WO2007087963A1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
WO2007087963A1
WO2007087963A1 PCT/EP2007/000143 EP2007000143W WO2007087963A1 WO 2007087963 A1 WO2007087963 A1 WO 2007087963A1 EP 2007000143 W EP2007000143 W EP 2007000143W WO 2007087963 A1 WO2007087963 A1 WO 2007087963A1
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WO
WIPO (PCT)
Prior art keywords
internal combustion
combustion engine
engine according
exhaust gas
accumulator
Prior art date
Application number
PCT/EP2007/000143
Other languages
German (de)
French (fr)
Inventor
Alfred Feuser
Original Assignee
Robert Bosch 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.)
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Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2007087963A1 publication Critical patent/WO2007087963A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines

Definitions

  • the invention relates to an internal combustion engine, in particular for a motor vehicle or a mobile working device according to the preamble of patent claim 1.
  • the heat energy contained in the hot exhaust gases of an internal combustion engine such as a diesel or gasoline engine is supplied to a Stirling engine (hot air engine) and converted via this into usable mechanical rotational energy, which can be used, for example, to drive a hydraulic pump of a hydraulic system.
  • a Stirling engine hot air engine
  • usable mechanical rotational energy which can be used, for example, to drive a hydraulic pump of a hydraulic system.
  • an internal combustion engine with an exhaust gas conducting exhaust system and a Stirling engine as an auxiliary unit is known in which the amount of heat contained in the exhaust gas of the engine supplied to the Stirling engine via a heat pipe and converted into mechanical useful energy, for example, to drive a hydraulic pump becomes.
  • a disadvantage of such internal combustion engines is that the hydraulic power of the driven by the Stirling engine hydraulic pump due to the design-limited performance of the Stirling engine is not sufficient to the hydraulic system, such as an agricultural Commercial vehicle or mobile implement, to provide adequate.
  • the present invention seeks to provide an internal combustion engine, which allows an improved hydraulic supply of a hydraulic system with minimal device complexity.
  • the internal combustion engine according to the invention has a drive train and an exhaust gas exhaust system, wherein the amount of heat contained in the exhaust gas is supplied to a Stirling engine for driving a first hydraulic pump.
  • at least one further hydraulic pump is provided, which is in operative connection with the drive train of the internal combustion engine. That is, in this solution, the supply of the hydraulic system takes place in contrast to the prior art according to DE 197 32 307 Al additionally via at least one directly via the internal combustion engine driven hydraulic pump.
  • the driven via the internal combustion engine hydraulic pump ensures a sufficient pressure medium supply of the hydraulic system even at high power requirements.
  • the hydraulic pumps are provided for charging at least one pressure fluid accumulator of a central hydraulic system of a vehicle or a working device.
  • the use of accumulators reduces the pump performance to the average power requirement of the consumer be because the volume flow pumped by the pump loads the memory when the volume flow required for the consumer is temporarily smaller than the pump volume flow.
  • One of the accumulator is preferably designed as a high-pressure accumulator and another accumulator as a low-pressure accumulator.
  • the suction sides of the hydraulic pumps are connected to the low pressure accumulator and the pressure sides to the high pressure accumulator.
  • the pressure medium lines of the high-pressure accumulator is preferably arranged in each case one blocking in the direction of the hydraulic pump check valve.
  • the non-return valves are used to shut off working groups under pressure and prevent pressure loss of the accumulator via the pumps.
  • the pressure fluid storage are designed as a membrane or bladder accumulator, so that they have a comparatively simple structure and low space requirement.
  • the Stirling engine is connected in an embodiment of the invention via a drive shaft with the first hydraulic pump.
  • the hydraulic pump can be arranged spatially spaced from the Stirling engine.
  • the second hydraulic pump is driven by an external gear arrangement of the drive train.
  • the amount of heat contained in the exhaust gas is supplied in a preferred embodiment, a heater of the Stirling engine.
  • the heater of the Stirling engine is arranged in the exhaust gas flow of the internal combustion engine, so that a direct heat transfer from the exhaust gas flow to the heater takes place and a high efficiency of the Stirling engine is ensured.
  • the heater is arranged on an exhaust pipe of the exhaust system such that the heater surrounds the exhaust pipe at least in sections annularly.
