EP1608866B1 - Soupape d'injection de carburant de moteurs a combustion interne - Google Patents

Soupape d'injection de carburant de moteurs a combustion interne Download PDF

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Publication number
EP1608866B1
EP1608866B1 EP03770899A EP03770899A EP1608866B1 EP 1608866 B1 EP1608866 B1 EP 1608866B1 EP 03770899 A EP03770899 A EP 03770899A EP 03770899 A EP03770899 A EP 03770899A EP 1608866 B1 EP1608866 B1 EP 1608866B1
Authority
EP
European Patent Office
Prior art keywords
valve
needle
guide section
bore
fuel
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
EP03770899A
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German (de)
English (en)
Other versions
EP1608866A1 (fr
Inventor
Thomas Kuegler
Jochen Mertens
Hasiman ÜSKÜDAR
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 EP1608866A1 publication Critical patent/EP1608866A1/fr
Application granted granted Critical
Publication of EP1608866B1 publication Critical patent/EP1608866B1/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
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric 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
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known from DE 30 36 583 A1.
  • a fuel injection valve has a valve body in which a bore is formed.
  • the bore is delimited at its combustion chamber end by a valve seat, from which depart a plurality of injection openings, which are arranged in an outer and an inner rows of injection openings and open in the installation position of the fuel injection valve in an internal combustion engine, the injection openings in the combustion chamber.
  • a valve outer needle is arranged longitudinally displaceable, which is guided in a side facing away from the combustion chamber in the bore. Between the valve outer needle and the wall of the bore remains a pressure chamber, which can be filled with fuel under pressure.
  • valve outer needle cooperates with its end facing the combustion chamber with the valve seat for opening and closing the outer row of injection openings, so that either fuel is injected from the pressure chamber via these injection openings into the combustion chamber, or the connection from the pressure chamber to the injection openings is interrupted.
  • the valve outer needle has a longitudinal bore in which a valve inner needle is arranged to be longitudinally displaceable.
  • the valve inner needle also cooperates with its combustion chamber end with the valve seat for opening and closing the inner row of injection openings so that when the valve outer needle is open can be controlled by the valve inner needle, the opening of the inner row of injection openings, so that, depending on the control of the valve needles, fuel is injected into the combustion chamber only through one or both rows of injection openings.
  • the valve inner needle is guided in two guide sections in the longitudinal bore of the valve outer needle.
  • the first guide section is in this case arranged away from the combustion chamber to the second guide section, so that between the guide sections, bounded by the valve inner needle and the wall of the longitudinal bore, an annular gap is formed.
  • the two guide sections serve to prevent tilting of the valve inner needle while maintaining exact guidance in the longitudinal bore.
  • the opening of the valve inner needle is against a closing force by hydraulic loading of a valve sealing surface, which is formed at the combustion chamber facing the end of the valve inner needle.
  • valve sealing surface of the valve inner needle is acted upon by the fuel pressure of the pressure chamber and thus leads to an opening force on the valve inner needle, which in turn lifts from the valve seat and releases the inner row of injection openings.
  • the valve inner needle may open only with a certain delay.
  • this is only limited the case, since the valve sealing surface is acted on immediately after the lifting of the valve outer needle by the fuel pressure of the pressure chamber and is thus immediately set in motion.
  • the closing force can be selectively controlled, which is very expensive and thus usually too expensive.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that, using structurally simple means, the valve inner needle with a time delay over the valve outer needle lifts from the valve seat.
  • the annular space which is formed between the valve inner needle and the wall of the longitudinal bore, connectable via a throttle connection with the pressure chamber, wherein the diameter of the first guide portion is greater than the diameter of the second guide portion. This ensures that the pressure in the annular space results in a resultant force on the inner valve needle, which is directed away from the valve seat. Only when the hydraulic forces in the annulus and the hydraulic force on a corresponding surface on the combustion chamber end of the inner valve needle interact, the valve inner needle opens.
  • the throttle connection is formed by the annular gap remaining between the second guide section of the valve inner needle and the wall of the longitudinal bore.
  • the throttle connection is only connected by the lifting of the valve outer needle from the valve seat to the pressure chamber, so that it only comes to an inflow of fuel from the pressure chamber into the annulus and thus to an increase in pressure in the annulus .
