SRI JAYACHAMARAJENDRA COLLEGE OF ENGINEERING, MYSURU
Engine Specification
Vehicle dimensions
Brakes
Steering
Wheels
TECHNICAL SPECIFICATION
DESIGN METHODOLOGY
Design Considerations
Density | 7.87g/cc |
Yield Strength | 370 MPa |
Poisons Ratio | 0.29 |
Ultimate Strength | 440 MPa |
Modulus Of Elasticity | 205 GPa |
Properties of AISI 1018
Element | Content |
Carbon(C) | 0.14-0.20% |
Sulphur(S) | <=0.050% |
Iron(Fe) | 98.81-99.26% |
Material | OD inch | ID inch | Bending Strength (Nm) | Stiffness | Weight/ meter (Kg) | Cost/ Kg (₹) |
AISI1018 | 1 | 0.874 | 240.93 | 1742.5 | 0.941 | 160/- |
AISI4130 | 1 | 0.874 | 308.22 | 1742.5 | 0.939 | 360/- |
AISI1018 | 1 | 0.842 | 286.29 | 2070.5 | 1.16 | 150/- |
AISI1018 | 1.25 | 1.124 | 402.52 | 3540.35 | 1.192 | 160/- |
AISI4130 | 1.25 | 1.124 | 498.39 | 3540.35 | 1.189 | 360/- |
Type of frame | Space frame |
Bends | 5 |
Welds | 80 |
Material length: OD=1” ,ID=0.874” OD=1.25” ,ID=1.124” | 457.67 inch 350 inch |
Chassis weight | 17.65Kg |
Driver Ergonomics
Wheelbase & Trackwidth
Design of chassis
Prototyping
Optimization
Selection of material
Analysis
Selection of material
Final Design
Front Impact
Rear Impact
Side Impact
Torsional Test
Loads and Constraints
Type of impact | Load | Equivalent stress | Deformation | FOS |
Front impact | 10000N ( 6.06G) | 195.45 | 2.1047 | 1.89 |
Rear impact | 10000N ( 6.06G) | 293.96 | 5.16 | 1.258 |
Side impact | 5000N ( 3.03G) | 282.48 | 5.716 | 1.309 |
Torsion test | 4000N ( 2.42G) | 355.91 | 14.273 | 1.0396 |
Deformation
Equivalent stress
Solver | Frontal |
Meshing method | Shell |
Nodes | 238649 |
Elements | 124207 |
Analysis
Assumptions made
Impact time | 0.2s |
Total weight | 165kg |
speed | 80Km/hr |
FINITE ELEMENT ANALYSIS
Human Comfort Assessment
Cockpit View
External Kill Switch
Safety Kit
Ergonomics | Angles |
Hip angle | 52 |
Knee angle | 104 |
Ankle angle | 82 |
Elbow angle | 130 |
Vision Cone angle | 45 |
Fire Extinguisher
ERGONOMICS AND SAFETY
STEERING
Parameters | Values | |
Turning Radius | 1.9m | |
Steering Ratio | 1:1 | |
Steering Angle | Inside Outside | 38 24.3 |
Steering Wheel Radius | 10” | |
Steering Wheel Torque | 6.68Nm | |
Steering Stops (centre To Lock) | 0 -38 | |
Tie Rod Length | 342mm | |
Ackerman Percentage | 102 | |
Ackerman Angle | 18 | |
King Pin Inclination | 80 | |
Caster Angle | 50 | |
Camber Angle | -40 | |
Steering Effort | 2.6kg/Hand | |
Column Inclination | 60 | |
Scrub Radius | 75mm | |
Toe Angle | Toe in 20 | |
Knuckle Analysis
C-Clamp Analysis
Pitman Arm Mechanism
Selection of suitable steering
Quick Responsive
Compact and less weight
Ease for calculation, simple geometry
Pure Rolling condition
Steering Geometry
Adams simulation
TEMPERATURE DISTRIBUTION
Brake Circuit
Brake calculations
Rotor Thermal Analysis
Brake Layout
Pedal Analysis
Stopping Distance | 8.97 m at 75kmph |
Pedal Force | 200 N |
Pedal Ratio | 1:6 |
Performance
Weight Transfer | 1036.28N |
Coefficient Of Friction(road) | 0.6 |
Static rolling radius | 0.135m |
Frictional Force | 3306.67N |
Clamping Force | 8266.68N |
Brake Torque | 32655 Nm |
Deceleration | 24.18m/s2 |
Pressure Inside TMC | 4.21 MPa |
Brake Type | Hydraulic disc brakes |
Master Cylinder Dia. | 19.05mm |
Calliper Cylinder | 25mm |
Brake Fluid | Dot 4 |
Selection
Drum/Disc brakes
Efficient braking
DISC brakes
Disc selection
Multiple output
TMC
Greater clamp force
Dual Piston
Reduce stopping distance
Rear disc
200mm dia.
