JP2006200494A - Cylinder-injection spark-ignition internal combustion engine - Google Patents

Cylinder-injection spark-ignition internal combustion engine Download PDF

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JP2006200494A
JP2006200494A JP2005015141A JP2005015141A JP2006200494A JP 2006200494 A JP2006200494 A JP 2006200494A JP 2005015141 A JP2005015141 A JP 2005015141A JP 2005015141 A JP2005015141 A JP 2005015141A JP 2006200494 A JP2006200494 A JP 2006200494A
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fuel
injected
cylinder
spark plug
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Hiroshi Nomura
啓 野村
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Toyota Motor Corp
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    • 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
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    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

<P>PROBLEM TO BE SOLVED: To fully suppress a misfire from occurring in a cylinder-injection spark-ignition internal combustion engine in which a block of a combustible air fuel mixture is directly formed in part of a cylinder by a fuel injection valve arranged almost in the center of a cylinder upper part, and stratified charged combustion is carried out. <P>SOLUTION: The block of the combustible air fuel mixture is formed by a plurality of injection fuels injected from an injection valve 5. The injection fuel f2 injected toward near an ignition plug 6 is made smaller in penetration force compared with an injection fuel f1 injected toward other than the ignition plug. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、筒内噴射式火花点火内燃機関に関する。   The present invention relates to a direct injection spark ignition internal combustion engine.

圧縮行程で噴射された燃料によって気筒内の一部だけに可燃混合気を形成し、この可燃混合気を点火プラグによって着火燃焼させることにより、気筒内全体の空燃比を理論空燃比よりリーンとした燃焼を可能とする成層燃焼が公知である。成層燃焼の可燃混合気を形成するために、噴射燃料をピストン頂面によって点火プラグ方向へ偏向させることが提案されているが、このためには、燃料噴射時期がピストン位置の制限を受けることとなる。   The fuel injected in the compression stroke forms a combustible air-fuel mixture only in a part of the cylinder, and this combustible air-fuel mixture is ignited and burned by the spark plug, so that the air-fuel ratio in the entire cylinder is made leaner than the stoichiometric air-fuel ratio. Stratified combustion that enables combustion is known. In order to form a flammable mixture for stratified combustion, it has been proposed to deflect the injected fuel in the direction of the spark plug by the top surface of the piston. For this purpose, the fuel injection timing is limited by the piston position. Become.

このような制限なしに燃料噴射時期を設定可能とするために、燃料噴射弁を気筒上部略中心に配置し、ピストン頂面を利用することなく燃料噴射弁からの噴射燃料によって気筒内に直接的に可燃混合気を形成することが提案されている（例えば、特許文献１参照）。点火プラグは、形成された可燃混合気内に点火ギャップを位置させるように、燃料噴射弁の近傍に配置されている。   In order to make it possible to set the fuel injection timing without such a restriction, the fuel injection valve is arranged at the substantially upper center of the cylinder, and directly into the cylinder by the injected fuel from the fuel injection valve without using the piston top surface. It has been proposed to form a combustible air-fuel mixture (see, for example, Patent Document 1). The spark plug is disposed in the vicinity of the fuel injection valve so as to position the ignition gap in the formed combustible mixture.

特表２００２−５３９３６５Special Table 2002-539365 特開２００３−２０１８４６JP2003-201846

前述の背景技術において、燃料噴射弁は中空円錐状に燃料を噴射するものであり、可燃混合気を形成するためには、噴射燃料全体を気筒内のある程度の範囲に分散させ、混合気が過剰リッチとなることを防止しなければならない。そのためには、噴射燃料の貫徹力は比較的大きくされる。   In the above-described background art, the fuel injection valve injects fuel in a hollow conical shape, and in order to form a combustible mixture, the entire injected fuel is dispersed to a certain extent in the cylinder, and the mixture is excessive. It must be prevented from becoming rich. For this purpose, the penetration force of the injected fuel is made relatively large.

しかしながら、こうして噴射燃料の貫徹力を比較的大きくすると、噴射燃料が気筒内の空気と共に混合気となって進行して可燃混合気となる際に、混合気の流速が比較的速くなるために、混合気が点火プラグ近傍を通過する際に点火ギャップで発生させた火花を吹き消して失火を発生させることがある。   However, if the penetrating force of the injected fuel is made relatively large in this way, the flow rate of the air-fuel mixture becomes relatively high when the injected fuel proceeds as an air-fuel mixture with the air in the cylinder and becomes a combustible air-fuel mixture. When the air-fuel mixture passes in the vicinity of the spark plug, the spark generated in the ignition gap may be blown out to cause misfire.

