JP2008095683A - Internal combustion engine having exhaust recirculation system and operation method - Google Patents

Internal combustion engine having exhaust recirculation system and operation method Download PDF

Info

Publication number
JP2008095683A
JP2008095683A JP2007260651A JP2007260651A JP2008095683A JP 2008095683 A JP2008095683 A JP 2008095683A JP 2007260651 A JP2007260651 A JP 2007260651A JP 2007260651 A JP2007260651 A JP 2007260651A JP 2008095683 A JP2008095683 A JP 2008095683A
Authority
JP
Japan
Prior art keywords
exhaust
internal combustion
combustion engine
cylinder
inlet valve
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.)
Pending
Application number
JP2007260651A
Other languages
Japanese (ja)
Inventor
Thomas Seidl
ザイトル トーマス
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.)
MAN Energy Solutions France SAS
Original Assignee
MAN Diesel SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Diesel SA filed Critical MAN Diesel SA
Publication of JP2008095683A publication Critical patent/JP2008095683A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
    • F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
    • F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • 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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D23/00—Controlling engines characterised by their being supercharged
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/20—Feeding recirculated exhaust gases directly into the combustion chambers or into the intake runners
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0276—Actuation of an additional valve for a special application, e.g. for decompression, exhaust gas recirculation or cylinder scavenging

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To prevent contamination of a part for guiding combustion air in an operation method of an internal combustion engine provided with an exhaust recirculation system for extracting a partial flow from exhaust air flow of the internal combustion engine, and cooling the exhaust air partial flow by an exhaust cooler to recirculate it for reducing generation of toxic materials in the internal combustion engine, particularly, an exhaust-driven supercharging heavy fuel oil diesel engine. <P>SOLUTION: Based on the invention, a recirculation flow of a cooled exhaust partial flow is carried directly to a cylinder of the internal combustion engine. Since mixing of exhaust air with compressed combustion air on the upstream of the cylinder of the internal combustion engine is dispensed with, contamination of the part for guiding the combustion air is never caused. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、請求項１の前文に記載の排気還流系（排気再循環系）を備えた内燃機関、特に排気駆動過給式の重油燃料ディーゼルエンジンの運転方法に関する。本発明は、請求項１１の前文に記載の内燃機関にも関する。   The present invention relates to an operating method of an internal combustion engine having an exhaust gas recirculation system (exhaust gas recirculation system) described in the preamble of claim 1, particularly an exhaust drive supercharged heavy oil fuel diesel engine. The invention also relates to an internal combustion engine according to the preamble of claim 11.

実際に既に、排気還流系を備えた排気駆動過給式の内燃機関は知られている。即ち、排気還流系を備えた排気駆動過給式の内燃機関の場合、内燃機関の排気流は、排気駆動過給機のタービン内で膨張し、その際、排気駆動過給機のタービンは、内燃機関に供給すべき燃焼空気流を圧縮する圧縮機を駆動する。内燃機関の排気流から部分流が、排気駆動過給機のタービンの上流で取り出され、この部分流は圧縮済み燃焼空気流に還流（再循環）され、それと混合される。給気と排気部分流との混合は、内燃機関の上流、従ってシリンダの上流で行われる。還流された排気は不活性ガスとして作用し、内燃機関のシリンダにおける燃焼ピーク温度を低下し、もって有害物質の発生を減少する。   In fact, an exhaust-drive supercharged internal combustion engine having an exhaust gas recirculation system is already known. That is, in the case of an exhaust drive supercharged internal combustion engine equipped with an exhaust gas recirculation system, the exhaust flow of the internal combustion engine expands in the turbine of the exhaust drive supercharger, and at that time, the turbine of the exhaust drive supercharger A compressor for compressing a combustion air flow to be supplied to the internal combustion engine is driven. A partial stream is taken from the exhaust stream of the internal combustion engine upstream of the turbine of the exhaust-driven supercharger and this partial stream is recirculated (recirculated) into the compressed combustion air stream and mixed therewith. Mixing of the supply air and the exhaust partial flow takes place upstream of the internal combustion engine and thus upstream of the cylinder. The recirculated exhaust gas acts as an inert gas, lowering the combustion peak temperature in the cylinder of the internal combustion engine, thereby reducing the generation of harmful substances.

