1 / 21

Team Flying Sheep Engineering Analysis

Team Flying Sheep Engineering Analysis. Mark Berkobin John Nevin John Nott Christian Yaeger Michelle Rivero. System Review: Solid Edge Model. Possible Points of Failure for Analysis. Welds between horizontal supports and tilt mechanism Horizontal Supports in Bending and Shear

milo
Download Presentation

Team Flying Sheep Engineering Analysis

An Image/Link below is provided (as is) to download presentation Download Policy: Content on the Website is provided to you AS IS for your information and personal use and may not be sold / licensed / shared on other websites without getting consent from its author. Content is provided to you AS IS for your information and personal use only. Download presentation by click this link. While downloading, if for some reason you are not able to download a presentation, the publisher may have deleted the file from their server. During download, if you can't get a presentation, the file might be deleted by the publisher.

E N D

Presentation Transcript

  1. Team Flying SheepEngineering Analysis Mark Berkobin John Nevin John Nott Christian Yaeger Michelle Rivero

  2. System Review: Solid Edge Model

  3. Possible Points of Failure for Analysis • Welds between horizontal supports and tilt mechanism • Horizontal Supports in Bending and Shear • Vertical Supports in bending and shear • Bike Interface in bending and shear • Ratcheting Mechanism • Load Bearing Bolts

  4. Not Analyzed • Stability: System is Constrained by AISI 1018 HR Low Carbon Steel parts, stability should not be an issue • Fatigue Analysis: It is not expected that the system will be used more than once every several hours. Fatigue should not be an issue • Human interface: Is built into the mechanism of a popular, proven jack system incorporated into the system • All failure points on the jack itself: The jack is a proven commercial product that we are incorporating into the system, we assume it will continue not to fail

  5. FBD For Welds in Torsion FBD for Welds in Shear Welds Between Horizontal Supports and the Tilt Mechanism on the Base

  6. Weld Analysis in Torsion • Maximum length of from point of force application to weld: 8.75 inches • Length of Weld: 14 inches = 1.17 ft • Height of welded part (D): 1.5 inches = 0.125 in • Maximum Force at point of application = 600 lb • Maximum possible moment: 600 lb * 8.75 = 5250 lb-in • Weld thickness (a value) = 5/16 inch = 0.0260 ft • Bending Stress = (Normal Stress)/(2)0.5 • Bending Stress = M/(W*a*(a+D)) = 5250/(14*0.3125*(.3125+1.5)) = 662 psi • Assume: Welds are Equivalent Strength to Steel: Max Allowable Stress = 36 Kpsi • Safety Factor = 36,000 psi/662 psi = 54.4

  7. Weld Analysis in Shear • Maximum length of from point of force application to weld: 8.75 inches • Length of Weld: 14 inches = 1.17 ft • Height of welded part (D): 1.5 inches = 0.125 in • Maximum Force at point of application = 600 lb • Maximum possible moment: 600 lb * 5.75 = 3450 lb-in • Weld thickness (a value) = 5/16 inch = 0.0260 ft • Bending Stress = (Normal Stress)/(2)0.5 • Bending Stress = M/(W*a*(a+D)) = 3450/(14*0.3125*(.3125+1.5)) = 435 psi • Assume: Welds are Equivalent Strength to Steel: Max Allowable Shear Stress = 24.1 kpsi • Safety Factor = 24,100 psi/435 psi = 55.4

  8. Horizontal Supports Solid Edge Model

  9. Horizontal Support Bending Analysis • For the frame sliders side bar 600 lbs Max stress = M*c/I M = r X F =17 in x 600 lbs = 10,200 lb-in c = 0.75 I = ((Loutter)4 –(Linner)4)/3 = ((1.5)4-(1.25)4)/3 = .873 in4 Max stress = (10,200*.75)/.873 = 8,762 psi Max allowable Stress = 36 kpsi Safety Factor = Max Stress/Maximum Allowable Stress = 36,000/8,762 = 4.11 17 inches, from center point; Assume system is symmetrical around the midpoint

  10. Horizontal Support Shear Stress Analysis • At the support beams Side of square tube: 1.25 in Thickness:1/8 inches Area affected in shear: A=(1.25)2-(1.25-2(.125*2))2 A=.5625 in2 Maximum Allowable Shear Stress = 24.1 Kpsi Moment Max stress = P/A = 600/.5625 = 1,066 Safety Factor = Max Stress/Maximum Allowable Stress = 24,100/1,066 = 22.6 600 lbs Cross Sectional Area

  11. Vertical Support Solid Edge Model

  12. Solid Edge Model Free Body Diagram Bike Interface Description

  13. Vertical Support Bending Analysis • For purposes of this analysis the bike interface with the foot pegs (half tube) and the frame sliders (whole tube) will be treated as the same in terms of failure • Max stress = M*c/I • M = r X F = 3.25 in x 600 lbs = 1,950 lb-in • c = 0.75 • I = ((Loutter) 4 –(Linner)4)/3 = ((1.5)4-(1.25)4)/3 • = .873 in4 • Max stress = (1,950*.75)/.873 +600/(.2*.5) = 7,675 psi • Max allowable Stress = 36 kpsi • Safety Factor = Max Stress/Maximum Allowable Stress • = 36,000/7,675 = 4.69

  14. Solid Edge Model Free Body Diagram Description of Ratcheting Mechanim

  15. Design Characteristics Tooth height is .2 inches due to the need for adjustability Tooth width is variable to meet requirements, currently planned at 0.5 inches Mode of failure Pressure of bike will be straight down on the tooth, tooth likely to fail in shear Worst Case scenario: all of the bike’s weight resting on one “tooth” Ratcheting Analysis

  16. Ratcheting Analysis-Continued • Maximum Shear Stress:  = F/A = 600/(.2*.5) = 6000 psi = 6 kpsi • Maximum Allowable Shear Stress for AISI 1018 HR Low Carbon Steel: 32 kpsi • Safety Factor: (32 kpsi)/(6kpsi) = 5.34

  17. Solid Edge Model In Tension In shear Free Body Diagram Description of Load Bearing Bolts

  18. Bolt Analysis • Bolts Used throughout this project have been chosen as ½” diameter SAE Grade 8 bolts • Grade 8 bolts have the following properties:

  19. Bolt Analysis-Shear • For Coarse ½” diameter bolt • At=0.1419 in2 Proof Load Fp=AtSp Fp=17028 lbs Maximum expected Fp = 600 lb (weight of the motorcycle) Safety factor: 17028/600 = 23.4

  20. Bolt Analysis-Tension T=FL/HA L= 1.90 inches H = 3.99 inches T = (600*1.90)/(3.99*0.1419) = 2,013 psi Safety Factor = 150/2.013 = 74.5

  21. Questions?

More Related