WO2008046679A1 - injecteur d'injection de carburant - Google Patents

injecteur d'injection de carburant Download PDF

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Publication number
WO2008046679A1
WO2008046679A1 PCT/EP2007/058470 EP2007058470W WO2008046679A1 WO 2008046679 A1 WO2008046679 A1 WO 2008046679A1 EP 2007058470 W EP2007058470 W EP 2007058470W WO 2008046679 A1 WO2008046679 A1 WO 2008046679A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve piston
valve
seat
injector
pressure
Prior art date
Application number
PCT/EP2007/058470
Other languages
German (de)
English (en)
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
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
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to AT07788444T priority Critical patent/ATE491091T1/de
Priority to CN2007800388424A priority patent/CN101529078B/zh
Priority to DE502007005914T priority patent/DE502007005914D1/de
Priority to EP07788444A priority patent/EP2079922B1/fr
Publication of WO2008046679A1 publication Critical patent/WO2008046679A1/fr

Links

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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • Hubête high-pressure accumulator systems common rail systems
  • the injection pressure can be adapted to the load and speed.
  • the injection valve member is controlled via a servo control chamber.
  • the pressure in the control room is controlled by a solenoid valve with a spherical closing element.
  • a solenoid valve with a spherical closing element.
  • This is not pressure balanced and requires high spring forces, high magnetic switching forces and a lot of space.
  • the control with the ball solenoid valve has severe limitations in the multiple injection. Very short distances between injections can not be realized.
  • Pressure compensated control valves as are known in the art, have a high pressure-tight guide and a linear sealing seat, which corresponds to the guide diameter. As a result, the valve is pressure balanced in the static state.
  • An inventively designed injector for injecting fuel into a combustion chamber of an internal combustion engine comprises an injector housing, in which a control valve for controlling an injection valve member which releases or closes at least one injection opening is received.
  • the control valve comprises a valve piston, by means of which a connection from a control chamber to a low-pressure region can be opened or closed.
  • the valve piston comprises a substantially annular seat, which can be adjusted in a flat seat.
  • the control valve is designed to be pressure balanced.
  • a pressure-balanced control valve In a pressure-balanced control valve, no or only very small pressure surfaces are present on the high-pressure side outside the seat.
  • the valve piston is guided on the high pressure side in a valve guide.
  • the seat diameter of the seat, at which the high pressure is present, also corresponds approximately to the guide diameter.
  • essentially annular seating surface means that the seat surface can be annular, and it is also possible for the seating surface not to be exactly annular, for example, the seat surface may have small contours.
  • a shoulder is formed on the valve piston, which is arranged on the high pressure side of the valve piston such that the pressure force exerted by the fuel on the shoulder supports the closing movement of the valve piston.
  • annular sealing surface is that thereby the load on the sealing surface is reduced when needle closing and the stopper damping is increased. This improves the bouncing properties, i. that fewer or even no closing bounce occur, whereby the multiple injection capability is increased and the valve wear is reduced. Due to the sealing surface, an additional opening of the pressure force can occur, which however remains manageable with a pressure balanced valve piston with currently available magnetic actuators.
  • the seat surface is enclosed on the valve piston by a damping surface, wherein the damping surface and the seat surface form a step, so that the damping surface does not rest on the seat when the control valve is closed.
  • the damping surface optimizes the stop damping of the valve piston.
  • the damping surface can be realized in a simple manner in terms of manufacturing technology, since a reference surface for the distance dimension is present through the annular seat surface. Since the wear of the valve seat was minimized due to the seat, the damping surface over the life of the injector is stable to implement.
  • control valve of the inventively embodied injector is magnet-actuated.
  • control valve is actuated, for example with a piezoelectric actuator.
  • the high-pressure region on the control valve is connected via at least one throttle element to a high-pressure fuel line via which fuel under system pressure flows from a high-pressure accumulator to the injector.