従って、本発明の目的は、気筒上部略中心に配置された燃料噴射弁によって気筒内の一部に直接的に可燃混合気を形成して成層燃焼を実施する筒内噴射式火花点火内燃機関において、失火発生を十分に抑制することである。   Accordingly, an object of the present invention is an in-cylinder injection spark ignition internal combustion engine that performs stratified combustion by directly forming a combustible air-fuel mixture in a part of a cylinder by means of a fuel injection valve disposed substantially at the center of the cylinder upper portion. It is to sufficiently suppress the occurrence of misfire.

本発明による請求項１に記載の筒内噴射式火花点火内燃機関は、気筒上部略中心に配置された燃料噴射弁と、前記燃料噴射弁の近傍に配置された点火プラグとを具備し、前記燃料噴射弁により噴射された燃料により気筒内の一部に直接的に可燃混合気を形成し、前記点火プラグによって前記可燃混合気を着火燃焼させて成層燃焼を実施する筒内噴射式火花点火内燃機関において、前記可燃混合気は、前記燃料噴射弁から噴射された複数の噴射燃料によって形成され、前記点火プラグ近傍に向けて噴射される前記噴射燃料は、前記点火プラグ近傍以外に向けて噴射される前記噴射燃料に比較して、貫徹力が小さくされていることを特徴とする。   An in-cylinder injection spark ignition internal combustion engine according to claim 1 of the present invention includes a fuel injection valve disposed substantially at the center of an upper portion of a cylinder, and an ignition plug disposed in the vicinity of the fuel injection valve, In-cylinder injection spark ignition internal combustion in which a flammable mixture is directly formed in a part of a cylinder by fuel injected by a fuel injection valve, and the flammable mixture is ignited and burned by the ignition plug to perform stratified combustion In the engine, the combustible mixture is formed by a plurality of injected fuels injected from the fuel injection valve, and the injected fuel injected toward the vicinity of the spark plug is injected toward other than the vicinity of the spark plug. Compared with the injected fuel, the penetration force is reduced.

本発明による請求項１に記載の筒内噴射式火花点火内燃機関によれば、成層燃焼時に気筒内に形成される可燃混合気は、燃料噴射弁から噴射された比較的貫徹力の大きな複数の噴射燃料によって形成されるために、噴射燃料全体は気筒内のある程度の範囲に分散され、過剰リッチとなることはない。また、可燃混合気の形成に際して、点火プラグ近傍へ向けて噴射される噴射燃料は、点火プラグ近傍以外へ向けて噴射される噴射燃料に比較して貫徹力が小さくされているために、噴射燃料が気筒内の空気と共に混合気となって進行して点火プラグ近傍を通過する時の混合気の流速は比較的遅くなり、それにより、点火ギャップで発生させた火花が吹き消されることは殆どなく、失火発生を十分に抑制することができる。   According to the in-cylinder injection spark ignition internal combustion engine according to claim 1 of the present invention, the combustible air-fuel mixture formed in the cylinder during stratified combustion has a plurality of relatively high penetrating forces injected from the fuel injection valve. Since it is formed by the injected fuel, the entire injected fuel is dispersed to a certain extent in the cylinder and does not become excessively rich. Further, when the combustible air-fuel mixture is formed, the injected fuel injected toward the vicinity of the spark plug has a lower penetrating force than the injected fuel injected toward the vicinity of the spark plug. When the air travels as a mixture with the air in the cylinder and passes through the vicinity of the spark plug, the flow rate of the mixture becomes relatively slow, so that the spark generated in the ignition gap is hardly blown out. The occurrence of misfire can be sufficiently suppressed.

図１は本発明による筒内噴射式火花点火内燃機関の実施形態を示す概略縦断面図である。同図において、１は吸気弁２を介して気筒内へ通じる一対の吸気通路であり、３は排気弁４を介して気筒内へ通じる一対の排気通路である。   FIG. 1 is a schematic longitudinal sectional view showing an embodiment of a direct injection spark ignition internal combustion engine according to the present invention. In the figure, 1 is a pair of intake passages that lead into the cylinder via the intake valve 2, and 3 is a pair of exhaust passages that lead to the cylinder via the exhaust valve 4.

