EP1584814B1 - Injecteur de carburant commandé par une soupape asservie - Google Patents

Injecteur de carburant commandé par une soupape asservie Download PDF

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Publication number
EP1584814B1
EP1584814B1 EP05100659A EP05100659A EP1584814B1 EP 1584814 B1 EP1584814 B1 EP 1584814B1 EP 05100659 A EP05100659 A EP 05100659A EP 05100659 A EP05100659 A EP 05100659A EP 1584814 B1 EP1584814 B1 EP 1584814B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
piston
chamber
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 - Fee Related
Application number
EP05100659A
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German (de)
English (en)
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EP1584814A1 (fr
Inventor
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1584814A1 publication Critical patent/EP1584814A1/fr
Application granted granted Critical
Publication of EP1584814B1 publication Critical patent/EP1584814B1/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
    • 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
    • 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
    • F02M47/025—Hydraulically 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
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/006—Springs assisting hydraulic closing force
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve

Definitions

  • the invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.
  • a fuel injector for internal combustion engines with a pressure booster device for pressure boosting and with a servo valve for pressure-controlled control of the fuel injector is known.
  • the servo valve which is constructed as a 3/2-way control valve is controlled by a designed as a solenoid valve switching valve, whereby the pressure control of the fuel injector is realized.
  • the control valve has a longitudinally displaceable in a bore control piston with a control edge, which separates a high pressure system from a low pressure system. At the control piston of the control valve while various pressure chambers for connecting control lines are necessary, which are acted upon from the inside with the high pressure of the injection system.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the pressure piston portion and the control piston portion of the control piston, which are executed with different diameters, are guided in each case separate guide elements. For the different diameters of these sections of the control piston thus no double guide on a common guide element is necessary, whereby the manufacturing cost of the control valve is reduced. As a result, the technical controllability and reproducibility for series production is improved. At the same time acting in the control valve on the control piston and the components associated therewith compressive forces are compensated, whereby the deformation forces acting in the control valve are kept low. Consequently, no high notch stresses occur on the components, eg. B. in Bohrungsverschneidungen, so that the stresses occurring remain well below the fatigue strength values.
  • control cylinder surrounds the valve chamber and a cooperating with the control edge connecting channel formed in the pressure-balanced state with closed sealing seat of the control piston, a hydraulic connection between the pressure chamber and the valve chamber. It is also expedient if the control cylinder forms a further sealing seat in the pressure chamber which, in the pressure-relieved state, separates the pressure chamber from a valve chamber formed in the valve body. In this state, the connecting channel between the pressure chamber and valve chamber is closed at the same time.
  • the control piston is expediently designed so that it has a closing pressure surface in a control chamber and an operating pressure applied by the system pressure and the pressure chamber exposed pressure surface having.
  • the sealing seat of the control piston When the fuel injector is in the inactive state, the sealing seat of the control piston is closed and the slide seal provided with the control edge is opened on the control cylinder. In the active state of the fuel injector, the sealing seat of the control piston is opened and provided with the control edge slide seal on the control cylinder closed.
  • the movement speed of the control piston can be set arbitrarily.
  • a constantly defined opening force acts on the control piston. This results in an exact valve movement and a stable persistence of the control piston at the opening stop in the open state. Thereby, a slow opening movement of the control piston can be realized, so that a stable partial opening is possible, whereby the injection of a small amount can be ensured.
  • the control edge between the control piston portion of the control piston and the valve body can be executed in many ways.
  • the use of a flat seat for the sealing seats for sealing the pressure chamber with respect to the low-pressure or return system is particularly useful because it can compensate for any axial misalignment of the components occurring.
  • sufficient closing force is provided by the closing pressure force on the pressure surface of the control piston to ensure a sufficiently high surface pressure on the flat seat for a good tightness. It is also possible to have additional spring forces act on the control piston to support the valve movement of the control piston.
  • the control valve is particularly useful in conjunction with a pressure booster device which is connected between high-pressure source and injection valve, wherein the pressure booster device has a cooperating with a pressure booster piston rear chamber which can be controlled by the control valve, so that via a pressure change in the pressure chamber acting on the injection valve pressure intensification he follows.