  • the seat in which the annular seat is adjustable a flat seat. Due to the design of the valve seat as a flat seat, a two-part construction of the valve piston is possible. As a result, the guide of the valve piston and the annular seat can be manufactured in different components. This allows a good workability of the annular seating surfaces and thus a cost-effective production. If, instead of the flat seat, e.g. a conical seat is used, it is necessary to perform the annular seat and the guide of the valve piston on a component, since a liquid-tight closing of the control valve is only possible if the annular seat over the entire circumference of the conical seat. For this purpose, an exact guidance of the valve piston is required. In contrast, an axial displacement of the annular seat over a flat seat does not lead to a leakage in the closed control valve.
  • the flat seat e.g. a conical seat
  • valve piston is preferably formed integrally with an armature of the solenoid valve.
  • armature is received in an armature space which is decoupled from the return path of the amount of fuel used to control the injector.
  • the shoulder formed on the valve piston which is arranged on the high-pressure side of the valve piston such that the force exerted by the fuel on the shoulder pressure force supports the closing movement of the valve piston is that a hydraulic valve closing force is generated by the shoulder, which is the opening hydraulic forces of the compensated annular seat.
  • the control valve can be made with a larger sealing surface through the shoulder, whereby the damping properties of the sealing seat are improved and the wear is further reduced.
  • a hydraulic closing force is formed which prevents the valve from re-opening. This allows for optimized valve tuning and multiple injection capability.
  • a passage is formed in the valve piston, in which a pin is received, which is supported with its side facing away from the seat on the injector and the high pressure in the valve piston is guided. Through the pin, the valve piston can make pressure balanced.
  • the cross-sectional area of the shoulder is approximately 50% of the cross-sectional area of the annular seat surface.
  • the cross-sectional area of the passage is smaller than the cross-sectional area which is enclosed by the outer periphery of the annular seat surface of the valve piston.
  • the diameter of the guide is greater than or equal to the inner diameter of the seat and less than or equal to the outer diameter of the seat.
  • valve piston is guided in a guide, wherein for forming the shoulder on the valve piston, the cross-sectional area of the valve piston in the region of the guide is smaller than the cross-sectional area which is enclosed by the outer circumference of the seat surface.
  • the shoulder is formed on the outer circumference of the valve piston. So that the valve piston can be made almost pressure balanced, the cross-sectional area of the shoulder is about 50% of the cross-sectional area of the seat.
  • FIG. 1 shows a fuel injector designed according to the invention in a first embodiment
  • FIG. 2 shows a fuel injector designed according to the invention in a second embodiment.
  • FIG. 1 shows a fuel injector designed in accordance with the invention in a first embodiment.
  • a control valve 5 for actuating an injection valve member 7 is accommodated in an injector housing 9.
  • the injection valve member 7 releases at least one injection opening 11 or closes it.
  • the injection valve member 7 is enclosed by a nozzle chamber 13, which is connected via a high pressure line 15 to a fuel supply line 17.
  • the fuel supply line 17 connects a high-pressure accumulator 19 of a high-pressure accumulator injection system (common rail system) with the injector 1.
  • a control piston 21 adjoins the injection valve member 7. With a front face 23 facing away from the injection valve member 7, the control piston 21 delimits a control chamber 25.
  • the control piston 21 is guided in a piston guide 27, which is formed in a guide element 29.
  • the guide element 29 is closed by a pressure chamber 31, which is connected to the high-pressure accumulator 19 via the fuel supply line 17. Via a throttle element 33 of the pressure chamber 31 is connected to the control chamber 25.
  • fuel can flow out of the control chamber 25 into a fuel return 37 when the control valve 5 is open.
  • the fuel return 37 is connected to the low pressure region of the injection system.
  • the control valve 5 comprises a valve piston 39, on which an annular Wegfikiee 41 is formed.
  • the annular Wegfikiee 41 in a seat 43 can be adjusted.
  • the seat 43 is designed as a flat seat.
  • the seat 43 is formed as a conical seat or as a ball seat.
  • the annular seat 41 on the valve piston 39 is enclosed by a damping surface 45.
  • the damping surface 45 and the annular seat 41 thereby form a step 47, so that the Dämp Stahl Stahls constitutional unit 45 does not rest on the seat 43 when the control valve 5 is closed.
  • a passage 49 is formed, in which a pin 51 is received.
  • the pin 51 is supported by an end face 53 on the injector housing 9.
  • a shoulder 55 is formed in the passage 49 in the valve piston 39.
