JP2008051075A - Cylinder injection type spark ignition internal combustion engine - Google Patents

Cylinder injection type spark ignition internal combustion engine Download PDF

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JP2008051075A
JP2008051075A JP2006230830A JP2006230830A JP2008051075A JP 2008051075 A JP2008051075 A JP 2008051075A JP 2006230830 A JP2006230830 A JP 2006230830A JP 2006230830 A JP2006230830 A JP 2006230830A JP 2008051075 A JP2008051075 A JP 2008051075A
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fuel
injection
injected
cylinder
tumble flow
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JP4321567B2 (en
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Takeshi Ashizawa
剛 芦澤
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Toyota Motor Corp
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Priority to US12/282,915 priority patent/US7726282B2/en
Priority to EP07804677A priority patent/EP2047079A1/en
Priority to CN200780029165XA priority patent/CN101501310B/en
Priority to PCT/IB2007/002188 priority patent/WO2008015536A1/en
Priority to KR1020097002172A priority patent/KR101089032B1/en
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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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Abstract

<P>PROBLEM TO BE SOLVED: To efficiently enhance a tumble flow by fuel injected directly into a cylinder by a fuel injection valve. <P>SOLUTION: A going-through force F1 of the injected fuel having an injection direction substantially parallel to a plane parallel to the tumble flow T, out of the fuels injected from a plurality of injection holes of the fuel injection valve 1, is intensified by going-through forces of the injected fuels F2, F3 having injection directions crossed clearly with the plane, in this direct injection type spark ignition internal combustion engine of the present invention provided with the fuel injection valve 1 having the plurality of injection holes and for injecting directly the fuel into the cylinder, and capable of intensifying the tumble flow T by the fuel injected from the fuel injection valve in the vicinity of an intake stroke bottom dead point, in homogenous charge combustion. <P>COPYRIGHT: (C)2008,JPO&INPIT

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.

気筒内に均質混合気を形成し、この均質混合気を圧縮行程末期の点火時期において着火燃焼させる均質燃焼において、気筒内へ供給された吸気により気筒内にタンブル流を形成し、このタンブル流を圧縮行程末期の点火時期まで持続させることにより、点火時期において気筒内にタンブル流による乱れを存在させれば、この乱れによって均質混合気の燃焼速度が高まり良好な均質燃焼を実現することができる。   In homogeneous combustion in which a homogeneous mixture is formed in the cylinder and this homogeneous mixture is ignited and combusted at the ignition timing at the end of the compression stroke, a tumble flow is formed in the cylinder by the intake air supplied into the cylinder, and this tumble flow is If the turbulence caused by the tumble flow exists in the cylinder at the ignition timing by maintaining the ignition timing at the end of the compression stroke, the combustion speed of the homogeneous mixture is increased by the turbulence, and good homogeneous combustion can be realized.

タンブル流を圧縮行程末期の点火時期まで持続させるために、吸気ポート内に吸気流制御弁を配置し、この吸気流制御弁によって吸気を吸気ポート上壁に沿わせて気筒内へ供給することにより、気筒内に強いタンブル流を形成する筒内噴射式火花点火内燃機関が提案されている（例えば、特許文献１参照）。   In order to maintain the tumble flow until the ignition timing at the end of the compression stroke, an intake flow control valve is arranged in the intake port, and by this intake flow control valve, intake air is supplied into the cylinder along the upper wall of the intake port. An in-cylinder injection spark ignition internal combustion engine that forms a strong tumble flow in a cylinder has been proposed (see, for example, Patent Document 1).

特開２００５−１８０２４７JP 2005-180247 A

前述の筒内噴射式火花点火内燃機関において、吸気流制御弁により吸気を吸気ポート上壁に沿わせて気筒内に供給する時には、吸気流制御弁により吸気ポートが絞られることになる。それにより、必要吸気量が比較的少ない時においては、特に問題なく強いタンブル流を気筒内に形成することができるが、必要吸気量が比較的多くなる時においては、吸気流制御弁により吸気ポートを絞ると吸気不足が発生することがあるために、吸気流制御弁によって強いタンブル流を気筒内に形成することはできない。   In the above-described in-cylinder spark ignition internal combustion engine, when intake air is supplied into the cylinder along the upper wall of the intake port by the intake flow control valve, the intake port is throttled by the intake flow control valve. As a result, when the required intake air amount is relatively small, a strong tumble flow can be formed in the cylinder without any problem. However, when the required intake air amount is relatively large, the intake port is controlled by the intake air flow control valve. Since a shortage of intake may occur if the throttle valve is throttled, a strong tumble flow cannot be formed in the cylinder by the intake flow control valve.

このような吸気流制御弁を設けなくても、筒内噴射式火花点火内燃機関においては、燃料噴射方向を適当に選択して、吸気行程末期に貫徹力の強い燃料を噴射すればタンブル流を強めることができる。しかしながら、燃料噴射方向を適当に選択しただけでは、噴射燃料によりタンブル流を効率的に強めることはできない。   Even if such an intake flow control valve is not provided, in a direct injection spark ignition internal combustion engine, if the fuel injection direction is appropriately selected and fuel with a strong penetration force is injected at the end of the intake stroke, a tumble flow is generated. Can strengthen. However, the tumble flow cannot be effectively enhanced by the injected fuel only by appropriately selecting the fuel injection direction.