  • FIG. 1 shows a schematic sectional view of a fuel injector according to the invention.
  • the fuel injector shown in the figure is connected via a fuel line 3 with a high-pressure fuel source 5.
  • the high-pressure fuel source 5 comprises several elements, not shown, such as fuel tank, high-pressure pump and a high pressure line, for example, a known common rail system, the pump provides, for example, up to 1600 bar high fuel pressure via the high pressure line.
  • the fuel injector further comprises a fuel injection valve 10, which projects with injection openings 11 into a combustion chamber of an internal combustion engine.
  • the fuel injection valve 10 has a valve pin designed as a closing piston 12 with a pressure shoulder 13 which is surrounded by a pressure chamber 14.
  • the closing piston 12 is guided at an end facing away from the combustion chamber in a guide region 15, to which a closing pressure chamber 16 connects.
  • the closing piston 12 is biased by a closing spring 17 in the closing direction.
  • the fuel injector also has pressure amplification via a pressure booster 20.
  • the pressure booster 20 has a by means of a return spring 18 resiliently mounted booster piston 21, which has a first partial piston 22 and a smaller diameter second partial piston 23.
  • the partial pistons 22, 23 are each assigned a corresponding, stepped diameter-shaped cylinder 24, so that the smaller-diameter partial piston 23 in the cylinder 24 separates a high pressure chamber 25 from a rear space 26 liquid-tight.
  • the larger diameter first partial piston 22, which is guided in the cylinder portion of the cylinder 24 with the larger diameter, also separates the back space 26 of a pressure transmission chamber 27 from liquid-tight.
  • the return spring 18 is arranged, which is biased to produce a corresponding return movement for the booster piston 21 between a spring holder 28 and a ring member 29.
  • the fuel injector has a servo valve, which comprises a hydraulic control valve 30 and an electrically controllable switching valve 50, the drive being effected by an electromagnetic or piezoelectric actuator 51.
  • the switching valve 50 has an actuator piston 52 connected to the actuator 51, which is guided in an actuator bore 53.
  • the actuator piston 52 separates an actuator-side low-pressure chamber 55 from an actuator-side control chamber 56 in a liquid-tight manner with an actuator-side sealing seat 54.
  • the control valve 30 has a valve body 31 with a receptacle 32.
  • a bush 33 is arranged, in which a control piston 34 is guided with a pressure piston portion 35.
  • the control piston 34 further includes a control piston portion 36 having a smaller diameter than the pressure piston portion 35.
  • the control piston section 36 has a guide region with a control edge 45 acting as a sealing edge.
  • the control piston portion 36 is guided with the guide portion in a piston guide 43 of a control cylinder 41, wherein the control cylinder 41 is also disposed in the receptacle 32 and is present as a separate from the sleeve 33 guide member for the control piston 34.
  • the control piston 34 has at the pressure piston portion 35 a pointing into a control chamber 37 pressure surface 38. Between the pressure piston portion 35 and the control piston portion 36, an annular surface is formed, which forms an opening pressure surface 39, as will be explained later.
  • the receptacle 32 forms a pressure chamber 40, in which the bushing 33 and the control cylinder 41 are acted upon from the outside with system pressure.
  • a sealing seat 46 which acts on the bottom surface of the pressure space 40 and separates a valve chamber 47 formed in the control cylinder 41 from a connection chamber 48 connected to a low pressure or return system.
  • the control cylinder 41 further has an end face with a sealing surface or sealing edge, which forms a further sealing seat 42 at the bottom of the receptacle 32, which separates the pressure chamber 40 from the valve chamber 47.
  • a compression spring 49 acts, which presses the sealing seat 42, in particular in the pressure-relieved state against the bottom surface of the pressure chamber 40.
  • connecting channel 44 is formed, which forms a hydraulic connection between the pressure chamber 40 and the valve chamber 47 in the closed state of the sealing seat 46.
  • pressure booster 20, control valve 30 and switching valve 40 serve pressure lines, which are integrated, for example, in the fuel injector.
  • the pressure chamber 14 of the injection valve 10 is connected to a first pressure line 61 to the high-pressure chamber 25 of the pressure booster 20.
