WO2008139302A1 - Turbocharged internal combustion engine with 'v' arrangement of the cylinders - Google Patents

Turbocharged internal combustion engine with 'v' arrangement of the cylinders Download PDF

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Publication number
WO2008139302A1
WO2008139302A1 PCT/IB2008/001150 IB2008001150W WO2008139302A1 WO 2008139302 A1 WO2008139302 A1 WO 2008139302A1 IB 2008001150 W IB2008001150 W IB 2008001150W WO 2008139302 A1 WO2008139302 A1 WO 2008139302A1
Authority
WO
WIPO (PCT)
Prior art keywords
internal combustion
combustion engine
turbocharger
exhaust
turbine
Prior art date
Application number
PCT/IB2008/001150
Other languages
French (fr)
Inventor
Nicola Pini
Mauro Rioli
Original Assignee
Ferrari, S.P.A.
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 Ferrari, S.P.A. filed Critical Ferrari, S.P.A.
Publication of WO2008139302A1 publication Critical patent/WO2008139302A1/en

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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
    • F02B37/007—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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • 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
    • F02B37/16—Control of the pumps by bypassing charging air
    • 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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F01N13/107—More than one exhaust manifold or exhaust collector
    • 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 internal combustion engine 1 is provided with two turbochargers 8, which are identical to each other and each of which comprises a turbine 9 and a compressor 10 mechanically connected to each other by means of a common shaft .
  • the function of the two turbochargers 8 is to exploit the total enthalpy of the exhaust gases which are released from the cylinder 2 during the exhaust stroke to compress the fresh air which is aspirated into the cylinders 2 during the intake stroke so as to improve the filling of the cylinders 2 themselves.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Supercharger (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

An internal combustion engine (1) displaying: two banks (3) of cylinders (2) reciprocally arranged in a 'V'- shape and each provided with a same number of cylinders (2); two exhaust manifolds (6), each of which is connected to a corresponding bank (3); two intake manifolds (4), each of which is connected to a corresponding bank (3); two turbochargers (8), which are identical to each other and each of which includes a turbine (9) and a compressor (10) mechanically connected to each other; a first exhaust channel (Ha) for connecting a first exhaust manifold (6a) to the inlet of the turbine (9) of a first turbocharger (8a); a second exhaust channel (lib) for connecting a second exhaust manifold (6b) to the inlet of the turbine (9) of a second turbocharger (8b); a first intake channel (19a) for feeding compressed fresh air to the first intake manifold (4); and a second intake channel (19b) for feeding compressed fresh air to the second intake manifold (4).

