WO2001009495A1 - Turbocharger - Google Patents

Turbocharger Download PDF

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Publication number
WO2001009495A1
WO2001009495A1 PCT/GB2000/002913 GB0002913W WO0109495A1 WO 2001009495 A1 WO2001009495 A1 WO 2001009495A1 GB 0002913 W GB0002913 W GB 0002913W WO 0109495 A1 WO0109495 A1 WO 0109495A1
Authority
WO
WIPO (PCT)
Prior art keywords
turbocharger
stage
turbine
bypass valve
turbocharging
Prior art date
Application number
PCT/GB2000/002913
Other languages
French (fr)
Inventor
Brian Horner
Original Assignee
Alliedsignal Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alliedsignal Limited filed Critical Alliedsignal Limited
Priority to AU62998/00A priority Critical patent/AU6299800A/en
Publication of WO2001009495A1 publication Critical patent/WO2001009495A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a turbocharger for an internal combustion engine, particularly a sequential turbocharger .
  • turbocharger The performance of a turbocharger can be improved, and specifically its efficient operating range can be widened, by incorporating a variable geometry device, as is well known in this technical field.
  • variable geometry device As is well known in this technical field.
  • Such devices are complex and expensive.
  • turbochargers can be used to provide improved performance if two (or more) are arranged to be brought into operation sequentially to produce a variable capacity system.
  • performance of a sequential turbocharger under certain operating conditions is poor, in both the steady state and in transient performance, because a discontinuity occurs during switching from single to twin turbocharger operation, and back. This discontinuity appears in the steady state when the second turbocharger switches in, and also in the transient state as the second turbocharger accelerates up to operating speed.
  • turbocharging arrangement comprising a first stage and a second stage turbocharger, the first and second stages being arranged to operate in sequence, the first stage turbocharger comprising a turbine having a turbine bypass valve.
  • a bypass valve is otherwise known as a wastegate.
  • the size of the bypass valve is chosen to produce a smooth transition from single to twin turbocharger operation.
  • the gas bypassing the first stage turbine is used to accelerate the second stage turbocharger turbine during a load/speed change. This has the effect of reducing, and preferably negating, the transient discontinuity.
  • Electronic control of the diverted gas is preferable but the bypass valve or wastegate can be controlled by the pressure generated by the turbocharger compressor.
  • a turbocharging arrangement can result in improved steady state output from the engine over a wide operating range . It can also result in smoother changeovers from one to two turbocharger operation and reduce, or eliminate, the transient drop m air supply when the second turbocharger is switched in.
  • Figure 1 is a graph illustrating the performance of turbocharging arrangements according to the prior art and according to the present invention
  • Figure 2 is a schematic illustration of a turbocharging arrangement according to the prior art, operating at low engine load/speed, in the steady state;
  • Figure 3 is a schematic illustration of a turbocharging arrangement according to the present invention, operating at low to medium engine load/speed, in the steady state;
  • Figure 4 is a schematic illustration of a turbocharging arrangement according to the prior art operating at medium to high engine load/speed, in the steady state;
  • Figure 5 is a schematic illustration of a turbocharging arrangement according to a first embodiment of the invention operating full engine load/speed, in the steady state;
  • FIG. 6 is a schematic illustration of a turbocharging arrangement according to a second embodiment of the invention, in the transient state.
  • the turbocharger compressor output shown as "Engine Boost Pressure” is plotted against engine load/speed.
  • Three graphs are shown:
  • a single stage turbocharger according to the prior art .
  • a turbocharging arrangement according to the present invention.
  • graph C i.e. that according to the present invention, illustrates the more effective turbocharger of the three shown in Figure 1.
  • the engine boost pressure rises quickly and smoothly with engine load/speed.
  • Figure 2 illustrates a conventional turbocharging arrangement operating at low engine load/speed and thus with only one of the two turbochargers operating.
  • the turbochargers are shown schematically at 1 and 2, and are connected in parallel . Air intake through the compressor Cl of the first turbocharger 1, passes through valve 3 to become the air inlet 4 to engine 5. Exhaust gas
  • valve 7 to the turbine inlet Tl of turbo charger 1 and is expelled.
  • valves 3 At low engine load/speed turbocharger 2 is not operating because valves 3,
  • Turbocharger 2 is therefore idle because no gas is diverted to it .
  • the operation is thus equivalent to a single small turbine turbocharger and the performance graph is the first segment of line B (before point X) in Figure 1.
  • FIG. 3 illustrates a turbocharging arrangement according to one aspect of the present invention, operating at low to medium engine load/speeds.
  • This has a conventional wastegate first stage turbocharger 1, to allow some pressure release to atmosphere.
  • Turbocharger 1 is wastegated by means of bypass valve 8 operating to divert some of the exhaust gas away from the outlet Tl of turbocharger 1 to atmosphere .
  • bypass valve 8 At low to medium engine loads/speeds only first stage turbocharger 1 is operating but some of the exhaust gas is diverted by bypass valve 8 to outlet valve 9, and hence to atmosphere.
  • Figure 4 illustrates a typical prior art arrangement for a sequential turbocharger, as the engine load/speed increases to medium to high.
  • valve 7 switches mode so that it operates to divert some of the exhaust gas coming from engine exhaust 6 to turbine Tl of turbocharger
  • FIG. 5 illustrates the operation of turbochargers arranged according to the first aspect of the present invention operating at full engine speed. Both turbochargers 1 and 2 are brought into operation since valve
  • turbocharger 1 via bypass valve 8 and to turbine T2 of turbocharger 2.
  • turbocharger 1 is operating in wastegated mode because valve 9 allows gas to exit to atmosphere as shown by the arrows. This effectively smooths the transition between single turbocharger operation and twin turbocharger operation and thus provides the smoother curve shown at C in Figure 1.
  • FIG. 6 illustrates a second embodiment of the present invention at transient load/speed change. Initially turbocharger 1 is in full operation but turbocharger 2 is idle. As engine load, or speed increase is required, valve
  • control of the bypass valve or wastegate 8 on the first stage turbocharger 1 has the effect of controlling the boost pressure of both single and two-stage operation and reduces the steady state discontinuity or "hole" .
  • the size of the wastegate passage must be matched to both turbine housings for optimum performance .
  • the short-term direction of wastegate bypass gas into the second stage turbocharger prior to operation of the second stage turbocharge causes the second turbine to accelerate up to speed before the unit is fully switched in. This reduces the discontinuity for transient operation .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Abstract