Front calliper
SIEMENS NX
Speed | 30Kmph | 40Kmph | 50Kmph | 60Kmph |
Stopping Distance | 1.43m | 2.5m | 3.98m | 5.73m |
Stopping Distances
Brake Assembly
BRAKES
Engine Selection
Tyre Size
Front | 10-4.5/5” |
Rear | 11-7.1/5” |
Specification | Access | Vespa | Discover |
Displacement | 124cc | 125cc | 124.6 |
Max. Power | 8.7Ps@ 7000 rpm | 10.5Ps@ 7500rpm | 11.5Ps@ 8000rpm |
Max. Torque | 9.8Nm@5000 rpm | 10.6N m @ 6000rpm | 10.2Nm@6000rpm |
Transmission | CVT | CVT | Geared |
Design of shaft
Shaft Material | Stainless Steel 402 |
Shaft Dia. | 30 mm |
Hub Analysis
Ø30mm
42”
Selection of Engine w.r.t rulebook constraints
<130cc
Torque and Power requirement
Ease of transmission
CVT > Geared
Ease of Availability and cost
Access 125
Vehicle performance
Top speed | 85Kmph |
Acceleration | 2.68m/s2 |
Performance | 0-60kmph in 6.2sec |
Maximum towing capacity | 2250 kg |
Transmission unit
CVT Speed ratio | 2.2:1 – 0.7:1 |
Gear reduction Speed ratio | 7.57:1 |
Chain drive Speed ratio | 0.8:1 |
Overall ratio | 13.32:1 – 4.24:1 |
Engine Mount Analysis
POWERTRAIN
Equipment | Specification |
Bench Drilling | Capacity 25mm |
Radial Drilling | Capacity 35mm |
Power Saw | Max dia 175mm |
Arc Welding | O/P 60-160A |
Tig/Mig Welding | O/P 250A |
Milling Centre | Table size 1mx0.25m |
Press Forging | 2 Tonnes |
COLLEGE LABORATORY FACILITIES
Equipment | Specification |
Center Lathe | Centre Distance -1.5m |
CNC Turning | Max turning dia 250mm |
CNC Machining | Max load 600Kg |
Planar M/C | L=2.5m, w=1m |
Shaping M/C | Stroke = 915mm |
Cupola Furnace | Inner dia= 600mm |
Bench Grinder | dia=0.3m,t=20mm |
Processes Involved | Tool /Equipment Requirement |
1.Welding |
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2.Drilling |
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3.Grinding |
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4.Cutting |
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5.Bending |
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MANUFACTURING PROCESSES
DFMEA
Component | Function | Potential Failure Modes | Potential Failure Effects | S | Potential Failure Causes | O | D | R P N | Preventive Measures Action plan to lower RPN | S | O | D | R P N |
Chassis | Provides base on which all other components are mounted | Breakage of structural frame ,Torsion of chassis | Leads to collapse of vehicle, driver safety is endangered | 8 | Improper welding, not analysing using software, drilling into chassis | 5 | 2 | 80 | Analysis, proper design, proper material selection, welding selection | 3 | 2 | 2 | 12 |
Engine | Power unit of the vehicle | Improper lubrication, old spark plugs, improper fuel valve, overheating | Engine seizure, incomplete combustion, burnout of spark plugs, less mileage | 8 | Less lubricant volume, improper servicing of engine | 6 | 3 | 144 | Periodic service of engine, appropriate lubricant, proper cooling | 4 | 2 | 3 | 24 |
Rear Axle | Transfer of power from engine to wheels | Improper material selection and overloading | Failure of transmission system, Breakdown | 8 | Fatigue/cyclic loading, improper dia. of shaft, improper mountings | 7 | 3 | 168 | Selection of material based on max load, choosing proper dia. | 3 | 4 | 3 | 36 |
