EP1688611B1 - Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne - Google Patents

Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne Download PDF

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Publication number
EP1688611B1
EP1688611B1 EP05112500A EP05112500A EP1688611B1 EP 1688611 B1 EP1688611 B1 EP 1688611B1 EP 05112500 A EP05112500 A EP 05112500A EP 05112500 A EP05112500 A EP 05112500A EP 1688611 B1 EP1688611 B1 EP 1688611B1
Authority
EP
European Patent Office
Prior art keywords
space
side pressure
coupler
piston
actuator
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
EP05112500A
Other languages
German (de)
English (en)
Other versions
EP1688611A3 (fr
EP1688611A2 (fr
Inventor
Thomas Pauer
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 EP1688611A2 publication Critical patent/EP1688611A2/fr
Publication of EP1688611A3 publication Critical patent/EP1688611A3/fr
Application granted granted Critical
Publication of EP1688611B1 publication Critical patent/EP1688611B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F02M63/0061—Single actuator acting on two or more 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the invention relates to a fuel injector with direct needle control for an internal combustion engine according to the preamble of claim 1.
  • Fuel injectors with a so-called direct needle control are known. Such fuel injectors come without an intermediate control valve between an electrically actuated actuator and a nozzle needle. The power transmission between the actuator and the nozzle needle is realized by means of a pressure booster device.
  • piezoelectric actuators are suitable as actuators, which, depending on the energization in the closed state, have a direct or inverse control. In a direct control of the piezoelectric actuator is energized to open the nozzle needle, so that a linear expansion of the piezoelectric actuator realized by an oppressive movement opening of the injectors, which is amplified by the pressure booster device. In the closed state, the piezoelectric actuator has a smaller linear expansion.
  • the piezo actuator In an inverse control, the piezo actuator is energized in the closed state of the nozzle needle, so that the piezo actuator holds the nozzle needle closed in the state of its longitudinal expansion.
  • the piezoelectric actuator When the piezoactuator is actuated, the piezoelectric actuator is de-energized to initiate the injection process, so that pressure is released by a pulling movement of the piezoactuator in a control chamber of the pressure booster device. As a result, the lifting movement of the piezo actuator is hydraulically translated to open the nozzle needle.
  • the actuator In order to be able to open the injectors directly in fuel injectors with direct needle control by means of the actuator, the actuator must overcome a high opening force.
  • the required opening force to be applied by the actuator is due to the fact that the nozzle needle is pressurized with system pressure (pressure level in high-pressure accumulator) into its seat.
  • system pressure pressure level in high-pressure accumulator
  • the forces required to open the nozzle needle from its seat can be up to 400 Newton.
  • the nozzle needle performs a maximum stroke of several 100 microns.
  • the size of the actuator also referred to as the actuator volume, is essentially proportional to the opening force to be applied and the maximum stroke of the nozzle needle to be represented.
  • the fuel injector in this case has a guided in a nozzle body nozzle needle, which is exposed to a pressure shoulder a nozzle chamber and acts on a Düsennadeldichtsitzes, and a piezoelectric actuator and a hydraulic pressure booster on.
  • the pressure booster device comprises a coupler chamber, a pressure chamber and a control chamber, the coupler chamber and the pressure chamber being exposed to an actuator-side pressure booster piston connected to the piezo actuator.
  • the control chamber which is exposed to a nozzle needle-side pressure booster piston communicating with the nozzle needle, is hydraulically connected to the coupler chamber.
  • a pressing Aktorhub is generated, which moves the pressure booster piston in the direction of the pressure chamber, so that the pressure in the pressure chamber increases and the volume in the rear coupler space increases. This reduces the pressure in the coupler compartment.
