EP1509693B1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne Download PDF

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Publication number
EP1509693B1
EP1509693B1 EP03740006A EP03740006A EP1509693B1 EP 1509693 B1 EP1509693 B1 EP 1509693B1 EP 03740006 A EP03740006 A EP 03740006A EP 03740006 A EP03740006 A EP 03740006A EP 1509693 B1 EP1509693 B1 EP 1509693B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve seat
fuel injection
annular groove
valve needle
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.)
Expired - Lifetime
Application number
EP03740006A
Other languages
German (de)
English (en)
Other versions
EP1509693A1 (fr
Inventor
Wilhelm Christ
Bernd Dittus
Friedrich Boecking
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Priority claimed from DE10318989A external-priority patent/DE10318989A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1509693A1 publication Critical patent/EP1509693A1/fr
Application granted granted Critical
Publication of EP1509693B1 publication Critical patent/EP1509693B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M61/1866—Valve seats or member ends having multiple cones
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known from WO 96/19661.
  • a valve needle is arranged longitudinally displaceably in a bore, wherein the bore is arranged a conical valve seat at the combustion chamber end.
  • the valve needle is guided in a portion facing away from the combustion chamber in the bore, and between the combustion chamber facing portion of the valve needle and the wall of the bore, a pressure chamber is formed which can be filled with fuel under high pressure.
  • the pressure chamber in this case extends to the valve seat, which is conical and in which at least one injection opening is formed.
  • the valve needle At the end facing the valve seat, the valve needle has a substantially conical valve sealing surface, so that fuel can flow from the pressure space between the valve seat and the valve sealing surface through the injection openings when the valve sealing surface is lifted from the valve seat.
  • the valve needle is acted upon by a closing force which presses the valve sealing surface against the valve seat and thus prevents injection of fuel through the injection openings in the absence of further forces.
  • a first conical surface is formed whose opening angle is smaller than the opening angle of the conical valve seat.
  • another conical surface on the valve sealing surface formed, whose opening angle is greater than the opening angle of the valve seat.
  • annular groove is formed, which extends in a radial plane of the valve needle and adjacent to both conical surfaces.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the wear on the valve seat is reduced.
  • a part of the valve sealing surface is acted upon by a hydraulic force in the closed position of the valve needle, so that the total force is reduced to the valve needle in its closed position.
  • the valve needle is hydraulically connected to the pressure chamber, so that in this annular groove always the same fuel pressure prevails as in the pressure chamber.
  • the annular groove is connected to the pressure chamber through at least one connecting bore extending in the valve needle.
  • connection bores can be easily introduced into the valve needle by various methods, preferably before the hardening of the valve needle.
  • Another advantage is that the other outer shape of the valve needle and its mechanical stability remain virtually unchanged.
  • the design of the connecting bores as transverse bores is advantageous for the drilling method, since the angle to the surfaces at which the transverse bore emerges is greater.
  • the diameter of the transverse bore can be increased up to the width of the annular groove.
  • the hydraulic connection of the annular groove with the pressure chamber is produced by at least one recess formed in the first cone surface. Such recesses are easy from the outside into the valve needle, even after the hardening process.
  • the seat angle difference between the second conical surface and the valve seat is smaller than the seat angle difference between the first conical surface and the valve seat.
  • the sealing edge formed at the transition of the annular groove to the second cone surface first comes into contact with the valve seat.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention.
  • a bore 3 is formed, which is closed at its combustion chamber end by a conical valve seat 11.
