WO2014136309A1 - 燃料噴射弁 - Google Patents

燃料噴射弁 Download PDF

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Publication number
WO2014136309A1
WO2014136309A1 PCT/JP2013/078450 JP2013078450W WO2014136309A1 WO 2014136309 A1 WO2014136309 A1 WO 2014136309A1 JP 2013078450 W JP2013078450 W JP 2013078450W WO 2014136309 A1 WO2014136309 A1 WO 2014136309A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel injection
fuel
passage
swirl
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2013/078450
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
岡本　良雄
一樹 吉村
前川　典幸
小林　信章
石井　英二
貴博 齋藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Priority to CN201380044026.XA priority Critical patent/CN104583578B/zh
Priority to IN1032DEN2015 priority patent/IN2015DN01032A/en
Publication of WO2014136309A1 publication Critical patent/WO2014136309A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0667—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature acting as a valve or having a short valve body attached thereto
    • 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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • 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
    • 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
    • F02M61/1853—Orifice plates

Definitions

  • the present invention relates to a fuel injection valve used in an internal combustion engine, and relates to a fuel injection valve capable of improving atomization performance by injecting swirling fuel.
  • Patent Document 1 A fuel injection valve described in Patent Document 1 is known as a prior art that promotes atomization of fuel injected from a plurality of fuel injection holes using a swirl flow.
  • the injector plate has a lateral passage communicating with the downstream end and a swirl chamber whose downstream end is opened in a tangential direction, and the fuel injection hole for injecting the swirled fuel in the swirl chamber
  • the fuel injection hole is disposed with a predetermined distance offset from the center of the swirl chamber to the upstream end side of the lateral passage.
  • Such a configuration can effectively promote atomization of fuel injected from each fuel injection hole.
  • a fuel injection valve described in Patent Document 2 includes a valve seat body having a stationary valve seat, a valve closing body that cooperates with the valve seat body and is movable in the axial direction along a valve longitudinal axis, A perforated disc disposed downstream of the seat, the perforated disc having at least one inflow region and at least one outflow opening, the upper side having at least one inflow region
  • the functional seat has a different opening geometry from the lower functional plane with at least one outflow opening as viewed in cross section
  • the valve seat body being at least one inflow of the perforated disc
  • the region is partly directly covered by the lower end surface, and at least two outflow openings are covered by the valve seat.
  • the swirling flow is substantially symmetric at the outlet of the fuel injection hole (
  • a flow path shape including a swirl chamber (swirl chamber) shape and a lateral passage (swirl passage).
  • the total volume of the fuel flow path affects the accuracy of the injection characteristics (accuracy decreases as the volume increases)
  • the present invention has been made in view of such circumstances, and an object thereof is to provide a fuel injection valve with improved uniformity in the circumferential direction of the swirling flow.
  • a fuel injection valve has a valve body slidably provided, a valve seat surface on which the valve body sits when the valve is closed, and a fuel flow.
  • a nozzle body having an opening on the downstream side, a turning passage provided downstream of the opening of the nozzle body, and communicating with the opening, formed downstream of the turning passage, and having a cylindrical shape
  • a swirl chamber having an inner surface and swirling fuel inside to impart a swirl force; a bottom surface of the swirl passage having a fuel injection hole formed in a cylindrical shape at the bottom of the swirl chamber and injecting fuel to the outside Protrusions that direct the flow of fuel toward the upper surface of the swirling passage are provided in the section.
  • the fuel has improved symmetry of the swirling flow at the fuel injection hole, and the symmetry of the spray from the fuel injection hole is improved.