  • the pressure reduction of the coupler chamber is transmitted to the hydraulically connected control chamber, so that the force acting on the nozzle needle closing force in the control chamber is reduced.
  • the simultaneously increasing pressure in the pressure chamber is transmitted to the hydraulically connected nozzle chamber, whereby the force acting on the nozzle needle opening force is supported.
  • the nozzle needle lifts off the nozzle needle seat and fuel is injected at the system pressure.
  • the nozzle needle moves in one stage according to the movement of the pressure booster piston in dependence on the pressure ratio between the coupler space and the control room.
  • the object of the invention is to provide a fuel injector with direct needle control and inverse control, which is simple and manages with a small size.
  • the fuel injector to realize a two-stage translation of the nozzle needle.
  • the object of the invention is achieved with a fuel injector with the characterizing measures of claim 1.
  • a particularly simple design can be achieved if the nozzle needle-side booster piston and the control piston in a stop position of the control piston in the coupler space facing common kopplerraum workede pressure surface forms, which forms a first pressure transmission ratio for a first gear ratio with a formed on the actuator-side pressure booster piston third kopplerraum workede pressure surface.
  • Appropriately, is to form a stop surface for the realization of the stop position of the control piston in the cylinder chamber, wherein the control piston is biased against the stop surface with a compression spring.
  • a second booster stage is realized in that a pressure compensation, which is transmitted from the outer rear space via the inner rear space to the control piston takes place, through which the control piston occupies a position raised from the stop surface, so that the annular surface pointing from the nozzle needle side pressure booster piston into the coupler space is effective Pressure surface forms a second pressure transmission ratio with the pressure surface formed by the actuator-side pressure booster piston and pointing into the coupler space, which realizes an opening stroke extending beyond the stroke of the actuator.
  • the fuel injector can be realized by guiding the actuator-side pressure booster piston and the nozzle needle-side pressure booster piston in a guide sleeve. It is also expedient if the actuator-side pressure booster piston is biased by a piston spring opposite to the closing direction of the nozzle needle and when the piston spring is supported on the guide sleeve.
  • FIG. 1 shows a schematic diagram of a fuel injector according to the invention in longitudinal section.
  • the fuel injector shown has an injector housing 10 with a nozzle body 11 which projects with its lower end into a combustion chamber of an internal combustion engine. Between injector housing 10 and nozzle body 11 is a nozzle needle guide 12 with a Guide bore 13 is arranged. In the guide bore 13, a nozzle needle 14 is guided axially displaceable. Between the tip of the nozzle needle 14 and the nozzle body 11 is a sealing seat 15 is formed, which are formed in the nozzle body 11 and projecting into the combustion chamber injection nozzles 16 downstream.
  • the sealing seat 15 is preceded by a high-pressure chamber 17 is formed.
  • the injector housing 10 has an actuator receiving space 18 in an upper area, to which a fuel inlet 19 is connected.
  • a piezoelectric actuator 20 is arranged in Aktorfactraum 18 .
  • the fuel inlet 19 is connected to a high-pressure system, for example, to a common rail system of a diesel injection device.
  • a connecting bore 21 passes through the nozzle needle guide 12, so that the fuel introduced via the fuel feed 19 into the actuator receiving space 18 is conducted at high pressure into the high-pressure space 17 assigned to the nozzle needle 14.
  • the actuator receiving space 18 merges into a receiving space 22 for a pressure booster 30.
  • the pressure booster 30 has an actuator-side pressure booster piston 31, a nozzle needle side pressure booster piston 32, a coupler space 33, a control piston 34, a guide sleeve 35, an inner rear space 36 and an outer rear space 37.