  • the excess air in the exhaust gas is utilized for afterburning in order to improve the efficiency of the Stirling engine in partial load operation and with decreasing exhaust gas temperature.
  • at least one burner in the exhaust system is provided in front of the heater of the Stirling engine, is added to the fuel in accordance with the respective residual air content and burned, so that the Stirling engine is operated in the optimal temperature range for the efficiency.
  • FIGURE shows a schematic representation of a circuit diagram of an internal combustion engine according to the invention.
  • the figure shows a schematic representation of an internal combustion engine 1 according to the invention, as used for example in a motor vehicle or a mobile implement (not shown).
  • the internal combustion engine 1 has a drive train 2 and an exhaust gas 4 conducting exhaust system 6, wherein the amount of heat contained in the exhaust gas stream is fed to a Stirling engine 8 for driving a first hydraulic pump 10 of a hydraulic system 12.
  • the Stirling engine 8 is connected via a drive shaft 14 to the hydraulic pump 10 so that it is spatially spaced from the Stirling engine 8.
  • the amount of heat contained in the exhaust gas 4 is at least partially supplied to the Stirling engine 8 via a heater, not shown, so that sets a temperature gradient .DELTA.T in the exhaust gas flow via the Stirling engine 8.
  • the heater is arranged on an exhaust pipe 16 of the exhaust system 6, that it surrounds this at least partially approximately annular. Thereby, a large heat transfer area between the exhaust pipe 16 and heater is achieved without affecting the exhaust gas flow in the exhaust pipe 16.
  • the heater is arranged in the exhaust stream of the internal combustion engine 1, so that a direct heat transfer from the exhaust gas 4 to the heater takes place and an improved efficiency of the Stirling engine 8 is achieved.
  • a second hydraulic pump 18 is provided, which is connected to the drive train 2 of the internal combustion engine 1 in FIG Active connection is to ensure a sufficient pressure medium supply of the hydraulic system 12 even at high. This additional hydraulic pump 18 is driven by the drive train 2 of the internal combustion engine 1 via an external gear arrangement 20.
  • the hydraulic pumps 10, 18 are used to charge a high-pressure accumulator 22 of a central hydraulic system of the vehicle or mobile implement.
  • the pressure sides of the pumps 10, 18 via a respective pressure medium line 24, 26 connected to the high-pressure accumulator 22.
  • the working lines for supplying the consumers and the return lines of the hydraulic system 12 are not shown.
  • In the pressure medium lines 24, 26 are provided in the direction of the hydraulic pumps 10, 18 blocking check valves 28, 30, which prevent discharge of the high-pressure accumulator 22 via the pumps 10, 18.
  • the suction side of the internal combustion engine 1 associated hydraulic pump 18 is connected via a supply line 32 to a low pressure accumulator 34.
  • a supply line 36 branches off to the suction side of the hydraulic pump 10 connected to the Stirling engine 8 via the drive shaft 14.
  • the two formed as a membrane or bladder accumulator accumulator 22, 34 have a comparatively simple structure with low space requirement.
  • the internal combustion engine 1 is not limited to the described hydraulic system 12 with two hydraulic pumps 10, 18, but can be assigned to the drive train 2 more than one hydraulic pump be, as well as several Stirling engines 8 for driving each of a pump in operative connection with the exhaust system 6 are.
  • an internal combustion engine 1 in particular for a motor vehicle or a mobile working device, with a drive train 2 and an exhaust gas 4 conductive exhaust system 6, 'wherein the amount of heat contained in the exhaust gas 4 is fed to a Stirling engine 8 for driving a first hydraulic pump 10.
  • at least one further hydraulic pump 18 is provided, which is driven by the drive train 2 of the internal combustion engine 1.

Abstract

An internal combustion engine (1) is disclosed, in particular for a motor vehicle or a mobile piece of equipment, having a drive train (2) and an exhaust-gas system (6) which conducts exhaust gases (4), wherein the thermal energy which is contained in the exhaust gas is fed to a Stirling engine (8) for driving a first hydraulic pump (10). According to the invention, at least one second hydraulic pump (18) is provided which is driven by the drive train of the internal combustion engine.

