EP1731754A1 - Méthode de fabrication d'un injecteur - Google Patents

Méthode de fabrication d'un injecteur Download PDF

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Publication number
EP1731754A1
EP1731754A1 EP06114885A EP06114885A EP1731754A1 EP 1731754 A1 EP1731754 A1 EP 1731754A1 EP 06114885 A EP06114885 A EP 06114885A EP 06114885 A EP06114885 A EP 06114885A EP 1731754 A1 EP1731754 A1 EP 1731754A1
Authority
EP
European Patent Office
Prior art keywords
valve
bellows
spring
effective cross
sectional area
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
EP06114885A
Other languages
German (de)
English (en)
Other versions
EP1731754B1 (fr
Inventor
Claus Anzinger
Willibald SCHÜRZ
Martin Simmet
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.)
Continental Automotive GmbH
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1731754A1 publication Critical patent/EP1731754A1/fr
Application granted granted Critical
Publication of EP1731754B1 publication Critical patent/EP1731754B1/fr
Expired - Fee Related 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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps

Definitions

  • the invention relates to a method for producing a valve which comprises a valve body, a valve needle and a valve spring and which has a bellows for sealing a high-pressure region with respect to a low-pressure region of the valve.
  • a valve for direct injection of fuel into a combustion chamber of a gasoline engine has a valve needle which is axially movable out of its closed position for metering the fuel.
  • Fuel flow through the valve is dictated by a stroke of the valve needle, a diameter of a seat of the valve needle in the valve, and a fuel pressure in the valve.
  • the valve needle is held in its closed position by a spring force of a valve spring and a hydraulic force component resulting from the fuel pressure when the valve needle is not moved out of its closed position by a lift actuator of the valve.
  • a stroke of the Hubaktors, and thus the stroke of the valve needle is dependent on an axial force which counteracts a displacement of the Hubaktors and must be overcome to open the valve by the Hubaktor.
  • the stroke of the lifting actuator is dependent on a control of the Hubaktors.
  • the object of the invention is to provide a method for producing a valve in which a dispersion of an axial force for actuating the valve is low.
  • the invention is characterized by a method of manufacturing a valve comprising a valve body, a valve needle and a valve spring. Furthermore, the valve has a bellows for sealing a high-pressure region with respect to a low-pressure region of the valve.
  • a variable representing a hydraulically effective cross-sectional area of the bellows is determined.
  • the valve spring is selected based on its spring force depending on the size representing the hydraulically effective cross-sectional area of the bellows.
  • the valve needle is disposed in the valve body and is coupled via the valve spring and the bellows with the valve body to open the valve by means of a predetermined axial force acting on the valve needle, depending on a prevailing in the low pressure range or the high pressure area fluid pressure to close.
  • the predetermined axial force can be achieved particularly precisely and with small scattering. Thereby, the predetermined axial force can be reliably adjusted for all valves produced by this method. An additional calibration step for setting the predetermined axial force is thus not required after assembly of the valve. A desired flow through the valve can be achieved so easily and reliably without having to consider an individually required axial force for opening or closing the valve for driving the valve.
  • the invention is characterized by a method of manufacturing a valve comprising a valve body, a valve needle and a valve spring.
  • the valve further includes a bellows for sealing a high pressure region from a low pressure region of the valve.
  • a spring force of the valve spring is determined.
  • the bellows is selected relative to a variable representing its hydraulically effective cross-sectional area, depending on the spring force of the valve spring.
  • the valve needle is placed in the valve body. Further, the valve needle is coupled via the valve spring and the bellows with the valve body, that the valve by means of a predetermined axial force acting on the valve needle, depending on a prevailing in the low pressure region or the high pressure area fluid pressure to open or close.
  • the predetermined axial force can be achieved particularly precisely and with low scattering. Thereby, the predetermined axial force can be reliably adjusted for all valves produced by this method. An additional calibration step for setting the predetermined axial force is thus not required after assembly of the valve. The desired flow through the valve can be achieved so easily and reliably, without having to consider the individually required axial force for opening or closing the valve for driving the valve.
