WO2010000285A1 - Exploitation de l'énergie des gaz d'échappement à l'aide d'un processus de turbine à gaz ouverte - Google Patents

Exploitation de l'énergie des gaz d'échappement à l'aide d'un processus de turbine à gaz ouverte Download PDF

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Publication number
WO2010000285A1
WO2010000285A1 PCT/EP2008/005433 EP2008005433W WO2010000285A1 WO 2010000285 A1 WO2010000285 A1 WO 2010000285A1 EP 2008005433 W EP2008005433 W EP 2008005433W WO 2010000285 A1 WO2010000285 A1 WO 2010000285A1
Authority
WO
WIPO (PCT)
Prior art keywords
gas turbine
internal combustion
combustion engine
compressor
turbine
Prior art date
Application number
PCT/EP2008/005433
Other languages
German (de)
English (en)
Inventor
Stefan Pischinger
Original Assignee
Fev Motorentechnik Gmbh
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 Fev Motorentechnik Gmbh filed Critical Fev Motorentechnik Gmbh
Priority to PCT/EP2008/005433 priority Critical patent/WO2010000285A1/fr
Priority to DE112008003879T priority patent/DE112008003879A5/de
Publication of WO2010000285A1 publication Critical patent/WO2010000285A1/fr

Links

Classifications

    • 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
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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
    • 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
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • 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
    • 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
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • 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 invention relates to a method for operating an internal combustion engine, wherein the thermal energy of the exhaust gas stream is converted into mechanical power, as well as an internal combustion engine with system components for the application of the method.
  • the present invention is therefore based on the object of providing a method for utilizing the exhaust gas energy of an internal combustion engine and an internal combustion engine of the type mentioned above, which can be represented with low construction costs.
  • the solution to this problem consists in a method of operating an internal combustion engine converting thermal exhaust gas heat into mechanical power, in which the heat extracted from the exhaust gas flow is supplied to the gaseous medium of an open gas turbine process between a compressor and a gas turbine, wherein the mechanical power of the gas turbine process for Drive a work machine is used.
  • the pre-compressed gaseous medium at least temporarily heat from a combustion process in a before the
  • certain boost functions for the driven by the gas turbine engine working machine can be represented thereby easier.
  • the compressor can be coupled directly to the turbine of the gas turbine plant and driven by it. In this embodiment, the other embodiments relate.
  • Air is used as the working medium of the open gas turbine process.
  • a first process control is provided that the exhaust gas stream of the engine heat is removed behind the turbine of an exhaust gas turbocharger of the internal combustion engine and fed to the working fluid of the gas turbine process.
  • sufficient energy is available for driving the exhaust gas turbocharger in the exhaust gas line in each operating state.
  • the design changes in existing engine concepts are easier to make, since the heat exchanger of the gas turbine plant can be arranged relatively motorfem.
  • the exhaust gas stream heat can be supplied before the turbine of the exhaust gas turbocharger after the working fluid of the gas turbine process, ie the heat exchanger of the gas turbine plant must be very close to the engine, for example, integrated in the exhaust manifold.
  • This has the advantage that at full load cooling of the exhaust stream and thus a component protection of the turbine of the exhaust gas turbocharger of the internal combustion engine and the components for the exhaust aftertreatment (catalysts) takes place.
  • acceleration from partial load or similar operating conditions at low load, during idling and during coasting, heat extraction from the exhaust gas is not permitted, so that the drive and the acceleration of the exhaust gas turbocharger is not impaired.
  • the corresponding heat exchanger must be bypassed in phases by the exhaust gas or the flow of the working medium of the gas turbine plant through the heat exchanger must be interrupted in phases.
  • Appropriate control means are provided in the corresponding cable guides. This leaves sufficient energy for the drive of the exhaust gas turbocharger and thus for the undisturbed operation of the internal combustion engine available in case of need.
  • the open gas turbine process is started after a start of the internal combustion engine with foreign energy, initially there is no flow connection between the outlet side of the compressor and the inlet side of the gas turbine and this only upon reaching a starting speed of the compressor and Gas turbine is produced via the heat exchanger. This is true in any case when the compressor is driven directly by the gas turbine.