従って、本発明の目的は、燃料噴射弁により気筒内へ直接的に噴射される燃料によってタンブル流を効率的に強めることができる筒内噴射式火花点火内燃機関を提供することである。   Accordingly, an object of the present invention is to provide an in-cylinder injection spark ignition internal combustion engine that can effectively enhance the tumble flow by the fuel directly injected into the cylinder by the fuel injection valve.

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、複数の噴孔を有して気筒内へ直接的に燃料を噴射する燃料噴射弁を具備し、均質燃焼時に吸気下死点近傍において前記燃料噴射弁から噴射される燃料によりタンブル流を強める筒内噴射式火花点火内燃機関において、前記燃料噴射弁の複数の噴孔から噴射されるうちのタンブル流と平行な平面と略平行な噴射方向を有する噴射燃料の貫徹力は、前記平面と交差する噴射方向を有する噴射燃料の貫徹力より大きくされることを特徴とする。   According to a first aspect of the present invention, the in-cylinder injection spark ignition internal combustion engine includes a fuel injection valve that has a plurality of injection holes and directly injects fuel into the cylinder. In a cylinder injection spark ignition internal combustion engine in which a tumble flow is strengthened by fuel injected from the fuel injection valve in the vicinity of the point, a plane parallel to the tumble flow of the plurality of injection holes of the fuel injection valve is substantially parallel to the plane. The penetration force of the injected fuel having a parallel injection direction is made larger than the penetration force of the injection fuel having the injection direction intersecting the plane.

本発明による請求項２に記載の筒内噴射式火花点火内燃機関は、気筒内へ直接的に燃料を噴射する燃料噴射弁を具備し、均質燃焼時に吸気下死点近傍において前記燃料噴射弁から噴射される燃料によりタンブル流を強める筒内噴射式火花点火内燃機関において、燃料噴射期間の単位時間当たりの吸入空気量が多い時には前記燃料噴射期間の単位時間当たりの吸入空気量が少ない時に比較して前記燃料噴射弁から噴射される燃料の貫徹力を大きくすることを特徴とする。   According to a second aspect of the present invention, there is provided an in-cylinder injection spark ignition internal combustion engine comprising a fuel injection valve that directly injects fuel into the cylinder, and is located near the intake bottom dead center at the time of homogeneous combustion. In a cylinder-injection spark ignition internal combustion engine that enhances the tumble flow by the injected fuel, when the intake air amount per unit time during the fuel injection period is large, compared to when the intake air amount per unit time during the fuel injection period is small. The penetration force of the fuel injected from the fuel injection valve is increased.

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、燃料噴射弁の複数の噴孔から噴射されるうちのタンブル流と平行な平面と略平行な噴射方向を有する噴射燃料は、この平面と明らかに交差する噴射方向を有する噴射燃料より効果的にタンブル流を強めることができるために、平面と略平行な噴射方向を有する噴射燃料の貫徹力が平面と交差する噴射方向を有する噴射燃料の貫徹力より大きくされることにより、全体的な燃料噴射量を増加させることなく、効率的にタンブル流を強めることができる。また、複数方向に噴射される燃料は、気筒内全体に燃料を分散させ易く、良好な均質混合気を形成するのに有利である。   According to the cylinder injection type spark ignition internal combustion engine of the first aspect of the present invention, the injection having an injection direction substantially parallel to a plane parallel to the tumble flow out of the plurality of injection holes of the fuel injection valve. The fuel can intensify the tumble flow more effectively than the injected fuel having an injection direction that clearly intersects this plane, so that the penetration force of the injected fuel having an injection direction substantially parallel to the plane intersects the plane. By making it larger than the penetration force of the injected fuel having a direction, the tumble flow can be effectively strengthened without increasing the overall fuel injection amount. Further, the fuel injected in a plurality of directions is easy to disperse the fuel in the entire cylinder, and is advantageous for forming a good homogeneous mixture.

本発明による請求項２に記載の筒内噴射式火花点火内燃機関によれば、燃料噴射期間の単位時間当たりの吸入空気量が多い時には燃料噴射期間の単位時間当たりの吸入空気量が少ない時に比較して燃料噴射弁から噴射される燃料の貫徹力を大きくするようになっているために、単位時間当たりの吸入空気量が多い時には噴射燃料の貫徹力が大きく、単位時間当たりの吸入空気量が少ない時には噴射燃料の貫徹力が小さくされ、噴射燃料がタンブル流を突き抜けて噴射燃料のエネルギの多くがタンブル流を強めるのに利用されないことが抑制され、全体的な燃料噴射量を増加させることなく、効率的にタンブル流を強めることができる。   According to the in-cylinder spark-ignition internal combustion engine of the second aspect of the present invention, when the intake air amount per unit time in the fuel injection period is large, it is compared with when the intake air amount per unit time in the fuel injection period is small. Therefore, when the intake air amount per unit time is large, the penetration force of the injected fuel is large and the intake air amount per unit time is large. When it is low, the penetrating force of the injected fuel is reduced, preventing the injected fuel from penetrating through the tumble flow and much of the energy of the injected fuel not being used to strengthen the tumble flow, and without increasing the overall fuel injection amount , Can effectively strengthen the tumble flow.

