# 7 Centrifugal loads and angular accelerations

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2 Figure 7 2 Von Mises stress in a spoke with angular acceleration about the left end 7.2 Building a segment geometry The desired rotating spin_grid is shown in Figure 7 3. The part has a inner shaft hole diameter, and outermost diameter of 1 inch and 4 inches, respectively. It has six curved slots ¼ inch wide, symmetric about the 36 degree line, and end in a semi circular arc that is 1/8 inch from the 0 degree line. The grid is 0.20 inches thick. Figure 7 3 Full geometry and its one fifth symmetry Prepare a sketch in the top view with several radial and arc construction lines via: 1. Front Insert Sketch, build several construction lines for the center of the slots, the symmetry plane, and an off set horizontal line for the fillet centers. Add arcs, and line segments to close the shape. Extrude, about the mid plane, to the specified thickness. 2. Define the axis of rotation. In this case it s the axis of the inner circular hole. Use Insert Reference Geometry Axis to open the Axis panel. In the Axis panel check Cylindrical/Conical Face and select the inner most cylindrical surface segment of the part and Axis 1 will be defined as a reference geometry entity. Draft 10.2 Copyright All rights reserved. 119

3 At this point the smallest geometrical region is complete and you can move on the SW Simulation Feature Manager to conduct the deflection and stress analysis. 7.3 Initial SW Simulation angular velocity model Analysis type and material choice To open a centrifugal analysis you have to decide if it is classified as static, vibration, or something else. Instead of applying Newton s second law, F = m a, for a dynamic formulation (where is F the resultant external force vector and is a the acceleration vector of mass m), D Alembert s principle is invoked to use a static formulation of F F I = 0, where the inertia force magnitude is F I = m r ω 2 in the radial direction and/or m r α in the tangential direction. That is, we reverse the acceleration terms and treat it as a static problem. Since this part has symmetry in the radial and circumferential directions, the angular velocity case can be obtained with the smaller 36 degree segment. In SW Simulation: 1. Right click on the Part_name Study, Name the part (spin_grid here), pick Static analysis. The study defaults to solid elements. (A planar model is almost always the cheapest and fastest way to do initial studies of a constant thickness part.) 2. When the Study Menu appears right click on Solid Edit/Define Material. 3. In the Material panel pick Library Steel Cast Alloy. Select Units English. Note that the yield stress, SIGYLD, is about 35e3 psi. That material property will be compared to the von Mises Stress failure criterion later. (The mass density, DENS, is actually weight density, γ = ρg, and is mislabeled.) Draft 10.2 Copyright All rights reserved. 120

6 1. Right click Mesh Apply Control to activate the Mesh Control panel. 2. There pick the six bottom arc faces as the Selected Entities and specify an element size. 3. Then right click Mesh Create. The initial mesh looks a little coarse, but okay for a first analysis. 4. Start the equation solver by right clicking on the study name and selecting Run. When completed review the results Post processing review Both the displacements and stresses should always be checked for reasonableness. Sometimes the stresses depend only on the shape of the material. The deflections always depend on the material properties. Some tight tolerance mechanical designs (or building codes) place limits on the deflection values. SW Simulation deflection values can be exported back to SolidWorks, along with the mesh model, so that an interference study can be done in SolidWorks Displacements You should always see if the displacements look reasonable: 1. Double click on Results Define Displacement Plot to see their default display, which is a continuous color contour format. Such a pretty picture is often handy to have in a report to the boss, but the author believes that more useful information is conveyed with the discrete band contours. 2. Right click on Plot 1 Settings Fringe Options Discrete. The default deformed shape displacement contours appear. Draft 10.2 Copyright All rights reserved. 123

7 3. Since displacements are vector quantities you convey the most accurate information with vector plots. Right click Plot1; Edit Definition Advanced Show as a vector plot. 4. When the vector plot appears, dynamically control it with Vector Plot Options and increase Size. Then dynamically vary the Density (of nodes displayed) to see different various nodes and their vectors displayed. Retain the one or two plots that are most informative. As expected, the center of the outer most rim has the largest displacement while the smallest displacement occurs along the radial spoke centered on the 0 degree plane. You may want to compare the relative displacement of the outer ring to a handbook approximation in order to validate the computed displacement results (and your knowledge of SW Simulation). Localized information about selected displacements at nodes or lines are also available. For problems with angular velocity or angular accelerations you should also view the displacements in cylindrical coordinate components. For that use: 1. Edit Definition Advanced and select axis 1 from the part tree. Then the part s radial displacement component will be displayed as UX. Draft 10.2 Copyright All rights reserved. 124

