EP1446571A1 - Soupape d'injection de carburant pour des moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour des moteurs a combustion interne

Info

Publication number
EP1446571A1
EP1446571A1 EP02767066A EP02767066A EP1446571A1 EP 1446571 A1 EP1446571 A1 EP 1446571A1 EP 02767066 A EP02767066 A EP 02767066A EP 02767066 A EP02767066 A EP 02767066A EP 1446571 A1 EP1446571 A1 EP 1446571A1
Authority
EP
European Patent Office
Prior art keywords
valve needle
valve
sealing edge
needle
row
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
EP02767066A
Other languages
German (de)
English (en)
Other versions
EP1446571B1 (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 EP1446571A1 publication Critical patent/EP1446571A1/fr
Application granted granted Critical
Publication of EP1446571B1 publication Critical patent/EP1446571B1/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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1866—Valve seats or member ends having multiple cones
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, 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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as it corresponds to the preamble of claim 1.
  • a fuel injection valve is known for example from published patent application DE 30 36 583 AI.
  • the fuel injection valve known from the prior art has a valve body with a bore formed therein. An outer valve needle is guided in the bore and an inner valve needle is in turn guided in the outer valve needle. Both valve needles work together with a valve seat that closes off the hole at the combustion chamber end. An outer and an inner row of injection openings are formed in the valve seat, the inner row of injection openings being controlled by the inner valve needle and the outer row of injection openings by the outer valve needle.
  • a longitudinal movement of the valve needles in the bore against a closing force either opens only the outer row of injection openings or both rows of injection ports simultaneously, so that fuel can flow to the injection openings, from where it is injected into the combustion chamber of the internal combustion engine.
  • Both the outer valve needle and the inner valve needle have on their valve sealing surfaces with which they are Valve seat, each have a sealing edge, which ensures that the pressure chamber is sealed against the respective row of injection openings.
  • this has the disadvantage that the injection valve does not sufficiently seal the two rows of injection openings against one another during the closed phase, in which no fuel is to escape through the injection openings.
  • combustion gases from the combustion chamber can penetrate into the space between the two valve needles as a so-called back-blowing.
  • fuel that is also between the valve needles during operation can leak into the combustion chamber and cause an increase in hydrocarbon emissions there.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that no leakage and thus no leakage of fuel between the injections is possible and that no combustion gases can penetrate into the fuel injection valve from the combustion chamber through the injection openings.
  • the outer valve needle has an inwardly projecting sealing lip which has an inner sealing edge. This inner sealing edge comes into contact with the valve seat in the closed position of the outer valve needle and thus seals the outer row of injection openings against the inner row of injection openings. Due to the inner sealing edge formed on the sealing lip, no fuel can get between the injections from the annular space through the injection openings and thus into the combustion chamber in an uncontrolled manner.
  • an annular space is formed between the outer valve needle and the inner valve needle, which is filled with fuel can be filled under high pressure.
  • the fuel in the annular space acts on the pressure surface formed on the inner valve needle, so that a force directed away from the valve seat is exerted on the inner valve needle.
  • the inner valve needle can be hydraulically controlled in a simple manner, the annular space being able to be implemented with little effort.
  • the outer valve needle is essentially hollow-cylindrical, and the pressure chamber is formed by a groove in the inner surface of the outer valve needle.
  • This design of the annulus is easy to manufacture and allows any design of the annulus in terms of volume and location.
  • it can advantageously be provided to connect the annular space to a pressure space via at least one bore formed in the outer valve needle, so as to fill the annular space with fuel under high pressure.
  • the sealing lip has a seat surface facing away from the valve, on which the inner valve needle comes to rest with a sealing surface in the closed position.
  • the outer valve needle has an additional outer sealing edge in addition to the inner sealing edge, which is arranged upstream of the inner sealing edge and also upstream of the outer row of injection openings.
  • the inner and outer sealing edges completely close the outer row of injection openings, so that no fuel flows through the outer row of injection openings can get into the combustion chamber in an uncontrolled manner. Conversely, no combustion gases can enter the fuel injector from the combustion chamber.
  • the sealing lip is designed such that when the outer valve needle closes, the inner sealing edge first comes into contact with the valve seat and only with the further closing movement with elastic deformation of the sealing lip does the outer sealing edge also come into contact.
  • the elastic deformation of the sealing lip increases the contact pressure on the inner sealing edge, so that in the case where only the inner valve needle lifts off the valve seat and thereby releases the inner row of injection openings, a secure seal on the inner sealing edge of the outer valve needle remains given is.
  • FIG. 2 shows an enlargement of the section from FIG. 1 and designated II
  • Figure 3 is an enlargement of Figure 2 in the area of the valve seat.
  • a fuel injector is shown in longitudinal section.
  • a bore 3 is made in a valve body 1. formed, the bore 3 is closed by a valve seat 10 which is substantially conical.
  • this valve seat 10 is arranged at the combustion-gray end of the bore 3.
  • An outer valve needle 5 is arranged in the bore 3, which is longitudinally displaceable there and is guided in a section of the bore 3 facing away from the combustion chamber.
  • a piston-shaped inner valve needle 7 is guided so as to be longitudinally displaceable, which has a longitudinal axis 2 which coincides with the longitudinal axis of the outer valve needle 5.
  • the outer valve needle 5 has at its end facing the valve seat 10 a substantially conical valve sealing surface 6, which comes into contact with the valve seat 10 in the closed position of the outer valve needle 5.
  • the inner valve needle 7 also has an essentially conical sealing surface 8, which also comes into contact with the valve seat 10 in the closed position.
  • a pressure shoulder 11 is formed facing the combustion chamber toward the guided section of the outer valve needle 5.
  • a pressure chamber 16 is formed between the outer valve needle 5 and the wall of the bore 3 and can be filled with fuel under high pressure via an inlet channel 18 formed in the valve body 1.
  • the pressure space 16 is expanded radially, so that the inlet channel 18 can be formed in the valve body 1 without weakening the guidance of the outer valve needle 5 in the bore 3 by an insufficient wall thickness between the bore 3 and the inlet channel 18 ,