  • FIG. 1 is a longitudinal sectional view showing the overall configuration of a fuel injection valve 1 according to one of the embodiments of the present invention in a section along the valve axis.
  • a fuel injection valve 1 has a structure in which a nozzle body 2 and a valve body 6 are accommodated in a thin stainless steel pipe 13 and the valve body 6 is reciprocated (open / closed) by an electromagnetic coil 11 disposed outside. is there. Details of the structure will be described below.
  • a fuel injection chamber 4 that allows passage of fuel flowing through the clearance between the valve seat surface 3, the valve body 6 and the valve seat surface 3, and a plurality of fuel injection holes 23 a, 23 b, 23 c, downstream of the fuel injection chamber 4, And an orifice plate 20 having 23d (see FIGS. 2 to 4).
  • a spring 8 as an elastic member for pressing the valve body 6 against the valve seat surface 3 is provided at the center of the core 7.
  • the elastic force of the spring 8 is adjusted by the pushing amount of the spring adjuster 9 in the direction of the valve seat surface 3.
  • valve body 6 is moved by the electromagnetic force until it contacts the lower end surface of the core 7 facing the valve 11 to open the valve.
  • the fuel injection valve 1 is provided with a fuel passage 12 having a filter 14 at the inlet.
  • the fuel passage 12 includes a through-hole portion that penetrates the center of the core 7 and is pressurized by a fuel pump (not shown). This is a passage that guides the fuel that has passed through the fuel injection valve 1 to the plurality of fuel injection holes 23a, 23b, 23c, and 23d.
  • the outer portion of the fuel injection valve 1 is covered with a resin mold 15 and electrically insulated.
  • the operation of the fuel injection valve 1 controls the amount of fuel supplied by switching the position of the valve body 6 between the valve open state and the valve closed state in accordance with energization (injection pulse) to the coil 11. is doing.
  • valve body design is designed so that there is no fuel leakage, especially when the valve is closed.
  • This type of fuel injection valve uses a ball (steel ball for ball bearing of JIS standard product) having a high roundness and a mirror finish on the valve body 6, which is beneficial for improving the sheet property.
  • valve seat angle of the valve seat surface 3 with which the ball is in close contact is an optimum angle of 80 ° to 100 ° with good grindability and high roundness, and the sheet property with the above-mentioned ball is extremely high. It can be maintained.
  • the hardness of the nozzle body 2 having the valve seat surface 3 is increased by quenching, and unnecessary magnetism is removed by demagnetization treatment.
  • valve body 6 enables injection amount control without fuel leakage. Therefore, it is set as the valve body structure excellent in cost performance.
  • FIG. 2 is a longitudinal sectional view showing the vicinity of the nozzle body 2 in the fuel injection valve 1 according to one embodiment of the present invention.
  • the orifice plate 20 has an upper surface 20 a that is in contact with the lower surface 2 a of the nozzle body 2, and the outer periphery of this contact portion is laser-welded and fixed to the nozzle body 2.
  • the cross section of the orifice plate 20 is a cross section in the A direction of FIG.
  • the vertical direction is based on FIG. 1, and the inlet side of the fuel passage 12 is on the upper side and the plurality of fuel injection holes 23a, 23b, 23c, 23d are on the lower side in the axial direction of the fuel injection valve 1. Let it be the side.
  • the lower end portion of the nozzle body 2 is provided with a fuel introduction hole 5 having a diameter smaller than the diameter ⁇ S of the seat portion 3 a of the valve seat surface 3.
  • the valve seat surface 3 has a conical shape, and a fuel introduction hole 5 is formed at the center of the downstream end thereof.
  • valve seat surface 3 and the fuel introduction hole 5 are formed so that the center line of the valve seat surface 3 and the center line of the fuel introduction hole 5 coincide with the valve axis Y. Due to the fuel introduction hole 5, an inflow opening 20 b communicating with the fuel passage is formed on the contact surface between the lower end surface 2 a of the nozzle body 2 and the upper surface 20 a of the orifice plate 20 corresponding to the fuel passage located downstream.
  • FIG. 3 is a plan view of the orifice plate 20 located at the lower end of the nozzle body 2 in the fuel injection valve 1 according to one embodiment of the present invention.
