GB2088964A - Dual Turbine Turbo Charger - Google Patents

Dual Turbine Turbo Charger Download PDF

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Publication number
GB2088964A
GB2088964A GB8039549A GB8039549A GB2088964A GB 2088964 A GB2088964 A GB 2088964A GB 8039549 A GB8039549 A GB 8039549A GB 8039549 A GB8039549 A GB 8039549A GB 2088964 A GB2088964 A GB 2088964A
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GB
United Kingdom
Prior art keywords
turbine
turbocharger
scroll
housing
dual
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
GB8039549A
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Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to GB8039549A priority Critical patent/GB2088964A/en
Priority to FR8027088A priority patent/FR2496761A1/en
Priority to DE3100107A priority patent/DE3100107A1/en
Publication of GB2088964A publication Critical patent/GB2088964A/en
Withdrawn legal-status Critical Current

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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
    • F02B37/12—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
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/023—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines the working-fluid being divided into several separate flows ; several separate fluid flows being united in a single flow; the machine or engine having provision for two or more different possible fluid flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Supercharger (AREA)

Abstract

A dual turbine turbo-supercharger for an engine comprising a first turbine wheel 34 and a second turbine wheel 36 mounted on a common shaft in a dual scroll turbine housing for receiving exhaust gases. The twin turbines are isolated from each other by a partition 40 separating the dual scrolls of the turbine housing. The scrolls begin as separate inlet ports for connection to isolated exhaust gas discharge systems. <IMAGE>