  • the valve seat 11 is followed downstream by a blind bore 21, depart from the injection openings 9, which connect the blind bore with the combustion chamber of the internal combustion engine.
  • a piston-shaped valve needle 5 is arranged longitudinally displaceably, which is sealingly guided in a guide portion 103 of the bore 3 with a guide portion 105. Starting from the guide portion 105 of the valve needle 5, the valve needle 5 tapers the valve seat 11 to form a pressure shoulder 13 and passes into a shaft 205 having a smaller diameter than the guide portion 105.
  • the combustion chamber end of the valve needle 5, directly to the Shank 205 borders, is formed by a substantially conical valve sealing surface 7, which cooperates with the valve seat 11 and whose exact shape and function will be explained below.
  • an annular-channel-shaped pressure chamber 19 is formed, which is radially expanded at the level of the pressure shoulder 13.
  • the pressure chamber 19 can be filled with fuel under high pressure via an inlet channel 25 extending in the valve body 1, the inlet channel 25 opening into the radial extension of the pressure chamber 19.
  • the valve needle 5 is acted upon at its end remote from the combustion chamber by a closing force, which is generated by a device, not shown in the drawing.
  • a closing force which is generated by a device, not shown in the drawing.
  • devices are known which generate the closing force with the aid of spring elements and devices which generate the closing force hydraulically.
  • the valve needle 5 is pressed with the valve sealing surface 7 against the valve seat 11, so that the injection openings 9, which are formed in the valve seat 11 and connect the valve seat 11 to the combustion chamber of the internal combustion engine, are separated from the pressure chamber 19.
  • a high fuel pressure which can be between 100 and 200 MPa depending on the system used.
  • either the pressure in the pressure chamber 19 can be increased or the closing force on the valve needle 5 can be lowered. In any case, it must be achieved that the hydraulic forces on the pressure shoulder 13 and on parts of the valve sealing surface 7 are greater than the closing force on the valve needle 5. If this is the case, the valve needle 5 moves away from the valve seat 11, so that Fuel from the pressure chamber 19 between the valve sealing surface 7 and the valve seat 11 can flow through to the injection openings 9. By increasing the closing force or an interruption of the fuel supply into the pressure chamber 19, the force relationships on the valve needle 5 return, so that the valve needle 5 moves back to its closed position until it comes to rest with the valve sealing surface 7 on the valve seat 11.
  • FIG. 2 shows an enlargement of FIG. 1 in the region of the section denoted by II, ie in the region of the valve seat 11.
  • the valve sealing surface 7 of the valve needle 5 has a first conical surface 30, which borders directly on the shaft 205.
  • the first conical surface 30 points in this case an opening angle which is smaller than the opening angle of the conical valve seat 11, so that between the first conical surface 30 and the valve seat 11, a difference angle ⁇ 1 is formed.
  • Downstream of the fuel flow to the injection openings 9 adjoins the first conical surface 30 an annular groove 35 which surrounds the valve needle 5 on its entire circumference and extends in a radial plane of the longitudinal axis 15 of the valve needle 5.
  • a second conical surface 32 connects, which also forms the end of the valve needle 5.
  • the opening angle of the second conical surface 32 is greater than the opening angle of the valve seat 11, so that a differential angle ⁇ 2 is formed between these two surfaces.
  • the two conical surfaces 30, 32 and the annular groove 35 are arranged on the valve sealing surface 7 such that the circular section line of the imaginary extension of the first conical surface 30 and the second conical surface 32 is at the level of the annular groove 35.
  • the annular groove 35 is introduced at the end of the production process of the valve needle 5 in the valve sealing surface 7, this ensures that the upper edge 37 of the annular groove 35, which forms the boundary line to the first conical surface 30, and the sealing edge 38, which forms the boundary line second cone surface 32 forms exactly in a radial plane of the longitudinal axis 15.
  • the annular groove 35 is connected to the pressure chamber 19.
