WO2017217156A1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
WO2017217156A1
WO2017217156A1 PCT/JP2017/017994 JP2017017994W WO2017217156A1 WO 2017217156 A1 WO2017217156 A1 WO 2017217156A1 JP 2017017994 W JP2017017994 W JP 2017017994W WO 2017217156 A1 WO2017217156 A1 WO 2017217156A1
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WO
WIPO (PCT)
Prior art keywords
fuel injection
hole
valve
injection valve
central axis
Prior art date
Application number
PCT/JP2017/017994
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French (fr)
Japanese (ja)
Inventor
一樹 吉村
泰介 杉井
石井　英二
義人 安川
清隆 小倉
威生 三宅
智 飯塚
Original Assignee
日立オートモティブシステムズ株式会社
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Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Publication of WO2017217156A1 publication Critical patent/WO2017217156A1/en

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    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for

Definitions

  • the present invention relates to a fuel injection valve used in an internal combustion engine such as a gasoline engine, wherein a valve body abuts against a valve seat to prevent fuel leakage, and injection is performed when the valve body is separated from a valve seat surface.
  • the present invention relates to a fuel injection valve.
  • Patent Document 1 discloses a technique for preventing the fuel from adhering to the injection opening by having a volume between the fuel jet and the inner wall of the outflow region at the injection opening.
  • Patent Document 2 discloses a technique for avoiding the interference between the spray and the wall surface by decentering the center axis of the diffusion region to the side farther from the center axis of the fuel injection valve than the center axis of the guide region.
  • an object of the present invention is to provide a fuel injection valve that can reduce the amount of fuel droplets scattered during spraying attached to the tip of the fuel injection valve.
  • the fuel injection valve of the present invention comprises: a valve body; a valve seat surface that contacts the valve body to seat fuel; and a position where the valve seat surface and the valve body abut.
  • the hole formation is seen when the fuel injection hole is viewed from the downstream direction.
  • the distance formed between the seat-side wall surface of the inner periphery of the section and the center axis of the fuel injection hole is smaller than the distance formed between the wall surface of the hole forming section on the center axis side of the fuel injection valve. Configured.
  • FIG. 1 is a cross-sectional view showing an example of an electromagnetic fuel injection valve as an example of a fuel injection valve according to the present invention.
  • FIG. 2 is an enlarged cross-sectional view of the tip of the fuel injection valve according to the present invention.
  • FIG. 3 is a cross-sectional view of the vicinity of the fuel injection hole and the counterbore of the fuel injection valve according to the present embodiment.
  • FIG. 4 is a diagram for explaining that the counterbore is eccentric with respect to the fuel injection hole in FIG. 3.
  • FIG. 5 is a diagram for explaining the fuel flow and the effects of the invention in this embodiment.
  • FIG. 1 is a cross-sectional view showing an example of an electromagnetic fuel injection valve as an example of a fuel injection valve according to the present invention.
  • FIG. 2 is an enlarged cross-sectional view of the tip of the fuel injection valve according to the present invention.
  • FIG. 3 is a cross-sectional view of the vicinity of the fuel injection hole and the counterbore of the fuel injection valve according to the present embodiment
  • FIG. 6 is a diagram for explaining an optimum counterbore eccentric direction with respect to the inclination angle of the fuel injection hole.
  • FIG. 7 is a view for explaining the fuel flow in a structure to which the present embodiment is not applied.
  • the electromagnetic fuel injection valve 100 shown in FIG. 1 is an example of an electromagnetic fuel injection valve for a direct injection type gasoline engine, but the effect of the present invention is an electromagnetic type for a port injection type gasoline engine. It is also effective in a fuel injection valve or a fuel injection valve driven by a piezo element or a magnetostrictive element.
  • FIG. 1 Fuel is supplied from a fuel supply port 112 and is supplied into the fuel injection valve.
  • the electromagnetic fuel injection valve 100 shown in FIG. 1 is a normally closed electromagnetic drive type, and when the coil 108 is not energized, the valve body 101 is urged by the spring 110 and pressed against the seat member 102. The fuel is sealed. The valve body 101 can be displaced in the axial direction of the fuel injection valve 100. At this time, in the in-cylinder injection type fuel injection valve that injects fuel directly into the cylinder of the engine, the supplied fuel pressure is in the range of about 1 MPa to 50 MPa.
  • FIG. 2 is an enlarged cross-sectional view of the tip of the fuel injection valve.
  • the nozzle body 104 is a member that is disposed on the outer peripheral side of the valve body 101 and forms a fuel flow path.
  • the outer peripheral portion of the sheet member 102 is joined to the nozzle body 104 by welding with a welding beam from the downstream direction.
  • the method for fixing the sheet member 102 to the nozzle pair 104 is not limited to welding, and may be screwing or press-fitting.
  • a conical valve seat surface 203 is formed on the surface of the seat member 102 facing the valve body 101.
  • a fuel injection hole 201 is provided at the tip of the sheet member 102. More specifically, the fuel injection hole 201 is provided in the seat member 102 on the downstream side of the contact portion (contact position) with the valve body 101.
  • the fuel injection hole 201 of this embodiment is formed by punching to form a substantially cylindrical fuel injection hole 201, and a counterbore 202 having a larger diameter than the fuel injection hole 201 is punched downstream of the fuel injection hole 201.
  • the length of the fuel injection hole 201 in the longitudinal direction is adjusted by being formed by processing.
  • 202 is referred to as a counterbore, but may be simply referred to as a dent or a hole forming portion.
  • the method of forming the fuel injection hole 201 by punching has been described, but the present invention is not limited to this, and may be formed by, for example, laser processing.
  • the valve body 101 is guided by the guide member 103 in the downstream portion, and is guided by the valve body guide 105 configured separately from the guide portion 103 in the upstream portion.
  • the guide member 103 and the valve body guide 105 are also fixedly supported by the inner peripheral portion of the nozzle body 104.
  • the anchor 106 is configured separately and independently from the valve body 101, and the rod portion of the valve body 101 is inserted into a valve body insertion hole formed on the inner peripheral side. Further, a flange portion having an outer diameter larger than that of the rod portion is formed in the upstream portion of the valve body 101, and this flange portion contacts the valve body support portion of the anchor 106 when the valve is closed in a non-energized state. Thus, the anchor 106 is energized to form a gap between the anchor 106 and the core 107.
  • the anchor 106 is attracted toward the core 107 by the magnetic attraction force. At this time, the valve body support portion of the anchor 106 and the collar portion of the valve body 101 are engaged, and the valve body 101 is engaged. Is biased toward the core 107, so that the valve can be opened.
  • FIG. 3 is an enlarged cross-sectional view of the fuel injection hole 201 and the counterbore 201.
  • the fuel injection hole 201 provided in the seat member 102 is provided with a counterbore 202a provided on the downstream side (exit side) of the fuel injection hole 201 and further on a downstream side (exit side) of the counterbore 202a.
  • the injection hole length is adjusted by the second counterbore 202b.
  • the injection hole length of the fuel injection hole 201 is defined by the length of a line connecting the center of the inlet surface and the center of the outlet surface of the fuel injection hole 201.
  • the central axis 211 of the fuel injection hole has an inclination of ⁇ with respect to the central axis 210 of the fuel injection valve.
  • the distance formed by the center axis 211 of the fuel injection hole and the side wall surface on the seat side of the counterbore 202a is indicated by an arrow L1
  • the distance formed by the side wall surface on the side of the central axis 210 of the fuel injection valve is indicated by an arrow.
  • the seat side means a direction in which a contact portion between the valve body 101 and the valve seat surface 203 of the seat member 102 is formed.
  • the distance formed by the center axis 211 of the fuel injection hole and the side wall surface on the seat side of the counterbore 202b is indicated by an arrow L1b
  • the distance formed by the side wall surface on the side of the central axis 210 of the fuel injection valve is indicated by an arrow. .
  • FIG. 4 is a view for explaining the positional relationship between the fuel injection hole 201 and the counterbore 202a and 202b, as viewed from the fuel injection hole outlet side. It consists of a fuel injection hole 201 and counterbore 202a and 202b. Similarly to FIG. 3, the distances L1a, L2a, L1b, and L2b formed by the central axis 211 of the fuel injection hole and the side wall surface of the counterbore are shown by arrows.
  • the fuel injection hole 201 has a counterbore 202a formed on the downstream side thereof, and a second counterbore 202b formed on the downstream side of the counterbore 202a.
  • the relationship between the distance L1a between the center axis 211 of the fuel injection hole and the seat-side wall surface of the counterbore 202a with respect to the fuel injection hole 201 and the distance L2a between the wall surface on the center axis 210 side is L1a.
  • ⁇ L2a is configured. That is, as shown in FIG. 4, the counterbore 202a is eccentric to the fuel injection hole 201 toward the center axis 210 of the fuel injection valve.
  • the counterbore 202b on the downstream side of the counterbore 202a is similarly eccentric to the center axis 210 side. That is, with respect to the fuel injection hole 201, a distance L1b formed by the distance between the center axis 211 of the fuel injection hole and the wall surface on the seat side of the inner periphery of the counterbore 202b, and a distance formed by the wall surface on the side of the central axis 210.
  • L2b is configured to satisfy L1b ⁇ L2b.
  • FIG. 5 is a diagram for explaining the flow of fuel and air and the effects of the invention in this embodiment.
  • the fuel is supplied mainly from the seat side as in 301.
  • the inclination angle ⁇ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve is large (for example, in the range of 20 ° to 90 ° for ⁇ in the figure)
  • the fuel on the seat side of the fuel injection hole 201 The angle 205 of the nozzle hole edge formed by the wall surface of the injection hole and the valve seat surface 203 becomes small, and it becomes difficult for the fuel that has flown to adhere to the wall surface of the fuel injection hole.
  • the counterbore 202a or 202b is decentered toward the central axis 210 of the fuel injection valve. That is, the wall surface on the sheet side of the counterbore (202a, 202b) is brought closer to the spray region 302 with respect to the side where the fuel is likely to adhere, that is, the side where the separation region 301 is likely to occur.
  • the fuel injection hole 201 is moved from the downstream direction.
