![Mike Fiedler](/img/default-banner.jpg)
- Видео 31
- Просмотров 15 881
Mike Fiedler
США
Добавлен 12 мар 2021
Sharing some videos about things that I enjoy in my professional life (finite element analysis) and personal life.
Autodesk Nastran Validation 17
This video is a finite element buckling analysis of a vertical round bar that is 10 inches long with a 10lbf compressive load applied at the top. The beam is checked for the buckling multiplier and buckling load in comparison to the theoretical solution.
Просмотров: 145
Видео
Autodesk Fusion 360 Validation 16 - Circular Disc with Angular Velocity
Просмотров 2942 года назад
This video is a finite element analysis stress results validation model of a circular disc of conical cross section, rotating about its own axis at 2500 rpm using the angular global load. The disc will then be checked for radial stress and tangential stress. Thanks!
Autodesk Inventor Nastran Validation 15 - Thermal Stress of a Thick Walled Cylinder
Просмотров 2542 года назад
This video is a stress results validation model of a thick walled cylinder. The outer radius is 10", inner radius is 5", height is 13" with an external pressure of 50 psi. We compare the displacement and stress of the cylinder from our Autodesk Inventor Nastran simulation with theory.
Autodesk Fusion 360 Validation 15 - Thermal Stress of a Thick Walled Cylinder
Просмотров 792 года назад
This video is a stress results validation model of a thick walled cylinder. The outer radius is 10", inner radius is 5", height is 13" with an external pressure of 50 psi. We compare the displacement and stress of the cylinder from our Autodesk Fusion 360 simulation with theory. P.S., I am aware I have skipped a couple sequential numbers in the validation series - keeping it consistent with my ...
Autodesk Inventor Nastran Validation 14 - Uniform Beam with Both Ends Fixed
Просмотров 5342 года назад
This video is a normal modes (natural frequencies) results validation model of a 1"x1" square cross beam with both ends fixed. The beam is 10 inches in length, meshed at a 0.2" size. We compare the frequencies from our Autodesk Inventor Nastran simulation with theory.
Thermal Expansion Thermal Gradient
Просмотров 2,2 тыс.2 года назад
I have been getting more questions lately about thermal stress in Inventor Nastran, so I created 2 videos to share to outline the process. This video cover the set up when there will be a thermal gradient in the part or assembly - running a thermal analysis first and then bringing those temperatures in to stress analysis. See also the video 'Thermal Expansion Uniform Temperature Distribution' f...
Thermal Expansion Uniform Temperature Distribution
Просмотров 1,4 тыс.2 года назад
I have been getting more questions lately about thermal stress in Inventor Nastran, so I've created 2 videos to share to outline the process. This video covers the process to set up a thermal stress all from within a linear static analysis - which is the approach when the part or assembly is all at the same elevated or reduced temperature (uniform temperature). The second video (thermal expansi...
Autodesk Inventor Nastran Validation 13 - Flat Plate, Two Sides Fixed, Two Simply Supported
Просмотров 3752 года назад
This video is a linear static stress results validation model of a flat rectangular plate with two sides fixed and two sides simply supported. The dimensions are 20 inches x 10 inches x 0.1 inch thick. We will use shell elements and apply a pressure load of 10 psi. We compare the stress and deflection from our Autodesk Inventor Nastran simulation with theory.
Autodesk Inventor Nastran Validation 12 - Flat Rectangular Plate, Edges Fixed, and Uniform Pressure
Просмотров 6752 года назад
This video is a linear static stress results validation model of a flat rectangular plate with all edges fixed. The dimensions are 12 inches x 6 inches x 0.25 inch thick. We will use shell elements and apply a pressure load of 100 psi. We compare the max stress tensor in the local y direction from our Autodesk Inventor Nastran simulation with theory.
Autodesk Inventor Nastran Validation 11 - Thermal Stress of a Thick Walled Cylinder
Просмотров 2,8 тыс.2 года назад
This video is a thermal stress results validation model of a thick walled cylinder. The outer radius is 2", inner radius is 1", height is 4" with a temp. difference of 10°F (cooler inside). We compare the hoop stress on the inside and outside of the cylinder from our Autodesk Inventor Nastran simulation with theory. We start with a linear steady state heat transfer analysis and use the temperat...