C-Clamp | For Proper positioning of knuckle | Shear of clamp bolts, breakage from chassis frame | Leads to total collapse of vehicle | 10 | Improper designing and mounting, improper welding | 5 | 3 | 150 | Providing ribs between chassis and c clamps for extra strength, load analysis | 3 | 2 | 3 | 18 |
Brakes | To decrease the speed of a vehicle | Excess heat generation, cracks in rotor, expansion of brake fluid | Brake failure, brake fade, wheel locking | 9 | Improper selection of brake fluid, improper mounting of rotor | 5 | 2 | 90 | Thermal analysis of brake rotor, proper selection of brake fluid | 2 | 4 | 20 | 16 |
DESIGN VALIDATION PLAN
Department/ Component | Test Description | Acceptance Criteria | Test Stage | Date of Implemen-tation | Test Respons-ibility | Date of Completi-on | Pass/ Not pass | Test results | Notes or inference |
Chassis
| Impact test Torsion test | Factor of safety > 1, Driver safety | Analysis using ANSYS 15.0 | 30-05-2017 | Deshik | 1-06-2017 | Pass | FOS Impact Front= Side= Rear= Torsional= | Design is applicable for a gokarting vehicle |
Steering 1.Tie rod 2.Steering column 3.Knuckle |
Testing using simulation
| Light weight, Proper assemblage, Higher FOS, Verification of Ackermann principle | Finite element Analysis using ANSYS 15.0, Simulation using ADAMS, 2D diagrams in SOLID EDGE | 2-06-2017 | Kaustubh | 4-06-2017 | Pass | True rolling condition is achieved with % of Ackermann principle | Driver is able to steer the vehicle with ease and comfort |
Brakes 1.Disc Rotor 2.Rotor hub |
| Good heat flux rate, Proper heat dissipation | Thermal analysis using ANSYS 15.0 Finite element analysis using | 2-06-2017 | Lokin | 5-06-2017 | Pass | Max. Temperature generated= , Heat flux= , FOS of Rotor= | Design of rotor hub is safe with higher FOS, High thermal resistant rotor, Proper heat dissipation |
Power train 1.Drive shaft 2.Chain drive |
| Sustain light shock loads, Safe design FOS, Better strength for tension loads | Theoretical calculations, Chain drive calculation using RENOLD Calculator | 4-06-2017 | Aditya | 7-06-2017 | Pass | The chain and sprockets and shafts are designed accordingly to the loads | The design withstands the loads |
GANTT CHART
Power Transmission Adithya M A Vivek Gourav Vijay Kumar Akshay Achar Vishnu Sharma Architha Bhat Chethan Akash Acharya Monisha Purushotham Gowda |
Chassis Deshik K J(vice captain) Nikhil M R(captain) Sathwik U Prasanna Kulkarni |
Brakes Lokin Chandan Naik Sandeep Rafiq Sonal Pal Shantraj Kottur |
Steering Kaustubh Ashish Wali Ashish M Himani Porwal Prithviraj |
Faculty Advisor Dr G Mallesh Associate Professor Dept Of Mechanical Engineering Sjce , Mysore |
Team division:
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SL.NO | MATERIAL | COST | WEIGHT |
1 | Chassis
Total | Rs 5000 Rs 1000 Rs 6000 | 17.65kg 5.75kg 23.4kg |
2. | Brake
Total | Rs 1710 Rs 1500 Rs 500 Rs 400 Rs 985 Rs 180 Rs 5270 | 1.6kg 1.9kg 0.5kg 0.2kg 0.9kg ----- 5.1kg |
3. | Steering
Total | Rs 1745 Rs 745 Rs 745 Rs 1500 Rs 1400 Rs 6135 | 1kg 1kg 1kg 0.5kg 1.5kg 5kg |
4. | Power Train
Total | Rs 30000 Rs 1800 Rs 1050 Rs 600 Rs 6300 Rs 12000 Rs 51750 | 38kg 6kg 3.2kg 2kg 2kg 8kg 59.2kg |
5. | Miscellaneous
Total
| Rs 1875 Rs 3500 Rs 500 Rs 5875 | 3kg 6.5kg 3kg 12.5kg |
COST AND WEIGHT ANALYSIS
Weight
Cost
Total Weight=105.2kg
Total Cost= Rs 75030
Project Financing
Sponsors | Rs 25000 |
College | Rs 20000 |
Team members | Rs 1400 each |
THANK YOU