  • the actuator-side pressure booster piston 31 and the nozzle needle-side pressure booster piston 32 are guided in the guide sleeve 35.
  • a piston spring 38 is arranged, which presses a formed on the guide sleeve 35 sealing surface 39 against an opening formed on the nozzle needle guide 12 face 23.
  • the piston spring 38 also biases the actuator-side pressure booster piston 31 against the piezo-actuator 20.
  • a closing spring 25 which presses the nozzle needle 14 in the closing direction, engages on the nozzle needle 14.
  • the nozzle needle-side pressure booster piston 32 is designed with an inner cylinder chamber 40 in which the control piston 34 is guided axially movable. Towards the coupler space 33, the inner cylinder space 40 is provided with a circular opening 41, so that a first, annular, coupler-space-side pressure surface 42 on the nozzle needle-side pressure booster piston 32 forms toward the coupler space 33.
  • the diameter of the cylinder chamber 40 is greater than the diameter of the opening 41, so that at the opening 41 in the cylinder chamber 40 facing annular abutment surface 43 for the control piston 34 is formed.
  • the cylinder chamber 40 and the control piston 34 are designed so that the control piston 34 in the cylinder chamber 40 at the side facing away from the coupler chamber 33 side with a rear-side pressure surface 48 in the inner rear space 36 has.
  • a further compression spring 44 is arranged, which presses the control piston 34 against the stop surface 43.
  • the control piston 34 has a second, circular, coupler space-side pressure surface 45, which points into the coupler space 40 and corresponds to the cross-section of the opening 41.
  • the actuator-side pressure booster piston 31 has a third pressure surface 46 on the coupler-space side in the coupler space 33.
  • a stepped piston To the tip of the nozzle needle 14 toward the nozzle needle-side booster piston 32 is designed as a stepped piston with an annular surface 24 which is associated with the outer rear space 37 within the guide sleeve 35.
  • the outer rear space 37 and the inner rear space 36 are connected via a hydraulic connection 47, for example a bore.
  • the sealing seat 15 of the nozzle needle 16 is closed.
  • the system pressure reached via the fuel supply 19 into the actuator receiving space 18 and into the pressure chamber 17 is equal in all pressure chambers. In this case, there are leakage gaps on the guide sleeve 35, so that the system pressure can reach both into the coupler space 33 and into the outer rear space 37 and via the connection 47 into the inner rear space 36.
  • the pressure booster 30 is pressure balanced.
  • the actuator 20 is supplied with a voltage and thereby elongated in its energized state in its vertical direction.
  • the system pressure applied in the coupler chamber 33 acts in the closing direction on the nozzle needle-side pressure-translating piston 32, so that in this state of the piezo-actuator 20, the sealing seat 15 of the nozzle needle 14 is closed.
  • the length of the piezoelectric actuator 20 in the vertical direction is likewise reduced. Due to the biased by the piston spring 38 in the direction of the piezo-actuator 20 actuator-side pressure booster piston 31 this is also moved in the vertical direction due to the reduced vertical length of the piezo-actuator 20. As a result of this outwardly directed pulling movement of the actuator-side pressure booster piston 31 in the guide sleeve 35, the volume in the coupler space 33 increases, whereby there takes place a pressure reduction which delivers an opening pressure p ö1 for a first stage for opening the nozzle needle 14.
  • the pressure ratio for the first opening stage is formed by the ratio of the actuator-side pressure booster piston 31 formed third kopplerraum detaileden pressure surface 46 to the common kopplerraum subjecten pressure surface, wherein the common kopplerraum dealte pressure surface is composed of the first annular kopplerraum technologyen pressure surface 42 of the nozzle needle side pressure booster piston 32 and the second, circular kopplerraum disorderen pressure surface 45 of the control piston 34.