Description

TURBOCHARGED INTERNAL COMBUSTION ENGINE WITH ttV" ARRANGEMENT OF THE CYLINDERS
TECHNICAL FIELD
The present invention relates to a turbocharged internal combustion engine with "V" arrangement of the cylinders .
PRIOR ART
In the currently marketed turbocharged internal combustion engines with "V" arrangement of the cylinders, twin turbochargers are generally used, each of which is associated to a cylinder bank to be actuated by the exhaust gases produced by its cylinder bank and to compress the fresh air aspirated by its cylinder bank. The size of the turbochargers is always an accommodation between the need to use a small turbocharger to have a low mechanical inertia (and thus a prompt response to low engine speeds without the undesired response delay which is typical of large turbochargers) , and the need to use a large turbocharger to obtain a high performance increase at high engine speeds. In other words, the size of the turbochargers is always an accommodation between the need to have a high torque at low engine speeds (i.e. a small turbocharger) and the need to have high power and torque at maximum engine speeds (large turbocharger) .
In order to attempt to solve the above-described problem, i.e. in order to attempt to have both a high torque at low engine speeds and high power and torque at maximum engine speeds, it has been suggested the use of two turbochargers (or a volumetric compressor and a turbocharger) for each bank: a small-sized turbocharger which is mostly used at low engine speeds and a large- sized turbocharger which is mostly used at high engine speeds. However, this solution is expensive and, above all, very cumbersome and thus difficult to be used except in vehicles provided with a very large engine compartment .
Some examples of turbocharged internal combustion engines with "V" arrangement of the cylinders are disclosed in patent applications US2007056281A1 and DE10015291A1.
DESCRIPTION OF THE INVENTION
It is the object of the present invention to provide a turbocharged internal combustion engine with "V" arrangement of the cylinders, which engine is easy and cost-effective to make and free from the aforesaid drawbacks .
According to the present invention, a turbocharged internal combustion engine with "V" arrangement of the cylinders is made as set forth in the appended claims.
BRIEF DESCRIPTION OF THE DRAWING
The present invention will now be described with reference to the accompanying drawing, which illustrates a non-limitative embodiment thereof; specifically, the accompanying figure is a diagrammatic view of a turbocharged internal combustion engine with "V" arrangement of the cylinders made in accordance with the present invention.
PREFERRED EMBODIMENTS OF THE INVENTION
In figure 1, numeral 1 indicates as a whole an internal combustion engine comprising eight cylinders 2 arranged in two banks 3 which are "V" -arranged and reciprocally form a 90° angle. According to a different embodiment (not shown) , the engine 1 comprises a different number of cylinders 2 (e.g. six, ten or twelve) and/or the angle between the two banks 3 is different from 90°.
The internal combustion engine 1 comprises two intake manifolds 4, each of which is connected to a corresponding bank 3 to feed fresh air to the cylinders 2 of the bank 3 by means of four intake pipes 5 adjusted by corresponding intake valves (not shown) . Furthermore, the internal combustion engine 1 comprises two exhaust manifolds 6, each of which is connected to a corresponding bank 3 to receive the exhaust gases from the cylinders 2 of the bank 3 by means of four exhaust pipes 6 adjusted by corresponding exhaust valves (not shown) .
The internal combustion engine 1 is provided with two turbochargers 8, which are identical to each other and each of which comprises a turbine 9 and a compressor 10 mechanically connected to each other by means of a common shaft . The function of the two turbochargers 8 is to exploit the total enthalpy of the exhaust gases which are released from the cylinder 2 during the exhaust stroke to compress the fresh air which is aspirated into the cylinders 2 during the intake stroke so as to improve the filling of the cylinders 2 themselves.
An exhaust channel 11a connects the exhaust manifold 6a to the inlet of the turbine 9 of the turbocharger 8a and an exhaust channel lib connects the exhaust manifold 6b to the inlet of the turbine 9 of the turbocharger 8b. The outlet of the turbines 9 of the two turbochargers 8 is connected to an exhaust system 12 to introduce the exhaust gases produced by the combustion into the atmosphere. According to the embodiment shown in the accompanying figure, the exhaust system 12 comprises two catalyzers 13 each of which receives the exhaust gases from a turbine 9 of a corresponding turbocharger 8; preferably, an interconnection pipe 14, which connects the inlets of the two catalyzers 13 to each other, is provided. According to a different embodiment (not shown), a single catalyzer 13, which receives the exhaust gases from both the turbines 9 of the two turbochargers 8, is comprised.
The inlets of the compressors 10 of the two turbochargers 8 receive the fresh air by means of two feeding pipes 15 provided with corresponding filters 16. Two flow rate sensors (normally air-mass meters) are preferably arranged along the feeding pipes 15 immediately downstream of the filters 16 to detect the flow rate of fresh air which flows through the feeding pipes 15.
A distribution pipe 18 is provided, which distribution pipe receives compressed fresh air from both the compressors 10 of the two turbochargers 8 and feeds the compressed fresh air to the two intake manifolds 4 by means of two corresponding intake channels 19. A corresponding intercooler 20 is preferably arranged along each intake channel 19 for cooling the fresh air which is fed to the cylinders 2. Furthermore, a butterfly valve 21 is arranged along each intake channel 19 immediately upstream of the corresponding intake manifold 4; alternatively, a butterfly valve 21 could be provided for each cylinder 2.