Autodesk Fusion 360 Validation 11 - Thermal Stress of a Thick Walled Cylinder
Просмотров 3332 года назад
This video is a thermal stress results validation model of a thick walled cylinder. The outer radius is 2", inner radius is 1", height is 4" with a temp. difference of 10°F (hotter inside). We compare the hoop stress on the inside and outside of the cylinder from our Autodesk Fusion 360 simulation with theory.
Autodesk Inventor Nastran Validation 10 - Thick Walled Cylinder with Radial Pressure
Просмотров 3502 года назад
This video is a static stress results validation model of a thick walled cylinder subjected to 10ksi. We compare the results of deflection and hoop stress from our Nastran analysis with theory.
Autodesk Fusion 360 Validation 10 - Thick-Walled Cylindrical Vessel with Internal Radial Pressure
Просмотров 1582 года назад
This video is a static stress results validation model of a 1/4 symmetry cylindrical vessel that has an outside radius of 10", inside radius of 7", height is 8" and an internal pressure of 10ksi. The material properties utilize a Poisson's ratio of 0.3 and a Young's Modulus of 30e6 psi. We will validate hoop stress and radial deflection.
Autodesk Nastran Validation 9 - Thick-Walled Spherical Vessel under Uniform Internal Pressure
Просмотров 4302 года назад
This video is a static stress results validation model of a 1/8th section of a spherical model that has a 10 in. outer radius and 7 in. inner radius. Internal pressure of 10,000 psi is applied. We compare the results of maximum deflection and maximum hoop stress from our Autodesk Inventor Nastran simulation with theory.
Autodesk Fusion 360 Validation 9 - Thick-Walled Spherical Vessel under Uniform Internal Pressure
Просмотров 1512 года назад
This video is a static stress results validation model of a 1/8th section of a spherical model that has a 10 in. outer radius and 7 in. inner radius. Internal pressure of 10,000 psi is applied. We compare the results of maximum deflection and maximum hoop stress from our Autodesk Fusion 360 simulation with theory.
Autodesk Nastran Validation 8 - Beam Guided at One End, Fixed at the Opposite End, Center Loaded
Просмотров 3272 года назад
Autodesk Nastran Validation 8 - Beam Guided at One End, Fixed at the Opposite End, Center Loaded
Autodesk Fusion 360 Validation 8 - Beam Guided at One End, Fixed at the Opposite End, Center Loaded
Просмотров 2082 года назад
Autodesk Fusion 360 Validation 8 - Beam Guided at One End, Fixed at the Opposite End, Center Loaded
Autodesk Inventor Nastran Validation 7 - Toroidal Shell with Uniform Internal Pressure
Просмотров 4443 года назад
Autodesk Inventor Nastran Validation 7 - Toroidal Shell with Uniform Internal Pressure
Autodesk Fusion 360 Validation 7 - Toroidal Shell with Uniform Internal Pressure
Просмотров 1223 года назад
Autodesk Fusion 360 Validation 7 - Toroidal Shell with Uniform Internal Pressure
Autodesk Nastran Validation 6 - Cantilever Beam with Nodal Force at Midspan
Просмотров 3583 года назад
Autodesk Nastran Validation 6 - Cantilever Beam with Nodal Force at Midspan
Autodesk Fusion 360 Validation 6 - Cantilever Beam with Nodal Force
Просмотров 1233 года назад
Autodesk Fusion 360 Validation 6 - Cantilever Beam with Nodal Force
Autodesk Nastran Static Stress Validation 5 - Flat Plate with 3 Edges Simply Supported
Просмотров 2683 года назад
Autodesk Nastran Static Stress Validation 5 - Flat Plate with 3 Edges Simply Supported
Autodesk Fusion 360 Static Stress Validation 5 - Flat Plate with 3 Edges Supported
Просмотров 353 года назад
Autodesk Fusion 360 Static Stress Validation 5 - Flat Plate with 3 Edges Supported
Autodesk Nastran Static Stress Validation 4 - Flat Plate with Pressure
Просмотров 7333 года назад
Autodesk Nastran Static Stress Validation 4 - Flat Plate with Pressure
Autodesk Fusion 360 Static Stress Validation 4 - Flat Plate with Pressure
Просмотров 3613 года назад
Autodesk Fusion 360 Static Stress Validation 4 - Flat Plate with Pressure
Autodesk Nastran Static Stress Validation
Просмотров 4223 года назад
Autodesk Nastran Static Stress Validation
Autodesk Fusion 360 - Static Stress - Validation Model
Просмотров 2493 года назад
Autodesk Fusion 360 - Static Stress - Validation Model
Autodesk Inventor Nastran - Static Stress - Validation Model
Просмотров 1,4 тыс.3 года назад
Autodesk Inventor Nastran - Static Stress - Validation Model
Hi Mike... Thanks for this tutorial. For me it is a very helpful video. Could you please tell me how we can extract the bending and membrane stresses for shell elements in Inventor Nastran?
