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EP1379775B1 - Soupape pour commander le passage de fluides - Google Patents

Soupape pour commander le passage de fluides Download PDF

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Publication number
EP1379775B1
EP1379775B1 EP02729861A EP02729861A EP1379775B1 EP 1379775 B1 EP1379775 B1 EP 1379775B1 EP 02729861 A EP02729861 A EP 02729861A EP 02729861 A EP02729861 A EP 02729861A EP 1379775 B1 EP1379775 B1 EP 1379775B1
Authority
EP
European Patent Office
Prior art keywords
valve
actuating piston
piston
actuating
valve according
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
EP02729861A
Other languages
German (de)
English (en)
Other versions
EP1379775A1 (fr
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
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 EP1379775A1 publication Critical patent/EP1379775A1/fr
Application granted granted Critical
Publication of EP1379775B1 publication Critical patent/EP1379775B1/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
    • 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
    • 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
    • F02M47/025—Hydraulically 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
    • 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
    • F02M2200/70—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
    • 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 is based on a valve for controlling fluids according to the type defined in more detail in the preamble of claim 1.
  • Such a valve is known in practice and is used for example in conjunction with an injection valve, in particular an injection valve of a common rail accumulator injection system for diesel internal combustion engines.
  • an injection valve known from the document US Pat. No. 6,076,800, has a valve control piston, which forms a structural unit with a nozzle needle and is at least partially enclosed by a space which is connected to a high-pressure connection via a fuel supply line and contains fuel.
  • the nozzle needle acts with a correspondingly formed valve seat together, so that in dependence on the position of the valve spool via a to a Combustion chamber of the combustion engine leading opening of the injection valve, the fuel injection into the combustion chamber can be controlled.
  • the position of the valve control piston and thus that of the nozzle needle is determined by means of the initially mentioned valve for controlling fluids, which is in operative connection with the valve control piston via a so-called valve control chamber.
  • the valve control chamber is connected via an inlet throttle with the fuel supply line and via a so-called outlet throttle with the aforementioned valve, the so-called valve control module, in operative connection and adjacent to the free end, i. at the end of the valve spool facing away from the nozzle needle.
  • This structure allows a targeted, triggered by the valve control module, described below pressure build-up and pressure reduction in the valve control chamber.
  • valve-shaped valve control module In the closed position of the valve-shaped valve control module prevails in the valve control chamber acting on the inlet throttle high pressure, in the case of a Common Räil injection system, the so-called rail pressure. Under these pressure conditions, the valve spool and thus also the nozzle needle is in the closed position. If, for example, the piezoelectric actuator of the valve control module is actuated, then the valve closing element of the valve control module opens. As a result, the fuel located in the valve switch compartment can drain into a return duct via a control bore and a drainage chamber, which are assigned to the valve control module, the pressure being increased reduced in the valve control room.
  • the assembly consisting of the valve spool and the nozzle needle shifts toward the valve control space, so that the opening leading to the combustion chamber is released and fuel is injected thereinto.
  • the so-called rail pressure builds up again in the valve control chamber via the inlet throttle, and the valve control piston is moved back into the closed position.
  • the injection valve is sealed to the combustion chamber, and there is no fuel in the latter.
  • valve according to the invention with the features of claim 1, wherein the actuating piston is mounted at least with a closed valve closing member substantially hydraulically balanced, has the advantage that significantly lower forces are required to open the valve closure member. Because here the actuating piston does not have - as with the Valves according to the prior art - against the force acting on the valve closing member fluid pressure, in the case of a common-rail injection system against the so-called rail pressure, which may be up to 1.6 kbar, are opened.
  • the particular piezoelectric actuator in the valve according to the invention can also be driven with a lower voltage, which in turn leads to a reduction of the energy requirement compared to the valves according to the prior art.
  • the valve closure member is preferably part of the actuating piston.
  • the actuating piston has an axial bore which branches off from the control chamber and engages through the actuating piston. This axial bore leads from the arranged in front of the valve seat control chamber to a arranged on the opposite side of the actuating piston space, so that in this prevails at least when the valve closing member of the pressure prevailing in the control chamber.
  • the axial bore is formed as a stepped bore, wherein the region of increased diameter formed on the end remote from the control chamber end of the actuating piston and in this area a guide pin is arranged.
  • This guide pin then limits the space at the end remote from the control chamber end of the actuating piston lies and in which prevails the pressure prevailing in the control room.
