me1104-08 elliot rose scott hamilton conrad meekhof
TRANSCRIPT
ME1104-08 Elliot Rose
Scott Hamilton Conrad Meekhof
Faculty Advisor: Dr. Claudia Fajardo Industrial Sponsor: DENSO North America Foundation
�  Project Goals •  Design a forced-air induction system for a Suzuki RM-Z450 for use in the
WMU Formula race car •  Meet or exceed previous engine power to weight ratio •  Increase fuel efficiency •  Increase volumetric efficiency and engine torque
�  Why? •  Increase in points awarded for fuel economy from 5 to10% of total
competition points •  Accomplished using engine downsizing •  Power output decreases by engine downsizing
�  Method
•  Design was completed using parametric solid modeling, one-dimensional engine simulation software and experimental testing.
�  Forced induction system selection �  Engine system modeling (Ricardo Wave Software) �  Engine model validation
•  Restrictor
•  Analytical peak pressure calculation (MathCAD) �  Sensitivity Study �  Design Iterations �  Cam Profile Design �  Design Results �  Conclusions, Recommendation and Future Work
http://www.wmich.edu/engineer/images/splash/2-9.jpg
�  Current Engine •  Suzuki GSX-R600 �  Four-cylinder, 600cc displacement �  4 valves per cylinder �  Weight: 125 lbs �  Port fuel injected �  Vehicle power to weight ratio: 0.14
�  Proposed Engine •  Suzuki RM-Z450 �  Single-cylinder, 450cc displacement �  4 valves per cylinder �  Weight: 75 lbs �  Gas direct injection redesign �  Vehicle power to weight ratio: 0.11
�  Eaton R410 Roots Supercharger •  Weight: 15 lbs •  Parasitic loss: 6.0 HP– 8.0 HP •  Effect on throttle response •  Designed for 500cc – 1400cc
displacement engines
�  Honeywell GT12 Turbocharger •  Weight: 8.8 lbs •  Parasitic Loss: 0 HP •  No effect on throttle response •  Designed for 500cc – 1,200cc
displacement engines
�  Honeywell GT15VNT Turbocharger •  Weight: 10 lbs •  Parasitic Loss: 0 HP •  Maximum exhaust input temperature
of 825 °C •  Variable vane turbine •  Designed for 1000cc – 1600cc
displacement engines
Supercharger Turbocharger
http://www.eaton.com/ecm/groups/public/@pub/@eaton/@per/documents/content/ct_126004.jpg
http://www51.honeywell.com/honeywell/news-events/graphic-library-n3/transport-systems/images/3.5.3.4.1_gt12_turbo_charger_2.jpg
�  Ricardo Wave (1-D engine simulation software) �  Restrictor implementation (FSAE rules) �  Turbocharger implementation �  Camshaft measurement
•  Design Variables �  Overlap �  Lift �  Duration
�  Mathematical model
Camshaft profiles
Validated Base Model
Turbocharged Engine Model with Restrictor
Restrictor
Turbocharger
�  Restrictor verification •  Flow bench
•  Less than 14% error
�  Stock cam profiles
•  Directly correlate to the cam profiles in the validated engine model
0
50
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0 0.1 0.2 0.3 0.4 0.5 0.6 Volu
met
ric
flow
rat
e (C
FM
)
Pressure Drop (psi) Exparimental Ricardo
0.00
0.10
0.20
0.30
0.40
-400 -200 0 200 400
Valv
e L
ift (
in)
Crank Angle (Degrees from TDC) Intake Exhaust
�  Design variables •  8 variables identified •  This would result in greater than 1,000 iterations
�  Identify critical components
�  Component variation •  Packaging •  6 pipe lengths varied from 2 inches to 8 inches •  2 plenum volumes varied from 0.5 L to 4 L
Varied Component
Power at 7000 RPM
Min (hp) Max (hp) Percent difference
Restrictor to compressor Runner 26.1 26.3 0.7
Compressor to Plenum Runner 26.1 26.3 0.9
Intake Plenum 26.0 27.6 6
Plenum to cylinder Runner 26.9 30.2 10.8
Cylinder to plenum Runner 24.4 29.4 16.9
Exhaust Plenum 18.5 31.3 40.8
Plenum to turbine Runner 26.0 26.3 1.2
Turbine to muffler Runner 25.8 26.2 1.4
�  Limits set by packaging constraints �  Number of iterations: 290
�  Analyzed according to design criteria
�  Turbocharged restricted engine model •  Marginal performance improvements at engine speeds below
8,000 RPM over the stock restricted engine model •  Greatest performance improvements located above 8,000 RPM
�  15% improvement at 8,000 RPM �  60% improvement at 12,000 RPM
Component Final Size
Restrictor to compressor runner 2 in
Compressor to plenum runner 3 in
Intake plenum 2 L
Plenum to cylinder runner 5 in
Cylinder to plenum runner 5 in