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り、均質燃焼のための燃料噴射時期である吸気下死点近傍を示している。同図において、１は気筒上部略中心に配置されて気筒内へ直接的に燃料を噴射するための燃料噴射弁であり、２は燃料噴射弁１の吸気弁側近傍に配置された点火プラグである。図２は図１の気筒内をピストン側から見た図であり、図２に示すように、図１における気筒上部の右側には一対の吸気弁３が配置されており、左側には一対の排気弁４が配置されている。５はピストンである。   FIG. 1 is a schematic longitudinal sectional view showing an embodiment of an in-cylinder injection spark ignition internal combustion engine according to the present invention, and shows the vicinity of an intake bottom dead center which is a fuel injection timing for homogeneous combustion. In the figure, reference numeral 1 denotes a fuel injection valve that is disposed substantially at the center of the cylinder and directly injects fuel into the cylinder, and 2 is an ignition plug that is disposed near the intake valve side of the fuel injection valve 1. is there. FIG. 2 is a view of the inside of the cylinder of FIG. 1 as viewed from the piston side. As shown in FIG. 2, a pair of intake valves 3 are arranged on the right side of the upper part of the cylinder in FIG. An exhaust valve 4 is arranged. 5 is a piston.

本実施形態の筒内噴射式火花点火内燃機関は、燃料噴射弁１により吸気下死点近傍（例えば、燃料噴射終了クランク角度を吸気下死点近傍とするように燃料噴射量に応じて燃料噴射開始クランク角度を設定するか、又は、燃料噴射量に関係なく吸気行程後半に燃料噴射開始クランク角度を設定する）に気筒内へ直接的に燃料を噴射することにより、圧縮行程末期の点火時期には気筒内に均質混合気を形成し、この均質混合気を火花点火させて均質燃焼を実施する。   The in-cylinder injection spark ignition internal combustion engine of the present embodiment uses the fuel injection valve 1 to inject fuel in the vicinity of the intake bottom dead center (for example, in accordance with the fuel injection amount so that the fuel injection end crank angle is in the vicinity of the intake bottom dead center). By setting the start crank angle or setting the fuel injection start crank angle in the latter half of the intake stroke regardless of the fuel injection amount), the fuel is directly injected into the cylinder, thereby achieving the ignition timing at the end of the compression stroke. Forms a homogenous mixture in the cylinder, and sparks the homogeneous mixture to perform homogeneous combustion.

燃料噴射弁１は複数の噴孔を有し、各噴孔から噴射される燃料Ｆ１、Ｆ２、及びＦ３は、図１に示すように、斜め下方向にシリンダボアの排気弁側（好ましくは、吸気下死点近傍におけるシリンダボアの排気弁側下部）へ向けて噴射される。燃料噴射弁１から噴射される燃料Ｆ１、Ｆ２、及びＦ３の貫徹力は、燃料噴射開始から１ｍｓ後の燃料先端が６０ｍｍ以上に達するように設定される。   The fuel injection valve 1 has a plurality of injection holes, and the fuels F1, F2, and F3 injected from the injection holes are obliquely downward as shown in FIG. It is injected toward the exhaust valve side lower part of the cylinder bore near the bottom dead center. The penetration force of the fuels F1, F2, and F3 injected from the fuel injection valve 1 is set so that the fuel tip after 1 ms from the start of fuel injection reaches 60 mm or more.

このように強い貫徹力の燃料Ｆ１、Ｆ２、及びＦ３が気筒上部略中心からシリンダボアの排気弁側へ向けて斜め下方向に噴射されると、気筒内の排気弁側を下降して吸気弁側を上昇するように気筒内に形成されたタンブル流Ｔを燃料の貫徹力により強めることができる。こうして強められたタンブル流Ｔは、圧縮行程後半まで確実に気筒内に持続し、圧縮行程末期の点火時期には気筒内に乱れを発生させるために、燃焼速度の速い良好な均質燃焼を実現することができる。   When such strong penetrating fuels F1, F2, and F3 are injected obliquely downward from the approximate center of the cylinder top toward the exhaust valve side of the cylinder bore, the exhaust valve side in the cylinder descends and the intake valve side The tumble flow T formed in the cylinder so as to rise can be strengthened by the penetration force of the fuel. The strengthened tumble flow T is reliably maintained in the cylinder until the latter half of the compression stroke, and turbulence is generated in the cylinder at the end of the compression stroke, thereby realizing good homogeneous combustion with a high combustion speed. be able to.

