Simulating Bolted Assemblies
Learn more about SimuTrain or get started today by purchasing your subscription. They do not measure rotation. This article illustrates how to use APDL commands to refer to an existing Remote Point, and measure translation and rotation at the point. If the remote point interacts with a face that is set to Deformable, an averaged value of face movement is measured. If there is no load on the remote point, movement is measured without affecting the result. The Deformation Probe supports a non-default choice of Remote Points as location for the measurement of deformation.
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If a Remote Point associated surface behavior is set to Deformable, an average deformation of the surface can be measured for the Remote Point without affecting the model:. Note Deformable Behavior in Definition. Users must be aware of the Units employed in solution in reading the translation Results above, and that these rotations have been converted to Degrees.
Input Arguments could pass values to a SET command in the script.
A result that is measured with a Surface created within Construction Geometry can be used to report a result where the Surface cuts across one or more bodies. The surface has to touch elements of the bodies. A Directional Deformation in Z has been measured on the Surface.
This technique does not report the rotation, however. Note that the Average reported above matches the Z movement measured by other techniques in this article. The above use of a Remote Point does not report an average Temperature in a thermal analysis.
A Surface as above will report an average temperature where the Surface cuts across the elements of one or more bodies. Another APDL technique can be used to generate average temperatures for selected faces, and has been described in a previous article. To measure an averaged rotation, a General Body-Ground joint can be attached to the face of interest. The Behavior of the selected face is set to deformable. The following figure illustrates settings and the result:. A finite value here can restrict how much of the surface is included in forming the average.
With either the Remote Point approach, or a General Joint approach, choosing a face with a large number of nodes will increase wavefront during Solve, and will result in a longer solution time.
A finite pinball diameter can restrict how many nodes are involved. Workbench Mechanical supports a Deformation Probe that can scope to a Remote Point to measure movements at a face on a model.
If the associated face is set to Deformable at the Remote Point definition, then an averaged value can be measured on the face without affecting the model. Deformation Probes do not currently support measurement of rotation.Nvidia geforce 940mx best settings
APDL Commands Objects can record the node number of the Remote Point of interest, and in postprocessing can measure translations and rotations of the remote point. When a General Joint is employed for the measurement, not APDL commands are needed, and the units for the Probe results are automatically set.
Get SimuTrain Now! Materials Semiconductors Optical Systems. Local Seminars Webinars. Stay connected: Newsletter.I need to connect different parts for a project, and I noticed that there are 2 options.
One is using the bonded contact region and one is using the fixed joint. Both can be used for surfaces so I am wondering what the exact difference is. I've done a test by connecting two parts and then calculating some modes as I need to do modal analysis and compared the connection methods to see if the result would be the same, but it is not. Bonded : This is the default configuration and applies to all contact regions surfaces, solids, lines, faces, edges.
If contact regions are bonded, then no sliding or separation between faces or edges is allowed. If contact is determined on the mathematical model, any gaps will be closed and any initial penetration will be ignored. Fixed joint can be used instead. The last line indicates that both can be used for similar purpose but that bonded contact region is not supported for Rigid Dynamics.
For solid bodies that share a face and need to be "glued" together, there are ways to achieve that connection that is neither bonded contact nor fixed joint. You can use "Shared Topology" and have the elements on each side of the coincident faces share nodes. The benefit of this is a smaller model. You can get the same effect with Node Merge if each face has mesh controls to force the nodes to line up.
Shared topology does this automatically. Imagine two tubes that are placed end-to-end and the annular faces need to be connected. Say the other end of one tube is a fixed support and the far end of the other tube has a lateral load so the tube is a cantilevered beam and some bending occurs. In the annular ring, the force is transmitted locally all around the face.
Depending on the contact formulation, you can get some penetration of nodes into the target surface. That doesn't happen with the shared topology method.Oc sith lord fanfiction
A fixed joint creates a point at the centroid of the faces, and builds a spider of elements out to all the nodes on each face. All the forces and moments go through that one point. That is one of the benefits of using a joint, you can easily extract those quantities from your model.
But there is no local node-to-node forces transferred around the annular face. The force has to go down the spider, though the point and back out on another spider to get to the other side. There is a danger when creating joints in Mechanical. Never use duplicate on a joint in the Outline to make another joint to use elsewhere in the model because the point that was created for the first joint is used in the new joint, rather that being updated to the location of the new faces.
That means the invisible spiders that are created can go from one of the new faces, all the way over to a point on the other side of your model through a point, and then all the way back. You can imagine that a small tension on the tubes of the new joint will have a result that includes a HUGE moment, and a small force, when it should have a zero moment. This can cause the solver to have convergence difficulties. This kind of mistake cannot happen with bonded contact.
