EP1657427A1 - Injecteur de carburant avec amplification de pression commandée hydrauliquement - Google Patents

Injecteur de carburant avec amplification de pression commandée hydrauliquement Download PDF

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Publication number
EP1657427A1
EP1657427A1 EP05105254A EP05105254A EP1657427A1 EP 1657427 A1 EP1657427 A1 EP 1657427A1 EP 05105254 A EP05105254 A EP 05105254A EP 05105254 A EP05105254 A EP 05105254A EP 1657427 A1 EP1657427 A1 EP 1657427A1
Authority
EP
European Patent Office
Prior art keywords
pressure
chamber
piston
piston part
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.)
Granted
Application number
EP05105254A
Other languages
German (de)
English (en)
Other versions
EP1657427B1 (fr
Inventor
Dirk Vahle
Christian Grimminger
Heinz-Bernd Haiser
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1657427A1 publication Critical patent/EP1657427A1/fr
Application granted granted Critical
Publication of EP1657427B1 publication Critical patent/EP1657427B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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

Definitions

  • Fuel injectors are used to supply fuel to combustion chambers of self-igniting internal combustion engines. Fuel injectors can be both stroke and pressure controlled. The required system pressure is generated by pump-nozzle units, pump-line-nozzle units or accumulator injection systems. In order to achieve high specific power and reduce emissions, the highest possible injection pressure is required. The use of pressure intensifiers further increases the injection pressure compared to the system pressure.
  • a fuel injector with hydraulic pressure booster is known for example from DE-A 101 23 911.
  • a fuel injector which can be supplied by a high-pressure fuel source comprises a pressure booster device, in which a movable piston separates a space connected to the high-pressure fuel source from a high-pressure chamber connected to the injector.
  • the high-pressure chamber is connected to a spring chamber via a fuel line, so that the high-pressure chamber can be filled with fuel via the spring chamber.
  • the spring chamber pressure is relieved, so that the fuel acting on the movable piston with system pressure moves the piston into the high-pressure chamber.
  • the fuel in the high-pressure chamber is compressed and the pressure is increased.
  • the nozzle needle releases the injection openings.
  • the spring chamber is again pressurized with system pressure. So that the piston is moved back into the starting position, a spring element is accommodated in the spring chamber, which exerts an additional force on the piston.
  • a fuel injection device in which the pressure booster piston is moved back by acting on these hydraulic forces in the starting position.
  • the pressure booster piston on a high-pressure surface and three control surfaces.
  • One of the control surfaces is opposite to the high-pressure surface and defines a continuously pressure-free control chamber.
  • An annular-disc-shaped control surface facing in the same direction is in a pressurized system with the first control chamber and the second control surface facing in the same direction as the high-pressure surface lies in a second control chamber which is acted upon by a multi-way valve and a throttle temporarily by the system pressure and temporarily is depressurized.
  • the erfmdungsconcee fuel injector for injecting fuel into a combustion chamber of an internal combustion engine which ensures a safe function and is built compact even with fluctuating dimensional tolerances in production, comprises at least one injection opening releasing or closing hydraulically actuated nozzle needle and a pressure booster to the injection pressure compared to the system pressure to amplify, wherein the pressure booster comprises a pressure booster piston with a return piston part, a control piston part and a high pressure piston part.
  • the return piston part is surrounded by a spring chamber, in which a fuel line opens, via which the spring chamber is supplied with under system pressure fuel.
  • the return piston is guided in a guide pot, which is provided with a front side in a sealing seat against a spring space defining end face.
  • the system pressure may be provided by a high pressure accumulator or may be created in a pump-nozzle unit or pump-line-nozzle unit. With the help of the pressure booster, the injection pressure is further increased compared to the system pressure.
  • the pressure booster piston is hydraulically actuated by the control piston enteil limited with the side facing away from the guide pot side a control room.
  • the control room is preferably Connected to the supply line via a 3/2-way valve, which supplies the fuel at system pressure.
  • the control chamber In the second position of the 3/2-way valve, the control chamber is connected to a low-pressure side drain.
  • the pressure force acting on the end face of the control piston part increases and the pressure intensifier piston is moved out of the control chamber.