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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)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Claims (8)

  1. Injecteur de carburant pour un moteur à combustion interne comportant une aiguille d'injecteur (14) guidée dans un corps d'injecteur (11), l'aiguille coopérant avec un siège d'étanchéité d'aiguille d'injecteur (15), un actionneur (20) et une installation de démultiplication hydraulique de pression (30) comportant un piston démultiplicateur de pression (31) coopérant côté actionneur avec l'actionneur (20) et un piston démultiplicateur de pression (32) coopérant côté aiguille d'injecteur avec l'aiguille d'injecteur (14), ces pistons agissant sur une chambre de couplage (33) et
    en fonction de la pression régnant dans la chambre de couplage (33), l'aiguille d'injecteur (14) sera soulevée par rapport à son siège d'étanchéité (15) et ainsi du carburant mis à haute pression sera injecté à partir de la chambre haute pression (17) dans une chambre de combustion du moteur à combustion interne,
    caractérisé par
    une chambre de cylindre (40) réalisée dans le piston démultiplicateur de pression (32) côté aiguille d'injecteur, cette chambre guidant axialement un piston de commande (34) exposé par une surface de poussée (45) côté chambre de couplage à la chambre de couplage (33) et par une surface de poussée (48) côté chambre arrière avec une chambre arrière intérieure (36) réalisée dans la chambre de cylindre (40) et
    une chambre arrière extérieure (37) est associée au piston démultiplicateur de pression (32), côté aiguille d'injecteur, cette chambre étant reliée par une liaison hydraulique (47) à la chambre arrière intérieure (36) agissant sur le piston de commande (34).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la chambre arrière extérieure (37) est prévue sur le côté du piston démultiplicateur de pression (32) opposé à celui de la chambre de couplage (33).
  3. Injecteur de carburant selon la revendication 1 ou 2,
    caractérisé en ce que
    le piston démultiplicateur de pression (32) côté aiguille d'injecteur forme avec le piston de commande (34) en position de butée, une surface de poussée commune, côté chambre de couplage, tournée vers la chambre de couplage (33), et qui forme un premier rapport de démultiplication de pression pour un premier étage de démultiplication avec une troisième surface de poussée (46) côté chambre de couplage du piston de démultiplication de pression (31) côté actionneur, et est tournée vers la chambre de couplage (25).
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    la chambre de cylindre (40) comporte une surface de butée (43) pour définir la position de butée du piston de commande (34).
  5. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que
    le piston de commande (34) est précontraint par un ressort de pression (44) contre la surface de butée (43).
  6. Injecteur de carburant selon la revendication 4 ou 5,
    caractérisé en ce que
    pour une position du piston de commande (34) soulevée par rapport à la surface de butée (43), la première surface de poussée (43) de forme annulaire, côté chambre de couplage, et qui est dirigée à partir du piston démultiplicateur de pression (32) côté aiguille d'injecteur dans la chambre de couplage (33), forme avec la troisième surface de poussée (46) côté chambre de couplage, tournée vers la chambre de couplage (34) du piston démultiplicateur de pression (31) côté actionneur, un second rapport de démultiplication de pression qui réalise une course d'ouverture dépassant la course de l'actionneur (20) pour un second niveau de démultiplication.
  7. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le piston démultiplicateur de pression (31), côté actionneur, et le piston démultiplicateur de pression (32), côté aiguille d'injecteur, sont guidés dans un manchon de guidage (35).
  8. Injecteur de carburant selon la revendication 7,
    caractérisé en ce que
    le piston démultiplicateur de pression (31), côté actionneur, est précontraint par un ressort de piston (38) dans la direction opposée à la direction de fermeture de l'aiguille d'injecteur (14) et le ressort de piston (38) s'appuie contre le manchon de guidage (35).
EP05112500A 2005-02-02 2005-12-20 Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne Ceased EP1688611B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005004738A DE102005004738A1 (de) 2005-02-02 2005-02-02 Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1688611A2 EP1688611A2 (fr) 2006-08-09
EP1688611A3 EP1688611A3 (fr) 2007-01-10
EP1688611B1 true EP1688611B1 (fr) 2008-07-30

Family

ID=36182388

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05112500A Ceased EP1688611B1 (fr) 2005-02-02 2005-12-20 Injecteur de carburant à commande de pointeau directe pour un moteur à combustion interne

Country Status (4)

Country Link
US (1) US7419103B2 (fr)
EP (1) EP1688611B1 (fr)
AT (1) ATE403082T1 (fr)
DE (2) DE102005004738A1 (fr)

Families Citing this family (19)

