analysis of sequential turbocharger systems for diesel engines · analysis of sequential...
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Analysis of Sequential Turbocharger Systems for Diesel EnginesRob Stalman, Vanco Smiljanowski, Uwe Späder,Ford Research & Advanced Europe
October 24th 2011, Ford Forschungszentrum Aachen GmbH, All rights reserved
Contents:
• Introduction & motivation• Comparison of Sequential Turbocharging Systems• Switching of a parallel sequential system• Summary
Page 2 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Contents:
• Introduction & motivation• Comparison of Sequential Turbocharging Systems• Switching of a parallel sequential system• Summary
Page 3 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Specific Power of Passenger Car Diesel Engines in Europe.
0
10
20
30
40
50
60
70
80
90
100
1930 1940 1950 1960 1970 1980 1990 2000 2010 2020
Year [-]
Spec
ific
Pow
er [k
W/l]
Page 4
Introduction
Naturally AspiratedTurbochargedTurbocharged & IntercooledSequential Systems
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Page 5
Introduction
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
0 50 100 150 200 250 3000
5
10
15
20
25
30
-80% PM
-56% NOx -28% NOx
EU6 EU5
PM
[mg/
km]
EU4
NOx [mg/km]
Contents:
• Introduction & motivation• Comparison of Sequential Turbocharging Systems• Switching of a parallel sequential system• Summary
Page 6 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Page 7
Sequential Boosting Systems Layout
TC1 TC2
CompressorRecirc Valve
TC1
TC2
TurbineBypass Valve
CompressorBypass Valve
TurbineShutoff Valve
wastegate
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Series SequentialParallel Sequential
Page 8
Sequential Boosting Systems Layout
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Series SequentialParallel Sequential
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07.11.2006
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Massenstrom
Compressor 2Compressor 1Pr
essu
re ra
tio
Pres
sure
ratio
Mass flow Mass flow
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Compressor Maps – Parallel Sequential
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07.11.2006
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Massenstrom
Compressor 2Compressor 1
Full load –single turbo
first operating pointparallel (twin turbo)
first operating pointparallel (twin turbo)
Pres
sure
ratio
Pres
sure
ratio
Mass flow Mass flow
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Compressor Maps – Parallel Sequential
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20.11.2006
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Massenstrom
Compressor 2Compressor 1
20.11.2006
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Massenstrom
Full loadparallel
Full loadparallel
Pres
sure
ratio
Pres
sure
ratio
Mass flow Mass flow
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Compressor Maps – Parallel Sequential
Compressor Maps – Series Sequential
02.11.200602.11.200602.11.200602.11.200602.11.2006
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MassenstromC:\users\hkindl\CTI\2stufig2.ipw 02.11.200602.11.200602.11.200602.11.200602.11.2006
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MassenstromC:\users\hkindl\CTI\2stufig2.ipw02.11.200602.11.200602.11.200602.11.200602.11.2006
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MassenstromC:\users\hkindl\CTI\2stufig2.ipw02.11.200602.11.200602.11.200602.11.200602.11.2006
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Pres
sure
ratio
Mass flow
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Page 13
Single VNTSeries SequentialSeries Sequential + VNTParallel Sequential
1000 4000
Torq
ue
Engine Speed
Application with lowest weight
FTP75 & US06
Full Load Performance & Emissions Range
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Comparison• Package:
– Series Sequential general has a very big TC2 which is a challenge to package.
– Parallel Sequential is more compact and flexible to package.– All are more complex to package than single VNT.
• Aftertreatment / Emissions:– Series sequential turbine side has a high thermal inertia that impacts
temperature available for the aftertreatment system..– The boosting systems in general compete for the same package space as
parts of the aftertreatment system. This can lead to unfavourable compromises.
