JP4758828B2 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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JP4758828B2
JP4758828B2 JP2006155061A JP2006155061A JP4758828B2 JP 4758828 B2 JP4758828 B2 JP 4758828B2 JP 2006155061 A JP2006155061 A JP 2006155061A JP 2006155061 A JP2006155061 A JP 2006155061A JP 4758828 B2 JP4758828 B2 JP 4758828B2
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engine
hydraulic machine
hydraulic
exhaust
load
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JP2006342801A (en
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ゼンゲン マチアス
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MAN B&W Diesel GmbH
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MAN B&W Diesel GmbH
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    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/10—Engines with prolonged expansion in exhaust turbines
    • 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
    • F02B37/14—Control of the alternation between or the operation of exhaust drive and other drive of a pump, e.g. dependent on speed
    • 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
    • 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
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • 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
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • F02B37/105—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump exhaust drive and pump being both connected through gearing to engine-driven shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
    • 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

Description

本発明は排気駆動過給式内燃機関に関する。   The present invention relates to an exhaust-drive supercharged internal combustion engine.

内燃機関の効率を高めるべく、内燃機関に排気駆動過給機を装備することは従来から公知である。排気駆動過給運転ないしターボチャージ運転の場合、エンジンから排出される排気ガスが排気駆動過給機のタービンで膨張し、その際、タービンがエンジンに供給すべき燃焼空気を圧縮する圧縮機を駆動する。この圧縮済み燃焼空気を所定の温度に冷却するため、排気駆動過給機の圧縮機とエンジンとの間にインタクーラが接続されている。かかる排気駆動過給運転ないしターボチャージ運転により、内燃機関の効率が向上する。   In order to increase the efficiency of an internal combustion engine, it is conventionally known to equip an internal combustion engine with an exhaust drive supercharger. In the case of exhaust drive supercharging operation or turbo charge operation, exhaust gas discharged from the engine expands in the turbine of the exhaust drive supercharger, and at that time, the turbine drives the compressor that compresses the combustion air to be supplied to the engine To do. In order to cool the compressed combustion air to a predetermined temperature, an intercooler is connected between the compressor of the exhaust drive supercharger and the engine. The efficiency of the internal combustion engine is improved by the exhaust drive supercharging operation or the turbo charge operation.

排気駆動過給機は、排気駆動過給機が内燃機関のエンジンにおける最良の空燃比を得るために必要ない余剰動力を用意する程の高い効率を示す。その余剰動力を利用すべく、特許文献１は、排気駆動過給機で発生した余剰動力を駆動動力に転換するため、排気駆動過給機に液圧ポンプを連結し、内燃機関の駆動軸に液圧モータを連結することを開示している。更に特許文献１は、排気ガスエネルギが不足している内燃機関の運転時、排気駆動過給機に連結された液圧ポンプを、駆動軸に連結された液圧モータから切り離し、液圧ポンプを電動補助ポンプによってモータとして駆動することを提案している。
独国特許第３５３２９３８号明細書 Exhaust-driven superchargers exhibit such high efficiency that they provide excess power that is not necessary for the exhaust-driven supercharger to obtain the best air-fuel ratio in the engine of an internal combustion engine. In order to use the surplus power, Patent Document 1 discloses that in order to convert surplus power generated in the exhaust drive supercharger into drive power, a hydraulic pump is connected to the exhaust drive supercharger, and the drive shaft of the internal combustion engine is connected. It discloses disclosing a hydraulic motor. Furthermore, Patent Document 1 discloses that during operation of an internal combustion engine that lacks exhaust gas energy, the hydraulic pump connected to the exhaust drive supercharger is disconnected from the hydraulic motor connected to the drive shaft, and the hydraulic pump is It has been proposed to be driven as a motor by an electric auxiliary pump.
German Patent No. 3532938

上述の点から出発して、本発明の課題は、新しい内燃機関を提供することにある。   Starting from the above points, the object of the present invention is to provide a new internal combustion engine.