  • the annular gap between the second guide portion and the longitudinal bore remains, a smaller flow resistance than the annular gap between the first guide portion and the wall of the longitudinal bore, so that it comes through the inflow of fuel to a rapid pressure increase in the annulus.
  • annular space is connected via the annular gap formed between the first guide portion and the wall of the longitudinal bore with a leakage oil space, so that in the injection pauses when both valve needles are again in contact with the valve seat, the fuel pressure in the annular space is reduced ,
  • the throttle connection of the annular space with the pressure chamber is formed by a transverse bore in the valve outer needle. This refinement is appropriate when the pressure in the pressure chamber is not constantly high fuel pressure, but only when an injection of fuel is to take place. Such a throttle connection can be produced more easily than a precisely dimensioned annular gap between the second guide section and the longitudinal bore of the valve outer needle.
  • lateral polished sections are formed on the second guide section.
  • valve 1 shows a fuel injection valve according to the invention is shown in longitudinal section.
  • a bore 3 is formed, at the combustion chamber end of which a conical valve seat 5 is formed, which delimits the bore 3. From the valve seat 5 go at least 2 injection ports 7, which open in installation position of the fuel injection valve in the combustion chamber of the internal combustion engine.
  • a valve outer needle 10 is arranged, at the combustion chamber end of which a valve sealing surface 18 is formed, which is also conically shaped and with which the valve outer needle 10 cooperates with the valve seat 5.
  • a pressure chamber 14 is formed, which is widened adjacent to the guided portion of the valve outer needle 10 radially.
  • the valve seat 5 is set to Pressure chamber 14 to the valve seat 5 on.
  • the pressure chamber 14 can be filled with fuel under high pressure in the region of its radial expansion via a feed channel extending in the valve body 1 and not shown in the drawing.
  • a pressure shoulder 11 is formed by the force due to the fuel pressure in the pressure chamber 14 a directed away from the valve seat 5 opening force on the valve outer needle 10 acts.
  • a longitudinal bore 15 is formed over its entire length, in which a likewise piston-shaped valve inner needle 12 is arranged to be longitudinally displaceable.
  • the valve inner needle 12 has a valve sealing surface 20, with which it interacts with the valve seat 5.
  • the inner valve needle 12 has a first guide section 24 and a second guide section 25 arranged facing the valve seat 5 and with which the inner valve needle 12 is guided in the longitudinal bore 15. Between the guide portions 24, 25, bounded by the valve inner needle 12 and the wall of the longitudinal bore 15, an annular space 22 is formed, which is filled with fuel.
  • the valve inner needle 12 has at its combustion chamber end a pressure surface 26 which is acted upon by the fuel of the pressure chamber 14 when the valve outer needle 10 has lifted from the valve seat 5.
  • valve outer needle 10 and valve inner needle 12 are shown in more detail with the valve seat 5.
  • the injection openings 7 are arranged in an outer injection opening row 107 and an inner row of injection openings 207 located closer to the combustion chamber, the rows of injection openings 107, 207 each comprising a plurality of injection openings 7 which extend over the circumference of the valve body 1 are arranged distributed.
  • the valve outer needle 10 and the valve inner needle 12 lie with their sealing surfaces 18, 20 on the valve seat 5 and close both the outer Einspritzö Maschinens Herbert 107 and the inner Einspritzö Maschinens Herbert 207.
  • valve outer needle 10 and the inner valve needle 12 by a in the drawing device, not shown, acted upon by a closing force acting in the direction of the valve seat 5 and so presses both valve pins 10, 12 against the valve seat 5.
  • the devices for generating the closing force are, for example, springs which each act on a valve needle 10, 12. If only the valve outer needle 10 lifts away from the valve seat 5, fuel can pass from the pressure chamber 14 to the outer injection opening row 107 and is injected from there into the combustion chamber of the internal combustion engine. If the valve inner needle 12 also moves away from the valve seat 5, it releases the inner injection opening row 207 and the fuel is injected through both the outer injection opening row 107 and the inner injection opening row 207.
  • FIG. 3 shows an enlargement of FIG. 1 in the region of the first guide section 24 of the inner valve needle 12.
  • the first guide section 24 is formed by a radial extension of the valve inner needle 12.
  • the diameter of the first guide section 24 is greater than the diameter of the second guide section 25, which is possible for example by a longitudinal bore 25 stepped in diameter.
  • the ring shoulder 29 formed on the combustion chamber facing the end of the first guide section 24 thereby has a larger, in the longitudinal direction of the valve inner needle 12 effective hydraulic surface than the shoulder 27 on the second guide section 25. This results from the fuel pressure in the annular space 22, a resulting hydraulic force on the valve inner needle 12, which is directed away from the valve seat 5.