Thanks so much for your videos. Greetings from Colombia.
Glad you like them!
Is there a way to print out a report showing what the thermal expansion values are, and the locations of the max/min deflections?
Apologies for the late reply - but the answer to your question is yes. (1.) When you generate the report (right mouse click on Analysis in the Model Tree - Generate Report), presuming that you have Min/Max Markers turned on - when the program takes various images for the report, Displacement should be one of those images. The Min/Max markers should display location and value. (2a.) You can get all of the displacement values printed to the *.OUT file. If you double click on the analysis type (e.g. Linear Static) in the Model Tree, this should bring up the Analysis form. The default 'Output Options' pull-down you'll see is set to Plot by default. If you change that setting to Print, it will write all the displacements to the .out file. Note that if you have many nodes in the model, this can make for a very large out file. help.autodesk.com/view/NINCAD/2024/ENU/?guid=GUID-10BFD564-87F7-465B-B3BB-05F61E291DFA (2b.) If there is a smaller region of interest, it might be better to use the XY plot and select an edge of the geometry (for instance) or a few select nodes and then after plotting the values you can export that as a .csv file (which can open in Excel). help.autodesk.com/view/NINCAD/2024/ENU/?guid=GUID-3B982345-7F90-455E-894C-0B20F5D32A09
How to apply temperature and pressure on same time for the storage tank
Thank you for a very informative video. You applied a temperature load on the inside surface, and on the outside surface. What temperatures does NASTRAN apply automatically to the surfaces on which no temperatures are applied? Is it T_REF? Or is it simply 0°C?
Hello Jura! Because it is a steady state linear thermal analysis, the program is finding the thermal distribution after some 'infinite' amount of time, so the initial temperatures of the 'other' nodes does not matter because the lowest and highest temperatures in the model will be dictated by the loads that we did apply to the model and all other nodes will end up somewhere between those extremes. That said, two things to note (1.) if no load of any type is applied to a surface, the surface is treated as an adiabatic surface and (2.) the temperature of the other nodes would matter in a transient thermal analysis where we might want to see how fast something heats up or cools down. If it is a transient thermal analysis, then you would want to make sure that an initial temp is defined... this could be done with the 'initial condition' load with the 'sub type' of temperature - or first running a steady thermal to get the starting distribution for the transient analysis. I'll make sure to get to some transient thermal analysis as an example.
@@mikefiedler2039 Thank you for a clear explanation!
Hi. Can you please let me know the name of the software that you have used in this video to draw a figure of a torus? Thank you.
Hello Zeinab. This geometry was constructed in Autodesk Fusion 360. The Fusion 360 product has cad modeling abilities along with simulation, drawing creation, rendering and more. You can find more information about that product here www.autodesk.com/products/fusion-360/overview?term=1-YEAR&tab=subscription Disclosure: While these videos are done in my leisure to help educate and promote the use of FEA, they are not officially part of Autodesk formal learning content - though I am an Autodesk employee. Thanks for watching!
gracias por la buena explicacion
ᑭᖇOᗰOᔕᗰ
nice tutorial! thanks
You're welcome!
Thanks for this video, very clear explanation!!
You are welcome!
Thanks Mike. I work for a company that makes pressure vessels and heat exchangers. Historically we used to use Abaqus for our stress analysis. But due to budget constraints, we are moving to Inventor Nastran as the only FEA option. Your videos are great help for me in making that shift.