本発明を限定するものではないが、本実施形態において、燃料噴射弁１は、図１及び図２に示すように五つの噴孔を有している。各噴孔から噴射される五つの柱状噴射燃料は、タンブル流Ｔの旋回方向と平行な平面と略平行な噴射方向を有する噴射燃料Ｆ１と、タンブル流Ｔの旋回方向と平行な平面に明らかに交差する噴射方向を有する二つの噴射燃料Ｆ２と、タンブル流Ｔの旋回方向と平行な平面に明らかに交差する噴射方向を有する二つの噴射燃料Ｆ３とである。   Although this invention is not limited, in this embodiment, the fuel injection valve 1 has five injection holes as shown in FIG.1 and FIG.2. The five columnar injected fuels injected from the respective nozzle holes are clearly shown in the injection fuel F1 having an injection direction substantially parallel to the plane parallel to the swirl direction of the tumble flow T and the plane parallel to the swirl direction of the tumble flow T. Two injection fuels F2 having intersecting injection directions and two injection fuels F3 having injection directions clearly intersecting a plane parallel to the swirl direction of the tumble flow T.

二つの噴射燃料Ｆ２及び二つの噴射燃料Ｆ３は、それぞれ、平面視において、タンブル流Ｔの旋回方向に平行な気筒軸線を通る平面Ｐに対して対称な方向に噴射され、この平面Ｐに対する噴射方向の鋭角側の角度は、二つの噴射燃料Ｆ３より二つの噴射燃料Ｆ２の方が小さくなっている。二つの噴射燃料Ｆ３は、平面視において平面Ｐと略直交するように、すなわち、平面Ｐに直交する平面にほぼ沿って噴射される。本実施形態では、このように気筒内の比較的広範囲に燃料が噴射されるために、噴射燃料を気筒内全体に分散させ易く、良好な均質混合気を形成することができる。   The two injected fuels F2 and the two injected fuels F3 are each injected in a direction symmetric with respect to the plane P passing through the cylinder axis parallel to the turning direction of the tumble flow T in a plan view. The angle of the acute angle of the two injected fuels F2 is smaller than that of the two injected fuels F3. The two injected fuels F3 are injected so as to be substantially orthogonal to the plane P in a plan view, that is, substantially along a plane orthogonal to the plane P. In the present embodiment, since the fuel is injected in a relatively wide range in the cylinder as described above, the injected fuel can be easily dispersed throughout the cylinder, and a good homogeneous mixture can be formed.

燃料噴射弁１の噴孔数がさらに増加される場合には、平面視の燃料噴射方向を噴射燃料Ｆ３より排気弁４側とし、いずれの噴射燃料も、斜め下方向にシリンダボアの排気弁側（好ましくは、吸気下死点近傍におけるシリンダボアの排気弁側下部）へ向けて燃料が噴射されるようにして、全ての噴射燃料が気筒内の燃料噴射弁１より排気弁側へ噴射されるようにすることが好ましい。それにより、噴射燃料が燃料噴射弁１より吸気弁３側に配置された点火プラグ２を濡らすことはなく、点火時期においてアークを確実に発生させることができる。   When the number of injection holes of the fuel injection valve 1 is further increased, the fuel injection direction in a plan view is set to the exhaust valve 4 side from the injection fuel F3, and all the injection fuels are inclined downward in the cylinder bore exhaust valve side ( Preferably, the fuel is injected toward the exhaust valve side lower part of the cylinder bore in the vicinity of the intake bottom dead center so that all the injected fuel is injected from the fuel injection valve 1 in the cylinder to the exhaust valve side. It is preferable to do. Thus, the injected fuel does not wet the spark plug 2 disposed on the intake valve 3 side of the fuel injection valve 1, and an arc can be reliably generated at the ignition timing.

ところで、こうして複数の方向に燃料が噴射される場合において、全ての噴射燃料がタンブル流Ｔを良好に強めることにはならず、タンブル流Ｔと平行な平面に略平行な噴射方向を有する噴射燃料Ｆ１が最もタンブル流Ｔを強めるのに寄与し、その他の噴射燃料は、噴射方向がタンブル流Ｔと平行な平面に対する平行程度が薄れるほど（平面視における噴射方向とタンブル流Ｔと平行な平面との鋭角側の交差角度が大きくなるほど）、タンブル流Ｔを強めるのに寄与しなくなり、タンブル流Ｔと平行な平面に直交する平面に沿う噴射方向を有する噴射燃料Ｆ３は、殆どタンブル流Ｔを強めるのに寄与しない。   By the way, in the case where fuel is injected in a plurality of directions in this way, all the injected fuel does not enhance the tumble flow T well, and the injected fuel has an injection direction substantially parallel to a plane parallel to the tumble flow T. F1 contributes to strengthening the tumble flow T most, and the other injected fuels are such that the injection direction becomes less parallel to the plane parallel to the tumble flow T (the injection direction in plan view and the plane parallel to the tumble flow T). As the crossing angle on the acute angle side increases, the fuel does not contribute to strengthening the tumble flow T, and the injected fuel F3 having an injection direction along a plane orthogonal to the plane parallel to the tumble flow T almost strengthens the tumble flow T. Does not contribute.