  • the connecting bores 40 are in this case preferably distributed uniformly over the circumference of the valve needle 5. It is thus ensured that, regardless of the position of the valve needle 5 to the valve seat 11, the annular groove 35 at least substantially always has the same fuel pressure as the pressure chamber 19th
  • valve needle 5 Due to the opening angle of the first conical surface 30, the second conical surface 32, the valve seat 11 and the annular groove 35, the valve needle 5 is at its combustion chamber side End formed such that during the closing movement of the valve needle 5 first the sealing edge 38 on the valve seat 11 comes to Anlange and only in the course of further closing the downstream boundary edge of the annular groove 35.
  • the valve needle 5 is drawn in exactly this position, ie in the moment in which the sealing edge 38 comes to the valve seat 11 to Anlange. Without elastic deformation of the valve needle 5 and the valve seat 11, the valve needle 5 would remain in this position. However, since acts on the valve needle 5, a high closing force, both the valve sealing surface 7 of the valve needle 5 and the valve seat 11 deformed.
  • FIG. 4 shows a further exemplary embodiment of the fuel injection valve according to the invention, wherein the same section as in FIG. 2 is selected.
  • the connecting bores 40 instead of the connecting bores 40, at least two connecting grooves 42 are formed on the first conical surface 30, by means of which the annular groove 35 remains hydraulically connected to the pressure chamber 19.
  • the connecting grooves 42 are in this case preferably distributed uniformly over the circumference of the valve needle 5 and have a depth of a few 1/10 mm.
  • FIG. 5 shows a further embodiment in which the annular groove 35, as in the embodiment shown in Figures 2 and 3, is connected via a connecting bore with the pressure chamber, however, the connecting hole is formed here as a transverse bore 44.
  • the transverse bore 44 extends from the annular groove 35 and leads transversely through the valve needle 5 to the shaft 205.
  • Such a transverse bore 44 can be made simpler than a connecting bore 40, as shown in FIG. 2, since here a large angle to the surface of the valve needle 5 is present at both ends of the transverse bore 44.
  • FIG. 6 shows a cross section through the injection valve shown in FIG. 5 along the line VI-VI.
  • the annular groove 35 is connected via a plurality of transverse bores 44 with the pressure chamber, wherein the transverse bores 44 in the projection on the plane indicated by the line VI-VI level in Figure 5 are parallel to each other.
  • the transverse bores 44 are aligned such that the end of the transverse bore 44 emerging from the shaft 205 is as far as possible opposite the end in the annular groove 35 without the transverse bores 44 intersecting.
  • the diameter of the transverse bore 44 may in this case correspond to the width of the annular groove 35 or also have a smaller diameter.
  • valve needle 5 In modern fuel injection systems, as they are used in particular for self-igniting internal combustion engines in high-speed engines, great demands are placed on efficiency and pollutant emissions today. This requires on the one hand that it is injected with a very high pressure, which can be up to 200 MPa in modern fuel injection systems. On the other hand, very short switching times of the valve needle 5 are necessary in order to enable rapidly successive injections, in particular in order to realize a pre-injection and a post-injection within one injection cycle.
  • a typical fuel injection valve for passenger cars, which is at a pressure of, for example 150 MPa, has a needle diameter in the guide portion 105 of about 4 mm. When lifted from the valve seat 11 valve needle 5 thus results in a force of about 1900 N on the open valve needle 5.
  • this force must be compensated by a closing force, which is significantly higher than 1900 N is to allow rapid closing of the valve needle 5.
  • a closing force which is significantly higher than 1900 N is to allow rapid closing of the valve needle 5.
  • the closing force must have a certain minimum value so that the valve needle 5 always remains closed even with a correspondingly high pressure in the combustion chamber between the individual injections.
  • the fuel injection valve according to the invention solves this problem by an additional annular groove in the valve sealing surface 7 is exposed to the pressure in the pressure chamber 19, so that the resultant force is reduced to the valve needle 5.

