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EP2205841A1 - Internal combustion engine comprising an exhaust-gas turbocharger and a charge-air cooler - Google Patents

Internal combustion engine comprising an exhaust-gas turbocharger and a charge-air cooler

Info

Publication number
EP2205841A1
EP2205841A1 EP08802450A EP08802450A EP2205841A1 EP 2205841 A1 EP2205841 A1 EP 2205841A1 EP 08802450 A EP08802450 A EP 08802450A EP 08802450 A EP08802450 A EP 08802450A EP 2205841 A1 EP2205841 A1 EP 2205841A1
Authority
EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
wastegate
turbine
exhaust
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.)
Ceased
Application number
EP08802450A
Other languages
German (de)
French (fr)
Inventor
Dirk Hagelstein
Jens Kühlmeyer
Eckhard Pult
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volkswagen AG
Original Assignee
Volkswagen AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=40200725&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2205841(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Volkswagen AG filed Critical Volkswagen AG
Publication of EP2205841A1 publication Critical patent/EP2205841A1/en
Ceased legal-status Critical Current

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
    • 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
    • F02B29/0437—Liquid cooled heat exchangers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10006—Air intakes; Induction systems characterised by the position of elements of the air intake system in direction of the air intake flow, i.e. between ambient air inlet and supply to the combustion chamber
    • F02M35/10026—Plenum chambers
    • F02M35/10032—Plenum chambers specially shaped or arranged connecting duct between carburettor or air inlet duct and the plenum chamber; specially positioned carburettors or throttle bodies with respect to the plenum chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/1015—Air intakes; Induction systems characterised by the engine type
    • F02M35/10157—Supercharged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10242—Devices or means connected to or integrated into air intakes; Air intakes combined with other engine or vehicle parts
    • F02M35/10268—Heating, cooling or thermal insulating means
    • 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 an internal combustion engine, in particular of a motor vehicle, with a suction pipe in a fresh air system, which opens into intake passages in a cylinder head of the internal combustion engine, an exhaust system and an exhaust gas turbocharger, a turbine arranged in the exhaust system and driven by the turbine in the fresh air system wherein the turbine has a wastegate passage for bypassing the exhaust gas past a turbine wheel of the turbine, wherein in the wastegate channel, a wastegate valve for selectively opening and closing the wastegate channel is arranged, wherein an electric actuator for actuating the wastegate valve is provided, wherein in the fresh air system downstream of the compressor, a charge air cooler is arranged, according to the preamble of patent claim 1.
  • turbocharged turbochargers with rigid geometry and wastegate control are predominantly used in turbocharged gasoline engines, since here the widespread use of the VTG technology (adjustable turbine geometry) for diesel applications is due above all to the high costs associated with the significantly higher exhaust gas temperatures compared to the Diesel are, stand in the way. For price-sensitive applications, the turbo-charged gasoline engine will therefore also have rigid geometry ATL and wastegate control in the future.
  • the demand on the wastegate actuator is derived from the fact that in low-end torque and transient operation, the wastegate are closed with high force must and in the range of the rated power sufficient control reserve must be present, so that in the amount of nominal power can be controlled safely, or a reduction can be made to protect against overspeed at the ATL.
  • the exhaust back pressure in part-load operation should be as low as possible in order to set a low-consumption minimum charge exchange work can. This tradeoff can only be resolved inadequately by the previous, with overpressure controlled pneumatic actuators on the gasoline engine.
  • One solution is electrically operated wastegate actuators, which can be independently operated or regulated by the pressures applied to the engine.
  • a generic internal combustion engine with an electric actuator for the wastegate and a charge air cooler is known from DE 10 2005 056 011 A1. This results in particular advantages for the electrical actuation of the wastegate, that the exhaust gas flowing through the wastegate is fed to its own exhaust gas flow.
  • the invention is based on the object, an internal combustion engine og. To improve fuel economy and load response performance.
  • the intercooler is integrated into the intake manifold and that the intercooler is formed with a water-cooled heat exchanger.
  • the water-cooled heat exchanger of the intercooler is connected to a cooling circuit of the internal combustion engine.
  • the charge air cooler is a water-air charge air cooler (WL-LLK).
  • the electric actuator for actuating the wastegate valve has an electric motor, which is arranged and designed such that the electric motor converts an electrical output signal of an engine control unit directly into an adjusting movement of the wastegate valve.
  • the wastegate valve is designed as a wastegate flap.
  • Fig. 1 is a schematic representation of a preferred embodiment of an internal combustion engine according to the invention.
  • FIG. 2 shows a characteristic diagram for a regulation of the wastegate by means of an electric actuator.
  • an internal combustion engine comprises an engine block 10, an exhaust system 12, an exhaust gas turbocharger 14 (ATL) and a fresh air system 16.
  • the ATL 14 has a disposed in the exhaust system 12 turbine 18 and one in the fresh air system 16th arranged compressor 20.
  • a wastegate channel 22 is further arranged with a wastegate valve 24 such that a portion of the exhaust gas is selectively bypassed by opening the wastegate valve 24 to the turbine.
  • the wastegate valve 24, which is preferably designed as a wastegate flap, has an electric actuator 26 for actuating the wastegate valve 24.
  • a catalytic converter 28 Downstream of the turbine 18, a catalytic converter 28, in particular a pre-catalytic converter or a main catalytic converter close to the engine, is arranged in the exhaust system 12.
  • a bypass passage 30 bridging the compressor 20 is arranged with a diverter valve 32 (SUV). Furthermore, a throttle valve 34 (DKL) and a suction tube 36 is arranged in the fresh air system 16.
  • a charge air cooler is integrated with a water-cooled heat exchanger. This water-cooled heat exchanger is connected to a cooling water circuit 38 of the internal combustion engine. This cooling water circuit 38 has a pump 40 and a low-temperature cooler 42.
  • FIG. 2 illustrates a characteristic diagram for controlling the wastegate valve 24 by means of the electric actuator 26.
  • a rotational speed in [1 / min] is plotted on a horizontal axis 44 and a relative mean pressure in [%] on a vertical axis 46 .
  • a first map area 48 the wastegate valve 24 is closed, in a second map area 50, the wastegate valve 24 is opened and in a third map area 52, the wastegate valve 24 is controlled.
  • the actuator control also takes place as a function of an accelerator pedal gradient in such a way that at a rapid passage of the pedal, the wastegate valve 24 is basically immediately closed and remains closed until the maximum allowable boost pressure, if the driver does not go from the gas before.
  • the charge air cooler is integrated into the suction pipe 36 and equipped with a water-cooled heat exchanger. This ensures that the open in the partial load wastegate valve 24 causes no significant delay in the response of the engine, since there is only a small volume of air between ATL compressor outlet and entry into the combustion chambers of the internal combustion engine. Therefore, the two technologies "electric wastegate actuator” and a "integrated in the intake manifold, water-cooled intercooler” are combined according to the invention.
  • the electric wastegate actuator can achieve its advantage, namely the regulation of the wastegate valve 24 independent of operating point-dependent pressures, only by the resulting, very small compressed air volume due to the integrated in the suction tube 36 WL-LLK, without a deterioration of the dynamics at load request from lower Part load when opened there Wastegateventil 24 must be taken into account, in which the entire compressed air volume is at a much lower pressure level than conventional pneumatic actuators, but also cause a 1 -2% higher fuel consumption.
  • the dynamic behavior is indeed improved at least to the level of pneumatic actuators, but this is the consumption in the entire map area in an undesirable manner on the worse level of the pneumatic wastegate actuators.
  • wastegate valve 24 With open at partial load wastegate valve 24, which represents the desired state, since the primary motivation for the use of an electric wastegate actuator 26, the reduction consumption, can be through the use of an electric wastegate actuator 26 improve both the dynamics and the consumption, because by the combination of integrated in the intake manifold 36 LLK and electric wastegate actuator 26, the consumption can be improved without a disadvantage. to suffer the dynamic behavior. This also provides the opportunity to provide the wastegate valve 24 according to purely motor, thermodynamic criteria. This results in the characteristic diagram according to FIG. 2. With the operating strategy of an electric wastegate actuator 24 shown here, the advantages of the electrical control are maximized. The prerequisite for the implementation of this map as shown in FIG. 2 is integrated in the intake manifold 36 WL-LLK.
  • electrical wastegate actuator 26 means an actuator that directly converts an electrical output signal of a motor control device by means of an electric motor into the desired setting movement of the wastegate valve or the wastegate flap. This means independence of operating point-dependent supply pressures of the engine.