  • a device can exert a closing force on the outer valve needle 5 and, independently thereof, on the inner valve needle 7, the respective closing force acting on both valve needles 5, 7 in the direction of the valve seat 10.
  • a longitudinal movement of the valve needles 5, 7 in the bore 3 takes place in that either the opening force on the outer valve needle 5, the hydraulic force on the pressure shoulder 11 is generated, the closing force exceeds the closing force due to the increasing pressure in the pressure chamber 16, or the closing force on the outer valve needle 5 is reduced when the fuel pressure in the pressure chamber 16 is at least approximately constant.
  • the longitudinal movement of the inner valve needle 7 can also be controlled according to the same principle.
  • FIG. 2 shows an enlargement of the section from FIG. 1, designated II.
  • a plurality of injection openings are formed which connect the valve seat 10 to the combustion chamber of the internal combustion engine.
  • the injection openings are in two rows of injection openings 12; 14 is arranged, the inner row of injection openings 12 being closer to the longitudinal axis 2 than the outer row of injection openings 14.
  • the inner valve needle 7 has at its end facing the combustion chamber a sequence of a conical surface 107, a first cylinder surface 117 adjoining it, and a second one which follows Cone surface 207, a subsequent second cylinder surface 217 and an adjoining third cone surface 307.
  • the opening angle of the third cone surface 307 is greater than the opening angle of the conical valve seat 10, so that a sealing edge 27 is formed at the transition from the second cylinder surface 217 to the third cone surface 307, which comes into contact with the valve seat 10 in the closed position of the inner valve needle 7.
  • the sealing edge 27 comes to bear upstream of the inner row of injection openings 12 on the valve seat 10, so that the sealing edge 27 can close the inner row of injection openings 12.
  • the outer valve needle 5 has a groove 19 near its end on the combustion chamber side, so that an annular space 20 is formed between the inner valve needle 7 and the outer valve needle 5.
  • the annular space 20 is connected to the pressure space 16 via a plurality of connection bores 22 distributed over the circumference of the outer valve needle 5, and thus the same pressure prevails in the annular space 20 as in the pressure chamber 16.
  • the end surface of the outer valve needle 5 on the combustion chamber side is approximately conical and, by means of an annular bead formed thereon, has an outer sealing edge 32 which closes the pressure chamber 16 against the outer row of injection openings 14 when it is in contact with the valve seat 10.
  • an inwardly projecting sealing lip 25 is formed, on which an inner sealing edge 30 is formed by an annular bead, which also comes into contact with the valve seat 10 in the closed position of the outer valve needle 5.
  • the inner sealing edge 30 and the outer sealing edge 32 are arranged in such a way that the outer sealing edge 32 is arranged upstream and the inner sealing edge 30 is arranged downstream of the outer row of injection openings 14, so that when the two sealing edges 30, 32 bear against the valve seat 10, the outer row of injection openings 14 is sealed.
  • the sealing lip 25 is elastically deformable and designed such that when the outer valve needle 5 lifted from the valve seat 10 closes, the inner sealing edge 30 first comes into contact with the valve seat 10 and only then does the outer sealing edge 32 also due to an elastic deformation of the sealing lip 25
  • the side of the sealing lip 25 facing away from the valve seat 10 is designed as a seat surface 26 which, when the inner valve needle 7 is in the closed position, on the second cone surface 207 serving as a sealing surface is applied. This results in an additional closing force on the sealing lip 25 and thus on the inner sealing edge 30, which reinforces the sealing effect of the inner sealing edge 30.
  • FIG. 3 shows an enlargement in the area of the valve seat 10 of FIG. 2.
  • the strengthening of the sealing effect on the inner sealing edge 30 of the sealing lip 25 is only given if the sealing lip 25 is sufficiently far inside NEN protrudes so that it rests on the second cone surface 207 in the closed position of the inner valve needle 7. If this reinforcement of the sealing effect on the inner sealing edge 30 is not desired, it can also be provided that the sealing lip 25 is shortened accordingly, so that there is no longer any contact with the inner valve needle 7.
  • the extension of the sealing lip 25 by the distance h thus allows the contact force and thus the sealing effect to be set on the inner sealing edge 30.
  • the fuel injector works as follows: If injection is to take place only through part of the injection openings, in this design example through the inner row of injection openings 12, fuel is introduced into the pressure chamber 16 under high pressure. By reducing the closing force on the inner valve needle 7, the hydraulic force on the first cone surface 107, which is designed as a pressure surface, results in an opening force on the inner valve needle 7 away from the valve seat 10, so that the sealing edge 27 lifts off the valve seat 10 and connects the annular space 20 with the inner row of injection openings 12. Due to a correspondingly high closing force on the outer valve needle 5, both the inner sealing edge 30 and the outer sealing edge 32 remain in contact with the valve seat 10 and thus keep the outer row of injection openings 14 closed.
  • the inner valve needle 7 continues its opening movement until it comes to rest against a stop, not shown in the drawing. If injection is to take place through the entire injection cross-section, the closing force on the outer valve needle 5 is also reduced, and the outer valve needle 5 first lifts off from the valve seat 10 with the outer sealing edge 32 and then also with the inner sealing edge 30, so that fuel now flows through both rows of injection openings 12, 14 is injected.
  • the fuel injection valve is closed in an analogous manner by increasing the closing force on the inner one Valve needle 7 and on the outer valve needle 5, it being possible to simultaneously reduce the pressure in the pressure chamber 16. As a result, both valve needles move back towards the valve seat 10 until they bear with the sealing edge 27 or with the inner sealing edge 30 and the outer sealing edge 32 on the valve seat 10. Due to the contact of the inner valve needle 7 with the conical surface 207 on the seat surface 26, the sealing lip 25 and thus also the inner sealing edge 30 are additionally pressed onto the valve seat 10.
  • the pressure in the combustion chamber between the individual injections is sometimes very high, so that combustion gases can penetrate into the fuel injection valve through the injection openings. In the present injection valve, this is effectively prevented by the inner injection opening row 12 being securely sealed by the inner valve needle 7 and the outer injection opening row 14 being sealed by two sealing edges, namely the inner sealing edge 30 and the outer sealing edge 32. Combustion chamber gases can neither get into the pressure chamber 16 nor into the annulus 20. Conversely, it is also not possible for fuel from the annular space 20 to get into the combustion chamber of the internal combustion engine in an uncontrolled manner through the injection openings and to result in increased hydrocarbon emissions there.