  • this starting process takes place in such a way that the heat exchanger is shut off on the working medium side before entry and after exit, so that in the heat exchanger a gas volume is preheated while the pressure is being increased.
  • the externally driven compressor can blow off the working medium on the pressure side and the turbine can suck in secondary air. Only when the compressor and turbine are at a suitable starting speed is a connection initially established from the heat exchanger to the turbine, which can then indicate a short-term mechanical power to the compressor by means of a pressure pulse from the heat exchanger; is then connected to the input side of the heat exchanger, so that sets a self-sustained gas turbine process.
  • both the inlet between the heat exchanger and turbine and the return from the compressor to the heat exchanger are not continuously connected at rest of the gas turbine plant are closed in the inlet and outlet to the heat exchanger by valves, so that the heat exchanger on its secondary side to the gas turbine process is completed and the compressor in the gas turbine process is open on both sides.
  • the heating of the gas in the heat exchanger is then waited until a sufficient pressure has built up.
  • the delay is needed to prevent the gas pressure in the heat exchanger from escaping in the wrong direction.
  • Compressor with the heat exchanger input, the speed of the turbocharger or the pressure behind the compressor can be used.
  • Compressor output can at the appropriate time with the
  • Heat exchangers are connected as soon as the pressure build-up behind the compressor exceeds the pressure in the heat exchanger.
  • a gas storage can be provided between the compressor and the turbine, which can be integrated in particular in the secondary side of the heat exchanger.
  • the power surplus of the gas turbine plant can be absorbed by a working machine in the broadest sense.
  • an electric machine can be used in the simplest way, in particular as a starter Generator may be formed, on the one hand serves as a starter for the gas turbine plant and on the other hand can run after starting in the generator mode, wherein the electrical energy can be stored in a battery.
  • Another possibility is to let the compressor drive a chiller or a heat pump from the gas turbine plant.
  • the possibility can be combined to integrate the evaporator of said chiller or heat pump in the air intake of the engine as an additional intercooler.
  • Figure 1 shows an investment scheme in the basic structure with an arranged behind the turbine of the exhaust gas turbocharger of the internal combustion engine heat exchanger of the gas turbine plant;
  • Figure 2 shows an investment scheme in the basic structure with a front of the turbine of the exhaust gas turbocharger of the internal combustion engine arranged heat exchanger of the gas turbine plant;
  • Figure 3 shows an investment scheme similar to Figure 1 with a compressor of a chiller as a consumer of the mechanical power of the gas turbine plant
  • Figure 4 shows an investment scheme similar to Figure 2 with a compressor of a chiller as a consumer of the mechanical power of the gas turbine plant.
  • FIG 1 an investment scheme is shown, which can detect an internal combustion engine 11 with an air intake line 12 and an exhaust line 13. It is a supercharged internal combustion engine with an exhaust gas turbocharger 14, the compressor 15 is located in the air intake 12 of the engine 11 and the turbine 16 is located in the exhaust line 13 of the internal combustion engine. Behind the compressor 15 of the exhaust gas turbocharger 14, a charge air cooler 17 is shown in the air intake line, which may preferably be air-cooled. Compressor 15 and turbine 16 of the exhaust gas turbocharger 14 are mechanically coupled to each other via a shaft 18.
  • It is also an open gas turbine plant 21 which includes a compressor 22 and a gas turbine 23, which are mechanically coupled via a shaft 24.
  • a wiring harness 25 connects the pressure side of the compressor 22 to the high pressure side of the gas turbine 23.
  • the compressor 22 sucks in air from the environment as the working medium.
  • the line 25 leads via a heat exchanger 26, which is located in the exhaust line 13 of the internal combustion engine 11 behind the turbine 16 of the exhaust gas turbocharger 14. In the heat exchanger 26, heat is transferred from the hot exhaust gas of the internal combustion engine 11 to the precompressed gas of the gas turbine plant in the wiring harness 25, which is relaxed after the heat supply in the heat exchanger 26 in the turbine 23 of the gas turbine plant 21 and generates an excess of power.
  • a combustion chamber 29 in the wiring harness 25 in front of the turbine 23 can serve as an option for further heat supply to the medium of the gas turbine process.
  • two valves are indicated, a blow-off and check valve 27 on the pressure side of the compressor and a secondary air and check valve 28 on the high-pressure side of the turbine. These valves 27, 28 are to open for starting the gas turbine plant 21 to the compressor and the turbine and at the same time to close before the heat exchanger and behind the heat exchanger.
  • the startup of the gas turbine plant 21 takes place with external energy via a motor 31, which via a shaft 32 with the Compressor 22 is mechanically coupled.