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)

Abstract

The invention relates to an internal combustion engine, in particular of a motor vehicle, comprising an intake pipe (36) in a fresh air system (16), said pipe opening into intake ports in a cylinder head of the internal combustion engine, an exhaust-gas system (12) and an exhaust-gas turbocharger (14) with a turbine (18) that is located in the exhaust-gas system (12) and a compressor (20) that is driven by the turbine (18) and located in the fresh air system (16). The turbine (18) has a waste gate channel (22) that allows the exhaust gas to flow past a turbine wheel of the turbine (18). A waste gate valve (24) is situated in the waste gate channel (22), for selectively opening and closing said channel (22) and an electric actuator (26) for actuating the waste gate valve (24) is also provided. A charge-air cooler is situated in the fresh air system (16), downstream of the compressor (20). The charge-air cooler is integrated into the intake pipe (36) and the charge-air cooler has a water-cooled heat exchanger.

Description

Beschreibung description

Brennkraftmaschine mit Abgasturbolader und LadeluftkühlerInternal combustion engine with exhaust gas turbocharger and intercooler

Die Erfindung betrifft eine Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, mit einem Saugrohr in einer Frischluftanlage, welches in Einlasskanäle in einem Zylinderkopf der Brennkraftmaschine mündet, einer Abgasanlage und einem Abgasturbolader, der eine in der Abgasanlage angeordnete Turbine und einen von der Turbine angetriebenen, in der Frischluftanlage angeordneten Verdichter aufweist, wobei die Turbine einen Wastegate-Kanal zum überbrückenden Vorbeiströmen des Abgases an einem Turbinenrad der Turbine vorbei aufweist, wobei in dem Wastegate-Kanal ein Wastegateventil zum wahlweise Öffnen und Verschließen des Wastegate-Kanals angeordnet ist, wobei ein elektrischer Aktuator zum Betätigen des Wastegateventils vorgesehen ist, wobei in der Frischluftanlage stromab des Verdichters ein Ladeluftkühler angeordnet ist, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to an internal combustion engine, in particular of a motor vehicle, with a suction pipe in a fresh air system, which opens into intake passages in a cylinder head of the internal combustion engine, an exhaust system and an exhaust gas turbocharger, a turbine arranged in the exhaust system and driven by the turbine in the fresh air system wherein the turbine has a wastegate passage for bypassing the exhaust gas past a turbine wheel of the turbine, wherein in the wastegate channel, a wastegate valve for selectively opening and closing the wastegate channel is arranged, wherein an electric actuator for actuating the wastegate valve is provided, wherein in the fresh air system downstream of the compressor, a charge air cooler is arranged, according to the preamble of patent claim 1.