  • distances (L1a, L1b) between the seat-side wall surface of the inner peripheral portion of the hole forming portion (borebore 202a, 202b) provided on the downstream side of the fuel injection hole 201 and the central axis 211 of the fuel injection hole 201 is configured to be smaller than the distance (L2a, L2b) formed by the wall surface of the hole forming portion (counterbore 202a, 202b) on the side of the central axis 210 of the fuel injection valve. That is, the relationship is L1a ⁇ L2a or L1b ⁇ L2b.
  • the upper limit value of the inclination angle ⁇ at which separation occurs is about 90 °. Therefore, the predetermined range of the inclination angle ⁇ to which this embodiment is applied is desirably about 20 ° to 90 °.
  • the fuel injection hole 201 is centered.
  • the wall surface on the seat side is the wall surface on the inner peripheral portion of the hole forming portion (the counterbore 202a, 202b) provided on the downstream side of the fuel injection hole 201. It can be said that the wall surface of the hole forming portion (the counterbore 202a, 202b) on the side of the central axis 210 of the fuel injection valve is the wall surface on the side that is difficult to peel off.
  • the wall surface of the inner peripheral portion of the hole forming portion (bore 202a, 202b) provided on the downstream side of the fuel injection hole 201 is on the side that is easy to peel off.
  • the distance (L1a, L1b) between the wall surface of the hole forming portion (borebore 202a, 202b) and the central axis 211 of the fuel injection hole 201 is the surface of the hole forming portion (borebore 202a, 202b) that is difficult to peel off and the fuel injection. It may be said that the configuration is such that the distance (L2a, L2b) between the hole 201 and the central axis 211 is smaller.
  • the scattered droplets 306 and the adhering fuels 303, 304, and 305 are easily caught in and sprayed by the air currents 311 and 312 induced by the spray region 302. Therefore, it is possible to reduce the amount of fuel (303, 304, 305) adhering to the hole forming portions (bore 202a, 202b) and the tip of the fuel injection valve.
  • the attached fuel 303 in the counterbore 202a can be reduced by the eccentricity of the counterbore 202a, and the attached fuel 304 and the fuel 305 attached to the tip of the fuel injection valve can be reduced by the eccentricity of the counterbore 202b.
  • the adhering fuel 305 may be referred to as fuel adhering to the vicinity of the outer peripheral side of the most downstream outlet surface of the fuel injection hole 201.
  • the relationship between the distance L1a formed by the distance between the center axis 211b of the fuel injection hole and the wall surface on the seat side of the inner periphery of the counterbore 202c, and the distance L2a formed by the wall surface on the side of the central axis 210 is L1a> L2a.
  • the relationship between the distance L1b formed by the distance between the center axis 211b of the fuel injection hole and the wall surface on the seat side of the inner periphery of the counterbore 202d and the distance L2b formed by the wall surface on the side of the central axis 210 are L1b> It is configured to be L2b.
  • the fuel injection hole 201 is directed downstream of the central axis 211.
  • the distance (L1a, L1b) formed between the seat-side wall surface of the inner peripheral portion of the hole forming portion (counterbore 202a, 202b) provided on the downstream side of the fuel injection hole 201 and the central axis 211 of the fuel injection hole 201 ) Is larger than the distance (L2a, L2b) formed by the wall surface of the hole forming portion (counterbore 202a, 202b) on the central axis 210 side of the fuel injection valve. That is, the relationship is L1a> L2a or L1b> L2b.
  • FIG. 7 is a diagram for explaining the flow of fuel and air in a structure to which the present embodiment is not applied, for comparison with the present embodiment.
  • the fuel injection hole 201 and the center axes of the counterbore 202e, 202f are coincident.
  • the gap between the spray region 302 and the counterbore side wall surface is larger on the separation region 310 side, so the velocity of the air flow 311b induced by the spray is small.
  • the velocity of the airflow induced by spraying is greatest in the vicinity of the spray region 302, and the velocity of the airflow decreases as the distance from the spray region 302 increases.
  • the distance between the fuel attachment positions 303b, 304b, and 305b and the spray region 302 is farther than in this embodiment. Therefore, in the structure of FIG. 7, the force for blowing off the attached fuel by the airflows 311 b and 312 at the attachment position is weaker than that of this embodiment. That is, it is important for reducing the amount of attached fuel that the spray region and the counterbore wall are brought closer to the side where the flow field peels in the fuel injection hole.
  • the inclination angle ⁇ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve among the plurality of fuel injection holes 201 is It is desirable to perform the eccentricity shown in FIGS. 3 and 4 for the fuel injection valve of a predetermined value or more (for example, 20 ° or more). That is, when the inclination angle ⁇ is within a predetermined large range (20 ° to 90 °), the hole provided on the downstream side of the fuel injection hole 201 when the fuel injection hole 201 in the relationship is viewed from the downstream direction.
  • the distance (L1a, L1b) formed between the seat-side wall surface of the inner peripheral portion of the forming portion (counterbore 202a, 202b) and the central axis 211 of the fuel injection hole 201 is the hole forming portion on the central axis 210 side of the fuel injection valve. It is configured so as to be smaller than the distance (L2a, L2b) formed by the wall surface of (the counterbore 202a, 202b).
  • the inclination angles ⁇ of all the plurality of fuel injection valves are within a large range, they may be similarly decentered with respect to the hole forming portions (counterbore 202a, 202b) of all the fuel injection valves.
  • the fuel injection hole 201b whose inclination angle ⁇ of the center axis 211b of the fuel injection hole 201b with respect to the center axis 210 of the fuel injection valve is less than a predetermined value (for example, less than 20 °)
  • a predetermined value for example, less than 20 °
  • the fuel droplets scattered during spraying and the fuel adhering to the tip of the fuel injection valve can be efficiently blown off by the airflow induced by the spraying. Therefore, it is possible to provide a fuel injection valve that can reduce the fuel adhering to the tip of the fuel injection valve and realize an internal combustion engine with improved exhaust performance.
  • FIG. 8 is a cross-sectional view showing the configuration of the valve body of the fuel injection valve in the present embodiment, and those assigned the same numbers as those in FIG. 3 have the same or equivalent functions as those in the first embodiment. .
  • the first embodiment is different from the first embodiment in that a hole forming portion (counterbore 202g) provided downstream of the fuel injection valve 201 is in one stage. Even when the counterbore has one stage, the effect of the present invention can be obtained if the separation position in the fuel injection hole and the relationship between L1a and L2a satisfy the conditions described in the first embodiment.
  • FIG. 9 is a cross-sectional view showing the configuration of the fuel injector and the flow field of the fuel in this embodiment.
  • the same reference numerals as those in FIG. 3 denote the same or equivalent functions as those in the first embodiment. It is what has.
  • This embodiment differs from the first embodiment in that R machining is applied to the connection portion between the side wall surface and the end surface of the counterbore 202h or the counterbore 202i provided downstream of the fuel injection valve 201. R processing is given to the said connection part.
  • the connection portion where the upstream end surface and the wall surface are connected is configured as an R portion.
  • the attached fuel 303c or 304c is likely to spread thinly due to surface tension, so that the area of contact between the airflow 311c induced between the spray region 302 and the counterbore and the attached fuel 303c or 304c increases, and the airflow 311c is increased. It becomes easy to be removed by being pulled.
  • FIG. 10 is a diagram showing an example of a counterbore shape of the fuel injection valve in the present embodiment.
  • the first embodiment is different from the first embodiment in that the counterbore 202j is configured by two curves having different curvatures, and thus L1a ⁇ L2a. That is, when the fuel injection hole 201 is viewed from the downstream direction, the cross-sectional shape of the hole forming portion 202j is formed from a plurality of curves having different curvatures, and thus L1a ⁇ L2a.
  • the effect of the present invention can be obtained without making the counterbore eccentric. Two or more curves forming a counterbore shape may be used.
  • Electromagnetic fuel injection valve 101 ... Valve body 102 ... Seat member 103 ... Guide member 104 ... Nozzle body 105 ... Valve body guide 106 ... Anchor 107 ... Core 108 ... Coil 109 ... Yoke 110 ... Spring 111 ... Connector 112 ... Fuel supply Ports 201, 201b ... Fuel injection holes 202, 202a, 202b, 202c, 202d, 202e, 202f, 202g, 202h, 202i, 202j ... Counterbore 203 ... Valve seat surface 204 ... Valve seat surface side contact portion 205, 206 ... Fuel Injection hole edge 210 ...

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Provided is a fuel injection valve used in internal combustion engines, the fuel injection valve being configured to reduce the amount of fuel adhering to the front end of the fuel injection valve. This fuel injection valve has: a valve body; a valve seat surface coming in contact with the valve body to seat the fuel; a fuel injection hole formed downstream of the position where the valve seat surface and the valve body come in contact with each other; and a hole-shaped section formed downstream of the fuel injection hole. The fuel injection valve is configured such that, when the fuel injection hole is viewed from the downstream side, the distance between the seat-side wall surface of the inner peripheral section of the hole-shaped section and the center axis of the fuel injection hole is less than the distance between the wall surface of the hole-shaped section, which is located on the side of the center axis of the fuel injection valve, and the center axis of the fuel injection hole.

Description

燃料噴射弁Fuel injection valve
　本発明は、ガソリンエンジン等の内燃機関に用いられる燃料噴射弁であって、弁体が弁座と当接することで燃料の漏洩を防止し、弁体が弁座面から離れることによって噴射を行なう、燃料噴射弁に関する。 The present invention relates to a fuel injection valve used in an internal combustion engine such as a gasoline engine, wherein a valve body abuts against a valve seat to prevent fuel leakage, and injection is performed when the valve body is separated from a valve seat surface. The present invention relates to a fuel injection valve.
　近年、自動車の排ガス規制が強化されており、この排ガス規制の強化に対応するため、筒内壁面（燃焼室内）や燃料噴射弁先端への液体燃料の付着低減が求められている。特に燃料噴射弁先端へ燃料が付着すると不完全燃焼によってデポジットが発生し、噴霧性能の変化や、未燃粒子状物質の発生要因となることが課題となっている。 In recent years, exhaust gas regulations for automobiles have been strengthened, and in order to respond to the strengthening of the exhaust gas regulations, it is required to reduce the adhesion of liquid fuel to the cylinder inner wall surface (combustion chamber) and the tip of the fuel injection valve. In particular, when fuel adheres to the tip of the fuel injection valve, deposits are generated due to incomplete combustion, which causes changes in spray performance and causes of generation of unburned particulate matter.
