EP1606511B1 - Dispositif d'injection de carburant pour moteur a combustion interne - Google Patents

Dispositif d'injection de carburant pour moteur a combustion interne Download PDF

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Publication number
EP1606511B1
EP1606511B1 EP03815794A EP03815794A EP1606511B1 EP 1606511 B1 EP1606511 B1 EP 1606511B1 EP 03815794 A EP03815794 A EP 03815794A EP 03815794 A EP03815794 A EP 03815794A EP 1606511 B1 EP1606511 B1 EP 1606511B1
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EP
European Patent Office
Prior art keywords
space
spring
pump
fuel
pressure
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
EP03815794A
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German (de)
English (en)
Other versions
EP1606511A1 (fr
Inventor
Gérard Duplat
Raphael Pourret
Alain Amblard
Raphael Combe
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1606511A1 publication Critical patent/EP1606511A1/fr
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Publication of EP1606511B1 publication Critical patent/EP1606511B1/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
    • F02M61/16—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
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with 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
    • 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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 198 44 891 A.
  • This fuel injection device has a high-pressure fuel pump and a fuel injection valve for a cylinder of the internal combustion engine.
  • the high-pressure fuel pump has a pump piston, which is driven by the internal combustion engine and delimits a pump working chamber, wherein a connection of the pump working chamber to a discharge region is controlled by an electrically controlled valve.
  • the fuel injection valve has an injection valve member through which at least one injection port is controlled and which is movable in an opening direction by the pressure prevailing in a pressure chamber having a connection with the pump working space against the force of a closing spring arranged in a spring chamber.
  • the closing spring is supported on the one hand at least indirectly on the injection valve member and on the other hand at least indirectly on a storage piston.
  • the storage piston limits on its side facing away from the closing spring a storage space which has a connection with the pump working space and is movable against the force of the closing spring in the spring chamber.
  • the spring chamber has a connection with a low-pressure region via a throttle point, wherein the low-pressure region is connected to a fuel feed.
  • the storage piston allows pre-injection of fuel by this is moved with increasing pressure in the pump chamber by the pressure prevailing in the storage space pressure in the spring chamber. With increasing pressure in the pump chamber and thus in the pressure chamber of the fuel injection valve whose injection valve member opens first for the pilot injection.
  • the bias of the closing spring and the pressure prevailing in the spring chamber pressure is increased, so that the injection valve member closes again.
  • the injection valve member opens against the increased bias of the closing spring and there is a main injection of fuel.
  • the amount of fuel that is injected during the pilot injection is specified in a characteristic field dependent on operating parameters of the internal combustion engine, in particular the rotational speed. It has been found that the fuel injection quantity in the pre-injection is substantially influenced by pressure fluctuations in the spring chamber, which in turn are caused by pressure fluctuations in the low-pressure region.
  • EP 0 844 384 A1 discloses a fuel injection device which has a high-pressure fuel pump and a fuel injection valve for a cylinder of an internal combustion engine.
  • the fuel injection valve has an injection valve member, is controlled by the at least one injection port and which is loaded by a closing spring.
  • the closing spring is arranged in a spring chamber, which is connected via a throttle point with a low pressure region.
  • the throttle point is arranged approximately in the middle of the longitudinal extent of the spring chamber and opens into a narrow gap between a valve body and a surrounding housing part, wherein the gap forms a channel which is connected to the low-pressure region.
  • the channel thus has only a small length, so that pressure fluctuations in the low-pressure region may be transmitted to the spring chamber.
  • the fuel injection device with the features of claim 1 has the advantage that pressure fluctuations in the spring chamber by the connection of the spring chamber with the low pressure region over the channel of great length, which thereby forms a damping chamber are reduced, and thus more accurately adhered to the fuel injection amount in the pilot injection can be.
  • FIG. 1 shows a fuel injection device for an internal combustion engine in a first longitudinal section
  • Figure 2 shows the fuel injection device in a second longitudinal section
  • Figure 3 shows the fuel injection device in a cross section along line III-III in Figure 1.
  • FIGS. 1 to 3 show a fuel injection device for an internal combustion engine of a motor vehicle.
  • the internal combustion engine has one or more cylinders, wherein a fuel injection device with a high-pressure fuel pump 10 and a fuel injection valve 12 is provided for each cylinder.