Landscapes

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

Abstract

L'invention concerne une soupape d'injection de carburant, comprenant un corps de soupape (1) dans lequel sont logés un pointeau de soupape extérieur (5) dans un alésage (3) ainsi qu'un pointeau de soupape intérieur (7), conduit dans le pointeau de soupape extérieur (5). Les pointeaux de soupape (5, 7) concourent avec un siège de soupape (10) qui est réalisé à l'extrémité côté chambre de combustion de l'alésage (3) et dans lequel sont placées une série extérieure d'orifices d'injection (14) et une série intérieure d'orifices d'injection (12). Le pointeau de soupape intérieur (7) commande l'ouverture de la série intérieure d'orifices d'injection (12) et le pointeau de soupape extérieur (5) commande l'ouverture de la série extérieure d'orifices d'injection (14). Le pointeau de soupape extérieur (5) présente une lèvre d'étanchéité périphérique (25) saillant vers l'intérieur et comprenant une arête d'étanchéité intérieure (30) qui vient s'appuyer sur le siège de soupape (10) dans la position de fermeture du pointeau de soupape extérieur (7).
EP02767066A 2001-11-09 2002-07-27 Soupape d'injection de carburant pour des moteurs a combustion interne Expired - Lifetime EP1446571B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10155227A DE10155227A1 (de) 2001-11-09 2001-11-09 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10155227 2001-11-09
PCT/DE2002/002776 WO2003040543A1 (fr) 2001-11-09 2002-07-27 Soupape d'injection de carburant pour des moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1446571A1 true EP1446571A1 (fr) 2004-08-18
EP1446571B1 EP1446571B1 (fr) 2005-04-06

