WO2004079181A1 - Soupape d'injection de carburant pour un moteur a combustion interne - Google Patents

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

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Publication number
WO2004079181A1
WO2004079181A1 PCT/DE2003/003494 DE0303494W WO2004079181A1 WO 2004079181 A1 WO2004079181 A1 WO 2004079181A1 DE 0303494 W DE0303494 W DE 0303494W WO 2004079181 A1 WO2004079181 A1 WO 2004079181A1
Authority
WO
WIPO (PCT)
Prior art keywords
injection valve
pressure
valve member
chamber
injection
Prior art date
Application number
PCT/DE2003/003494
Other languages
German (de)
English (en)
Inventor
Matthias Schnell
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
Priority to EP03775070A priority Critical patent/EP1601870A1/fr
Publication of WO2004079181A1 publication Critical patent/WO2004079181A1/fr

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
    • 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
    • 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
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric 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
    • F02M61/16—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 relates to a fuel injection valve for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection valve is known from DE 101 41 678 AI.
  • This fuel injection valve has two injection valve members, a second injection valve member being slidably guided in a hollow first injection valve member.
  • the first injection valve member controls at least one first injection opening and the second injection valve member controls at least one second injection opening.
  • the injection valve members each have a sealing surface with which they interact with a valve seat for controlling the injection openings.
  • the fuel injection valve has a pressure chamber connected to a high-pressure source, the first injection valve member being acted upon by the pressure prevailing in the pressure chamber against a closing force in an opening direction to release the at least one first injection opening.
  • the pressure prevailing in the pressure chamber can also move the second injection valve member against a closing force in an opening direction to release the at least one second injection opening.
  • Injection valve member is connected to a control piston which delimits a control chamber, the pressure in the control chamber causing a pressure in the control piston Opening direction acting on the second injector member force is generated.
  • the pressure prevailing in the control chamber is variably set in order to enable a variable opening pressure of the second injection valve member.
  • the diameter of the injection valve members is limited due to the limited space available on the internal combustion engine, the second injection valve member having a small diameter and in the closed position, when this is in contact with the valve seat with its sealing surface, only a small area is acted upon by the pressure prevailing in the pressure chamber , During the operation of the fuel injector, the sealing surface and / or the valve seat can wear, which leads to the pressure area of the second injection valve member changing, which in turn leads to a substantial change in the opening pressure of the second injection valve member because of the small area. It is then no longer guaranteed that the second injection valve member opens in the required manner and the amount of fuel injected can no longer be precisely controlled.
  • the fuel injection valve according to the invention with the features according to claim 1 has the advantage that in addition to the small area present on the second injection valve member, which is acted upon by the pressure in the pressure chamber, there is a further area acted upon by the same pressure as in the pressure chamber, so that the opening pressure of the second injection valve member is only to a lesser extent dependent on the size of the area on the second injection valve member that changes as a function of wear.
  • the opening pressure of the second injection valve member is only to a lesser extent dependent on the size of the area on the second injection valve member that changes as a function of wear.
  • FIG. 2 in an enlarged representation a section of the fuel injection device designated by II in FIG. 1
  • FIG. 3 in an enlarged representation a section of the fuel injection device designated by III in FIG. 1 according to a second exemplary embodiment
  • FIG. 4 shows a stroke profile of injection valve members over time.
  • a fuel injection valve 12 is shown, which is part of a
  • Fuel injection device for an internal combustion engine for example a motor vehicle.
  • the internal combustion engine is preferably a self-igniting
  • the fuel injection device can be designed, for example, as a so-called pump-nozzle system or as a pump-line-nozzle system and has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to each cylinder of the internal combustion engine.
  • the high-pressure fuel pump 10 is arranged away from the fuel injection valve 12 and connected to it via a line.
  • the fuel injection valve 12 can also be part of a
  • the fuel injection device is designed as a pump-nozzle system, the high-pressure fuel pump 10 and the fuel injection valve 12 being connected directly to one another are and form a structural unit.
  • the high-pressure fuel pump 10 has a pump piston 18 which is tightly guided in a cylinder bore 16 in a pump body 14 and is driven in a lifting movement by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19.
  • the pump piston 18 delimits a pump working chamber 22 in the cylinder 16, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18.
  • fuel from a fuel reservoir 24 of the motor vehicle is supplied to the pump working chamber 22 in a manner not shown in detail.
  • the fuel injection valve 12 has a valve body 26, which can be constructed in several parts, in which a first injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30.
  • the valve body 26 has at least one first, preferably a plurality of first injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine, which are arranged distributed over the circumference of the valve body 26.
  • the first injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the first injection openings 32 lead away.
  • valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which in its end region facing away from the valve seat 36 merges into a pressure space 40 surrounding the first injection valve member 28 by radial expansion of the bore 30.
  • the first injection valve member 28 has a reduction in cross section at the level of the pressure chamber 40
  • first prestressed closing spring 44 At the end facing away from the combustion chamber of the first injection valve member 28 engages directly or via an intermediate piece a first prestressed closing spring 44, by which the first injection valve member 28 is pressed toward the valve seat 36.
  • the first closing spring 44 is arranged in a first spring chamber of the valve body 26 which is formed by a bore 46 and which adjoins the bore 30.
  • the first injection valve member 28 of the fuel injection valve 12 is hollow and a second injection valve member 128 is slidably guided in a bore formed coaxially in the injection valve member 28.
  • the second injection valve member 128 controls at least one second injection opening 132 in the valve body 26.
  • the at least one second injection opening 132 is offset in the direction of the longitudinal axis of the injection valve members 28, 128 to the at least one first injection opening 32 toward the combustion chamber.
  • the second injection valve member 128 has, for example, an approximately conical sealing surface 134 on its end region facing the combustion chamber, which cooperates with a valve seat 136 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the second injection openings 132 lead away.
  • the second injection valve member 128 can be formed in two parts and have a part which has the sealing surface 134 and faces the combustion chamber and a second part which adjoins the first part away from the combustion chamber. Near the end of the second injection valve member 128 on the combustion chamber side, a pressure surface 142 is formed thereon, outside of the valve seat 136, on which the pressure prevailing in the pressure chamber 40 acts when the first injection valve member 28 is open.
  • FIGS. 1 and 3 Shown in the valve body 26 is a bore 146 which forms a second spring chamber and in which a second closing spring 144 acting on the second injection valve member 128 is arranged.