Die Ladedruckregelung bei Motoren mit Abgasturboaufladung erfolgt bei Wastegate- Turboladern nach dem Stand der Technik, wie beispielsweise aus der DE 198 24 913 A1 bekannt, mittels pneumatischen Druckaktuatoren. Bei aufgeladenen Ottomotoren kommen zum überwiegenden Teil Turbolader mit Starrgeometrie und Wastegate-Regelung zur Anwendung, da hier dem breiten Einsatz der beim Diesel zur Anwendung kommenden VTG-Technologie (verstellbare Turbinengeometrie) vor allem die hohen Kosten, die eine Folge der deutlich höheren Abgastemperaturen gegenüber dem Diesel sind, im Wege stehen. Für preissensitive Anwendungen wird der turboaufgeladene Ottomotor daher auch in Zukunft über Starrgeometrie- ATL und Wastegate-Regelung verfügen.The boost pressure control in engines with exhaust turbocharger takes place in wastegate turbochargers according to the prior art, as known for example from DE 198 24 913 A1, by means of pneumatic pressure actuators. Turbocharged turbochargers with rigid geometry and wastegate control are predominantly used in turbocharged gasoline engines, since here the widespread use of the VTG technology (adjustable turbine geometry) for diesel applications is due above all to the high costs associated with the significantly higher exhaust gas temperatures compared to the Diesel are, stand in the way. For price-sensitive applications, the turbo-charged gasoline engine will therefore also have rigid geometry ATL and wastegate control in the future.

Die Entwicklung bei diesen Motoren ist zunehmend von einem hohen LowEnd-Torque und einem verzögerungsfreien Ansprechverhalten geprägt. Diesen Sachverhalten wird mit einer ATL-Auslegung Rechnung getragen, die speziell für den unteren Drehzahibereich optimiert ist. Solche ATL's sind von ihrem Durchsatzvermögen her bezogen auf das Hubvolumen des Motors sehr klein, womit sie schon bei kleinen Abgasmassenströmen hohe Druckverhältnisse über den Lader realisieren können. Bei hohen Motordrehzahlen und großen Abgasmassenströmen müssen entsprechend große Abgasmengen über das Wastegate an der Turbine vorbei geführt werden.The development of these engines is increasingly characterized by a high low-end torque and a delay-free response. This situation is taken into account with an ATL design, which is optimized especially for the lower speed range. Such ATL's are very small in terms of their throughput capacity based on the stroke volume of the engine, which means they can realize high pressure ratios via the supercharger even with small exhaust gas mass flows. At high engine speeds and large exhaust gas mass flows correspondingly large amounts of exhaust gas must be passed over the wastegate on the turbine.

Die Anforderung an den Wastegate-Aktuator leitet sich daraus entsprechend ab, dass im LowEnd-Torque- und transienten Betrieb das Wastegate mit hoher Kraft geschlossen werden muss und im Bereich der Nennleistung ausreichend Regelreserve vorhanden sein muss, damit auch in der Höhe die Nennleistung sicher eingeregelt werden, bzw. eine Abregelung zum Schutz vor Überdrehzahl am ATL erfolgen kann. Darüber hinaus soll der Abgasgegendruck im Teillastbetrieb so gering wie möglich sein, um eine verbrauchsgünstige minimale Ladungswechselarbeit einstellen zu können. Dieser Tradeoff kann von den bisherigen, mit Überdruck geregelten Pneumatikaktuatoren am Ottomotor nur unzureichend aufgelöst werden. Eine Lösung stellen elektrisch betriebene Wastegate-Steller dar, die von den am Motor anliegenden Drücken unabhängig betätigt bzw. geregelt werden können.The demand on the wastegate actuator is derived from the fact that in low-end torque and transient operation, the wastegate are closed with high force must and in the range of the rated power sufficient control reserve must be present, so that in the amount of nominal power can be controlled safely, or a reduction can be made to protect against overspeed at the ATL. In addition, the exhaust back pressure in part-load operation should be as low as possible in order to set a low-consumption minimum charge exchange work can. This tradeoff can only be resolved inadequately by the previous, with overpressure controlled pneumatic actuators on the gasoline engine. One solution is electrically operated wastegate actuators, which can be independently operated or regulated by the pressures applied to the engine.

Eine gattungsgemäße Brennkraftmaschine mit einem elektrischen Aktuator für das Wastegate und einem Ladeluftkühler ist aus der DE 10 2005 056 011 A1 bekannt. Es ergeben sich dadurch besondere Vorteile für die elektrische Betätigung des Wastegates, dass das über das Wastegate strömende Abgas einer eigenen Abgasflut zugeführt wird.A generic internal combustion engine with an electric actuator for the wastegate and a charge air cooler is known from DE 10 2005 056 011 A1. This results in particular advantages for the electrical actuation of the wastegate, that the exhaust gas flowing through the wastegate is fed to its own exhaust gas flow.

Der Erfindung liegt die Aufgabe zugrunde, eine Brennkraftmaschine der o.g. Art hinsichtlich Kraftstoffverbrauch und Ansprechverhalten bei Lastanforderung zu verbessern.The invention is based on the object, an internal combustion engine og. To improve fuel economy and load response performance.

Diese Aufgabe wird erfindungsgemäß durch eine Brennkraftmaschine der o.g. Art mit den in Anspruch 1 gekennzeichneten Merkmalen gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den weiteren Ansprüchen beschrieben.This object is achieved by an internal combustion engine o.g. Art solved with the features characterized in claim 1. Advantageous embodiments of the invention are described in the further claims.

Dazu ist es bei einer Brennkraftmaschine der o.g. Art erfindungsgemäß vorgesehen, dass der Ladeluftkühler in das Saugrohr integriert ist und dass der Ladeluftkühler mit einem wassergekühlten Wärmetauscher ausgebildet ist.For this it is in an internal combustion engine o.g. Art according to the invention provided that the intercooler is integrated into the intake manifold and that the intercooler is formed with a water-cooled heat exchanger.

