The company i'm working used to draw their casted parts in Autocad. They added the extra material (before milling) with a dashed contour line. Now we work with Inventor 2010 and the models are all created 'finished'.
Now the situation is that the CNC-programmer is adding this 'given' material in his Gibs-cam application in order to write his program. Due to that the discussion appeared what is best. To add the material in Inventor or in Gibbs. I'm interested to hear some workaround according to this.
However, I have one iLogic routine that is giving me an error whenever I run it. Selecting continue allows it run as expected. Basically, it is to remind designers to set the material type to other than “Default”.
Here is the Materialsddd = 0' deleted parameter materialName = ThisDoc.Document.ComponentDefinition.Material.Name If materialName = "Default" Then MultiValue.List("MName") = iProperties.Materials MName = InputListBox("Select Material", MultiValue.List("MName"), Mname, Title := "Select Type", ListName := "MM List") iProperties.Material = Mname iLogicVb.UpdateWhenDone = True The Parameter MName does exist as a mulitlist parameter.
I am using the keyway generator to place a keyway in a hub and shaft, but the depth of the keyway (and the height of the associated key) is not right.
I am using an 18mm and a 20mm dia shaft, both of which should use a 6mm wide by 6mm high key according to the ISO standard. [URL]
But Inventor gives me a 6mm wide x 4mm high key and the keyways to fit; so if I use a standard 6mm high key in real life it won't fit. There doesn't seem to be any way to change to a custom key height.
Or is Inventor using a different set of standards? It's pretty good at matching standards in other places, for example the gear and fastener generators, so this seems strange to me.
I have created a report from a frame analysis of an arrangement of I-Beam steelwork. I need to check that I have placed the nodes in the right order and this is reflected in the results of the report. I have the parent and child nodes connected at the ends of the beams as shown on the attached screen shot. I'm interested to know if the order in which I have selected the nods makes any difference to the results. There a 3 node connection points at each corner section.
I have purchased the Autodesk Product Design Suite Premium. It comes with the Frame Generator but does not seem to have the Frame Analysis with it. Is that provided in other Suites or should I have it??
I have an 8" OD/5.523" ID steel tube. A 5.5" OD/4.957"ID tube is placed inside. The 8" and 5.5" tubes are placed over a 4.9375"OD shaft. So basically you have a hollow shaft attached to a drive shaft, with a filler tube placed between them to fill the gap. Two 1-1/2" UNC bolts are placed in matching1.531" diameter holes in every component (thru bolted) with a nut. Tightening the nut will tend to flatten the pipes, taking up the clearance between then and creating a contact pressure on the drive shaft. I have having trouble getting all of the contacts correct since the components are not in contact at the beginning of the simulation due to the radial clearances.
Two axial bolt loads of 129,000 lbs will be placed on the tubes. I have used a sliding/no separation contact between the bolt and nut. Then I put a fixed constraint on the bottom face of the nut (not in contact with the tube) and put a 129,000 force on the top of each bolt head to simulate the axial load created by the bolt preload. What type of contact should I use between the tubes that have radial clearance?
I have attached the tubes and drive shaft. The 1-1/2" bolts and nuts (both heavy hex) were found in the library.
I am trying to properly stress test a steel aircraft fuselage. I can easily model the estimated weight of the pilot, copilot, etc as loads on the airframe. However, when it comes to simulating a high-G situation, (a load factor of around 7.5 times the force of gravity), I am not sure what to do. On one hand, I can simply multiply the loads on the airframe by the load factor and see if the frame can take it. In most cases, it performs very poorly, (safety factor less than 1). However, if I model all the loads under normal conditions, (normal pilot weight, etc.), then add a gravity load equal to 7.5 G, the airframe performs well. Yet I am not sure if the loads on the airframe, (such as pilot weight), are being adjusted along with the increased gravitational load.
My question is, what is the best way to accurately simulate real world loading for high-G situations?
I am doing an eigen frequency analysis of a structure in the range of 0 to 1500 Hz. For my structure I am getting about 6 modes as expected.
For the final results I will mass normalize to convert to an energy based on the relative "displacements" However, each of the "displacements" for the 6 eigenfrequencies are the same?
I know this can not be right as it would mean that all have the same energy which is impossible.
I am trying to determine how to properley constrain the assembly below, so that the compression of the rubber gasket will be properly indicated.
Currently I am seeing the deflection of the shelf in the downward direction, but I do not see any indication of stress in the gasket behind.Currently the gasket is "bonded" to the steel tube the screws are bonded to the shelf bracket and the steel tube.
I put in "work axis" at the center line of the shelf bracket and the CL of the gasket, but I can't find a way to constrain to a work axis.The file is too large to upload here...
and it says I don't have enough memory! How can this be? Its not that complicated of an assembly. I have done bigger. I excluded all the part I'm not using and they are all basic plate and tube parts. There are less than 20 parts in the assembly.