An interconnection pipe 22 is comprised, which interconnection pipe connects the two exhaust channels 11 to each other so that the exhaust gases produced by both the banks 3 can be fed either to both the turbines 9 of the two turbochargers 8, or only to the turbine 9 of the turbocharger 8a. A shut-off valve 23 is arranged upstream (according to an embodiment, not shown) or downstream (according to the embodiment shown in the accompanying figure) of the turbine 9 of the turbocharger 8b, which shut-off valve is closed to interrupt the flow of exhaust gases through the turbine 9 of the turbocharger 8b. A further shut-off valve 24 is arranged along the feeding pipe 15b immediately upstream of the compressor 10 of the turbocharger 8b, which shut- off valve is closed to interrupt the flow of fresh air through the compressor 10 of the turbocharger 8b; alternatively, the shut-off valve 24 could be arranged immediately downstream of the compressor 10 of the turbocharger 8b .
According to a preferred embodiment, a bypass pipe 25 which connects the inlet and the outlet of the compressor 10 of the turbocharger 8b, and a bypass valve, which is arranged along the bypass pipe 25 and is opened to make the compressor 10 of the turbocharger 8b idle, are provided.
In order to detect the composition of the exhaust gases produced by the combustion and thus to be able to control the internal combustion engine 1, an exhaust gas probe 27 (an ON/OFF lambda probe or a UEGO lambda probe) is provided arranged along the interconnection pipe 22 and two exhaust gas probes 28 are provided, each of which is arranged downstream of a turbine 9 of a corresponding turbocharger 8.
According to a preferred embodiment shown in the accompanying figure, the exhaust manifolds 6 and the two turbochargers 8 are arranged inside the "V" formed by the two banks 3; alternatively, the exhaust manifolds 6 and the two turbochargers 8 could be arranged outside the "V" formed by the cylinders banks 3 on opposite sides of the two banks 3 themselves. It is important to note that the arrangement of the turbochargers 8 in the centre of the "V" (i.e. inside the "V" formed by the two banks 3) highly simplifies the arrangement of all the connection pipes and control valves making the installation in the vehicle much simpler.
The operation of the internal combustion engine 1 is described below.
At low engine speeds, the shut-off valve 23 is closed to interrupt the flow of exhaust gases through the turbine 9 of the turbocharger 8b; consequently, the exhaust gases produced in the cylinders 2 of the bank 3a and in the cylinders 2 of the bank 3b flow together through the turbine 9 of the turbocharger 8a. Specifically, not being able to flow through the turbine 9 of the turbocharger 8b, the exhaust gases produced in the cylinders 2 of the bank 3b are forced to pass through the interconnection pipe 22 which connects the two exhaust channels to each other. When the shut-off valve 23 is closed, the shut-off valve 24 is also closed in order to prevent the pressurized fresh air pumped by the compressor 10 of the turbocharger 8a from flowing back in an opposite direction through the compressor 10 of the turbocharger 8b and thus along the feeding pipe 15b.
At high engine speeds, the shut-off valves 23 and 24 are opened so that the exhaust gases produced in the cylinders 2 of the bank 3a rotate the turbine 9 of the turbocharger 8a and the exhaust gases produced in the cylinders 2 of the bank 3b rotate the turbine 9 of the turbocharger 8b; consequently, both compressors 10 of the two turbochargers 8 compress the fresh air aspirated from the outside and feed the compressed fresh air to the intake channels 19 through the distribution pipe 18.
As soon as the shut-off valve 23 is opened, the bypass valve 25 is also opened for a short start-up time. In this manner, the compressor 10 of the turbocharger 8b initially idles until it reaches a speed (and thus a compression capacity) equal to that of the turbocharger 8a; once the compressor 10 of the turbocharger 8b has reached a speed (and thus a compression capacity) equal to that of the turbocharger 8a, the bypass valve 25 is closed, the shut-off valve 24 is opened, and the compressor 10 of the turbocharger 8b starts feeding compressed fresh air to the intake channels 19. Due to the intervention of the bypass valve 25, the intervention of the turbocharger 8b is prevented from determining a temporary pressure drop of the compressed air fed to the intake channels 19 and thus a temporary pressure drop of the drive torque generated by the internal combustion engine 1.
When the shut-off valves 23 and 24 are closed, the interconnection pipe 14 which connects the inlets of the two catalyzers 13 to each other ensures that the exhaust gases also flow through the catalyzer 13b (which without the interconnection pipe 14 would remain otherwise unused) thus maintaining the catalyzer 13b at a constant temperature (i.e. preventing the catalyzer 13b from excessively cooling down and loosing its efficiency) .
From the above it is apparent that only the turbocharger 8a works at low engine speeds, while at high engine speeds both the turbochargers 8 work; in this manner, the turbochargers 8 always work with an exhaust gas flow rate which is comparable to the nominal flow rate and thus display both a prompt response (i.e. free from appreciable intervention delays), and a high compression capacity (i.e. ensuring a high increase of maximum torque and maximum power) .
The engine 1 described above displays many advantages because it is simple and cost-effective to make and above all displays both a high torque at low engine speeds, and high power and torque at maximum engine speeds. Furthermore, in virtue of the fact of using two reciprocally identical turbochargers 8, it is simpler to arrange the turbochargers 8 inside a small- sized engine compartment.

