Autodesk Inventor Simulation 2009 Getting Started Part No.
© 2008 Autodesk, Inc. All Rights Reserved. Except as otherwise permitted by Autodesk, Inc., this publication, or parts thereof, may not be reproduced in any form, by any method, for any purpose. Certain materials included in this publication are reprinted with the permission of the copyright holder. Trademarks The following are registered trademarks or trademarks of Autodesk, Inc., in the USA and other countries: 3DEC (design/logo), 3December, 3December.
Contents Stress Chapter 1 Analysis . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 Get Started With Stress Analysis . . . . . . . . . . . . . . . . . . 3 About Autodesk Inventor Simulation . . . . . . . . . . . . . . . . . . . 3 Learning Autodesk Inventor Simulation . . . . . . . . . . . . . . . . . . 3 Using Help . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4 Using Stress Analysis Tools . . . . . . . . . . . . . . . . . . . . . . . . .
Setting Parameters . . . . . . . Feature Suppression Tracking . Setting Solution Options . . . Obtaining Solutions . . . . . . Running Modal Analysis . . . . . . Chapter 3 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 20 . 21 . 21 . 23 . 23 View Results . . . . . . . . . . . . . . . . . . . . . . . . . . . . 25 Using Results Visualization . . . . . .
Chapter 7 Get Started with Simulation . . . . . . . . . . . . . . . . . . . 45 About Autodesk Inventor Simulation . . . Learning Autodesk Inventor Simulation . Using Help . . . . . . . . . . . . . . . . . Understanding Simulation Tools . . . . . Simulation Assumptions . . . . . . . . . Interpreting Simulation Results . . . . . Relative Parameters . . . . . . . . . Coherent Masses and Inertia . . . . Continuity of Laws . . . . . . . . . Chapter 8 . . . . . . . . . . . . . . . . . . . . . . . . . . . .
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Stress Analysis Part 1 of this manual presents the getting started information for Stress Analysis in the Autodesk® Inventor™ Simulation software. This add-on to the Autodesk Inventor part and sheet metal environments provides the capability to analyze the stress and frequency responses of mechanical part designs.
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Get Started With Stress Analysis 1 Autodesk® Inventor™ Simulation software provides a combination of industry-specific tools that extend the capabilities of Autodesk Inventor for completing complex machinery and other product designs. Stress Analysis in Autodesk Inventor Simulation is an add-on to the Autodesk Inventor part and sheet metal environments. It provides the capability to analyze the stress and frequency responses of mechanical part designs.
documentation and tutorials, and complete the exercises in the Autodesk Inventor Simulation Getting Started manual. At a minimum, we recommend that you understand how to: ■ Use the assembly, part modeling, and sketch environments and browsers. ■ Edit a component in place. ■ Create, constrain, and manipulate work points and work features. ■ Set color styles. Be more productive with Autodesk® software.
Using Stress Analysis Tools Autodesk Inventor Simulation Stress Analysis provides tools for determining structural design performance directly on your Autodesk Inventor Simulation model. Autodesk Inventor Simulation Stress Analysis includes tools to place loads and constraints on a part and calculate the resulting stress, deformation, safety factor, and resonant frequency modes. Enter the stress analysis environment in Autodesk Inventor Simulation with an active part.
■ Apply a force, pressure, bearing, moment, or body load to vertices, faces, or edges of the part, or apply a motion load directly to a part. ■ Apply fixed or non-zero displacement constraints to the model. ■ Evaluate the impact of multiple parametric design changes. ■ View the analysis results in terms of equivalent stress, minimum and maximum principal stresses, deformation, safety factor, or resonant frequency modes.
evaluating vibration effects, geometry plays a critical role in the resonant frequency of a part. Avoiding or, in some cases, targeting critical resonant frequencies literally is the difference between part failure and expected part performance. For any analysis, detailed or fundamental, it is vital to keep in mind the nature of approximations, study the results, and test the final design. Proper use of stress analysis greatly reduces the number of physical tests required.