この課題は請求項１に記載の内燃機関により解決される。本発明に従う内燃機関はエンジンと排気駆動過給機とを利用し、エンジンは燃料を燃焼させて燃料燃焼で生じた動力でエンジンの駆動軸を駆動し、排気駆動過給機は内燃機関のエンジンから出る排気ガス流をタービン内で膨張させ、その際に得られた動力で、エンジンに供給する燃焼空気流を圧縮すべく圧縮機を駆動し、排気駆動過給機のタービンロータと圧縮機インペラで形成された排気駆動過給機ランナは第１液圧機械に連結され、エンジンの駆動軸は第２液圧機械に連結される。エンジンがその負荷上限値より大きな負荷で運転されているとき、排気駆動過給機ランナに連結された第１液圧機械が、液圧を発生するジェネレータ運転で排気駆動過給機ランナから機械的動力を取り出して液圧動力に転換し、この液圧動力が、エンジンの駆動軸に連結された第２液圧機械のモータ運転で機械的動力に転換され、駆動軸に伝達されこれを駆動する。エンジンがエンジン負荷下限値より小さな負荷で運転されているとき、エンジンの駆動軸に連結された第２液圧機械のジェネレータ運転で駆動軸から機械的動力を取り出して液圧動力に転換し、この液圧動力が、排気駆動過給機ランナに連結された第１液圧機械の、液圧を回転力に変換するモータ運転で機械的動力に転換され、排気駆動過給機に伝達されてこれを駆動する。排気駆動過給機ランナに連結された第１液圧機械と、駆動軸に連結された第２液圧機械とは、エンジン油槽を介在してエンジン油回路の油管を介して接続されている。   This problem is solved by the internal combustion engine according to claim 1. An internal combustion engine according to the present invention uses an engine and an exhaust driving supercharger, the engine burns fuel and drives the drive shaft of the engine with power generated by the fuel combustion, and the exhaust driving supercharger is an engine of the internal combustion engine. The exhaust gas flow coming out of the turbine is expanded in the turbine, and the compressor is driven by the power obtained at that time to compress the combustion air flow supplied to the engine. The turbine rotor and the compressor impeller of the exhaust drive supercharger The exhaust-drive supercharger runner formed in the above is connected to the first hydraulic machine, and the drive shaft of the engine is connected to the second hydraulic machine. When the engine is operated at a load greater than its upper load limit, the first hydraulic machine connected to the exhaust drive supercharger runner is mechanically driven from the exhaust drive supercharger runner by a generator operation that generates hydraulic pressure. The power is taken out and converted into hydraulic power. This hydraulic power is converted into mechanical power by the motor operation of the second hydraulic machine connected to the drive shaft of the engine, and transmitted to the drive shaft to drive it. . When the engine is operated at a load smaller than the engine load lower limit value, mechanical power is taken out of the drive shaft by the generator operation of the second hydraulic machine connected to the drive shaft of the engine, and converted to hydraulic power. The hydraulic power is converted into mechanical power by the motor operation of the first hydraulic machine connected to the exhaust-drive supercharger runner, which converts the hydraulic pressure into rotational force, and is transmitted to the exhaust-drive supercharger. Drive. The first hydraulic machine connected to the exhaust drive supercharger runner and the second hydraulic machine connected to the drive shaft are connected via an oil pipe of an engine oil circuit with an engine oil tank interposed therebetween.

このため本発明による内燃機関では、排気駆動過給機ランナに連結された第１液圧機械および駆動軸に連結された第２液圧機械が、内燃機関のエンジン負荷上限値より大きな負荷運転時並びにエンジン負荷下限値より小さな負荷運転時、エンジン油回路の油管並びにエンジン油回路のエンジン油槽を介して接続される。本発明に従い、従来の特許文献１における技術で必要であった補助ポンプ等の別個の液圧配管が省かれる。この結果内燃機関の構造は著しく単純になる。排気駆動過給機を駆動軸に液圧的に連結するためにエンジン油回路を利用することで、内燃機関の構造を非常にコンパクトになし得る。   Therefore, in the internal combustion engine according to the present invention, when the first hydraulic machine connected to the exhaust-drive supercharger runner and the second hydraulic machine connected to the drive shaft are in a load operation larger than the engine load upper limit value of the internal combustion engine. In addition, during a load operation smaller than the engine load lower limit value, connection is made via an oil pipe of the engine oil circuit and an engine oil tank of the engine oil circuit. In accordance with the present invention, separate hydraulic piping such as an auxiliary pump, which was necessary with the technique in the prior art document 1, is omitted. As a result, the structure of the internal combustion engine is significantly simplified. By using the engine oil circuit to hydraulically connect the exhaust drive supercharger to the drive shaft, the structure of the internal combustion engine can be made very compact.