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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

L'invention concerne une soupape d'injection de carburant, comprenant un corps de soupape (1) dans lequel un pointeau de soupape (5) ayant un axe longitudinal (15) peut être déplacé longitudinalement dans un alésage (3). A l'extrémité de l'alésage (3), du côté de la chambre de combustion, se trouve un siège de soupape conique (11), une chambre de pression (19) pouvant être remplie de carburant et allant jusqu'au siège de soupape (11) étant ménagée entre le pointeau de soupape (5) et la paroi de l'alésage (3). Sur le pointeau de soupape (5) est réalisée une surface d'étanchéité de soupape (7) qui concourt avec le siège de soupape (11) pour la commande d'au moins un orifice d'injection partant du siège de soupape (11) et dans laquelle est réalisée une rainure annulaire (35) s'étendant dans un plan radial du pointeau de soupape (5). L'arête aval de la rainure annulaire (35) est réalisée sous forme d'arête d'étanchéité (38) et est toujours reliée hydrauliquement à la chambre de pression (19).

Claims (9)

  1. Injecteur de carburant pour moteurs à combustion interne, comprenant un corps de soupape (1) dans lequel une aiguille de soupape (5) d'un axe longitudinal (15) est mobile le long d'un alésage (3), un siège de soupape conique (11) à l'extrémité de l'alésage (3) située du côté de la chambre de combustion, et une chambre de pression (19) pouvant être remplie de carburant entre une partie de l'aiguille de soupape (5) et la paroi de l'alésage (3) et qui s'étend jusqu'au siège de soupape (11), l'injecteur comprenant également une surface d'étanchéité de soupape (7) formée sur l'aiguille de soupape (5) et qui, en coopérant avec le siège de soupape (11) pour commander au moins un orifice d'injection partant du siège de soupape (11), comporte une rainure annulaire (35) dont les bords aval servent d'arête d'étanchéité (38) s'étendant dans le plan radial de l'aiguille de soupape (5),
    la rainure annulaire (35) étant en liaison hydraulique constante avec la chambre de pression (19) alors que la surface d'étanchéité de soupape (7) comprend une première surface conique (30) et une deuxième surface conique (32) en aval de la première, entre lesquelles s'étend la rainure annulaire (35),
    caractérisé en ce que
    l'angle d'ouverture de la première surface conique (30) est inférieur à l'angle d'ouverture du siège de soupape conique (11) et l'angle d'ouverture de la deuxième surface conique (32) est supérieur à celui-ci.
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la rainure annulaire (35) est adjacente à la première surface conique (30) et à la deuxième surface conique (32).
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la différence d'angle (δ2) entre la deuxième surface conique (32) et le siège de soupape (11) est inférieure à la différence d'angle (δ1) entre la première surface conique (30) et le siège de soupape (11).
  4. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la deuxième surface conique (32) vient d'abord en appui contre le siège de soupape (11) lors du mouvement de fermeture de l'aiguille de soupape (5) sur le siège de soupape (11), et ce n'est qu'après déformation de l'aiguille de soupape (5) et/ou du corps de soupape (11) que la première surface conique (30) vient aussi en appui.
  5. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la liaison hydraulique entre la rainure annulaire (35) et la chambre de pression (19) est réalisée par au moins un alésage de liaison (40) pratiqué dans l'aiguille de soupape (5).
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    l'alésage de liaison (40) est un alésage transversal (44).
  7. Injecteur de carburant selon la revendication 5 ou 6,
    caractérisé en ce que
    l'alésage de liaison (40) relie la rainure annulaire (35) avec la tige (205) de l'aiguille de soupape (5).
  8. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la liaison hydraulique entre la rainure annulaire (35) et la chambre de pression (19) est réalisée par au moins un évidement formé dans la première surface conique (30).
  9. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    lors du mouvement de fermeture de l'aiguille de soupape (5), l'arête d'étanchéité (38) formée sur la périphérie de la rainure annulaire (35) en direction de la deuxième surface conique (32) vient d'abord en appui contre le siège de soupape (11).
EP03740006A 2002-05-18 2003-05-15 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP1509693B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10222209 2002-05-18
DE10222209 2002-05-18
DE10318989A DE10318989A1 (de) 2002-05-18 2003-04-25 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10318989 2003-04-25
PCT/DE2003/001579 WO2003098031A1 (fr) 2002-05-18 2003-05-15 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1509693A1 EP1509693A1 (fr) 2005-03-02
EP1509693B1 true EP1509693B1 (fr) 2006-11-29