The total deformation is assumed to be small in comparison to the part thickness. For example, if studying the deflection of a beam, the calculated displacement must be less than the minimum cross-section of the beam. The results are temperature-independent. The temperature is assumed not to affect the material properties. The CAD representation of the physical model is broken down into small pieces (think of a 3D puzzle). This process is called meshing.
Here, the same part is broken into small blocks (meshed into elements), each with well-defined behaviors capable of being summed (solved) and easily interpreted (post-processed). For sheet metal, a special element type is used. It is assumed that the model is thin in one direction relative to the size of the other dimensions. The model has identical topologies on the top and bottom and has only one topology through the thickness of the model.
than expected, evaluate the analysis conditions and determine what is causing the discrepancy. Equivalent Stress Three-dimensional stresses and strains build up in many directions. A common way to express these multidirectional stresses is to summarize them into an Equivalent stress, also known as the von-Mises stress. A three-dimensional solid has six stress components.
A factor of safety can be calculated as the ratio of the maximum allowable stress to the equivalent stress (von-Mises) and must be over 1 for the design to be acceptable. (Less than 1 means there is some permanent deformation.) Factor of safety results immediately points out areas of potential yield, where equivalent stress results always show red in the highest area of stress, regardless of how high or low the value.
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Analyze Models 2 Once your model is defined, define the loads and constraints for the condition you want to test, and then perform an analysis of the model. Use the stress analysis environment to prepare your model for analysis, and then run the analysis. This chapter explains how to define loads, constraints, and parameters, and run your analysis. Working in the Stress Analysis Environment Use the stress analysis environment to analyze your part design and evaluate different options quickly.
Loads and constraints are listed under Loads & Constraints in the browser. If you right-click a load or constraint in the browser, you can: ■ Edit the item. The dialog box for that item opens so that you can make changes. ■ Delete the item. To rename an item in the browser, click it, enter a new name, and then press ENTER. Running Stress Analysis Once you build or load a part, you can run an analysis to evaluate it for its intended use.
Workflow: Perform a typical analysis 1 Enter the stress analysis environment. 2 Verify that the material used for the part is suitable, or select one. 3 On the Stress Analysis panel bar, select the type of load to apply. The choices are Force, Pressure, Bearing Load, Moment, Body Load, Motion load (for a part exported from Dynamic Simulation), or Fixed Constraint. 4 On the model, select the faces, edges, or vertices where you want to apply the load.
You can cancel this dialog box and continue setting up your stress analysis. However, when you attempt a stress analysis update, this dialog box is displayed so you can select a valid material before running the analysis. If the yield strength or density are zero, you cannot perform an analysis. Once you select a suitable material, click OK. Applying Loads The first step in preparing your model for analysis is applying one or more loads to the model.
After you select Force, you define the force on the Force dialog box. 2 Click faces, edges, or vertices on the part to select them. Use CTRL-click to remove a feature from the selection set. Once you select an initial feature, your selection is limited to features of the same type (only faces, only edges, only vertices). The location arrow turns white. 3 Click the direction arrow to set the direction of the force. You can set the direction normal to a face or work plane, or along an edge or work axis.
When the force location is a single face, the direction is automatically set to the normal of the face, with the force pointing to the outside of the part. 4 To reverse the direction of the force, click the Flip Direction button. 5 Enter the magnitude of the force. 6 To specify the force components, click the More button to expand the dialog box, and then select the check box for Use Components. 7 Enter either a numerical force value or an equation using defined parameters.
This table summarizes information about each load type: Load Load-Specific Information Force Apply a force to a set of faces, edges, or vertices. When the force location is a face, the direction is automatically set to the normal of the face, with the force pointing to the inside of the part. Define the direction planar faces, straight edges, and axes. Pressure Pressure is uniform and acts normal to the surface at all locations on the surface. Apply pressure only to faces.
3 Click the More button to specify a fixed displacement for the constraint, if needed. Check Use Components, and then check the box next to the global axis label (X, Y, or Z) along which the displacement occurs. You can use parameters and negative values. Use Components to specify a non-zero displacement that can be used as a load. 4 Click OK.