  • this advantageously has a blind bore, which lies substantially in the axis of the axial bore of the actuating piston.
  • the actuating piston is designed as a stepped cylinder.
  • the shoulder surface of this stepped cylinder may then form the surface of the actuating piston which is exposed to the pressure exerted by the hydraulic piston on the actuating piston by the actuating piston.
  • the shoulder surface may in this case be aligned so that the actuating piston moves in actuation of the actuator unit in the direction away from the control chamber.
  • the actuating piston can be biased in the closing direction by means of a compression spring arranged in a spring chamber.
  • the spring chamber may communicate with the return passage so that the pressure prevailing in the return passage is present in the spring chamber.
  • the spring chamber can be connected via a pressure equalization channel with an annular space formed by an annular groove on the circumference of the Adjusting piston is formed.
  • the embodiment shown in the figure shows a fuel injection valve 1, which is provided for installation in an internal combustion engine, not shown, of a motor vehicle and is designed here as Commen-rail injector for the injection of preferably diesel fuel.
  • the fuel injection valve 1 comprises a nozzle module 2 and a valve control module 3 as essential components.
  • the nozzle module 2 comprises a nozzle body 4, in which a so-called valve control piston 5 is arranged, which is in operative connection with a nozzle needle, not shown, which controls an opening of the injection valve 1 leading to a combustion chamber of the internal combustion engine or forms a structural unit therewith.
  • a spring plate 6 is further arranged, in which the free end of the valve control piston 5 is guided and limits a valve control chamber 7 together with the latter.
  • the spring plate 6 is supported via a spring 8 on a support 9, which is connected to the valve control piston 5.
  • inlet throttle 10 which leads from the valve control chamber 7 to a high-pressure chamber 11, which between the outer contour of the spring plate 6 and the enclosing him
  • Nozzle body 4 is formed and is connected via a fuel supply line 12 with a high-pressure accumulator, not shown here, the so-called common rail.
  • outlet throttle 13 In the axial direction of the valve control chamber 7 is connected via a so-called outlet throttle 13 with a control chamber 14 which is associated with the valve control module 3.
  • valve control piston 5 The position of the valve control piston 5 and thus that of the nozzle needle is controlled via the pressure level in the valve control chamber 7. This is in turn set by means of the valve control module 3.
  • the valve control module 3 comprises a control module body 15, in which a stepped formed actuating piston 16 is guided in a stepped bore 17.
  • the actuating piston 16 is connected via a hydraulic chamber 18 with an actuating piston 19 in operative connection.
  • the actuator piston 19 may be disposed at any location within or outside of the control body 15. It is actuated by means of a here as a piezoelectric actuator actuator unit 20 '.
  • the hydraulic chamber 18 here consists of a cylinder chamber 21 assigned to the adjusting piston 19 and bounding the free end side, a channel 22 and an annular annular space 23 surrounding the region of the reduced diameter of the stepped actuating piston 16.
  • valve closing member which cooperates with a valve seat 24 and the control chamber 14 separates in the closed position of a so-called drain chamber 25 from which a fuel return passage 26 branches off, which is not one here shown fuel storage tank leads.
  • actuating piston 16 is axially aligned, for example, designed as a bore channel 27 which leads from the control chamber 14 to the end remote from the actuating piston 16 and expands into a region 36 of increased diameter.
  • a guide pin 28 is arranged, which has a blind bore 29 on the side facing the control chamber 14 side.
  • the diameter d1 of the guide pin 28 and thus also that of the bore portion 36 substantially corresponds to the diameter d2 of the valve seat 24, i.
  • the guide pin 28 is formed so that it is guided with minimal play and maximum guide length L in the bore region 36.
  • the spring chamber 31 is connected via a transverse channel 32 to the fuel return passage 16. Downstream of the discharge point of the transverse channel 32, a pressure relief valve 33 is disposed in the fuel return passage 32.
  • the injection valve described above operates in the manner described below.
  • the guide pin 28 is guided with minimum clearance and maximum guide length L in the bore 36 of the actuating piston 16.
  • the ratio of the diameter d1 of the bore 36 and the sealing diameter d2 determines the hydraulic force acting on the actuating piston 16. This ratio is approximately equal to 1 in the present case, so that the actuating piston 16 is stored hydraulically balanced, is. As a result, only a small, by means of the actuator 20 ausziembode force is required for displacement of the actuating piston 16 by means of the actuating piston 19.
  • the pressure equalization channel 41 ensures that in the hydraulic chamber 21 always the same constant pressure as in the spring chamber 31 prevails. This may optionally be compensated by the radial clearance of the actuating piston 16 in the stepped bore 17 and the radial play of the actuating piston 19 in its guide bore resulting pressure differences, so that always constant loads of the piezoelectric actuator 20 prevail and scatters in the injected by the injector 1 injection quantities largely excluded are.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Fluid-Driven Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