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Publication number Priority date Publication date Assignee Title
DE10326259A1 (de) * 2003-06-11 2005-01-05 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
DE10352736A1 (de) * 2003-11-12 2005-07-07 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadeleinspritzung
DE102005012929A1 (de) * 2005-03-21 2006-09-28 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Steuerung des Einspritzventilglieds und variabler Übersetzung
DE102005016796A1 (de) * 2005-04-12 2006-10-19 Robert Bosch Gmbh Zweistufig öffnender Kraftstoffinjektor
DE102005025953A1 (de) * 2005-06-06 2006-12-07 Siemens Ag Einspritzventil und Ausgleichselement für ein Einspritzventil
DE102005036444A1 (de) * 2005-08-03 2007-02-08 Robert Bosch Gmbh Einspritzdüse
DE102006008648A1 (de) * 2006-02-24 2007-08-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine
US8074625B2 (en) 2008-01-07 2011-12-13 Mcalister Technologies, Llc Fuel injector actuator assemblies and associated methods of use and manufacture
DE102008008847A1 (de) 2008-02-13 2009-08-27 Robert Bosch Gmbh Kraftstoffinjektor mit einer direkt gesteuerten Ventilnadel
DE102008032133B4 (de) * 2008-07-08 2015-08-20 Continental Automotive Gmbh Kraftstoffeinspritzvorrichtung
DE102009024595A1 (de) * 2009-06-10 2011-03-24 Continental Automotive Gmbh Einspritzventil mit Übertragungseinheit
DE102009024596A1 (de) 2009-06-10 2011-04-07 Continental Automotive Gmbh Einspritzventil mit Übertragungseinheit
DE102012212266B4 (de) * 2012-07-13 2015-01-22 Continental Automotive Gmbh Fluidinjektor
DE102012212264B4 (de) 2012-07-13 2014-02-13 Continental Automotive Gmbh Verfahren zum Herstellen eines Festkörperaktuators
WO2014144807A1 (fr) * 2012-11-12 2014-09-18 Mcalister Technologies, Llc Systèmes et procédés permettant une compensation et une amplification de mouvement par déplacement de fluide
US20140131466A1 (en) 2012-11-12 2014-05-15 Advanced Green Innovations, LLC Hydraulic displacement amplifiers for fuel injectors
US9309846B2 (en) 2012-11-12 2016-04-12 Mcalister Technologies, Llc Motion modifiers for fuel injection systems
DE102013219225A1 (de) * 2013-09-25 2015-03-26 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoff-Direkteinspritzung
DE102014211334B3 (de) * 2014-06-13 2015-08-27 Continental Automotive Gmbh Verfahren zur Charakterisierung eines hydraulischen Koppelelementes eines Piezo-Injektors

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Publication number Priority date Publication date Assignee Title
US4784102A (en) * 1984-12-25 1988-11-15 Nippon Soken, Inc. Fuel injector and fuel injection system
DE19712921A1 (de) * 1997-03-27 1998-10-01 Bosch Gmbh Robert Brennstoffeinspritzventil mit piezoelektrischem oder magnetostriktivem Aktor
GB9925753D0 (en) * 1999-10-29 1999-12-29 Lucas Industries Ltd Fuel injector
DE60126380T2 (de) * 2000-07-18 2007-11-15 Delphi Technologies, Inc., Troy Kraftstoffeinspritzventil
US6766965B2 (en) * 2001-08-31 2004-07-27 Siemens Automotive Corporation Twin tube hydraulic compensator for a fuel injector
DE10326046A1 (de) 2003-06-10 2004-12-30 Robert Bosch Gmbh Einspritzdüse für Brennkraftmaschinen
DE10347769B3 (de) * 2003-10-14 2005-01-13 Siemens Ag Stellgerät

Also Published As

Publication number Publication date
ATE403082T1 (de) 2008-08-15
EP1688611A3 (fr) 2007-01-10
DE502005004874D1 (de) 2008-09-11
DE102005004738A1 (de) 2006-08-10
US7419103B2 (en) 2008-09-02
EP1688611A2 (fr) 2006-08-09
US20060169802A1 (en) 2006-08-03

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