You can define and edit parameters at any time, either during part modeling, analysis setup, or post-processing. If you change the parameters associated with a load or constraint after a solution is obtained, the Update command is enabled so you can run a new solution. You cannot delete the system-generated parameters, although they are deleted automatically if their associated loads or constraints are deleted. You also cannot delete parameters that are currently used by a system-generated parameter.
Setting Analysis Type Before starting your solution, on the Settings dialog box, Analysis Type, select Stress Analysis, Modal Analysis (to perform resonant frequency analysis) or Both (to run a stress analysis and a prestressed modal analysis of your part). Setting Mesh Control There are two meshing model types: standard solid model and optimized thin model. For a part, the default is standard solid model. It can be meshed in all X, Y, and Z directions.
model. You can see the mesh that to use at a particular setting by clicking Preview Mesh. Select the Results Convergence check box to allow Autodesk Inventor Simulation to improve the mesh adaptively. Multi-Step Motion Simulates the position for a part applied motion load from Dynamic Simulation in an assembly. Move Active Part Moves the active part and fixes other non-active parts with different time steps. Move Assembly Fixes the active part and moves other non-active parts.
Workflow: Run a modal analysis 1 Enter the stress analysis environment. 2 Verify that the material used for the part is suitable, or select one. 3 Apply any loads (optional). 4 Apply the necessary constraints (optional). 5 Before starting the solution, on the Settings dialog box, Analysis Type section, select Modal Analysis. Selecting Both runs a stress analysis and a modal analysis of your part. Selecting a modal analysis with a load applied produces a prestressed modal solution. 6 Click OK.
View Results 3 After analyzing your model under the stress analysis conditions that you defined, you can visually observe the results of the solution. This chapter describes the how to interpret the visual results of your stress analyses. Using Results Visualization Use results visualization to see how your part responds to the loads and constraints you apply to it. You can visualize the magnitude of the stresses that occur throughout the part, the deformation of the part, and the stress safety factor.
To view the different results sets, double-click them in the browser. While viewing the results, you can: ■ Change the color bar to emphasize the stress levels that are of concern. ■ Compare the results to the undeformed geometry. ■ View the mesh used for the solution. Use the normal view controls to manipulate the model for a 3-dimensional view of the results. To change any model parameters, return to part modeling, and then return to stress analysis and update the solution.
Edit the color bar 1 Click Color Bar on the Stress Analysis panel bar. By default, the maximum and minimum values shown on the color bar are the maximum and minimum result values from the solution. You can edit the extreme maximum and minimum values, and the values at the edges of the bands. 2 To edit the maximum and minimum critical threshold values, click the Automatic check box to clear the selection, and then edit the values in the text box. Click Apply to complete the change.
Reading Stress Analysis Results When the analysis is complete, you see the results of your solution. If you did a stress analysis or specified that both types of analyses to do, you initially see the equivalent stress results set displayed. If your initial analysis is a resonant frequency analysis (without a stress analysis), you see the results set for the first mode. To view a different results set, double-click that results set in the browser pane.
Minimum Principal Stress The minimum principal stress acts normal to the plane in which shear stress is zero. It helps you understand the maximum compressive stress induced in the part due to the loading conditions. Deformation The deformation results show you the deformed shape of your model after the solution. The color contours show you the magnitude of deformation from the original shape. The color contours correspond to the values defined by the color bar.
Setting Results Display Options While viewing your results, you can use the following commands located on the Stress Analysis Standard toolbar to modify the features of the results display for your model. Command Used to Maximum Turns on and off the display of the point of maximum result in the mode. Minimum Turns on and off the display of the point of minimum result in the model. Boundary Condition Turns on or off the display of the load symbols on the part.
Revise Models and Stress Analyses 4 After you run a solution for your model, you can evaluate how changes to the model or analysis conditions will affect the results of the solution. This chapter explains how to change solution conditions on the part and rerun the solution. Changing Model Geometry After you run an analysis on your model, you can change the design of your model. Rerun the analysis to see the effects of the changes.