  • the control chamber is connected to the low-pressure side outlet, the pressure and pressure force acting on the end face of the control piston part decreases and the pressure intensifier piston moves into the control chamber.
  • the pressure intensifier piston is fully hydraulically actuated. There is no spring element required to move the pressure intensifier piston back to its original position, as disclosed for example in DE-A 101 23 911. Furthermore, the hydraulically actuated pressure booster on a small number of moving parts. As a result, the probability of failure for the injector is reduced by, for example, friction, breakage or particles, etc.
  • At least one guide surface is mechanically separated from the other.
  • the guide surface for the return piston part is executed in the guide pot.
  • the guide pot is provided with a front side in a sealing seat movable against the spring space defining end face, the executed in the guide pot guide surface is radially aligned during assembly of the fuel injector by moving the guide pot.
  • a pressure- and liquid-tight connection between the guide pot and the end wall of the spring chamber is achieved in that the guide pot is acted upon by a spring force of a spring element received in the spring chamber and is placed with the aid of this spring force in the sealing seat.
  • the spring element is supported with one side against the guide pot and with the other side against a projecting into the spring chamber support member.
  • the spring element is preferably a helical spring designed as a compression spring.
  • the stroke of the pressure intensifier piston is limited by a stroke stop.
  • the stroke stop for example, by the support element, which protrudes into the spring chamber formed.
  • the stroke is limited by the fact that the control piston part, which is designed in a larger diameter than the remindstellkolbenteil, abuts against the surface of the support member, which is opposite to the surface on which the spring element is supported, with the guide pot is placed in the sealing seat.
  • the guide pot forms the stroke stop.
  • the return piston part is designed in two different diameters in a first embodiment.
  • the part of the return piston part which has closer to the control piston part, formed in a larger diameter.
  • the stroke of the pressure intensifier piston is limited.
  • a sleeve is formed on the guide pot, which encloses the return piston part and whose length is selected so that the stroke of the pressure booster piston is terminated by the fact that the control piston member abuts against the sleeve.
  • the stroke of the pressure intensifier piston is attenuated in a particularly preferred embodiment.
  • a step-shaped cross-sectional change is formed on the return piston part, wherein the part of the return piston part is guided with a larger diameter in a protruding from the guide pot in the spring chamber sleeve.
  • an annular space is formed, which is filled with fuel.
  • the annular space may be connected via a throttle acting as a bore with the return chamber.
  • the bore acting as a throttle is preferably designed in the region of the end position of the pressure intensifier piston.
  • Figure 1 shows a hydraulic circuit diagram of an inventively designed fuel injector.
  • a fuel injector 1 is supplied by a high-pressure accumulator 2 with fuel under system pressure. Via a supply line 3, which extends from the high-pressure accumulator 2 to the fuel injector 1, the fuel enters the fuel injector 1. In the supply line 3, a throttle point 4 can be integrated, are damped by which pressure pulsations.
  • a pressure booster 5 is received.
  • the pressure booster 5 comprises a pressure booster body 6, in which a pressure booster piston 7 is accommodated.
  • the pressure booster piston 7 is divided into a return piston part 8, a control piston part 9 and a high-pressure piston part 10.
  • the pressure booster piston 7 is designed with a circular cross-section. It is the Diameter d R of the return piston part 8 is smaller than the diameter d H of the high-pressure piston part 10, which in turn is smaller than the diameter d S of the control piston part 9.
  • the cross-sectional area of the return piston part 8 is smaller than the cross-sectional area of the high-pressure piston part 10, which in turn is smaller than Also, in pressure booster piston 7, which have no circular cross-section, it is necessary that the cross-sectional area of the return piston part 8 is smaller than the cross-sectional area of the high-pressure piston part 10 and this in turn smaller than the cross-sectional area of the control piston part.
  • the return piston member 8 protrudes with an end face 11 into a rear space 12. From the rear chamber 12, a first low-pressure side return line 13 leads.
  • the low-pressure side first return 13 is connected, for example, to a fuel tank not shown here.