Family

ID=29550935

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03740006A Expired - Lifetime EP1509693B1 (fr) 2002-05-18 2003-05-15 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US7100847B2 (fr)
EP (1) EP1509693B1 (fr)
JP (1) JP2005526212A (fr)
DE (1) DE50305850D1 (fr)
WO (1) WO2003098031A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10245573A1 (de) * 2002-09-27 2004-04-08 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102005025135A1 (de) * 2005-06-01 2006-12-07 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
US7360722B2 (en) 2005-08-25 2008-04-22 Caterpillar Inc. Fuel injector with grooved check member
US7578450B2 (en) 2005-08-25 2009-08-25 Caterpillar Inc. Fuel injector with grooved check member
DE102006052817A1 (de) * 2006-11-09 2008-05-15 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102008031271B4 (de) * 2008-07-02 2011-07-28 Continental Automotive GmbH, 30165 Düsenbaugruppe für ein Einspritzventil
JP2010053796A (ja) * 2008-08-29 2010-03-11 Hitachi Ltd 燃料噴射弁
US8602319B2 (en) 2010-10-07 2013-12-10 Caterpillar Inc. Needle valve member with frustoconical guide segment and fuel injector using same
IT1403006B1 (it) * 2010-12-06 2013-09-27 O M T Ohg Torino S P A Polverizzatore ad elevata vita operativa per iniettori meccanici ad alta pressione operanti con combustibile pesante
EP3006735B1 (fr) * 2014-10-10 2017-08-30 Siemens Aktiengesellschaft Dispositif sous-marin pour fournir un fluide sous pression
JP6354519B2 (ja) * 2014-10-23 2018-07-11 株式会社デンソー 燃料噴射弁
WO2016121475A1 (fr) * 2015-01-30 2016-08-04 日立オートモティブシステムズ株式会社 Robinet d'injection de carburant
KR101986973B1 (ko) * 2019-03-07 2019-06-07 이수철 이중 접촉면을 가지는 연료분사밸브
DE102019210551A1 (de) * 2019-07-17 2021-01-21 Robert Bosch Gmbh Kraftstoffinjektor

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
GB702797A (en) * 1950-11-13 1954-01-20 Rudolf L Orange Improvements in or relating to fuel-injection nozzles for internal combustion engines
JPS61118556A (ja) * 1984-11-14 1986-06-05 Toyota Central Res & Dev Lab Inc 間欠式渦巻噴射弁
DE3624476A1 (de) * 1986-07-19 1988-01-28 Bosch Gmbh Robert Einspritzventil
DE3719459A1 (de) * 1987-06-11 1988-12-29 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
US4974565A (en) * 1988-02-26 1990-12-04 Toyota Jidosha Kabushiki Kaisha Fuel swirl generation type fuel injection valve and direct fuel injection type spark ignition internal combustion engine mounted with the fuel injection valve
JP3144136B2 (ja) * 1993-03-31 2001-03-12 株式会社デンソー 三方電磁弁
JP4221898B2 (ja) * 2000-02-29 2009-02-12 株式会社デンソー 燃料噴射ノズル
IT1319988B1 (it) * 2000-03-21 2003-11-12 Fiat Ricerche Spina di chiusura di un ugello in un iniettore di combustibile permotori a combustione interna.

Also Published As

Publication number Publication date
US20050178860A1 (en) 2005-08-18
EP1509693A1 (fr) 2005-03-02
WO2003098031A1 (fr) 2003-11-27
DE50305850D1 (de) 2007-01-11
US7100847B2 (en) 2006-09-05
JP2005526212A (ja) 2005-09-02

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