L'invention concerne une soupape permettant de commander le passage de fluides, cette soupape comprenant une unité d'actionnement (20), en particulier piezoélectrique, pour actionner un obturateur. Cet obturateur comprend au moins un piston de commande (19) et au moins un piston d'actionnement (16) guidé dans un corps de soupape (15). Ce piston d'actionnement (16) actionne un élément de fermeture de soupape qui coopère avec au moins un siège de soupape (24) formé sur le corps de soupape (15) et, en position de fermeture, sépare un alésage de commande (14) d'une chambre de décharge (25) à laquelle un canal de retour (26) est relié. Une chambre hydraulique (18), disposée entre le piston de commande (19) et le piston d'actionnement (16), transmet un mouvement du piston de commande (19) au piston d'actionnement (16). Selon l'invention, pour que l'unité d'actionnement (20) conserve des dimensions réduites, le piston d'actionnement (16) est monté de telle sorte que les forces hydrauliques soient sensiblement équilibrées lorsque l'élément de fermeture de soupape est fermé.

Claims (11)

  1. Soupape (1) pour commander des liquides, comprenant un actionneur (20) en particulier piézoélectrique pour actionner un organe de soupape ayant au moins un piston de réglage (19) et au moins un piston d'actionnement (16) guidé dans un corps de soupape (15), et actionnant un organe de fermeture de soupape, qui coopère avec au moins un siège de soupape (24) formé sur le corps de soupape (15) et qui en position de fermeture sépare une chambre de commande (14) d'une chambre d'écoulement (25) de laquelle dérive un canal de retour (26), alors qu'entre le piston de réglage (19) et le piston d'actionnement (16) une chambre hydraulique (18) transmet un mouvement du piston de réglage (19) sur le piston d'actionnement (16),
    caractérisée en ce que
    le piston d'actionnement (16) présente un alésage axial (27) partant de la chambre de commande (14) et relié en permanence à cette chambre de commande (14), et qui traverse le piston d'actionnement (16) en présentant la forme d'un alésage étagé avec une zone d'alésage (36) d'un diamètre agrandi, et
    le diamètre (d1) de la zone d'alésage (36) d'un diamètre agrandi correspond au diamètre étanche (d2) de l'organe de fermeture de soupape, pour permettre de loger le piston d'actionnement (16), du moins lorsque l'organe de fermeture de soupape est fermé, de manière pour l'essentiel équilibrée au niveau de la force hydraulique par rapport à la pression régnant dans la chambre de commande (14).
  2. Soupape selon la revendication 1,
    caractérisée en ce que
    l'organe de fermeture de soupape fait partie du piston d'actionnement (16).
  3. Soupape selon la revendication 1 ou 2,
    caractérisée en ce qu'
    une tige de guidage (28) est disposée dans la zone d'alésage (36) de diamètre agrandi.
  4. Soupape selon la revendication 3,
    caractérisée en ce que
    la tige de guidage (28) présente un trou borgne (29) qui se situe pour l'essentiel dans l'axe de l'alésage axial (27) du piston d'actionnement (16).
  5. Soupape selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    le piston d'actionnement (16) présente pour l'essentiel la forme d'un cylindre étagé.
  6. Soupape selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    le piston d'actionnement (16) se déplace dans la direction opposée à la chambre de commande (14) lors d'un actionnement de l'unité l'actionneur (20).
  7. Soupape selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce que
    le piston d'actionnement (16) est précontraint dans la direction de la fermeture au moyen d'un ressort de pression (30) dans une chambre de ressort (31).
  8. Soupape selon la revendication 7,
    caractérisée en ce que
    la chambre de ressort (31) est en communication avec le canal de retour (26).
  9. Soupape selon l'une quelconque des revendications 1 à 8,
    caractérisée en ce qu'
    une soupape de surpression (33) est disposée dans le canal de retour (26).
  10. Soupape selon l'une quelconque des revendications 5 à 9,
    caractérisée en ce que
    la surface d'épaulement (34) du piston d'actionnement (16) en cylindre étagé forme la surface du piston d'actionnement (16) sur laquelle agit la pression que le piston de réglage (19) exerce sur le piston d'actionnement (16) au moyen de la chambre hydraulique (18).
  11. Soupape selon l'une quelconque des revendications 7 à 10,
    caractérisée en ce que
    la chambre de ressort (31) est reliée par un canal d'équilibrage de pression (41) à une chambre annulaire formée par une rainure annulaire (40) prévue à la surface périphérique du piston de réglage (19).
EP02729861A 2001-04-11 2002-04-09 Soupape pour commander le passage de fluides Expired - Lifetime EP1379775B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10118053 2001-04-11
DE10118053A DE10118053A1 (de) 2001-04-11 2001-04-11 Ventil zum Steuern von Flüssigkeiten
PCT/DE2002/001293 WO2002084106A1 (fr) 2001-04-11 2002-04-09 Soupape pour commander le passage de fluides