５は気筒上部略中心に配置された燃料噴射弁であり、６は燃料噴射弁５の近傍に配置された点火プラグであり、７はピストンである。８は吸気通路１に配置されたもう一つの燃料噴射弁であり、この燃料噴射弁８によって吸気弁２の開弁前又は開弁中に燃料を吸気通路１に噴射することにより、気筒内には均質混合気が形成され、均質燃焼を実現することができる。   Reference numeral 5 denotes a fuel injection valve arranged substantially at the upper center of the cylinder, 6 denotes a spark plug arranged in the vicinity of the fuel injection valve 5, and 7 denotes a piston. Reference numeral 8 denotes another fuel injection valve disposed in the intake passage 1. By injecting fuel into the intake passage 1 before or during the opening of the intake valve 2 by the fuel injection valve 8, the fuel injection valve 8 enters the cylinder. A homogeneous mixture is formed, and homogeneous combustion can be realized.

成層燃焼を実施するためには、圧縮行程において、気筒上部略中心に配置された燃料噴射弁５の複数の噴孔から複数の燃料ｆ１，ｆ２が柱状に噴射される。複数の噴孔として、燃料噴射弁５には、例えば、その軸線に対して放射状に形成された六つの噴孔が形成される。各燃料ｆ１，ｆ２は、気筒上部略中心に配置された燃料噴射弁５から斜め下方向に放射状にシリンダボアへ向けて噴射される。   In order to perform stratified combustion, in the compression stroke, a plurality of fuels f1 and f2 are injected in a columnar shape from a plurality of injection holes of the fuel injection valve 5 disposed substantially at the center of the cylinder upper portion. As the plurality of injection holes, the fuel injection valve 5 has, for example, six injection holes formed radially with respect to the axis thereof. The fuels f1 and f2 are injected radially and obliquely downward toward the cylinder bore from the fuel injection valve 5 arranged at the substantially upper center of the cylinder.

各噴射燃料ｆ１，ｆ２は、自身の貫徹力によって気筒内の空気を巻き込みながら混合気となって進行してシリンダボアに到達する以前にほぼ完全に気化し、燃料噴射弁５の近傍において互いに連結された一塊の可燃混合気となる。こうして、複数の噴射燃料ｆ１，ｆ２によって気筒内の一部には一塊の可燃混合気が形成される。少なくとも一つの噴射燃料ｆ２は、点火プラグ６近傍に向けて噴射され、この噴射燃料ｆ２により形成される可燃混合気の一部分が点火プラグ６の点火ギャップと接触しているようにし、この一部分から着火させることにより、一塊の可燃混合気全体の燃焼を可能としている。可燃混合気の形成に際して、燃料はピストン７頂面を利用して偏向されることはなく、ピストン位置に係らず可燃混合気の形成が可能である。   Each of the injected fuels f1 and f2 is vaporized almost completely before reaching the cylinder bore by being mixed with air in the cylinder by its penetrating force and connected to each other in the vicinity of the fuel injection valve 5. It becomes a lump of combustible air-fuel mixture. In this way, a lump of combustible air-fuel mixture is formed in a part of the cylinder by the plurality of injected fuels f1 and f2. At least one injected fuel f2 is injected toward the vicinity of the spark plug 6, and a part of the combustible air-fuel mixture formed by the injected fuel f2 is in contact with the ignition gap of the spark plug 6, and ignition occurs from this part. By doing so, it is possible to burn the entire flammable mixture. When the combustible mixture is formed, the fuel is not deflected using the top surface of the piston 7, and the combustible mixture can be formed regardless of the piston position.

図２はシリンダヘッドの拡大底面図である。燃料噴射弁５から前述のように噴射される複数の噴射燃料ｆ１の貫徹力は、形成される一塊の混合気が過剰リッチとならないように、噴射燃料を気筒内の一部に十分に分散させるために比較的大きくされている。しかしながら、点火プラグ６近傍に向けて噴射される噴射燃料ｆ２の貫徹力だけは、点火プラグ６近傍以外に向けて噴射される噴射燃料ｆ１の貫徹力に比較して小さくされている。   FIG. 2 is an enlarged bottom view of the cylinder head. The penetration force of the plurality of injected fuels f1 injected from the fuel injection valve 5 as described above sufficiently disperses the injected fuel in a part of the cylinder so that the lump of formed air-fuel mixture does not become excessively rich. Because of being relatively large. However, only the penetration force of the injected fuel f2 injected toward the vicinity of the spark plug 6 is made smaller than the penetration force of the injected fuel f1 injected toward the vicinity of other than the vicinity of the spark plug 6.