  • the diameter of the bore 146 forming the second spring chamber is somewhat smaller than that of the bore 46 forming the first spring chamber.
  • the end of the first injection valve member 28 projects into the first spring chamber and is supported on the first closing spring 144 in this.
  • the first closing spring 44 is supported with its end facing away from the first injection valve member 28 on a partition wall 47 arranged between the bore 46 forming the first spring chamber and the bore 146 forming the second spring chamber.
  • the second injection valve member 128 protrudes from the first injection valve member 28 with a push rod, which can be formed in one piece with the injection valve member 128 or as a separate part, and extends through the first spring chamber and through a bore 45 formed in the partition 47 with a smaller diameter in the bore 146.
  • the bore 146 forming the second spring chamber is larger in diameter than the bore 45.
  • a control piston 147 Arranged in the bore 146 is a control piston 147 which is connected to the push rod of the second injection valve member 128 or is formed integrally therewith, through which a control piston 147 enters the bore 146 toward the partition wall 47
  • Control room 50 is limited.
  • the push rod of the second injection valve member 128 is tightly guided in the bore 45, so that the control chamber 50 is separated from the first spring chamber.
  • the second closing spring 144 engages on the side of the control piston 147 facing away from the control chamber 50.
  • the second closing spring 144 is supported on the bottom of the second spring chamber with its end facing away from the control piston 147.
  • the space 148 delimited by the control piston 147 on the side facing away from the control space 50, in which the second closing spring 144 is arranged, has a connection 145 with a low-pressure area, for example with a return to the fuel reservoir 24.
  • a channel 48 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 into the pressure chamber 40 of the fuel injection valve 12.
  • An electrically controlled valve 23 controls a connection of the pump work chamber 22 to a relief chamber, such as the fuel reservoir 24 or at least indirectly, for example Area can serve in which a slightly higher pressure than the fuel tank 24 is maintained.
  • a relief chamber such as the fuel reservoir 24 or at least indirectly, for example Area can serve in which a slightly higher pressure than the fuel tank 24 is maintained.
  • the connection of the pump work chamber 22 to the relief chamber is opened by the control valve 23 controlled by an electronic control device 54, so that no high pressure can build up in the pump work chamber 22.
  • the control valve 23 separates the pump work chamber 22 from the relief chamber, so that high pressure can build up in the pump work chamber 22 during the delivery stroke of the pump piston 18.
  • the control valve 23 can be designed as a solenoid valve or as a piezo valve.
  • the control chamber 50 is connected to the channel 48, so that the pressure in the control chamber 50 is the same as in the pressure chamber 40 of the fuel injection valve 12.
  • the first injection valve member 28 is open, that is to say with its sealing surface 34 is lifted off the valve seat 36, the pressure surface is 142 of the second injection valve member 128 is acted upon by the pressure prevailing in the pressure chamber 40, by means of which a force is generated in the opening direction 29 on the second injection valve member 128 in accordance with the size of the pressure surface 142.
  • annular surface 149 of the control piston 147 delimiting the control chamber 50 is also of the pressure prevailing in the control chamber 50, which is the same as the pressure prevailing in the pressure chamber 40 is acted upon, by means of which a force in the opening direction 29 on the second injection valve member 128 is likewise generated in accordance with the size of the annular surface 149 of the control piston 147.
  • the annular surface 149 of the control piston 147 is larger than the pressure surface 142 of the second injection valve member 128. In the closing direction, the second injection valve member 128 acts on the second closing spring 144 and one in the space
  • the control valve 23 is opened so that fuel reaches the pump working chamber 22 from the fuel reservoir 24.
  • the start of the fuel injection is determined by the control valve 23 closing, so that the pump work chamber 22 is separated from the relief chamber and high pressure builds up in the pump work chamber 22.
  • the fuel injection valve 12 opens by the the first injection valve member 28 lifts with its sealing surface 34 from the valve seat 36 and the at least one first injection opening 32 opens.
  • the closing force exerted in the closing direction by the second closing spring 144 and the closing force exerted on the second injection valve member 128 in the chamber 148 is greater than the pressure prevailing in the pressure chamber 40 over the pressure surface 142 and the pressure prevailing in the control chamber 50 over the ring surface
  • FIG. 4 shows the course of the stroke h of the two injection valve members 28, 128 over the time t during an injection cycle. The stroke of the first
  • Injection valve member 28 is shown in solid lines and the stroke of second injection valve member 128 is shown in dashed lines.
  • the pre-injection is denoted by A and it can be seen that only the first injection valve member 28 opens and as a result only a small amount of fuel is injected.
  • the pilot injection is ended by the control valve 23 opening, so that the pressure in the pressure chamber 40 drops.
  • the control valve 23 is closed again, so that the pressure in the pump work chamber 22 rises again in accordance with the profile of the cam 20.
  • the first injection valve member 28 opens and opens the first injection openings 32.
  • the pressure prevailing in the pressure chamber 40 acts on the pressure surface 142 of the second injection valve member 128 and when the pressure prevailing in the pressure chamber 40 and in the control chamber 50 acts on the second in the opening direction 29 via the surfaces 142 and 149 Injection valve member 128 is greater than the force acting on it in the closing direction, the second injection valve member 128 also opens and opens the second injection openings 132.
  • the entire injection cross section of the fuel injection valve 12 Approved.
  • the opening movement of the second injection valve member 128 and thus the release of the second injection openings 132 takes place after the opening stroke movement of the first injection valve member 28 and the release of the first injection openings 32, as shown in FIG. 4 for the main injection designated B.
  • the control valve 23 is opened so that the pressure in the pressure chamber 40 and in the control chamber 50 drops and the injection valve members 28, 128 close.
  • the injection cross sections formed by the first injection openings 32 and the second injection openings 132 are at least approximately the same size, so that when only the first injection valve member 28 is opened, half of the total
  • Injection cross section is released.
  • the first injection openings 32 form a smaller or larger injection cross section than the second injection openings 132.
  • a throttle point 150 is arranged in the connection 145 of the space 148 to the low-pressure region.
  • the throttle point 150 allows fuel to be displaced only with a delay during the opening stroke movement of the second injection valve element 128, as a result of which the opening stroke movement of the second injection valve element 128 is damped. This results in a greater delay in the opening stroke movement of the second injection valve member 128 compared to the opening stroke movement in the first
  • the fuel injector 12 is shown in detail according to a second embodiment, in which the basic structure is the same as in the first embodiment, but the space 148 in addition to its connection 145 with the
  • Low-pressure area also has a connection 160 with the pump work chamber 22, a throttle point 162 being arranged in the connection 160.
  • the connection 160 of the space 148 to the pump working space 22 increases the force acting on the second injection valve member 128 in the closing direction in addition to the force of the second closing spring 144, as a result of which the opening and closing behavior of the second injection valve member 128 can be influenced.