Publications (2)

Publication Number Publication Date
EP1379775A1 EP1379775A1 (fr) 2004-01-14
EP1379775B1 true EP1379775B1 (fr) 2006-05-10

Family

ID=7681212

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02729861A Expired - Lifetime EP1379775B1 (fr) 2001-04-11 2002-04-09 Soupape pour commander le passage de fluides

Country Status (5)

Country Link
US (1) US6843464B2 (fr)
EP (1) EP1379775B1 (fr)
JP (1) JP2004518906A (fr)
DE (2) DE10118053A1 (fr)
WO (1) WO2002084106A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE10162045B4 (de) * 2001-12-17 2005-06-23 Siemens Ag Vorrichtung zum Übersetzen einer Auslenkung eines Aktors, insbesondere für ein Einspritzventil
US7278593B2 (en) * 2002-09-25 2007-10-09 Caterpillar Inc. Common rail fuel injector
DE10250720A1 (de) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Einspritzventil
DE10333752A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333697A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333699A1 (de) * 2003-07-24 2005-03-03 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333692B3 (de) * 2003-07-24 2004-09-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333688B3 (de) * 2003-07-24 2004-08-26 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333689B3 (de) * 2003-07-24 2004-08-26 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333691B3 (de) * 2003-07-24 2004-08-26 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
US6983895B2 (en) * 2003-10-09 2006-01-10 Siemens Aktiengesellschaft Piezoelectric actuator with compensator
ATE487057T1 (de) 2004-02-25 2010-11-15 Ganser Hydromag Brennstoffeinspritzventil für verbrennungskraftmaschinen
CH697562B1 (de) * 2005-08-09 2008-11-28 Ganser Hydromag Brennstoffeinspritzventil.
US7891586B2 (en) * 2006-10-16 2011-02-22 Ganser-Hydromag Ag Fuel injection valve for internal combustion engines
DE102006049050A1 (de) * 2006-10-18 2008-04-30 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff
DE102006053128A1 (de) * 2006-11-10 2008-05-15 Robert Bosch Gmbh Injektor zum Einpritzen von Kraftstoff
DE102007017729A1 (de) * 2007-04-16 2008-10-23 Robert Bosch Gmbh Druckausgeglichenes Stellelement
DE102007029793A1 (de) * 2007-06-27 2008-07-17 L'orange Gmbh Kraftstoffinjektor
DE102008040454A1 (de) * 2008-07-16 2010-01-21 Robert Bosch Gmbh Kraftstoffeinspritzventileinrichtung
DE102009027261A1 (de) * 2009-06-29 2010-12-30 Robert Bosch Gmbh Brennstoffeinspritzventil
EP2647827B1 (fr) 2012-04-05 2015-06-10 Delphi International Operations Luxembourg S.à r.l. Ensemble de soupape non-retour
DE102015223043A1 (de) * 2015-11-23 2017-05-24 Robert Bosch Gmbh Kraftstoff-Injektor
CN108506264B (zh) * 2018-06-01 2023-11-24 江西海源复合材料科技股份有限公司 一种充液阀

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Publication number Priority date Publication date Assignee Title
US4560871A (en) * 1983-12-22 1985-12-24 Marquest Medical Products, Inc. Actuator for control valves and related systems
JPH0436062A (ja) * 1990-05-31 1992-02-06 Nippondenso Co Ltd 内燃機関の燃料噴射弁
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
DE19709794A1 (de) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
US5884848A (en) * 1997-05-09 1999-03-23 Cummins Engine Company, Inc. Fuel injector with piezoelectric and hydraulically actuated needle valve
DE19843534A1 (de) * 1998-09-23 2000-03-30 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19843578A1 (de) * 1998-09-23 2000-03-30 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19946828C1 (de) * 1999-09-30 2001-07-12 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten

Also Published As

Publication number Publication date
DE50206746D1 (de) 2006-06-14
JP2004518906A (ja) 2004-06-24
WO2002084106A1 (fr) 2002-10-24
US20030132410A1 (en) 2003-07-17
US6843464B2 (en) 2005-01-18
DE10118053A1 (de) 2002-10-24
EP1379775A1 (fr) 2004-01-14

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