Description

Beschreibung description
BrennkraftmaschineInternal combustion engine
Die Erfindung betrifft eine Brennkraftmaschine, insbesondere für ein Kraftfahrzeug oder ein mobiles Arbeitsgerät gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to an internal combustion engine, in particular for a motor vehicle or a mobile working device according to the preamble of patent claim 1.
Bei derartigen Brennkraftmaschinen wird die in den heißen Abgasen eines Verbrennungsmotors, beispielsweise eines Diesel- oder Ottomotors enthaltene Wärmeenergie einem Stirlingmotor (Heißluftmotor) zugeführt und über diesen in nutzbare mechanische Rotationsenergie umgewandelt, die beispielsweise zum Antrieb einer Hydraulikpumpe eines Hydrauliksystems verwendbar ist. Dadurch wird der Gesamtwirkungsgrad der Brennkraftmaschine gegenüber einer herkömmlichen Brennkraftmaschine mit vergleichbarer Nennleistung verbessert und eine erhebliche Treibstoffeinsparung ermöglicht.In such internal combustion engines, the heat energy contained in the hot exhaust gases of an internal combustion engine, such as a diesel or gasoline engine is supplied to a Stirling engine (hot air engine) and converted via this into usable mechanical rotational energy, which can be used, for example, to drive a hydraulic pump of a hydraulic system. As a result, the overall efficiency of the internal combustion engine compared with a conventional internal combustion engine is improved with comparable nominal power and allows a significant fuel economy.
Aus der DE 197 32 307 Al ist beispielsweise eine Brennkraftmaschine mit einer Abgase leitenden Abgasanlage und einem Stirlingmotor als Hilfsaggregat bekannt, bei der die im Abgas des Verbrennungsmotors enthaltene Wärmemenge dem Stirlingmotor über eine Heatpipe zugeführt und in mechanische Nutzenergie, beispielsweise zum Antrieb einer Hydraulikpumpe, umgewandelt wird. Nachteilig bei derartigen Brennkraftmaschinen ist, dass die hydraulische Leistung der von dem Stirlingmotor angetriebenen Hydraulikpumpe aufgrund der bauartbedingt begrenzten Leistung des Stirlingmotors nicht ausreicht, um das Hydrauliksystem, beispielsweise eines landwirtschaftlichen Nutzfahrzeugs oder mobilen Arbeitsgeräts, hinreichend zu versorgen .From DE 197 32 307 Al, for example, an internal combustion engine with an exhaust gas conducting exhaust system and a Stirling engine as an auxiliary unit is known in which the amount of heat contained in the exhaust gas of the engine supplied to the Stirling engine via a heat pipe and converted into mechanical useful energy, for example, to drive a hydraulic pump becomes. A disadvantage of such internal combustion engines is that the hydraulic power of the driven by the Stirling engine hydraulic pump due to the design-limited performance of the Stirling engine is not sufficient to the hydraulic system, such as an agricultural Commercial vehicle or mobile implement, to provide adequate.
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Brennkraftmaschine zu schaffen, die eine verbesserte Hydraulikversorgung eines Hydrauliksystems bei minimalem vorrichtungstechnischem Aufwand ermöglicht.In contrast, the present invention seeks to provide an internal combustion engine, which allows an improved hydraulic supply of a hydraulic system with minimal device complexity.
Diese Aufgabe wird durch eine Brennkraftmaschine mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by an internal combustion engine having the features of patent claim 1.
Die erfindungsgemäße Brennkraftmaschine hat einen Antriebsstrang und eine Abgase leitende Abgasanlage, wobei die im Abgas enthaltene Wärmemenge einem Stirlingmotor zum Antrieb einer ersten Hydraulikpumpe zugeführt wird. Erfindungsgemäß ist zumindest eine weitere Hydraulikpumpe vorgesehen, die mit dem Antriebsstrang der Brennkraftmaschine in Wirkverbindung steht. Das heißt, bei dieser Lösung erfolgt die Versorgung des Hydrauliksystems im Unterschied zum Stand der Technik gemäß der DE 197 32 307 Al zusätzlich über zumindest eine direkt über die Brennkraftmaschine angetriebene Hydraulikpumpe. Die über die Brennkraftmaschine angetriebene Hydraulikpumpe gewährleistet auch bei hohem Leistungsbedarf eine ausreichende Druckmittelversorgung des Hydrauliksystems.The internal combustion engine according to the invention has a drive train and an exhaust gas exhaust system, wherein the amount of heat contained in the exhaust gas is supplied to a Stirling engine for driving a first hydraulic pump. According to the invention, at least one further hydraulic pump is provided, which is in operative connection with the drive train of the internal combustion engine. That is, in this solution, the supply of the hydraulic system takes place in contrast to the prior art according to DE 197 32 307 Al additionally via at least one directly via the internal combustion engine driven hydraulic pump. The driven via the internal combustion engine hydraulic pump ensures a sufficient pressure medium supply of the hydraulic system even at high power requirements.