Is there any reason you only applied Z sym only on the bottom of the cylinder instead of both top and bottom? I can see some gradient difference in your displacement plot at 6:41.
Hello Adil Apha - thanks for watching the video! So, the z symmetry constraint (or Tz) constraint is really there just added at one end of the model to keep the model statically stable - but I don't want to over constrain the model. To apply the z constraint at the opposite end would restrict any axial expansion or contraction that might happen in the model due to the loading. When we look at one of the radial directions, we do expect it to be a non-gradient result (e.g. same at the top and bottom)... but right, since I didn't control that growth or contraction, the model does experience about .0015" of axial contraction. So, at the 6:41 mark in the video, what is displayed is total displacement - or a combination of the x, y and z components - and because of that difference in the z results, we get the gradient. Good observation, hopefully that explanation makes sense to you. In short though - ultimately the most important thing is trying to make sure that your constraints match the 'real world' as much as possible when it comes time to perform your analysis... and good to observe how the decisions to apply (or not apply) particular constraints influence those results. Take care!
@@mikefiedler2039 Understood. Thank you for your detailed response.
i''m absolutely beginner thanks you very much for posting this video, this really help me to learn...
You're very welcome!
Excelente!
Thank you for watching!
Thanks Mike.
Certainly! Thank you for watching!
Thanks very much.
I think the result might change if instead of selecting the full face for a fixed constraint and we selected just the lower bottom edge of the bar fixed. One reason why many get different results. Anyway, nice video.
Nice video. Thanks. just a comment. This 5th edition of Roark and Young is one of the hardest editions to find online for purchase. Only 7th and 9th editions are available on amazon.
This is what i was looking for.
Nice video. Thanks for sharing.
excellent video thank you. Newbie to inventor nastran here. is there anyway to constrain axially by defining an axis?
Hello. Thanks for watching! In reply to your question, 2 different ways to possibly approach this; 1. When adding the constraint, note that 'Constraints' is a pull-down menu. If you change it to 'Pin", then you can apply constraints to be able to fix (or not fix) the radial, axial, and tangential directions. Note this must be applied to cylindrical faces. 2. Otherwise, further down the Model Tree, you should see an entry labeled 'Coordinate System'. There you can define other rectangular, cylindrical and spherical local coordinate systems. The newly defined coordinate systems can then be used when applying either constraints or loads on the model. Applying: knowledge.autodesk.com/support/inventor-nastran/learn-explore/caas/CloudHelp/cloudhelp/2019/ENU/NINCAD-UsersGuide/files/GUID-EB94687D-45AE-4A43-9BFF-6B367E4B59A6-htm.html Using the lcs: knowledge.autodesk.com/support/inventor-nastran/troubleshooting/caas/sfdcarticles/sfdcarticles/How-to-visualize-the-coordinate-system-in-Inventor-Nastran.html.
@@mikefiedler2039 Thank you.
1. When I tried doing the pin constraint, the solver came up with the fatal error "FATAL ERROR "E5000: SINGULARITY DETECTED". The model is very similar to that you have in the video.
@@navalfa7291 Constraints are a fairly common source of that issue. So, you indicated that you were using some pin constraints. Imagine you only constrain the tangential direction on a cylinder. If the loading should cause the model, as a whole, to (for example) translate axially, that would lead to it being statically unstable and end with that error. You should try and ensure that all possible directions of motion are accounted for in some way in a linear static stress model. The simple test to see if that is the source of the error would be to just add a fully fixed constraint somewhere on the part, try and run it again and see if that fixes it. If so, then you can remove the fully fixed constraint and try to apply something more appropriate. Material properties are another source of this error message. You should take a look at the material properties and make sure that all have a reasonable modulus of elasticity and Poisson's ration. If you have gravity or any other type of acceleration, make sure you also have an appropriate material density. The help page for this error message is here; knowledge.autodesk.com/support/inventor-nastran/troubleshooting/caas/sfdcarticles/sfdcarticles/FATAL-ERROR-E5000-in-Nastran-Analysis.html#:~:text=If%20the%20problem%20is%20caused,low)%20values%20in%20material%20properties.&text=If%20G3005%20warnings%20occur%20in,or%20using%20a%20finer%20mesh.