それにより、本実施形態では、タンブル流Ｔを強めるのに最も寄与する噴射燃料Ｆ１の貫徹力をその他の噴射燃料Ｆ２及びＦ３の貫徹力より強くするようにし、その分、噴射燃料Ｆ２及びＦ３の貫徹力は弱くされ、燃料噴射量を増量することなく、効果的にタンブル流Ｔを強めるようにしている。また、タンブル流Ｔを強めるのに寄与する噴射燃料ほど貫徹力を強くすることが好ましく、噴射燃料Ｆ２の貫徹力は噴射燃料Ｆ３の貫徹力より強くされる。   Thereby, in this embodiment, the penetration force of the injected fuel F1 that contributes most to strengthening the tumble flow T is made stronger than the penetration forces of the other injected fuels F2 and F3. The penetrating force is weakened, and the tumble flow T is effectively strengthened without increasing the fuel injection amount. Moreover, it is preferable that the penetration force of the injected fuel that contributes to strengthening the tumble flow T is increased, and the penetration force of the injected fuel F2 is made stronger than the penetration force of the injected fuel F3.

図３は燃料噴射弁１の先端部の断面図であり、図４は弁体１ａを省略した図３のＡ−Ａ断面図である。燃料噴射弁１内には燃料通路１ｂが形成され、燃料通路１ｂ内には軸線方向に上下動可能な弁体１ａが配置されている。燃料通路１ｂの円錐形状先端部には、噴射燃料Ｆ１用の第一噴孔Ｈ１と、噴射燃料Ｆ２用の二つの第二噴孔Ｈ２と、噴射燃料Ｆ３用の二つの第三噴孔Ｈ３とが形成されている。弁体１ａのシール部１ｃが燃料通路１ｂの円錐形状先端部における各噴孔Ｈ１、Ｈ２、及びＨ３の上流側のシート部に当接すると、各噴孔からの燃料噴射は停止される。一方、弁体１ａをリフトさせてシール部１ｃがシート部から離間すると、燃料通路１ｂ内の高圧燃料が各噴孔Ｈ１、Ｈ２、及びＨ３を介して噴射される。   3 is a cross-sectional view of the tip portion of the fuel injection valve 1, and FIG. 4 is a cross-sectional view taken along the line AA of FIG. A fuel passage 1b is formed in the fuel injection valve 1, and a valve body 1a capable of moving up and down in the axial direction is disposed in the fuel passage 1b. At the conical tip of the fuel passage 1b, there are a first injection hole H1 for the injected fuel F1, two second injection holes H2 for the injected fuel F2, and two third injection holes H3 for the injected fuel F3. Is formed. When the seal portion 1c of the valve body 1a comes into contact with the seat portion on the upstream side of each nozzle hole H1, H2, and H3 at the conical tip of the fuel passage 1b, fuel injection from each nozzle hole is stopped. On the other hand, when the valve body 1a is lifted and the seal portion 1c is separated from the seat portion, the high-pressure fuel in the fuel passage 1b is injected through the injection holes H1, H2, and H3.

各噴孔Ｈ１、Ｈ２、及びＨ３の内側開口は、図４に示すように、中心軸線回りの同一半径上に形成される。第一噴孔Ｈ１の内側開口は第一設定角度ａ１の中心に位置し、第二噴孔Ｈ２の内側開口はそれぞれ第二設定角度ａ２の中心に位置し、第三噴孔Ｈ３の内側開口はそれぞれ第三設定角度ａ３の中心に位置している。ここで、第一設定角度ａ１と、第二設定角度の二倍と、第三設定角度の二倍との合計は３６０°となるように設定される。   As shown in FIG. 4, the inner openings of the nozzle holes H1, H2, and H3 are formed on the same radius around the central axis. The inner opening of the first injection hole H1 is located at the center of the first setting angle a1, the inner opening of the second injection hole H2 is located at the center of the second setting angle a2, and the inner opening of the third injection hole H3 is Each is located at the center of the third set angle a3. Here, the sum of the first set angle a1, twice the second set angle, and twice the third set angle is set to be 360 °.

単純には、燃料通路１ｂの円錐形状先端部における第一設定角度ａ１内の燃料が第一噴孔Ｈ１から噴射され、第二設定角度ａ２内の燃料が第二噴孔Ｈ２から噴射され、第三設定角度ａ３内の燃料が第三噴孔Ｈ３から噴射されると考えて良く、第一設定角度ａ１（例えば１８０°）を最も大きくすることにより、第一噴孔Ｈ１から噴射されてタンブル流Ｔを強めるのに最も寄与する噴射燃料Ｆ１の貫徹力をその他の噴射燃料Ｆ２及びＦ３の貫徹力より強くすることができる。   Simply, the fuel within the first setting angle a1 at the tip of the conical shape of the fuel passage 1b is injected from the first injection hole H1, the fuel within the second setting angle a2 is injected from the second injection hole H2, and the first It can be considered that the fuel within the three set angles a3 is injected from the third nozzle hole H3. By making the first set angle a1 (for example, 180 °) the largest, the fuel is injected from the first nozzle hole H1 and is a tumble flow. The penetration force of the injected fuel F1 that contributes most to strengthening T can be made stronger than the penetration forces of the other injected fuels F2 and F3.

また、第二設定角度ａ２（例えば、６０°）を第三設定角度ａ３（例えば、３０°）より大きくすることにより、第二噴孔Ｈ２から噴射されてタンブル流Ｔを強めるのに寄与する噴射燃料Ｆ２の貫徹力を第三噴孔Ｈ３から噴射されてタンブル流Ｔを強めるのに殆ど寄与しない噴射燃料Ｆ３の貫徹力より強くすることができる。   Further, by making the second set angle a2 (for example, 60 °) larger than the third set angle a3 (for example, 30 °), the injection that is injected from the second injection hole H2 and contributes to strengthening the tumble flow T The penetration force of the fuel F2 can be made stronger than the penetration force of the injected fuel F3 which is injected from the third injection hole H3 and hardly contributes to strengthening the tumble flow T.