　これに対して、特許文献１では、噴射開口において燃料噴流と流出領域の内壁の間に容積を有することで、噴射開口に対する燃料付着を阻止する技術が開示されている。特許文献２では、拡散領域の中心軸をガイド領域の中心軸よりも燃料噴射弁の中心軸から遠い側に偏心することで、噴霧と壁面の干渉を回避する技術が開示されている。 On the other hand, Patent Document 1 discloses a technique for preventing the fuel from adhering to the injection opening by having a volume between the fuel jet and the inner wall of the outflow region at the injection opening. Patent Document 2 discloses a technique for avoiding the interference between the spray and the wall surface by decentering the center axis of the diffusion region to the side farther from the center axis of the fuel injection valve than the center axis of the guide region.
特表２００６－５１０８４９号公報JP-T 2006-510849 特開２０１４－００１６６０号公報JP 2014-001660 A
　上記従来技術においては、噴霧と壁面の干渉を回避することにより、燃料噴射弁先端への燃料付着を回避するザグリ形成の技術が公開されている。一方で、噴霧中に燃料噴射弁の先端近傍で細かな液滴に分裂して飛散する燃料液滴が、燃料噴射弁の先端に付着することについては考慮されていない。 In the above prior art, a counterbore forming technique for avoiding fuel adhesion to the tip of the fuel injection valve by avoiding interference between the spray and the wall surface is disclosed. On the other hand, it is not taken into account that fuel droplets that break up into fine droplets near the tip of the fuel injection valve during spraying and adhere to the tip of the fuel injection valve.
　そこで、本発明の目的は、噴霧中に飛散する燃料液滴が燃料噴射弁の先端へ付着する量を低減できる燃料噴射弁を提供することである。 Therefore, an object of the present invention is to provide a fuel injection valve that can reduce the amount of fuel droplets scattered during spraying attached to the tip of the fuel injection valve.
　上記目的を達成するために、本発明の燃料噴射弁は、　弁体と、前記弁体と当接して燃料をシートする弁座面と、前記弁座面と前記弁体とが当接する位置よりも下流側に形成された燃料噴射孔と、前記燃料噴射孔よりも下流側に形成された孔形成部と、を有する燃料噴射弁において、前記燃料噴射孔を下流方向から見て、前記孔形成部の内周部のシート側の壁面と前記燃料噴射孔の中心軸との成す距離が、前記燃料噴射弁の中心軸の側の前記孔形成部の壁面とが成す距離に対して小さくなるように構成された。 In order to achieve the above object, the fuel injection valve of the present invention comprises: a valve body; a valve seat surface that contacts the valve body to seat fuel; and a position where the valve seat surface and the valve body abut. In the fuel injection valve having a fuel injection hole formed on the downstream side and a hole forming portion formed on the downstream side of the fuel injection hole, the hole formation is seen when the fuel injection hole is viewed from the downstream direction. The distance formed between the seat-side wall surface of the inner periphery of the section and the center axis of the fuel injection hole is smaller than the distance formed between the wall surface of the hole forming section on the center axis side of the fuel injection valve. Configured.
　本発明によれば、噴霧中に飛散する燃料液滴が燃料噴射弁の先端へ付着する量を低減できる燃料噴射弁を提供することが可能となる。本発明の上記した以外の構成、作用、効果については、以下の実施例において詳細に説明する。 According to the present invention, it is possible to provide a fuel injection valve that can reduce the amount of fuel droplets scattered during spraying attached to the tip of the fuel injection valve. The configurations, operations, and effects of the present invention other than those described above will be described in detail in the following examples.
本発明に係る燃料噴射弁の実施例を示す断面図である。It is sectional drawing which shows the Example of the fuel injection valve which concerns on this invention. 本発明に係る燃料噴射弁の先端の実施例を示す断面図である。It is sectional drawing which shows the Example of the front-end | tip of the fuel injection valve which concerns on this invention. 本発明の第１実施例に係る燃料噴射弁の燃料噴射孔とザグリ近傍の断面図である。It is sectional drawing of the fuel injection hole and counterbore vicinity of the fuel injection valve which concerns on 1st Example of this invention. 本発明の第１実施例に係る燃料噴射孔とザグリの位置関係を説明するための図である。It is a figure for demonstrating the positional relationship of the fuel-injection hole and counterbore which concerns on 1st Example of this invention. 本発明の第１実施例に係る燃料噴射孔とザグリ近傍の燃料流れを説明するための図である。It is a figure for demonstrating the fuel injection hole which concerns on 1st Example of this invention, and the fuel flow of the counterbore vicinity. 本発明の第１実施例に係る燃料噴射孔の傾斜角度の変化に対する最適構造を説明するための図である。It is a figure for demonstrating the optimal structure with respect to the change of the inclination-angle of the fuel injection hole which concerns on 1st Example of this invention. 本発明の第１実施例との比較のための本実施例を適用しない構造における燃料流れを説明するための図である。It is a figure for demonstrating the fuel flow in the structure which does not apply the present Example for the comparison with 1st Example of this invention. 本発明の第２実施例に係る燃料噴射弁の燃料噴射孔とザグリ近傍の断面図である。It is sectional drawing of the fuel-injection hole and counterbore vicinity of the fuel injection valve which concerns on 2nd Example of this invention. 本発明の第３実施例に係る燃料噴射弁の燃料噴射孔とザグリ近傍の断面図である。It is sectional drawing of the fuel-injection hole and counterbore vicinity of the fuel injection valve which concerns on 3rd Example of this invention. 本発明の第４実施例に係る燃料噴射孔とザグリ形状近傍を説明するための図である。It is a figure for demonstrating the fuel-injection hole and counterbore shape vicinity which concern on 4th Example of this invention.
　以下、本発明に係る実施例を説明する。 Hereinafter, examples according to the present invention will be described.
　本発明の第１の実施例に係る燃料噴射弁について、図１から図７を用いて以下説明する。　
　図１は、本発明に係わる燃料噴射弁の例として、電磁式燃料噴射弁の例を示す断面図である。図２は、本発明に係る燃料噴射弁の先端を拡大した断面図である。図３は、本実施例に係る燃料噴射弁の燃料噴射孔とザグリ近傍の断面図である。図４は、図３において燃料噴射孔に対してザグリが偏心していることを説明する図である。図５は、本実施例における燃料流れと発明の効果を説明するための図である。図６は、燃料噴射孔の傾斜角度に対する最適なザグリ偏心方向を説明するための図である。図７は、本実施例を適用しない構造における燃料流れを説明するための図である。図１に示した電磁式燃料噴射弁１００は、筒内直接噴射式のガソリンエンジン向けの電磁式燃料噴射弁の例であるが、本発明の効果は、ポート噴射式のガソリンエンジン向けの電磁式燃料噴射弁や、ピエゾ素子や磁歪素子で駆動される燃料噴射弁においても有効である。 A fuel injection valve according to a first embodiment of the present invention will be described below with reference to FIGS.
FIG. 1 is a cross-sectional view showing an example of an electromagnetic fuel injection valve as an example of a fuel injection valve according to the present invention. FIG. 2 is an enlarged cross-sectional view of the tip of the fuel injection valve according to the present invention. FIG. 3 is a cross-sectional view of the vicinity of the fuel injection hole and the counterbore of the fuel injection valve according to the present embodiment. FIG. 4 is a diagram for explaining that the counterbore is eccentric with respect to the fuel injection hole in FIG. 3. FIG. 5 is a diagram for explaining the fuel flow and the effects of the invention in this embodiment. FIG. 6 is a diagram for explaining an optimum counterbore eccentric direction with respect to the inclination angle of the fuel injection hole. FIG. 7 is a view for explaining the fuel flow in a structure to which the present embodiment is not applied. The electromagnetic fuel injection valve 100 shown in FIG. 1 is an example of an electromagnetic fuel injection valve for a direct injection type gasoline engine, but the effect of the present invention is an electromagnetic type for a port injection type gasoline engine. It is also effective in a fuel injection valve or a fuel injection valve driven by a piezo element or a magnetostrictive element.
　［電磁式燃料噴射弁の基本動作］
　図１において、燃料は燃料供給口１１２から供給され、燃料噴射弁の内部に供給される。図１に示す電磁式燃料噴射弁１００は、通常時閉型の電磁駆動式であって、コイル１０８に通電がないときには、弁体１０１がスプリング１１０によって付勢されてシート部材１０２に押し付けられ、燃料がシールされるようになっている。弁体１０１は燃料噴射弁１００の軸方向に変位可能である。このとき、エンジンの筒内に直接、燃料を噴射する筒内噴射型燃料噴射弁では、供給される燃料圧力がおよそ１ＭＰａから５０ＭＰａの範囲である。 [Basic operation of electromagnetic fuel injection valve]
In FIG. 1, fuel is supplied from a fuel supply port 112 and is supplied into the fuel injection valve. The electromagnetic fuel injection valve 100 shown in FIG. 1 is a normally closed electromagnetic drive type, and when the coil 108 is not energized, the valve body 101 is urged by the spring 110 and pressed against the seat member 102. The fuel is sealed. The valve body 101 can be displaced in the axial direction of the fuel injection valve 100. At this time, in the in-cylinder injection type fuel injection valve that injects fuel directly into the cylinder of the engine, the supplied fuel pressure is in the range of about 1 MPa to 50 MPa.
　図２は燃料噴射弁の先端を拡大した断面図である。ノズル体１０４は、弁体１０１の外周側に配置され、燃料の流路を形成する部材である。ノズル体１０４にはシート部材１０２の外周部が下流方向からの溶接ビームにより溶接で接合される。なお、このシート部材１０２のノズル対１０４への固定方法は溶接に限ったものではなく、ネジ止めや圧入であっても良い。シート部材１０２の弁体１０１との対向面には、円錐形状の弁座面２０３が形成される。 FIG. 2 is an enlarged cross-sectional view of the tip of the fuel injection valve. The nozzle body 104 is a member that is disposed on the outer peripheral side of the valve body 101 and forms a fuel flow path. The outer peripheral portion of the sheet member 102 is joined to the nozzle body 104 by welding with a welding beam from the downstream direction. The method for fixing the sheet member 102 to the nozzle pair 104 is not limited to welding, and may be screwing or press-fitting. A conical valve seat surface 203 is formed on the surface of the seat member 102 facing the valve body 101.