  • turning passages 21a, 21b, 21c, and 21d that extend radially from the position separated from the center of the orifice plate 20 toward the radially outer peripheral side are formed.
  • the turning passages 21a, 21b, 21c, and 21d are arranged at equal intervals (intervals of 90 degrees) in the circumferential direction.
  • These turning passages 21 a, 21 b, 21 c, and 21 d form a concave fuel passage provided on the upper surface 20 a side of the orifice plate 20.
  • the downstream end of the turning passage 21a is connected to communicate with the turning chamber 22a
  • the downstream end of the turning passage 21b is connected to communicate with the turning chamber 22b
  • the downstream end of the turning passage 21c is connected to the turning chamber 22c.
  • the downstream end of the turning passage 21d is connected to communicate with the turning chamber 22d.
  • the turning passages 21a, 21b, 21c, and 21d are fuel passages that supply fuel to the turning chambers 22a, 22b, 22c, and 22d, respectively. In this sense, the turning passages 21a, 21b, 21c, and 21d are turned into the turning fuel supply passage 21a. , 21b, 21c, 21d.
  • the wall surfaces of the swirl chambers 22a, 22b, 22c, and 22d are formed so that the curvature gradually increases from the upstream side toward the downstream side (so that the radius of curvature gradually decreases). At this time, the curvature may be continuously increased, or may be gradually increased from the upstream side toward the downstream side while keeping the curvature constant within a predetermined range.
  • the curve in which the curvature continuously increases from the upstream side to the downstream side there are an involute curve (shape) or a spiral curve (shape) and a curve based on the design method of the centrifugal fan.
  • shape shape
  • shape shape
  • curve based on the design method of the centrifugal fan the spiral curve is described, but the description can be similarly made even if the above curve is adopted assuming that the curvature gradually increases from the upstream side toward the downstream side.
  • FIG. 4 is an enlarged plan view showing the relationship between the protrusion 25a provided on the bottom 21ab of the turning passage 21a, the turning chamber 22a, and the fuel injection hole 23a.
  • FIG. 5 is a cross-sectional view in the B direction of FIG. 4 and is a view for explaining the height h direction of the protrusion 25a.
  • One swirl passage 21a is opened in a tangential direction of the swirl chamber 22a, and a fuel injection hole 23a is opened at the vortex center of the swirl chamber 22a.
  • the inner peripheral wall of the swirl chamber 22a is formed so as to draw a spiral curve on a plane (cross section) perpendicular to the valve shaft center line, and the swirl chamber 22a composed of the spiral curve is formed.
  • the characteristic configuration is briefly described below.
  • extension line (tangent line) of the inner wall surface of the swirl chamber 22a and the extension line of one side wall surface 21as of the swirl passage 21a are designed not to intersect on the swirl chamber 22a side.
  • a thickness forming portion 24a is provided between the end of the inner wall surface of the swirl chamber 22a and the side wall surface 21as of the swirl passage 21a.
  • the thickness forming portion 24a is a thickness portion necessary for processing.
  • the starting point of the spiral curve (which can be said to be the end point in this embodiment) coincides with the center of the fuel injection hole 23a.
  • the vortex center of the flow along the spiral wall surface coincides with the center of the fuel injection hole 23a.
  • the inner peripheral wall of the swirl chamber 22a is designed by the equal differential spiral equations (1) and (2).
  • the center o of the reference circle X when drawing the equal helix, the center o when forming the swirl chamber 22a, and the center o of the fuel injection hole 23a are located.
  • R D / 2 ⁇ (1 ⁇ a ⁇ ⁇ )
  • a Wk / (D / 2) / (2 ⁇ )
  • R is the distance from the center o when the swirl chamber 22a is formed to the inner peripheral wall of the swirl chamber
  • D is the diameter of the reference circle X when drawing the equidistant spiral
  • Wk is swirled with the end point E of the swirl chamber 22a. This is the distance of the starting point S of the chamber 22a.
  • the swirling passage 21a shows a passage width W and a height H for allowing the passage of fuel.