こうして、気筒内全体に噴射燃料を分散させ易くするには必要であるが、タンブル流Ｔを強めるのには殆ど寄与しない噴射燃料Ｆ３の貫徹力は弱められ、それにより、噴射燃料Ｆ３がシリンダボアへ到達してエンジンオイルを希釈させるようなことはない。   Thus, the penetration force of the injected fuel F3, which is necessary for facilitating the dispersion of the injected fuel in the entire cylinder but hardly contributes to increasing the tumble flow T, is weakened, whereby the injected fuel F3 is transferred to the cylinder bore. Never reach to dilute the engine oil.

本実施形態において、燃料噴射弁１は気筒上部略中心に配置したが、これは本発明を限定するものではなく、気筒上部周囲の二つの排気弁４の間、又は、気筒上部周囲の二つの吸気弁３の間に配置するようにしても良い。燃料噴射弁が気筒上部周囲の二つの排気弁４の間に配置される場合には、各噴射燃料は、タンブル流Ｔを強めるためにピストン頂面の排気弁側に向けて噴射されることが好ましい。また、燃料噴射弁が気筒上部周囲の二つの吸気弁３の間に配置される場合には、各噴射燃料は、タンブル流Ｔを強めるためにシリンダボアの排気弁側上部へ向けて噴射されることが好ましい。   In the present embodiment, the fuel injection valve 1 is disposed substantially at the center of the upper part of the cylinder, but this does not limit the present invention, and two fuel valves 4 around the upper part of the cylinder, or two around the upper part of the cylinder. It may be arranged between the intake valves 3. When the fuel injection valve is disposed between the two exhaust valves 4 around the cylinder upper portion, each injected fuel may be injected toward the exhaust valve side of the piston top surface in order to strengthen the tumble flow T. preferable. Further, when the fuel injection valve is disposed between the two intake valves 3 around the upper part of the cylinder, each injected fuel is injected toward the upper part on the exhaust valve side of the cylinder bore in order to strengthen the tumble flow T. Is preferred.

いずれの場合にも、燃料噴射弁の複数の噴孔からは、タンブル流Ｔと平行な平面に略平行な噴射方向を有する燃料と、タンブル流Ｔと平行な平面に明らかに交差する噴射方向を有する燃料とが噴射されるようにして、前述同様に噴射燃料の貫徹力を異ならせれば良い。   In any case, from the plurality of injection holes of the fuel injection valve, the fuel having an injection direction substantially parallel to the plane parallel to the tumble flow T and the injection direction clearly intersecting the plane parallel to the tumble flow T are shown. The penetration force of the injected fuel may be made different as described above so that the fuel it has is injected.

ところで、気筒内に供給される単位時間当たりの吸入空気量（吸入空気重量）は、吸気弁開弁時から吸気弁閉弁時まで徐々に増加し、吸気弁閉弁直前が最も多くなる。それにより、吸気下死点近傍の燃料噴射期間において、気筒内に生成されるタンブル流Ｔは燃料噴射開始時期から燃料噴射終了時期まで徐々に強くなる。こうして、燃料噴射期間の後半は、前半に比較してタンブル流が強くなる。   By the way, the intake air amount (intake air weight) supplied into the cylinder gradually increases from the time when the intake valve is opened to the time when the intake valve is closed, and is the largest immediately before the intake valve is closed. As a result, during the fuel injection period near the intake bottom dead center, the tumble flow T generated in the cylinder gradually increases from the fuel injection start timing to the fuel injection end timing. Thus, the tumble flow is stronger in the second half of the fuel injection period than in the first half.

気筒内に生成されているタンブル流が弱い時に貫徹力の強い燃料が噴射されても、噴射燃料は、タンブル流を突き抜けて噴射燃料のエネルギが十分にタンブル流を強めるのに利用されない。それにより、本実施形態では、図５に示すように、弁体１ａのリフト量を燃料噴射期間の前半Ｔ１では小さく後半Ｔ２では大きくするように制御している。弁体１ａのリフト量が大きくなるほど、弁体１ａのシール部１ｃと燃料通路１ｃのシート部との隙間が大きくなるために、この隙間を通過する際の燃料の抵抗が小さくなって各噴孔から噴射される燃料の貫徹力を強くすることができる。   Even if fuel with a strong penetration force is injected when the tumble flow generated in the cylinder is weak, the injected fuel is not used to penetrate the tumble flow and the energy of the injected fuel sufficiently enhances the tumble flow. Thereby, in this embodiment, as shown in FIG. 5, the lift amount of the valve body 1a is controlled to be small in the first half T1 and large in the second half T2 of the fuel injection period. The larger the lift amount of the valve body 1a, the larger the gap between the seal portion 1c of the valve body 1a and the seat portion of the fuel passage 1c. Therefore, the resistance of the fuel when passing through this gap decreases, and each nozzle hole The penetration force of the fuel injected from the fuel can be increased.