　電磁式燃料噴射弁１００が閉弁状態にあるときには、弁体１０１の先端部がシート部材１０２の弁座面２０３と当接することによって燃料のシールを保つようになっている。シート部材１０２の先端には燃料噴射孔２０１が設けられる。より具体的には、シート部材１０２には、弁体１０１との当接部（当接位置）よりも下流側において、燃料噴射孔２０１が設けられる。本実施例の燃料噴射孔２０１は打ち抜き加工により、ほぼ円筒形状の燃料噴射孔２０１が形成され、そして、燃料噴射孔２０１よりも下流側において、燃料噴射孔２０１よりも大径のザグリ２０２が打ち抜き加工により形成されることによって燃料噴射孔２０１の長手方向の長さが調整される。以下においては、２０２をザグリと呼ぶが、単に凹み部と呼んでも良いし、孔形成部と呼んでも良い。本実施例では打ち抜き加工により燃料噴射孔２０１を形成する方法を説明したが、本発明はこれに限定される訳では無く、たとえばレーザ加工により形成しても良い。 When the electromagnetic fuel injection valve 100 is in the closed state, the tip of the valve body 101 is brought into contact with the valve seat surface 203 of the seat member 102 to keep the fuel seal. A fuel injection hole 201 is provided at the tip of the sheet member 102. More specifically, the fuel injection hole 201 is provided in the seat member 102 on the downstream side of the contact portion (contact position) with the valve body 101. The fuel injection hole 201 of this embodiment is formed by punching to form a substantially cylindrical fuel injection hole 201, and a counterbore 202 having a larger diameter than the fuel injection hole 201 is punched downstream of the fuel injection hole 201. The length of the fuel injection hole 201 in the longitudinal direction is adjusted by being formed by processing. In the following description, 202 is referred to as a counterbore, but may be simply referred to as a dent or a hole forming portion. In the present embodiment, the method of forming the fuel injection hole 201 by punching has been described, but the present invention is not limited to this, and may be formed by, for example, laser processing.
　図１に示したコネクタ１１１を介してコイル１０８に通電されると、電磁弁の磁気回路を構成するコア（固定コア）１０７、ヨーク１０９、アンカー１０６に磁束密度が生じる。そして、コア１０７とアンカー１０６の間には非通電時において空隙が形成されており、コア１０７にアンカー１０６が吸引されるような磁気吸引力が生じる。アンカー１０６には下流方向に向かってスプリング１１０の付勢力と前述の燃料圧力による付勢力がかかっているが、通電による磁気吸引力がこれらの付勢力よりも大きくなると、アンカー１０６がコア１０７に向かって移動する。 When the coil 108 is energized through the connector 111 shown in FIG. 1, magnetic flux density is generated in the core (fixed core) 107, the yoke 109, and the anchor 106 constituting the magnetic circuit of the electromagnetic valve. A gap is formed between the core 107 and the anchor 106 when no current is applied, and a magnetic attractive force that attracts the anchor 106 to the core 107 is generated. The urging force of the spring 110 and the urging force due to the above-described fuel pressure are applied to the anchor 106 in the downstream direction. However, when the magnetic attraction force by energization becomes larger than these urging forces, the anchor 106 moves toward the core 107. Move.
　弁体１０１は下流部においてガイド部材１０３によりガイドされ、上流部においてガイド部１０３とは別体で構成された弁体ガイド１０５にガイドされる。なお、ガイド部材１０３、弁体ガイド１０５もノズル体１０４の内周部により固定支持される。アンカー１０６は弁体１０１とは別体で独立して構成され、内周側に形成された弁体挿入穴に弁体１０１のロッド部が挿入される。また弁体１０１の上流部にはロッド部よりも外径の大きいつば部が形成されており、非通電状態の閉弁時においては、このつば部がアンカー１０６の弁体支持部に接触することで、アンカー１０６を付勢し、アンカー１０６とコア１０７との空隙を形成する。 The valve body 101 is guided by the guide member 103 in the downstream portion, and is guided by the valve body guide 105 configured separately from the guide portion 103 in the upstream portion. The guide member 103 and the valve body guide 105 are also fixedly supported by the inner peripheral portion of the nozzle body 104. The anchor 106 is configured separately and independently from the valve body 101, and the rod portion of the valve body 101 is inserted into a valve body insertion hole formed on the inner peripheral side. Further, a flange portion having an outer diameter larger than that of the rod portion is formed in the upstream portion of the valve body 101, and this flange portion contacts the valve body support portion of the anchor 106 when the valve is closed in a non-energized state. Thus, the anchor 106 is energized to form a gap between the anchor 106 and the core 107.
　一方で、コイル１０８に通電されると磁気吸引力によりアンカー１０６がコア１０７の側に吸引され、このときアンカー１０６の弁体支持部と弁体１０１のつば部が係合して、弁体１０１をコア１０７の側に付勢するため、開弁状態とすることができる。 On the other hand, when the coil 108 is energized, the anchor 106 is attracted toward the core 107 by the magnetic attraction force. At this time, the valve body support portion of the anchor 106 and the collar portion of the valve body 101 are engaged, and the valve body 101 is engaged. Is biased toward the core 107, so that the valve can be opened.
　開弁状態となると、弁座面２０３と弁体１０１の当接部に隙間（ストローク）を生じ、燃料の噴射が開始される。燃料の噴射が開始されると、燃料圧力として与えられたエネルギは運動エネルギに変換されて燃料噴射孔２０１に至り、図示していないが、エンジンの筒内に向かって噴射される。 When the valve is opened, a gap (stroke) is generated at the contact portion between the valve seat surface 203 and the valve body 101, and fuel injection is started. When fuel injection is started, the energy given as the fuel pressure is converted into kinetic energy and reaches the fuel injection hole 201, which is injected into the cylinder of the engine (not shown).
　［燃料噴射孔の詳細な形状］
　次に、燃料噴射孔２０１とザグリ２０２の詳細な形状について図３及び図４を用いて説明する。　
　図３は、燃料噴射孔２０１とザグリ２０１の拡大断面図である。本実施例において、シート部材１０２に設けられた燃料噴射孔２０１は、燃料噴射孔２０１の下流側（出口側）に設けられたザグリ２０２ａと、さらにザグリ２０２ａの下流側（出口側）に設けられた第二のザグリ２０２ｂと、により噴射孔長さが調整される。燃料噴射孔２０１の噴射孔長さは、燃料噴射孔２０１の入口面中心と出口面中心とを結ぶ線の長さで定義される。 [Detailed shape of fuel injection hole]
Next, detailed shapes of the fuel injection hole 201 and the counterbore 202 will be described with reference to FIGS. 3 and 4.
FIG. 3 is an enlarged cross-sectional view of the fuel injection hole 201 and the counterbore 201. In this embodiment, the fuel injection hole 201 provided in the seat member 102 is provided with a counterbore 202a provided on the downstream side (exit side) of the fuel injection hole 201 and further on a downstream side (exit side) of the counterbore 202a. The injection hole length is adjusted by the second counterbore 202b. The injection hole length of the fuel injection hole 201 is defined by the length of a line connecting the center of the inlet surface and the center of the outlet surface of the fuel injection hole 201.
　燃料噴射孔の中心軸２１１は燃料噴射弁の中心軸２１０に対してθの傾斜を持つ。燃料噴射孔の中心軸２１１と、ザグリ２０２ａのシート側の側壁面とが成す距離をＬ１ａ、燃料噴射弁の中心軸２１０側の側壁面とが成す距離をＬ２ａとして矢印で図示している。ここで、シート側とは弁体１０１とシート部材１０２の弁座面２０３との当接部が構成される方向を意味している。また、燃料噴射孔の中心軸２１１と、ザグリ２０２ｂのシート側の側壁面とが成す距離をＬ１ｂ、燃料噴射弁の中心軸２１０側の側壁面とが成す距離をＬ２ｂとして矢印で図示している。 The central axis 211 of the fuel injection hole has an inclination of θ with respect to the central axis 210 of the fuel injection valve. The distance formed by the center axis 211 of the fuel injection hole and the side wall surface on the seat side of the counterbore 202a is indicated by an arrow L1, and the distance formed by the side wall surface on the side of the central axis 210 of the fuel injection valve is indicated by an arrow. Here, the seat side means a direction in which a contact portion between the valve body 101 and the valve seat surface 203 of the seat member 102 is formed. In addition, the distance formed by the center axis 211 of the fuel injection hole and the side wall surface on the seat side of the counterbore 202b is indicated by an arrow L1b, and the distance formed by the side wall surface on the side of the central axis 210 of the fuel injection valve is indicated by an arrow. .
　図４は燃料噴射孔出口側から見た、燃料噴射孔２０１とザグリ２０２ａと２０２ｂの位置関係を説明するための図である。燃料噴射孔２０１とザグリ２０２ａ及び２０２ｂで構成されている。また、図３と同様に燃料噴射孔の中心軸２１１とザグリの側壁面が成す距離Ｌ１ａ、Ｌ２ａ、Ｌ１ｂ、Ｌ２ｂを矢印で図示している。 FIG. 4 is a view for explaining the positional relationship between the fuel injection hole 201 and the counterbore 202a and 202b, as viewed from the fuel injection hole outlet side. It consists of a fuel injection hole 201 and counterbore 202a and 202b. Similarly to FIG. 3, the distances L1a, L2a, L1b, and L2b formed by the central axis 211 of the fuel injection hole and the side wall surface of the counterbore are shown by arrows.