I have used a few times 'Stress analysis' before. Today I discovered it is disabled. I applied a software update (SP1, build 222), after which I could run a Stress analysis again. However, Inventor crashed soon, and after restarting it, Stress analysis is disabled again. In 'Add-In Manager' the 'Simulation: Stress analysis' is shown as 'Automatic/Loaded'.
UPDATE: I have unchecked the 'Load Automatically' option for this module, quit Inventor, started it again, loaded the module and now it seems to work. I don't know yet for how long...
UPDATE2: well I could start a Stress analysis, but everything is disabled there, I can not create a simulation for example.
I am trying to run a simulation on a 4 layer part that has two base layers of I-beams, a frame I made in the frame generator (below) and a solid sheet on top. I am having some issues with the FEA side and was curios to see if the frame analysis tool would yield the same results as the stress analysis simulation. For the frame generator I saw 4 times the amount of deflection despite using (what I believe) are similar loading and constraints, however now I am unsure if I can trust to run an FEA simulation with a frame generated component. The frame is made up of 2 inch steel box beam with a 0.25 inch wall thickness. For the frame analysis package, I have applied a pressure that equates to a 70 kN load across four different sections of the frame. Supports have been placed under all four corners, with 1 being fixed and the other 3 free to move. For the FEA simulation, I applied a similar pressure by creating 2 inch wide plates and applying the same pressure at the same four points. There are also 2 inch square pads under the four corners of the frame with one edge of one pad being fixed and the bottom of the pads having a frictionless constraint. There are separation contacts between both the pressure plates on top of the frame and the frame as well as between the pads and the frame.
with the frame generator is that all the segments of the frame are bonded together (under contacts) which makes sense since they are welded together. However when I put a sheet on top of the frame, there are 3 contact points created between each beam on the frame and the sheet (one on the face of the frame that is in contact with the sheet and the other two on the rounds of the frame and the sheet, even though the rounds are not actually in contact with the sheet). Either way, I am seeing deflections of less than 0.1 mm when a 70 kN load is applied which I know is not right and just want to know if using a frame generated component is not possible with an FEA simulation.
We just migrated from Inv 2011 where I had set the letter A as a shortcut for Zoom All. I tried setting it up again and ran into an issue where two commands were tied to it with the other command being Interference Analysis. I can't find interference analysis in the keyboard customization section and am wondering if there is a way to get rid of it's association with the letter A.
I work for a tank building company and we are starting to use Inventor for stress analysis. We have a tank that we are designing that has a tank inside of another tank. The internal tank will be holding product while the outside tank is there to prevent product leakage in the event that the internal tank has a leak. There is piping that is welded to both the inside tank and the outside tank.
So here's my question: We know the radial deflection of the piping on the internal tank due to pressure, but we want to know what the stress is going to be on the external tank shell. Is there a way that I can input the amount of deflection and so that inventor will calculate the stresses involved?
I saw thermal properties in the list of Inventor's materials. However, I didn't find how to make a thermal analysis using Inventor MEF. Is it possible?
So I have an assembly made up of several smaller assemblies and have constrained them in the main assembly but when I run the analysis, the interaction does not seem to exist.
An image has been displayed below, the pin should line up with the holes.
I'm a student working on a team project to build a vehicle and we're required to do a stress analysis to make sure if the vehicle (chassis, supports, etc) can withstand the weight of the driver, etc.
The problem is that the analysis that I did doesn't seem to make any sense at all, like there was no stress between the joints, the frame bent when the applied force was only 5 kg...
Having an assembly, modeled in the frame generator, then with some additional parts (ribs, plates, etc) added to the assembly as parts and constrained with assembly constraints.. which is the best way to do a frame analysis with the frame analysis enviroment for considering the all structure (frame generators parts + the additional enforcing parts) ?
The assembly look like for example, to this (modeled in autocad).
I am using Inventor 2009 professional and I have to run a stress analysis on a beam. I put the constraints and the forces I need and when I hit the calculate button, the results so up, but when I click on the results, nothing appears. I need to run this calculation and do not want to resort to hand calculations.
I'm trying to run a simulation on a part to test it's resistance to explosive forces and pressures. All the tutorials I find on stress analysis seem to be grader toward mechanical parts or tables.
When I go to Environments>Frame Analysis, I used to get a menu for Constraints, Loads and other settings (similar to the Stress Analyisis menu). I don't get that now. I can right-click on an existing simulation and add constraints and loads, but I would really like to get the menu back.
I can go to tools>Customize, Toolbars tab and Frame Analysis Panel is there. I can click Show and it will show the panel but it stays up all the time. Not what I want.
I have tried resetting the menu, repair installing Inventor and Reinstalling Inventor, but still not joy. How do I get this back to the original setting so that it comes up when I select Frame Analysis?
I'm trying to create a report on a stress analysis I've made. Reading the report I don't find any result on safetyfactor. When I was browsing the forum I found a thread concerning safety factor and a report file attached. My report is missing some of the information that I found in this attached report (such as "result summary".