Dies hat den Vorteil, dass sich ein geringes Volumen in der Frischluftanlage stromab des Verdichters ergibt, wodurch auch bei im Teillastbetrieb geöffnetem Wastegateventil bzw. Wastegateklappe bei Lastanforderung ein schnelles Ansprechen der Brennkraftmaschine sichergestellt ist. Dadurch ist der reduzierte Kraftstoffverbrauch durch Öffnen des Wastegateventils im Teillastbereicht nicht mehr mit einem verschlechterten Ansprechverhalten bei Lastanforderung kombiniert.This has the advantage that there is a small volume in the fresh air system downstream of the compressor, whereby a fast response of the internal combustion engine is ensured even when opened in part-load operation wastegate valve or wastegate flap at load request. As a result, the reduced fuel consumption by opening the wastegate valve in the part load range is no longer combined with a deteriorated response to load request.

Zweckmäßigerweise ist der wassergekühlte Wärmetauscher des Ladeluftkühlers mit einem Kühlkreislauf der Brennkraftmaschine verbunden.Conveniently, the water-cooled heat exchanger of the intercooler is connected to a cooling circuit of the internal combustion engine.

In einer bevorzugten Ausführungsform ist der Ladeluftkühler ein Wasser-Luft-Ladeluftkühler (WL-LLK). Zweckmäßigerweise weist der elektrische Aktuator zum Betätigen des Wastegateventils einen Elektromotor auf, welcher derart angeordnet und ausgebildet ist, dass der Elektromotor ein elektrisches Ausgangssignal eines Motorsteuergerätes direkt in eine Stellbewegung des Wastegateventils umsetzt.In a preferred embodiment, the charge air cooler is a water-air charge air cooler (WL-LLK). Expediently, the electric actuator for actuating the wastegate valve has an electric motor, which is arranged and designed such that the electric motor converts an electrical output signal of an engine control unit directly into an adjusting movement of the wastegate valve.

In einer besonders bevorzugten Ausführungsform ist das Wastegateventil als Wastegateklappe ausgebildet.In a particularly preferred embodiment, the wastegate valve is designed as a wastegate flap.

Die Erfindung wird im Folgenden anhand der Zeichnung näher erläutert. Diese zeigt inThe invention will be explained in more detail below with reference to the drawing. This shows in

Fig. 1 eine schematische Darstellung einer bevorzugten Ausführungsform einer erfindungsgemäßen Brennkraftmaschine undFig. 1 is a schematic representation of a preferred embodiment of an internal combustion engine according to the invention and

Fig. 2 ein Kennfeld für eine Regelung des Wastegates mittels eines elektrischen Aktuators.2 shows a characteristic diagram for a regulation of the wastegate by means of an electric actuator.

Die in Fig. 1 dargestellte, bevorzugte Ausführungsform einer erfindungsgemäßen Brennkraftmaschine umfasst einen Motorblock 10, eine Abgasanlage 12, einen Abgasturbolader 14 (ATL) und eine Frischluftanlage 16. Der ATL 14 weist eine in der Abgasanlage 12 angeordnete Turbine 18 und einen in der Frischluftanlage 16 angeordneten Verdichter 20 auf. In der Abgasanlage 12 ist ferner ein Wastegate-Kanal 22 mit einem Wastegateventil 24 derart angeordnet, dass ein Teil des Abgases durch Öffnen des Wastegateventils 24 wahlweise an der Turbine vorbeigeleitet wird. Das Wastegateventil 24, welches bevorzugt als Wastegateklappe ausgebildet ist, weist einen elektrischen Aktuator 26 zum Betätigen des Wastegateventils 24 auf. Stromab der Turbine 18 ist in der Abgasanlage 12 ein Katalysator 28, insbesondere ein Vorkatalysator oder ein motornaher Hauptkatalysator, angeordnet.The illustrated in Fig. 1, preferred embodiment of an internal combustion engine according to the invention comprises an engine block 10, an exhaust system 12, an exhaust gas turbocharger 14 (ATL) and a fresh air system 16. The ATL 14 has a disposed in the exhaust system 12 turbine 18 and one in the fresh air system 16th arranged compressor 20. In the exhaust system 12, a wastegate channel 22 is further arranged with a wastegate valve 24 such that a portion of the exhaust gas is selectively bypassed by opening the wastegate valve 24 to the turbine. The wastegate valve 24, which is preferably designed as a wastegate flap, has an electric actuator 26 for actuating the wastegate valve 24. Downstream of the turbine 18, a catalytic converter 28, in particular a pre-catalytic converter or a main catalytic converter close to the engine, is arranged in the exhaust system 12.

In der Frischluftanlage 16 ist ein den Verdichter 20 überbrückender Bypasskanal 30 mit einem Schubumluftventil 32 (SUV) angeordnet. Weiterhin ist in der Frischluftanlage 16 eine Drosselklappe 34 (DKL) und ein Saugrohr 36 angeordnet. In das Saugrohr 36 ist ein Ladeluftkühler mit einem wassergekühlten Wärmetauscher integriert. Dieser wassergekühlte Wärmetauscher ist mit einem Kühlwasserkreislauf 38 der Brennkraftmaschine verbunden. Dieser Kühlwasserkreislauf 38 weist eine Pumpe 40 und einen Niedertemperaturkühler 42 auf.In the fresh air system 16, a bypass passage 30 bridging the compressor 20 is arranged with a diverter valve 32 (SUV). Furthermore, a throttle valve 34 (DKL) and a suction tube 36 is arranged in the fresh air system 16. In the suction pipe 36, a charge air cooler is integrated with a water-cooled heat exchanger. This water-cooled heat exchanger is connected to a cooling water circuit 38 of the internal combustion engine. This cooling water circuit 38 has a pump 40 and a low-temperature cooler 42.