Gemäß einem besonders bevorzugten Ausführungsbeispiel der Erfindung sind die Hydraulikpumpen zum Laden zumindest eines Druckmittelspeichers einer Zentralhydraulik eines Fahrzeugs oder eines Arbeitsgeräts vorgesehen. Durch den Einsatz von Druckmittelspeichern kann die Pumpenleistung auf den mittleren Leistungsbedarf der Verbraucher gesenkt werden, da der von den Pumpen geförderte Volumenstrom den Speicher lädt, wenn der für die Verbraucher benötigte Volumenstrom zeitweise kleiner ist als der Pumpenvolumenstrom.According to a particularly preferred embodiment of the invention, the hydraulic pumps are provided for charging at least one pressure fluid accumulator of a central hydraulic system of a vehicle or a working device. The use of accumulators reduces the pump performance to the average power requirement of the consumer be because the volume flow pumped by the pump loads the memory when the volume flow required for the consumer is temporarily smaller than the pump volume flow.
Einer der Druckmittelspeicher ist vorzugsweise als Hochdruckspeicher und ein weiterer Druckmittelspeicher als Niederdruckspeicher ausgebildet. Vorzugsweise sind die Saugseiten der Hydraulikpumpen mit dem Niederdruckspeicher und die Druckseiten mit dem Hochdruckspeicher verbunden.One of the accumulator is preferably designed as a high-pressure accumulator and another accumulator as a low-pressure accumulator. Preferably, the suction sides of the hydraulic pumps are connected to the low pressure accumulator and the pressure sides to the high pressure accumulator.
In den Druckmittelleitungen des Hochdruckspeichers ist vorzugsweise jeweils ein in Richtung der Hydraulikpumpen sperrendes Rückschlagventil angeordnet. Die Rückschlagventile dienen zur Absperrung unter Druck stehender Arbeitskreise und verhindern einen Druckverlust des Druckmittelspeichers über die Pumpen.In the pressure medium lines of the high-pressure accumulator is preferably arranged in each case one blocking in the direction of the hydraulic pump check valve. The non-return valves are used to shut off working groups under pressure and prevent pressure loss of the accumulator via the pumps.
Vorzugsweise sind die Druckmittelspeicher als Membranoder Blasenspeicher ausgebildet, so dass diese einen vergleichsweise einfachen Aufbau und geringen Bauraumbedarf aufweisen .Preferably, the pressure fluid storage are designed as a membrane or bladder accumulator, so that they have a comparatively simple structure and low space requirement.
Der Stirlingmotor ist bei einem erfindungsgemäßen Ausführungsbeispiel über eine Antriebswelle mit der ersten Hydraulikpumpe verbunden. Dadurch kann die Hydraulikpumpe räumlich beabstandet von dem Stirlingmotor angeordnet sein.The Stirling engine is connected in an embodiment of the invention via a drive shaft with the first hydraulic pump. As a result, the hydraulic pump can be arranged spatially spaced from the Stirling engine.
Als besonders vorteilhaft hat es sich erwiesen, wenn die zweite Hydraulikpumpe über eine Außenzahnradanordnung von dem Antriebsstrang angetrieben ist. Die im Abgas enthaltene Wärmemenge wird bei einem bevorzugten Ausführungsbeispiel einem Erhitzer des Stirlingmotors zugeführt.It has proven to be particularly advantageous if the second hydraulic pump is driven by an external gear arrangement of the drive train. The amount of heat contained in the exhaust gas is supplied in a preferred embodiment, a heater of the Stirling engine.
