2.2mahle downsizing 14-may-2010 gasgoo
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MAHLE
The MAHLE Downsizing Engine
High Performance and Low Fuel Consumption
Written by: Volker Korte, Grant Lumsden, Neil Fraser,
Jonathan Hall;
Presented by: Paul WARD
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Contents
Introduction
Targets
Engine Design
Engine Development
Results and Outlook
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Introduction
Maximising fuel economy and thereby minimising CO2 emissions are among the most importantobjectives for the future development of engines and vehicles.
MAHLE have recently designed and built an engine to demonstrate the application of aggressivedownsizing to gasoline engines in order to improve operating efficiency.
A robust combustion system that allows a high compression ratio to maintain part loadefficiency
Good low speed torque and transient performance
Real world fuel consumption benefits through a reduction in full load fuel enrichment
Base engine robustness and durability
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Targets
The targets were to produce an engine capable of replacing a typical 2.4l V6 PFi engine used ina C or D class European vehicle platform (circa 1600 kg). The engine would be compliant withEU5 / ULEV2 emissions from conception.
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Engine Design
The main engine design parameters
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Engine Design
The main engine design parameters
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Engine Design
Cylinder Head and Combustion Chamber
Tumble inlet ports
Centrally mounted direct injector for spray-guided operation
Cooling around the injector tip
Compact chamber with low surface area
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Engine Design
Air Path and Charging System
High degree of integration The air filter, mass air flow meter and charge cooler
Aluminium charge cooler
Light-weight plastic inlet manifold are, boost levels > 2.8 bar
Cooled exhaust gas recirculation (EGR)
The two-stage system is shown schematically
EGR valve
EGR cooler
Charge
aircooler
Compressor
bypass
HP stage
TurbineBypass Valve
LP stageTurbine
Wastegate
C
C T
T
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> 2.8 bar
ERG
EGR valve
EGR cooler
Charge
aircooler
Compressor
bypass
HP stage
TurbineBypass Valve
LP stageTurbine
Wastegate
C
C T
T
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Engine Design
Cylinder Block and Crank Case
Aluminium bedplate
MAHLE Nikasil parent bore
Through bolting system for cylinder head and block
Piston cooling with feed via separate non filtered oil channel direct from oil pump controlgallery
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MAHLE Nikasil
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Engine Design
Crank Train, Valve Train and Balancer System
Balancer system comprises two crank-driven plastic gears carrying the balance weights
Forged aluminium pistons
A ring pack with two compression rings and a 3-piece oil-scraper ring
DLC coated piston pins
Forged steel conrods
A steel crankshaft
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DLC
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Engine Development
High Load Combustion System
Optimisation of compression ratio and combustion chamber
Optimisation of ignition timing and cam phasing,
Combustion system development
Turbocharger configuration
Piezo injectors in a spray-guided concept
Fuel injection timing,
Fuel pressure (at part load between 100 and 200 bar)
Fuel injection strategy (single or double injection per cycle)
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Engine Development
High Load Combustion System
Example of Camshaft Position Optimization for WOT Performance at3000 rpm (Results at BLD Spark Timing, l = 1.0)
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3000 rpm
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Engine Development
Two-Stage Boosting System
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Engine Development
Two-Stage Boosting System
Initial investigations with single turbochargers have been carried out to define suitableturbine/compressor configurations.
TC01 max. flow 0.06 m3/s
TC02 max. flow 0.09 m3/s
TC03 max. flow 0.14 m3/s
TC04 max. flow 0.16 m3/s
TC01 and TC04 were chosen for testing in
two-stage configuration.
