AutoCAD Inventor :: Adding Right Constraint In Stress Analysis (bolted Connection)
Jul 27, 2012
adding constraints to assemblies, in particular which choice of force constraint to add when using a bolted connection.
My scenario - I have a steel tube bolted to a plate which I have performed a stress analysis on. I have opted for the pin constraint where the tube is bolted to the plate and selected the bolt this option to add the constraints. This to me would seem like the best choice as the bolt is held by this constraint.
Autodesk Inventor Professional 2013 SP2 64-Bit Edition
Windows 7 HP Z400, Intel Xeon W3550 3.07GHz
12.0GB RAM, ATI FirePro V4800 (FireGL)
Does inventor take into account threads? I want to do a pull test on BSP thread connection but the surfaces between the threads are shown as "bonded" so I gues that the stress analysis will treat it as one part glued together.
I've been doing a lot of work with the Stress Analysis recently, and I have wondered if a certain feature exits. When I am interpreting the results of a simulation, I'll use the probe to find out the stress in certain areas. The problem is that I can't be certain that I've picked the point of highest stress in a certain area. I know that I can find the highest overall stress, but it's hit or miss finding the 'highest local stress' as I've come to call it. I need to be able to prove that a certain member's stress is below the allowable stress, and I can't be certain of the member's highest stress unless y'all know of some way.
I am running Autodesk Inventor Professional 2014, 64-bit.
I've copied Standard CC libraries to read/write libraries and modified the tables. Mostly fasteners. I've prefixed the family name and family description with our company name. When I "place from content center", it's easy to see our content because the families are prefixed with our company name. However, when I use bolted connection, some of the families do not show our family name as a prefix like "place from content center" does. People constantly pick the wrong fasteners. They select fasteners without our Item number, etc. Then, they need to delete the fastener and try again. I can't seem to get bolted connection to show some fasteners with the company name prefix like Place from CC does. However, some families do show it.
Is it possible to break my bolted connection, so that i can change the information given by inventor in the BOM? Its always grayed out and i can`t seems to find a way to make it "ungrayed".
I could change it directly on the .idw but me and my project leader would like to not go on that road. Our teams are seperated in to two. Ones in charge of modeling & the other is in charge of the presentation. We would like to give, as much as possible, not to much leeway on those in charge of the presentation.
I have a simple bolted connection (bolt, nut and washer) and have tried to pattern this to make a toal of 4 bolted connections in a linear pattern. The preview looks fine however when I hit apply the patterned components disappear. I'm not sure why this is, I am using Inventor 2013 64-Bit SP 1.1
Autodesk Inventor Professional 2013 SP2 64-Bit Edition Windows 7 HP Z400, Intel Xeon W3550 3.07GHz 12.0GB RAM, ATI FirePro V4800 (FireGL)
I installed a bolted connection into my assembly and realized I chose the wrong length. I simply want to delete the connection and start over but there is no option to delete.Ctrl-Z will not let me back out of the connection either.
I am trying to assembly some party, when after i do the bolted connection and select the fastener, after i choose him i cant select the length, he do this automatically. and because of that my fastener come out of my part.
Where can i change the length of the bolt? i use inventor 2012.
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 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 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'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...
I`m joining pipes together using the nut/bolt/washer method using constraints in assembly then using pattern feature.I`ve not used the bolted connection generator before so i am looking for some feedback on whether this is a better method to use.Is there any advantage to using the bolted connection generator over the placement of nuts/bolts/washer with constraints and then using pattern feature?
I've lost my Bolted Connection Templates... you know, the pre-defined bolt-washer-nut selections available for re-use at the bottom of the Bolted Connection dialoge box.
Did I lose or over-write a file? What file do my Bolted Connection Templates live in?
Having trouble bolting through a beam onto a tappered face of a channel. In RL a tapered washer would be used, though they exist in Content Centre it doesnt work with the application.