Vorzugsweise ist der Erhitzer des Stirlingmotors im Abgasstrom der Brennkraftmaschine angeordnet, so dass ein direkter Wärmeübergang von dem Abgasstrom zu dem Erhitzer erfolgt und ein hoher Wirkungsgrad des Stirlingmotors gewährleistet ist.Preferably, the heater of the Stirling engine is arranged in the exhaust gas flow of the internal combustion engine, so that a direct heat transfer from the exhaust gas flow to the heater takes place and a high efficiency of the Stirling engine is ensured.
Gemäß einer Variante der Erfindung ist der Erhitzer derart an einem Abgasrohr der Abgasanlage angeordnet, dass der Erhitzer das Abgasrohr zumindest abschnittsweise ringförmig umgibt . Dadurch wird eine große Wärmeübertragungsfläche zwischen Abgasrohr und Erhitzer erreicht, ohne die Abgasströmung im Abgasrohr zu beeinflussen. *-According to a variant of the invention, the heater is arranged on an exhaust pipe of the exhaust system such that the heater surrounds the exhaust pipe at least in sections annularly. As a result, a large heat transfer area between the exhaust pipe and heater is achieved without affecting the exhaust gas flow in the exhaust pipe. * -
Bei einem bevorzugten Ausführungsbeispiel der Brennkraftmaschine wird der Luftüberschuss im Abgas für eine Nachverbrennung ausgenutzt, um den Wirkungsgrad des Stirlingmotors im Teillastbetrieb und bei sinkender Abgastemperatur zu verbessern. Hierzu wird vor dem Erhitzer des Stirlingmotors zumindest ein Brenner in der Abgasanlage vorgesehen, in den entsprechend dem jeweiligen Restluftanteil zugemessener Brennstoff zugesetzt und verbrannt wird, so dass der Stirlingmotor im für den Wirkungsgrad optimalen Temperaturbereich betrieben wird.In a preferred embodiment of the internal combustion engine, the excess air in the exhaust gas is utilized for afterburning in order to improve the efficiency of the Stirling engine in partial load operation and with decreasing exhaust gas temperature. For this purpose, at least one burner in the exhaust system is provided in front of the heater of the Stirling engine, is added to the fuel in accordance with the respective residual air content and burned, so that the Stirling engine is operated in the optimal temperature range for the efficiency.
Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche. Nachstehend wird die Erfindung anhand eines bevorzugten Ausführungsbeispiels näher erläutert. Die einzige Figur zeigt eine schematische Darstellung eines Schaltbildes einer erfindungsgemäßen Brennkraftmaschine .Other advantageous developments of the invention are the subject of further subclaims. The invention will be explained in more detail below with reference to a preferred embodiment. The single FIGURE shows a schematic representation of a circuit diagram of an internal combustion engine according to the invention.
Die Figur zeigt eine schematische Darstellung einer erfindungsgemäßen Brennkraftmaschine 1, wie sie beispielsweise in einem Kraftfahrzeug oder einem mobilen Arbeitsgerät (nicht dargestellt) Verwendung findet. Die Brennkraftmaschine 1 hat einen Antriebsstrang 2 und eine Abgase 4 leitende Abgasanlage 6, wobei die im Abgasstrahl enthaltene Wärmemenge einem Stirlingmotor 8 zum Antrieb einer ersten Hydraulikpumpe 10 eines Hydrauliksystems 12 zugeführt wird. Der Stirlingmotor 8 ist über eine Antriebswelle 14 mit der Hydraulikpumpe 10 verbunden, so dass diese räumlich beabstandet von dem Stirlingmotor 8 angeordnet ist. Die im Abgas 4 enthaltene Wärmemenge wird dem Stirlingmotor 8 über einen nicht dargestellten Erhitzer zumindest teilweise zugeführt, so dass sich über den Stirlingmotor 8 ein Temperaturgefälle ΔT in der Abgasströmung einstellt. Der Erhitzer ist derart an einem Abgasrohr 16 der Abgasanlage 6 angeordnet, dass er dieses zumindest abschnittsweise etwa ringförmig umgibt. Dadurch wird eine große Wärmeübertragungsfläche zwischen Abgasrohr 16 und Erhitzer erreicht, ohne die Abgasströmung im Abgasrohr 16 zu beeinflussen. Gemäß einer nicht dargestellten Variante der Erfindung ist der Erhitzer im Abgasstrom der Brennkraftmaschine 1 angeordnet, so dass ein direkter Wärmeübergang von dem Abgas 4 zu dem Erhitzer erfolgt und ein verbesserter Wirkungsgrad des Stirlingmotors 8 erreicht wird. Erfindungsgemäß ist eine zweite Hydraulikpumpe 18 vorgesehen, die mit dem