Claims

1. An internal combustion engine (1) comprising: two banks (3) of cylinders (2) arranged reciprocally in a "V"-shape and each comprising a same number of cylinders (2); two exhaust manifolds (6), each of which is connected to a corresponding bank (3); two intake manifolds (4) , each of which is connected to a corresponding bank (3); two turbochargers (8), each of which comprises a turbine (9) and a compressor (10) mechanically connected to each other; a first exhaust channel (Ha) for connecting a first exhaust manifold (6a) to the inlet of the turbine (9) of a first turbocharger (8a) ; a second exhaust channel (lib) for connecting a second exhaust manifold (6b) to the inlet of the turbine (9) of a second turbocharger (8b); a first intake channel (19a) for feeding compressed fresh air to the first intake manifold (4) ; and a second intake channel (19b) for feeding compressed fresh air to the second intake manifold (4); the internal combustion engine (1) is characterized in that it comprises: a first interconnection pipe (22) which connects the two exhaust channels (11) to each other; a distribution pipe (18) which receives the compressed fresh air from both the compressors (10) of the two turbochargers (8) and feeds the compressed fresh air to the two intake channels (19); and a first shut-off valve (21), which is arranged either upstream or downstream of the turbine (9) of the second turbocharger (8b) and is closed to interrupt the flow of exhaust gases through the turbine (9) of the second turbocharger (8b) .
2. An internal combustion engine (1) according to claim 1 and comprising a second shut-off valve (24) , which is arranged either upstream or downstream of the compressor (10) of the second turbocharger (8b) and is closed to interrupt the flow of fresh air through the compressor (10) of the second turbocharger (8b) .
3. An internal combustion engine (1) according to claim 2 and comprising: a bypass pipe (25) , which connects the inlet and the outlet of the compressor (10) of the second turbocharger (8b) ; and a bypass valve (26), which is arranged along the bypass pipe (25) and is opened to make the compressor (10) of the second turbocharger (8b) idle.
4. An internal combustion engine (1) according to claim 1, 2 or 3 and comprising a single catalyzer which receives the exhaust gases from both the turbines (9) of the two turbochargers (8 ) .
5. An internal combustion engine (1) according to claim 1, 2 or 3 and comprising two catalyzers (13), each of which receives the exhaust gases from a turbine (9) of a corresponding turbocharger (8) .
6. An internal combustion engine (1) according to claim 1, 2 or 3 and comprising a second interconnection pipe (14) which connects the inlets of the two catalyzers (13) to each other.
7. An internal combustion engine (1) according to any one of the claims from 1 to 6 and comprising a first probe (27) of the exhaust gases arranged along the first interconnection pipe (22) .
8. An internal combustion engine (1) according to any one of the claims from 1 to 7 and comprising two second probes (28) of the exhaust gases, each of which is arranged downstream of a turbine (9) of a corresponding turbocharger (8) .
9. An internal combustion engine (1) according to any one of the claims from 1 to 8 and comprising two intercoolers (20) , each of which is arranged along a corresponding intake channel (19).
10. An internal combustion engine (1) according to any one of the claims from 1 to 9 and comprising two butterfly valves (21), each of which is arranged along a corresponding intake channel (19) immediately upstream of the corresponding intake manifold (4) .
11. An internal combustion engine (1) according to any one of the claims from 1 to 10, wherein the exhaust manifolds (6) and the two turbochargers (8) are arranged inside the "V" formed by the two banks (3) .
12. An internal combustion engine (1) according to any one of the claims from 1 to 10, wherein the exhaust manifolds (6) and the two turbochargers (8) are arranged outside the "V" formed by the two banks (3) on opposite sides of the two banks (3) themselves.
13. An internal combustion engine (1) according to any one of the claims from 1 to 12, wherein the two turbochargers (8) are identical the each other.
PCT/IB2008/001150 2007-05-11 2008-05-09 Turbocharged internal combustion engine with 'v' arrangement of the cylinders WO2008139302A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000352A ITBO20070352A1 (en) 2007-05-11 2007-05-11 TURBOCHARED INTERNAL COMBUSTION MOTOR WITH "V" ARRANGEMENT OF THE CYLINDERS
ITBO2007A000352 2007-05-11