  • the diameter of the passage 49 is larger than the inner diameter of the annular seat 41.
  • the cross-sectional area of the passage is greater than the free cross-sectional area of the annular seat.
  • the cross-sectional area of the shoulder 55 is approximately 50% of the cross-sectional area of the annular seating surface 41.
  • the diameter of the passage 49 is less than or equal to the outside diameter of the annular seating surface 41, so that the cross-sectional area of the Feedthrough 49 is smaller than or equal to the cross-sectional area which is enclosed by the outer circumference of the annular seat surface 41 of the valve piston 39.
  • an armature 57 of the magnetic actuator is integrally formed on the valve piston 39.
  • On the side facing away from the annular seat 41 side of the armature 57 is opposite to a coil 59 of the magnetic actuator.
  • the coil 59 is received in a magnetic core 61 for amplifying the magnetic force.
  • the magnetic core 61 encloses a spring chamber 63, in which a spring element 65 is accommodated.
  • the spring element 65 is supported on one side against an end face 67 on the valve piston 39 and on the other side on the injector housing 9.
  • the spring element 65 encloses the pin 51.
  • the spring element 65 is preferably designed as a helical spring compression spring.
  • the control piston 21 is enclosed by an annular space 69.
  • a second spring element 71 is accommodated, which surrounds the control piston 21.
  • the second spring element 71 is preferably designed as a helical spring compression spring.
  • the second spring element 71 is supported on one side on the guide element 29 and on the other side on a ring 73 on the control piston 21.
  • the annular space 69 is connected via a channel 75 to the fuel return 37.
  • the coil 59 of the solenoid actuator is energized.
  • the armature 57 which is connected to the valve piston 39, from the coil 59th dressed.
  • the annular seat 41 rises from the seat 43 and releases the connection from the control chamber 25 into the fuel return 37.
  • the pressure in the control chamber 25 drops.
  • the injection valve member thus lifts out of its seat 79 and thus releases the at least one injection opening.
  • the energization of the coil 59 of the magnetic actuator is terminated.
  • the actuator 57 is not further attracted by the coil 59.
  • the spring element 65 of the valve piston 39 is provided with the annular seat 41 in its seat 43.
  • a pressure cushion is formed on the annular seat 41, which dampens the movement of the valve piston 39.
  • the movement of the valve piston 39 is damped by the damping surface 45, at which also forms a pressure pad.
  • the movement of the valve piston 39 is slowed down so shortly before the closing of the control valve 5. A striking of the annular seat 41 on the seat 43, which could lead to a rebounding of the valve piston 39 is thus avoided.
  • fuel flows into the control chamber 25.
  • the pressure in the control chamber 25 increases.
  • the control piston 21 is moved in the direction of the injection valve member 7.
  • the injection valve member 7 is thus placed in its seat 79 and closes the at least one injection opening eleventh
  • FIG. 2 shows a fuel injector designed according to the invention in a second embodiment.
  • the control piston 21 is surrounded by a pressure chamber 81. About free surfaces 83 on the injection valve member 7, the pressure chamber 81 is connected to the nozzle chamber 13. In the embodiment shown here, the control piston 21 and the injection valve member 7 are integrally formed.
  • the control piston 21 is enclosed by a sealing sleeve 85.
  • the sealing sleeve 85 delimits the control chamber 25 from the pressure chamber 81.
  • the sealing sleeve 85 is provided with a biting edge 87 against a valve member 89, wherein the valve member 89 limits the control chamber 25 on the control piston 21 opposite side.
  • the control chamber 25 is connected via the throttle element 33 to the pressure chamber 81.
  • the throttle element 33 is formed in the sealing sleeve 85.
  • a shoulder 93 is formed on the valve piston 39.
  • the shoulder 93 is formed by the outer diameter of the annular seat 41 being larger than the outer diameter of a guide section 95, with which the valve piston 39 is guided in a guide 97. 2
  • the cross-sectional area of the shoulder 93 is approximately 50% of the cross-sectional area of the annular seating surface 41.
  • the diameter of the guide section 97 is smaller for this purpose
  • the diameter of the guide section 195 is preferably greater than or equal to the inner diameter of the annular seat surface 41.
  • the armature 57 is received in an armature space 99 to make the switching dynamics of the control valve 5 independent of the return conditions from the valve space 91.
  • the armature chamber 99 is decoupled from the return from the valve chamber 91. This is achieved in that the armature space 99 is not connected to the valve chamber 91 but directly to the fuel return 37 via a duct 101.