図４は、燃料噴射弁５の開弁信号Ａと、点火プラグ６近傍の流速Ｂ１，Ｂ２と、点火プラグ６近傍の空燃比Ｃ１とを示すタイムチャートである。図４に示されているように、燃料噴射弁５の開弁によって燃料ｆ２が噴射されると、噴射燃料ｆ２は気筒内の空気と共に混合気となって進行し、この混合気によって点火プラグ６近傍の空燃比は急激にリッチとなり、燃料噴射弁５の閉弁によって燃料ｆ２の噴射が停止されると、点火プラグ６近傍の空燃比は徐々にリーンとなる。一点鎖線Ｃ２は点火プラグ６により着火可能な混合気空燃比のリーン限界であり、一点鎖線Ｃ３は点火プラグ６により点火可能な混合気空燃比のリッチ限界である。すなわち、点火プラグ６近傍の混合気空燃比が二つの一点鎖線Ｃ２，Ｃ３の間にある時にだけ着火が可能となる。   FIG. 4 is a time chart showing the valve opening signal A of the fuel injection valve 5, the flow rates B1 and B2 in the vicinity of the spark plug 6, and the air-fuel ratio C1 in the vicinity of the spark plug 6. As shown in FIG. 4, when the fuel f2 is injected by opening the fuel injection valve 5, the injected fuel f2 advances as an air-fuel mixture with the air in the cylinder. The air-fuel ratio in the vicinity suddenly becomes rich, and when the injection of the fuel f2 is stopped by closing the fuel injection valve 5, the air-fuel ratio in the vicinity of the spark plug 6 gradually becomes lean. A one-dot chain line C2 is a lean limit of the air-fuel ratio that can be ignited by the spark plug 6, and a one-dot chain line C3 is a rich limit of the air-fuel ratio that can be ignited by the spark plug 6. That is, ignition is possible only when the air-fuel ratio in the vicinity of the spark plug 6 is between the two alternate long and short dash lines C2 and C3.

もし、噴射燃料ｆ２が、他の噴射燃料ｆ１と同様に比較的大きな貫徹力を有していると、点線Ｂ１で示すように、噴射燃料ｆ２により形成される混合気の流速は速くなる。この混合気の少なくとも一部は、点火プラグ６の点火ギャップを通過するために、その流速が一点鎖線Ｂ３で示す限界流速より高いと、点火プラグ６により発生される火花を吹き消す可能性が高い。それにより、噴射燃料ｆ２の貫徹力を比較的大きくした場合には、点火プラグ６近傍の流速が限界流速Ｂ３以下であって、点火プラグ６近傍の空燃比がリーン限界Ｃ２とリッチ限界Ｃ３との間にある非常に短い期間Ｒ１だけでしか、点火プラグ６によって混合気を着火させることはできないこととなる。こうして、僅かな点火時期のずれ等によって容易に失火が発生してしまう。   If the injected fuel f2 has a relatively large penetration force like the other injected fuels f1, the flow rate of the air-fuel mixture formed by the injected fuel f2 becomes faster as indicated by the dotted line B1. Since at least a part of the air-fuel mixture passes through the ignition gap of the spark plug 6, if the flow velocity is higher than the limit flow velocity indicated by the alternate long and short dash line B3, there is a high possibility that the spark generated by the spark plug 6 is blown out. . As a result, when the penetration force of the injected fuel f2 is relatively large, the flow velocity in the vicinity of the spark plug 6 is equal to or less than the limit flow velocity B3, and the air-fuel ratio in the vicinity of the spark plug 6 is between the lean limit C2 and the rich limit C3. The air-fuel mixture can be ignited by the spark plug 6 only in a very short period R1 between them. Thus, misfiring easily occurs due to a slight difference in ignition timing.