  • the return piston part 8 adjoins the control piston part 9. On the control piston part 9 facing side of the return piston part 8, the return piston part 8 is surrounded by a spring chamber 14. Between the spring chamber 14 and the rear space the return piston part 8 is enclosed by a guide pot 15. The guide pot 15 is placed in a sealing seat 16 against a spring space 14 limiting end face 17. As a result, the spring chamber 14 is separated from the rear space 12.
  • a support member 18 in the spring chamber 14 On the control piston part 9 facing side of the spring chamber 14 projects a support member 18 in the spring chamber 14. On the support member 18 is a spring element 19 is supported, which is supported with the other side against the guide pot 15.
  • the spring element 19 is preferably designed as a compression spring in the form of a spiral spring and surrounds the return piston part 8. By the spring force of the spring element 19 of the guide pot 15 is placed in the sealing seat 16.
  • control piston part 9 delimits a control chamber 20 with an end face 21 facing the high-pressure piston part 10.
  • the high-pressure piston part 10 opens into a high-pressure space 23 with an end face 22 lying opposite the end face 11 of the return piston part 8.
  • the high-pressure chamber 23 is connected to a nozzle chamber 25.
  • the nozzle chamber 25 encloses a nozzle needle 26.
  • a likewise the nozzle needle 26 enclosing annular space 27 extends over the annular space 27 is at least one injection port 28 with standing under high pressure Fuel supplied. The fuel passes through the at least one injection opening 28 when the injection opening 28 is open into a combustion chamber 29.
  • the nozzle needle 26 terminates in a hydraulic space 30.
  • a damping piston 31 is received in the hydraulic chamber 30.
  • a spring element 32 is received, which acts on the nozzle needle 26.
  • the spring element 32 is preferably a helical spring acting as a compression spring, which surrounds the damping piston 31.
  • a bore 33 is formed, via which a damping chamber 34, which is bounded by an end face 35 of the damping piston 31, is hydraulically connected to the hydraulic space.
  • a throttle point 36 is preferably formed for damping of pressure pulsation.
  • a nozzle needle 26 without additional damping piston 31 is used. It is also possible, as described for example in DE-A 102 29 415, to provide a step-shaped widening on the side of the damping piston 31 facing the nozzle needle 26, to which a further, not shown, spring element acts.
  • nozzle needle 6 and the damping piston 31 can be hydraulically actuated in any other manner known to those skilled in the art.
  • a fuel line 37 which branches off from the supply line 3, the control chamber 20 and the hydraulic chamber 30 are supplied with fuel under system pressure.
  • a throttle point 28 is preferably formed before it opens into the hydraulic chamber 30.
  • a control valve 39 is received in the fuel line 37.
  • the control valve 39 is preferably designed as a 3/2-way valve. In one switching position of the 3/2-way valve, fuel flows from the high-pressure accumulator 2 via the fuel line 37 into the control chamber 20 and the hydraulic chamber 30. In the second switching position, fuel flows from the hydraulic chamber 30 and the control chamber 20 into a low-pressure return line 40, which is connected to the fuel tank, for example.
  • the high-pressure space 23 is supplied with fuel via a channel 41 via the hydraulic space 30.
  • a check valve 42 is received in the channel 40.
  • the spring chamber 14, the control chamber 20, the high-pressure chamber 23, the hydraulic chamber 30 and the nozzle chamber 25 are under system pressure. That is, the entire fuel injector 1 is pressure balanced and the at least one injection port 28 is closed.
  • the control valve 39 is switched to the second position. Due to the lower pressure at the low-pressure side return 40, fuel flows out of the control chamber 20 and the hydraulic chamber 30. Due to the outflowing fuel, the pressure in the control chamber 20 decreases and the pressure booster piston 7 moves in the direction of the high-pressure chamber 23. In this way, the volume in the high-pressure chamber 23 increases and the pressure increases.
  • the check valve 42 closes so that no fuel can flow via the check valve 42 in the direction of the hydraulic chamber 30.
  • the high-pressure chamber 23 is hydraulically connected to the nozzle chamber 25 via the high-pressure line 24.
  • the pressure in the nozzle chamber 25 also increases.
  • the increasing pressure in the nozzle chamber 25 and the decreasing pressure in the hydraulic chamber 30 cause the nozzle needle 27 to move into the hydraulic chamber 30 and thus the at least one injection opening 28 releases. As soon as the at least one injection opening 28 is released, fuel flows into the combustion chamber 29.
  • the control valve 39 is switched back into the position shown in Figure 1.
  • fuel under system pressure flows into the control chamber 20, in which the pressure rises again, which leads to a movement of the pressure booster piston 7 from the high-pressure chamber 23.
  • the volume of the high pressure chamber 23 is increased and the pressure in the high pressure chamber 23 and thus also in the nozzle chamber 25 decreases.