Fig. 2 veranschaulicht ein Kennfeld für eine Regelung des Wastegateventils 24 mittels des elektrischen Aktuators 26. In Fig. 2 ist auf einer horizontalen Achse 44 eine Drehzahl in [1/ιmin] und auf einer vertikalen Achse 46 ein relativer Mitteldruck in [%] aufgetragen. In einem ersten Kennfeldbereich 48 ist das Wastegateventil 24 geschlossen, in einem zweiten Kennfeldbereich 50 ist das Wastegateventil 24 geöffnet und in einem dritten Kennfeldbereich 52 wird das Wastegateventil 24 geregelt.2 illustrates a characteristic diagram for controlling the wastegate valve 24 by means of the electric actuator 26. In FIG. 2, a rotational speed in [1 / min] is plotted on a horizontal axis 44 and a relative mean pressure in [%] on a vertical axis 46 , In a first map area 48, the wastegate valve 24 is closed, in a second map area 50, the wastegate valve 24 is opened and in a third map area 52, the wastegate valve 24 is controlled.

Darüber hinaus erfolgt die Aktuatoransteuerung auch in Abhängigkeit von einem Fahrpedalgradienten in der Art, dass bei einem schnellen Durchtreten des Pedals das Wastegateventil 24 grundsätzlich sofort geschlossen wird und bis zum Erreichen des maximal zulässigen Ladedruckes geschlossen bleibt, wenn der Fahrer nicht vorher vom Gas geht.In addition, the actuator control also takes place as a function of an accelerator pedal gradient in such a way that at a rapid passage of the pedal, the wastegate valve 24 is basically immediately closed and remains closed until the maximum allowable boost pressure, if the driver does not go from the gas before.

Damit der Vorteil der Entdrosselung im Teillastbetrieb durch ein geöffnetes Wastegateventil 24 auch in einen entsprechenden Verbrauchsvorteil umgesetzt werden kann, ist erfindungsgemäß der Ladeluftkühler in das Saugrohr 36 integriert und mit einem wassergekühlten Wärmetauscher ausgerüstet. Dies stellt sicher, dass das in der Teillast geöffnete Wastegateventil 24 keine merkliche Verzögerung im Ansprechverhalten des Motors bedingt, da ein lediglich geringes Luftvolumen zwischen ATL-Verdichteraustritt und Eintritt in die Brennräume der Brennkraftmaschine vorliegt. Daher sind erfindungsgemäß die beiden Technologien "elektrischer Wastegate-Aktuator" und ein "im Saugrohr integrierter, wassergekühlter Ladeluftkühler" miteinander kombiniert.So that the advantage of Entdrosselung can be implemented in part-load operation by an open wastegate valve 24 in a corresponding consumption advantage, according to the invention, the charge air cooler is integrated into the suction pipe 36 and equipped with a water-cooled heat exchanger. This ensures that the open in the partial load wastegate valve 24 causes no significant delay in the response of the engine, since there is only a small volume of air between ATL compressor outlet and entry into the combustion chambers of the internal combustion engine. Therefore, the two technologies "electric wastegate actuator" and a "integrated in the intake manifold, water-cooled intercooler" are combined according to the invention.

Erst durch die Kombination aus den beiden bekannten Technologien, nämlich "im Saugrohr 36 integrierter WL-LLK" und "elektrischer Wastegate-Aktuator", ist es möglich, die Vorteile des elektrischen Wastegate-Aktuators in der Praxis umzusetzen.Only through the combination of the two known technologies, namely "WL-LLK integrated in the suction tube 36" and "electrical wastegate actuator", it is possible to implement the advantages of the electric wastegate actuator in practice.

Der elektrische Wastegate-Aktuator kann seinen Vorteil, nämlich die Regelung des Wastegateventils 24 unabhängig von betriebspunktabhängigen Drücken, erst durch das sich ergebende, sehr geringe Druckluftvolumen aufgrund des im Saugrohr 36 integrierten WL-LLK erzielen, ohne dass eine Verschlechterung der Dynamik bei Lastanforderung aus niedriger Teillast bei dort geöffnetem Wastegateventil 24 in Kauf genommen werden muss, bei dem sich das gesamte Druckluftvolumen auf einem deutlich geringerem Druckniveau befindet als bei herkömmlichen Pneumatikaktuatoren, die aber auch einen 1 -2% höheren Kraftstoffverbrauch verursachen.The electric wastegate actuator can achieve its advantage, namely the regulation of the wastegate valve 24 independent of operating point-dependent pressures, only by the resulting, very small compressed air volume due to the integrated in the suction tube 36 WL-LLK, without a deterioration of the dynamics at load request from lower Part load when opened there Wastegateventil 24 must be taken into account, in which the entire compressed air volume is at a much lower pressure level than conventional pneumatic actuators, but also cause a 1 -2% higher fuel consumption.

Wird das Wastegateventil 24 schon in der niedrigen Teillast geschlossen, wird das dynamische Verhalten zwar mindestens auf das Niveau von pneumatischen Aktuatoren verbessert, aber dafür ist der Verbrauch im gesamten Kennfeldbereich in unerwünschter Weise auf dem schlechteren Niveau der pneumatischen Wastegate-Aktuatoren.If the wastegate valve 24 is already closed in the low part load, the dynamic behavior is indeed improved at least to the level of pneumatic actuators, but this is the consumption in the entire map area in an undesirable manner on the worse level of the pneumatic wastegate actuators.