  • the turbine-side valve 28 When the unit of compressor and turbine is brought by means of the motor 31 to speed, the turbine-side valve 28 is first closed to the environment and opened between the heat exchanger 26 and turbine 23 with a short time offset, so that a gas burst of preheated gas from the heat exchanger causes a power output of the turbine. Shortly thereafter, the blow-off and shut-off valve 27 of the compressor is closed to the environment, thereby opening the connection between the compressor 22 and the heat exchanger 26, so that now the turbine power driven compressor maintains the gas turbine process under constant heat supply to the working fluid in the heat exchanger. The motor 31 can now receive mechanical power from the gas turbine plant during generator operation.
  • FIG. 2 shows a similar system diagram as in FIG. 1 comprising an internal combustion engine 11 and a gas turbine installation 21.
  • the heat exchanger 26 of the gas turbine plant 21 is here in the engine nearer the exhaust line 13 of the engine 11, namely in front of the turbine 16 of the exhaust gas turbocharger 14.
  • the exhaust gas temperature level is in this case in a favorable manner higher than behind the turbine of the exhaust gas turbocharger.
  • FIG. 3 shows a layout diagram which shows an internal combustion engine 11 with an air intake line 12 and an exhaust line 13. It is a supercharged internal combustion engine with an exhaust gas turbocharger 14 whose compressor 15 is located in the air intake line 12 of the internal combustion engine 11 and whose turbine 16 is located in the exhaust line 13 of the internal combustion engine 11. Behind the compressor 15 of the exhaust gas turbocharger, a charge air cooler 17 is shown in the air intake line, which may preferably be air-cooled. Compressor 15 and turbine ne 16 of the exhaust gas turbocharger 14 are mechanically coupled to each other via a shaft 18.
  • An open gas turbine plant 21 is furthermore shown, which comprises a compressor 22 and a gas turbine 23, which are mechanically coupled via a shaft 24.
  • a wiring harness 25 connects the pressure side of the compressor 22 to the high pressure side of the gas turbine 23.
  • the compressor 22 sucks in air from the environment as the working medium.
  • the line 25 leads via a heat exchanger 26, which is located in the exhaust line 13 of the internal combustion engine 11 behind the turbine 16 of the exhaust gas turbocharger 14.
  • In the heat exchanger 26 there is a heat transfer from the hot exhaust gas of the internal combustion engine 11 to the pre-compressed gas of the gas turbine plant in the wiring harness 25, which is relaxed after the heat supply in the heat exchanger 26 in the turbine 23 of the gas turbine plant 21 and generates a power surplus.
  • a combustion chamber 29 in the wiring harness 25 in front of the turbine 23 can be used as an option for further heat supply to the medium of the gas turbine process.
  • two valves are indicated, a blow-off and check valve 27 on the pressure side of the compressor and a secondary air and check valve 28 on the high-pressure side of the turbine. These valves 27, 28 are to be opened to start the Gasturbinenstrom 21 to the compressor and the turbine and at the same time to close before the heat exchanger and behind the heat exchanger.
  • the startup of the gas turbine plant 21 takes place with external energy via a motor 31, which is mechanically coupled via a shaft 32 to the compressor 22.
  • the turbine-side valve 28 When the unit of compressor and turbine is brought by the motor 31 to speed, the turbine-side valve 28 is first closed to the environment and opened between the heat exchanger 26 and turbine 23 with a short time delay, so that a gas impact of preheated gas from the heat exchanger a Power output of the turbine causes. Shortly thereafter, the blow-off and shut-off valve 27 of the compressor is closed to the environment while the connection PHg between compressor 22 and heat exchanger 26 is opened, so that now the turbine power driven compressor maintains the gas turbine process under constant heat supply to the working fluid in the heat exchanger. The motor 31 can now receive mechanical power from the gas turbine plant during generator operation.
  • the engine 31 can be decoupled from this after start-up of the gas turbine plant 21.
  • the compressor 42 of a heat pump or chiller 41 is provided in this embodiment, which has a closed coolant circuit 46 and at which the units compressor 42, condenser 43, throttle 44 and evaporator 45 can be seen.
  • the evaporator 45 is here as another charge air cooler in the air intake 12 of the engine 1 1 and thus contributes to the improvement of the process efficiency of the internal combustion engine as such.
  • FIG. 4 shows a similar system diagram as in FIG. 3, including an internal combustion engine 11 and a gas turbine plant 21.
  • the heat exchanger 26 of the gas turbine plant 21 is located closer to the engine in the exhaust line 13 of the internal combustion engine 11, namely in front of the turbine 16 of the exhaust gas turbocharger 14.
  • the exhaust gas temperature level is advantageously higher as behind the turbine of the exhaust gas turbocharger.

