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Table 2: Reaction Moments Action on the Trailing Arm from the Road Forces
| Case | MDx ( |
|---|
| kNm) | MDy ( |
|---|
| kNm) | MDz ( |
|---|
| kNm) | |||
|---|---|---|---|
| Accelerating & Cornering (Inside Rear Wheel) | 0.1945 | 0.0588 | 0.4835 |
| Accelerating & Cornering (Outside Rear Wheel) | 0.1945 | 0.0588 | -0.2514 |
With these forces and moments acting on the trailing arm, a forces analysis can be used to determine the reaction loads on A, B, and C.
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With this the unknowns are Ay, Az, Bx, By, Bz, Cy, and Cz. The six net force and moment equations were written, and one equation that relates the Cy and Cz forces.
Edit: Equation 4 should be (Dx)(Dad(z)) not (Dx)(Dad(y))
The following distances were taken from the CAD model
Table 3: Distances of the Rear Suspension
| Term | Distance (mm) |
|---|---|
| d(AB(x)) | 164.002 |
| d(AD(y)) | 89.5521 |
| d(AC(z)) | 155.0708 |
| d(AC(y)) | 1.7462 |
| d(AD(z)) | 286.6926 |
| Theta | 69.6 degrees |
The equations were then placed in a matrix solver in order to solve for the reaction loads. Those loads are outlined in the follownig table:
Table 4: Final Reaction Loads
Similar to the front suspension, the trailiing arm was simulated using a dummy body as the wheel. A force was applied to the contact patch and supports were added to the rod end, plain bearing and coilover clevis on the trailing arm.
Results
| von Mises Stress |
|
|---|---|
| Displacement |
|
| Mesh Independence |
|
Conclusion & Recommendation
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