  • the reference circular diameter which is a reference for the diameter of the fuel injection hole 23a and the size of the swirling chamber 22a is as follows. A value close to the required specification is selected from various data obtained experimentally in advance. That is, it is selected according to the flow rate and spray angle required for the fuel injection valve.
  • FIG. 9 is a partially enlarged view for explaining the flow of the swirl passage 21a and swirl chamber 22a in the orifice plate 20.
  • FIG. FIG. 10 is a cross-sectional view in the direction D of FIG. 9, and is a view for explaining a characteristic portion of the flow in the length direction of the turning passage 21a.
  • FIG. 11 is a cross-sectional view in the E direction of FIG. 9 and is a view for explaining a characteristic portion of the flow in the height direction of the turning passage 21a and the turning chamber 22a.
  • the flow 30b swirling at the inlet side of the turning chamber 22a is more likely to flow into the fuel injection hole 23a and has a higher speed than the 21at side. It is formed on the side wall 21as side of the use passage 21a. On the other hand, a flow 31c having a lower speed than the side wall 21as side is formed on the side wall 21at side.
  • the inflow opening 20 b is a substantially semicircular gap formed between the opening of the fuel introduction hole 5 and the orifice plate 20.
  • the flow 30a colliding with the bottom surface 21ab of the turning passage 21a becomes a flow 30e with reduced speed while proceeding in the longitudinal direction, but the flow toward the height direction of the turning chamber 22a is weak enough. The turning effect cannot be obtained.
  • the flow 30f toward the lower side of the turning passage 21a is induced by the flow 30e, and as a result, forms a dead water area 30i.
  • the flow at the entrance of the swirl chamber 22a flows along the bottom surface 21ab of the swirl passage 21a as indicated by an arrow 30g and flows into the thickness portion 24a side of the swirl chamber 22a. For this reason, it strongly interferes with the flow 30d (see FIG. 9) on the fuel injection hole 23a side. Due to the influence of the interference, a flow 30h with a large velocity is formed at the inlet of the fuel injection hole 23a, thereby hindering flow symmetry (uniform swirl flow). Therefore, as shown in FIG. 12, the spray from the fuel injection hole 23a is asymmetric.
  • the projections 25a, 25b, 25c, and 25d according to one embodiment of the present invention suppress such a steep flow and rectify the flow at the inlet of the swirl chamber 22a in the height direction.
  • the protrusion 25a is provided in the entire region in the width W direction of the turning passage 21a. Further, the length b in the longitudinal direction is set to 1/3 or less of the length L of the turning passage 21a.
  • the height h of the protrusion 25a is 1/6 or less with respect to the height H of the turning passage 21a.
  • the protrusion 25a is formed so as to be located on the downstream side of the turning passage 21a (the inlet side of the turning chamber 22a). That is, the protrusion 25a is formed on the upstream side of the downstream end of the turning passage 21a and in the vicinity of the downstream end.
  • the fuel flowing in from the inflow opening 20a flows from the bottom surface 21ab of the swirl passage 21a toward the upper surface of the swirl chamber 22a as shown in FIGS. 14 and 15, and in the height direction of the swirl chamber 22a. Since the current is rectified (41a, 41b), sufficient swirl is imparted in the swirl chamber 22a to reach the fuel injection hole 23a. Accordingly, the swirl flow can be made symmetric at the outlet of the fuel injection hole 23a. Therefore, as shown in FIG. 13, the symmetry of the spray from the fuel injection hole 23a is improved.
  • FIG. 6 is a partially enlarged plan view of the turning passage portion in the orifice plate according to the present invention, as in FIG.
  • the difference from the orifice plate 20 according to the first embodiment is that the protruding portion 26a is partially formed in the width direction of the turning passage 21a.
  • the length in the width direction of the protrusion 26a is set to 1/3 or less of the width W of the turning passage 21a.
  • the characteristic part of the present embodiment is that the protruding portion 26a is provided on the side wall 21as side of the turning passage 21a. With such a configuration, the fuel passing through the portion without the protruding portion 26a turns. It is guided to the inner peripheral wall surface of the chamber 22a and is effectively turned.