A turbocharging arrangement comprises a first stage (1) and a second stage (2) turbocharger, the first and second stages being arranged to operate in sequence, the first stage turbocharger comprising a turbine having a turbine bypass valve (8), or a wastegate. The size of the bypass valve (8) is chosen to produce a smooth transition from single to twin turbocharger operation. The gas bypassing the first stage turbine (T1) is used to accelerate the second stage turbocharger turbine (T2) during a load/speed change. This has the effect of reducing, and preferably negating, the transient discontinuity. Electronic control of the diverted gas is preferable but the bypass valve or wastegate can be controlled by the pressure generated by the turbocharger compressor. Improved steady state output is seen from the engine over a wide operating range.

Description

TURBOCHARGER DESCRIPTION
The present invention relates to a turbocharger for an internal combustion engine, particularly a sequential turbocharger .
The performance of a turbocharger can be improved, and specifically its efficient operating range can be widened, by incorporating a variable geometry device, as is well known in this technical field. However such devices are complex and expensive.
Conventional turbochargers can be used to provide improved performance if two (or more) are arranged to be brought into operation sequentially to produce a variable capacity system. However the performance of a sequential turbocharger under certain operating conditions is poor, in both the steady state and in transient performance, because a discontinuity occurs during switching from single to twin turbocharger operation, and back. This discontinuity appears in the steady state when the second turbocharger switches in, and also in the transient state as the second turbocharger accelerates up to operating speed.
It is an object of the present invention to provide a sequential turbocharging arrangement with improved performance and a smoother changeover. According to the present invention there is provided a turbocharging arrangement comprising a first stage and a second stage turbocharger, the first and second stages being arranged to operate in sequence, the first stage turbocharger comprising a turbine having a turbine bypass valve. A bypass valve is otherwise known as a wastegate.
The size of the bypass valve is chosen to produce a smooth transition from single to twin turbocharger operation.
According to a preferred embodiment of the present invention the gas bypassing the first stage turbine is used to accelerate the second stage turbocharger turbine during a load/speed change. This has the effect of reducing, and preferably negating, the transient discontinuity. Electronic control of the diverted gas is preferable but the bypass valve or wastegate can be controlled by the pressure generated by the turbocharger compressor.
However, electronic control is particularly preferred in transient mode to optimise performance.
A turbocharging arrangement according to the present invention can result in improved steady state output from the engine over a wide operating range . It can also result in smoother changeovers from one to two turbocharger operation and reduce, or eliminate, the transient drop m air supply when the second turbocharger is switched in.
For a better understanding of the present invention, and to show how the same may be carried into effect, reference will now be made to the accompanying drawings, in whic :
Figure 1 is a graph illustrating the performance of turbocharging arrangements according to the prior art and according to the present invention;
Figure 2 is a schematic illustration of a turbocharging arrangement according to the prior art, operating at low engine load/speed, in the steady state;
Figure 3 is a schematic illustration of a turbocharging arrangement according to the present invention, operating at low to medium engine load/speed, in the steady state;
Figure 4 is a schematic illustration of a turbocharging arrangement according to the prior art operating at medium to high engine load/speed, in the steady state;
Figure 5 is a schematic illustration of a turbocharging arrangement according to a first embodiment of the invention operating full engine load/speed, in the steady state;
Figure 6 is a schematic illustration of a turbocharging arrangement according to a second embodiment of the invention, in the transient state. In Figure 1, the turbocharger compressor output, shown as "Engine Boost Pressure" is plotted against engine load/speed. Three graphs are shown:
A. A single stage turbocharger, according to the prior art .
B. A sequential turbocharging arrangement, according to the prior art .