  • the size representing the hydraulically effective cross-sectional area of the bellows is an outer diameter of the bellows. This is based on the finding that due to the manufacturing process of the bellows essentially only the Outer diameter of the bellows has a relevant deviation from a target value of the outer diameter and other sizes of the bellows, such as an inner diameter or a thickness or stiffness of the material of the bellows, substantially correspond to their respective setpoint. Thus, the hydraulically effective cross-sectional area of the bellows is substantially dependent on its outer diameter. As a result, determining the size representing the hydraulically effective cross-sectional area of the bellows is particularly simple, since the outside diameter of the bellows can be determined very easily.
  • a valve for example an injection valve for an internal combustion engine, comprises a valve body 1, in which a valve needle 2 is arranged (FIG. 1).
  • a valve cover 3 is tightly secured, for example by welding, the has a fluid inlet 4 and which separates a high-pressure region of the valve within the valve body 1 from a low-pressure region of the valve outside of the valve body 1.
  • a fluid such as fuel
  • the fluid is supplied at a high fluid pressure, eg 200 bar.
  • a first fastening ring 5 is tightly secured, e.g. by welding.
  • the valve needle 2 is arranged axially movable in the first fastening ring 5.
  • a second fastening ring 6 is fixed, e.g. by pressing on.
  • a bellows 7, which is preferably formed as a metal bellows, is fastened with a first axial end to the first fastening ring 5 and with a second axial end to the second fastening ring 6, e.g. by welding.
  • a valve spring 8 between the valve body 1 and a spring plate 9 is further arranged.
  • the spring plate 9 is coupled to the second fastening ring 6.
  • a spring force F3 of the valve spring 8 acts on the valve needle 2 such that it is drawn into a valve seat 10 of the valve body 1 and thus closes the valve.
  • a Hubaktor 11 is disposed in the low pressure region of the valve.
  • the Hubaktor 11 is formed for example as a piezoelectric actuator and is designed so that the valve needle 2 is movable axially out of its closed position as a function of electrical actuation of the lifting actuator 11 against the spring force F3.
  • a stroke of Hubaktors 11, and thus a stroke of the valve needle 2 is dependent on the control of the Hubaktors 11 and an axial force which counteracts a deflection of the Hubaktors 11 and which is directed so that the valve needle 2 in its closed position is pulled.
  • a hydraulically effective cross-sectional area of the bellows 7 is dependent on the hydraulically effective diameter D1 of the bellows 7.
  • the hydraulically effective diameter D1 of the bellows 7 and the hydraulically effective cross-sectional area of the bellows 7 are particularly dependent on an outer diameter of the bellows 7, but can also be dependent on a different size of the bellows 7. Due to the manufacturing process of the bellows 7, the hydraulically effective cross-sectional area of the bellows 7 can essentially only be dependent eg on its outer diameter. The outer diameter of the bellows 7 is then a hydraulically effective cross-sectional area of the bellows 7 representing size.
  • the size representing the hydraulically effective cross-sectional area of the bellows 7 may also be, for example, the hydraulically effective cross-sectional area of the bellows 7 or the hydraulically effective diameter D1 of the bellows 7.
  • the hydraulic effective size representing cross-sectional area and a relationship with the hydraulically effective cross-sectional area for a type or design of the bellows 7 determined experimentally, so that by means of representing the hydraulically effective cross-sectional area size simply on the hydraulically effective cross-sectional area of the respective bellows 7 of this type or this design can be closed.
  • a mathematical derivation of the relationship is optionally also possible for the type or design of the bellows 7.
  • the high fluid pressure e.g. several tens or a hundred bar.
  • the low fluid pressure e.g. less than ten bar.
  • a hydraulically opening force F2 acts on the valve needle 2 of the hydraulically closing force F1 depending on the fluid pressure in the high-pressure region of the valve and depending on a sealing circle diameter D2 of the valve seat 10 (FIG. 3).
  • the hydraulic closing force F1 and the hydraulic opening force F2 are preferably coordinated so that the hydraulic closing force F1 is at least as large as the hydraulic opening force F2. This ensures that even with increasing fluid pressure in the high pressure region of the valve, the valve needle 2 is pressed into its closed position in the valve seat 10 and thus the valve closes reliable and tight.
  • the valve spring 8 ensures that the valve remains closed even when the fluid pressure in the high-pressure region of the valve is very low, for example during a pause in the operation of the valve.
  • the hydraulically effective cross-sectional area of the bellows 7 or the spring force F3 of the valve spring 8 for each bellows 7 produced or for each manufactured valve spring 8 may be different.
  • a balance of the spring force F3, the hydraulic closing force F1 and the hydraulic opening force F2 can vary from valve to valve.
  • the axial force which the lifting actuator 11 has to apply in order to be able to move the valve needle 2 out of its closed position can also vary accordingly. Since the stroke of Hubaktors 11 is also dependent on the force acting on the Hubaktor 11 axial force, thus, at a predetermined control of the Hubaktors 11 and an opening degree of the valve vary.