本発明の有利な実施態様を従属請求項および以下の説明から明らかにする。次に図を参照して本発明の実施例を詳細に説明するが、本発明はこれに限定されない。   Advantageous embodiments of the invention emerge from the dependent claims and the following description. Next, examples of the present invention will be described in detail with reference to the drawings, but the present invention is not limited to these.

以下図１〜図４を参照して本発明を詳細に説明する。   Hereinafter, the present invention will be described in detail with reference to FIGS.

図１および図２は、本発明に基づく内燃機関１０の第１実施例を、２つの異なった運転状態について示している。内燃機関１０はエンジン１１を利用し、該エンジン１１は燃料を燃焼させ、その燃焼で発生した動力で、エンジン１０のクランク軸ないし駆動軸１２を駆動する。また内燃機関１０は排気駆動過給機１３を利用し、該過給機１３はタービンと圧縮機を備えている。内燃機関１０のエンジン１１から出る排気ガス流が排気駆動過給機１３のタービン内で膨張し、その際に生じた動力が、エンジン１１に供給する燃焼空気流を圧縮すべく、排気駆動過給機の圧縮機に供給される。排気駆動過給機１３のタービンロータと圧縮機インペラは軸を介して連結され、排気駆動過給機１３の所謂排気駆動過給機ランナを形成している。   1 and 2 show a first embodiment of an internal combustion engine 10 according to the invention for two different operating conditions. The internal combustion engine 10 uses an engine 11, which burns fuel and drives the crankshaft or drive shaft 12 of the engine 10 with the power generated by the combustion. The internal combustion engine 10 uses an exhaust drive supercharger 13, and the supercharger 13 includes a turbine and a compressor. The exhaust gas flow coming out of the engine 11 of the internal combustion engine 10 expands in the turbine of the exhaust drive supercharger 13, and the power generated at that time compresses the combustion air flow supplied to the engine 11 so that the exhaust drive supercharge Supplied to the compressor of the machine. The turbine rotor of the exhaust drive supercharger 13 and the compressor impeller are connected via a shaft to form a so-called exhaust drive supercharger runner of the exhaust drive supercharger 13.

図１および図２において、排気駆動過給機１３にクラッチ１４を介して第１液圧機械１５が連結されている。また、エンジン１１の駆動軸１２にクラッチ１６を介して第２液圧機械１７が連結されている。両液圧機械１５、１７はジェネレータ運転並びにモータ運転で駆動でき、内燃機関１０のエンジン油回路のエンジン油槽１８に油管１９〜２１（図１参照）ないし油管２２〜２４（図２参照）を介して接続されている。   1 and 2, a first hydraulic machine 15 is connected to an exhaust drive supercharger 13 via a clutch 14. A second hydraulic machine 17 is connected to the drive shaft 12 of the engine 11 via a clutch 16. Both hydraulic machines 15 and 17 can be driven by generator operation and motor operation, and are connected to an engine oil tank 18 of an engine oil circuit of the internal combustion engine 10 via oil pipes 19 to 21 (see FIG. 1) to oil pipes 22 to 24 (see FIG. 2). Connected.