これに対して、本実施形態のように、噴射燃料ｆ２の貫徹力を他の噴射燃料ｆ１に比較して小さくした場合には、実線Ｂ２で示すように、噴射燃料ｆ２により形成される混合気の流速は遅くなって、点火プラグ６により発生される火花を吹き消す可能性の高い限界流速Ｂ３を超えることはなく、点火プラグ６近傍の空燃比がリーン限界Ｃ２とリッチ限界Ｃ３との間にある比較的長い期間Ｒ２において、点火プラグ６によって混合気を確実に着火させ、一塊の可燃混合気全体を燃焼させることができる。こうして、僅かな点火時期のずれ等によっても失火が発生することは殆どない。   On the other hand, when the penetration force of the injected fuel f2 is made smaller than that of the other injected fuel f1 as in the present embodiment, the air-fuel mixture formed by the injected fuel f2 is shown by the solid line B2. The flow velocity of the spark plug 6 does not exceed the critical flow velocity B3 that is highly likely to blow out the spark generated by the spark plug 6, and the air-fuel ratio in the vicinity of the spark plug 6 is between the lean limit C2 and the rich limit C3. In a relatively long period R2, the air-fuel mixture can be reliably ignited by the spark plug 6, and the entire combustible air-fuel mixture can be burned. Thus, a misfire hardly occurs even if the ignition timing is slightly shifted.

このように、点火プラグ６近傍へ向けて噴射される噴射燃料ｆ２の貫徹力は、点火プラグ６近傍の混合気の流速が常に限界流速Ｂ２を超えないように設定されることが好ましい。しかしながら、噴射燃料ｆ２の貫徹力を、点火プラグ６近傍以外へ向けて噴射される噴射燃料ｆ１の貫徹力より小さく設定することで、噴射燃料ｆ１の貫徹力と同じに設定した場合に比較して、点火プラグ６によって混合気を着火可能な期間を延長することができる。   Thus, the penetration force of the injected fuel f2 injected toward the vicinity of the spark plug 6 is preferably set so that the flow rate of the air-fuel mixture in the vicinity of the spark plug 6 does not always exceed the limit flow rate B2. However, the penetration force of the injected fuel f2 is set to be smaller than the penetration force of the injected fuel f1 that is injected toward the vicinity of the spark plug 6 in comparison with the case where it is set to be the same as the penetration force of the injected fuel f1. The period during which the air-fuel mixture can be ignited by the spark plug 6 can be extended.

図３は燃料噴射弁５の噴孔近傍の断面図である。同図において、５ａは点火プラグ６近傍以外へ向けて燃料を噴射するための第１噴孔であり、５ｂは点火プラグ６近傍へ向けて燃料を噴射するための第２噴孔である。第２噴孔５ｂの長さＬ２は、十分に大きな直径を有するザグリ穴５ｃによって、第１噴孔５ａの長さＬ１に比較して短くされ、第２噴孔５ｂの噴射燃料ｆ２の貫徹力を小さくしている。そのままでは、第２噴孔５ｂの噴射燃料ｆ２の流量が第１噴孔５ａの噴射燃料ｆ１の流量に比較して多くなり過ぎるために、第２噴孔５ｂの直径Ｄ２は、第１噴孔５ａの直径Ｄ１に比較して小さくされている。噴孔長さと噴孔径との比（Ｌ／Ｄ）を小さくするほど、噴射燃料の貫徹力は小さくなることが解かっており、これに基づき、第２噴孔５ｂの燃料噴射ｆ２の貫徹力を第１噴孔５ａの噴射燃料の貫徹力より小さくすると共に、第１噴孔５ａ及び第２噴孔５ｂの噴射燃料の流量がそれぞれに最適となるように、第１噴孔５ａ及び第２噴孔５ｂの長さＬ及び直径Ｄを選択することが好ましい。   FIG. 3 is a cross-sectional view of the vicinity of the injection hole of the fuel injection valve 5. In the figure, reference numeral 5a denotes a first injection hole for injecting fuel to the vicinity of the spark plug 6 and 5b denotes a second injection hole for injecting fuel to the vicinity of the ignition plug 6. The length L2 of the second injection hole 5b is made shorter than the length L1 of the first injection hole 5a by the counterbore hole 5c having a sufficiently large diameter, and the penetrating force of the injected fuel f2 in the second injection hole 5b. Is made smaller. As it is, since the flow rate of the injected fuel f2 in the second nozzle hole 5b is excessively larger than the flow rate of the injected fuel f1 in the first nozzle hole 5a, the diameter D2 of the second nozzle hole 5b is set to the first nozzle hole. It is made smaller than the diameter D1 of 5a. It has been found that as the ratio (L / D) between the nozzle hole length and the nozzle hole diameter decreases, the penetration force of the injected fuel decreases. Based on this, the penetration force of the fuel injection f2 in the second nozzle hole 5b is reduced. The first injection hole 5a and the second injection hole 5a are made smaller than the penetration force of the injection fuel in the first injection hole 5a, and the flow rates of the injection fuel in the first injection hole 5a and the second injection hole 5b are respectively optimum. It is preferable to select the length L and the diameter D of the hole 5b.