Bei in der Teillast offenem Wastegateventil 24, was den gewünschten Zustand darstellt, da die primäre Motivation für den Einsatz eines elektrischen Wastegate-Aktuators 26 die Reduktion des Verbrauches ist, lassen sich durch den Einsatz eines elektrischen Wastegate-Aktuators 26 sowohl die Dynamik als auch der Verbrauch verbessern, denn durch die Kombination von im Saugrohr 36 integriertem LLK und elektrischem Wastegate-Aktuator 26 lässt sich der Verbrauch verbessern ohne einen Nachteil bzgl. des dynamischen Verhaltens erleiden zu müssen. Hierdurch ergibt sich zudem die Möglichkeit, das Wastegateventil 24 nach rein motorischen, thermodynamischen Kriterien zu stellen. Damit ergibt sich das Kennfeld gemäß Fig. 2. Mit der hier dargestellten Betriebsstrategie eines elektrischen Wastegate-Aktuators 24 werden die Vorteile der elektrischen Ansteuerung maximiert. Die Voraussetzung für die Implementierung dieses Kennfeldes gemäß Fig. 2 ist der im Saugrohr 36 integrierte WL-LLK.With open at partial load wastegate valve 24, which represents the desired state, since the primary motivation for the use of an electric wastegate actuator 26, the reduction consumption, can be through the use of an electric wastegate actuator 26 improve both the dynamics and the consumption, because by the combination of integrated in the intake manifold 36 LLK and electric wastegate actuator 26, the consumption can be improved without a disadvantage. to suffer the dynamic behavior. This also provides the opportunity to provide the wastegate valve 24 according to purely motor, thermodynamic criteria. This results in the characteristic diagram according to FIG. 2. With the operating strategy of an electric wastegate actuator 24 shown here, the advantages of the electrical control are maximized. The prerequisite for the implementation of this map as shown in FIG. 2 is integrated in the intake manifold 36 WL-LLK.

Hierin bedeutet elektrischer Wastegate-Aktuator 26 einen Aktuator, der ein elektrisches Ausgangssignal eines Motorsteuergerätes mittels eines elektrischen Motors in die gewünschte Stellbewegung des Wastegateventils bzw. der Wastegateklappe direkt umsetzt. Dies bedeutet Unabhängigkeit von betriebspunktabhängigen Versorgungsdrücken des Motors. Herein, electrical wastegate actuator 26 means an actuator that directly converts an electrical output signal of a motor control device by means of an electric motor into the desired setting movement of the wastegate valve or the wastegate flap. This means independence of operating point-dependent supply pressures of the engine.

Claims

Patentansprüche claims 1. Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, mit einem Saugrohr (36) in einer Frischluftanlage (16), welches in Einlasskanäle in einem Zylinderkopf der Brennkraftmaschine mündet, einer Abgasanlage (12) und einem Abgasturbolader (14), der eine in der Abgasanlage (12) angeordnete Turbine (18) und einen von der Turbine (18) angetriebenen, in der Frischluftanlage (16) angeordneten Verdichter (20) aufweist, wobei die Turbine (18) einen Wastegate-Kanal (22) zum überbrückenden Vorbeiströmen des Abgases an einem Turbinenrad der Turbine (18) vorbei aufweist, wobei in dem Wastegate-Kanal (22) ein Wastegateventil (24) zum wahlweise Öffnen und Verschließen des Wastegate-Kanals (22) angeordnet ist, wobei ein elektrischer Aktuator (26) zum Betätigen des Wastegateventils (24) vorgesehen ist, wobei in der Frischluftanlage (16) stromab des Verdichters (20) ein Ladeluftkühler angeordnet ist, dadurch gekennzeichnet, dass der Ladeluftkühler in das Saugrohr (36) integriert ist und dass der Ladeluftkühler mit einem wassergekühlten Wärmetauscher ausgebildet ist.1. internal combustion engine, in particular of a motor vehicle, with a suction pipe (36) in a fresh air system (16), which opens into intake ports in a cylinder head of the internal combustion engine, an exhaust system (12) and an exhaust gas turbocharger (14) having a in the exhaust system (12 ) arranged turbine (18) and one of the turbine (18) driven in the fresh air system (16) arranged compressor (20), wherein the turbine (18) has a wastegate channel (22) for bridging bypassing the exhaust gas to a turbine wheel the turbine (18) passing, wherein in the wastegate channel (22) a wastegate valve (24) for selectively opening and closing the wastegate channel (22) is arranged, wherein an electrical actuator (26) for actuating the wastegate valve (24 ) is provided, wherein in the fresh air system (16) downstream of the compressor (20) a charge air cooler is arranged, characterized in that the intercooler is integrated in the suction pipe (36) and there Is the intercooler formed with a water-cooled heat exchanger. 2. Brennkraftmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass der wassergekühlte Wärmetauscher des Ladeluftkühlers mit einem Kühlkreislauf (38) der Brennkraftmaschine verbunden ist.2. Internal combustion engine according to claim 1, characterized in that the water-cooled heat exchanger of the charge air cooler is connected to a cooling circuit (38) of the internal combustion engine. 3. Brennkraftmaschine nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Ladeluftkühler ein Wasser-Luft-Ladeluftkühler (WL-LLK) ist.3. Internal combustion engine according to at least one of the preceding claims, characterized in that the charge air cooler is a water-air charge air cooler (WL-LLK). 4. Brennkraftmaschine nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der elektrische Aktuator (26) zum Betätigen des Wastegateventils (24) einen Elektromotor aufweist, welcher derart angeordnet und ausgebildet ist, dass der Elektromotor ein elektrisches Ausgangssignal eines Motorsteuergerätes direkt in eine Stellbewegung des Wastegateventils (24) umsetzt.4. Internal combustion engine according to at least one of the preceding claims, characterized in that the electric actuator (26) for actuating the wastegate valve (24) comprises an electric motor, which is arranged and designed such that the electric motor, an electrical output signal of an engine control unit directly into an actuating movement of the wastegate valve (24). 5. Brennkraftmaschine nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Wastegateventil (24) als Wastegateklappe ausgebildet ist. 5. Internal combustion engine according to at least one of the preceding claims, characterized in that the wastegate valve (24) is designed as a wastegate flap.
EP08802450A 2007-10-29 2008-09-20 Internal combustion engine comprising an exhaust-gas turbocharger and a charge-air cooler Ceased EP2205841A1 (en)

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DE102007051505A DE102007051505A1 (en) 2007-10-29 2007-10-29 Internal combustion engine with exhaust gas turbocharger and intercooler
PCT/EP2008/007948 WO2009056197A1 (en) 2007-10-29 2008-09-20 Internal combustion engine comprising an exhaust-gas turbocharger and a charge-air cooler

