EP1404966A1 - Soupape de commande d'un injecteur de carburant pour la compression/decompression d'une chambre de commande - Google Patents

Soupape de commande d'un injecteur de carburant pour la compression/decompression d'une chambre de commande

Info

Publication number
EP1404966A1
EP1404966A1 EP02754253A EP02754253A EP1404966A1 EP 1404966 A1 EP1404966 A1 EP 1404966A1 EP 02754253 A EP02754253 A EP 02754253A EP 02754253 A EP02754253 A EP 02754253A EP 1404966 A1 EP1404966 A1 EP 1404966A1
Authority
EP
European Patent Office
Prior art keywords
valve
control chamber
chamber
fuel injector
anspmch
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.)
Granted
Application number
EP02754253A
Other languages
German (de)
English (en)
Other versions
EP1404966B1 (fr
Inventor
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1404966A1 publication Critical patent/EP1404966A1/fr
Application granted granted Critical
Publication of EP1404966B1 publication Critical patent/EP1404966B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • F02M63/0014—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
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0068—Actuators specially adapted for partial and full opening of the valves

Definitions

  • injection systems with high-pressure plenums are used today to ensure a uniform, pulsation-free injection pressure level during the injections.
  • the cylinders of an air-compressing internal combustion engine are each assigned fuel injectors via which the fuel is injected into the combustion chambers of an internal combustion engine.
  • the injection process depends on the injection processes, among other things. on the speed at which the nozzle needle in the housing of the fuel injector opens or closes the injector.
  • the composition of the exhaust gas of the internal combustion engine for example with regard to HC emissions, is highly dependent on the course of the injection into the combustion chamber.
  • a servo valve has a movable valve element on which a throttle element is formed in the fuel flow direction to the injection nozzle.
  • the throttle element serves to influence the initial phase of the injection and furthermore has a piston-shaped extension over a groove which emerges from a bore in the main phase of the injection and then releases a direct path for the fuel bypassing the throttle.
  • US 5,460,329 relates to a fuel injector with pressure-intensifying translation.
  • the fuel reaches the pressure booster in the injector via an electromagnetic control valve designed as a slide valve.
  • the electromagnetic pressure on the control valve puts the fuel from the pressure booster under high pressure at specified times or crankshaft angles.
  • the fuel under high pressure causes the injector valve needle to lift from its seat. This clears the way for the fuel to the injector injector.
  • DE 199 08 418 Cl relates to a control valve for use in a storage injection system for a diesel engine.
  • the control valve includes a housing with an input port, an output port. and a return connection.
  • a first seat valve with a first valve body and a second seat valve with a second valve body are provided.
  • the first poppet valve is located between the outlet port and the return port and is normally closed, the second poppet valve between the inlet port and the outlet port is normally open.
  • the second valve body is arranged coaxially in the first valve body.
  • US 4,972,997 relates to a fuel injection valve with an axially displaceable, piston-shaped valve member.
  • the valve member has a conical valve sealing surface on its combustion chamber end, with which it interacts with a conical valve seat surface on the valve body, which is formed on the inwardly projecting end of the closed valve bore.
  • a contact edge between the valve sealing surface on the valve member and the valve seat surface forms a circumferential sealing edge. This sealing edge formed when the injection valve is closed seals off a pressure space adjacent upstream of the sealing edge when the injection valve is closed. Downstream of this sealing edge, at least one injection opening, which opens into the combustion chamber of the internal combustion engine to be supplied, is provided in the wall of the valve body and leads away from the valve seat surface.
  • valve member The operating times of the valve member are too long for fast-switching injection valves due to the large hydraulic forces that occur. Furthermore, due to the large number of components lying axially one behind the other, this fuel injection valve is very large, which limits the usability on engines with little available space.
  • DE 197 44 518 AI shows a fuel injection valve for internal combustion engines. It is a fuel injection valve for internal combustion engines with an axially displaceable valve member which is arranged in a valve body and which has a conical valve sealing surface at its end facing the combustion chamber of the internal combustion engine, with which it has a conical valve seat surface on the valve body for controlling an injection cross-section. cut interacts.
  • the valve member is slidably guided by an internal guide on a pin of a stationary insert body.
  • the pressure relief is brought about via a switching valve which is designed as a 3/3-way valve.
  • the valve body of the 3/3-way switching valve can be switched into several positions in the valve space surrounding it.
  • the permanent pressurization of the control chamber via the inlet throttle can be interrupted by closing this inlet, so that the pressure relief of the control chamber takes place via the pressure relief line and the throttle element integrated into it.
  • the throttle assigned to the outlet from the control chamber of the nozzle needle acts as an outlet throttle when the control chamber is depressurized and as its inlet throttle when the control chamber is pressurized.
  • valve body If the valve body is spherical, it can be actuated, for example, using a piezo actuator and two opening speeds can be set. In addition to completely closing the inlet throttle in a lower seat, the valve body can be switched to a central position, in which the control chamber is also relieved of pressure, but there is simultaneous pressurization of the valve chamber of the switching valve, so that the pressure relief of the control chamber takes place at a lower speed.
  • the inlet from a high-pressure source such as, for example, a high-pressure collection space is still provided with an inlet throttle element, but according to this further embodiment variant of the solution according to the invention, the outlet throttle is in the outlet line from the valve chamber of the valve body of a 3/3 Directional control valve relocated.
  • a very rapid pressure relief of the control room can be achieved, since the inlet throttle can be completely closed.
  • the valve body of the 3/3-way control valve can be in one Move middle position, whereby the outflow of the control volume from the control room can also be slowed down.
  • Figure 1 is a control chamber of a nozzle needle associated switching valve with pressure and pressure relief line for the control room and
  • Figure 2 is a control valve assigned to the control chamber, the valve chamber inlet and valve chamber outlet contain throttle elements.
  • FIG. 1 shows a control chamber of a nozzle needle, to which a switching valve is assigned, the pressure relief and pressure relief line of the control chamber being provided with a throttle element.
  • a multi-way valve 3 is accommodated in a housing 2 of an injector body 1.
  • the multi-way valve 3 is preferably designed as a 3/3-way control valve, the valve body 4 of which is a spherical element in the exemplary embodiment shown.
  • the valve body 4 can be moved into several switching positions in the valve chamber 5 surrounding it in the housing 2 of the injector housing 1.
  • the actuation of the spherically configured valve body 4 of the multi-way valve 3 takes place via a transmission element 6, which can be actuated by an actuator, not shown here, be it a piezo actuator or a solenoid valve.
  • a mechanical / hydraulic translator can also be provided as the actuating element of the transmission element 6.