4 In the browser, right-click a sketch for the feature that you want to edit. Click Visibility to make the sketch visible on the model. 5 Double-click the dimension that you want to change, enter the new value in the text box, and then click the green check mark. The sketch updates. 6 Click Applications ➤ Stress Analysis. 7 On the Standard toolbar, click Stress Analysis Update.
2 Click the location arrow on the left side of the dialog box to enable feature picking. You are initially limited to selecting the same type of feature (face, edge, or vertex) that is currently used for the load or constraint. To remove any of the current features, control-click them. If you remove all of the current features, your new selections can be of any type. 3 Click the white Direction arrow to change the direction of the load. 4 Click the Flip Direction button to reverse the direction, if needed.
The preview mesh is shown on the undeformed shaded view of your part. Change the analysis type 1 On the Stress Analysis panel bar, click Stress Analysis Settings. 2 On the Settings dialog box, Analysis Type menu, select the new analysis type. If you choose Stress Analysis or Modal Analysis, only the results sets for the selected analysis type are displayed in the browser. Any previously obtained results sets are removed.
Generate Reports 5 Once you run an analysis on a part, you can generate a report that provides you with a written record of the analysis environment and results. This chapter tells you how to generate a report for an analysis and interpret the report, and how to save and distribute the report. Running Reports After you run a stress analysis on a part, you can save the details of that analysis for future reference.
Summary The summary contains an overview of the files used for the analysis and the analysis conditions and results. Introduction The introduction describes the contents of the report and how to use them in interpreting your analysis. Scenario The scenario gives details about the various analysis conditions.
■ Safety factor ■ Frequency response results Appendices Appendices include labeled scenario figures, which show the contours for the different results sets. The sets include equivalent stress, maximum and minimum principal stresses, deformation, safety factor, and mode shapes Saving and Distributing Reports The report is generated as a set of files to view in a Web browser. It includes the main HTML page, style sheets, generated figures, and other files listed at the end of the report.
Distributing Reports To make the report available from a Web site, move all the files associated with the report to your Web site. Distribute a URL that points to the main page of the report, the first file listed in the table.
Manage Stress Analysis Files 6 Running a stress analysis in Autodesk® Inventor™ Simulation creates a separate file that contains the stress analysis information. In addition, the part file is modified to indicate the presence of a stress file and the name of the file. This chapter explains how the files are interdependent, and what to do if the files become separated.
in a separate file. The stress analysis file has the same name as your part file, but uses the extension .ipa. By default, the .ipa file is stored in the same folder as the .ipt file. The _structure.rst (for stress analysis) and the _modal.rst (for modal analysis) files, used to export to ANSYS, are generated after you save. If you select both, the _strucure.esave and _structure.db files, used to export to ANSYS, are also generated and stored in a subfolder like the .ipt file.
conditions. There is a possibility that errors can occur when you try to reassociate the files. Copying Geometry Files You can create a copy of an .ipt file using the Save Copy As command or your operating system file copy command. The copy of the .ipt file still references the original .ipa file. Resolving File Link Failures In some cases, the .ipa file might fail to resolve when you try to perform an analysis of the part. For example, you rename or move the .ipa file, or a vendor receives a copy of an .
Creating New Analysis Files To create an .ipa file, click the Stress Analysis Update button on the standard toolbar and save it. Inventor attempts to create an .ipa file in the default location using the default name. If a file exists using this name and location, Inventor checks the .ipa file to see if it points to the active .ipt file. If it does, the new .ipa file replaces the old one. When you create a file, the new .ipa file has boundary conditions that match the conditions stored in the .ipt file.
Simulation Part 2 of this manual presents the getting started information for Autodesk® Inventor™ Simulation. This application environment provides tools to predict dynamic performance and peak stresses before building prototypes.
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Get Started with Simulation 7 About Autodesk Inventor Simulation Autodesk®Inventor™ Simulation provides tools to simulate and analyze the dynamic characteristics of an assembly in motion under various load conditions. You can also export load conditions at any motion state to Stress Analysis in Autodesk Inventor Simulation to see how parts respond from a structural point of view to dynamic loads at any point in the range of motion of the assembly.