特に重油燃料ディーゼルエンジンの場合、実際に公知のこの種排気還流（排気再循環）は、重油がかなりのアスファルト、灰、硫黄を含み、このため重油の燃焼時に残滓が生ずるので問題がある。即ち、残滓は、圧縮済み燃焼空気流と還流すべき排気部分流との混合後に、燃焼空気流を案内する部品に付着し、この結果部品の機能を害する。   This type of exhaust gas recirculation (exhaust gas recirculation), which is known in practice, is particularly problematic in the case of heavy oil fueled diesel engines because the heavy oil contains significant asphalt, ash, and sulfur, and therefore residue is produced during combustion of the heavy oil. That is, the residue adheres to the component that guides the combustion air flow after mixing the compressed combustion air flow and the exhaust partial flow to be recirculated, thereby impairing the function of the component.

これは、連続して内燃機関の是認できない運転悪化を生じさせ、内燃機関についての経費のかかる点検、特に浄化作業が必要となる。   This continuously causes unacceptable operational deterioration of the internal combustion engine and requires expensive inspections, particularly purification work, for the internal combustion engine.

本発明の課題は、上述の問題から出発して、新たな排気還流系を備えた内燃機関の運転方法と新たな内燃機関を提供することにある。   An object of the present invention is to provide an operating method of an internal combustion engine having a new exhaust gas recirculation system and a new internal combustion engine, starting from the above problems.

この課題は、請求項１に記載の方法によって解決される。   This problem is solved by the method according to claim 1.

特に重油燃料ディーゼルエンジンを運転するために用いる本発明の方法では、排気再循環の目的で還流すべき排気部分流を、内燃機関のシリンダに直接導入する。本発明に基づく方法の場合、内燃機関のシリンダの上流での圧縮済み燃焼空気と排気との混合が不要となり、燃焼空気を案内する部品の汚染を防げる。   In particular, in the method of the present invention used to operate a heavy oil fuel diesel engine, an exhaust partial flow to be recirculated for the purpose of exhaust gas recirculation is introduced directly into the cylinder of the internal combustion engine. In the case of the method according to the invention, it is not necessary to mix the compressed combustion air and the exhaust upstream of the cylinder of the internal combustion engine, thus preventing contamination of the parts guiding the combustion air.

本発明の有利な実施態様では、冷却済み排気部分流を、給気行程中に４サイクル式内燃機関のシリンダに、少なくとも１個の燃焼空気入口弁が開いた状態で、各シリンダのピストンが上死点から下死点に向けて移動する内燃機関の各シリンダの給気行程中に、各シリンダの１個或いは各燃焼空気入口弁が下死点に到達する前に閉じるようにして供給し、給気行程において１個或いは各燃焼空気入口弁の閉鎖後に、冷却済み排気部分流を各シリンダに導入する。即ち、シリンダ内での燃焼空気の膨張のためにシリンダ内の圧力が還流排気圧力レベルに到達したとき又は還流排気圧力レベルより低く下がったときに導入する。   In a preferred embodiment of the invention, the cooled partial exhaust stream is fed into the cylinders of a four-stroke internal combustion engine during the charge stroke, with the pistons of each cylinder up with at least one combustion air inlet valve open. During the air supply stroke of each cylinder of the internal combustion engine moving from the dead center to the bottom dead center, one of each cylinder or each combustion air inlet valve is supplied so as to be closed before reaching the bottom dead center, After closing one or each combustion air inlet valve in the intake stroke, a cooled exhaust partial flow is introduced into each cylinder. That is, it is introduced when the pressure in the cylinder reaches the recirculation exhaust pressure level or falls below the recirculation exhaust pressure level due to the expansion of the combustion air in the cylinder.

各シリンダへの冷却済み排気部分流の還流は、シリンダ内の圧力が還流排気圧力レベルに到達したときに終了する。   The recirculation of the cooled exhaust partial flow to each cylinder ends when the pressure in the cylinder reaches the recirculation exhaust pressure level.

本発明に基づく内燃機関を請求項１１に示す。   An internal combustion engine according to the present invention is shown in claim 11.

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。以下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. Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings, but the present invention is not limited thereto.