C. A turbocharging arrangement, according to the present invention.
It will be seen that graph C, i.e. that according to the present invention, illustrates the more effective turbocharger of the three shown in Figure 1. The engine boost pressure rises quickly and smoothly with engine load/speed.
With a single stage turbocharger (graph A) the engine boost pressure rises smoothly with engine load/speed but the gradient is rather low, indicating poor performance.
Using a sequential turbocharger as in graph B provides a faster rise of the engine boost pressure with engine load/speed but there is a discontinuity at X where the second turbocharger switches in, and this has an adverse effect on both steady state and transient performance of the turbocharger .
However these problems are reduced in the arrangement of the present invention as seen by graph C. Figure 2 illustrates a conventional turbocharging arrangement operating at low engine load/speed and thus with only one of the two turbochargers operating.
The turbochargers are shown schematically at 1 and 2, and are connected in parallel . Air intake through the compressor Cl of the first turbocharger 1, passes through valve 3 to become the air inlet 4 to engine 5. Exhaust gas
6 from the engine 5 passes through valve 7 to the turbine inlet Tl of turbo charger 1 and is expelled. At low engine load/speed turbocharger 2 is not operating because valves 3,
7 and 8 are configured in uni-directional mode, as indicated by the arrows. Turbocharger 2 is therefore idle because no gas is diverted to it . The operation is thus equivalent to a single small turbine turbocharger and the performance graph is the first segment of line B (before point X) in Figure 1.
Figure 3 illustrates a turbocharging arrangement according to one aspect of the present invention, operating at low to medium engine load/speeds. This has a conventional wastegate first stage turbocharger 1, to allow some pressure release to atmosphere. Turbocharger 1 is wastegated by means of bypass valve 8 operating to divert some of the exhaust gas away from the outlet Tl of turbocharger 1 to atmosphere . At low to medium engine loads/speeds only first stage turbocharger 1 is operating but some of the exhaust gas is diverted by bypass valve 8 to outlet valve 9, and hence to atmosphere.
Figure 4 illustrates a typical prior art arrangement for a sequential turbocharger, as the engine load/speed increases to medium to high.
At a medium engine load/speed, the valve 7 switches mode so that it operates to divert some of the exhaust gas coming from engine exhaust 6 to turbine Tl of turbocharger
1 via bypass valve 8, and some to turbine T2 of turbocharger
2. Thus both turbochargers 1 and 2 are operating sequentially, in parallel. However, as is seen from graph B in Figure 1, the point at which valve 7 switches to divert mode and turbocharger 2 starts operation, causes the discontinuity X, which is detrimental to engine performance.
Figure 5 illustrates the operation of turbochargers arranged according to the first aspect of the present invention operating at full engine speed. Both turbochargers 1 and 2 are brought into operation since valve
7 diverts exhaust gases to both turbine Tl of turbocharger
1 via bypass valve 8 and to turbine T2 of turbocharger 2. However, in this embodiment, turbocharger 1 is operating in wastegated mode because valve 9 allows gas to exit to atmosphere as shown by the arrows. This effectively smooths the transition between single turbocharger operation and twin turbocharger operation and thus provides the smoother curve shown at C in Figure 1.
Figure 6 illustrates a second embodiment of the present invention at transient load/speed change. Initially turbocharger 1 is in full operation but turbocharger 2 is idle. As engine load, or speed increase is required, valve
9 directs the wastegated gas from valve 8 to turbine T2 of turbocharger 2. In" this way the gas is used to bring turbine T2 of turbocharger 2 up to speed, in readiness for the next steady state phase, i.e. the operation of both turbochargers 1 and 2 as shown in Figure 5.
Thus it will be seen that control of the bypass valve or wastegate 8 on the first stage turbocharger 1 has the effect of controlling the boost pressure of both single and two-stage operation and reduces the steady state discontinuity or "hole" . The size of the wastegate passage must be matched to both turbine housings for optimum performance .
In addition, the short-term direction of wastegate bypass gas into the second stage turbocharger prior to operation of the second stage turbocharge, causes the second turbine to accelerate up to speed before the unit is fully switched in. This reduces the discontinuity for transient operation .