　図３と図４を用いて本実施例の構造による作用、効果を説明する。図３に示したように、燃料噴射孔２０１は、その下流側にザグリ２０２ａが形成され、さらにザグリ２０２ａの下流側に第二のザグリ２０２ｂが形成される。そして燃料噴射孔２０１に対して、燃料噴射孔の中心軸２１１とザグリ２０２ａの内周部のシート側の壁面との成す距離Ｌ１ａ、中心軸２１０の側の壁面とが成す距離Ｌ２ａの関係がＬ１ａ＜Ｌ２ａとなるように構成する。つまり、図４に示すように、燃料噴射孔２０１に対して、ザグリ２０２ａが燃料噴射弁の中心軸２１０側に偏心させる。 The operation and effect of the structure of the present embodiment will be described with reference to FIGS. As shown in FIG. 3, the fuel injection hole 201 has a counterbore 202a formed on the downstream side thereof, and a second counterbore 202b formed on the downstream side of the counterbore 202a. The relationship between the distance L1a between the center axis 211 of the fuel injection hole and the seat-side wall surface of the counterbore 202a with respect to the fuel injection hole 201 and the distance L2a between the wall surface on the center axis 210 side is L1a. <L2a is configured. That is, as shown in FIG. 4, the counterbore 202a is eccentric to the fuel injection hole 201 toward the center axis 210 of the fuel injection valve.
　また、本実施例では、ザグリ２０２ａの下流側のザグリ２０２ｂについても同様に中心軸２１０の側に偏心させる。つまり、燃料噴射孔２０１に対して、燃料噴射孔の中心軸２１１とザグリ２０２ｂの内周部のシート側の壁面との成す距離とが成す距離Ｌ１ｂ、中心軸２１０の側の壁面とが成す距離Ｌ２ｂの関係がＬ１ｂ＜Ｌ２ｂとなるように構成する。 Further, in this embodiment, the counterbore 202b on the downstream side of the counterbore 202a is similarly eccentric to the center axis 210 side. That is, with respect to the fuel injection hole 201, a distance L1b formed by the distance between the center axis 211 of the fuel injection hole and the wall surface on the seat side of the inner periphery of the counterbore 202b, and a distance formed by the wall surface on the side of the central axis 210. The relationship of L2b is configured to satisfy L1b <L2b.
　ザグリ２０２ａ、またはザグリ２０２ｂを偏心させたことによる作用、効果は以下に説明するが、本発明はザグリ２０２ａだけでも同様の作用、効果を得ることができ、必ずしもザグリ２０２ａ及びザグリ２０２ｂに限定される訳ではない。 Actions and effects resulting from the eccentricity of the counterbore 202a or the counterbore 202b will be described below, but the present invention can provide the same action and effect with the counterbore 202a alone, and is not necessarily limited to the counterbore 202a and the counterbore 202b. Not a translation.
　［本実施例の流れ、効果］
　上記のように燃料噴射孔及びザグリを構成したことによる作用効果を、図５から図７を用いて説明する。 [Flow and effects of this embodiment]
The operational effects of configuring the fuel injection hole and the counterbore as described above will be described with reference to FIGS.
　図５は、本実施例における燃料と空気の流れ及び発明の効果を説明するための図である。燃料の供給が開始されると、燃料は３０１のように主にシート側から供給される。このとき、燃料噴射弁の中心軸２１０に対する燃料噴射孔２０１の中心軸２１１の傾斜角θが大きい場合（例えば図のθでは２０°から９０°の範囲）、燃料噴射孔２０１のシート側では燃料噴射孔壁面と弁座面２０３が成す噴孔縁の角度２０５が小さくなり、流入した燃料が燃料噴射孔の壁面に付着しにくくなるため、はく離領域３１０が生じる。はく離領域３１０が生じると、燃料噴射孔２０１の内部へ空気が侵入する虞が生じる。またはく離領域３１０によりキャビテーションが生じ燃料の流れの乱れを発生させる虞がある。そしてこれらの現象により気液界面で流れの乱れが発生し、液滴への分裂が促進される。 FIG. 5 is a diagram for explaining the flow of fuel and air and the effects of the invention in this embodiment. When the supply of fuel is started, the fuel is supplied mainly from the seat side as in 301. At this time, when the inclination angle θ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve is large (for example, in the range of 20 ° to 90 ° for θ in the figure), the fuel on the seat side of the fuel injection hole 201 The angle 205 of the nozzle hole edge formed by the wall surface of the injection hole and the valve seat surface 203 becomes small, and it becomes difficult for the fuel that has flown to adhere to the wall surface of the fuel injection hole. When the peeling region 310 is generated, there is a risk that air may enter the fuel injection hole 201. Alternatively, cavitation may occur due to the separation region 310, and the fuel flow may be disturbed. These phenomena cause flow disturbance at the gas-liquid interface and promote breakup into droplets.
　これにより、噴霧領域３０２以外の領域に飛散する液滴３０６が多く発生する。この液滴が壁面に付着することで、一段目のザグリ２０２ａの角部に付着した燃料３０３や、二段目のザグリ２０２ｂの角部に付着した燃料３０４、燃料噴射弁の先端に付着した３０５が形成されることが問題となる。 As a result, a large number of droplets 306 that scatter in a region other than the spray region 302 are generated. As the droplets adhere to the wall surface, the fuel 303 attached to the corner of the first-stage counterbore 202a, the fuel 304 attached to the corner of the second- stage counterbore 202b, and 305 attached to the tip of the fuel injection valve. It becomes a problem that is formed.
　そこで、本実施例では図３、４に示したように、燃料噴射弁の中心軸２１０に向かってザグリ２０２ａ、または２０２ｂを偏心させる。つまり、燃料が付着しやすい側、つまりはく離領域３０１の発生しやすい側に対して、ザグリ（２０２ａ、２０２ｂ）のシート側の壁面を噴霧領域３０２と近づける。 Therefore, in this embodiment, as shown in FIGS. 3 and 4, the counterbore 202a or 202b is decentered toward the central axis 210 of the fuel injection valve. That is, the wall surface on the sheet side of the counterbore (202a, 202b) is brought closer to the spray region 302 with respect to the side where the fuel is likely to adhere, that is, the side where the separation region 301 is likely to occur.
　より具体的には、燃料噴射弁の中心軸２１０に対する燃料噴射孔２０１の中心軸２１１の傾斜角θが所定値以上（たとえば２０°以上）であった場合に、燃料噴射孔２０１を下流方向から見て、燃料噴射孔２０１の下流側に設けられた孔形成部（ザグリ２０２ａ、２０２ｂ）の内周部のシート側の壁面と燃料噴射孔２０１の中心軸２１１との成す距離（Ｌ１ａ、Ｌ１ｂ）が、燃料噴射弁の中心軸２１０の側の孔形成部（ザグリ２０２ａ、２０２ｂ）の壁面とが成す距離（Ｌ２ａ、Ｌ２ｂ）に対して小さくなるように構成する。つまり、Ｌ１ａ＜Ｌ２ａ、又はＬ１ｂ＜Ｌ２ｂの関係となる。 More specifically, when the inclination angle θ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve is a predetermined value or more (for example, 20 ° or more), the fuel injection hole 201 is moved from the downstream direction. As seen, distances (L1a, L1b) between the seat-side wall surface of the inner peripheral portion of the hole forming portion (borebore 202a, 202b) provided on the downstream side of the fuel injection hole 201 and the central axis 211 of the fuel injection hole 201 However, it is configured to be smaller than the distance (L2a, L2b) formed by the wall surface of the hole forming portion ( counterbore 202a, 202b) on the side of the central axis 210 of the fuel injection valve. That is, the relationship is L1a <L2a or L1b <L2b.
　なお、本発明者らの鋭意検討の結果によれば、はく離が生じる傾斜角θの上限値はだいたい９０°付近であることがわかっている。したがって、本実施例を適用する傾斜角θの所定範囲はおよそ２０°～９０°程度であることが望ましい。 In addition, according to the result of earnest examination by the present inventors, it is known that the upper limit value of the inclination angle θ at which separation occurs is about 90 °. Therefore, the predetermined range of the inclination angle θ to which this embodiment is applied is desirably about 20 ° to 90 °.
　別の言い方をすると燃料噴射弁の中心軸２１０に対する燃料噴射孔２０１の中心軸２１１の傾斜角θが所定範囲（２０°≦θ≦９０°）であった場合には、燃料噴射孔２０１を中心軸２１１の下流方向から見て、燃料噴射孔２０１の下流側に設けられた孔形成部（ザグリ２０２ａ、２０２ｂ）の内周部の壁面において、シート側の壁面がはく離し易い側の壁面であり、燃料噴射弁の中心軸２１０の側の孔形成部（ザグリ２０２ａ、２０２ｂ）の壁面ははく離し難い側の壁面であると言える。 In other words, when the inclination angle θ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve is within a predetermined range (20 ° ≦ θ ≦ 90 °), the fuel injection hole 201 is centered. As seen from the downstream side of the shaft 211, the wall surface on the seat side is the wall surface on the inner peripheral portion of the hole forming portion (the counterbore 202a, 202b) provided on the downstream side of the fuel injection hole 201. It can be said that the wall surface of the hole forming portion (the counterbore 202a, 202b) on the side of the central axis 210 of the fuel injection valve is the wall surface on the side that is difficult to peel off.
　したがって、燃料噴射孔２０１を中心軸２１１の下流方向から見て、燃料噴射孔２０１の下流側に設けられた孔形成部（ザグリ２０２ａ、２０２ｂ）の内周部の壁面において、はく離し易い側の孔形成部（ザグリ２０２ａ、２０２ｂ）の壁面と燃料噴射孔２０１の中心軸２１１との成す距離（Ｌ１ａ、Ｌ１ｂ）が、はく離し難い側の孔形成部（ザグリ２０２ａ、２０２ｂ）の壁面と燃料噴射孔２０１の中心軸２１１との成す距離（Ｌ２ａ、Ｌ２ｂ）に対して小さくなるように構成するといっても良い。 Accordingly, when the fuel injection hole 201 is viewed from the downstream direction of the central axis 211, the wall surface of the inner peripheral portion of the hole forming portion ( bore 202a, 202b) provided on the downstream side of the fuel injection hole 201 is on the side that is easy to peel off. The distance (L1a, L1b) between the wall surface of the hole forming portion (borebore 202a, 202b) and the central axis 211 of the fuel injection hole 201 is the surface of the hole forming portion (borebore 202a, 202b) that is difficult to peel off and the fuel injection. It may be said that the configuration is such that the distance (L2a, L2b) between the hole 201 and the central axis 211 is smaller.