  • the high-pressure fuel pump 10 and the fuel injection valve 12 are combined to form a so-called pump-nozzle unit.
  • the high-pressure fuel pump 10 has a pump body 14, in which in a cylinder 16, a pump piston 18 is guided tightly, which is driven by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19 in a lifting movement.
  • the pump piston 18 defines in the cylinder 16 a pump working chamber 22 in which the delivery stroke of the pump piston 18 compresses fuel under high pressure.
  • the pump working chamber 22 18 fuel during a suction stroke of the pump piston 18 is supplied from a fuel tank 24, for example by means of a feed pump 21.
  • the pump chamber 22 has a connection with a discharge area, as can serve as a return to the fuel tank 24, and that of an electrically operated Control valve 23 is controlled.
  • the control valve 23 is connected to an electronic control device 25.
  • the fuel injection valve 12 has a valve body 26, which may be designed in several parts, and which is connected to the pump body 14, for example with the interposition of at least one intermediate body 27. Between the intermediate body 27 and the pump body 14, a disk 15 may be arranged.
  • an injection valve member 28 is guided longitudinally displaceably in a bore 30.
  • the bore 30 extends at least approximately parallel to the cylinder 16 of the pump body 14, but may also extend inclined thereto.
  • the valve body 26 At its end region facing the combustion chamber of the cylinder of the internal combustion engine, the valve body 26 has at least one, preferably a plurality of injection openings 32.
  • the injection valve member 28 has at its end region facing the combustion chamber, for example, a conical sealing surface 34 which cooperates with a in the valve body 26 in the end region facing the combustion chamber, for example, also approximately conical valve seat 36, from or after the discharge the injection ports 32.
  • annular space 38 is present between the injection valve member 28 and the bore 30 toward the valve seat 36, which merges in its end region remote from the valve seat 36 by a radial widening of the bore 30 into a pressure chamber 40 surrounding the injection valve member 28.
  • the injection valve member 28 has at the level of the pressure chamber 40 by a cross-sectional reduction on the valve seat 36 facing the pressure shoulder 42.
  • a prestressed closing spring 44 At the end remote from the combustion chamber of the injection valve member 28 engages a prestressed closing spring 44, through which the injection valve member 28 is pressed to the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 formed by a bore 47 of a spring-holding body 45, which forms part of the valve body 26 and which adjoins the bore 30.
  • the pressure space 40 has a connection 48 extending through the valve body 26, the disks 43, the spring holding body 45, the intermediate body 27, the disk 15 and the pump body 14 with the pump working space 22.
  • the closing spring 44 is supported on the one hand at least indirectly, for example via a spring plate, on the injection valve member 28 and on the other hand at least indirectly, for example also via a spring plate, on a storage piston 50.
  • the accumulator piston 50 is guided in a coaxial with the spring chamber 46 subsequent bore 51 in the intermediate body 27 and limited with its closing spring 44 facing away from the end face in the bore 51 a storage space 52.
  • the storage space 52 has a through the intermediate body 27, the disc 15th and the pump body 14 extending connection 54 with the pump working chamber 22.
  • the valve body 26 and the pump body 14 are connected and clamped together by means of a clamping nut 60 with the interposition of the spring holding body 45, the intermediate body 27 and the disc 15.
  • the clamping nut 60 engages over the valve body 26 and is screwed onto an external thread formed on the pump body 14.
  • an annular space 62 is formed between the clamping nut 60 and the valve body 26 is at the level of the pressure chamber 40 and the bore 30 in which the injection valve member 28 is tightly guided.
  • an annular space 62 is formed between the clamping nut 60 and the valve body 26 is at the level of the pressure chamber 40 and the bore 30 in which the injection valve member 28 is tightly guided.
  • the clamping nut 60 has in the region of the annular space 62 in its periphery a plurality of openings 64, each having a small cross-section, which form filter openings.
  • the clamping nut 60 is surrounded in the region of the annular space 62 on its outer side by a further annular space 66 which is formed between the clamping nut 60 and a bore 68 in a cylinder head of the internal combustion engine, in which the fuel injection device is inserted.
  • a fuel feed from the feed pump 21 opens forth.
  • the fuel supplied by the feed pump 21 passes through the filter openings 64 in the annular space 62 and from there via channels 70 in the discs 43, in the spring holder body 45, in the intermediate body 27, in the disc 50 and in the pump body 14 in a valve chamber 72 of the control valve 23rd
  • the valve chamber 72 can optionally be connected to the pump working chamber 22, depending on the switching position, and can be separated from the pump working chamber 22.
  • the valve chamber 72 also has a connection with a return to the fuel tank 24.
  • the annular space 62 forms a low-pressure region with which the spring chamber 46 is connected.
  • a channel 76 in the form of a bore, which extends along the spring chamber 46, is formed in the spring holding body 45.