本発明による筒内噴射式火花点火内燃機関の実施形態を示す概略縦断面図である。1 is a schematic longitudinal sectional view showing an embodiment of a direct injection spark ignition internal combustion engine according to the present invention. 図１の筒内噴射式火花点火内燃機関におけるシリンダヘッドの拡大底面図である。FIG. 2 is an enlarged bottom view of a cylinder head in the cylinder injection type spark ignition internal combustion engine of FIG. 1. 燃料噴射弁の噴孔近傍の断面図である。It is sectional drawing of the nozzle hole vicinity of a fuel injection valve. 燃料噴射弁の開弁信号と、点火プラグ近傍の流速と、点火プラグ近傍の空燃比とを示すタイムチャートである。4 is a time chart showing a valve opening signal of a fuel injection valve, a flow velocity in the vicinity of the spark plug, and an air-fuel ratio in the vicinity of the spark plug.

符号の説明Explanation of symbols

１ 吸気通路
３ 排気通路
５ 燃料噴射弁
６ 点火プラグ 1 Intake passage 3 Exhaust passage 5 Fuel injection valve 6 Spark plug

Claims (1)

気筒上部略中心に配置された燃料噴射弁と、前記燃料噴射弁の近傍に配置された点火プラグとを具備し、前記燃料噴射弁により噴射された燃料により気筒内の一部に直接的に可燃混合気を形成し、前記点火プラグによって前記可燃混合気を着火燃焼させて成層燃焼を実施する筒内噴射式火花点火内燃機関において、前記可燃混合気は、前記燃料噴射弁から噴射された複数の噴射燃料によって形成され、前記点火プラグ近傍に向けて噴射される前記噴射燃料は、前記点火プラグ近傍以外に向けて噴射される前記噴射燃料に比較して、貫徹力が小さくされていることを特徴とする筒内噴射式火花点火内燃機関。   A fuel injection valve disposed substantially in the center of the cylinder and a spark plug disposed in the vicinity of the fuel injection valve. The fuel injected by the fuel injection valve directly combusts a part of the cylinder. In a cylinder injection spark ignition internal combustion engine that forms an air-fuel mixture and ignites and burns the combustible air-fuel mixture with the spark plug to perform stratified combustion, the combustible air-fuel mixture is a plurality of fuel injected from the fuel injection valve. The injected fuel formed by the injected fuel and injected toward the vicinity of the spark plug has a penetrating force smaller than that of the injected fuel injected toward other than the vicinity of the spark plug. An in-cylinder injection spark ignition internal combustion engine.
JP2005015141A 2005-01-24 2005-01-24 Cylinder-injection spark-ignition internal combustion engine Pending JP2006200494A (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6241829U (en) * 1985-08-31 1987-03-13
JPH11159421A (en) * 1997-11-26 1999-06-15 Hitachi Ltd Fuel injection valve
JP2002227651A (en) * 2001-02-01 2002-08-14 Hitachi Ltd Control system for cylinder fuel injection and spark ignition type engine
JP2003120299A (en) * 2001-10-09 2003-04-23 Hitachi Ltd Cylinder injection gasoline engine
JP2005248857A (en) * 2004-03-04 2005-09-15 Mitsubishi Electric Corp Combustion control device for internal combustion engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6241829U (en) * 1985-08-31 1987-03-13
JPH11159421A (en) * 1997-11-26 1999-06-15 Hitachi Ltd Fuel injection valve
JP2002227651A (en) * 2001-02-01 2002-08-14 Hitachi Ltd Control system for cylinder fuel injection and spark ignition type engine
JP2003120299A (en) * 2001-10-09 2003-04-23 Hitachi Ltd Cylinder injection gasoline engine
JP2005248857A (en) * 2004-03-04 2005-09-15 Mitsubishi Electric Corp Combustion control device for internal combustion engine

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