9 Principal stresses Figure 7 5 The von Mises failure criterion and deformed shape due to angular velocity The magnitude and direction of the maximum principal stress P1 is informative (and critical for brittle materials). Since they are vector quantities they give a good visual check of the directions of the stress flow, especially in planar studies (they can be quite messy in 3 D): 1. Right click in the graphics area, select Edit Description then pick P1 Maximum Principal Stress, and Vector style and view the whole mesh again. 2. If the arrows are too small (look like dots) zoom in where they seem biggest and further enhance you plot with a right click in the graphics area, select Vector Plot Options and increase the vector size, and reduce the percentage of nodes used for the vector plot. A typical P1 plot, with the deformed shape, is given in Figure 7 6 for the outermost ring junction with the radial spoke Factor of safety Figure 7 6 Principal stress P1 at outer ring, due to angular velocity For this material you would use the von Mises effective stress failure criterion. That is, your factor of safety is defined as the yield stress divided by the maximum effective stress. It was noted above that the ratio is greater than ten in this preliminary study. Draft 10.2 Copyright All rights reserved. 126

12 7.5 Post processing approximate restraint results Displacements for approximate cyclic restraints The displacements, of Figure 7 9, are mainly in the tangential direction. To obtain the plots in polar components, use Edit Definition UY Advanced Axis 1 OK. The graph, along the bottom edge, of the circumferential deflection will be compared to the larger formal cyclic symmetry study presented next. Figure 7 9 Circumferential displacements for approximate cyclic restraints Figure 7 10 Radial displacements for approximate cyclic restraints Draft 10.2 Copyright All rights reserved. 129

13 7.5.2 Stress results for approximate restraints The effective stresses (Figure 7 11) are quite low, for the current angular acceleration value. Increasing the angular acceleration by a factor of about 25 would put the stress just below the yield point. The maximum stresses occur around the innermost slot. Figure 7 12 shows that the maximum tension (principal stress P1) occurs on the lower right edge of the first grove. Both the maximum compression and shear occur in the lower left (red) regions of Figure Figure 7 11 Region of maximum von Mises failure criterion Figure 7 12 Maximum principal stress vectors and values around slot base for approximate restraint You should expect the maximum shear stress (Figure 7 13) to occur near there also. The (reaction) torque necessary to accomplish the specified angular acceleration is transmitted radially by the spokes. The ribs can be viewed as similar to lumped masses attached to a cantilever spoke. As you move from the outer rib toward the rotation axis you are picking up more mass, and you get the maximum torque by the inner hole. That torque is transmitted by shear stresses here. The first open gap has the largest torque going through the spoke thickness. Draft 10.2 Copyright All rights reserved. 130

14 7.6 Cyclic symmetry model Figure 7 13 Twice the maximum shear stress for approximate cyclic restraints The above studies show that you can often pick symmetry regions in rotational loadings and drastically reduce the computer resources required. Here it seems like you could refine the outer spoke mesh further to see worst angular velocity effects and refine the innermost gap ends to see the worst angular acceleration effects. Actually, the full model can be replaced by the 72 degree segment using the SW Simulation cyclic (circular) symmetry boundary condition. The automation of a cyclic symmetry analysis requires that the software can express the degrees of freedom in terms of changing coordinate systems established tangential and normal to the repeated surface of cyclic symmetry. That is illustrated in Figure 7 14 (left) where the top view of a cyclic symmetry impeller solid shows some of the pairs of tangential and normal displacements that have to be established and coupled by the analysis software. SW Simulation includes this ability to impose that the normal and tangential displacements on the two limiting surfaces are the same, even though initially unknown. That figure shows that the limiting surfaces do not have to be flat (as in the current example). A similar impeller solid body with cyclic symmetry appears in Figure Out of plane body parts there would be more influenced by angular acceleration. Figure 7 14 An impeller well suited for cyclic symmetry analysis Draft 10.2 Copyright All rights reserved. 131