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 qui comprend deux éléments de soupape d'injection (28, 128), le deuxième élément de soupape d'injection (128) étant guidé déplaçable dans le premier élément de soupape d'injection creux (28). Le premier élément de soupape d'injection (28) commande, en coopération avec un siège de soupape (36), au moins un premier orifice d'injection (32) au moyen d'une surface d'étanchéité (34) située sur l'élément et le deuxième élément de soupape d'injection (128) commande, en coopération avec un siège de soupape (136), au moins un deuxième orifice d'injection (132) au moyen d'une surface d'étanchéité (134) située sur l'élément. La soupape d'injection de carburant selon l'invention comprend également une chambre de pression (40) reliée à une source haute pression (10, 22). Les éléments de soupape d'injection (28, 128) sont mis sous pression par la pression régnant dans la chambre de pression (40) lorsqu'ils sont en position de fermeture contre une surface de pression (42, 142) et peuvent être déplacés à l'encontre d'une force de fermeture dans un sens d'ouverture (29). On associe au deuxième élément de soupape d'injection (128) un piston de commande (147) qui délimite une chambre de commande (50) et qui exerce une force en sens d'ouverture (29) sur le deuxième élément de soupape d'injection (128) au moyen de la pression régnant dans la chambre de commande (50). La chambre de commande (50) est reliée à la source haute pression (10, 22).
PCT/DE2003/003494 2003-03-03 2003-10-18 Soupape d'injection de carburant pour un moteur a combustion interne WO2004079181A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03775070A EP1601870A1 (fr) 2003-03-03 2003-10-18 Soupape d'injection de carburant pour un moteur a combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10309078.9 2003-03-03
DE2003109078 DE10309078A1 (de) 2003-03-03 2003-03-03 Kraftstoffeinspritzventil für eine Brennkraftmaschine

