WO2004057177A1 - Systeme d'injection de carburant pour moteur a combustion - Google Patents

Systeme d'injection de carburant pour moteur a combustion Download PDF

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Publication number
WO2004057177A1
WO2004057177A1 PCT/DE2003/004156 DE0304156W WO2004057177A1 WO 2004057177 A1 WO2004057177 A1 WO 2004057177A1 DE 0304156 W DE0304156 W DE 0304156W WO 2004057177 A1 WO2004057177 A1 WO 2004057177A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel
pump
fuel injection
combustion engine
internal combustion
Prior art date
Application number
PCT/DE2003/004156
Other languages
German (de)
English (en)
Inventor
Carlos Alvarez-Avila
Dieter Aulich
Claus Westphal
Alexander Redlich
Joerg-Peter Fischer
Régis BLANC
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 WO2004057177A1 publication Critical patent/WO2004057177A1/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
    • 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
    • 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
    • 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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F02M59/445—Selection of particular materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8069—Fuel injection apparatus manufacture, repair or assembly involving removal of material from the fuel apparatus, e.g. by punching, hydro-erosion or mechanical operation
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9038—Coatings
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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

Definitions

  • the invention is based on one
  • Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from EP 0 987 431 A.
  • This fuel injection device each has a high-pressure fuel pump and a fuel injection valve connected to it for each cylinder of the internal combustion engine.
  • the high-pressure fuel pump has a pump piston which is tightly guided in a cylinder bore and which delimits a pump work space in the cylinder bore and is connected to the fuel injection valve.
  • the pump piston is driven by a cam drive of the internal combustion engine in one stroke.
  • the cam drive also causes transverse forces on the pump piston, which can lead to seizure and therefore heavy wear on the pump piston and the cylinder bore due to insufficient lubrication of the pump piston.
  • the function of the fuel injection device is impaired, since the pump working chamber can no longer be reliably sealed by the pump piston and fuel can escape from the pump working chamber.
  • the fuel injection device according to the invention with the features according to claim 1 has the advantage over the that the lubrication of the pump piston is improved by the micro-depressions and thus an increased wear resistance of the pump piston and the cylinder bore is achieved.
  • micro-depressions of the pump piston also reduce the leakage of fuel from the pump work space, as a result of which dilution of the lubricating oil of the internal combustion engine can be reduced in the case of a cam drive which is lubricated according to claim 2.
  • the wear resistance of the pump piston can be further improved.
  • FIG. 1 shows a detail of an internal combustion engine with a fuel injection device in a schematic representation
  • FIG. 2 shows a detail of the surface of a pump piston of the fuel injection device in an enlarged representation according to a first exemplary embodiment
  • FIG. 3 shows the pump piston surface according to a second exemplary embodiment
  • FIG. 4 shows the pump piston surface according to a third exemplary embodiment
  • FIG 5 shows the pump piston surface according to a fourth exemplary embodiment.
  • FIG. 1 shows a detail of an internal combustion engine of a motor vehicle, only a part of it a cylinder of the internal combustion engine is shown.
  • the internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders.
  • a fuel injection device is provided, which is preferably designed as a so-called pump-nozzle unit and which has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it for each cylinder of the internal combustion engine, which form a common structural unit.
  • the fuel injection device is provided, which is preferably designed as a so-called pump-nozzle unit and which has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it for each cylinder of the internal combustion engine, which form a common structural unit.
  • the fuel injection device is provided, which is preferably designed as a so-called pump-nozzle unit and which has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to it for each cylinder of the internal combustion engine, which form a common structural unit.
  • Fuel injection device can also be designed as a so-called pump-line nozzle system, in which the high-pressure fuel pump and the fuel injection valve of each cylinder are arranged separately from one another and are connected to one another via a line.
  • High-pressure fuel pump 10 has a pump body 14 with a cylinder bore 16, in which a pump piston 18 is tightly guided.
  • the pump piston 18 is at least indirectly by a cam 20 of a camshaft 21 of the internal combustion engine against the force of a return spring
  • a rocker arm 23 can be arranged, which on the one hand on the cam