Landscapes

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

Abstract

L'invention concerne un injecteur qui injecte du carburant dans la chambre de combustion (3) d'un moteur à combustion interne, qui présente un boîtier d'injecteur (9) dans lequel est logée une soupape-pilote (5) qui commande un organe (7) de soupape d'injection qui libère ou ferme au moins une ouverture d'injection (11), la soupape-pilote (5) comprenant un piston de soupape (39) qui permet de libérer ou de fermer une liaison entre une chambre-pilote (25) et un retour de carburant (37). Le piston de soupape (39) comprend une surface annulaire de soutien (41) qui peut être placée dans un siège (43). Un épaulement (55, 93) disposé sur le côté haute pression du piston de soupape (39) de telle sorte que la force de poussée exercée par le carburant sur l'épaulement (55; 93) soutienne le déplacement de fermeture du piston de soupape (39) est formé sur le piston de soupape (39).
PCT/EP2007/058470 2006-10-18 2007-08-15 injecteur d'injection de carburant WO2008046679A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AT07788444T ATE491091T1 (de) 2006-10-18 2007-08-15 Injektor zum einspritzen von kraftstoff
CN2007800388424A CN101529078B (zh) 2006-10-18 2007-08-15 用于喷射燃料的喷射器
DE502007005914T DE502007005914D1 (de) 2006-10-18 2007-08-15 Injektor zum einspritzen von kraftstoff
EP07788444A EP2079922B1 (fr) 2006-10-18 2007-08-15 Injecteur d'injection de carburant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006049050A DE102006049050A1 (de) 2006-10-18 2006-10-18 Injektor zum Einspritzen von Kraftstoff
DE102006049050.9 2006-10-18

Publications (1)

Publication Number Publication Date
WO2008046679A1 true WO2008046679A1 (fr) 2008-04-24

Family

ID=38717215

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/058470 WO2008046679A1 (fr) 2006-10-18 2007-08-15 injecteur d'injection de carburant

Country Status (5)

Country Link
EP (1) EP2079922B1 (fr)
CN (1) CN101529078B (fr)
AT (1) ATE491091T1 (fr)
DE (2) DE102006049050A1 (fr)
WO (1) WO2008046679A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009132879A2 (fr) * 2008-04-28 2009-11-05 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2011029829A1 (fr) * 2009-09-10 2011-03-17 Robert Bosch Gmbh Injecteur
WO2011051060A1 (fr) * 2009-10-26 2011-05-05 Robert Bosch Gmbh Dispositif d'injection de carburant
EP2333296A1 (fr) * 2009-12-10 2011-06-15 Delphi Technologies Holding S.à.r.l. Élément de soupape pour agencement de vanne de liquide

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007011685A1 (de) * 2007-03-09 2008-09-11 Robert Bosch Gmbh Kraftstoffinjektor mit verbessertem Steuerventil
DE102009045335A1 (de) 2009-10-05 2011-04-07 Robert Bosch Gmbh Injektor
DE102012104531A1 (de) * 2012-05-25 2013-10-24 L'orange Gmbh Ventilanordnung, insbesondere für Kraftstoff-Einspritzinjektoren
DE102012209841A1 (de) 2012-06-12 2013-12-12 Robert Bosch Gmbh Injektor für ein Fluid, insbesondere Kraftstoffinjektor
DE102012223166A1 (de) 2012-12-14 2014-06-18 Robert Bosch Gmbh Kraftstoffinjektor
DE102013212140A1 (de) 2013-06-25 2015-01-08 Robert Bosch Gmbh Steuerventil
GB201400650D0 (en) * 2014-01-15 2014-03-05 Delphi Tech Holding Sarl Bobbin with venting conduit
DE102015223168A1 (de) 2015-11-24 2017-05-24 Robert Bosch Gmbh Kraftstoffinjektor
CN110529316B (zh) * 2019-08-22 2020-11-03 一汽解放汽车有限公司 一种燃料喷射阀及发动机
CN114060193A (zh) * 2020-08-04 2022-02-18 温特图尔汽柴油公司 大型柴油机的燃料喷射阀以及大型柴油机