図１は、エンジン１１がエンジン全負荷の好適には８５％のエンジン負荷上限値より大きな負荷で運転されている運転状態にある内燃機関を示しれている。この運転状態では、図１に示すように、エンジン油槽１８が油管１９を介して、排気駆動過給機１３に連結された第１液圧機械１５に接続され、該液圧機械１５が油管２０を介して、駆動軸１２に連結された第２液圧機械１７に接続され、この第２液圧機械１７が油管２１を介してエンジン油槽１８に接続されている。この場合、排気駆動過給機１３に連結された第１液圧機械１５はジェネレータ運転され、排気駆動過給機１３の機械的余剰動力が、第１液圧機械１５によって液圧動力に転換され、この動力は第２液圧機械１７のモータ運転により機械的動力に転換され、駆動軸１２に伝達されてこれを駆動する。従って、エンジン負荷上限値より大きなエンジン負荷時に、両液圧機械１５、１７により排気駆動過給機１３の機械的余剰動力が、駆動軸１２用の駆動動力に転換される。両液圧機械１５、１７は油管１９、２０、２１を介して相互に、並びにエンジン油回路のエンジン油槽１８に接続されている。   FIG. 1 shows an internal combustion engine in an operating state in which the engine 11 is operated at a load greater than the engine load upper limit, preferably 85% of the engine full load. In this operating state, as shown in FIG. 1, the engine oil tank 18 is connected to the first hydraulic machine 15 connected to the exhaust drive supercharger 13 via the oil pipe 19, and the hydraulic machine 15 is connected to the oil pipe 20. Is connected to a second hydraulic machine 17 connected to the drive shaft 12, and the second hydraulic machine 17 is connected to an engine oil tank 18 via an oil pipe 21. In this case, the first hydraulic machine 15 connected to the exhaust drive supercharger 13 is operated as a generator, and the mechanical surplus power of the exhaust drive supercharger 13 is converted into hydraulic power by the first hydraulic machine 15. This power is converted into mechanical power by the motor operation of the second hydraulic machine 17 and is transmitted to the drive shaft 12 to drive it. Therefore, when the engine load is larger than the engine load upper limit value, the mechanical surplus power of the exhaust drive supercharger 13 is converted into drive power for the drive shaft 12 by the hydraulic machines 15 and 17. Both hydraulic machines 15 and 17 are connected to each other and to an engine oil tank 18 of an engine oil circuit through oil pipes 19, 20 and 21.

エンジンがエンジン全負荷の、好適には２５％のエンジン負荷下限値より小さな負荷で運転されている場合、図２に示すように、エンジン油槽１８が油管２２を経て駆動軸１２に連結された第２液圧機械１７に接続され、この第２液圧機械１７が油管２３を経て排気駆動過給機１３に連結された第１液圧機械１５に接続され、第１液圧機械１５が油管２４を経てエンジン油槽１８に接続されている。この際、駆動軸から機械的動力を取り出し、液圧動力に転換すべく、駆動軸１２に連結された第２液圧機械１７がジェネレータ運転される。その液圧動力は、排気駆動過給機１３に連結された第１液圧機械１５によって機械的動力に転換され、排気駆動過給機１３に伝達されてこれを駆動する。従ってこの運転状態の場合も、両液圧機械１５、１７はエンジン油回路の油管を介して接続されている。   When the engine is operated at a load smaller than the engine load lower limit value, preferably 25% of the engine full load, the engine oil tank 18 is connected to the drive shaft 12 via the oil pipe 22 as shown in FIG. The second hydraulic machine 17 is connected to the first hydraulic machine 15 connected to the exhaust drive supercharger 13 via the oil pipe 23, and the first hydraulic machine 15 is connected to the oil pipe 24. And connected to the engine oil tank 18. At this time, the second hydraulic machine 17 connected to the drive shaft 12 is operated as a generator in order to take out mechanical power from the drive shaft and convert it into hydraulic power. The hydraulic power is converted into mechanical power by a first hydraulic machine 15 connected to the exhaust driving supercharger 13 and transmitted to the exhaust driving supercharger 13 to drive it. Therefore, even in this operating state, both hydraulic machines 15 and 17 are connected via the oil pipe of the engine oil circuit.

図１と２の実施例では、液圧機械１５、１７を定容積形液圧機械として形成している。両液圧機械１５、１７を貫流する流量は、可調整吸込み絞り２５、２６で調整できる。エンジン１１をエンジン負荷上限値より大きな負荷で運転している図１の運転状態では、吸込み絞り２５は活動し、吸込み絞り２６は活動していない。これに対しエンジン１１をエンジン負荷下限値より小さな負荷で運転している図２の運転状態では、吸込み絞り２６が活動し、吸込み絞り２５が活動していない。両吸込み絞り２５、２６は、油の流れ方向において各液圧機械１５、１７に前置接続されている。油管１９〜２１並びに油管２２〜２４を通る油の流れ方向を、図１および図２では油管内の矢印で示している。   In the embodiment of FIGS. 1 and 2, the hydraulic machines 15, 17 are formed as constant displacement hydraulic machines. The flow rate through the hydraulic machines 15, 17 can be adjusted by adjustable suction restrictors 25, 26. In the operating state of FIG. 1 in which the engine 11 is operated at a load larger than the engine load upper limit value, the suction throttle 25 is active and the suction throttle 26 is not active. On the other hand, in the operation state of FIG. 2 in which the engine 11 is operated with a load smaller than the engine load lower limit value, the suction throttle 26 is activated and the suction throttle 25 is not activated. Both suction throttles 25 and 26 are connected in front to the hydraulic machines 15 and 17 in the oil flow direction. The flow direction of the oil passing through the oil pipes 19 to 21 and the oil pipes 22 to 24 is indicated by arrows in the oil pipe in FIGS.