  • the pump piston 18 delimits a pump working chamber 22 in the cylinder bore 16, in which fuel is compressed under high pressure during the pumping stroke of the pump piston 18.
  • the pump work chamber 22 is supplied with fuel from a fuel reservoir 24 of the motor vehicle, for example by means of a delivery pump 25.
  • the fuel injection valve 12 has a valve body 26 which is connected to the pump body 14 and which can be constructed in several parts, and in which at least one injection valve member 28 in a bore 30 is guided slidably.
  • the valve body 26 has at least one, preferably a plurality of injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine.
  • the 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 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 injection valve member 28 by a radial expansion of the bore 30.
  • the injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 due to a reduction in cross section.
  • a prestressed closing spring 44 engages, by means of which the injection valve member 28 is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of the valve body 26, which adjoins the bore 30. It can be provided that the first injection valve member 28 of the fuel injection valve 12 is hollow and a second injection valve member is slidably guided therein, by means of which at least one second injection opening is controlled.
  • a further bore 48 in which a control piston 50 is tightly connected, which is connected to the injection valve member 28.
  • the bore 48 is made smaller in diameter than the spring chamber 46.
  • the control piston 50 is connected to the piston rod 51 via a piston rod 51 which is smaller in diameter than the latter
  • the control piston 50 can be formed in one piece with the injection valve member 28, but is preferably connected to the injection valve member 28 as a separate part for reasons of assembly.
  • a channel 60 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 to the pressure chamber 40 of the fuel injection valve 12.
  • a channel 62 leads from the pump work chamber 22 or from the channel 60 to the control pressure chamber 52.
  • a channel 64 which connects, also flows into the control pressure chamber 52 forms a relief area than that at least indirectly can serve the fuel reservoir 24 or another area in which a low pressure prevails.
  • a connection 66 leads from the pump work chamber 22 or from the channel 60 to a relief region 24, which can serve at least indirectly as the fuel reservoir 24, which is controlled by a first electrically operated control valve 68.
  • the control valve 68 can be designed as a 2/2-way valve, as shown in FIG. 1.
  • connection 64 of the control pressure chamber 52 to the relief area 24 is controlled by a second electrically operated control valve 70, which can be designed as a 2/2-way valve.
  • a throttle point 63 is provided in the connection 62 between the control pressure chamber 52 and the pump work chamber 22, and there is one in the connection between the control pressure chamber 52 and the relief chamber 24
  • Throttle point 65 provided.
  • the inflow of fuel from the pump work chamber 22 into the control pressure chamber 52 and the outflow of fuel from the control pressure chamber 52 can be adjusted to a required extent by suitable dimensioning of the throttle points 63, 65.
  • a sufficient inflow of fuel into the control pressure chamber 52 is required for a quick closing of the fuel injection valve 12 and a sufficient outflow of fuel from the control pressure chamber 52 is required for a quick opening of the fuel injection valve 12.
  • Control valves 68, 70 can be an electromagnetic actuator or have a piezo actuator and are controlled by an electronic control device 72.
  • the pressure in the control pressure chamber 52 is controlled by the second control valve 70, wherein when the control valve 70 is closed, at least approximately the same pressure is established in the control pressure chamber 52 as in the pump work chamber 22, while when the control valve 70 is open, a lower pressure in the control pressure chamber 52 results due to the connection to the relief region 24 sets as in the pump work space 22.
  • the total closing force acting on the injection valve member 28 is therefore dependent on the force of the closing spring 44 and on the pressure prevailing in the control pressure chamber 52, which pressure is controlled by the second control valve 70.
  • the control pressure chamber 52 and the second control valve 70 can also be omitted, so that the
  • Opening pressure of the fuel injection valve 12 is determined only by the closing spring 44.
  • the pump piston 18 of the high-pressure pump 10 is shown enlarged in each case in FIGS. 2 to 5.
  • the pump piston 18 is provided with a plurality of micro-depressions 80 at least in a partial area of its surface which is tightly guided in the cylinder bore 16.
  • the width of the micro-depressions 80 is, for example, between approximately 10 ⁇ m and approximately 30 ⁇ m, their depth is, for example, between approximately 2 ⁇ m and approximately 30 ⁇ m and their distance from one another is, for example, between approximately 30 ⁇ m and approximately 150 ⁇ m.