  • the fuel passing through the protruding portion 26a flows from the bottom surface 21ab of the turning passage 21a toward the top surface of the turning chamber 22a and is rectified in the height direction of the turning chamber 22a, as in the first embodiment. Therefore, a sufficient swirl is provided in the swirl chamber 22a. Therefore, as shown in FIG. 13, the symmetry of the spray from the fuel injection hole 23a is improved.
  • the protrusion 26a is formed so as to protrude from the side wall 21as of the turning passage 21a toward the center in the width direction of the turning passage 21a.
  • FIG. 8 is a longitudinal sectional view showing the vicinity of the nozzle body in the fuel injection valve.
  • the difference from the first embodiment is that the nozzle body 52 is provided with a fuel inflow opening 55a from the valve shaft direction. is there.
  • the nozzle body 52 includes a valve seat surface 53 in contact with the valve body 6, a fuel injection chamber 54 that allows passage of fuel flowing through the gap between the valve body 6 and the valve seat surface 53, and a plurality of nozzle bodies 52 downstream of the fuel injection chamber 54.
  • the orifice plate 20 having the fuel injection holes 23a, 23b, 23c, and 23d (similar to the first embodiment) is provided.
  • the fuel reaches the turning passage 21a and the turning chamber 22a of the orifice plate 20 from the fuel injection chamber 54 through the inflow opening 55a inclined with respect to the valve shaft center.
  • the fuel flowing in from the inflow opening 55a flows from the bottom surface 21ab of the swirl passage 21a toward the top surface of the swirl chamber 22a and is rectified in the height direction of the swirl chamber 22a. It is given and reaches the fuel injection hole 23a. Accordingly, as shown in FIG. 13, as in the first embodiment, the symmetry of the spray from the fuel injection hole 23a is improved.
  • the inflow opening 55a is provided in the nozzle body 52 instead of the fuel introduction hole 5 of the first embodiment, the volume of the fuel injection chamber 54 can be made very small. Therefore, the injection control can be performed with higher accuracy.
  • the nozzle body 2 and the nozzle body 52 and the orifice plate 20 are not illustrated, but are configured so that the positioning of both is performed easily and easily using a jig or the like. Therefore, the dimensional accuracy when combined is improved.
  • the orifice plate 20 is manufactured by press molding (plastic processing) advantageous for mass productivity.
  • press molding plastic processing
  • a method with high processing accuracy that is relatively free of stress such as electric discharge machining, electroforming, and etching may be considered.
  • the flow direction is switched from the bottom surface portion of the turning passage to the upper surface direction of the passage by the protruding portion provided in the turning passage that can restrict the flow.
  • the flow is rectified in the cross section (width direction, height direction) of the turning passage.
  • the variation in the flow velocity of the fuel flow in the height direction (the flow velocity on the upper surface side becomes slower than the flow velocity on the bottom surface side) is improved, and the flow velocity of the fuel flow is uniform in the height direction. It becomes.
  • the swirl chamber is guided to the inner wall surface of the swirl chamber and has a sufficient swirl.
  • a uniform swirl flow is formed at the inlet portion of the fuel injection hole arranged at the vortex center of the swirl flow, and the thinning of the fuel is promoted.
  • SYMBOLS 1 Fuel injection valve, 2,52 ... Nozzle body, 3 ... Valve seat surface, 4 ... Fuel injection chamber, 5 ... Fuel introduction hole, 10 ... Yoke, 11 ... Coil, 20 ... Orifice plate, 21a, 21b, 21c, 21d ... turning passage, 22a, 22b, 22c, 22d ... turning chamber, 23a, 23b, 23c, 23d ... fuel injection hole, 24a, 24b, 24c, 24d ... thickness forming part, 25a, 25b, 25c, 25d, 26a ...protrusion.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
PCT/JP2013/078450 2013-03-08 2013-10-21 燃料噴射弁 Ceased WO2014136309A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201380044026.XA CN104583578B (zh) 2013-03-08 2013-10-21 燃料喷射阀
IN1032DEN2015 IN2015DN01032A (enrdf_load_stackoverflow) 2013-03-08 2013-10-21