従って、本発明に基づく内燃機関では、両液圧機械は、エンジン負荷上限値より大きな負荷運転状態とエンジン負荷下限値より小さな負荷運転状態では、エンジン油回路の油管を経て互いに接続されている。本発明に従い元来存在するエンジン油回路の油管を利用することで、追加的な液圧配管を必要としない内燃機関の非常にコンパクトな構造を実現でき。この内燃機関は、コンパクトな構造と小さな単位出力当たり重量の点で優れている。   Therefore, in the internal combustion engine according to the present invention, the two hydraulic machines are connected to each other via the oil pipe of the engine oil circuit in a load operation state larger than the engine load upper limit value and a load operation state smaller than the engine load lower limit value. By utilizing the oil pipe of the engine oil circuit that originally exists in accordance with the present invention, a very compact structure of the internal combustion engine that does not require additional hydraulic piping can be realized. This internal combustion engine is excellent in terms of a compact structure and a small weight per unit output.

図３と４は、本発明に基づく内燃機関２７の異なる実施例を示す。これら図に示す実施例の内燃機関２７は、ほぼ図１と２の実施例の内燃機関１０に相当している。従って、両者における同一構造群についての重複説明を避けるべく、同一構造群に同一符号を付している。図３は、エンジン負荷上限値より大きな負荷運転状態における内燃機関、図４は、エンジン負荷下限値より小さな負荷運転状態における内燃機関を示している。以下、図３と４の内燃機関２７が図１と２の内燃機関と異なっている点だけを説明する。   3 and 4 show different embodiments of the internal combustion engine 27 according to the invention. The internal combustion engine 27 of the embodiment shown in these drawings substantially corresponds to the internal combustion engine 10 of the embodiment of FIGS. Therefore, the same reference numerals are given to the same structural groups in order to avoid redundant description of the same structural groups in both. FIG. 3 shows the internal combustion engine in a load operation state larger than the engine load upper limit value, and FIG. 4 shows the internal combustion engine in a load operation state smaller than the engine load lower limit value. Only the differences between the internal combustion engine 27 of FIGS. 3 and 4 from the internal combustion engine of FIGS. 1 and 2 will be described below.

即ち図３と４の実施例では、液圧機械１５、１７を可変容積形液圧機械として形成し、もって別個に形成した吸込み絞りを省いている。この種可変容積形液圧機械では、それを貫流する容積流量を直接調整できる。かかる可変容積形液圧機械を利用する場合、内燃機関の構造を簡素化し、構造重量を一層減少できる。   That is, in the embodiment of FIGS. 3 and 4, the hydraulic machines 15 and 17 are formed as variable displacement hydraulic machines, and the suction throttle formed separately is omitted. In this type of variable displacement hydraulic machine, the volume flow through it can be adjusted directly. When such a variable displacement hydraulic machine is used, the structure of the internal combustion engine can be simplified and the structure weight can be further reduced.

本発明に基づく内燃機関の第１実施例におけるエンジン負荷上限値より大きな負荷運転状態の概略図。1 is a schematic diagram of a load operating state larger than an engine load upper limit value in a first embodiment of an internal combustion engine according to the present invention. FIG. 図１の内燃機関におけるエンジン負荷下限値より小さな負荷運転状態の概略図。FIG. 2 is a schematic diagram of a load operation state smaller than an engine load lower limit value in the internal combustion engine of FIG. 1. 本発明に基づく内燃機関の第２実施例におけるエンジン負荷上限値より大きな負荷運転状態の概略図。Schematic of a load operation state larger than the engine load upper limit value in the second embodiment of the internal combustion engine according to the present invention. 図３の内燃機関におけるエンジン負荷下限値より小さな負荷運転状態の概略図。FIG. 4 is a schematic diagram of a load operation state smaller than an engine load lower limit value in the internal combustion engine of FIG.