　これにより、飛散した液滴３０６や付着燃料３０３、３０４、３０５を、噴霧領域３０２が誘起する気流３１１、３１２によって噴霧に巻き込んで吹き飛ばしやすくしている。
したがって、孔形成部（ザグリ２０２ａ、２０２ｂ）や燃料噴射弁先端への付着燃料（３０３、３０４、３０５）の量を低減することが可能となる。 As a result, the scattered droplets 306 and the adhering fuels 303, 304, and 305 are easily caught in and sprayed by the air currents 311 and 312 induced by the spray region 302.
Therefore, it is possible to reduce the amount of fuel (303, 304, 305) adhering to the hole forming portions ( bore 202a, 202b) and the tip of the fuel injection valve.
　ザグリ２０２ａの偏心によりザグリ内での付着燃料３０３を低減することができ、またザグリ２０２ｂの偏心によりザグリ内での付着燃料３０４と燃料噴射弁先端への付着燃料３０５を低減することができる。付着燃料３０５は燃料噴射孔２０１の最下流側出口面の外周側近傍に付着する燃料と言っても良い。 The attached fuel 303 in the counterbore 202a can be reduced by the eccentricity of the counterbore 202a, and the attached fuel 304 and the fuel 305 attached to the tip of the fuel injection valve can be reduced by the eccentricity of the counterbore 202b. The adhering fuel 305 may be referred to as fuel adhering to the vicinity of the outer peripheral side of the most downstream outlet surface of the fuel injection hole 201.
　以上においては燃料噴射孔内のシート側において、はく離が生じる場合について説明した。一方で、図６のようにθが小さい、もしくは燃料噴射孔が燃料噴射弁の中心軸２１０方向に向かって開口している場合、燃料噴射孔２０１ｂの内部において、図５とは逆に燃料噴射弁の中心軸２１０側において燃料噴射孔壁面と弁座面２０３が成す噴孔縁の角度２０６が小さくなり、流入する燃料が燃料噴射孔の壁面に付着しにくくなるため、はく離３１０ｂが生じる。 In the above, the case where separation occurs on the seat side in the fuel injection hole has been described. On the other hand, when θ is small as shown in FIG. 6 or the fuel injection hole is opened toward the central axis 210 of the fuel injection valve, fuel injection is performed inside the fuel injection hole 201b, contrary to FIG. The angle 206 of the nozzle hole edge formed by the fuel injection hole wall surface and the valve seat surface 203 on the side of the central axis 210 of the valve becomes small, and the inflowing fuel is less likely to adhere to the wall surface of the fuel injection hole, thus causing the separation 310b.
　この場合、図６には図示していないが、図５のザグリ２０２ａの角部に付着した燃料３０３、ザグリ２０２ｂの角部に付着した燃料３０４、燃料噴射弁の先端に付着した燃料３０５が、それぞれ図５とは逆に燃料噴射弁の中心軸２１０の側に付着する虞がある。そこで、これに対しては、シート側に向かってザグリ２０２ａ、または２０２ｂを偏心させる。 In this case, although not shown in FIG. 6, the fuel 303 attached to the corner of the counterbore 202a in FIG. 5, the fuel 304 attached to the corner of the counterbore 202b, and the fuel 305 attached to the tip of the fuel injection valve, Contrary to FIG. 5, there is a risk of adhering to the center axis 210 side of the fuel injection valve. Therefore, the counterbore 202a or 202b is decentered toward the sheet side.
　つまり燃料噴射孔の中心軸２１１ｂとザグリ２０２ｃの内周部のシート側の壁面との成す距離とが成す距離Ｌ１ａ、中心軸２１０の側の壁面とが成す距離Ｌ２ａの関係がＬ１ａ＞Ｌ２ａとなるように構成する。また一方で、燃料噴射孔の中心軸２１１ｂとザグリ２０２ｄの内周部のシート側の壁面との成す距離とが成す距離Ｌ１ｂ、中心軸２１０の側の壁面とが成す距離Ｌ２ｂの関係がＬ１ｂ＞Ｌ２ｂとなるように構成する。これにより、それぞれの付着燃料を、噴霧領域が誘起する気流によって噴霧３１１、３１２に巻き込んで吹き飛ばしやすくしている。 That is, the relationship between the distance L1a formed by the distance between the center axis 211b of the fuel injection hole and the wall surface on the seat side of the inner periphery of the counterbore 202c, and the distance L2a formed by the wall surface on the side of the central axis 210 is L1a> L2a. Configure as follows. On the other hand, the relationship between the distance L1b formed by the distance between the center axis 211b of the fuel injection hole and the wall surface on the seat side of the inner periphery of the counterbore 202d and the distance L2b formed by the wall surface on the side of the central axis 210 are L1b> It is configured to be L2b. Thereby, each adhering fuel is easily caught in the sprays 311 and 312 by the air current induced by the spray region and easily blown off.
　つまり、燃料噴射弁の中心軸２１０に対する燃料噴射孔２０１の中心軸２１１の傾斜角θが所定値未満（θ＜２０°）であった場合には、燃料噴射孔２０１を中心軸２１１の下流方向から見て、燃料噴射孔２０１の下流側に設けられた孔形成部（ザグリ２０２ａ、２０２ｂ）の内周部のシート側の壁面と燃料噴射孔２０１の中心軸２１１との成す距離（Ｌ１ａ、Ｌ１ｂ）が、燃料噴射弁の中心軸２１０の側の孔形成部（ザグリ２０２ａ、２０２ｂ）の壁面とが成す距離（Ｌ２ａ、Ｌ２ｂ）に対して大きくなるように構成する。つまり、Ｌ１ａ＞Ｌ２ａ、又はＬ１ｂ＞Ｌ２ｂの関係となる。 That is, when the inclination angle θ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve is less than a predetermined value (θ <20 °), the fuel injection hole 201 is directed downstream of the central axis 211. , The distance (L1a, L1b) formed between the seat-side wall surface of the inner peripheral portion of the hole forming portion ( counterbore 202a, 202b) provided on the downstream side of the fuel injection hole 201 and the central axis 211 of the fuel injection hole 201 ) Is larger than the distance (L2a, L2b) formed by the wall surface of the hole forming portion ( counterbore 202a, 202b) on the central axis 210 side of the fuel injection valve. That is, the relationship is L1a> L2a or L1b> L2b.
　図７は、本実施例と比較するための、本実施例を適用しない構造における燃料と空気の流れを説明する図である。図７の構造では燃料噴射孔２０１とザグリ２０２ｅ、２０２ｆの中心軸が一致している。実施例と比較して、はく離領域３１０側において噴霧領域３０２とザグリの側壁面の隙間が大きいため、噴霧によって誘起される気流３１１ｂの速度は小さい。また、噴霧によって誘起される気流の速度は噴霧領域３０２の近傍が最も大きく、噴霧領域３０２から離れるほど気流の速度が小さくなる。 FIG. 7 is a diagram for explaining the flow of fuel and air in a structure to which the present embodiment is not applied, for comparison with the present embodiment. In the structure of FIG. 7, the fuel injection hole 201 and the center axes of the counterbore 202e, 202f are coincident. Compared to the embodiment, the gap between the spray region 302 and the counterbore side wall surface is larger on the separation region 310 side, so the velocity of the air flow 311b induced by the spray is small. In addition, the velocity of the airflow induced by spraying is greatest in the vicinity of the spray region 302, and the velocity of the airflow decreases as the distance from the spray region 302 increases.
　図７の構造では燃料付着位置３０３ｂ、３０４ｂ、３０５ｂと噴霧領域３０２との距離が本実施例よりも遠い。そのため、図７の構造では付着位置における気流３１１ｂ、３１２によって付着燃料を吹きとばす力が本実施例よりも弱い。つまり、燃料噴射孔内で流れ場がはく離する側に対して、噴霧領域とザグリ壁面を近づけることが付着燃料量の低減には重要となる。 In the structure of FIG. 7, the distance between the fuel attachment positions 303b, 304b, and 305b and the spray region 302 is farther than in this embodiment. Therefore, in the structure of FIG. 7, the force for blowing off the attached fuel by the airflows 311 b and 312 at the attachment position is weaker than that of this embodiment. That is, it is important for reducing the amount of attached fuel that the spray region and the counterbore wall are brought closer to the side where the flow field peels in the fuel injection hole.
　また、図７の構造において、単にザグリ径を狭くすることで燃料噴射孔の中心軸とザグリ側壁面の距離を小さくすることが可能である。しかしながら、噴霧は燃料噴射孔の中心軸に対して対称であるとは限らず、噴霧がザグリの角等に接触することを考えると、ザグリ径を変更できる自由度は低くなる。噴霧干渉を回避するようにザグリ径を最適化した上で、本実施例により、さらに燃料付着量を低減するためのザグリ位置の最適化が可能となる。 In the structure of FIG. 7, it is possible to reduce the distance between the central axis of the fuel injection hole and the counterbore side wall surface by simply reducing the counterbore diameter. However, the spray is not necessarily symmetric with respect to the central axis of the fuel injection hole, and considering that the spray contacts the counterbore corner or the like, the degree of freedom to change the counterbore diameter is low. After optimizing the counterbore diameter so as to avoid spray interference, this embodiment makes it possible to optimize the counterbore position in order to further reduce the fuel adhesion amount.