When there is a significant gap between the faces that need to be "glued together", the fixed joint will always work by simply choosing the two faces, but bonded contact may not create any contact elements and the bodies will not be glued. The corrective action is to type in a Pinball radius to make sure that the contact elements are created. You don't need to to that for Fixed Joints.Log In. Thank you for helping keep Eng-Tips Forums free from inappropriate posts.
The Eng-Tips staff will check this out and take appropriate action. Click Here to join Eng-Tips and talk with other members! Already a Member? Join your peers on the Internet's largest technical engineering professional community. It's easy to join and it's free. Register now while it's still free! Already a member? Close this window and log in. Are you an Engineering professional? Join Eng-Tips Forums! Join Us!
By joining you are opting in to receive e-mail. Promoting, selling, recruiting, coursework and thesis posting is forbidden. Students Click Here. Related Projects. Hi All, I'm currently trying to solve an analysis in Ansys The hub is arrested at the bottom by other components of the assembly and I need to apply an axial force and Moment on the other end of the riser.
But, for moment, I've created a remote point exactly on the symmetric plane and with behaviors and results as mentioned below: 1. Remote point with rigid behavior - Moment is being taken early in the analysis at LS-2 itself where I've not applied any moment and as a result, elements are getting distorted and the analysis is being shut down abruptly because of excessive plastic strain exceeding the default value of 0.
Remote point with Deformable behavior : Moment is not being taken 3. Remote point with beam behavior with high Young's modulus : Moment not being taken Is it because of the same surface having different formulations for Tension and Moment loadsteps?
Any kind of help regarding this will be very helpful. Thanks in advance everyone. PS: I've tried the Rigid behavior formulation for Tensile force load step but the problem is that the surface is not moving axially but getting bent. Which is not the behavior I'm looking for. So I chose the Coupled behavior formulation.
It could be a result of applying multiple constraints equations remote force, remote point, Try deactivating loads in addition to setting the value to 0 when they are not active. Either deformable or rigid behaviour should be sufficient. If you have defined a remote point with rigid behaviour, it is applied to every load step, even though there is no load defined using it. It constrains the selected nodes not to move in relation to each other.
Please post some pictures.
I ran a test model and encountered the same issue moment is not shown in reaction moment. Try using either deformable or rigid behaviours for the loads and it should work.Among the many ways parts can be assembled together, bolts are useful when parts need to be disassembled for maintenance or repair. They can also be used to connect parts made of dissimilar materials, when welding is more challenging.
From a FEA standpoint, bolts can be modeled in many different ways, from simple links between parts using constraint equations to fully detailed models of the bolts, potentially including full thread details. Whatever the model one will use, simulating bolted assemblies will usually require a multiple steps analysis to mimic the reality.
The assemblies are first bolted, and then used in their environment with corresponding loads and boundary conditions.
A structural analysis model will let you apply loads in a similar way. Bolt pretensions are applied first, generating stresses and deformations in the model.
Then, once bolts have been locked, additional loads will be applied. What are the challenges you will face in building such a model? What do you need to look at? Well, one of the biggest challenges when dealing with bolts is that you rarely have a single bolt.
In reality, chances are you will have dozens if not hundreds of them. How can you efficiently deal with a high number of bolts? Can you easily setup one bolt and replicate the setup for all other ones?Root android 9 without pc apk
How can you efficiently setup your model to reflect all contacts between bolts and the various connected parts? The video below demonstrates how to efficiently create pretension bolts in a model and how multiple steps analyses can be used to analyze the design of your bolted assembly.
Once the geometry has been imported, contacts will be automatically detected in the assembly. You just have to make sure the contact between your bolts and the connected parts have the appropriate properties, for example frictionless or with a given friction coefficient. A nice idea would be to group your contacts accordingly, so you can identify them later when reusing your model.
Contacts between bolts and connected parts. Then you need to define the pretension on each bolt. The best solution here is to create the loading conditions on a single bolt and then replicate to all other bolts with the same properties. In a few mouse clicks, you will generate the conditions on all bolts in your model. Definition of bolt pretension and automated generation of loads on multiple bolts. As mentioned earlier, your simulation will usually have a minimum of two steps: one to apply the pretension, one to apply other loads while bolts are locked in their constrained state.
The first one mimics the assembly of your product, the second one the real behavior of your product under real loading conditions. Whether you define the bolt pretension through a load or an adjustment, you will likely be interested in looking at reaction forces to make sure all loads have been properly applied.
Here again, automation will save you huge amount of times — define the results you want to look at on one bolt and automate the creation of results on all other bolts. Typical results for a bolted assembly. Contact pressure at the bolt head for pretensioned state and under real loading conditions. Stress induced by bolts and pretension results.