  • the transmission element passes through a bore in the housing 2 of the injector body 1. Between the outer surface of the transmission element 6 and the bore in the housing 2 of the injector 1, an annular space 8 is formed, from which a leak oil drain 9 runs into the low-pressure region of the fuel injector.
  • the annular gap 8 between the transmission element 6 and the housing 2 of the fuel injector 1 functions as an annular throttle element.
  • an inlet 13 from a high-pressure source not shown here, such as a high-pressure collecting chamber (common rail), opens into the valve chamber 5 in the housing 2 of the injector body 1.
  • an inlet throttle element 14 is integrated in the inlet 13 from the high-pressure source, which element is designed in an inlet throttle cross section 15.
  • the inlet 13 opens out on the side opposite the transmission element 6, with which the valve body 4 of the multi-way valve 3 can be actuated.
  • a control chamber duct 16 also opens into the valve chamber 5 of the multi-way valve 3.
  • the control chamber 20 and the valve chamber 5 of the multi-way valve 3 are connected via the control chamber duct 16.
  • the control chamber 20 of the fuel injector is delimited by a wall 21 of the housing 2.
  • a stop surface 22 is also received, which is opposite an upper end face 24 of a nozzle needle 23, the nozzle needle 23 in the housing 2 of the injector body 1 being movable up and down in the vertical direction according to the double arrow 25.
  • the control chamber 20 can be depressurized in the relief direction 17 from a control volume enclosed therein.
  • a throttle element 19 accommodated in the control chamber duct 16 functions as a discharge throttle in the pressure relief direction 17 with respect to the control chamber 20, whereas the throttle element 19 functions as an inlet throttle to the control chamber 20 when the control chamber duct 16 is acted upon in the opposite direction.
  • the valve body 4 of the multi-way valve 3 can be moved into a first switching position 10.1.
  • the first switching position 10.1 the spherical outer surface of the valve body 4 bears against the seat 10 of the valve chamber 5.
  • fuel under high pressure passing through the throttle element 14 in the inlet 13 flows into the valve chamber 5 via the inlet 13 from the high-pressure source.
  • the fuel which is under high pressure, flows from the latter via the control chamber duct 16 in the load direction 18 the throttle element 19 passing into the control chamber 20.
  • pressure builds up in the control chamber 20 so that the nozzle needle 23 is moved in the downward direction and closes one or more injection openings.
  • the spherically configured valve body 4 of the multi-way valve 3 is in its second switching position 11.1, i.e. moved into its lower seat 11 in the valve chamber 5, the inlet 13 is sealed off from the high pressure source, not shown here.
  • the control chamber 20 can be relieved of pressure very rapidly via the control chamber duct 16 in the pressure relief direction 17 via the valve chamber 5, the annular gap into the leakage oil drain 9. The faster the pressure can be reduced in the control chamber 20, the faster the nozzle needle 23 can be opened from its nozzle needle-side seat, not shown here. This is an advantage in the embodiment variant according to FIG.
  • the spherically configured valve body 4 If, on the other hand, the spherically configured valve body 4 is moved into its central position 12, the outflow of the control chamber volume from the control chamber 20 can be slowed down, since in the central position 12 the inlet 13, which opens into the valve chamber 5, is open and thereby a counterpressure is related is generated on the flow direction of the control chamber volume from the control chamber 20. As a result, the control chamber 20 is in the housing
  • FIG. 2 shows a further embodiment variant of the concept on which the invention is based, in which a switching valve assigned to the control chamber comprises a valve chamber, the inlet and outlet of which are provided with throttle elements.
  • valve chamber of the multi-way valve 3 can be connected via an inlet 13 to a throttle element 14 with a high-pressure source, not shown here.
  • a control chamber duct 16 extends from the valve chamber 5 to a control chamber 20 in the housing 2 of the injector body 1, which is delimited on the one hand by a wall 21 of the housing 2 and on the other hand by an end face 24 of the nozzle needle 23 which can be moved in the direction of movement 25 in the housing 2 of the injector body 1.
  • a stop surface 22 is formed analogously to the illustration according to FIG.
  • control chamber channel 16 which connects the pressure-relieved control chamber 20 to the valve chamber 5, does not comprise a throttle element.
  • the control chamber duct 16 can only be acted upon in a pressure relief direction 17 with respect to the control chamber 20 and in a load direction 18 with a fluid, for example fuel.
  • the throttle element 19 accommodated in the control chamber duct 16 according to FIG. 1 is now integrated in the leak oil drain 9 branching off from the annular gap 8 between the transmission element 6 and the housing 2.
  • valve body 4 of the multi-way valve 3 On the valve chamber 5, which surrounds the spherically configured valve body 4 of the multi-way valve 3, an upper seat 10 corresponding to a first switching position 10.1 and an opposing lower seat 11 are formed, in which the valve body 4 of the multi-way valve 3 can be set to a second switching position 11.1 is.
  • the valve body 4 of the multi-way valve 3 In the state shown in Figure 2, the valve body 4 of the multi-way valve 3 is in a central position
  • the switch positions 10.1, 11.1 and 12 of the valve body 4 essentially correspond to the switch positions 10.1, 11.1 and 12, which have already been described in connection with the embodiment variant according to FIG.
  • a higher flow rate of the control chamber volume from the control chamber 20 into the valve chamber 5 of the multi-way valve 3 can be achieved by removing the throttle element 19 from the control chamber channel 16, which connects the control chamber 20 and the valve chamber 5.
  • a further increased flow velocity in the pressure relief of the control chamber 20 can be achieved compared to the illustration according to FIG. 1.
  • the multi-way valve 3 placed in its second switching position 11.1 closes the otherwise permanently acting inflow of fuel via the inflow 13 from a high-pressure source (not shown here) into the valve chamber 5 and from there via the control chamber duct 16 into the control chamber 20.
  • pressure relief of the control chamber 20 can take place at a first higher speed if in the control chamber duct 16 according to no throttle element 19 is included in the illustration in FIG. If the embodiment variant in FIG. 2, the valve body 4 is moved into its central position 12, a somewhat slower pressure relief speed in the pressure relief direction 17 in the control chamber channel 16 can be set in the valve chamber 5. This essentially also applies to the embodiment variant as shown in FIG. 1, the outflow speed of the control chamber volume from the control chamber 20 being reduced in comparison to the solution according to FIG.
  • a throttle element 19 is accommodated in the control chamber channel 16.
  • this is located in the leak oil drain 9 on the low pressure side behind the valve chamber 5 of the multi-way valve, which is preferably configured as a 3/3-way control valve.
  • the rapid opening of the nozzle needle 23 from its seat that can be achieved with the illustrated embodiment variants according to FIGS. 1 and 2 leads to the reduction of exhaust gas emissions of a self-igniting internal combustion engine operated in this way.
  • the central position 12 in which the Ventilgro ⁇ er 4 of the multi-way valve 3 can be adjusted, a slow opening of the nozzle needle 3 in the control chamber 20 and thus a slower release of the injection opening can be achieved.
  • This gives the possibility of shaping the course of the injection and adapting it to the progress of the combustion in the combustion chamber of the internal combustion engine.