  • an injection amount of the fluid is dependent on the sealing circle diameter D2 and the opening degree of the valve.
  • the injection quantity of the fluid can accordingly also vary accordingly.
  • the outer diameter of the bellows 7 may differ by about 0.2 millimeters from its nominal value. This can lead to a deviation of the axial force by e.g. about 20 to 30 Newtons lead.
  • the axial force acting on the lifting actuator 11 must be approximately the same for each injection valve. This can be achieved by selecting a suitable combination of the valve spring 8 with respect to its spring force F3 and the bellows 7 with respect to its hydraulically effective cross-sectional area during the assembly of the valve or its size representing the hydraulically effective cross-sectional area.
  • FIG. 4 shows a flow chart of a first method for producing the valve.
  • the method starts in a step S1.
  • the variable representing the hydraulically effective cross-sectional area of the bellows 7 is determined, e.g. the outer diameter of the bellows 7 or the hydraulically effective diameter D1 of the bellows 7.
  • the valve spring 8 is selected based on their spring force F3, depending on the size representing the hydraulically effective cross-sectional area of the bellows 7.
  • the spring force F3 of the valve spring 8 is chosen to be larger, the smaller the hydraulically effective cross-sectional area of the bellows 7. Accordingly, the spring force F3 of the valve spring 8 is selected to be smaller, the larger the hydraulically effective cross-sectional area of the bellows 7.
  • the selection is preferably carried out automatically, for example by means of a control program.
  • the control program has, for example, access to the respective spring force F3 of the valve springs 8 available for mounting the valve.
  • the control program determines, for example from the variable representing the hydraulically effective cross-sectional area of the bellows 7 that valve spring 8 whose spring force F3 cooperates with the hydraulically effective cross-sectional area of the bellows 7 representing size leads to the axial force which deviates as little as possible from the predetermined axial force.
  • the bellows 7 and the valve spring 8 correspond to two parallel springs whose spring forces add up.
  • an axial force to act on the valve needle 2 can be given.
  • step S4 the valve needle 2 is arranged in the valve body 1 and coupled via the valve spring 8 and the bellows 7 with the valve body 1, that to open the valve by means of the predetermined axial force depending on the prevailing in the low pressure region or the high pressure fluid pressure or close.
  • step S5. the valve needle 2 is arranged in the valve body 1 and coupled via the valve spring 8 and the bellows 7 with the valve body 1, that to open the valve by means of the predetermined axial force depending on the prevailing in the low pressure region or the high pressure fluid pressure or close.
  • FIG. 5 shows a flowchart of a second method for producing the valve, which starts in a step S6.
  • the spring force F3 of the valve spring 8 is determined.
  • the bellows 7 is selected based on the variable representing its hydraulically effective cross-sectional area.
  • the selection takes place in such a way that the hydraulically effective cross-sectional area of the bellows 7 is selected to be greater, the smaller the spring force F3 of the valve spring 8, and the smaller the larger the spring force F3 of the valve spring 8 is.
  • the selection is preferably carried out automatically, for example by means of the control program.
  • the control program has, for example, access to the respective hydraulically effective
  • the control program determines, for example from the spring force F3 that bellows 7, the hydraulically effective cross-sectional area representing size in cooperation with the spring force F3 leads to the axial force, the predetermined axial force deviates as little as possible.
  • valve needle 2 is arranged in the valve body 1 and coupled via the valve spring 8 in the bellows 7 so with the valve body 1 that the valve by means of the predetermined axial force acting on the valve needle 2, depending on the in the Low pressure range or the high pressure area prevailing fluid pressure to open or close is.
  • the method ends in a step S10.
  • the two methods for producing the valve make it possible to produce a plurality of valves which can be actuated with the same predetermined axial force, without having to perform an individual calibration with respect to the predetermined axial force after the assembly of the respective valve. Further, the determination of the spring force F3 of the valve spring 8 or the size representing the hydraulically effective cross-sectional area of the bellows 7 and the selection of the proper combination of the valve spring 8 and the bellows 7 for setting the predetermined axial force can be easily automated.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Lift Valve (AREA)
  • Fluid-Driven Valves (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20060114885 2005-06-06 2006-06-02 Méthode de fabrication d'un injecteur Expired - Fee Related EP1731754B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510025952 DE102005025952B4 (de) 2005-06-06 2005-06-06 Verfahren zum Herstellen eines Ventils