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Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005004122A1 (en) * 2005-01-28 2006-08-03 Volkswagen Ag Dual-charged internal combustion engine, especially for vehicle, has charger pressure outlet connected to intake inlet and to intake pipe via butterfly valves; charge cooler is integrated into intake pipe to give intake/charge cooler module
US8333072B2 (en) * 2008-10-01 2012-12-18 Honda Motor Co., Ltd. Wastegate control system and method
DE102010025873A1 (en) 2010-07-02 2011-04-21 Daimler Ag Suction module e.g. charged air manifold for petrol engine of passenger car, has cooling device arranged in sections and cooling air that flows through housing of chamber, where air supplying exhaust gas of engine is cooled by device
DE102010047092A1 (en) * 2010-10-01 2012-04-05 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Charge air cooling device for an internal combustion engine
GB2487747B (en) * 2011-02-02 2016-05-18 Ford Global Tech Llc An engine system
JP5325254B2 (en) * 2011-03-31 2013-10-23 三菱重工業株式会社 Intake air cooling system for stationary internal combustion engine
JP5903917B2 (en) * 2012-02-08 2016-04-13 トヨタ自動車株式会社 Cooling device for internal combustion engine
DE102012212867A1 (en) * 2012-07-23 2014-01-23 Behr Gmbh & Co. Kg Charge air cooling system and associated method of providing charge air cooling for an internal combustion engine
DE102013215347B4 (en) 2012-09-21 2015-12-10 Ford Global Technologies, Llc Method for discharging liquid from an intake tract of a turbocharger arrangement and turbocharger arrangement for carrying out such a method
US9359941B2 (en) 2012-10-17 2016-06-07 Ford Global Technologies, Llc Method for purging condensate from a charge air cooler
US20140182266A1 (en) * 2012-12-28 2014-07-03 GM Global Technology Operations LLC Integrated waste heat recovery
KR101526388B1 (en) * 2013-07-18 2015-06-08 현대자동차 주식회사 Engine system
DE102013015138A1 (en) * 2013-09-13 2015-03-19 Man Truck & Bus Ag Device for controlling a throttle valve, in particular a throttle valve of an intake system of an internal combustion engine
DE102013019150A1 (en) * 2013-11-14 2015-05-21 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Method for load-dependent opening and closing of a blow-off valve flap of an internal combustion engine with a turbocharger
FR3014616B1 (en) 2013-12-05 2016-01-08 Continental Automotive France METHOD FOR CONTROLLING A CONTROL OF AN ELECTRICAL ACTUATOR OF WASTEGATE BY MEASURING CURRENT ACROSS THE ELECTRIC ACTUATOR
US9709065B2 (en) * 2014-11-06 2017-07-18 Ford Global Technologies, Llc System and method for a turbocharger driven coolant pump
US10300786B2 (en) 2014-12-19 2019-05-28 Polaris Industries Inc. Utility vehicle
CN105041391A (en) * 2015-08-19 2015-11-11 江苏恒尚动力高科有限公司 Turbocharger of automatic temperature adjusting device
AT518102B1 (en) * 2015-12-29 2017-10-15 Ge Jenbacher Gmbh & Co Og Condition determination of a filter module
CN109372626A (en) * 2018-12-17 2019-02-22 潍柴动力股份有限公司 An integrated heat exchanger and engine
WO2020223379A1 (en) 2019-04-30 2020-11-05 Polaris Industries Inc. Vehicle
US12187127B2 (en) 2020-05-15 2025-01-07 Polaris Industries Inc. Off-road vehicle
CA3156559A1 (en) 2021-05-05 2022-11-05 Polaris Industries Inc. Exhaust assembly for a utility vehicle

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04103834A (en) * 1990-08-22 1992-04-06 Mazda Motor Corp Controller for engine with supercharger
DE4202077A1 (en) * 1992-01-25 1993-07-29 Audi Ag Suction distributor for I.C engine - involves air cooler or charging air cooler integrated in manifold of suction distributor
JPH06219188A (en) * 1992-10-23 1994-08-09 Mazda Motor Corp Control device for power train
US5791145A (en) * 1994-09-30 1998-08-11 Cooper Cameron Corporation Natural gas engine control system
DE19840616C1 (en) * 1998-09-05 1999-12-02 Daimler Chrysler Ag V=engine with mechanically driven turbocharger
DE19824913A1 (en) * 1998-06-04 1999-12-16 Daimler Chrysler Ag Arrangement for adjusting bypass valve in exhaust system of internal combustion engine with variably adjustable turbocharger
EP1219799A2 (en) * 2000-12-26 2002-07-03 Hitachi, Ltd. Exhaust gas turbine for internal combustion engine and exhaust turbo-supercharger
DE10215779A1 (en) * 2002-04-10 2003-11-06 Bosch Gmbh Robert Internal combustion engine with charging device has air module compactly combining electric choke flap, electric charge air compressor, charge air cooler, electric coolant pump, induction pipe module
EP1387063A2 (en) * 2002-08-03 2004-02-04 DaimlerChrysler AG Exhaust system for an internal combustion engine
EP1586756A1 (en) * 2004-04-01 2005-10-19 Robert Bosch Gmbh Method and device for operating an internal combustion engine
DE102006000136A1 (en) * 2005-03-28 2006-10-19 Denso Corp., Kariya Control device for an internal combustion engine and associated control method
DE102005053500B3 (en) * 2005-11-09 2007-05-10 Siemens Ag Induction pipe for motor vehicle engine, has upper part which is provided with cover and hollow space is formed between upper part and cover which results in cooled fluid flowing through radiator chamber
JP2007132217A (en) * 2005-11-08 2007-05-31 Fuji Heavy Ind Ltd Combustion control device for compression ignition engine
JP2007247560A (en) * 2006-03-16 2007-09-27 Toyota Motor Corp Internal combustion engine
DE102007018618A1 (en) * 2006-04-19 2007-10-25 Borgwarner Inc., Auburn Hills Turbo-supercharger for handling exhaust gas has a turbine casing with a cleaning device for altering the amount of exhaust gas flowing through a turbine