Publications (1)

Publication Number Publication Date
WO2008139302A1 true WO2008139302A1 (en) 2008-11-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2008/001150 WO2008139302A1 (en) 2007-05-11 2008-05-09 Turbocharged internal combustion engine with 'v' arrangement of the cylinders

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IT (1) ITBO20070352A1 (en)
WO (1) WO2008139302A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2472830A (en) * 2009-08-20 2011-02-23 Gm Global Tech Operations Inc Automotive twin turbo system with bypassable compressor(s)
GB2529540B (en) * 2014-07-09 2019-01-30 Porsche Ag Forced induction device for a combustion engine, combustion engine and method for operating a combustion engine
CN111164297A (en) * 2017-12-04 2020-05-15 宝马股份公司 Internal combustion engine, motor vehicle having such an internal combustion engine, and method for operating an internal combustion engine
US10690052B2 (en) 2017-05-19 2020-06-23 GM Global Technology Operations LLC Turbocharger assembly

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63309726A (en) * 1987-06-10 1988-12-16 Yanmar Diesel Engine Co Ltd Exhaust gas treatment device for internal combustion engine with exhaust turbosupercharger
DE19835978C1 (en) * 1998-08-08 1999-11-25 Daimler Chrysler Ag Motor vehicle twin turbocharger internal combustion engine with exhaust gas recycling
JP2001012234A (en) * 1999-06-30 2001-01-16 Fuji Heavy Ind Ltd Exhaust system of engine with supercharger
US20020056444A1 (en) * 2000-10-05 2002-05-16 Etsuo Chou Air-supplying structure for multi-cylinder engine
EP1316698A1 (en) * 2001-11-29 2003-06-04 Renault s.a.s. Device and method of supercharging an internal combustion engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63309726A (en) * 1987-06-10 1988-12-16 Yanmar Diesel Engine Co Ltd Exhaust gas treatment device for internal combustion engine with exhaust turbosupercharger
DE19835978C1 (en) * 1998-08-08 1999-11-25 Daimler Chrysler Ag Motor vehicle twin turbocharger internal combustion engine with exhaust gas recycling
JP2001012234A (en) * 1999-06-30 2001-01-16 Fuji Heavy Ind Ltd Exhaust system of engine with supercharger
US20020056444A1 (en) * 2000-10-05 2002-05-16 Etsuo Chou Air-supplying structure for multi-cylinder engine
EP1316698A1 (en) * 2001-11-29 2003-06-04 Renault s.a.s. Device and method of supercharging an internal combustion engine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2472830A (en) * 2009-08-20 2011-02-23 Gm Global Tech Operations Inc Automotive twin turbo system with bypassable compressor(s)
US8615999B2 (en) 2009-08-20 2013-12-31 GM Global Technology Operations LLC Twin turbo assembly and method for operating a twin turbo assembly
GB2472830B (en) * 2009-08-20 2014-12-17 Gm Global Tech Operations Inc Twin turbo assembly and method for operating a twin turbo assembly
GB2529540B (en) * 2014-07-09 2019-01-30 Porsche Ag Forced induction device for a combustion engine, combustion engine and method for operating a combustion engine
US10690052B2 (en) 2017-05-19 2020-06-23 GM Global Technology Operations LLC Turbocharger assembly
CN111164297A (en) * 2017-12-04 2020-05-15 宝马股份公司 Internal combustion engine, motor vehicle having such an internal combustion engine, and method for operating an internal combustion engine
US11199143B2 (en) 2017-12-04 2021-12-14 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine, motor vehicle comprising same, and method for operating an internal combustion engine

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