Claims

1. A turbocharging arrangement comprising a first stage (1) and a second stage turbocharger, the first and second stages being arranged to operate in sequence, the first stage turbocharger (1) comprising a turbine (Tl) having a turbine bypass valve (8) .
2. A turbocharging arrangement according to claim 1 wherein the size of the bypass valve (8) is chosen to produce a smooth transition from single to twin turbocharger operation.
3. A turbocharging arrangement according to claim 1 or 2 arranged so that the gas bypassing the first stage turbine (Tl) is used to accelerate the second stage turbocharger turbine (T2) during a load/speed change.
4. A turbocharging arrangement according to any preceding claim comprising means to effect electronic control of the diverted gas .
5. A turbocharging arrangement according to any one of claims 1 to 3 wherein the bypass valve is controlled by the pressure generated by the turbocharger compressor.
PCT/GB2000/002913 1999-07-30 2000-07-28 Turbocharger WO2001009495A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU62998/00A AU6299800A (en) 1999-07-30 2000-07-28 Turbocharger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB9918070.5A GB9918070D0 (en) 1999-07-30 1999-07-30 Turbocharger
GB9918070.5 1999-07-30

Publications (1)

Publication Number Publication Date
WO2001009495A1 true WO2001009495A1 (en) 2001-02-08

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GB (1) GB9918070D0 (en)
WO (1) WO2001009495A1 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1291505A3 (en) * 2001-09-06 2003-11-05 Caterpillar Inc. Turbocharger with controllable wastegate for two stage turbine
FR2915240A1 (en) * 2007-04-20 2008-10-24 Peugeot Citroen Automobiles Sa SUPER-POWER SYSTEM COMPRISING TWO TURBOCHARGERS AND A BI-PERMEABILITY VALVE
DE102007028522A1 (en) * 2007-06-21 2008-12-24 Ford Global Technologies, LLC, Dearborn Method for operating turbocharged internal combustion engine, involves discharging exhaust gas mass flow, where two exhaust pipes are provided, and two exhaust gas turbo chargers are connected parallel to one another
DE10314583B4 (en) * 2002-04-08 2009-01-22 General Motors Corp. (N.D.Ges.D. Staates Delaware), Detroit Engine with on-demand turbocharger and cylinder deactivation
DE102007046655A1 (en) * 2007-09-28 2009-04-09 Audi Ag Internal-combustion engine operating method for motor vehicle, involves supplying exhaust gases through valve of turbocharger, and temporarily closing exhaust gas-bypass during change-over of speed of engine from low to high engine-speed
DE102008048681A1 (en) * 2008-09-24 2010-04-22 Audi Ag Internal combustion engine with two loaders and method for operating the same
CN102251887A (en) * 2011-06-14 2011-11-23 哈尔滨工程大学 Air intake pressure stabilizing device of sequential supercharged diesel engine and control method thereof
US8490395B2 (en) 2004-12-14 2013-07-23 Borgwarner Inc. Turbine regulating valve system
US9074521B2 (en) 2012-03-21 2015-07-07 Ford Global Technologies, Llc Turbocharger system having a shared bypass conduit and wastegate