Publications (2)

Publication Number Publication Date
EP1731754A1 true EP1731754A1 (fr) 2006-12-13
EP1731754B1 EP1731754B1 (fr) 2010-03-31

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Family Applications (1)

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EP20060114885 Expired - Fee Related EP1731754B1 (fr) 2005-06-06 2006-06-02 Méthode de fabrication d'un injecteur

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EP (1) EP1731754B1 (fr)
DE (2) DE102005025952B4 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2290221A1 (fr) * 2009-07-08 2011-03-02 Robert Bosch GmbH Dispositif d'injection de carburant
EP2366888A1 (fr) * 2010-03-17 2011-09-21 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection, soupape d'injection et procédé pour assembler un ensemble de soupape d'une soupape d'injection
WO2012048999A3 (fr) * 2010-10-14 2012-08-16 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2013075876A1 (fr) * 2011-11-24 2013-05-30 Robert Bosch Gmbh Soupape de dosage d'un milieu en écoulement
EP3037650A1 (fr) * 2014-12-22 2016-06-29 Continental Automotive GmbH Ensemble de soupape et soupape d'injection de fluide
WO2017060154A1 (fr) * 2015-10-07 2017-04-13 Continental Automotive Gmbh Injecteur de fluide conçu pour faire fonctionner un véhicule automobile, et procédé de production d'un injecteur de fluide

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102380754B (zh) * 2011-05-05 2014-01-22 金龙精密铜管集团股份有限公司 一种空调用波纹集气管路件的生产方法
EP2568155B1 (fr) 2011-09-09 2018-11-14 Continental Automotive GmbH Ensemble de soupape et soupape d'injection

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4141274A1 (de) * 1991-12-14 1993-06-17 Frantisek Sobkovcik Vorrichtung zum einspritzen von kraftstoff
EP1079099A2 (fr) * 1999-08-24 2001-02-28 Siemens Aktiengesellschaft Soupape de dosage
US6311950B1 (en) * 1999-04-20 2001-11-06 Siemens Aktiengesellschaft Fluid metering device
US20040004139A1 (en) * 2000-11-02 2004-01-08 Bernhard Fischer Fluid dosing device with a throttle point
US20040011892A1 (en) * 2001-07-09 2004-01-22 Gunther Hohl Fuel injection valve

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10250720A1 (de) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Einspritzventil
DE10344880A1 (de) * 2003-09-26 2005-04-14 Robert Bosch Gmbh Brennstoffeinspritzventil

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4141274A1 (de) * 1991-12-14 1993-06-17 Frantisek Sobkovcik Vorrichtung zum einspritzen von kraftstoff
US6311950B1 (en) * 1999-04-20 2001-11-06 Siemens Aktiengesellschaft Fluid metering device
EP1079099A2 (fr) * 1999-08-24 2001-02-28 Siemens Aktiengesellschaft Soupape de dosage
US20040004139A1 (en) * 2000-11-02 2004-01-08 Bernhard Fischer Fluid dosing device with a throttle point
US20040011892A1 (en) * 2001-07-09 2004-01-22 Gunther Hohl Fuel injection valve

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2290221A1 (fr) * 2009-07-08 2011-03-02 Robert Bosch GmbH Dispositif d'injection de carburant
EP2366888A1 (fr) * 2010-03-17 2011-09-21 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection, soupape d'injection et procédé pour assembler un ensemble de soupape d'une soupape d'injection
WO2011113746A1 (fr) * 2010-03-17 2011-09-22 Continental Automotive Gmbh Ensemble clapet pour clapet d'injection, clapet d'injection et procédé d'assemblage d'un ensemble clapet d'un clapet d'injection
US9046066B2 (en) 2010-03-17 2015-06-02 Continental Automotive Gmbh Valve assembly for an injection valve, injection valve and method for assembling a valve assembly of an injection valve
WO2012048999A3 (fr) * 2010-10-14 2012-08-16 Robert Bosch Gmbh Dispositif d'injection de carburant
JP2013539838A (ja) * 2010-10-14 2013-10-28 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング 燃料噴射装置
WO2013075876A1 (fr) * 2011-11-24 2013-05-30 Robert Bosch Gmbh Soupape de dosage d'un milieu en écoulement
CN103930667A (zh) * 2011-11-24 2014-07-16 罗伯特·博世有限公司 用于定量配给流动介质的阀
US9822750B2 (en) 2011-11-24 2017-11-21 Robert Bosch Gmbh Valve for metering in a flowing medium
EP3037650A1 (fr) * 2014-12-22 2016-06-29 Continental Automotive GmbH Ensemble de soupape et soupape d'injection de fluide
WO2016102237A1 (fr) * 2014-12-22 2016-06-30 Continental Automotive Gmbh Ensemble de soupape et soupape d'injection de fluide
WO2017060154A1 (fr) * 2015-10-07 2017-04-13 Continental Automotive Gmbh Injecteur de fluide conçu pour faire fonctionner un véhicule automobile, et procédé de production d'un injecteur de fluide

Also Published As

Publication number Publication date
DE102005025952A1 (de) 2006-12-07
DE502006006550D1 (de) 2010-05-12
EP1731754B1 (fr) 2010-03-31
DE102005025952B4 (de) 2009-01-29

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