それにより、単位時間当たりの吸入空気量が多くタンブル流が強い燃料噴射期間後半の各噴射燃料の貫徹力は、単位時間当たりの吸入空気量が少なくタンブル流が弱い燃料噴射期間前半の各噴射燃料の貫徹力より強くなり、噴射燃料がタンブル流Ｔを突き抜けることが抑制される。こうして、噴射燃料のエネルギが十分にタンブル流Ｔの強化に利用されると共に、噴射燃料がシリンダボアへ到達し難くなり、エンジンオイル希釈も抑制される。   As a result, the penetration force of each injected fuel in the second half of the fuel injection period with a large amount of intake air per unit time and a strong tumble flow is equal to each injected fuel in the first half of the fuel injection period with a small amount of intake air per unit time and a weak tumble flow Therefore, the injected fuel is prevented from penetrating the tumble flow T. In this way, the energy of the injected fuel is sufficiently utilized for strengthening the tumble flow T, the injected fuel hardly reaches the cylinder bore, and engine oil dilution is also suppressed.

機関回転数が高くなるほど、また、機関負荷が高くなるほど、必要燃料量が多くなるために燃料噴射時間が長くなる。このような燃料噴射時間に対して常に前半のリフト量を小さく後半のリフト量を大きくすれば良い。もちろん、弁体１ａのリフト量を大中小の三段階に変化させることができれば、燃料噴射期間の前期のリフト量を小とし、中期のリフト量を中とし、後期のリフト量を大とすれば良い。   The higher the engine speed and the higher the engine load, the longer the fuel injection time because the required amount of fuel increases. The lift amount in the first half should always be small and the lift amount in the second half should be large with respect to such fuel injection time. Of course, if the lift amount of the valve body 1a can be changed into three stages of large, medium and small, if the lift amount in the first half of the fuel injection period is made small, the lift amount in the middle period is made medium, and the lift amount in the latter half is made large good.

また、必要燃料量の増加に伴って気筒内へ供給される吸気量も全体的に多くなり、タンブル流Ｔも全体的に強くなるために、少なくとも必要燃料量が設定範囲内である時には燃料噴射時間を一定として、必要燃料量が多くなるほど、燃料噴射時間前側のリフト量を小さくする時間Ｔ１を短くし、燃料噴射時間後側のリフト量を大きくする時間Ｔ２を長くするようにして燃料噴射量を多くすれば、全体的に強くなるタンブル流Ｔを確実に強めることができる。また、必要燃料量が少なくなるほど、燃料噴射時間前側のリフト量を小さくする時間Ｔ１を長くし、燃料噴射時間後側のリフト量を大きくする時間Ｔ２を短くするようにして燃料噴射量を少なくすれば、全体的に弱くなるタンブル流Ｔに対して噴射燃料の突き抜けを確実に抑制することができる。   Further, as the required fuel amount increases, the amount of intake air supplied into the cylinder increases as a whole, and the tumble flow T also increases as a whole. Therefore, at least when the required fuel amount is within the set range, fuel injection is performed. The fuel injection amount is set such that the time T1 for reducing the lift amount before the fuel injection time is shortened and the time T2 for increasing the lift amount after the fuel injection time is lengthened as the required fuel amount increases with the time constant. If t is increased, the tumble flow T that becomes stronger as a whole can be surely strengthened. Further, the smaller the required fuel amount, the longer the time T1 for reducing the lift amount before the fuel injection time, and the shorter the time T2 for increasing the lift amount after the fuel injection time, so that the fuel injection amount can be reduced. Thus, it is possible to reliably suppress the penetration of the injected fuel with respect to the tumble flow T that becomes weak as a whole.

このような弁体のリフト量の制御は、複数の噴孔を有する燃料噴射弁に限定されることはなく、燃料噴射弁は、単一噴孔から中実又は中空の円錐形状として燃料を噴射するものでも良い。また、燃料噴射弁は、スリット状噴孔から比較的厚さの薄い略扇形状とし燃料を噴射するものでも良い。また、燃料噴射弁は、円弧状スリット噴孔や複数の直線スリット噴孔の組み合わせにより、上側及び排気弁側を凸とする比較的厚さの薄い円弧状断面形状又は折れ線状断面形状として燃料を噴射するものでも良い。いずれにしても、噴射燃料が前述したような強い貫徹力を有して、気筒内のタンブル流Ｔを加速させるように噴射方向が選択されていれば良い。   Such control of the lift amount of the valve body is not limited to a fuel injection valve having a plurality of injection holes. The fuel injection valve injects fuel from a single injection hole as a solid or hollow conical shape. You can do it. Further, the fuel injection valve may be a substantially fan shape having a relatively thin thickness from the slit-shaped injection hole, and may inject fuel. In addition, the fuel injection valve is a combination of a circular slit nozzle hole or a plurality of linear slit nozzle holes, and the fuel is supplied in a relatively thin arc-shaped cross section or polygonal cross section having a convex shape on the upper side and the exhaust valve side. You may inject. In any case, it is only necessary that the injection direction is selected so that the injected fuel has a strong penetration force as described above and accelerates the tumble flow T in the cylinder.