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19839572A1 (de) * 1997-11-03 1999-05-06 Caterpillar Inc Treibstoffeinspritzvorrichtung
DE19839581A1 (de) * 1997-11-04 1999-05-06 Lucas Ind Plc Treibstoffeinspritzvorrichtung
GB2336628A (en) * 1998-04-24 1999-10-27 Lucas Ind Plc A fuel injector, for an I.C. engine, having a three way two position needle control valve
EP1043497A2 (fr) * 1999-04-07 2000-10-11 Delphi Technologies, Inc. Soupape de commande
GB2350662A (en) * 1999-06-03 2000-12-06 Lucas Ind Plc Valve for a fuel injector
WO2002084106A1 (fr) * 2001-04-11 2002-10-24 Robert Bosch Gmbh Soupape pour commander le passage de fluides
EP1302653A1 (fr) * 2001-10-12 2003-04-16 C.R.F. Società Consortile per Azioni Améliorations pour un injecteur de carburant de moteur à combustion interne comprenant une soupape électromagnétique de dosage
WO2007128613A1 (fr) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Injecteur de carburant comportant une soupape de commande à compensation de pression

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10333696A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19839572A1 (de) * 1997-11-03 1999-05-06 Caterpillar Inc Treibstoffeinspritzvorrichtung
DE19839581A1 (de) * 1997-11-04 1999-05-06 Lucas Ind Plc Treibstoffeinspritzvorrichtung
GB2336628A (en) * 1998-04-24 1999-10-27 Lucas Ind Plc A fuel injector, for an I.C. engine, having a three way two position needle control valve
EP1043497A2 (fr) * 1999-04-07 2000-10-11 Delphi Technologies, Inc. Soupape de commande
GB2350662A (en) * 1999-06-03 2000-12-06 Lucas Ind Plc Valve for a fuel injector
WO2002084106A1 (fr) * 2001-04-11 2002-10-24 Robert Bosch Gmbh Soupape pour commander le passage de fluides
EP1302653A1 (fr) * 2001-10-12 2003-04-16 C.R.F. Società Consortile per Azioni Améliorations pour un injecteur de carburant de moteur à combustion interne comprenant une soupape électromagnétique de dosage
WO2007128613A1 (fr) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Injecteur de carburant comportant une soupape de commande à compensation de pression

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009132879A2 (fr) * 2008-04-28 2009-11-05 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2009132879A3 (fr) * 2008-04-28 2010-01-14 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2011029829A1 (fr) * 2009-09-10 2011-03-17 Robert Bosch Gmbh Injecteur
WO2011051060A1 (fr) * 2009-10-26 2011-05-05 Robert Bosch Gmbh Dispositif d'injection de carburant
CN102597484A (zh) * 2009-10-26 2012-07-18 罗伯特·博世有限公司 燃料喷射装置
EP2333296A1 (fr) * 2009-12-10 2011-06-15 Delphi Technologies Holding S.à.r.l. Élément de soupape pour agencement de vanne de liquide

Also Published As

Publication number Publication date
EP2079922A1 (fr) 2009-07-22
CN101529078A (zh) 2009-09-09
DE102006049050A1 (de) 2008-04-30
EP2079922B1 (fr) 2010-12-08
DE502007005914D1 (de) 2011-01-20
ATE491091T1 (de) 2010-12-15
CN101529078B (zh) 2012-07-18

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