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Application Number Priority Date Filing Date Title
JP2013046086A JP5887291B2 (ja) 2013-03-08 2013-03-08 燃料噴射弁
JP2013-046086 2013-03-08

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JP (1) JP5887291B2 (enrdf_load_stackoverflow)
CN (1) CN104583578B (enrdf_load_stackoverflow)
IN (1) IN2015DN01032A (enrdf_load_stackoverflow)
WO (1) WO2014136309A1 (enrdf_load_stackoverflow)

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JP6594713B2 (ja) * 2015-09-15 2019-10-23 日立オートモティブシステムズ株式会社 燃料噴射弁
JP7020542B2 (ja) * 2018-03-26 2022-02-16 新東工業株式会社 ショット処理装置
JP2019183848A (ja) * 2019-06-27 2019-10-24 日立オートモティブシステムズ株式会社 燃料噴射弁
KR102764374B1 (ko) 2020-12-18 2025-02-07 한화에어로스페이스 주식회사 연료 공급 장치

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JP2002332935A (ja) * 2001-05-08 2002-11-22 Hitachi Ltd 燃料噴射弁および内燃機関
JP2004340121A (ja) * 2003-04-25 2004-12-02 Toyota Motor Corp 燃料噴射弁
JP2011196328A (ja) * 2010-03-23 2011-10-06 Hitachi Automotive Systems Ltd 燃料噴射弁
JP2013024176A (ja) * 2011-07-25 2013-02-04 Hitachi Automotive Systems Ltd 燃料噴射弁

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WO1996030644A1 (de) * 1995-03-29 1996-10-03 Robert Bosch Gmbh Lochscheibe, inbesondere für einspritzventile und verfahren zur herstellung einer lochscheibe
DE19637103A1 (de) * 1996-09-12 1998-03-19 Bosch Gmbh Robert Ventil, insbesondere Brennstoffeinspritzventil
DE19703200A1 (de) * 1997-01-30 1998-08-06 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10118276A1 (de) * 2001-04-12 2002-10-17 Bosch Gmbh Robert Brennstoffeinspritzventil
JP3715253B2 (ja) * 2002-05-17 2005-11-09 株式会社ケーヒン 燃料噴射弁
JP4218696B2 (ja) * 2006-05-19 2009-02-04 トヨタ自動車株式会社 燃料噴射ノズル
JP2009162239A (ja) * 2009-04-27 2009-07-23 Nippon Soken Inc 燃料噴射弁および内燃機関

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002332935A (ja) * 2001-05-08 2002-11-22 Hitachi Ltd 燃料噴射弁および内燃機関
JP2004340121A (ja) * 2003-04-25 2004-12-02 Toyota Motor Corp 燃料噴射弁
JP2011196328A (ja) * 2010-03-23 2011-10-06 Hitachi Automotive Systems Ltd 燃料噴射弁
JP2013024176A (ja) * 2011-07-25 2013-02-04 Hitachi Automotive Systems Ltd 燃料噴射弁

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Publication number Publication date
JP5887291B2 (ja) 2016-03-16
IN2015DN01032A (enrdf_load_stackoverflow) 2015-06-26
CN104583578B (zh) 2017-06-13
JP2014173476A (ja) 2014-09-22
CN104583578A (zh) 2015-04-29

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