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1807042A (en) * 1927-06-13 1931-05-26 J R Burgamy Cooling intake for internal combustion engines
CH366169A (en) * 1957-02-20 1962-12-15 Nordberg Manufacturing Co Internal combustion engine with charging device
AT283824B (en) * 1966-02-23 1970-08-25 H C Hans Dipl Ing Dr Dr List Internal combustion engine with exhaust gas turbocharger and charge air cooler
DE2343300C2 (en) * 1973-08-28 1983-03-31 Klöckner-Humboldt-Deutz AG, 5000 Köln Water-cooled internal combustion engine with supercharging
US4269158A (en) * 1978-07-06 1981-05-26 Allis-Chalmers Corporation Intercooler for internal combustion engine
DE3201246A1 (en) * 1982-01-16 1983-07-28 Klöckner-Humboldt-Deutz AG, 5000 Köln INTERNAL COMBUSTION ENGINE WITH AN EXHAUST TURBOCHARGER
JPS6036728A (en) * 1983-08-08 1985-02-25 Diesel Kiki Co Ltd Supercharging pressure controlling apparatus
JPS627925A (en) * 1985-07-03 1987-01-14 Yanmar Diesel Engine Co Ltd Intake device having air cooler for multiple cylinder engine
JPS6266228U (en) * 1985-10-15 1987-04-24
US5201285A (en) * 1991-10-18 1993-04-13 Touchstone, Inc. Controlled cooling system for a turbocharged internal combustion engine
JP3023229B2 (en) * 1991-11-16 2000-03-21 三信工業株式会社 Outboard motor
US5269143A (en) 1992-12-07 1993-12-14 Ford Motor Company Diesel engine turbo-expander
US5551236A (en) * 1994-05-02 1996-09-03 Dresser Industries, Inc. Turbocharger control management system
JPH09511813A (en) * 1995-02-10 1997-11-25 フィリップス エレクトロニクス ネムローゼ フェンノートシャップ Device for actuating the control member
US6079210A (en) * 1998-07-16 2000-06-27 Woodward Governor Company Continuously variable electrically actuated flow control valve for high temperature applications
DE19927607A1 (en) * 1999-06-17 2000-12-21 Behr Gmbh & Co Charging air cooler for vehicle engine has air entry end exit pipes coupled via stack of flat rectangular pipe sections enclosed by housing mantle through which cooling medium is passed
SE522700C2 (en) * 2000-07-07 2004-03-02 Volvo Car Corp Internal combustion engine
US7725238B2 (en) * 2004-11-19 2010-05-25 Perkins Michael T System and method for smart system control for flowing fluid conditioners
DE102005056011A1 (en) 2005-11-24 2007-06-06 Volkswagen Ag Internal combustion engine for motor vehicle, has exhaust system and exhaust gas turbocharger whereby disperse-outlet of turbine is connected with first exhaust gas flux
CN100451309C (en) * 2007-03-15 2009-01-14 武汉第二船舶设计研究所 Turbocharging engine booster air intercooler

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04103834A (en) * 1990-08-22 1992-04-06 Mazda Motor Corp Controller for engine with supercharger
DE4202077A1 (en) * 1992-01-25 1993-07-29 Audi Ag Suction distributor for I.C engine - involves air cooler or charging air cooler integrated in manifold of suction distributor
JPH06219188A (en) * 1992-10-23 1994-08-09 Mazda Motor Corp Control device for power train
US5791145A (en) * 1994-09-30 1998-08-11 Cooper Cameron Corporation Natural gas engine control system
DE19824913A1 (en) * 1998-06-04 1999-12-16 Daimler Chrysler Ag Arrangement for adjusting bypass valve in exhaust system of internal combustion engine with variably adjustable turbocharger
DE19840616C1 (en) * 1998-09-05 1999-12-02 Daimler Chrysler Ag V=engine with mechanically driven turbocharger
EP1219799A2 (en) * 2000-12-26 2002-07-03 Hitachi, Ltd. Exhaust gas turbine for internal combustion engine and exhaust turbo-supercharger
DE10215779A1 (en) * 2002-04-10 2003-11-06 Bosch Gmbh Robert Internal combustion engine with charging device has air module compactly combining electric choke flap, electric charge air compressor, charge air cooler, electric coolant pump, induction pipe module
EP1387063A2 (en) * 2002-08-03 2004-02-04 DaimlerChrysler AG Exhaust system for an internal combustion engine
EP1586756A1 (en) * 2004-04-01 2005-10-19 Robert Bosch Gmbh Method and device for operating an internal combustion engine
DE102006000136A1 (en) * 2005-03-28 2006-10-19 Denso Corp., Kariya Control device for an internal combustion engine and associated control method
JP2007132217A (en) * 2005-11-08 2007-05-31 Fuji Heavy Ind Ltd Combustion control device for compression ignition engine
DE102005053500B3 (en) * 2005-11-09 2007-05-10 Siemens Ag Induction pipe for motor vehicle engine, has upper part which is provided with cover and hollow space is formed between upper part and cover which results in cooled fluid flowing through radiator chamber
JP2007247560A (en) * 2006-03-16 2007-09-27 Toyota Motor Corp Internal combustion engine
DE102007018618A1 (en) * 2006-04-19 2007-10-25 Borgwarner Inc., Auburn Hills Turbo-supercharger for handling exhaust gas has a turbine casing with a cleaning device for altering the amount of exhaust gas flowing through a turbine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2009056197A1 *

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DE102007051505A1 (en) 2009-04-30
US8051842B2 (en) 2011-11-08
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JP2011501043A (en) 2011-01-06
WO2009056197A1 (en) 2009-05-07
CN101842565A (en) 2010-09-22

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