Exhaust plenum 5 L
Plenum to turbine runner 18 in
Turbine to muffler runner 3.5 in
0 10 20 30 40 50 60 70 80
3000 5000 7000 9000 11000
Pow
er (h
p)
Engine Speed (RPM)
Initial Redesign Restricted
�  Problem •  Excessive exhaust pressure causing
backflow �  Objective
•  Reduce exhaust backflow •  Increase volumetric efficiency
�  Profile redesign •  Intake valve opening shifted 65 crank angles •  Reduced valve overlap by 66%
0 5
10 15 20 25 30 35 40
3000 5000 7000 9000 11000
Pre
ssu
re (p
si)
Engine Speed (RPM)
Intake Exhaust
0.00 0.05 0.10 0.15 0.20 0.25 0.30 0.35 0.40
-400 -200 0 200 400
Valv
e L
ift (
in)
Crank Angle (Degree from TDC) Exhaust Intake Intake Redesign
�  Performance results •  Improved performance throughout the engine speed range
�  Increased brake power by ~30%
�  Increased volumetric efficiency by ~19% to 56% �  Lowered exhaust back flow by ~ 50%
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10
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3000 5000 7000 9000 11000
Bra
ke
Pow
er (h
p)
Engine Speed (RPM) Stock Camshafts Redesigned Camshafts
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0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
3000 5000 7000 9000 11000
Volu
met
ric
Eff
icie
ncy
Engine Speed (RPM) Stock Camshafts Redesigned Camshaft
�  Goals •  Recover power to weight ratio
lost when down sizing •  Increase fuel efficiency
�  Power increase •  Final design increased peak power by
41% over restricted stock engine
�  Power to weight ratio •  Increased by 35% over restricted
stock engine •  Increased 21% over the GSX-R 600
�  Fuel efficiency •  Marginally decreased over the engine
operating range
•  Fuel efficiency gains from direct-injection design will compensate for this reduction
0.2
0.225
0.25
0.275
0.3
0.325
0.35
3000 5000 7000 9000 11000
Bra
ke
Spec
ific
Fu
el
Con
sum
pti
on (k
g/k
W/h
r)
Engine Speed (RPM) Stock Restricted Final Design
0 10 20 30 40 50 60 70 80
3000 5000 7000 9000 11000
Bra
ke
Pow
er (h
p)
Engine Speed (RPM)
Stock Restricted Final Design
�  Goals
•  Increase low end torque •  Increase volumetric efficiency
�  Torque increase •  35% over stock restricted
engine
�  Volumetric efficiency •  Stock restricted: 87% at 8,000
RPM •  Final design: 144% at 9,000
RPM
0
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
3000 5000 7000 9000 11000
Vol
um
etri
c E
ffic
ien
cy
Engine Speed (RPM) Stock Restricted Final Design
0 5
10 15 20 25 30 35 40 45
3000 5000 7000 9000 11000
Bra
ke
Torq
ue
(Ft-
lbs)
Engine Speed (RPM)
Stock Restricted Final Design
�  Implement forced air induction system featuring: •  Honeywell Garrett GT12 Turbocharger •  Plenum volume �  Intake: 2 L �  Exhaust: 5 L
•  Critical runner lengths �  Plenum to intake: 5 in. �  Exhaust to plenum: 5 in.
•  Cam change �  Delay intake opening 65 crank angles �  66% reduced overlap
� Gear vehicle drivetrain to best utilize power produced.
Picture Courtesy of Honeywell
�  Experimental validation of simulation model •  Physical system build
�  Further refinement of engine packaging •  Exploration of plenum geometries
�  Ricardo VECTIS
•  3-D computational fluid dynamics software •  Intake and exhaust system flow characteristics
�  WMU Mechanical & Aeronautical Engineering Department
�  Dr. Claudia Fajardo
�  Dr. Richard Hathaway
�  Michael Nienhuis
�  DENSO
�  Garrett by Honeywell
•  Nathan Theiss
�  Eaton
•  Zach Tuyls
�  Ricardo PLC
� Benchmarking •  Intercooling was not used in successful designs
� Plenum •  Allows time for intake air to cool
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3000 5000 7000 9000 11000
Inta
ke
Tem
per
atu
re (°
F)
Engine Speed (RPM)
Final Design Stock Restricted
� Dual Cycle •  Partial heat addition at constant volume •  Partial heat addition at constant pressure
� Results •  33% error in peak pressures between mathematical
model and simulation �  Mathematical model does not account for heat loss.
Expansion
Compression
Constant Volume
Constant Pressure
� Waste gate controls knock by limiting intake pressure •  Exhaust gas bypasses turbine
� Knock was not detected in any simulation which included airflow restriction
� Boost ratio in simulations was 1.8 •  Turbo remained in most efficient region