I have a problem with the Bolted Connection tool in inventor. When I use it to place fasteners in my assembly everything works fine, i can select the material I want, etc... The problem is whenever I need to change something in it, the fasteners changes to the first one in the list that appears when you click the ... button, which means that I always get the wrong fasteners. The workaround we found was to click the ... button again for all the fasterners, and this has to be done in the right order (start to end) otherwise I will get again the wrong fasteners and to select the fasteners again.
One more thing, I'd like to know if it is possible to have a more user-friendly way to change the bolts in bolted connection. I would like it to be like when you import a component from the content center, with that dialog box. As for now, I have to choose the bolts with their part number while when I import them with the content center, I have all set the key values.
One of my parts had "Invalid origin/axis" problems and I got all my visible aketches fixed. But I have what I call "ghost" sketches left from bolted connection updates, erasures etc. I can get rid of the visible points but cannot access the sketches to erase them.
The red + sign showing irritates me and I want rid of it.
I have attached the file, 2014 version, some of the adaptive features may not come thru or they may work better on another computer, who would know.
Adding of a single bolted connection using design accelerator is painfully slow, each command is taking up to 3 minutes? It's in Inventor 2012 by the way
Autodesk Inventor Professional 2013 SP2 64-Bit Edition Windows 7 HP Z400, Intel Xeon W3550 3.07GHz 12.0GB RAM, ATI FirePro V4800 (FireGL)
It doesn't change to match the diameter of the hole (which is a hole feature in both parts) and it doesn't bring up a list of fasteners. Everything is still highlighted in the assembly. It just won't do anything with it.
Infrastructure DSP '14 / Product DSP '14 / Vault Professional 2014 Dell Precision T1650 Windows 7 Professional SP1 64-bit Intel E3-1270 V2 3.5GHz / 32G RAM Nvidia Quadro 2000, Driver 331.82 Space Navigator, Driver Version 6.17.7
I am using the calculation tab in the bolted connection generator. Is the maximal tangent force (Ft) the total force of plates in shear or per fastener? It appears to be the total force because changing the number of bolts changes the results.
I have been running different configurations due to a failure in a test cell and the numbers don’t seem correct. The calculation indicates that the fastener would fail at a much lower force than it actually is.
I having a stroke or something. I could swear I have used a work plane for a termination plane before in a Bolted Connection. Tried it just now and can't pick the work plane.
Inventor Pro 2013 (PDS Ultimate) Vault Pro 2013 Windows 7 64 Xeon 2.4 Ghz 12GB
When I use the DA to generate a bolted joint that utilizes flat head cap screws (English, 82 deg), the countersunk hole is not large enough and it leaves the heads sticking out slightly proud of the surface. Most of the time when I use FHCS fasteners, the heads must be below flush.
I went into the Clearance.xls file and increased the diameter values for the 82 degree holes. However, it doesn't appear that the DA actually pulls its hole data from this file. I saved the XLS file, closed it, closed IV, retarted IV, deleted the old DA assembly and started over. And I still got the same undersized hole.
However, I did verify that if I just place a HOLE on that point and set the hole as countersunk and clearance for that size of fastener, it will use the hole size that I specified in Clearance.xls.
Bolted connection, clevis pin and bearing are all not working for me. I can go through the steps of selecting the start plane and then the circular reference and the termination point. That is all successful but the bolt doesn't appear, whether I use a clevis pin or a bearing, I get the same result.
Working with sheet metal or FrameMaker all work fine. My content center shows all the bolts, clevis pins and bearings. The content center seems to be working fine. I'm using inventor 2011.
I'm trying to bolt a solid body (Honda GX160 engine) onto a piece of angle iron (from frame generator). Starting with a point on a plane on the engine, the Bolted Connection Generator will not let me select a termination plane on the angle iron.
IV Pro 2011 64bit SP2; Win7 Ultimate SP1 ASUS MB Intel i5-3450 @ 3.10 GHz, 8GB RAM ATI AMD Radeon HD 6600 Series, 1GB RAM