本発明は、排気還流系（排気再循環系）を有する内燃機関、特に排気駆動過給式の重油燃料ディーゼルエンジンの運転方法に関する。かかる内燃機関の場合、排気流を排気駆動過給機に供給し、排気駆動過給機のタービンで排気流を膨張させる。排気駆動過給機のタービンは、内燃機関に供給すべき燃焼空気流ないし新鮮空気を圧縮する排気駆動過給機の圧縮機を駆動する。排気を還流する際、排気駆動過給機のタービンの上流で、内燃機関の排気流から部分流を取り出し、排気部分流を排気冷却器で冷却し、内燃機関の有害物質発生を減少するために還流（再循環）させる。その場合、本発明に基づき、冷却済みの排気部分流の還流は内燃機関のシリンダに直接行う。   The present invention relates to an internal combustion engine having an exhaust gas recirculation system (exhaust gas recirculation system), and more particularly, to an operation method of an exhaust drive supercharged heavy oil fuel diesel engine. In the case of such an internal combustion engine, an exhaust flow is supplied to an exhaust drive supercharger, and the exhaust flow is expanded by a turbine of the exhaust drive supercharger. The turbine of the exhaust drive supercharger drives the compressor of the exhaust drive supercharger that compresses the combustion air flow or fresh air to be supplied to the internal combustion engine. In order to reduce the generation of toxic substances in the internal combustion engine by extracting the partial flow from the exhaust flow of the internal combustion engine upstream of the turbine of the exhaust drive supercharger when the exhaust gas is recirculated and cooling the exhaust partial flow with an exhaust cooler Reflux (recycle). In that case, according to the present invention, the recirculation of the cooled exhaust partial flow is carried out directly to the cylinder of the internal combustion engine.

以下、本発明に基づく方法を、図１の４サイクル式内燃機関におけるインジケータ線図を参照して詳細に説明する。図１は、４サイクル式内燃機関における所謂ｐ（圧力）−Ｖ（容積）線図を示す。４サイクル式内燃機関のシリンダの動程は４つの行程、即ち、所謂吸気、圧縮、膨張および排気行程に分けられる。   Hereinafter, the method according to the present invention will be described in detail with reference to an indicator diagram in the four-cycle internal combustion engine of FIG. FIG. 1 shows a so-called p (pressure) -V (volume) diagram in a four-cycle internal combustion engine. The cylinder stroke of a four-cycle internal combustion engine is divided into four strokes, namely the so-called intake, compression, expansion and exhaust strokes.

図１のｐ−Ｖ線図は、原理的に、２つの領域、即ち所謂高圧部１０と転換給気部１１に分けられる。高圧部１０は、運転点１と運転点２との間を延びる圧縮行程と、運転点２と運転点３、運転点３と運転点３′、運転点３′と運転点４、運転点４と運転点１との間を各々延びる運転行程を有する。転換給気部１１は排気行程と給気行程を有し、排気行程は運転点１と運転点５との間、給気行程は運転点６と運転点１との間を延びている。   The pV diagram of FIG. 1 is divided in principle into two regions, namely the so-called high pressure part 10 and the conversion air supply part 11. The high pressure unit 10 includes a compression stroke extending between the operating point 1 and the operating point 2, an operating point 2 and an operating point 3, an operating point 3 and an operating point 3 ′, an operating point 3 ′ and an operating point 4, and an operating point 4. And driving points 1 and 2 respectively. The conversion air supply unit 11 has an exhaust stroke and an air supply stroke. The exhaust stroke extends between the operating point 1 and the operating point 5, and the air supply stroke extends between the operating point 6 and the operating point 1.

内燃機関のシリンダへの本発明に基づく直接的な排気還流は、４サイクル式内燃機関では、内燃機関の各シリンダの給気行程中に行う。給気行程において、各シリンダのピストンが、少なくとも１個の燃焼空気入口弁が開かれた状態で、上死点ＯＴ（運転点６）から下死点ＵＴ（運転点１）に向けて移動する。給気行程中に下死点ＵＴに到達する前に、各シリンダの１個或いは各燃焼空気入口弁が運転点７で閉じられる。   In the four-cycle internal combustion engine, the direct exhaust gas recirculation according to the present invention to the cylinder of the internal combustion engine is performed during the supply stroke of each cylinder of the internal combustion engine. In the air supply stroke, the piston of each cylinder moves from the top dead center OT (operating point 6) toward the bottom dead center UT (operating point 1) with at least one combustion air inlet valve opened. . One or each combustion air inlet valve of each cylinder is closed at the operating point 7 before reaching the bottom dead center UT during the air supply stroke.

