Title: Moonbuggy Rear Suspension Analysis
1 - Moonbuggy Rear Suspension Analysis
- ME450 Computer-Aided Engineering Analysis
- Department of Mechanical Engineering, IUPUI
- Instructor Dr. Koshrow Nematollahi
- May 1, 2006
- John Fearncombe
- Brandin Ray
- Amber Russell
2Objectives
- Perform finite element analysis of moon buggy
suspension using ANSYS Workbench - Evaluate stress and deformation resulting from
applied load - Perform iterations as needed until a satisfactory
design is realized
3Introduction
- Moon buggy originally designed in Spring 2005 by
ME 462 design team - Lower a-arms on original suspension failed
- Normal loading conditions were determined to be
approximately 200 pounds-force - The initial design was modeled to determine if it
could be modified and safely used
4Theoretical Background
- Utilized ten-node SOLID92 tetrahedral elements
- Ideal for complicated solids with curved
boundaries
5Model Details for Existing Design
- Originally modeled in Pro/Engineer (IGES), then
imported into ANSYS Workbench - Static analysis only
- Aluminum alloy construction
- 200 pounds-force load applied at shock mount
- Fixed supports at axes of rotation
- Displacement constrained in transverse direction
6ANSYS Workbench Model of Existing Design
7Deformed Geometry for Existing Design
- Maximum Deflection of 2.7810-3 inches
- Maximum deformation occurs near shock absorber
mount
8Principal Stresses for Existing Design
- Maximum principal stress of 1.791 ksi
- Yield stress for 6061 aluminum alloy is 35 ksi
- Maximum stresses occur where the part failed
9Shear Stress for Existing Design
- Maximum shear stress of 1.421 ksi
- Deemed insignificant
- Failure due to fatigue in aluminum
10Model Details for First Iteration
- Modeled and constrained as before
- Aluminum alloy construction
- 200 pound-force load again applied at shock mount
- Modeled as one-piece construction with no welds
11Results - ANSYS Model of First Iteration
12Deformed Geometry for First Iteration
- Maximum Deflection of 5.4210-3 inches
- Occurs below shock absorber mounting bolt
13Principal Stresses for First Iteration
- Maximum principal stress of 221.267 psi
- Yield stress for 6061 aluminum alloy is 35 ksi
- Maximum stresses occur near the shock absorber
mounting bolt
14Shear Stress for First Iteration
- Maximum shear stress of 20.917 psi
- Shear stress concentrated near welds
- Quality of welds had been an issue
15Model Details for Final Iteration
- Modeled and constrained as before
- Aluminum alloy construction with steel
reinforcement plates at shock absorber mount - Two points of attachment to wheel hub housing to
relieve stress on aluminum members
16ANSYS Workbench Model of Final Iteration
17Deformed Geometry for Final Iteration
- Maximum Deflection of .11410-3 inches
- Located at mid-section of shock absorber bolt
18Principal Stresses for Final Iteration
- Maximum principal stress of 1.875 ksi
- Yield stress
- 6061 aluminum alloy is 35 ksi
- 4140 steel is 45 ksi
- Maximum stresses occur in the steel reinforcing
plates
19Shear Stress for Final Iteration
- Maximum shear stress of 1.170 ksi
- Located in steel reinforcing plates
- Achieved objective of localizing stresses within
steel elements
20Impact Statement
- Through the use of finite element analysis on the
rear suspension of the moon buggy the vehicle has
become more safe, stable, and easier to maintain.
- By optimizing the design before production, we
have alleviated costly and potentially dangerous
failures.
21Conclusion - Advantages of Final Iteration
- Maximum stress is distributed on steel
reinforcing plates - Ability to quickly and inexpensively replace the
parts most likely to fail - Easier fabrication
- No reliance on welds for structural stability
22Suspension Test
23Bibliography
- ME 450 Course Text
- ANSYS Website www.ansys.com
- Car Suspension and Handling. Bastow, Donald.
London Pentech Press Warrendale, Penn.
Society of Automotive Engineers, 1993. - Chassis design principles and analysis
Milliken, William F., 1911- - www.engineersedge.com Material Properties