• Transient & driveability:– Both sequential systems have better transient behaviour than single VNT – Parallel has slightly better transient behaviour.– Series Sequential is more suited to extend engine rpm range
Page 14 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Comparison
• Fuel economy over NEDC slightly better for parallel sequential• Longer design lead time for complex boosting systems, special care
must be taken in case of series sequential. Series Sequential usually involves a big exhaust manifold casting including one of the turbine stages, requiring design effort
• Turbine side valves are critical for both (leakage, DP, response, robustness).
• Both systems cost more than a single VNT.• Mode switching performance critical.
– Mode switch of parallel sequential discrete, serial sequential much more smooth
– Switching with EGR?
Page 15 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Contents:
• Introduction & motivation• Comparison of Sequential Turbocharging Systems• Switching of a parallel sequential system• Summary
Page 16 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Page 17
2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4
0
20
40
60
80
100Open
Turbine shut-off valve
Para
met
er [%
]
Time [sec]
Closed
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Parallel Sequential Switching - Valves
Page 18
2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4
0
20
40
60
80
100Open
Turbine shut-off valve Compressor bypass valve Recirculation valve
Para
met
er [%
]
Time [sec]
Closed
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Parallel Sequential Switching - Valves
Page 19
2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4
0
20
40
60
80
100Open
Turbine shut-off valve Compressor bypass valve Recirculation valve Turbine VNT position
Para
met
er [%
]
Time [sec]
Closed
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Parallel Sequential Switching - Valves
Page 20
2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4
0
20
40
60
80
100Open
Turbine shut-off valve Compressor bypass valve Recirculation valve Turbine VNT position
Dashed: measured signals
Para
met
er [%
]
Time [sec]
Closed
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Parallel Sequential Switching - Valves
Page 21
time [s]2.00 2.20 2.40 2.60 2.80 3.00
Torq
ue, P
ress
ure
(rel)
[%]
30
40
50
60
70
80
90
100
110
Torque Boost Pressure Pressure ds TC1 Pressure ds TC2
Sign
al [%
]
-10
10
30
50
70
90
110
VT2 VNT Position Compressor Shut Off Valve Recirculation Valve
TC s
peed
[rpm
]
0
60000
120000
180000
240000
Speed TC1 Speed TC2
time [s]2.00 2.20 2.40 2.60 2.80 3.00
Torq
ue, P
ress
ure
(rel)
[%]
30
40
50
60
70
80
90
100
110
Torque Boost Pressure Pressure ds TC1 Pressure ds TC2
Sign
al [%
]
-10
10
30
50
70
90
110
VT2 VNT Position Compressor Shut Off Valve Recirculation Valve
TC s
peed
[rpm
]
0
60000
120000
180000
240000
Speed TC1 Speed TC2
time [s]2.00 2.20 2.40 2.60 2.80 3.00
Torq
ue, P
ress
ure
(rel)
[%]
30
40
50
60
70
80
90
100
110
Torque Boost Pressure Pressure ds TC1 Pressure ds TC2
Sign
al [%
]
-10
10
30
50
70
90
110
VT2 VNT Position Compressor Shut Off Valve Recirculation Valve
TC s
peed
[rpm
]
0
60000
120000
180000
240000
Speed TC1 Speed TC2
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Parallel Sequential Switching - Measured
Page 22
Switch from single turbo to biturbo, high partload, measured. Video courtesy of L. Bartsch
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Parallel Sequential Switching - Measured
Contents:
• Introduction & motivation• Comparison of Sequential Turbocharging Systems• Switching of a parallel sequential system• Summary
Page 23 GT Power User Conference 2011, Rob Stalman, Ford R&A Europe
Page 24
• Both Parallel Sequential and Series Sequential offer the potential to increase specific power and torque, with Series Sequential more suitable for engine rpm increase.
• This increase can either be used to increase performance or allow downsizing.
• Both systems face a number of constraints: – package– cost– complexity
• High thermal inertia is a risk for series sequential• “Step-wise” switching poses a challenge for parallel sequential• Correct system choice depends entirely on the application (In-Line
or V-engine, vehicle, duty cycle etc....)
Summary
GT Power User Conference 2011, Rob Stalman, Ford R&A Europe