■ Calculate the force required to keep a dynamic simulation in static equilibrium. ■ Convert assembly constraints to motion joints. ■ Use friction, damping, stiffness, and elasticity as functions of time when defining joints. ■ Use dynamic part motion interactively to apply dynamic force to the jointed simulation. ■ Use Inventor Studio to output realistic or illustrative video of your simulation.
■ In any dialog box, click the ? icon. Understanding Simulation Tools Large and complex moving assemblies coupled with hundreds of articulated moving parts can be simulated. Autodesk Inventor Simulation Simulation provides: ■ Interactive, simultaneous, and associative visualization of 3D animations with trajectories; velocity, acceleration, and force vectors; and deformable springs. ■ Graphic generation tool for representing and post-processing the simulation output data.
the motion of a child part according to a parent part through the degree of freedom (DOF) of the joint that links them. As a result, select the initial velocity of a degree of freedom carefully. Coherent Masses and Inertia Ensure that the mechanism is well-conditioned. For example, the mass and inertia of the mechanism should be in the same order of magnitude. The most common error is a bad definition of density or volume of the CAD parts.
Simulate Motion 8 With the dynamic simulation or the assembly environment, the intent is to build a functional mechanism. Dynamic simulation adds to that functional mechanism the dynamic, real-world influences of various kinds of loads to create a true kinematic chain. Understanding Degrees of Freedom Though both have to do with creating mechanisms, there are some critical differences between the dynamic simulation and the assembly environment.
3 To see how the assembly moves, drag the door. As you work through the following exercises, save this assembly periodically. Converting Assembly Constraints Notice that the assembly moves just as it did in the assembly environment. It seems to contradict preceding explanations, however, the motion you see is borrowed from the assembly environment. Even though you are in Autodesk Inventor Simulation Simulation, you are not yet running a simulation.
The Dynamic Simulation browser turns gray and the status slider on the simulation panel moves, indicating that a simulation is running. Since we have not created any joints (and have not specified any driving forces) the assembly is grounded and does not move. 3 If the status slider is still moving, click the Stop button. Even though the simulation is not running, the simulation mode is still active. 4 Attempt to drag the Door component. It does not move.
6 On the Dynamic Simulation Settings dialog box, remove the check mark next to Automatically Convert Constraints to Standard Joints. NOTE Selecting this option deletes all joints already in the assembly. 7 Click OK. Convert constraints 1 On the Dynamic Simulation panel bar, click Convert Assembly Constraints.
Axial constraint between the hinge axes Face-to-face constraint between hinge top and bottom flat faces 4 Select the check box next to Mate1: (door:1, pillar:1). It is the axial constraint.
Notice that the joint type (Cylindrical) is listed in the Joint field and the animation switches to the Cylindrical Joint animation. Autodesk Inventor Simulation Simulation automatically selects the appropriate joint needed for the constraint conversion. 5 Remove the check mark next to Mate:1 (door:1, pillar:1), and then select the check box next to Mate2: (door:1, pillar:1) (the face-to-face constraint). Taken by itself, the face-to-face constraint converts to a planar joint.
5 Click OK. 6 Drag and position the door approximately, as shown.
Creating Simulations The Simulation Panel contains many fields including: 1 Final Time 2 Images 3 Filter 4 Simulation Time 5 Percent of Realized Simulation 6 Real Time of Computation Simulation Panel Final Time field Controls the total time available for simulation. Images field Controls the number of image frames available for a simulation. Filter field Controls the frame display step. If the value is set to 1, all frames play. If the value is set to 5, every fifth frame displays, and so on.
TIP You can click the Screen Refresh button to turn off screen refresh during the simulation. The simulation runs, but there is no graphic representation. Before you run the simulation, increase the simulation Final Time value. Run a simulation 1 On the Simulation Panel, in the Final Time field, enter 10 s. 2 Click Run on the Simulation Panel. The Door component moves, with acceleration and deceleration in response to the force of gravity and the inertia of the part.
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Construct Moving Assemblies 9 To simulate the dynamic motion in an assembly, define mechanical joints between the parts. This chapter provides basic workflows for constructing joints. Creating Rigid Bodies In some cases, it may be appropriate that certain parts move as a rigid body and a joint is not required. As far as the movement of these parts is concerned, the welded body functions like a subassembly moving in a constraint chain within a parent assembly.