Antriebsstrang 2 der Brennkraftmaschine 1 in Wirkverbindung steht, um auch bei hohem .Leistungsbedarf eine ausreichende Druckmittelversorgung des Hydrauliksystems 12 zu gewährleisten. Diese zusätzliche Hydraulikpumpe 18 wird von dem Antriebsstrang 2 der Brennkraftmaschine 1 über eine Außenzahnradanordnung 20 angetrieben.The figure shows a schematic representation of an internal combustion engine 1 according to the invention, as used for example in a motor vehicle or a mobile implement (not shown). The internal combustion engine 1 has a drive train 2 and an exhaust gas 4 conducting exhaust system 6, wherein the amount of heat contained in the exhaust gas stream is fed to a Stirling engine 8 for driving a first hydraulic pump 10 of a hydraulic system 12. The Stirling engine 8 is connected via a drive shaft 14 to the hydraulic pump 10 so that it is spatially spaced from the Stirling engine 8. The amount of heat contained in the exhaust gas 4 is at least partially supplied to the Stirling engine 8 via a heater, not shown, so that sets a temperature gradient .DELTA.T in the exhaust gas flow via the Stirling engine 8. The heater is arranged on an exhaust pipe 16 of the exhaust system 6, that it surrounds this at least partially approximately annular. Thereby, a large heat transfer area between the exhaust pipe 16 and heater is achieved without affecting the exhaust gas flow in the exhaust pipe 16. According to a variant of the invention, not shown, the heater is arranged in the exhaust stream of the internal combustion engine 1, so that a direct heat transfer from the exhaust gas 4 to the heater takes place and an improved efficiency of the Stirling engine 8 is achieved. According to the invention, a second hydraulic pump 18 is provided, which is connected to the drive train 2 of the internal combustion engine 1 in FIG Active connection is to ensure a sufficient pressure medium supply of the hydraulic system 12 even at high. This additional hydraulic pump 18 is driven by the drive train 2 of the internal combustion engine 1 via an external gear arrangement 20.
Bei dem gezeigten Ausführungsbeispiel der Erfindung werden die Hydraulikpumpen 10, 18 zum Laden eines Hochdruckspeichers 22 einer Zentralhydraulik des Fahrzeugs oder mobilen Arbeitsgeräts verwendet. Hierzu sind die Druckseiten der Pumpen 10, 18 über jeweils eine Druckmittelleitung 24, 26 mit dem Hochdruckspeicher 22 verbunden. Die Arbeitsleitungen zur Versorgung der Verbraucher und die Rücklaufleitungen des Hydrauliksystems 12 sind nicht dargestellt. In den Druckmittelleitungen 24, 26 sind in Richtung der Hydraulikpumpen 10, 18 sperrende Rückschlagventile 28, 30 vorgesehen, die ein Entladen des Hochdruckspeichers 22 über die Pumpen 10, 18 verhindern. Die Saugseite der der Brennkraftmaschine 1 zugeordneten Hydraulikpumpe 18 ist über eine Versorgungsleitung 32 mit einem Niederdruckspeicher 34 verbunden. Von der Versorgungsleitung 32 zweigt eine Zuführleitung 36 zu der Saugseite der über die Antriebswelle 14 mit dem Stirlingmotor 8 verbundenen Hydraulikpumpe 10 ab. Die beiden als Membran- oder Blasenspeicher ausgebildeten Druckmittelspeicher 22, 34 weisen einen vergleichsweise einfachen Aufbau bei geringem Bauraumbedarf auf .In the illustrated embodiment of the invention, the hydraulic pumps 10, 18 are used to charge a high-pressure accumulator 22 of a central hydraulic system of the vehicle or mobile implement. For this purpose, the pressure sides of the pumps 10, 18 via a respective pressure medium line 24, 26 connected to the high-pressure accumulator 22. The working lines for supplying the consumers and the return lines of the hydraulic system 12 are not shown. In the pressure medium lines 24, 26 are provided in the direction of the hydraulic pumps 10, 18 blocking check valves 28, 30, which prevent discharge of the high-pressure accumulator 22 via the pumps 10, 18. The suction side of the internal combustion engine 1 associated hydraulic pump 18 is connected via a supply line 32 to a low pressure accumulator 34. From the supply line 32, a supply line 36 branches off to the suction side of the hydraulic pump 10 connected to the Stirling engine 8 via the drive shaft 14. The two formed as a membrane or bladder accumulator accumulator 22, 34 have a comparatively simple structure with low space requirement.