Description

SPECIFICATION Dual Turbine Turbo-supercharger This invention relates to turbocharger systems and more particularly relates to multiple turbocharger systems.
Internal combustion engines are frequently equipped with turbo-superchargers to provide a boost in horsepower. However, the boost and usefulness of the turbocharger is usually limited to a very narrow range of engine speeds. The turbine section of the turbo-supercharger essentially depends upon exhause gas volume and exhaust gas pressure to drive the centrifugal compressor portion, more commonly referred to as the supercharger.
Conventional turbochargers have a very limited operational efficiency range that limits their maximum effectiveness to approximately 25% of the range of an engine's RPM capability. This means that it is possible to select a turbine size that will function well within a narrow band of an engine's total RPM range. Thus, a small turbine will function well at low engine speeds (RPM); Whereas, a large one will not function at all at these speeds. Conversely, a large turbine will function well at high engine speeds (RPM), while a small turbine, though able to function with a low volume of exhaust gases provided by an engine at low speeds, will produce excessive back pressure at high engine RPM. In fact a small turbine can actually be detrimental to engine performance at higher RPM, so much so that the engine at times can perform better in that range without the turbocharger.The large turbine, though it would not produce high back pressure at high engine speed, is conditionally inefficient because it simply will operate very little or not at all with the low volume of exhaust gas available at low engine speeds.
As the air flow requirements of a turbosupercharged engine increase, more turbine power must be provided in order to rotate the centrifugal compressor to meet the increased flow requirements. One traditional method of accomplishing this is to allow the exhaust gas pressure that is entering the turbine to increase proportionately. Consequently, numerous turbocharger arrangement have been devised to alleviate the problems. Examples of devices used to alleviate this problem are systems with two completely separate turbochargers or the use of a dual scroll with a single turbine wheel.
However, these devices necessarily result in complex configurations requiring sophisticated control systems and have not been particularly effective in specialized vehicle applications. The disadvantage of the present dual scroll turbines used in conjunction with dual exhaust systems to increase efficiency is that although they have separate inlets, they direct the exhaust gas flow through a common annular space to react against a single turbine wheel. This allows normally isolated engine exhaust gas streams to partially react against each other, thereby decreasing engine breathing efficiency.This defeats the purpose of isolated exhaust manifolds to prevent interference at overlap events. (An overlap event occurs when both intake and exhaust valves are opened simultaneously in the same cylinder.) Exhaust gas that initially leaves the cylinder when an exhaust valve opens is at high pressure and flows at high velocity. The flow that exists when an exhaust valve is closing and intake is opening referred to as an overlap event is at low pressure and low velocity. With some of the prior art systems, highpressure events are not isolated from low-pressure events, allowing exhaust gas reversion.
The purpose of the present invention is to provide the advantages of a small-size turbine and a large-size turbine in a single turbocharger.
In order to broaden the operational range of a turbocharger, two turbines are employed to drive a single centrifugal compressor in the present invention. The turbines are preferably mounted on a common shaft with each turbine possessing a totally isolated housing. The twin turbocharger of the present invention can be particularly advantageous when used with the diverter valve disclosed and described in U.S. Patent No.
3,559,397, issued February 2, 1971, to the inventor of the present invention. One turbine receives the total exhaust gas output from the engine and the flow to the second turbine is prevented by the diverter valve of the above patent. The diverter valve is kept in the single turbine mode until the exhaust gas pressure to operate the turbine becomes excessive. Then it is shifted to a dual turbine operation, thereby extending the engine's range of efficient turbocharger operation. With the twin turbine concept of the present invention, turbine wheel area is doubled in order to increase turbine power without increasing the back pressure.
Simply stated, when double the turbine area is provided to drive the centrifugal compressor, double the power is available. An additional advantage of the twin turbine concept of the present invention is that it allows total isolation of the twin exhaust gas systems for an engine.
When the turbocharger is operating in a twin turbine mode, half the engine cylinders are connected to the inlet port feeding one turbine, while the other half of the cylinders are connected to the inlet port feeding the second turbine.
The separation of the exhaust systems is according to firing order as is the customary practice in high-efficiency, normally aspirated engines. This arrangement in some ways is actually more important to a turbocharged engine than to a normally aspirated engine. The significance of trying to minimize the back pressure is to prevent re-entry of exhaust gas into cylinders that are at the overlap event described above, where both an intake and exhaust valve are opened simultaneously in the same cylinder.
In the preferred construction of a twin turbine turbocharger of the present invention a dual scroll with separate inlets is provided for isolating the dual turbines from each other. The dual turbines include dual turbine wheels mounted on a common shaft in each scroll of the turbocharger housing with a partition isolating the turbine wheels. Thus, back-to-back dual turbines are mounted in a housing attached to a common shaft for operating the usual centrifugal compressor with the diverter valve of the patent identified hereinabove. A single turbine is operated at low RPM providing efficient operation with moderate back pressure, while at higher RPM, the divertervalve delivers the exhaust gases separately to each turbine to increase the turbine power without increasing the back pressure.
Thus, with both turbine wheels being driven by isolated exhaust gas systems, double the turbine area is provided to drive the centrifugal compressor and double the power is available.
An embodiment of the invention will now be described, by way of example, with reference to the accompanying drawings, in which like parts are identified by like numbers throughout, and in which: Figure 1 is a fragmentary view of an internal combustion engine exhaust system connected by a diverter valve to the twin turbine turbocharger of the invention.
Figure 2 is a view of the twin turbine turbocharger of the present invention taken at 2-2 of Figure 1.
Figure 3 is a sectional view of the twin turbine turbocharger of the present invention taken at 3-3 of Figure 2.
Figure 4 is a sectional view illustrating the operation of the twin turbine turbocharger in the single turbine mode.
Figure 5 is a sectional view illustrating the operation of the twin turbine turbocharger in the dual turbine mode.
The twin turbine turbocharger is shown in Figure 1 at 10 connected to the exhaust manifold 12 of the usual internal combustion engine by means of a diverter valve 14. Preferably the diverter valve 14 is the supercharger control mechanism described and disclosed in U.S.
patent No. 3,559,397, issued February 2, 1971 to the same inventor of the invention disclosed herein. The exhaust system 12 is a split-exhaust system comprised of manifolds 16 and 18 to keep high-pressure events isolated from low-pressure events reducing the possibility of exhaust gas reversion.
The twin turbine turbocharger of the present invention is illustrated in Figures 2 and 3. The turbocharger is comprised of a housing 20 having dual scrolls 22 and 24 with exhaust inlet ports 26 and 28. Exhaust from scroll 24 exits from port 30 while exhaust from scroll 22 exits from port 32 (Figure 2). Dual turbine wheels 34 and 36 are mounted on a common turbine shaft 38. The twin turbines are isolated from each other by means of a split partition comprised of semi-circular plates 40 and 42 fitting around shaft 38 and held in place by annular groove 44 of scroll housing 22 and 24. The partition plates 40 and 42-are held in place by means of bolts 46 attaching scroll housing 24 to scroll housing 22.
A centrifugal compressor wheel 52 is attached to the forward end of turbine shaft 38 passing through bearing housing 48 which includes a conical heat shield or deflector 50 protecting bearings for shaft 38. Compressor wheel 52 is connected to the forward end of the turbocharger shaft 38 by means of nut 54. Lubricating ports 56 and 58 on bearing housing 48 provide lubrication by circulating oil through the bearings of the turbocharger. Such lubrication systems are conventional in the art and details of such are not necessary to this invention.
The operation of the twin turbine of the present invention is illustrated in Figures 4 and 5. It should be noted that in both these figures the twin turbine turbocharger of the present invention is connected to the internal combustion engine exhaust system through a diverter control mechanism disclosed in the patent referred to above, but may be connected directly to the engine exhaust. While use of the diverter control mechanism shown is preferred, the system will operate more efficiently than prior dual scrolls without the diverter valve because the totally isolated dual turbine turbocharger still will have an advantage over the conventional dual housing single-turbine type, or the multiple turbine system.
For low RPM operation, the dual turbine turbocharger will operate as illustrated in Figure 4. The twin turbine turbocharger will be connected to the engine exhaust system 12 by means of diverter control valve 14. When the manifold pressure is below a predetermined minimum pressure, the spring 60 of the diverter valve 14 biases the spindle 62 to the left in Figure 4 so that valve member 66 seats, closing off the passageway 68 from passageway 70. At this time the valve member 74 is displaced from its seat, connecting passageway 70 to passageway 72.
Passageway 72 is connected to exhaust manifold 1 6 while passageway 70 is connected to exhaust manifold 18. With the diverter valve 14 in the position shown in Figure 4, all of the exhaust gases are diverted to scroll 22 against turbine wheel 34 for driving the centrifugal compressor wheel 52.
When the exhaust manifold pressure rises above the predetermined minimum pressure, the diaphragm 76 is caused to move against the spring pressure 60 to move the spindle 62 to the position shown in Figure 5. In this position the valve 74 is seated while the valve member 66 is open, connecting passageway 68 to passageway 70, while closing off passageway 70 from passageway 72. In this mode, exhaust gases from manifold 1 6 are directed into scroll 22 of turbine 10 driving turbine wheel 34, while exhaust gases from manifold 1 8 pass through passageways 70 and 68 into scroll 24, driving turbine wheel 36.
Thus, the twin turbines are being separateiy driven to operate centrifugal compressor wheel 52. The turbine area is thus doubled, increasing turbine power without increasing turbine back pressure. With double the turbine area provided to drive the centrifugal compressor wheel, double the power is available. With the dual-turbine concept of the present invention, distinct advantages over dual-turbine types with or without the diverter valve are provided.
Obviously, many modifications and variations of the present invention are possible in light of the above teachings. It is therefore to be understood that the full scope of the invention is not limited to the details disclosed herein but may be practiced otherwise than as specifically described and within the scope of the accompanying claims.