符号の説明Explanation of symbols

１０、２７ 内燃機関、１１ エンジン、１２ 駆動軸、１３ 排気駆動過給機、１４、１６ クラッチ、１５、１７ 液圧機械、１８ エンジン油槽、１９〜２３ 油管、２５、２６ 吸込み絞り 10, 27 Internal combustion engine, 11 Engine, 12 Drive shaft, 13 Exhaust drive supercharger, 14, 16 Clutch, 15, 17 Hydraulic machine, 18 Engine oil tank, 19-23 Oil pipe, 25, 26 Suction throttle

Claims (3)

エンジン油槽（１８）を装備してなるエンジン（１１）と排気駆動過給機（１３）とを備え、前記エンジン（１１）で燃料を燃焼させ、当該燃焼で発生した動力によってエンジン（１１）の駆動軸（１２）を駆動し、前記排気駆動過給機（１３）が当該内燃機関における前記エンジン（１１）から排出される排気ガス流をタービン内で膨張せしめ、当該膨張の際に得られた動力によって、前記エンジンに供給すべき燃焼空気流を圧縮する圧縮機を駆動するように設定されており、かつ前記排気駆動過給機（１３）のタービンロータと圧縮機インペラとで形成された排気駆動過給機ランナが第１液圧機械（１５）に連結されていると共に、前記エンジン（１１）の前記駆動軸（１２）が第２液圧機械（１７）に連結されている内燃機関において、
（ａ） 前記エンジン（１１）が、当該エンジン（１１）における所定の負荷上限値よりも大きな負荷で運転されている状態にあるときには、前記第１液圧機械（１５）の液流出口を、前記エンジン（１１）に装備されている前記エンジン油槽（１８）を介すことなく直接に前記第２液圧機械（１７）の液流入口へと接続すると共に、前記第２液圧機械（１７）の液流出口を、前記エンジン（１１）に装備されている前記エンジン油槽（１８）を介して間接に前記第１液圧機械（１５）の液流入口に接続することで、前記排気駆動過給機ランナに連結された前記第１液圧機械（１５）を液圧ジェネレータとして機能せしめて、前記排気駆動過給機ランナの機械的動力を液圧動力に転換し、当該液圧動力を前記第２液圧機械（１７）へと直接に流体的に伝達し、当該第２液圧機械（１７）によって前記液圧動力を機械的動力に転換せしめて、当該機械的動力を前記駆動軸（１２）の軸出力に追加し、
（ｂ） 前記エンジン（１１）が、当該エンジン（１１）における所定の負荷下限値よりも小さな負荷で運転されている状態にあるときには、前記第２液圧機械（１７）の液流出口を、前記エンジン（１１）に装備されている前記エンジン油槽（１８）を介すことなく直接に前記第１液圧機械（１５）の液流入口へと接続すると共に、前記第１液圧機械（１５）の液流出口を、前記エンジン（１１）に装備されている前記エンジン油槽（１８）を介して間接に前記第２液圧機械（１７）の液流入口に接続することで、前記駆動軸（１２）に連結された前記第２液圧機械（１７）を液圧ジェネレータとして機能せしめて、前記駆動軸（１２）の機械的動力の少なくとも一部分を液圧動力に転換し、当該液圧動力を前記第１液圧機械（１５）へと直接に流体的に伝達し、当該第１液圧機械（１５）によって前記液圧動力を機械的動力に転換せしめて、当該機械的動力を前記排気駆動過給機（１３）の駆動力として用いる
ように設定されており、
かつ、
前記エンジン負荷上限値が、前記エンジン（１１）における前記圧縮機に供給される駆動力に余裕が生じる負荷の閾値である、前記エンジン（１１）の全負荷の８５％であり、前記エンジン負荷下限値が、前記エンジン（１１）における前記圧縮機に供給される駆動力に不足が生じる負荷の閾値である、前記エンジン（１１）の全負荷の２５％である
ことを特徴とする内燃機関。 It provided with an engine comprising equipped with an engine oil tank (18) (11) and the exhaust drive supercharger (13), wherein the fuel is combusted in the engine (11), the power generated in the combustion of the engine (11) drive shaft (12) driven, the exhaust drive supercharger (13) is the engine (11) exhaust gas stream that will be emitted exhaust from the said internal combustion engine inflated in the turbine, obtained during the expansion It is set so as to drive a compressor that compresses the combustion air flow to be supplied to the engine by the motive power , and is formed by a turbine rotor and a compressor impeller of the exhaust drive supercharger (13). internal combustion engine exhaust driven turbocharger runner with being connected to the first hydraulic machine (15), wherein the drive shaft of the engine (11) (12) is connected to the second hydraulic machine (17) In
(A) the engine (11), when in the state in the engine (11) is operated at high load than a predetermined load limit value, the liquid outlet of the first hydraulic machine (15) Is directly connected to the liquid inlet of the second hydraulic machine (17) without passing through the engine oil tank (18) installed in the engine (11), and the second hydraulic machine By connecting the liquid outlet of (17) indirectly to the liquid inlet of the first hydraulic machine (15) via the engine oil tank (18) equipped in the engine (11), connected to an exhaust driven supercharger runners the first hydraulic machine (15) and caused to function as a hydraulic generator, to convert the mechanical power of the exhaust drive supercharger runner hydraulic power, the hydraulic pressure Direct power to the second hydraulic machine (17) To transmit, the in allowed converted into mechanical power to the hydraulic power by a second hydraulic machine (17), to add the mechanical power to the shaft output of the drive shaft (12),
(B) the engine (11), when in the state in the engine (11) is operated with a small load than a predetermined load limit value, the liquid outlet of the second hydraulic machine (17) Is connected directly to the liquid inlet of the first hydraulic machine (15) without passing through the engine oil tank (18) provided in the engine (11), and the first hydraulic machine By connecting the liquid outlet of (15) indirectly to the liquid inlet of the second hydraulic machine (17) via the engine oil tank (18) equipped in the engine (11), which are connected to a drive shaft (12) second hydraulic machine (17) and caused to function as a hydraulic generator, and converted into hydraulic power to at least a portion of the mechanical power of the drive shaft (12), the liquid and a hydraulic power to said first hydraulic machine (15) Fluidly communicated to contact, the in allowed converted into mechanical power to the hydraulic power by a first hydraulic machine (15), using the mechanical power as a driving force of the exhaust drive supercharger (13)
Is set to
And,
The engine load upper limit, the a threshold value of the allowance to the driving force supplied to the compressor occurs load in the engine (11), 85% of the full load of the engine (11), before Symbol engine load An internal combustion engine characterized in that the lower limit value is 25% of the total load of the engine (11) , which is a threshold value of a load that causes a deficiency in the driving force supplied to the compressor in the engine (11) . 前記第１液圧機械（１５）および前記第２液圧機械（１７）が、それら自体を各々貫流する液体の容積流量を直接調節可能な可変容積形液圧機械として形成されたものである
ことを特徴とする請求項１記載の内燃機関。 It said first hydraulic machine (15) and said second hydraulic machine (17), and is formed a volumetric flow rate of the liquid respectively flowing through themselves as direct adjustable variable volume forms hydraulic machine < The internal combustion engine according to claim 1, wherein 前記第１液圧機械（１５）および前記第２液圧機械（１７）が、定容積形液圧機械として形成され、当該各液圧機械（１５、１７）には、それぞれ吸込み絞り（２５、２６）が前置接続（つまり液流入口側に配置）されている
ことを特徴とする請求項１記載の内燃機関。
 It said first hydraulic machine (15) and said second hydraulic machine (17) is formed as a constant volumetric form hydraulic machine, the said each hydraulic machine (15, 17), intake throttle, respectively (25, internal combustion engine according to claim 1, wherein <br/> that 26) is connected upstream (disposed clogging fluid inlet side).
JP2006155061A 2005-06-09 2006-06-02 Internal combustion engine Expired - Fee Related JP4758828B2 (en)

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