Family

ID=7705287

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02767066A Expired - Lifetime EP1446571B1 (fr) 2001-11-09 2002-07-27 Soupape d'injection de carburant pour des moteurs a combustion interne

Country Status (4)

Country Link
EP (1) EP1446571B1 (fr)
JP (1) JP4191606B2 (fr)
DE (2) DE10155227A1 (fr)
WO (1) WO2003040543A1 (fr)

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10247958A1 (de) * 2002-10-15 2004-04-29 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
WO2004044414A1 (fr) * 2002-11-11 2004-05-27 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs à combustion interne
DE10315820A1 (de) * 2002-11-11 2004-05-27 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10305303A1 (de) * 2003-02-10 2004-08-19 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für Brennkraftmaschinen mit Kraftstoff-Direkteinspritzung
DE10306808A1 (de) * 2003-02-18 2004-09-02 Siemens Ag Injektor zum Einspritzen von Kraftstoff
DE10322826A1 (de) * 2003-05-19 2004-12-09 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
US7032566B2 (en) * 2003-05-30 2006-04-25 Caterpillar Inc. Fuel injector nozzle for an internal combustion engine
DE10351460A1 (de) * 2003-11-04 2005-06-09 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, sowie Verfahren zu deren Herstellung
DE10354878A1 (de) * 2003-11-24 2005-06-09 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung, sowie Verfahren zu ihrer Herstellung
ATE335925T1 (de) 2004-02-20 2006-09-15 Delphi Tech Inc Einspritzdüse
EP1566538B1 (fr) * 2004-02-20 2006-08-09 Delphi Technologies, Inc. Buse d'injection
DE102004011095A1 (de) * 2004-03-06 2005-09-22 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102004011096A1 (de) * 2004-03-06 2005-09-22 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102004021340A1 (de) * 2004-04-30 2005-11-24 Siemens Ag Düsenbaugruppe und Ventil
ATE388319T1 (de) * 2004-08-13 2008-03-15 Delphi Tech Inc Einspritzdüse
DE102004059974A1 (de) * 2004-11-23 2006-06-01 Siemens Ag Düsenbaugruppe und Einspritzventil
DE102005001675A1 (de) * 2005-01-13 2006-07-27 Siemens Ag Düsenbaugruppe und Einspritzventil
DE602005024510D1 (de) * 2005-03-04 2010-12-16 Delphi Tech Holding Sarl Einspritzdüse
DE102005037954A1 (de) * 2005-08-11 2007-02-15 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
JP4454567B2 (ja) * 2005-11-14 2010-04-21 株式会社デンソー 燃料噴射ノズル
DE102006041071A1 (de) * 2006-09-01 2008-03-06 Robert Bosch Gmbh Injektor zur Einspritzung von Kraftstoff in Zylinderbrennräume von Brennkraftmaschinen; insbesondere Common-Rail-Injektor
DE102012205840A1 (de) * 2012-04-11 2013-10-17 Continental Automotive Gmbh Injektor
GB201404131D0 (en) * 2014-03-10 2014-04-23 Delphi Int Operations Lux Srl Fuel injector
DE102014220928A1 (de) 2014-10-15 2016-04-21 Continental Automotive Gmbh Registerdüse zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine
JP2016205197A (ja) * 2015-04-21 2016-12-08 日立オートモティブシステムズ株式会社 燃料噴射装置
US10392987B2 (en) 2017-03-29 2019-08-27 Cummins Emission Solutions Inc. Assembly and methods for NOx reducing reagent dosing with variable spray angle nozzle
WO2018195894A1 (fr) * 2017-04-28 2018-11-01 浙江巴腾动力系统有限公司 Injecteur de carburant pour automobile

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Also Published As

Publication number Publication date
DE50202740D1 (de) 2005-05-12
EP1446571B1 (fr) 2005-04-06
JP4191606B2 (ja) 2008-12-03
WO2003040543A1 (fr) 2003-05-15
DE10155227A1 (de) 2003-05-22
JP2005508474A (ja) 2005-03-31

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