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

Abstract

L'invention concerne un procédé de fonctionnement d'un moteur à combustion interne 11 avec conversion de l'énergie thermique des gaz d'échappement en puissance mécanique. La chaleur provenant du flux de gaz d'échappement du moteur à combustion interne 11 est transférée à un fluide gazeux précomprimé d'un processus de turbine à gaz ouverte dans un échangeur thermique 26 monté entre un compresseur 22 et une turbine à gaz 23. La puissance mécanique du processus de turbine à gaz est fournie à une machine de travail.
PCT/EP2008/005433 2008-07-03 2008-07-03 Exploitation de l'énergie des gaz d'échappement à l'aide d'un processus de turbine à gaz ouverte WO2010000285A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/EP2008/005433 WO2010000285A1 (fr) 2008-07-03 2008-07-03 Exploitation de l'énergie des gaz d'échappement à l'aide d'un processus de turbine à gaz ouverte
DE112008003879T DE112008003879A5 (de) 2008-07-03 2008-07-03 Abgasenergienutzung mittels offenem Gasturbinenprozess

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2008/005433 WO2010000285A1 (fr) 2008-07-03 2008-07-03 Exploitation de l'énergie des gaz d'échappement à l'aide d'un processus de turbine à gaz ouverte

Publications (1)

Publication Number Publication Date
WO2010000285A1 true WO2010000285A1 (fr) 2010-01-07

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Country Status (2)

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DE (1) DE112008003879A5 (fr)
WO (1) WO2010000285A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010056238A1 (de) * 2010-12-24 2012-06-28 Audi Ag Antrieb mit einer Brennkraftmaschine und einer Expansionsmaschine mit Gasrückführung
AT510623B1 (de) * 2010-11-11 2012-09-15 Avl List Gmbh Antriebseinheit für ein fahrzeug
AT512042B1 (de) * 2010-11-11 2013-05-15 Avl List Gmbh Antriebseinheit für ein Fahrzeug
WO2013167726A2 (fr) * 2012-05-11 2013-11-14 Avl List Gmbh Véhicule, en particulier véhicule de course
US8925317B2 (en) 2012-07-16 2015-01-06 General Electric Company Engine with improved EGR system
DE102015205737A1 (de) 2015-03-30 2016-10-06 Avl List Gmbh Brennkraftmaschine mit Abgasenergienutzung und Verfahren zum Betrieb einer solchen Brennkraftmaschine
DE102015215518A1 (de) 2015-08-14 2017-02-16 Bayerische Motoren Werke Aktiengesellschaft System zur Energierückgewinnung aus dem Abgas einer Brennkraftmaschine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB813990A (en) * 1954-09-10 1959-05-27 Henschel & Sohn Ges Mit Beschr Improvements in gas turbines utilising the waste heat of internal combustion engines
DE2757236A1 (de) * 1977-12-22 1979-06-28 Porsche Ag Antriebsaggregat, insbesondere fuer kraftfahrzeuge
DE19960762A1 (de) * 1999-12-16 2001-06-28 Daimler Chrysler Ag Energiegewinnung aus der Abgaswärme eines Verbrennungsmotors

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB813990A (en) * 1954-09-10 1959-05-27 Henschel & Sohn Ges Mit Beschr Improvements in gas turbines utilising the waste heat of internal combustion engines
DE2757236A1 (de) * 1977-12-22 1979-06-28 Porsche Ag Antriebsaggregat, insbesondere fuer kraftfahrzeuge
DE19960762A1 (de) * 1999-12-16 2001-06-28 Daimler Chrysler Ag Energiegewinnung aus der Abgaswärme eines Verbrennungsmotors

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT510623B1 (de) * 2010-11-11 2012-09-15 Avl List Gmbh Antriebseinheit für ein fahrzeug
AT512042B1 (de) * 2010-11-11 2013-05-15 Avl List Gmbh Antriebseinheit für ein Fahrzeug
AT512042A4 (de) * 2010-11-11 2013-05-15 Avl List Gmbh Antriebseinheit für ein Fahrzeug
DE102010056238A1 (de) * 2010-12-24 2012-06-28 Audi Ag Antrieb mit einer Brennkraftmaschine und einer Expansionsmaschine mit Gasrückführung
US9096116B2 (en) 2010-12-24 2015-08-04 Audi Ag Drive with an internal combustion engine and an expansion machine with gas return
WO2013167726A2 (fr) * 2012-05-11 2013-11-14 Avl List Gmbh Véhicule, en particulier véhicule de course
WO2013167726A3 (fr) * 2012-05-11 2014-01-16 Avl List Gmbh Véhicule, en particulier véhicule de course
US8925317B2 (en) 2012-07-16 2015-01-06 General Electric Company Engine with improved EGR system
DE102015205737A1 (de) 2015-03-30 2016-10-06 Avl List Gmbh Brennkraftmaschine mit Abgasenergienutzung und Verfahren zum Betrieb einer solchen Brennkraftmaschine
EP3078824A1 (fr) 2015-03-30 2016-10-12 AVL List GmbH Moteur a combustion interne dote un dispositif d'utilisation de l'energie des gaz d'echappement et procede de fonctionnement d'un tel moteur a combustion interne
DE102015215518A1 (de) 2015-08-14 2017-02-16 Bayerische Motoren Werke Aktiengesellschaft System zur Energierückgewinnung aus dem Abgas einer Brennkraftmaschine

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