15 Figure 7 15 An impeller solid with 16 segments of cyclic symmetry Mirroring the part for the circular symmetry geometry Continuing from the 36 degree segment, use Insert Pattern/Mirror Mirror to open the Mirror panel. Select the previous part as the Features to Mirror and pick one of the free ring faces as the Mirror Plane, OK. You could pick any 72 degree segment of the part as the cyclic symmetry geometry, but the above choice seemed most logical Proper cyclic symmetry restraints In this case the two limiting surfaces, having the same unknown displacements, are flat radial planes. To invoke circular symmetry use Fixtures Advanced Circular Symmetry to open the Circular Symmetry Panel. There pick Axis 1 as the common axis for the cyclic symmetry innermost inner edges, pick one face, and then pick that face s revolved location as the second face, OK. The SW Simulation will automatically establish matching meshes on those two faces and create normal and tangential coordinates at each node on those two faces (like in Figure 7 14). While you see two different nodes at corresponding points on those surface meshes, you should think of them as a single node having normal, and tangential displacement components to be determined by the specific loading conditions. Draft 10.2 Copyright All rights reserved. 132

16 7.6.3 Shaft restraints The angular acceleration in this example is input by its fixation to the outer surface of the center shaft (not shown). That would usually be accomplished by a shrink fit, which would also prevent rigid body motion in the axial direction of the shaft. Apply those restraints with Fixtures Advanced On Cylindrical Faces Preventing rigid body motion The restraints described above would prevent the six possible rigid body motions. In this case, since the part is flat there will be no axial displacements. Thus, you can reduce the number of unknowns to be solved, and better stabilize an iterative solver, by alternately preventing the z axis RBM by treating the top face as a symmetry plane. Change the symbol colors to remind yourself that it is more an efficiency restraint as well as restraint against RBM. Use Fixtures Advanced Symmetry. Draft 10.2 Copyright All rights reserved. 133

17 7.6.5 Mesh generation Here you generate solid elements in the full 72 degree segment Solution method The fast iterative solver has worked for crude cyclic symmetry meshes; however it failed for practical mesh sizes. The direct sparse solver is better suited to problems with multipoint constraints, like circular symmetry. It takes much longer to run and requires more memory and disk space but is most likely to yield an accurate solution. The results were obtained with it. They will be compared to the approximate validation predictions from the previous discussions Cylindrical component displacements Once again, it is logical to present the displacements in terms of their radial (UX) and circumferential (UY) values (the axial UZ values are essentially zero). The amplified deformed cyclic symmetry shape is given in Figure That figure also shows the color levels for the magnitude of the main circumferential displacement values. To verify that the circular symmetry solve has indeed computer the same displacements on the two limiting surfaces the circumferential values are graphed along the zero and 72 degree line segments. The graphs, in Figure 7 17, are compared with the approximation given above as a validation result. The agreement is surprisingly good. Draft 10.2 Copyright All rights reserved. 134

18 The radial displacements, for angular acceleration only, are about a factor of ten times smaller. Their amplitudes are shown in Figure The radial displacements along the outer arc are graphed on the left in Figure 7 19 and are compared with the half model approximation on the right of that figure. Here, the radial displacements are anti symmetric about the middle 36 degree line. Figure 7 16 Amplified deformed shape, with circumferential displacement colors Figure 7 17 Cyclic symmetry UY values at 0 and 72 degrees (top) compared with approximate validation Draft 10.2 Copyright All rights reserved. 135

19 Figure 7 18 The radial displacements, UX, are about ten times smaller than UY Figure 7 19 Outer arc radial deflection, UX, compared to (half) validation estimate on the right Possible failure criteria The von Mises stress is always positive so it shows symmetric distributions (Figure 7 20) under this angular acceleration loads. The levels are quite low and would not govern when compared to the angular velocity results. The maximum principal normal stress, P1, is also quite small, as seen in Figure The maximum shear stresses are given in Figure 7 22 and they are also small. All of these possible material failure criterions are directly proportional to the angular acceleration value. They are also within about 20% of the approximate validation estimates given above. That is unusually good agreement. Figure 7 20 Cyclic symmetry von Mises stress from angular acceleration Draft 10.2 Copyright All rights reserved. 136

20 Figure 7 21 Cyclic symmetry principal stress P1 is anti symmetric 7.7 Full part model Figure 7 22 Twice the maximum shear stress is symmetric for cyclic symmetry restraints If you failed to recognize the above cyclic symmetry cases then you might be forced to employ a full part model. To do that you must first build the full part. An efficient approach would be to use a fine mesh in one repeating segment while having a very coarse mesh elsewhere, as seen in Figure Draft 10.2 Copyright All rights reserved. 137

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