Adding Joints Permanent joints are the most commonly used joints and are based of different combinations of rotating and translating degrees of freedom. 1 Click the Convert Assembly Constraints tool. 2 Select the Pillar part (2). 3 Select the Link part (3). 4 Select the check box next to both constraints, and then click Apply. 5 Select the Link part (5). 6 Select the Jack Body (6). 7 Select the check boxes next to the mate constraints, and then click OK.
8 Click the Insert Joint tool. The drop-down menu in the top portion of the Insert Joint dialog box lists the various kinds of available joints. The lower portion provides selection tools appropriate to the selected joint type. The Revolution joint is specified by default and the revolution animation plays in a continuous loop. 9 Select Cylindrical from the joint menu.
2 In the graphics window, right-click and select Continue. It enables the selection tools in the Component 2 field. 3 Select the cylindrical surface of the jack stem part (3). In this example, it is not necessary to specify the origins and X-axes. However, it is necessary that the Z-axes on the two parts align and point in the same direction. For most joint types, the Z-axes of the two selections must align and point in the same direction.
that its X, Y, Z-axes are derived from the selected geometry and have nothing to do with the part or assembly coordinate systems. Another difference is that the joint triad uses shapes rather than color to differentiate the axes. The X vector is indicated with a single arrow head. The Y vector uses a double arrow. The Z vector uses a triple arrow. NOTE It is not necessary to specify the X-axis, unless a specific X-axis is needed for a particular action in the Output Grapher.
7 Click OK. Return to the default isometric view. 8 Drag and position the door approximately, as shown. 9 Click Run on the Simulation Panel. The parts move as a unified mechanism. 10 If the simulation is still running, click the Stop button. 11 Click the Activate construction mode button. Next, you use a contact joint between the door and pillar parts to stop the door when it reaches the tab stop. Insert a contact joint 1 Click the Insert Joint tool, and then select 2D Contact joint.
3 Select the point on the tab stop. 4 Click OK. The vector for this joint must be inverted.
Invert a vector 1 In the browser, right-click 2D Contact joint (door:1, pillar:1), and then select Properties. 2 Click the Invert normal button. 3 Click OK. 4 Return to the isometric view, change the value for Images to 4000, and then click Play on the Simulation Panel. The door contacts the tab stop. 5 Click the Stop button. 6 Click the Activate construction mode button. In reality, the swing of the door is not controlled by gravity, but is positively controlled by some device or mechanism.
6 Right click and select Continue. 7 Rotate the model, and then select the face of the jack stem.
8 Click OK. The spring is created. By default, the spring is active. Define the spring 1 Under the Force Joints node, right-click Spring/Damper/Jack, and then select Properties.
2 On the Spring/Damper/Jack Properties dialog box, enter 1 N/mm in the Stiffness field. 3 Expand the dialog box. Select Spring Damper from the Type menu. 4 Click OK. 5 Return to isometric view. 6 Click Run on the Simulation panel. The spring forces the door against the tab stop. The inertia of the door and the resistance of the spring create a rebounding cycle. The resistance of the spring gradually overcomes the inertia of the door.
2 Click the Force tool. 3 Select the vertex on the door. 4 Select the edge, for the force direction. 5 The direction indicator should point away from the tab stop on the pillar. On the Force dialog box, click the Flip Direction button to flip the vector. 6 Enter 10-N in the Magnitude field and click OK. 7 Return to isometric view. 8 Drag the door until it rests near or against the tab stop. 9 Run the simulation. The force overcomes the spring and holds the gate open.
10 Return to Construction Mode. The force is a constant value and unrelenting. As the dynamic, counteracting influences of the force, part inertia, spring damping, and spring tension cancel each other, the mechanism settles into a state of static equilibrium. Notice that even though the angle of the edge we used to specify the force vector changes with respect to the mechanism, the vector remains constant. In this section, you add torque damping to one of the joints.