運転点７における１個或いは各燃焼空気入口弁の閉鎖後、各シリンダのピストンが、下死点ＵＴに向けて更に移動する。この際、シリンダに吸い込まれた燃焼空気が膨張し、このためシリンダ内の圧力は、吸い込まれた燃焼空気の圧力ｐＬから出発して低下する。   After closing one or each combustion air inlet valve at the operating point 7, the piston of each cylinder further moves toward the bottom dead center UT. At this time, the combustion air sucked into the cylinder expands, so that the pressure in the cylinder decreases starting from the pressure pL of the sucked combustion air.

シリンダ内の圧力は、給気行程の運転点８で還流排気圧力レベルｐＡに到達し、シリンダ内の圧力が還流排気圧力レベルｐＡに到達し或いは還流排気圧力レベルｐＡより低く下がったとき、冷却済み排気部分流が、内燃機関の各シリンダに直接導入される。   When the pressure in the cylinder reaches the recirculation exhaust pressure level pA at the operating point 8 of the supply stroke and the pressure in the cylinder reaches the recirculation exhaust pressure level pA or falls below the recirculation exhaust pressure level pA, the cylinder is cooled. An exhaust partial flow is introduced directly into each cylinder of the internal combustion engine.

そのため、給気行程中に、各シリンダに付属する少なくとも１個の排気入口弁が開く。即ち、シリンダ内の圧力が還流排気圧力レベルｐＡに到達した際に直ぐに或いは時間的にシリンダ内の圧力が還流排気圧力レベルｐＡより低く下がった後で開かれる。   Therefore, at least one exhaust inlet valve attached to each cylinder opens during the air supply stroke. That is, it is opened as soon as the pressure in the cylinder reaches the recirculation exhaust pressure level pA or after the pressure in the cylinder drops below the recirculation exhaust pressure level pA over time.

内燃機関のシリンダへの直接的な排気還流は、各シリンダの圧力が還流排気圧力レベルｐＡに再び到達した際に終了する。これは、給気過程において、下死点ＵＴに到達する前又は下死点ＵＴに到達した後に行われ、或いは下死点ＵＴの到達後、従って、圧縮行程中でも行える。その際、各シリンダに付設した１個或いは各排気入口弁を閉鎖する。   The direct exhaust gas recirculation to the cylinders of the internal combustion engine ends when the pressure in each cylinder reaches the recirculated exhaust pressure level pA again. This can be done in the air supply process before reaching the bottom dead center UT, after reaching the bottom dead center UT, or after reaching the bottom dead center UT and thus also during the compression stroke. At that time, one or each exhaust inlet valve attached to each cylinder is closed.

シリンダの領域に殆ど局所的圧力差が存在しない故、内燃機関のシリンダへの直接的な排気還流は、各シリンダのシリンダヘッドの領域又はシリンダバレルの領域で行える。   Since there is almost no local pressure difference in the area of the cylinder, direct exhaust gas recirculation to the cylinder of the internal combustion engine can take place in the area of the cylinder head or cylinder barrel of each cylinder.

本発明の有利な発展形態では、排気流から取り出した部分流を、排気冷却器が汚染される危険を防止すべく、排気部分流を排気冷却器に導入する前に排気洗浄器に供給する。   In an advantageous development of the invention, a partial stream taken from the exhaust stream is supplied to the exhaust scrubber before it is introduced into the exhaust cooler in order to prevent the exhaust cooler from being contaminated.

本発明は、先ずは重油燃料ディーゼルエンジンの運転に適するが、オットーサイクルエンジン（ガソリンエンジン）にも採用できる。本発明に基づく方法は、内燃機関の運転に利用する燃料の種類に左右されない。   The present invention is suitable for operation of a heavy oil fuel diesel engine at first, but can also be used for an Otto cycle engine (gasoline engine). The method according to the invention does not depend on the type of fuel used for the operation of the internal combustion engine.