  • fuel that is under system pressure flows via the fuel line 37 into the hydraulic space 30, in which system pressure thus likewise sets. Due to the increasing pressure in the hydraulic chamber 30 and the falling pressure in the nozzle chamber 25, the nozzle needle 26 moves in the direction of the at least one injection port 28 and closes it.
  • FIG. 2 shows a pressure booster in a first embodiment.
  • the pressure booster 5 comprises the pressure booster piston 7 and the pressure booster body 6.
  • the pressure booster piston 7 is accommodated in the pressure booster body 6.
  • the return piston portion 8 of the pressure booster piston 7 opens into the rear chamber 12.
  • the rear space 12 is hydraulically separated from the spring chamber 14 by the guide pot 15.
  • By formed as a compression spring spring element 19 of the guide pot 15 is placed in the sealing seat 16.
  • the sealing seat 16 is for example - as shown in Figure 2 - formed as a flat seat with a sealing surface or as a sealing edge.
  • the spring chamber 14 is limited by the control piston part 9 of the pressure booster piston 7.
  • In the spring chamber 14 projects the support member 18 on which the spring element 19 is supported, with which the guide pot 15 is placed in the sealing seat 16.
  • the support member 18 acts simultaneously as a stroke limiter for the stroke of the pressure booster piston 7.
  • By abutment of the control piston part 9 to the support member 18, the movement of the pressure booster piston 7 is limited in the direction of the rear space 12.
  • control piston part 9 delimits the control chamber 20 with the end face 21.
  • the high-pressure piston part 10 is formed on the pressure intensifier piston 7 on the end face 21.
  • the high-pressure chamber 23 is separated from the control chamber 20 by a first guide surface 43, in which the high-pressure piston part 10 is guided.
  • a hydraulic separation of the control chamber 20 from the spring chamber 14 is effected by the control piston part 9, which is guided in a second guide surface 44, which is formed in the pressure booster body 6.
  • the return piston part 8 is guided on a third guide surface, which is formed in the guide pot 15.
  • FIG. 3 shows the pressure booster 5 in a further embodiment.
  • the stroke stop of the pressure booster piston 7 is realized by the guide pot in the embodiment shown in Figure 3.
  • a stepped extension 46 is formed on the return piston part 8.
  • the diameter of the return piston part 8 on the side facing the control piston part 9 increases.
  • FIG. 4 shows a pressure amplifier 5 in a further embodiment.
  • a sleeve extension 48 is formed on the guide pot 15. The length of the sleeve extension 48 is selected so that it ends in a stop surface 47, against which the control piston part 9 abuts to limit the stroke of the pressure intensifier piston 7.
  • the third guide surface 45 is formed in the embodiment shown in Figure 4 by the guide pot 15 and formed on the guide pot 15 sleeve extension 48.
  • FIG. 5 shows a pressure booster with piston damping in a first embodiment.
  • a sleeve extension 48 is formed on the guide pot 15. Furthermore, a stepped extension 46 is formed on the return piston part 8, wherein the part of the return piston part 8 with the larger diameter on the control piston part 9 facing side is formed.
  • FIG. 6 shows a pressure amplifier with damping of the stroke movement of the pressure intensifier piston in a further embodiment.
  • a bore 51 is formed in the sleeve extension 48, via which the annular damping chamber 49 is connected to the spring chamber 14.
  • fuel is displaced from the annular damping chamber 49 into the spring chamber 14. In this way it can be avoided that the pressure intensifier piston 7 rebounds due to the pressure arising in the annular damping chamber 49.
  • FIG. 7 shows a pressure amplifier with damping of the stroke movement of the pressure intensifier piston in a further embodiment.
  • the sleeve extension 48 is provided with the stop surface 47 against which the control piston member 9 abuts to limit the stroke of the pressure booster piston 7.
  • a bore 51 is formed in the annular damping chamber 49, can be displaced via the fuel from the annular damping chamber 49 in the spring chamber 14.
  • a stepped enlargement 46 is also formed on the return piston part 8 in the embodiment shown in FIG. The portion of the return piston portion 8 of larger diameter is guided along the fourth guide surface 50 in the sleeve extension 48.
  • the guide pot 15 shown in Figures 4, 5, 6 and 7 with the sleeve extension 48 is made in one piece in a preferred embodiment.
  • a two-part design is possible, wherein the sleeve extension 58 is then preferably non-positively or materially connected to the guide pot 15.
  • FIGS. 1 to 7 the same reference numerals designate the same components. In order to avoid repetitions in the description, only the differences from the other embodiments were described in the embodiments shown in FIGS. 2 to 7.