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10 Simulation Tools This chapter tells you how to vary the joint torque using the Input Grapher, how to analyze a simulation using the Output Grapher, and how to export a load to Stress Analysis in Autodesk®Inventor™ Simulation. Input Grapher Like the force, the damping value is also constant. You can change the damping value to a variable. 1 Right-click Revolution:1 (door:1, pillar:1), and then select Properties. 2 Click the DOF 1 (R) tab. 3 Click the Edit Joint Torque button.
2 Double-click the line near the 0.75 value to add another datum point. The four datum points define three sectors. Each sector represents the condition of the damping value. We will move the datum points to plot changes in velocity to create variable damping. 3 Select the first sector. 4 Ensure the X1 and Y1 fields in the Starting Point section are set to 0. 5 In the X2 field of the Ending Point section, enter 0.5 s. It is the ending time value for the selected sector. 6 Enter 70 N mm in the Y2 field.
8 In the X2 field of the Ending Point section, enter 1.1 s. 9 Enter 70 N mm in the Y2 field. Notice that the values in the Starting Point section are inherited from the Ending Point section of the preceding sector: the ending point for a preceding sector is the starting point for the following sector. 10 Select the third sector. 11 In the X2 field of the Ending Point section, enter 2.2s. 12 Enter 0 N mm in the Y2 field. Press the Tab key to exit the field and update the graph.
With this plot, the torque ramps up over approximately 0.50 second, remains constant for 0.60 second, and then ramps down. 13 Click OK, and then click OK on the Joint Properties dialog box. 14 Run the simulation. Though it may not be visually perceptible, the variable damping modifies the motion of the gate. 15 Return to Construction mode.
Add torque to the joint between the pillar and link parts. 9 Right-click Revolution (pillar:1, link:1), and then select Properties. 10 Click the DOF 1 (R) tab. 11 Click the Edit Joint Torque button. 12 On the Edit Joint Torque dialog box, select the Enable joint torque check box. 13 In the Damping field, enter 50 N mm s/deg. 14 Click OK. Output grapher 1 Click the Output Grapher tool. 2 In the Output Grapher browser, expand Standard Joints, and expand Revolution:2 (pillar:1, link:1).
4 On the dialog box, click OK. Select faces 1 On the FEA Load-Bearing Faces Selection dialog box, click link:1. 2 Click Revolution (pillar:1, link:1). 3 In the graphics window, on the link part, select the two cylinder faces of the corresponding revolution joint. 4 On the dialog box, click Revolution (link:1, jack body:1). 5 In the graphics window, on the link part, select the cylinder face of this revolution joint. 6 On the dialog box, click OK. Select time steps 1 Run a simulation.
Index continuity of laws 48 contour colors 28 A analyses 7–9, 11, 14, 22–23, 25, 28, 31, 34–35, 42 complex 42 meshing 8 modal 23 post processing 9 reports 35 rerunning on edited designs 31 results, reading 25, 28 solving 7 types, setting 22, 34 updating 34 vibration 11 workflows 14 analysis (.
Force dialog box 17 forces 69, 71 simulating 69 frequency modes 11 Frequency Options dialog box frequency results options 24 meshes 8, 23, 26, 30, 33 creating 8 displaying 30 setting sizes 23 size settings 33 viewing 26 Minimum command 30 modal analyses 11, 23–24 model geometry, editing 31 modes 11, 24 frequency 11 result options 24 moment loads 18 24 G geometry, editing 31 H Help system 4, 46 N I natural resonant frequencies non-zero displacement loads Input Grapher 73 Insert Joint tool 63, 66 O
deformation 10 display options 30 equivalent stresses 10 frequency options 24 resonant frequency 29 reviewing 9 safety factor 10 stress analysis, reading 28 updating 34 viewing analyses 25 rigid bodies, creating 59 functionality 6 results 28 tools 5 workflows 14 Stress Analysis Settings dialog box 21 Stress Analysis Update command 23, 34 stresses, equivalent 10 T tools, stress analysis 13 torque damping, adding to joints types of analyses, setting 22 S safety factor results 10, 29 Simulation Panel 56 dia