If you are interested in further detailed analysis of your bolts, you may want to include the details of the thread.Log In. Thank you for helping keep Eng-Tips Forums free from inappropriate posts. The Eng-Tips staff will check this out and take appropriate action.
Click Here to join Eng-Tips and talk with other members! Already a Member? Join your peers on the Internet's largest technical engineering professional community. It's easy to join and it's free. Register now while it's still free! Already a member?Bluetooth available devices misc
Close this window and log in. Are you an Engineering professional? Join Eng-Tips Forums! Join Us! By joining you are opting in to receive e-mail. Promoting, selling, recruiting, coursework and thesis posting is forbidden.
Students Click Here. Related Projects. Hello, I am conducting a harmonic response analysis of a shaft. I put point masses for corresponding rotor parts to include mass and inertia effect. I applied "rotational velocity" in the modal analysis and "rotating force" under Harmonic response section.
My problem is, during rotating force configuration, i defined location by giving a remote point. I gave the same remote point for Hit Point selection. However, program gave me an error as "Selected remote point location is different from hit point location".
The truth is they are the same. Do you know what might cause this problem?Learn more about SimuTrain or get started today by purchasing your subscription.
A Point Mass a remote masscan be added to an ANSYS FEA model to include the load due to mass that does not stiffen a structure, but that is important to capturing inertial loads such as those due to gravity, rotation about an axis, or dynamics.
The point mass will load the associated faces. Face behavior can be set to deformable or rigid. It may be of interest to measure the forces on the point mass. A Point Mass can be added to a Workbench model, positioned in space, and associated with chosen surfaces. The surface behavior can be set to Rigid or Deformable. When the Deformable choice is made, the Point Mass will move in an average sense with the associated surfaces, and the surfaces can thermally expand and flex without local constraint.
The associated surfaces should usually be free of constraints and other loads. Advantages of having a Remote Point promotion for a Point Mass include identification of the node located at the Point Mass. Figure 4: Identify the Node at the Point Mass. It is also possible to find out the Real number for the contact elements associated with the Remote Point.
If recorded in a parameter, this could make is possible to identify the contact elements later in other APDL Commands Objects. In the present example, the surface where forces are to be measured is identified by a Named Selection. It should be the same surface as was used for the Point Mass and therefore the Remote Point. An alternative approach could be to identify the Real number of the Remote Point, as mentioned above, in order to find the contact surface in a later Commands Object.
Figure 5: Surface of Interest Identified. Static analysis results in forces and moments on the surfaces associated with a Point Mass, as transferred from the Point Mass.
In Figure 6 below, contents of a postprocessing Commands Object are illustrated. Figure 6: Force on Point Mass. Other attempts to retrieve force on the Point Mass did not succeed, as illustrated in Figure 7 on the right for the Remote Point associated with the Point Mass.
Harmonic analysis results in real and imaginary numbers in the result, which imply amplitude and phase in the response. We would like to examine the amplitude of the force on the Point Mass. The Analysis Settings object did not provide enough control to do this. This is done without actually knowing the phase angle. This frequency was chosen because of the results of a Modal Analysis that preceded the Harmonic Analysis—the frequency is close to a resonant frequency with vertical motion by the top face that is associated with the Point Mass.
There are several Results parameters, mostly presented for user information. In Figure 11 below, a Frequency Response object is used to find the frequency and phase angle at which a maximum Y movement response is found on the selected face.
This is the movement for which the vertical force on the Point Mass has been measured. Frequency Response plots also give insight into movements in a Harmonic Response analysis. Figure Frequency Response Chart for Face. The user must supply the ARG1 parameter the frequency of interest in cycles per second as an Input in the Details of the object:. UY of node at remote mass! Get SimuTrain Now! Materials Semiconductors Optical Systems.
Local Seminars Webinars. Stay connected: Newsletter.Did you know that there are three main ways to apply force and displacement in a structural analysis? What are the different behaviors and how can you add a new load to an analysis you wish to restart?
Read more below:. Deformable — Load is distributed to the nodes of the face weighted by the distance from the remote point. Coupled — The specified degree of freedom solutions are equal across the entire face. All of the above loads are compatible with nonlinear restarts but only tabular data after the desired restart point may be modified and only on a pre-existing load.
This is because the regular and remote loads actually create surface effect elements SURF to implement the load behind the scenes. While this confers several benefits, such as the ability to have overlapping loads on the same face, it is not compatible with nonlinear restarts since adding new elements would change the model too much.
This functionality is not available for direct displacements since a displacement of 0 is a constraint and would invalidate the restart points. Did you find this useful?
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