Die erfindungsgemäße Brennkraftmaschine 1 ist nicht auf das beschriebene Hydrauliksystem 12 mit zwei Hydraulikpumpen 10, 18 beschränkt, vielmehr können dem Antriebsstrang 2 mehr als eine Hydraulikpumpe zugeordnet sein, sowie mehrere Stirlingmotoren 8 zum Antrieb jeweils einer Pumpe in Wirkverbindung mit der Abgasanlage 6 stehen.The internal combustion engine 1 according to the invention is not limited to the described hydraulic system 12 with two hydraulic pumps 10, 18, but can be assigned to the drive train 2 more than one hydraulic pump be, as well as several Stirling engines 8 for driving each of a pump in operative connection with the exhaust system 6 are.
Offenbart ist eine Brennkraftmaschine 1, insbesondere für ein Kraftfahrzeug oder ein mobiles Arbeitsgerät, mit einem Antriebsstrang 2 und einer Abgase 4 leitenden Abgasanlage 6, 'wobei die im Abgas 4 enthaltene Wärmemenge einem Stirlingmotor 8 zum Antrieb einer ersten Hydraulikpumpe 10 zugeführt wird. Erfindungsgemäß ist zumindest eine weitere Hydraulikpumpe 18 vorgesehen, die von dem Antriebsstrang 2 der Brennkraftmaschine 1 angetrieben ist. Disclosed is an internal combustion engine 1, in particular for a motor vehicle or a mobile working device, with a drive train 2 and an exhaust gas 4 conductive exhaust system 6, 'wherein the amount of heat contained in the exhaust gas 4 is fed to a Stirling engine 8 for driving a first hydraulic pump 10. According to the invention, at least one further hydraulic pump 18 is provided, which is driven by the drive train 2 of the internal combustion engine 1.

Claims

Ansprüche claims
1. Brennkraftmaschine, insbesondere für ein Kraftfahrzeug oder ein mobiles Arbeitsgerät, mit einem Antriebsstrang (2) und einer Abgase (4) leitenden Abgasanlage (6), wobei die im Abgas (4) enthaltene Wärmemenge einem Stirlingmotor (8) zum Antrieb einer ersten Hydraulikpumpe (10) zugeführt wird, gekennzeichnet durch zumindest eine weitere Hydraulikpumpe (18), die von dem Antriebsstrang (2) der Brennkraftmaschine (1) angetrieben ist.1. Internal combustion engine, in particular for a motor vehicle or a mobile working device, with a drive train (2) and an exhaust gas (4) conductive exhaust system (6), wherein the exhaust gas (4) contained heat amount of a Stirling engine (8) for driving a first hydraulic pump (10), characterized by at least one further hydraulic pump (18) which is driven by the drive train (2) of the internal combustion engine (1).
2. Brennkraftmaschine nach Anspruch 1, wobei die Hydraulikpumpen (10, 18) zum Laden zumindest eines Druckmittelspeichers (22, 34) einer Zentralhydraulik eines Fahrzeugs oder eines Arbeitsgeräts vorgesehen sind.2. Internal combustion engine according to claim 1, wherein the hydraulic pumps (10, 18) for charging at least one pressure medium reservoir (22, 34) of a central hydraulic system of a vehicle or a working device are provided.
3. Brennkraftmaschine nach Anspruch 2, wobei ein Druckmittelspeicher als Hochdruckspeicher (22) und ein Druckmittelspeicher als Niederdruckspeicher (34) ausgebildet ist.3. Internal combustion engine according to claim 2, wherein a pressure medium accumulator as a high pressure accumulator (22) and a pressure medium accumulator as a low pressure accumulator (34) is formed.