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 de carburant pour moteurs à combustion interne, comportant un corps d'injecteur (1), dans le boîtier (2) duquel est logé un pointeau (23) mobile qui obture et libère les orifices d'injection. Ce pointeau (23) est actionné par l'intermédiaire d'une chambre de commande (20) pouvant être décompressée, laquelle est alimentée en carburant sous haute pression par l'amenée (13) d'une source de haute pression. Le boîtier (2) du corps d'injecteur (1) comprend la boîte de distribution (5) d'un distributeur multivoie (3). La chambre de commande (20) est reliée à la boîte de distribution (5) du distributeur multivoie (3) par un canal (16) qui, relativement à la chambre de commande (20) est alimenté à la fois dans le sens de la décompression (17) et dans le sens de la compression (18).
EP02754253A 2001-06-29 2002-06-21 Soupape de commande d'un injecteur de carburant pour la compression/decompression d'une chambre de commande Expired - Lifetime EP1404966B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10131617 2001-06-29
DE2001131617 DE10131617A1 (de) 2001-06-29 2001-06-29 Kraftstoffinjektor-Schaltventil zur Druckentlastung/Belastung eines Steuerraumes
PCT/DE2002/002290 WO2003004864A1 (fr) 2001-06-29 2002-06-21 Soupape de commande d'un injecteur de carburant pour la compression/decompression d'une chambre de commande