  • the channel 76 continues through the discs 43 and opens into the annular space 62.
  • the channel 76 ends on the other hand on the intermediate body 27.
  • the spring chamber 46 is connected to the channel 76 via a throttle point 78 which is disposed near the storage piston 50 facing the end of the spring chamber 46.
  • the channel 76 thus extends from the storage piston 50 facing end portion of the spring chamber 46 to the annular space 62 and has a large length.
  • the low-pressure region 62 is arranged in the direction of the longitudinal axis 13 of the fuel injection valve 12 at a distance from the spring chamber 46.
  • the spring chamber 46 is thus connected via the long channel 76 with the low-pressure region forming annular space 62, wherein the channel 76 forms a damping chamber, are attenuated in the pressure fluctuations in the annular space 62, so that they lead only to small pressure fluctuations in the spring chamber 46.
  • the pump working chamber 22 is filled with fuel during the suction stroke of the pump piston 18 when the control valve 23 is open.
  • the pumped by the feed pump 21 fuel passes into the annular space 66, passes through the filter openings 64 through into the annular space 62 and passes from this through the channels 70 in the valve chamber 72 and from this into the pump working chamber 22.
  • the control valve 23 is initially opened, so that no high pressure can build up in the pump working chamber 22.
  • the control valve 23 is closed by the control device 25, so that the pump chamber 22 is separated from the valve chamber 72 and thus from the fuel inlet and the return to the fuel tank 24 and builds up in this high pressure.
  • the injection valve member 28 moves in the opening direction 29 and releases the at least one injection opening 32, is injected through the fuel into the combustion chamber of the cylinder.
  • the accumulator piston 50 is in this case in an initial position in which this is arranged closest to the disc 15. The pressure in the pump working chamber 22 subsequently increases according to the profile of the cam 20 on.
  • the accumulator piston 50 performs an evasive stroke movement and moves away from the disc 15 into the spring chamber 46 into, the storage space 52 is increased.
  • an increase in pressure in the spring chamber 46 is caused because of this because of the throttle point 78 only delayed fuel can flow out, and also increases the bias of the closing spring 44, which is supported on the accumulator piston 50.
  • the fuel injection valve 12 Due to the pressure increase in the spring chamber 46 and the increase in the bias of the closing spring 44 results in an increased force in the closing direction of the injection valve member 28 so that it is moved back in the closing direction, comes with its sealing surface 34 on the valve seat 36 to the plant and the injection ports 32 closes so that the fuel injection is interrupted.
  • the fuel injection valve 12 is open only for a short period of time and it is injected only a small amount of fuel as a pilot injection into the combustion chamber. The amount of fuel injected depends inter alia on the pressure prevailing in the spring chamber 46, which generates a force acting in the closing direction on the injection valve member 28 as indicated above.
  • the opening stroke of the injection valve member 28 during the pilot injection may be hydraulically limited by a damper.
  • the injection valve member 28 dives with a pressure pin 80 in a fuel-filled damping chamber 82 which is bounded by a formed by an end face of the disc 43 stationary shoulder 84, which forms a stroke stop for an annular shoulder 86 on the injection valve member 28.
  • a throttle cross-section is formed between the wall of the damping chamber 82 and the pressure pin 80, which is formed as administratnanschliff 88 and via which the damping chamber 82 is connected to the spring chamber 46.
  • the foundednanschliff 88 on the pressure pin 80 has an axial distance to the annular shoulder 86 on the injection valve member 28, in the region of the thrust pin 80 corresponds to the diameter of the bore in the disc 43, so that a control edge 90 is formed, the driving over the paragraph 84 the driving of the hydraulic damping chamber 82 controls.
  • the Preinjection passes through the injection valve member 28 only a sectionö réelleshub which is limited by passing over the control edge 90 on the injection valve member 28 via the shoulder 84 of the disc 43, as a result, the damping chamber 82 is controlled, so that the closing force on the injection valve member 28 increases.
  • the pressure in the pump working chamber 22 subsequently continues to rise in accordance with the profile of the cam 20, so that the force acting on the injection valve member 28 compressive force in the opening direction 29 increases again and exceeds due to the increased bias of the closing spring 44 and the increased pressure in the spring chamber 46 increased closing force, so that the fuel injection valve 12 opens again.
  • a larger amount of fuel is injected over a longer period of time than during the pilot injection.
  • the time duration and the amount of fuel injected during this main injection are determined by the time at which the control valve 23 is opened again by the control device 25.
  • the pump chamber 22 is again connected to the return to the fuel tank 24 so that it is relieved and the fuel injection valve 12 closes.
  • the storage piston 50 is moved back by the force of the closing spring 44 back to its original position.