上記のように、内燃機関のシリンダに排気を直接導入すべく、各シリンダに少なくとも１個の排気入口弁を付設する。本発明では排気入口弁を開閉すべく、排気入口弁を、カムにより機械式に制御するか、電気或いは電子式に制御する。   As described above, at least one exhaust inlet valve is attached to each cylinder in order to directly introduce the exhaust into the cylinder of the internal combustion engine. In the present invention, in order to open and close the exhaust inlet valve, the exhaust inlet valve is controlled mechanically by a cam, or controlled electrically or electronically.

本発明に基づく排気還流系（排気再循環系）を備えた内燃機関におけるインジケータ線図（ｐ−Ｖ線図）である。It is an indicator diagram (pV diagram) in an internal combustion engine provided with an exhaust gas recirculation system (exhaust gas recirculation system) based on the present invention.

符号の説明Explanation of symbols

１〜８ 運転点、１０ 高圧部、１１ 転換給気部 1 to 8 operating points, 10 high pressure section, 11 conversion air supply section

Claims (12)

内燃機関の排気流から部分流を取り出し、この排気部分流を排気冷却器で冷却し、内燃機関の有害物質発生を減少するために還流する排気還流系を備えた内燃機関の運転方法において、
冷却済み排気部分流の還流を、内燃機関のシリンダに直接行うことを特徴とする内燃機関の運転方法。 In an operating method of an internal combustion engine having an exhaust gas recirculation system that takes out a partial flow from an exhaust flow of the internal combustion engine, cools the exhaust partial flow with an exhaust cooler, and recirculates to reduce generation of harmful substances in the internal combustion engine.
A method of operating an internal combustion engine, wherein the recirculation of the cooled exhaust partial flow is performed directly to a cylinder of the internal combustion engine. 冷却済み排気部分流を、給気行程中に４サイクル式内燃機関のシリンダに、少なくとも１個の燃焼空気入口弁が開いた状態で各シリンダにおけるピストンが上死点から下死点に向けて移動する内燃機関の各シリンダの給気行程中に、各シリンダの１個或いは各燃焼空気入口弁が下死点に到達する前に閉じるようにして供給し、給気行程において１個或いは各燃焼空気入口弁の閉鎖後に、冷却済み排気部分流を各シリンダに導入することを特徴とする請求項１記載の方法。   The cooled exhaust partial flow is moved to the cylinders of a 4-cycle internal combustion engine during the air supply stroke, and the piston in each cylinder moves from the top dead center to the bottom dead center with at least one combustion air inlet valve opened. During the intake stroke of each cylinder of the internal combustion engine, one or each combustion air inlet valve of each cylinder is supplied so as to close before reaching the bottom dead center, and one or each combustion air is supplied in the intake stroke. 2. A method according to claim 1, wherein a cooled exhaust partial stream is introduced into each cylinder after the inlet valve is closed. 給気行程中に、各シリンダに付設した少なくとも１個の排気入口弁を開くことを特徴とする請求項２記載の方法。   3. A method according to claim 2, characterized in that at least one exhaust inlet valve associated with each cylinder is opened during the air supply stroke. 各シリンダへの冷却済み排気部分流の還流を、シリンダ内の圧力が還流排気圧力レベルに到達したときに終了することを特徴とする請求項２又は３記載の方法。   4. A method according to claim 2 or 3, characterized in that the recirculation of the cooled exhaust partial flow to each cylinder is terminated when the pressure in the cylinder reaches the recirculation exhaust pressure level. 給気行程の下死点到達後に、各シリンダに付設した１個或いは各排気入口弁を閉じることを特徴とする請求項４記載の方法。   5. The method according to claim 4, wherein one or each exhaust inlet valve attached to each cylinder is closed after reaching the bottom dead center of the air supply stroke. 給気行程の下死点到達前或いは下死点到達後の給気行程中に、各シリンダに付設した１個或いは各排気入口弁を閉じることを特徴とする請求項４記載の方法。   5. The method according to claim 4, wherein one or each exhaust inlet valve attached to each cylinder is closed before the bottom dead center of the air supply stroke is reached or during the air supply stroke after the bottom dead center is reached. 冷却済み排気部分流を、内燃機関のシリンダにシリンダヘッドの領域において導入することを特徴とする請求項１から６の１つに記載の方法。   7. A method according to claim 1, wherein the cooled partial exhaust stream is introduced into the cylinder of the internal combustion engine in the region of the cylinder head. 冷却済み排気部分流を、内燃機関のシリンダにシリンダバレルの領域において導入することを特徴とする請求項１から６の１つに記載の方法。   7. A method according to claim 1, wherein the cooled exhaust partial stream is introduced into the cylinder of the internal combustion engine in the region of the cylinder barrel. 排気部分流を、排気冷却器への導入前に、排気洗浄器に供給し、そこで浄化することを特徴とする請求項１から８の１つに記載の方法。   9. A method according to claim 1, wherein the exhaust partial stream is supplied to an exhaust scrubber and purified there before being introduced into the exhaust cooler. 内燃機関の排気部分流を、排気駆動過給機のタービンの上流で取り出すことを特徴とする請求項１から９の１つに記載の方法。   10. A method according to claim 1, wherein the exhaust gas partial flow of the internal combustion engine is taken upstream of the turbine of the exhaust-driven supercharger. 排気還流系を備えた内燃機関において、
冷却済み排気部分流の還流が、内燃機関のシリンダに直接行われることを特徴とする排気還流路を備えた内燃機関。 In an internal combustion engine equipped with an exhaust gas recirculation system,
An internal combustion engine having an exhaust gas recirculation path, wherein the recirculation of a cooled exhaust partial flow is directly performed in a cylinder of the internal combustion engine. 請求項１から１０の１つに記載の方法により開閉される各々少なくとも１個の排気入口弁が、各シリンダに付設されたことを特徴とする請求項１１記載の内燃機関。   12. The internal combustion engine according to claim 11, wherein at least one exhaust inlet valve opened and closed by the method according to claim 1 is attached to each cylinder.
JP2007260651A 2006-10-12 2007-10-04 Internal combustion engine having exhaust recirculation system and operation method Pending JP2008095683A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006048269A DE102006048269B4 (en) 2006-10-12 2006-10-12 Method for operating an internal combustion engine with exhaust gas recirculation and internal combustion engine