Claims (12)

Claims
1. A turbocharger for internal combustion engines, comprising a housing, connecting me suns on said housing for connecting said turbocharger to a manifold, a first turbine in said housing, a second turbine in said housing, and separating means separating said first turbine from said second turbine.
2. A turbocharger according to claim 1 wherein said housing includes a dual split scroll for said first and second turbines.
3. A turbocharger according to claim 2 wherein said connecting means includes separate inlets to each side of said split scroll for connecting said turbocharger to isolated sections of said manifold.
4. A turbocharger according to claim 2 or 3 wherein said separating means comprising an isolating partition between said dual scrolls.
5. A turbocharger according to claim 1 wherein said first and second turbines comprise a shaft, a first turbine wheel on said shaft, a second turbine wheel on said shaft, and a turbine scroll surrounding said first and second turbines.
6. A turbocharger according to claim 5 wherein said turbine scroll is a split scroll whereby said separating means separates each side of said split scroll.
7. A turbocharger according to claim 6 wherein said separating means comprises an isolating partition between said turbine wheels separating said split scrolls.
8. A turbocharger system comprising a housing, a pair of turbines in said housing for driving a centrifugal compressor, connecting means for connecting said turbocharger to a manifold, and valve means for selectively valving the flow from said manifold to one or both of said turbines.
9. A turbocharger system according to claim 8 wherein said pair of turbines comprises a pair of turbine wheels on a single output shaft.
10. A turbocharger system according to claim 9 including a dual split scroll in said housing with one half of said scroll associated with each turbine wheel.
11. A turbocharger system according to claim 10 including means for isolating each half of said dual scroll thereby isolating each turbine wheel.
12. A turbocharger according to claim 11 wherein said means for isolating each half of the scroll comprises an isolating partition between the turbine wheels.
1 3. A turbocharger for internal combustion engines substantially as hereinbefore described with reference to the accompanying drawings.
GB8039549A 1980-12-10 1980-12-10 Dual Turbine Turbo Charger Withdrawn GB2088964A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
GB8039549A GB2088964A (en) 1980-12-10 1980-12-10 Dual Turbine Turbo Charger
FR8027088A FR2496761A1 (en) 1980-12-10 1980-12-19 TURBOCHARGER FOR INTERNAL COMBUSTION ENGINES
DE3100107A DE3100107A1 (en) 1980-12-10 1981-01-03 Turbocharger for internal combustion engines

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB8039549A GB2088964A (en) 1980-12-10 1980-12-10 Dual Turbine Turbo Charger
FR8027088A FR2496761A1 (en) 1980-12-10 1980-12-19 TURBOCHARGER FOR INTERNAL COMBUSTION ENGINES
DE3100107A DE3100107A1 (en) 1980-12-10 1981-01-03 Turbocharger for internal combustion engines