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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)
EP20050105254 2004-10-23 2005-06-15 Injecteur de carburant avec amplification de pression commandée hydrauliquement Expired - Fee Related EP1657427B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200410051757 DE102004051757A1 (de) 2004-10-23 2004-10-23 Kraftstoffinjektor mit hydraulisch betätigbarem Druckübersetzer

Publications (2)

Publication Number Publication Date
EP1657427A1 true EP1657427A1 (fr) 2006-05-17
EP1657427B1 EP1657427B1 (fr) 2009-12-02

Family

ID=35613844

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050105254 Expired - Fee Related EP1657427B1 (fr) 2004-10-23 2005-06-15 Injecteur de carburant avec amplification de pression commandée hydrauliquement

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Country Link
EP (1) EP1657427B1 (fr)
DE (2) DE102004051757A1 (fr)
ES (1) ES2336458T3 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007027667A1 (de) 2007-06-15 2008-12-18 Robert Bosch Gmbh Injektor mit Druckverstärker und Nadelhubsteuerung über DV-Kolben

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4015557A1 (de) * 1989-05-26 1990-11-29 Volkswagen Ag Kraftstoff-einspritzvorrichtung fuer eine brennkraftmaschine
DE19949848A1 (de) * 1999-10-15 2001-04-19 Bosch Gmbh Robert Druckübersetzer für ein Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10123911A1 (de) * 2001-05-17 2002-11-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit Druckübersetzungseinrichtung und Druckübersetzungseinrichtung
WO2004036027A1 (fr) * 2002-10-14 2004-04-29 Robert Bosch Gmbh Dispositif d'injection de carburant a pression multipliee, pourvu d'une conduite de commande interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4015557A1 (de) * 1989-05-26 1990-11-29 Volkswagen Ag Kraftstoff-einspritzvorrichtung fuer eine brennkraftmaschine
DE19949848A1 (de) * 1999-10-15 2001-04-19 Bosch Gmbh Robert Druckübersetzer für ein Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10123911A1 (de) * 2001-05-17 2002-11-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit Druckübersetzungseinrichtung und Druckübersetzungseinrichtung
WO2004036027A1 (fr) * 2002-10-14 2004-04-29 Robert Bosch Gmbh Dispositif d'injection de carburant a pression multipliee, pourvu d'une conduite de commande interne

Also Published As

Publication number Publication date
EP1657427B1 (fr) 2009-12-02
DE102004051757A1 (de) 2006-04-27
DE502005008613D1 (de) 2010-01-14
ES2336458T3 (es) 2010-04-13

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