Publications (1)

Publication Number Publication Date
JP2008095683A true JP2008095683A (en) 2008-04-24

Family

ID=38468658

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007260651A Pending JP2008095683A (en) 2006-10-12 2007-10-04 Internal combustion engine having exhaust recirculation system and operation method

Country Status (5)

Country Link
JP (1) JP2008095683A (en)
KR (1) KR101345827B1 (en)
CN (1) CN101165330B (en)
DE (1) DE102006048269B4 (en)
FI (1) FI124647B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008061399A1 (en) 2008-12-10 2010-06-17 Man Diesel Se Internal combustion engine with two exhaust gas turbochargers connected in series
CN104234864B (en) * 2013-09-12 2016-03-16 摩尔动力(北京)技术股份有限公司 Gas closed engine
DE102015216099A1 (en) * 2015-08-24 2017-03-02 Robert Bosch Gmbh Method and device for operating an internal combustion engine with exhaust gas recirculation

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08319902A (en) * 1995-05-25 1996-12-03 Mitsubishi Motors Corp Egr device for engine
JP2000038962A (en) * 1998-07-23 2000-02-08 Isuzu Motors Ltd Egr cooler and egr device with egr cooler
JP2004211688A (en) * 2002-12-17 2004-07-29 Toyota Motor Corp Internal combustion engine
JP2005061325A (en) * 2003-08-13 2005-03-10 Honda Motor Co Ltd Control device for compression ignition internal combustion engine
JP2006144711A (en) * 2004-11-22 2006-06-08 Mazda Motor Corp Intake and exhaust controller for four cycle gasoline engine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2061622A1 (en) * 1970-12-15 1972-07-06 Daimler-Benz Ag, 7000 Stuttgart Internal combustion engine
AT402432B (en) * 1988-02-25 1997-05-26 Avl Verbrennungskraft Messtech INTERNAL COMBUSTION ENGINE
JPH05157008A (en) * 1991-11-29 1993-06-22 Mazda Motor Corp Engine
DE19541362C1 (en) * 1995-11-07 1997-01-23 Mtu Friedrichshafen Gmbh Exhaust gas feedback system for turbocharged diesel engine
AU2003277286A1 (en) * 2002-10-04 2004-05-04 Honeywell International Inc. Internal combustion engine system
DE10324988A1 (en) * 2003-06-03 2004-12-30 Man B & W Diesel Ag Exhaust gas recirculation device for reciprocating piston engines has valve-controlled duct in each cylinder leading to common exhaust gas collection vessel