Publications (1)

Publication Number Publication Date
WO2004079181A1 true WO2004079181A1 (fr) 2004-09-16

Family

ID=32864037

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/003494 WO2004079181A1 (fr) 2003-03-03 2003-10-18 Soupape d'injection de carburant pour un moteur a combustion interne

Country Status (4)

Country Link
EP (1) EP1601870A1 (fr)
CN (1) CN1756903A (fr)
DE (1) DE10309078A1 (fr)
WO (1) WO2004079181A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008040881A1 (de) * 2007-08-10 2009-02-26 Robert Bosch Gmbh Kompakte Einspritzvorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4285471A (en) * 1977-03-16 1981-08-25 Robert Bosch Gmbh Fuel injection nozzle
DE4115477A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE10058130A1 (de) * 2000-11-22 2002-05-23 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10141678A1 (de) * 2001-08-25 2003-05-08 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4285471A (en) * 1977-03-16 1981-08-25 Robert Bosch Gmbh Fuel injection nozzle
DE4115477A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE10058130A1 (de) * 2000-11-22 2002-05-23 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10141678A1 (de) * 2001-08-25 2003-05-08 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Also Published As

Publication number Publication date
CN1756903A (zh) 2006-04-05
DE10309078A1 (de) 2004-09-16
EP1601870A1 (fr) 2005-12-07

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