  • the micro-depressions 80 are preferably distributed uniformly over the surface of the pump piston 18.
  • the micro-recesses 80 of the pump piston 18 Fuel that acts as a lubricant is stored and enables good lubrication and thus low friction between the pump piston 18 and the cylinder bore 16.
  • the micro-depressions 80 also act as a labyrinth seal, so that little or no fuel from the pump working chamber 22 between the pump piston 18 and the cylinder bore 16 can emerge and reach the cam drive 20, 21, 23 of the internal combustion engine. This avoids dilution of the lubricating oil of the internal combustion engine.
  • the micro-depressions 80 are designed as cups.
  • the micro-depressions 80 are designed as grooves which can run in the longitudinal direction or in the transverse direction or at any inclination over the circumference of the pump piston 18.
  • the micro-depressions 80 are designed as intersecting grooves.
  • the micro-depressions 80 are designed as grooves running spirally over the circumference of the pump piston 18.
  • the micro-depressions 80 can be introduced into the surface of the pump piston 18, for example by means of laser processing, hard turning, spark erosion or by means of a lithopraphic method.
  • the pump piston 18 and the cylinder bore 16 can be machined by pairing loops.
  • the pump piston 18 can be in addition to the micro-depressions 80 at least in a partial area of it in the Cylinder bore 16 tightly guided surface may be provided with a coating 82 made of wear-resistant material.
  • the coating 82 can in particular consist of carbon or carbon compounds which have a high hardness.
  • first control valve 68 When the first control valve 68 is open, pump piston 18 is supplied with fuel from the fuel reservoir 24 by means of the feed pump 25. When the pump piston 18 moves, the fuel injection begins with a pre-injection, the first control valve 68 being closed by the control device 72, so that the pump working chamber 22 is separated from the relief region 24 and high pressure builds up in the pump working chamber 22 with the pump piston 18 pumping stroke.
  • the second control valve 70 is also closed by the control device 72, so that the control pressure chamber 52 is separated from the relief region 24. In this case, high pressure builds up in the control pressure chamber 52 at least approximately as in the pump work chamber 22.
  • a fuel injection cycle begins with a pre-injection of a small amount of fuel.
  • the second control valve 70 is opened by the control device 72 so that the control pressure chamber 52 with the relief area 24 is connected. Fuel can then flow out of the control pressure chamber 52 via the throttle point 65 to the relief region 24, so that the pressure in the control pressure chamber 52 drops.
  • the injection valve member 28 moves in the opening direction 29 and releases the at least one injection opening 32.
  • the control device 72 closes the second control valve 70, so that the control pressure chamber 52 is separated from the relief region 24.
  • the first control valve 68 remains in its closed position. High pressure builds up in the control pressure chamber 52 as in the pump work chamber 22, so that a large pressure force acts on the control piston 50 in the closing direction. Since the force acting on the injection valve member 28 in the opening direction 29 is now less than that
  • the fuel injection valve 12 closes the sum of the force of the closing spring 44 and the pressure force on the control piston 50. Several successive pre-injections of fuel can also be provided.
  • the second control valve 70 is in turn opened by the control device 72 at a certain point in time and for a certain period of time, so that the pressure in the control pressure chamber 52 drops.
  • the fuel injection valve 12 then opens due to the reduced pressure force on the control piston 50 and the injection valve member 28 moves in the opening direction 29.
  • the second control valve 70 is open, a small amount of fuel flows through the throttle points 63, 65 to the relief chamber 24, but the throttle points can
  • 63,65 are formed with a small flow cross-section, so that the outflowing fuel quantity and the reduction in pressure in the pump work chamber 22 is small.
  • Control valve 70 through the control device 72 in its brought closed switching position, so that the control pressure chamber 52 is separated from the relief region 24 and 52 high pressure builds up in the control pressure chamber. Due to the high pressure in the control pressure chamber 52 and the closing spring 44, a greater force then acts on the injection valve member 28 in the closing direction than in the opening direction 29 and the fuel injection valve 12 closes.
  • the first control valve 68 may be in its open or closed position to complete the main injection. Subsequent to the main injection, a post-injection can be carried out at
  • Fuel injection cycle take place.
  • the second control valve 70 is opened again by the control device 72 at a time determined by this, so that the fuel injection valve 12 opens as a result of the falling pressure in the control pressure chamber 52.
  • the control device 72 opens the first control valve 68 and / or closes the second control valve 70 so that the fuel injection valve 12 closes.