  • the annular space 22 is connected through the annular gap, which is formed between the first guide portion 24 of the valve inner needle 12 and the wall of the longitudinal bore 15, with a leakage oil space, not shown in the drawing, in which there is always a low fuel pressure. This ensures that a high fuel pressure in the annular space 22 is relieved after a certain time via this annular gap and thus assumes the low fuel pressure in the leakage oil space.
  • the operation of the fuel injection valve is as follows: In the operating mode, in which constantly high fuel pressure in the pressure chamber 14 is applied, the injection of fuel is initiated by a reduction of the closing force on the valve outer needle 10. As a result, the hydraulic force now predominates on the pressure shoulder 11 of the valve outer needle 10 and on parts of the valve sealing surface 18, so that the valve outer needle 10 lifts off from the valve seat 5 and opens the outer injection opening row 107 in the manner described above. As a result, the pressure surface 26 is now acted upon by the fuel pressure on the inner valve needle 12, which is not sufficient to allow the valve inner needle 12 to lift off the valve seat 5 counter to the closing force acting on it.
  • the closing force is increased to the valve outer needle 10 and this slides back into its closed position, ie in contact with the valve seat 5.
  • the pressure in the annular space 22 builds up on the annular gap between the first guide portion 24 and Wall of the bore 15 is formed in the leakage oil from, so that after a certain time, the closing force on the valve inner needle 12 exceeds the opening forces and the valve inner needle 12 also slides back to its closed position.
  • the closing force on the inner valve needle 12 is variable and at the same time increased or decreased with the closing force on the valve outer needle 10, it may also be the case that the inner valve needle 12 closes in front of the valve outer needle 10.
  • the entire injection process takes place here in injection valves, as used for high-speed internal combustion engines, within a few milliseconds.
  • the fuel injection valve In the operating mode of the fuel injection valve, in which the pressure in the pressure chamber 14 is not constantly constant, but only increased when an injection is to take place, the fuel injection valve operates in the same manner, however, the closing force on the valve outer needle 10 remains constant. Due to the rising fuel pressure in the pressure chamber 14, the opening force on the pressure shoulder 11 and the valve sealing surface 18 is increased until it is greater than the closing force and the valve outer needle 10 opens. The opening of the valve inner needle 12 is carried out in the manner described above, as soon as this through the open valve outer needle 10 connection to the pressure chamber 14 has. To end the injection of the pressure chamber 14 is relieved, so that the hydraulic pressure on the valve needles 10,12 is eliminated. Depending on the size of the closing forces, the valve inner needle 12 or the valve outer needle 10 first moves back into the closed position.
  • FIG. 4 shows the same detail as FIG. 2 of a further exemplary embodiment.
  • the inflow of fuel into the annulus 22 be at the necessary rate to achieve the pressure rise in the desired time.
  • the remaining between the second guide portion 25 and the wall of the longitudinal bore 15 annular gap which is only very narrow, preferably 2-3 microns, this is not sufficient, it may be provided that on the second guide portion 25 bevels 32 are formed over the an extension of the throttle connection from the annular space 22 to the pressure chamber 14 is possible.
  • the flow resistance can be set arbitrarily at this point.
  • the opening speed is also influenced by the ratio of the diameters of the first guide section 24 and the second guide section 25: If the valve inner needle 12 moves away from the valve seat 5 with the valve outer needle 10 stationary, the volume of the annular space 22 increases. This acts on the pressure build-up by the fuel, which penetrates through the annular gap 28 into the annular space 22, counter, so that the opening speed of the valve inner needle 12 is reduced.
  • the annular gap 28 is also used for the opening dynamics of the valve needles 10, 12 in addition to the throttle bore 35.
  • the pressure in the annular space 22 increases via the throttle bore 35.
  • an opening force on the inner valve needle 12 and, on the other hand, a closing closing force on the valve seat 5 on the valve outer needle 10 result from the diameter difference between the first Guide section 24 and the second guide section 25. This increases the opening pressure on the valve outer needle 10, which thus lifts only when a higher pressure in the pressure chamber 14 from the valve seat 5 is reached.
  • the pressure in the annular space 22 now also increases by inflow of fuel through the annular gap 28 until the hydraulic forces are sufficient to open the valve inner needle 12.
  • the pressure build-up in the annular space 22 and thus the opening dynamics of the valve needles 10, 12 depends here on the coordination between the cross section of the throttle bore 35 and that of the annular gap 28.