Publications (2)

Publication Number Publication Date
EP1404966A1 true EP1404966A1 (fr) 2004-04-07
EP1404966B1 EP1404966B1 (fr) 2008-02-20

Family

ID=7690062

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02754253A Expired - Lifetime EP1404966B1 (fr) 2001-06-29 2002-06-21 Soupape de commande d'un injecteur de carburant pour la compression/decompression d'une chambre de commande

Country Status (3)

Country Link
EP (1) EP1404966B1 (fr)
DE (2) DE10131617A1 (fr)
WO (1) WO2003004864A1 (fr)

Families Citing this family (12)

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Publication number Priority date Publication date Assignee Title
DE10349639A1 (de) * 2003-10-24 2005-05-19 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102004024215A1 (de) * 2004-05-15 2005-12-08 L'orange Gmbh Steuerventil
JP4855946B2 (ja) 2006-06-08 2012-01-18 株式会社デンソー 燃料噴射弁
JP2008002306A (ja) * 2006-06-21 2008-01-10 Denso Corp 燃料噴射弁
JP5043761B2 (ja) 2008-06-18 2012-10-10 本田技研工業株式会社 燃料噴射装置
DE102010040989A1 (de) * 2010-09-17 2012-03-22 Continental Automotive Gmbh Steuerventileinheit für einen Kraftstoffinjektor
CH704454A1 (de) * 2011-02-08 2012-08-15 Liebherr Machines Bulle Sa Einspritzvorrichtung für ein Fluid.
DE102012202055A1 (de) 2012-02-10 2013-08-14 Robert Bosch Gmbh Kraftstoffinjektor
DE102012220025A1 (de) 2012-06-29 2014-01-02 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102012221624A1 (de) 2012-11-27 2014-05-28 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102012223199A1 (de) 2012-12-14 2014-06-18 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102012224398A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

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IT212432Z2 (it) 1987-08-25 1989-07-04 Weber Srl Valvola di iniezione del combustibile a comando elettromagnetico per motori a ciclo diesel
JPH0571438A (ja) * 1991-09-11 1993-03-23 Nippondenso Co Ltd 燃料噴射装置
US5460329A (en) 1994-06-06 1995-10-24 Sturman; Oded E. High speed fuel injector
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
DE19744518A1 (de) 1997-10-09 1999-04-15 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
JP2002516952A (ja) * 1998-05-28 2002-06-11 シーメンス アクチエンゲゼルシヤフト 内燃機関に用いられる燃料噴射弁
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DE19910589C2 (de) 1999-03-10 2002-12-05 Siemens Ag Einspritzventil für eine Brennkraftmaschine
JP3557996B2 (ja) * 1999-06-21 2004-08-25 トヨタ自動車株式会社 燃料噴射装置
DE19946828C1 (de) * 1999-09-30 2001-07-12 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
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JP4048699B2 (ja) * 1999-11-10 2008-02-20 株式会社デンソー 燃料噴射弁

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Also Published As

Publication number Publication date
EP1404966B1 (fr) 2008-02-20
DE50211740D1 (de) 2008-04-03
WO2003004864A1 (fr) 2003-01-16
DE10131617A1 (de) 2003-01-23

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