本実施形態において、均質燃焼の空燃比は、理論空燃比よりリーンとされ（好ましくは、ＮＯXの生成量が抑制されるリーン空燃比とされる）、燃料消費を抑制するようにしているために、燃焼が緩慢となり易く、前述のようにして燃焼速度を速めることは特に有効である。もちろん、均質燃焼の空燃比は、理論空燃比又はリッチ空燃比としても良く、この場合においても燃焼速度を速めることは有効である。 In the present embodiment, the air-fuel ratio of homogeneous combustion is made leaner than the stoichiometric air-fuel ratio (preferably, the lean air-fuel ratio in which the amount of NO x produced is suppressed), so that fuel consumption is suppressed. In addition, the combustion tends to be slow, and it is particularly effective to increase the combustion speed as described above. Of course, the air-fuel ratio of homogeneous combustion may be a stoichiometric air-fuel ratio or a rich air-fuel ratio. In this case as well, it is effective to increase the combustion speed.

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において気筒内をピストン側から見た図である。It is the figure which looked at the inside of a cylinder from the piston side in FIG. 燃料噴射弁の先端部の概略断面図である。It is a schematic sectional drawing of the front-end | tip part of a fuel injection valve. 弁体が省略された図３のＡ−Ａ断面図である。It is AA sectional drawing of FIG. 3 with which the valve body was abbreviate | omitted. 燃料噴射期間における弁体リフトのタイムチャートである。It is a time chart of the valve body lift in a fuel injection period.

符号の説明Explanation of symbols

１ 燃料噴射弁
２ 点火プラグ
３ 吸気弁
４ 排気弁
５ ピストン
Ｔ タンブル流
Ｆ１，Ｆ２，Ｆ３ 噴射燃料 DESCRIPTION OF SYMBOLS 1 Fuel injection valve 2 Spark plug 3 Intake valve 4 Exhaust valve 5 Piston T Tumble flow F1, F2, F3 Injection fuel

Claims (2)

複数の噴孔を有して気筒内へ直接的に燃料を噴射する燃料噴射弁を具備し、均質燃焼時に吸気下死点近傍において前記燃料噴射弁から噴射される燃料によりタンブル流を強める筒内噴射式火花点火内燃機関において、前記燃料噴射弁の複数の噴孔から噴射されるうちのタンブル流と平行な平面と略平行な噴射方向を有する噴射燃料の貫徹力は、前記平面と交差する噴射方向を有する噴射燃料の貫徹力より大きくされることを特徴とする筒内噴射式火花点火内燃機関。   In-cylinder having a fuel injection valve that has a plurality of injection holes and directly injects fuel into the cylinder, and intensifies the tumble flow by the fuel injected from the fuel injection valve in the vicinity of the intake bottom dead center during homogeneous combustion In the injection-type spark ignition internal combustion engine, the penetration force of the injected fuel having an injection direction substantially parallel to a plane parallel to the tumble flow out of a plurality of injection holes of the fuel injection valve is an injection intersecting the plane. An in-cylinder injection spark ignition internal combustion engine characterized by being made larger than the penetration force of the injected fuel having a direction. 気筒内へ直接的に燃料を噴射する燃料噴射弁を具備し、均質燃焼時に吸気下死点近傍において前記燃料噴射弁から噴射される燃料によりタンブル流を強める筒内噴射式火花点火内燃機関において、燃料噴射期間の単位時間当たりの吸入空気量が多い時には前記燃料噴射期間の単位時間当たりの吸入空気量が少ない時に比較して前記燃料噴射弁から噴射される燃料の貫徹力を大きくすることを特徴とする筒内噴射式火花点火内燃機関。   In a cylinder injection spark ignition internal combustion engine that includes a fuel injection valve that directly injects fuel into a cylinder, and intensifies a tumble flow with fuel injected from the fuel injection valve in the vicinity of intake bottom dead center during homogeneous combustion, When the intake air amount per unit time in the fuel injection period is large, the penetration force of the fuel injected from the fuel injection valve is increased compared to when the intake air amount per unit time in the fuel injection period is small. An in-cylinder injection spark ignition internal combustion engine.
JP2006230830A 2006-08-04 2006-08-28 In-cylinder injection spark ignition internal combustion engine Expired - Fee Related JP4321567B2 (en)

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JP2006230830A JP4321567B2 (en) 2006-08-28 2006-08-28 In-cylinder injection spark ignition internal combustion engine
US12/282,915 US7726282B2 (en) 2006-08-04 2007-07-31 Direct injection spark ignition internal combustion engine and fuel injection method for same
EP07804677A EP2047079A1 (en) 2006-08-04 2007-07-31 Direct injection spark ignition internal combustion engine and fuel injection method for same
CN200780029165XA CN101501310B (en) 2006-08-04 2007-07-31 Direct injection type spark ignition internal combustion engine and fuel injection method thereof
PCT/IB2007/002188 WO2008015536A1 (en) 2006-08-04 2007-07-31 Direct injection spark ignition internal combustion engine and fuel injection method for same
KR1020097002172A KR101089032B1 (en) 2006-08-04 2007-07-31 Direct injection spark ignition internal combustion engine and fuel injection method for same

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