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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)

Claims (9)

  1. Injecteur de carburant de moteurs à combustion interne, comportant un corps de soupape (1) avec un perçage (3) délimité sur son extrémité côté chambre de combustion par un siège de soupape (5) d'où partent au moins deux orifices d'injection (7), et une aiguille extérieure (10) dans le perçage (3) mobile longitudinalement pour ouvrir ou fermer avec son extrémité côté chambre de combustion au moins un orifice d'injection (7), avec une chambre de pression (14) pouvant être remplie de carburant entre l'aiguille de soupape extérieure (10) et la paroi du perçage (3), et l'aiguille de soupape extérieure (10) présentant un alésage longitudinal (15) logeant une aiguille interne (12) mobile longitudinalement qui ouvre ou ferme avec son extrémité côté chambre de combustion au moins un orifice d'injection (7) en étant guidée dans l'alésage longitudinal (15) par un premier (24) et un deuxième segment de guidage (25) disposé par rapport à celui-ci côté siège soupape, et avec une chambre annulaire (22) délimitée par l'aiguille de soupape interne (12) et la paroi de l'alésage longitudinal (15) entre les segments de guidage (24 ; 25),
    caractérisé en ce que
    la chambre annulaire (22) peut être reliée à la chambre de pression par une liaison d'étranglement (28 ; 35), le diamètre du premier segment de guidage (24) étant supérieur à celui du deuxième segment de guidage (25).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la liaison d'étranglement (28 ; 35) est formée par la fente annulaire (28) restant entre le deuxième segment de guidage (25) de l'aiguille interne (12) et la paroi de l'alésage longitudinal (15).
  3. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    la fente annulaire restant entre la paroi de l'alésage longitudinal (15) et le premier segment de guidage (24) présente une résistance plus faible au débit que la fente annulaire (28) entre le deuxième segment de guidage (25) et la paroi de l'alésage longitudinal (15).
  4. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    des coupes polies latérales (32) sont formées sur le deuxième segment de guidage (25).
  5. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la liaison d'étranglement (28 ; 35) est commandée par l'aiguille de soupape extérieure (10).
  6. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    les segments de guidage (24 ; 35) sont réalisés par un élargissement du diamètre de l'aiguille de soupape interne (12).
  7. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la liaison d'étranglement (28 ; 35) est un perçage d'étranglement (35) dans l'aiguille extérieure (12) qui relie la chambre annulaire (22) à la chambre de pression (14).
  8. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    l'alésage longitudinal (15) a un diamètre étagé.
  9. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la chambre annulaire (22) peut être reliée à une chambre d'huile de fuite par la fente annulaire formée entre le premier segment de guidage (24) et la paroi de l'alésage longitudinal (15).
EP03770899A 2003-03-21 2003-10-06 Soupape d'injection de carburant de moteurs a combustion interne Expired - Lifetime EP1608866B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10312586 2003-03-21
DE10312586A DE10312586A1 (de) 2003-03-21 2003-03-21 Kraftstoffeinspritzventil für Brennkraftmaschinen
PCT/DE2003/003304 WO2004085824A1 (fr) 2003-03-21 2003-10-06 Soupape d'injection de carburant de moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1608866A1 EP1608866A1 (fr) 2005-12-28
EP1608866B1 true EP1608866B1 (fr) 2006-08-09