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3906729A (en) * 1974-03-25 1975-09-23 Caterpillar Tractor Co Multiple turbocharger system
GB2005765A (en) * 1977-10-12 1979-04-25 Daimler Benz Ag Supercharged multicylinder four-stroke internal combustion engine
US5020327A (en) * 1988-03-19 1991-06-04 Mazda Motor Corporation Air supply control systems for turbocharged internal combustion engines
US5197287A (en) * 1989-08-31 1993-03-30 Mazda Motor Corporation Exhaust control system for engine with turbochargers
US5408979A (en) * 1990-05-15 1995-04-25 Ab Volvo Method and a device for regulation of a turbo-charging device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3906729A (en) * 1974-03-25 1975-09-23 Caterpillar Tractor Co Multiple turbocharger system
GB2005765A (en) * 1977-10-12 1979-04-25 Daimler Benz Ag Supercharged multicylinder four-stroke internal combustion engine
US5020327A (en) * 1988-03-19 1991-06-04 Mazda Motor Corporation Air supply control systems for turbocharged internal combustion engines
US5197287A (en) * 1989-08-31 1993-03-30 Mazda Motor Corporation Exhaust control system for engine with turbochargers
US5408979A (en) * 1990-05-15 1995-04-25 Ab Volvo Method and a device for regulation of a turbo-charging device

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1291505A3 (en) * 2001-09-06 2003-11-05 Caterpillar Inc. Turbocharger with controllable wastegate for two stage turbine
DE10314583B4 (en) * 2002-04-08 2009-01-22 General Motors Corp. (N.D.Ges.D. Staates Delaware), Detroit Engine with on-demand turbocharger and cylinder deactivation
US8490395B2 (en) 2004-12-14 2013-07-23 Borgwarner Inc. Turbine regulating valve system
FR2915240A1 (en) * 2007-04-20 2008-10-24 Peugeot Citroen Automobiles Sa SUPER-POWER SYSTEM COMPRISING TWO TURBOCHARGERS AND A BI-PERMEABILITY VALVE
WO2008139105A1 (en) * 2007-04-20 2008-11-20 Peugeot Citroën Automobiles SA Supercharging system including two turbochargers and a dual permeability valve
DE102007028522A1 (en) * 2007-06-21 2008-12-24 Ford Global Technologies, LLC, Dearborn Method for operating turbocharged internal combustion engine, involves discharging exhaust gas mass flow, where two exhaust pipes are provided, and two exhaust gas turbo chargers are connected parallel to one another
DE102007046655A1 (en) * 2007-09-28 2009-04-09 Audi Ag Internal-combustion engine operating method for motor vehicle, involves supplying exhaust gases through valve of turbocharger, and temporarily closing exhaust gas-bypass during change-over of speed of engine from low to high engine-speed
DE102007046655B4 (en) 2007-09-28 2019-01-17 Audi Ag Method for operating an internal combustion engine
DE102008048681A1 (en) * 2008-09-24 2010-04-22 Audi Ag Internal combustion engine with two loaders and method for operating the same
DE102008048681B4 (en) * 2008-09-24 2019-08-08 Audi Ag Internal combustion engine with two loaders and method for operating the same
CN102251887A (en) * 2011-06-14 2011-11-23 哈尔滨工程大学 Air intake pressure stabilizing device of sequential supercharged diesel engine and control method thereof
US9074521B2 (en) 2012-03-21 2015-07-07 Ford Global Technologies, Llc Turbocharger system having a shared bypass conduit and wastegate

Also Published As

Publication number Publication date
GB9918070D0 (en) 1999-10-06
AU6299800A (en) 2001-02-19

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