group 11- asme design competition
DESCRIPTION
Group 11- ASME Design Competition. Alicia Christie Desmond Bourgeois Toddrick Ruff. ASME Design Competition. Rule Update Rocks do need to touch receiving area 1 rock in each circle. Score S = Σ (R*t) +1000P - W - A - 1000T – 5s - PowerPoint PPT PresentationTRANSCRIPT
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Group 11- ASME Design Competition
• Alicia Christie
• Desmond Bourgeois
• Toddrick Ruff
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ASME Design CompetitionRule Update
•Rocks do need to touch receiving area
•1 rock in each circle
ScoreS = Σ (R*t) +1000P - W - A - 1000T – 5sR = designated rock score t = target multiplier W = Weight of the vehicle in grams A = milliamp-hours available to the device according to the battery labels T = Times device touches border tape s = seconds to complete task, maximum 240 P = bonus for parking vehicle at end of task (1 = parked, 0 = not parked)
2 – 1700 pt rocks1 – 1600 pt 2 - 1500pt2 – 1000pt
Schematic of Test Course
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Decision from Last Presentation3 – Wheel Design
Street Sweeper
Mechatronics, Ariel University Center
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Design Conceptrotate
move
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Must be in an equilateraltriange configuration forsymmetry
r
2*cos(30)[r+s/2]
s
L3.500
4.000
Wheel set distance D = 4r + s : if r = 1 in, s = 1.18 in, D = 5.18 in
D*2 + 4 in (box size with guides in back) = 14.36 in with wheels and box touching
Max length is 14.5 in
r + 2*cos(30)*[r+s/2] = 3.75 in
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Design Concept
4.00
3.50
r
3.5-r
d
r
?
d 42
3.5 r( )2 in
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Final Design
•Wheels are offset with front wheels on inside
barrier
barrier
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Idea for body expansion
• Switch blades
Approximate
Extension Length
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Interim Prototype
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3 Wheel Operating Principle
Exploded View Assembled View
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Assumptions•Const. load with uniform shock•Const. mesh with no backlash•Axial load is negligible•Qv < 5, low pinion velocity < 13m/s•99% reliability•Full-depth teeth with tip loading• Pressure angle 20º •Operating temps < 200º • Teeth form standard AGMA profile
Gear Force Analysis
RadialTangential
Axial
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Gear Force Analysis
TPH
p 20 deg H .121hp
TP 3.447N m
TP 2.542ft lbf
wt
TP
dp
2
wr wt tan wresultant
wt
cos
wt 229.768N wr 83.629N wresultant 244.514N
wt 51.654lbf wr 18.8lbf wresultant 54.969lbf
Resulting Forces
Given
.p 250rpm
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Rock Collector
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Free Body Diagram
Position #1• Assumptions
– Weight of box = 2lbs– Weight of Front = 7lbs– Tipping will not occur
on back wheel
TdWdWTM FrontBox )cos()cos(; 21
3.5in
2lb
1lb
3lb 3lb
1.5in5.9in
10.225in
M = 34.04 lb-in, moment created by rock collector would have to exceed this limit to tip over giving a negative moment
∑M = ∑F*d
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Cost Analysis
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Cost Analysis
Current Total: $943.70
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Future Plan
• FEM Analysis to determine ways to remove material
•Exact gear placement to minimize motor use
•Power input and velocity calculations
•Exact placement of wheels and expandable body to fit within size requirement
•Placement of batteries and motors
•Control configuration
•Amount of motors, gears, other control components
•Program control components