Th MAHLE D i i E i
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TC01 max. flow 0.06 m3/s
TC02 max. flow 0.09 m3/s
TC03 max. flow 0.14 m3/s
TC04 max. flow 0.16 m3/s
TC01 TC04
Th MAHLE D i i E i
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Engine Development
Two-Stage Boosting System
The compressor maps for the TC01 and TC04 plotted together
TC01/TC04 Compressor Maps with Characteristics for approx. 20 30 bar BMEP at 1,500rpm & 2,500 rpm
The MAHLE Do nsi ing Engine
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TC01 TC04
TC01/TC04 . 20 30 bar BMEP 1,500 rpm 2,500 rpm
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Engine Development
Two-Stage Boosting System
Provides a useful improvement in apparent volumetric efficiency
The reduced pre-turbine pressures drive the improved combustion phasing at a givenBMEP
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Engine Development
Transient Response
Transient behaviour is key for the acceptance of downsizing concepts by the customer.
Results of a load step from 2 bar BMEP to WOT at 1,250 rpm
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2 bar BMEP to WOT at 1,250 rpm
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Engine Development
Air Fuel Ratio Engine Map
The objective to operate the engine at l = 1 at all speeds and loads
Objective achieved, except around peak power, without the use of EGR
The maximum exhaust gas temperature has been limited to 1,020 C.
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l = 1
EGR
1,020 C
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Engine Development
Engine Mechanics and Friction
Higher valve-train losses (exhaust spring loads in particular) are the main cause of thesmall disadvantage at low speed.
The good result at medium and high engine speed is due to the very low power-cell frictionof the MAHLE downsizing engine
The effects of 3 vs. 4 cylinders,
Latest technology crank shaft bearings
Short stroke design
Very good bore roundness
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g g
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g g
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Results and Outlook
Torque and Power Output at WOT Targets Achieved
Torque at n = 1,000 rpm Md = 153 Nm 153 Nm(BMEP = 16 bar) 16 bar
Max. Torque (n = 3,000 rpm) Md = 286 Nm 287 Nm(BMEP = 30 bar) 30 bar
Max. Power (n = 6,000 rpm) Pe = 144 Kw 144 kW(Pe/VH = 120 kW/l)
Brake Specific Fuel Consumption Targets Achieved
Optimum be < 235 g/kWh 234 g/kWh
n= 2000 rpm, 4 bar BMEP be < 300 g/kWh 285 g/kWh
Torque[Nm]
0
50
100
150
200
250
300
Engine Speed [rpm]
0 1000 2000 3000 4000 5000 6000 7000
Po
wer[kW]
0
30
60
90
120
150
180
TargetsTorque (2-stage turbo)Power (2-stage turbo)
BM
EP[bar]
0
5
10
15
20
25
30
35
Engine Speed [rpm]
1000 2000 3000 4000 5000 6000
325300
300
300
275
275
250
250
234
285
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n = 1,000 rpm Md = 153 Nm 153 Nm(BMEP = 16 bar) 16 bar
(n = 3,000 rpm) Md = 286 Nm 287 Nm(BMEP = 30 bar) 30 bar
(n = 6,000 rpm) Pe = 144 Kw 144 kW(Pe/VH = 120 kW/l)
be < 235 g/kWh 234 g/kWh
n= 2000 rpm, 4 bar BMEP be < 300 g/kWh 285 g/kWh
Torque[Nm]
0
50
100
150
200
250
300
Engine Speed [rpm]
0 1000 2000 3000 4000 5000 6000 7000
Po
wer[kW]
0
30
60
90
120
150
180
TargetsTorque (2-stage turbo)Power (2-stage turbo)
BM
EP[bar]
0
5
10
15
20
25
30
35
Engine Speed [rpm]
1000 2000 3000 4000 5000 6000
325300
300
300
275
275
250
250
234
285
375
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Next steps
Simulation of the vehicle fuel economy in the NEDC (kerb weight m 1,600 kg).
This results in an improvement of fuel consumption and CO2 emission of up to 30%
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NEDC m 1,600 kg
30%
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Summary
Targets achieved
Peak power
Peak torque
Low Speed torque
BSFC
Next Step
Vehicle test
Thank-You
Contacts for further information:
Paul WARD
+86 159 2160 1669
Shouping CHEN
+86 138 1722 8830
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39MAHLE Powertrain Ltd. MAHLE
Contacts for further information:
Paul WARD
+86 159 2160 1669
Shouping CHEN
+86 138 1722 8830