4. Brennkraftmaschine nach Anspruch 3 , wobei die Saugseiten der Hydraulikpumpen (10, 18) mit dem Niederdruckspeicher (34) und die Druckseiten mit dem Hochdruckspeicher (22) verbunden sind.4. Internal combustion engine according to claim 3, wherein the suction sides of the hydraulic pumps (10, 18) with the low pressure accumulator (34) and the pressure sides with the high pressure accumulator (22) are connected.
5. Brennkraftmaschine nach einem der Ansprüche 2 bis 4, wobei in mit dem Hochdruckspeicher (22) verbundenen Druckmittelleitungen (24, 26) jeweils ein in Richtung der Hydraulikpumpen (10, 18) sperrendes Rückschlagventil (28, 30) angeordnet ist. 5. Internal combustion engine according to one of claims 2 to 4, wherein in the high-pressure accumulator (22) connected to pressure medium lines (24, 26) in each case one in the direction of the hydraulic pumps (10, 18) blocking check valve (28, 30) is arranged.
6. Brennkraftmaschine nach einem der Ansprüche 2 bis 5, wobei die Druckmittelspeicher (22, 34) als Membranoder Blasenspeicher ausgebildet sind.6. Internal combustion engine according to any one of claims 2 to 5, wherein the pressure fluid reservoir (22, 34) are formed as a membrane or bladder accumulator.
7. Brennkraftmaschine nach einem der vorhergehenden Ansprüche, wobei der Stirlingmotor (8) über eine Antriebswelle (14) mit der ersten Hydraulikpumpe (10) verbunden ist.7. Internal combustion engine according to one of the preceding claims, wherein the Stirling engine (8) via a drive shaft (14) with the first hydraulic pump (10) is connected.
8. Brennkraftmaschine nach einem der vorhergehenden Ansprüche, wobei die zweite Hydraulikpumpe (18) von dem Antriebsstrang (2) über eine Außenzahnradanordnung (20) angetrieben ist.8. Internal combustion engine according to one of the preceding claims, wherein the second hydraulic pump (18) from the drive train (2) via an external gear assembly (20) is driven.
9. Brennkraftmaschine nach einem der vorhergehenden Ansprüche, wobei die im Abgas (4) enthaltene Wärmemenge einem Erhitzer des Stirlingmotors (8) zugeführt wird.9. Internal combustion engine according to one of the preceding claims, wherein the amount of heat contained in the exhaust gas (4) is supplied to a heater of the Stirling engine (8).
10. Brennkraftmaschine nach Anspruch 9, wobei der Erhitzer des Stirlingmotors (8) im Abgasstrom angeordnet ist.10. Internal combustion engine according to claim 9, wherein the heater of the Stirling engine (8) is arranged in the exhaust gas stream.
11. Brennkraftmaschine nach Anspruch 9, wobei der Erhitzer ein Abgasrohr (16) der Abgasanlage (6) zumindest abschnittsweise ringförmig umgibt.11. Internal combustion engine according to claim 9, wherein the heater surrounds an exhaust pipe (16) of the exhaust system (6) at least partially annular.
12. Brennkraftmaschine nach einem der Ansprüche 9 bis 11, wobei in der Abgasanlage (6) vor dem Erhitzer des Stirlingmotors (8) zumindest ein Brenner zur Verbrennung zugesetzten Brennstoffs mit dem Restluftgehalt im Abgas (4) vorgesehen ist. 12. Internal combustion engine according to one of claims 9 to 11, wherein in the exhaust system (6) before the heater of the Stirling engine (8) at least one burner for combustion added fuel with the residual air content in the exhaust gas (4) is provided.
PCT/EP2007/000143 2006-01-31 2007-01-10 Internal combustion engine WO2007087963A1 (en)

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DE102006004422.3 2006-01-31
DE200610004422 DE102006004422A1 (en) 2006-01-31 2006-01-31 Combustion engine especially for a motor vehicle or mobile work unit has Stirling engine to drive hydraulic pump and additional hydraulic pump driven by combustion engine drive train

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