Publications (1)

Publication Number Publication Date
GB2088964A true GB2088964A (en) 1982-06-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB8039549A Withdrawn GB2088964A (en) 1980-12-10 1980-12-10 Dual Turbine Turbo Charger

Country Status (3)

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DE (1) DE3100107A1 (en)
FR (1) FR2496761A1 (en)
GB (1) GB2088964A (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0349211A1 (en) * 1988-06-29 1990-01-03 Isuzu Motors Limited Exhaust-driven electric generator system for internal combustion engines
WO1991007577A1 (en) * 1989-11-22 1991-05-30 Geoffrey Kershaw Multiple turbocharging
GB2253881A (en) * 1989-11-22 1992-09-23 Geoffrey Kershaw Multiple turbocharging
EP1541832A1 (en) 2003-11-28 2005-06-15 Renault s.a.s. Turbocharger having two turbine wheels
GB2427248A (en) * 2005-06-16 2006-12-20 Malcolm George Leavesley Turbocharger apparatus having a bearing housing with an integral heat shield
CN105986883A (en) * 2015-03-02 2016-10-05 北京汽车动力总成有限公司 Supercharging device of engine and turbocharged engine
GB2545942A (en) * 2015-12-30 2017-07-05 Dongfeng Commercial Vehicle Company Ltd Double channel power turbine system and control method thereof
CN107002552A (en) * 2014-12-12 2017-08-01 博格华纳公司 With the exhaust turbine supercharger for bypass valve and the combined adjusting device of flowing connection

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3838149A1 (en) * 1988-11-10 1990-05-17 Daimler Benz Ag Supercharging system for an internal combustion engine
DE102013216608B4 (en) * 2013-08-22 2017-05-11 Ford Global Technologies, Llc Exhaust turbo-charged internal combustion engine comprising a compressor with two impellers
DE102014215844B4 (en) 2013-08-22 2022-03-17 Ford Global Technologies, Llc Turbocharged internal combustion engine with radial turbine and grouped cylinders and method for operating such an internal combustion engine
FR3029567B1 (en) * 2014-12-05 2018-07-27 Peugeot Citroen Automobiles Sa COMPACT TURBOCHARGER FOR MOTOR VEHICLE THERMAL MOTOR

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0349211A1 (en) * 1988-06-29 1990-01-03 Isuzu Motors Limited Exhaust-driven electric generator system for internal combustion engines
WO1991007577A1 (en) * 1989-11-22 1991-05-30 Geoffrey Kershaw Multiple turbocharging
GB2253881A (en) * 1989-11-22 1992-09-23 Geoffrey Kershaw Multiple turbocharging
EP1541832A1 (en) 2003-11-28 2005-06-15 Renault s.a.s. Turbocharger having two turbine wheels
GB2427248A (en) * 2005-06-16 2006-12-20 Malcolm George Leavesley Turbocharger apparatus having a bearing housing with an integral heat shield
GB2427248B (en) * 2005-06-16 2010-10-06 Malcolm George Leavesley Turbocharger apparatus having a bearing housing with an integral heat shield
JP2017537259A (en) * 2014-12-12 2017-12-14 ボーグワーナー インコーポレーテッド Exhaust gas turbocharger with bypass valve and combined regulator for flow connection
CN107002552A (en) * 2014-12-12 2017-08-01 博格华纳公司 With the exhaust turbine supercharger for bypass valve and the combined adjusting device of flowing connection
DE112015005540B4 (en) * 2014-12-12 2020-12-10 Borgwarner Inc. Exhaust gas turbocharger with combined setting device for bypass valve and flow connection
US10941699B2 (en) 2014-12-12 2021-03-09 Borgwarner Inc. Exhaust gas turbocharger with combined adjustment device for bypass valve and flow connection
CN105986883A (en) * 2015-03-02 2016-10-05 北京汽车动力总成有限公司 Supercharging device of engine and turbocharged engine
CN105986883B (en) * 2015-03-02 2019-10-25 北京汽车动力总成有限公司 A kind of supercharging device and turbocharged engine of engine
GB2545942A (en) * 2015-12-30 2017-07-05 Dongfeng Commercial Vehicle Company Ltd Double channel power turbine system and control method thereof
DE102016111540B4 (en) * 2015-12-30 2018-08-02 Dongfeng Commercial Vehicle Company Limited Dual-channel drive turbine system and its control method
GB2545942B (en) * 2015-12-30 2019-04-03 Dongfeng Commercial Vehicle Company Ltd Double flow passage power turbine system and control method thereof

Also Published As

Publication number Publication date
FR2496761B3 (en) 1983-10-28
DE3100107A1 (en) 1982-08-12
FR2496761A1 (en) 1982-06-25

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