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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 (2)

  1. Installation d'injection de carburant d'un moteur à combustion interne comportant une pompe haute pression de carburant (10) et un injecteur (12) pour un cylindre du moteur à combustion interne,
    la pompe haute pression de carburant (10) ayant un piston de pompe (18) entraîné par le moteur à combustion interne et délimitant une chambre de travail de pompe (22),
    une soupape à commande électrique (23) qui commande au moins indirectement la communication entre la chambre de travail (22) et une zone de décharge (24),
    l'injecteur de carburant (12) ayant au moins un organe d'injection (28) qui commande au moins un orifice d'injection (32) et qui est déplacé dans le sens de l'ouverture (29),par la pression régnant dans une chambre de pression (40) ayant une liaison (48) avec la chambre de travail de pompe (22), contre la force d'un ressort de fermeture (44) installé dans une chambre à ressort (46),
    le ressort de fermeture (44) ayant une extrémité appuyée au moins indirectement contre l'organe de soupape (28) et l'autre extrémité au moins indirectement contre un piston accumulateur coulissant (50) qui délimite sur son côté opposé au ressort de fermeture (44), une chambre d'accumulation (52) ayant une liaison (54) avec la chambre de travail (22) et qui est mobile contre la force du ressort de fermeture (44) de la chambre à ressort (46) sous l'effet de la pression régnant dans la chambre d'accumulation (52),
    la chambre à ressort (46) ayant une liaison (76) par un point d'étranglement (78) avec une zone basse pression (62) reliée à l'arrivée de carburant et à la zone de décharge (24),
    caractérisée en ce que
    la liaison de la chambre à ressort (46) avec la zone basse pression (62) est réalisée par un canal (76) en forme de perçage,
    le canal (76) s'étend le long de la chambre à ressort (46) de l'extrémité tournée vers le piston accumulateur (50) au moins jusqu'à son extrémité à l'opposé du piston accumulateur (50),
    la chambre à ressort (46) étant reliée par le point d'étranglement (78) à la zone d'extrémité du canal (76) tournée vers le piston accumulateur (50) alors qu'à son extrémité opposée tournée vers le piston accumulateur (50), le canal (76) débouche dans la zone basse pression (62), et
    la zone basse pression (62) est réalisée sous la forme d'un volume annulaire entourant le corps de soupape (26) de l'injecteur (12), dans la direction de l'axe longitudinal (13) de l'injecteur (12), à distance de la chambre à ressort (46), sensiblement à la hauteur de la chambre de pression (40) de l'injecteur (12).
  2. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la zone basse pression (62) est réalisée entre le corps de soupape (26) et un écrou de serrage (60) entourant celui-ci,
    l'écrou de serrage (60) relie le corps de soupape (26) au corps de pompe (14) de la pompe à haute pression de carburant (10), et l'écrou de serrage (60) a dans sa périphérie, plusieurs orifices (74) reliant la zone basse pression (62) à l'alimentation en carburant.
EP03815794A 2003-03-17 2003-10-18 Dispositif d'injection de carburant pour moteur a combustion interne Expired - Lifetime EP1606511B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10311522 2003-03-17
DE2003111522 DE10311522A1 (de) 2003-03-17 2003-03-17 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
PCT/DE2003/003495 WO2004083624A1 (fr) 2003-03-17 2003-10-18 Dispositif d'injection de carburant pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1606511A1 EP1606511A1 (fr) 2005-12-21
EP1606511B1 true EP1606511B1 (fr) 2007-06-06

Family

ID=32920829

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03815794A Expired - Lifetime EP1606511B1 (fr) 2003-03-17 2003-10-18 Dispositif d'injection de carburant pour moteur a combustion interne

Country Status (3)

Country Link
EP (1) EP1606511B1 (fr)
DE (2) DE10311522A1 (fr)
WO (1) WO2004083624A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3017905B1 (fr) * 2014-02-24 2018-12-07 Delphi International Operations Luxembourg S.A R.L. Injecteur de carburant

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9624513D0 (en) * 1996-11-26 1997-01-15 Lucas Ind Plc Injector
DE19844891A1 (de) * 1998-09-30 2000-04-06 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10124511A1 (de) * 2001-05-19 2002-11-21 Volkswagen Ag Verfahren zum Steuern eines Kraftstoff-Einspritzsystems
DE10141678A1 (de) * 2001-08-25 2003-05-08 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Also Published As

Publication number Publication date
WO2004083624A1 (fr) 2004-09-30
DE10311522A1 (de) 2004-09-30
EP1606511A1 (fr) 2005-12-21
DE50307438D1 (de) 2007-07-19

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