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

Abstract

L'invention concerne un système d'injection de carburant comprenant, pour chaque cylindre du moteur à combustion, une pompe à carburant haute pression (10) respective et une soupape d'injection de carburant (12) respective reliée à cette pompe. Ladite pompe à carburant haute pression (10) comprend un piston (18) guidé de façon ajustée dans un logement cylindrique (16) dans lequel il délimite une chambre de travail (22) qui communique avec la soupape d'injection de carburant (12). Ledit piston (18) est entraîné par un système d'entraînement par came (20, 21, 23) du moteur à combustion de façon à effectuer un mouvement alternatif. Selon l'invention, ce piston (18) présente une pluralité de microdépressions (80) au moins dans une partie de sa surface qui est guidée de façon ajustée dans le logement cylindrique (16).
PCT/DE2003/004156 2002-12-20 2003-12-17 Systeme d'injection de carburant pour moteur a combustion WO2004057177A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10259955.6 2002-12-20
DE2002159955 DE10259955A1 (de) 2002-12-20 2002-12-20 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Publications (1)

Publication Number Publication Date
WO2004057177A1 true WO2004057177A1 (fr) 2004-07-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/004156 WO2004057177A1 (fr) 2002-12-20 2003-12-17 Systeme d'injection de carburant pour moteur a combustion

Country Status (2)

Country Link
DE (1) DE10259955A1 (fr)
WO (1) WO2004057177A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2824311A1 (fr) * 2013-07-10 2015-01-14 EFI Hightech AG Agencement d'un élément de piston et injecteur doté d'un agencement d'élément de piston
WO2015110242A1 (fr) * 2014-01-27 2015-07-30 Robert Bosch Gmbh Vanne à commande électromagnétique pour pompe à haute pression ainsi que pompe à haute pression

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011082740B4 (de) 2011-09-15 2022-03-03 Robert Bosch Gmbh Verfahren zur Herstellung einer Kolbenpumpe mit einem Gehäuse und mindestens einem in einer Kolbenführung des Gehäuses angeordneten axial bewegbaren Kolben
IT201700054112A1 (it) * 2017-05-18 2018-11-18 Bosch Gmbh Robert Gruppo pompa per l'alimentazione di carburante ad un motore a combustione interna
DE102021211397A1 (de) * 2021-10-08 2023-04-13 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0823551A2 (fr) * 1996-08-08 1998-02-11 Toyota Jidosha Kabushiki Kaisha Palier de galet pour pompe d'injection de carburant
WO1999002852A1 (fr) * 1997-07-11 1999-01-21 Robert Bosch Gmbh Pompe a piston pour l'alimentation haute pression en carburant
EP0967384A2 (fr) * 1998-04-24 1999-12-29 Sumitomo Electric Industries, Ltd Pompe d'injection de carburant
EP0987431A2 (fr) * 1998-09-18 2000-03-22 Lucas Industries Limited Injecteur de carburant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0823551A2 (fr) * 1996-08-08 1998-02-11 Toyota Jidosha Kabushiki Kaisha Palier de galet pour pompe d'injection de carburant
WO1999002852A1 (fr) * 1997-07-11 1999-01-21 Robert Bosch Gmbh Pompe a piston pour l'alimentation haute pression en carburant
EP0967384A2 (fr) * 1998-04-24 1999-12-29 Sumitomo Electric Industries, Ltd Pompe d'injection de carburant
EP0987431A2 (fr) * 1998-09-18 2000-03-22 Lucas Industries Limited Injecteur de carburant

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2824311A1 (fr) * 2013-07-10 2015-01-14 EFI Hightech AG Agencement d'un élément de piston et injecteur doté d'un agencement d'élément de piston
WO2015110242A1 (fr) * 2014-01-27 2015-07-30 Robert Bosch Gmbh Vanne à commande électromagnétique pour pompe à haute pression ainsi que pompe à haute pression

Also Published As

Publication number Publication date
DE10259955A1 (de) 2004-07-15

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