would go about adding dents or imperfections then do nonlinear buckling analysis
hello, I can not understand your question. Can you define it again ?
@@mericbuyukkoyuncu385 sorry about that. I wanted to ask how goes about introduction an initial imperfection to the model
@@hlulanirikhotso729 Okay I got it. In 21:58 we applied this little process. I carried solution of eigen-value buckling analysis into the new static structural's model. Therefore initial imperfection goes to the new static structural anaylsis.
@@mericbuyukkoyuncu385 Thank you very much. what sources do you recommend for a better understanding of Ansys?
@@hlulanirikhotso729 reach me on linkedin account
How do I contact the surfaces in case of T stiffeners? Is it okay if I select the web edge as a target and the flange face as the contact body by making another contact in ANSYS? I would be glad to get an answer.
Hi! One question: can you apply a given force instead of nodal displacement on the Non-linear buckling analysis? Cheers
Ilk burkulma yükünü nasıl bulabiliriz, (N_critical=N_applied*load factor ) denklemi makale sonucundan çok uzak bir burkulma yükü veriyor bu değeri bulmanın bir yolu var mıdır?
Ne kadar uzak bir değer veriyor ? Yaptığınız hesaplama yöntemi doğru
@@mericbuyukkoyuncu385 örneğin bu model için Load factor 1343 civarı cikiyor sizde de 1343.8 , N appliad 100 N/m kritik buckling yükü 134 KN çıkıyor makalele göre ise specimen A karşısında initial plate buckling olarak 74,5 KN yazıyor.
@@hakansezen2019 İşlem yaparken birimlere çok dikkat etmemiz lazım, bazen gözden kaçabiliyor. 1348,8 ile 100N/m çarpıldığı zaman 134 kN/m çıkmaktadır. Makaledeki birime çevirmek için yapılması gereken bir işlem daha var. Kritik buckling yükü hesabını aşağıdaki yorumlarda başka bir izleyici yapmıştı. İsterseniz onun hesabından kendinizinkini kontrol edebilirsiniz. Onun hesabı doğru gözüküyordu baktığımda.
@@mericbuyukkoyuncu385 Anladım teşekkür ederim ben KN/m ve KN ayrımını gözden kaçırmışım.
@@hakansezen2019 Tahmin ettim, rica ederim. Stiffener kenarlarının uzunluklarını da eklemeyi unutmayın hesaplarınızda.
In the non linear analysis, you have applied a displacement of 2.5mm to the bottom edge.
Should it not be 1.25mm to the bottom edge and 1.25mm to the top?
It would be. You can do it like that in your analysis. But due to the article, it should be like how I applied the boundary conditions.
Hi
How to add a displacement in order to get a chart of load V/S displacement
In the first "nodal displacement" I applied 2.5 mm displacement. At the 33:20 I add this displacement into the chart to draw load vs displacement
@@mericbuyukkoyuncu385
Sir,If I don't know the displacement values then what can I do
@@bhagyahb2811 just give a meaningful value and draw load vs displacement graph until you see the "peak" point like 34:47. Also you can see the graph here : hizliresim.com/OwAtQH
If displacement is getting too much, go back and make smaller. If graph could not reach "peak" point, increase the displacement value. By the way, If displacement is too much you are gonna see the error, but you can check the chart and see the meaningful values.
@@mericbuyukkoyuncu385
I will try it sir, thank you so much
@@mericbuyukkoyuncu385
Sir can you give me your Email id
Sir, what to do if I don't have the option to add nonlinear isotropic hardening power law in the plasticity?
Add multilinear hardening. Watch my other nonlinear buckling video
@@mericbuyukkoyuncu385 Okay thank you soo much sir for replying 😊
@@bettykuriakose2355 You're welcome :)
Good Jobs, thank u sir...
very helpful, thank you
hi, pls let me known buckling load the bigger the better or the smaller the better. thanks
Hi sir.
I have doubt that what if, you are getting negative load factor value, after running the non-linear buckling analysis for thin cylinder, where the pressure is applied outside and inside surface of the cylinder. While I'm using shell elements for meshing
Hi Prabhhu,
Sometimes load direction can be wrong. Sometimes you may define plasticity properties in the eigen-value buckling analysis. Sometimes applied load can be too much compared to the structure. You can check these firstly.
Thank you sir
The applied force in this paper is 500 Kn, how to convert into the distributed load ( linear pressure) 100N/m
It does not matter, load multiplier multiplies it anyway. You can apply 500 N/m. Does not matter
@@mericbuyukkoyuncu385 Ok, thank you sir
@@chagraouihamda2272 You are welcome
Sir, can you please tell us how to calculate initial buckling load (74.5KN) here?
I modelled same as you said and I got Loadfactor = 1.3453, Applied load = 100N/mm
so, 1.3453*100 = 134.5 N/mm. our panel edge dimension is sum of plate and stiffener edge that is 440 + (28*3) = 524mm.
hence buckling load is 524*134.5 = 70478N = 70.478KN. Is this correct ?? please correct me if i am wrong sir.. thanks in advance
It seems right.
Sir, could you please do a video on this journal as soon as possible Computational study of strengthening effects of stiffeners on regular and arbitrarily stiffened plates
October 2012
Thin-Walled Structures 59(1):78-86
DOI:10.1016/j.tws.2012.05.001
Can you give me the link of the article? I really need to check it out. please
drive.google.com/file/d/1lWitoGUCNtWHDxy771eYxHcKm6KFXMh6/view?usp=sharing
@@mericbuyukkoyuncu385 oh. Thank you so much
@@sinhpham538 you are welcome