　なお、シート部材１０２に複数の燃料噴射孔２０１が形成される場合には、複数の燃料噴射孔２０１のうち、燃料噴射弁の中心軸２１０に対する燃料噴射孔２０１の中心軸２１１の傾斜角θが所定値以上（たとえば２０°以上）の燃料噴射弁に対して、図３、４で示した偏心を行うことが望ましい。つまり、傾斜角θが所定の大きな範囲（２０°～９０°）である場合には、その関係にある燃料噴射孔２０１を下流方向から見て、燃料噴射孔２０１の下流側に設けられた孔形成部（ザグリ２０２ａ、２０２ｂ）の内周部のシート側の壁面と燃料噴射孔２０１の中心軸２１１との成す距離（Ｌ１ａ、Ｌ１ｂ）が、燃料噴射弁の中心軸２１０の側の孔形成部（ザグリ２０２ａ、２０２ｂ）の壁面とが成す距離（Ｌ２ａ、Ｌ２ｂ）に対して小さくなるように構成する。 When a plurality of fuel injection holes 201 are formed in the seat member 102, the inclination angle θ of the central axis 211 of the fuel injection hole 201 with respect to the central axis 210 of the fuel injection valve among the plurality of fuel injection holes 201 is It is desirable to perform the eccentricity shown in FIGS. 3 and 4 for the fuel injection valve of a predetermined value or more (for example, 20 ° or more). That is, when the inclination angle θ is within a predetermined large range (20 ° to 90 °), the hole provided on the downstream side of the fuel injection hole 201 when the fuel injection hole 201 in the relationship is viewed from the downstream direction. The distance (L1a, L1b) formed between the seat-side wall surface of the inner peripheral portion of the forming portion ( counterbore 202a, 202b) and the central axis 211 of the fuel injection hole 201 is the hole forming portion on the central axis 210 side of the fuel injection valve. It is configured so as to be smaller than the distance (L2a, L2b) formed by the wall surface of (the counterbore 202a, 202b).
　全ての複数の燃料噴射弁の傾斜角θが大きな範囲にあれば、全ての燃料噴射弁の孔形成部（ザグリ２０２ａ、２０２ｂ）に対して、同じように偏心させても良い。 If the inclination angles θ of all the plurality of fuel injection valves are within a large range, they may be similarly decentered with respect to the hole forming portions ( counterbore 202a, 202b) of all the fuel injection valves.
　一方で複数の燃料噴射孔のうち、当該燃料噴射弁の中心軸２１０に対する燃料噴射孔２０１ｂの中心軸２１１ｂの傾斜角θが所定値未満（たとえば２０°未満）の燃料噴射孔２０１ｂは、燃料噴射孔２０１ｂを下流方向から見て、孔形成部（ザグリ２０２ｃ、２０２ｄ）の内周部のシート側の壁面と当該燃料噴射孔２０１ｂの中心軸２１１ｂとの成す距離が、燃料噴射弁の中心軸２１０の側の孔形成部（ザグリ２０２ｃ、２０２ｄ）の壁面とが成す距離に対して大きくなるように構成する。あるいは同じになるように構成しても良い。 On the other hand, among the plurality of fuel injection holes, the fuel injection hole 201b whose inclination angle θ of the center axis 211b of the fuel injection hole 201b with respect to the center axis 210 of the fuel injection valve is less than a predetermined value (for example, less than 20 °) When the hole 201b is viewed from the downstream direction, the distance formed between the seat-side wall surface of the inner peripheral portion of the hole forming portion (counterbore 202c, 202d) and the central axis 211b of the fuel injection hole 201b is the central axis 210 of the fuel injection valve. It is configured so as to increase with respect to the distance formed by the wall surface of the hole forming portion (counterbore 202c, 202d) on this side. Or you may comprise so that it may become the same.
　以上の本実施例によれば、噴霧が誘起する気流によって、噴霧中に飛散した燃料液滴及び燃料噴射弁先端に付着した燃料を効率よく吹き飛ばすことが可能となる。したがって、燃料噴射弁先端に付着する燃料を低減でき、排気性能を高めた内燃機関を実現する燃料噴射弁を提供できる。 According to the present embodiment described above, the fuel droplets scattered during spraying and the fuel adhering to the tip of the fuel injection valve can be efficiently blown off by the airflow induced by the spraying. Therefore, it is possible to provide a fuel injection valve that can reduce the fuel adhering to the tip of the fuel injection valve and realize an internal combustion engine with improved exhaust performance.
　本発明の第２の実施例に係わる燃料噴射弁について、図８を用いて以下説明する。図８は本実施例における燃料噴射弁の弁体の構成を示す断面図であり、図３と同一の番号が割り当てられているものは、実施例１と同一もしくは同等の機能を有するものである。 A fuel injection valve according to the second embodiment of the present invention will be described below with reference to FIG. FIG. 8 is a cross-sectional view showing the configuration of the valve body of the fuel injection valve in the present embodiment, and those assigned the same numbers as those in FIG. 3 have the same or equivalent functions as those in the first embodiment. .
　第１の実施例とは、燃料噴射弁２０１の下流に設けられる孔形成部（ザグリ２０２ｇ）が一段になっている点が異なる。ザグリが１段になった場合でも、燃料噴射孔内のはく離位置と、Ｌ１ａとＬ２ａの関係が実施例１で説明した条件を満たしていれば、本発明の効果が得られる。 The first embodiment is different from the first embodiment in that a hole forming portion (counterbore 202g) provided downstream of the fuel injection valve 201 is in one stage. Even when the counterbore has one stage, the effect of the present invention can be obtained if the separation position in the fuel injection hole and the relationship between L1a and L2a satisfy the conditions described in the first embodiment.
　本発明の第３の実施例に係わる燃料噴射弁について、図９を用いて以下説明する。図９は本実施例における燃料噴射弁の弁体の構成と燃料の流れ場を示す断面図であり、図３と同一の番号が割り当てられているものは、実施例１と同一もしくは同等の機能を有するものである。 A fuel injection valve according to a third embodiment of the present invention will be described below with reference to FIG. FIG. 9 is a cross-sectional view showing the configuration of the fuel injector and the flow field of the fuel in this embodiment. The same reference numerals as those in FIG. 3 denote the same or equivalent functions as those in the first embodiment. It is what has.
　第１の実施例とは、燃料噴射弁２０１の下流に設けられるザグリ２０２ｈまたはザグリ２０２ｉの側壁面と端面の接続部にＲ加工が施されている点が異なる。前記接続部にＲ加工が施されている。具体的には孔形成部（ザグリ２０２ｈ、２０２ｉ）のそれぞれにおいて、上流側端面と壁面とが繋がる接続部がＲ部となるように構成される。これにより、付着燃料３０３ｃまたは３０４ｃが表面張力によって薄く広がりやすくなるため、噴霧領域３０２とザグリの間で誘起される気流３１１ｃと、付着燃料３０３ｃまたは３０４ｃとの接触する面積が増加し、気流３１１ｃに引っ張られて除去されやすくなる。 This embodiment differs from the first embodiment in that R machining is applied to the connection portion between the side wall surface and the end surface of the counterbore 202h or the counterbore 202i provided downstream of the fuel injection valve 201. R processing is given to the said connection part. Specifically, in each of the hole forming portions (counterbore 202h, 202i), the connection portion where the upstream end surface and the wall surface are connected is configured as an R portion. As a result, the attached fuel 303c or 304c is likely to spread thinly due to surface tension, so that the area of contact between the airflow 311c induced between the spray region 302 and the counterbore and the attached fuel 303c or 304c increases, and the airflow 311c is increased. It becomes easy to be removed by being pulled.
　本発明の第４の実施例に係わる燃料噴射弁について、図１０を用いて以下説明する。図１０は本実施例における燃料噴射弁のザグリ形状の例を示す図である。 A fuel injection valve according to a fourth embodiment of the present invention will be described below with reference to FIG. FIG. 10 is a diagram showing an example of a counterbore shape of the fuel injection valve in the present embodiment.
　第１の実施例とは、ザグリ２０２ｊが異なる曲率を持つ二つの曲線によって構成されており、これによりＬ１ａ＜Ｌ２ａを成している点が異なる。つまり燃料噴射孔２０１を下流方向から見て、孔形成部２０２ｊの断面形状が異なる曲率を持つ複数の曲線から形成され、これによりＬ１ａ＜Ｌ２ａを成している。このように、ザグリ形状により燃料噴射孔２０１の中心軸とザグリ側壁面の距離を変化させることにより、ザグリを偏心させなくても本発明の効果を得ることができる。なお、ザグリ形状を成す曲線は二つ以上でも良い。 The first embodiment is different from the first embodiment in that the counterbore 202j is configured by two curves having different curvatures, and thus L1a <L2a. That is, when the fuel injection hole 201 is viewed from the downstream direction, the cross-sectional shape of the hole forming portion 202j is formed from a plurality of curves having different curvatures, and thus L1a <L2a. Thus, by changing the distance between the central axis of the fuel injection hole 201 and the counterbore side wall surface according to the counterbore shape, the effect of the present invention can be obtained without making the counterbore eccentric. Two or more curves forming a counterbore shape may be used.
１００…電磁式燃料噴射弁
１０１…弁体
１０２…シート部材
１０３…ガイド部材
１０４…ノズル体
１０５…弁体ガイド
１０６…アンカー
１０７…コア
１０８…コイル
１０９…ヨーク
１１０…スプリング
１１１…コネクタ
１１２…燃料供給口
２０１、２０１ｂ…燃料噴射孔
２０２、２０２ａ、２０２ｂ、２０２ｃ、２０２ｄ、２０２ｅ、２０２ｆ、２０２ｇ、２０２ｈ、２０２ｉ、２０２ｊ…ザグリ
２０３…弁座面
２０４…弁座面側当接部
２０５、２０６…燃料噴射孔縁
２１０…燃料噴射弁の中心軸
２１１、２１１ｂ…燃料噴射孔の中心軸
３０１…燃料流れ
３０２、３０２ｂ…燃料噴霧領域
３０３、３０３ｂ、３０３ｃ、３０４、３０４ｂ、３０４ｃ、３０５、３０５ｂ…壁面への付着燃料
３０６…燃料液滴
３１０、３１０ｂ…はく離領域
３１１、３１１ｂ、３１１ｃ、３１２…気流
４０１…噴孔内の燃料 DESCRIPTION OF SYMBOLS 100 ... Electromagnetic fuel injection valve 101 ... Valve body 102 ... Seat member 103 ... Guide member 104 ... Nozzle body 105 ... Valve body guide 106 ... Anchor 107 ... Core 108 ... Coil 109 ... Yoke 110 ... Spring 111 ... Connector 112 ... Fuel supply Ports 201, 201b ... Fuel injection holes 202, 202a, 202b, 202c, 202d, 202e, 202f, 202g, 202h, 202i, 202j ... Counterbore 203 ... Valve seat surface 204 ... Valve seat surface side contact portion 205, 206 ... Fuel Injection hole edge 210 ... Fuel injection valve center axis 211, 211b ... Fuel injection hole center axis 301 ... Fuel flow 302, 302b ... Fuel spray region 303, 303b, 303c, 304, 304b, 304c, 305, 305b ... To wall surface Adhering fuel 306... Fuel droplet 310, 310 b. , 311b, 311c, 312 ... fuel of the air flow 401 ... in the injection hole

Claims (10)

  1. 　弁体と、前記弁体と当接して燃料をシートする弁座面と、前記弁座面と前記弁体とが当接する位置よりも下流側に形成された燃料噴射孔と、前記燃料噴射孔よりも下流側に形成された孔形成部と、を有する燃料噴射弁において、
    　前記燃料噴射孔を下流方向から見て、前記孔形成部の内周部のシート側の壁面と前記燃料噴射孔の中心軸との成す距離が、前記燃料噴射弁の中心軸の側の前記孔形成部の壁面とが成す距離に対して小さくなるように構成された燃料噴射弁。     A valve body, a valve seat surface that contacts the valve body and seats fuel, a fuel injection hole that is formed downstream of a position where the valve seat surface and the valve body abut, and the fuel injection hole A fuel injection valve having a hole forming portion formed on the downstream side of the fuel injection valve;
    When the fuel injection hole is viewed from the downstream direction, the distance formed between the seat-side wall surface of the inner periphery of the hole forming portion and the central axis of the fuel injection hole is the hole on the central axis side of the fuel injection valve. A fuel injection valve configured to be smaller than a distance formed by a wall surface of the forming portion.