Family

ID=32921045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03770899A Expired - Lifetime EP1608866B1 (fr) 2003-03-21 2003-10-06 Soupape d'injection de carburant de moteurs a combustion interne

Country Status (6)

Country Link
US (1) US20060196973A1 (fr)
EP (1) EP1608866B1 (fr)
JP (1) JP4126047B2 (fr)
CN (1) CN100400851C (fr)
DE (2) DE10312586A1 (fr)
WO (1) WO2004085824A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004060552A1 (de) * 2004-12-16 2006-06-22 Robert Bosch Gmbh Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE102005046665A1 (de) * 2005-09-29 2007-04-05 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
MX2011011420A (es) 2009-04-30 2012-02-13 Nissan Motor Dispositivo de control y metodo de control de transmision continuamente variable, basada en banda.
CN102305162A (zh) * 2011-08-19 2012-01-04 中国兵器工业集团第七○研究所 柴油机的喷油嘴偶件
DE102012203607A1 (de) * 2012-03-07 2013-09-12 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
GB201309122D0 (en) 2013-05-21 2013-07-03 Delphi Tech Holding Sarl Fuel Injector
DE102019205943A1 (de) * 2019-04-25 2020-10-29 Robert Bosch Gmbh Injektor zur dosierten Abgabe von zwei unterschiedlichen Fluiden und Verfahren zum Betreiben eines solchen Injektors

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3036583A1 (de) * 1980-09-27 1982-05-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzduese
US5899389A (en) * 1997-06-02 1999-05-04 Cummins Engine Company, Inc. Two stage fuel injector nozzle assembly
GB9813476D0 (en) * 1998-06-24 1998-08-19 Lucas Ind Plc Fuel injector
DE69922087T2 (de) * 1998-06-24 2005-12-01 Delphi Technologies, Inc., Troy Brennstoffeinspritzdüse
GB9905231D0 (en) * 1999-03-09 1999-04-28 Lucas Ind Plc Fuel injector
EP2003323B1 (fr) * 1999-10-06 2010-06-30 Delphi Technologies Holding S.à.r.l. Injecteur de carburant
DE10122241A1 (de) * 2001-05-08 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Also Published As

Publication number Publication date
US20060196973A1 (en) 2006-09-07
WO2004085824A1 (fr) 2004-10-07
DE10312586A1 (de) 2004-09-30
JP4126047B2 (ja) 2008-07-30
CN1759236A (zh) 2006-04-12
DE50304621D1 (de) 2006-09-21
JP2006511756A (ja) 2006-04-06
EP1608866A1 (fr) 2005-12-28
CN100400851C (zh) 2008-07-09

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