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08319902A (en) * 1995-05-25 1996-12-03 Mitsubishi Motors Corp Egr device for engine
JP2000038962A (en) * 1998-07-23 2000-02-08 Isuzu Motors Ltd Egr cooler and egr device with egr cooler
JP2004211688A (en) * 2002-12-17 2004-07-29 Toyota Motor Corp Internal combustion engine
JP2005061325A (en) * 2003-08-13 2005-03-10 Honda Motor Co Ltd Control device for compression ignition internal combustion engine
JP2006144711A (en) * 2004-11-22 2006-06-08 Mazda Motor Corp Intake and exhaust controller for four cycle gasoline engine

Also Published As

Publication number Publication date
KR20080033844A (en) 2008-04-17
DE102006048269B4 (en) 2012-10-04
FI124647B (en) 2014-11-28
FI20070588A (en) 2008-04-13
CN101165330A (en) 2008-04-23
KR101345827B1 (en) 2013-12-30
DE102006048269A1 (en) 2008-04-17
CN101165330B (en) 2011-06-08
FI20070588A0 (en) 2007-08-06

Similar Documents

Publication Publication Date Title
US8037873B2 (en) Residual burnt gas scavenging method with double intake valve lift in a direct-injection supercharged internal-combusion engine, notably of diesel type
US20070235011A1 (en) Exhaust gas recirculation system with in-cylinder valve actuation
KR101342815B1 (en) Method for operating an internal combustion engine
Millo et al. Computational analysis of internal and external EGR strategies combined with Miller cycle concept for a two stage turbocharged medium speed marine diesel engine
WO2006037564A8 (en) Method and device for increasing the torque of a reciprocating piston internal combustion engine, especially a diesel engine
JP2010151140A (en) Operation method for two-stroke reciprocation internal combustion engine
JP2011149428A (en) Residual combustion gas scavenging method in direct-injection supercharged internal-combustion multi-cylinder engine running under partial load
US6360701B1 (en) Method for operating a four stroke diesel engine
JP2008095683A (en) Internal combustion engine having exhaust recirculation system and operation method
US20120048218A1 (en) System and method for operating an internal combustion engine
JPH11247665A (en) Nitrogen oxides reducing structure of two cycle diesel engine
WO2004033888A3 (en) Internal combustion engine system
KR20130143017A (en) Method for reducing emissions of an internal combustion engine and internal combustion engine
CN110036193B (en) Internal combustion engine
KR101475834B1 (en) Method for operating a large, crosshead reciprocating piston internal combustion engine and suitable such engine
JP2009222060A (en) Exchanging (scavenging) method for combustion gas of two stroke engine
JP2012237231A (en) Blowby gas reflux device
WO2016018184A1 (en) Method at a 2-stroke engine, and a 2-stroke engine operating according to said method
JP2003201922A (en) Exhaust recirculating method and exhaust recirculating device for internal combustion engine
KR100534983B1 (en) Exhaust Gas Recirculating System
JP2005299396A (en) Four cycle multi-cylinder internal combustion engine with supercharger
EP4257812A1 (en) Internal combustion engine
US20120023916A1 (en) Diesel CGR process and structure
JP3592247B2 (en) Exhaust gas recirculation system for internal combustion engine
JP2005076490A (en) Two-cycle internal combustion engine and compression ignition two-cycle internal combustion engine

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20091002

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20100922

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20101005

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20101227

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20110621

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20111021

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20111130

A911 Transfer to examiner for re-examination before appeal (zenchi)

Free format text: JAPANESE INTERMEDIATE CODE: A911

Effective date: 20111206

A912 Re-examination (zenchi) completed and case transferred to appeal board

Free format text: JAPANESE INTERMEDIATE CODE: A912

Effective date: 20120210

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20120724

A602 Written permission of extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A602

Effective date: 20120730

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20120824

A602 Written permission of extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A602

Effective date: 20120829

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20130206

A602 Written permission of extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A602

Effective date: 20130213

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20130305