  2. 　請求項１に記載の燃料噴射弁において、
    　前記燃料噴射弁の中心軸に対する前記燃料噴射孔の中心軸の傾斜角θが所定値以上である燃料噴射弁。     The fuel injection valve according to claim 1, wherein
    A fuel injection valve in which an inclination angle θ of the central axis of the fuel injection hole with respect to the central axis of the fuel injection valve is a predetermined value or more.
  3. 　請求項１に記載の燃料噴射弁において、
    　前記孔形成部よりもさらに下流側に形成された下流側孔形成部を有し、
    　前記燃料噴射孔を下流方向から見て、前記下流側孔形成部の内周部のシート側の壁面と前記燃料噴射孔の中心軸との成す距離が、前記燃料噴射弁の中心軸の側の前記下流側孔形成部の壁面とが成す距離に対して小さくなるように構成された燃料噴射弁。     The fuel injection valve according to claim 1, wherein
    A downstream hole forming part formed further downstream than the hole forming part,
    When the fuel injection hole is viewed from the downstream direction, the distance formed between the seat-side wall surface of the inner peripheral portion of the downstream hole forming portion and the central axis of the fuel injection hole is on the central axis side of the fuel injection valve. A fuel injection valve configured to be smaller than a distance formed by a wall surface of the downstream hole forming portion.
  4. 　弁体と、前記弁体と当接して燃料をシートする弁座面と、前記弁座面と前記弁体とが当接する位置よりも下流側に形成された燃料噴射孔と、前記燃料噴射孔よりも下流側に形成された孔形成部と、を有する燃料噴射弁において、
    　前記孔形成部の内周部の壁面において、はく離し易い側の当該孔形成部の壁面と前記燃料噴射孔の中心軸との成す距離が、はく離し難い側の当該孔形成部の壁面と前記燃料噴射孔の中心軸との成す距離に対して小さくなるように構成された燃料噴射弁。     A valve body, a valve seat surface that contacts the valve body and seats fuel, a fuel injection hole that is formed downstream of a position where the valve seat surface and the valve body abut, and the fuel injection hole A fuel injection valve having a hole forming portion formed on the downstream side of the fuel injection valve;
    In the wall surface of the inner peripheral portion of the hole forming portion, the distance formed between the wall surface of the hole forming portion on the side that is easy to peel off and the central axis of the fuel injection hole is the wall surface of the hole forming portion on the side that is difficult to peel off A fuel injection valve configured to be small with respect to a distance formed with a central axis of the fuel injection hole.
  5. 　弁体と、前記弁体と当接して燃料をシートする弁座面と、前記弁座面と前記弁体とが当接する位置よりも下流側に形成された複数の燃料噴射孔と、前記複数の燃料噴射孔よりも下流側に形成された孔形成部と、を有する燃料噴射弁において、
    　前記複数の燃料噴射孔のうち、当該燃料噴射弁の中心軸に対する前記燃料噴射孔の中心軸の傾斜角θが所定値以上の燃料噴射孔は、当該燃料噴射孔を下流方向から見て、孔形成部の内周部のシート側の壁面と当該燃料噴射孔の中心軸との成す距離が、前記燃料噴射弁の中心軸の側の前記孔形成部の壁面とが成す距離に対して小さくなるように構成された燃料噴射弁。     A valve body, a valve seat surface that contacts the valve body and seats fuel, a plurality of fuel injection holes formed on a downstream side of a position where the valve seat surface and the valve body abut, and the plurality A fuel injection valve having a hole forming portion formed downstream of the fuel injection hole of
    Among the plurality of fuel injection holes, a fuel injection hole having an inclination angle θ of the central axis of the fuel injection hole with respect to the central axis of the fuel injection valve is a predetermined value or more, when viewed from the downstream direction. The distance formed between the seat-side wall surface of the inner peripheral portion of the forming portion and the central axis of the fuel injection hole is smaller than the distance formed between the wall surface of the hole forming portion on the central axis side of the fuel injection valve. A fuel injection valve configured as described above.
  6. 　請求項５に記載の燃料噴射弁において、
    　前記複数の燃料噴射孔の全てが、当該燃料噴射孔を下流方向から見て、孔形成部の内周部のシート側の壁面と当該燃料噴射孔の中心軸との成す距離が、前記燃料噴射弁の中心軸の側の前記孔形成部の壁面とが成す距離に対して小さくなるように構成された燃料噴射弁。     The fuel injection valve according to claim 5,
    When all of the plurality of fuel injection holes are viewed from the downstream direction, the distance formed between the seat-side wall surface of the inner periphery of the hole forming portion and the central axis of the fuel injection hole is the fuel injection hole. A fuel injection valve configured to be small with respect to a distance formed by a wall surface of the hole forming portion on the central axis side of the valve.
  7. 　請求項５に記載の燃料噴射弁において、
    　前記複数の燃料噴射孔のうち、当該燃料噴射弁の中心軸に対する前記燃料噴射孔の中心軸の傾斜角θが所定値未満の燃料噴射孔は、当該燃料噴射孔を下流方向から見て、孔形成部の内周部のシート側の壁面と当該燃料噴射孔の中心軸との成す距離が、前記燃料噴射弁の中心軸の側の前記孔形成部の壁面とが成す距離に対して大きくなるように構成された燃料噴射弁。     The fuel injection valve according to claim 5,
    Among the plurality of fuel injection holes, the fuel injection hole whose inclination angle θ of the central axis of the fuel injection hole with respect to the central axis of the fuel injection valve is less than a predetermined value is viewed from the downstream direction. The distance formed between the seat-side wall surface of the inner peripheral portion of the formation portion and the central axis of the fuel injection hole is larger than the distance formed between the wall surface of the hole formation portion on the central axis side of the fuel injection valve. A fuel injection valve configured as described above.
  8. 　請求項１に記載の燃料噴射弁において、
    　前記孔形成部の上流側端面と壁面とが繋がる接続部がＲ部となるように構成された燃料噴射弁。     The fuel injection valve according to claim 1, wherein
    The fuel injection valve comprised so that the connection part which the upstream end surface and wall surface of the said hole formation part may connect may become R part.
  9. 　請求項３に記載の燃料噴射弁において、
    　前記孔形成部及び前記下流側孔形成部のそれぞれにおいて、上流側端面と壁面とが繋がる接続部がＲ部となるように構成された燃料噴射弁。     The fuel injection valve according to claim 3,
    A fuel injection valve configured such that, in each of the hole forming portion and the downstream hole forming portion, a connection portion where an upstream end surface and a wall surface are connected is an R portion.
  10. 　請求項１に記載の燃料噴射弁において、
    　前記燃料噴射孔を下流方向から見て、前記孔形成部の断面形状が異なる曲率を持つ複数の曲線から形成された燃料噴射弁。     The fuel injection valve according to claim 1, wherein
    A fuel injection valve formed from a plurality of curves having curvatures with different cross-sectional shapes of the hole forming portion when the fuel injection hole is viewed from the downstream direction.
PCT/JP2017/017994 2016-06-17 2017-05-12 Fuel injection valve WO2017217156A1 (en)

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JP2006257992A (en) * 2005-03-17 2006-09-28 Toyota Motor Corp Fuel injection device
JP2008064094A (en) * 2006-09-05 2008-03-21 Robert Bosch Gmbh Fuel injection valve
JP2009236057A (en) * 2008-03-27 2009-10-15 Toyota Motor Corp Fuel injection valve and internal combustion engine
JP2010038126A (en) * 2008-08-08 2010-02-18 Hitachi Ltd Fuel injection valve
JP2011001864A (en) * 2009-06-18 2011-01-06 Hitachi Automotive Systems Ltd Fuel injection valve
JP2016089660A (en) * 2014-10-31 2016-05-23 日立オートモティブシステムズ株式会社 Fuel injection device

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Publication number Priority date Publication date Assignee Title
JP2001300360A (en) * 2000-04-26 2001-10-30 Aisan Ind Co Ltd Fluid injection nozzle and fluid injection valve provided with the fluid injection nozzle
JP2006257992A (en) * 2005-03-17 2006-09-28 Toyota Motor Corp Fuel injection device
JP2008064094A (en) * 2006-09-05 2008-03-21 Robert Bosch Gmbh Fuel injection valve
JP2009236057A (en) * 2008-03-27 2009-10-15 Toyota Motor Corp Fuel injection valve and internal combustion engine
JP2010038126A (en) * 2008-08-08 2010-02-18 Hitachi Ltd Fuel injection valve
JP2011001864A (en) * 2009-06-18 2011-01-06 Hitachi Automotive Systems Ltd Fuel injection valve
JP2016089660A (en) * 2014-10-31 2016-05-23 日立オートモティブシステムズ株式会社 Fuel injection device

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