  • a second pressure line 62 leads to the rear space 26 of the pressure booster 20.
  • connection line 63 with throttle between closing pressure chamber 16 and high-pressure chamber 25.
  • the hydraulic pressure of the high-pressure fuel source 5 is via the high-pressure line 3 in the pressure chamber 40 and from there via a pressure chamber line 64 into the pressure transmission chamber 27 of the pressure booster 20 guided.
  • the pressure transmission chamber 27 is thereby in communication with the pressure chamber 40 of the control valve 30.
  • a back-room line 65 connects the rear space 26 of the pressure booster 20 to the valve chamber 47 of the control valve 30.
  • a first return line 71 returns via the low-pressure or return system into a fuel tank (not shown).
  • the control chamber 33 of the control valve 30 is connected by means of a control line 66 via an outlet throttle 67 with the actuator-side control chamber 56 of the switching valve 50.
  • a second return line 72 leads out of the actuator-side low-pressure chamber 55 of the switching valve 50 into the low-pressure or return system.
  • the return lines 71, 72 may also be formed as a common return system.
  • a connecting bore 68 leads via an inlet throttle 69 from the control chamber 33 into the pressure chamber 40 of the control valve 30.
  • the operation of the fuel injector is as shown below: At the beginning of the injection process is due to the constant pressure in the high-pressure accumulator 5 the voltage applied in the pressure booster chamber 27 pressure on the back room line 65 in the back room 26 and via the second pressure line 62 and the connecting line 63 in the high-pressure chamber 25 and from there via the first pressure line 61 in the pressure chamber 14 of the injection valve 10.
  • the actuator 51 of the switching valve 50 which is a solenoid valve in the present embodiment, is energized so that the actuator piston 52 closes the control line 66, which is in communication with the control chamber 33 of the control valve 30, against the actuator-side low-pressure chamber 55 which is in communication with the second return line 72 ,
  • the voltage applied in the pressure chamber 40 System pressure or rail pressure transmitted via the connecting hole 68 in the control chamber 33.
  • the high pressure acting in the control chamber 33 acts on the pressure surface 38 and presses the control piston 41 with its sealing seat 46 against the bottom surface of the pressure chamber 40, so that the sealing seat 46 shuts off the communicating chamber 48 communicating with the return line 71.
  • control edge 45 is located outside the piston guide 43 of the valve body 41, so that a hydraulic connection via the connecting channel 44 between the pressure chamber 40 and the valve chamber 47 is made.
  • the first return line 71 is thus decoupled from the high pressure or system pressure and the injection valve 10 is closed.
  • the opening stroke of the closing piston 12 of the injection valve 10 is initiated by lifting the Aktorkolben 52 from the actuator-side sealing seat 54 due to a corresponding energization of the actuator 51, so that the control chamber 33 is connected to the actuator-side control chamber 56 and the Aktor facultyen low-pressure chamber 55.
  • the flow resistances of the inlet throttle 69 and the outlet throttle 67 are dimensioned such that the pressure in the control chamber 33 drops and the control piston 34 lifts off from the sealing seat 46 with the end face of the control piston section 36 and at the same time the control edge 45 on the piston guide 43 closes the connection channel 44.
  • valve chamber 47 is separated from the ruling in the pressure chamber 40 rail or system pressure and at the same time leading into the valve chamber 47 back-space line 65 is connected via the connecting chamber 48 to the return line 71 and thus to the low-pressure system. Accordingly, the pressure prevailing in the rear space 26 of the pressure booster 20 pressure on the return line 71 is released and the pressure in the rear chamber 26 drops.
  • the pressure booster device 20 is activated and the lower effective area afflicted second partial piston 23 compresses the fuel in the high pressure chamber 25, so that in the pressure chamber 14 connected to the high pressure chamber 25 in the opening direction of the pressure shoulder 13 acting pressure force increases and the closing piston 12 releases the injection ports , As long as the rear space 26 is depressurized, the pressure booster device 20 remains activated and compresses the fuel in the high-pressure space 25.
  • the switching valve 50 is returned to its initial position. This is due to the seating of the control piston 34 the sealing seat 46 of the rear chamber 26 of the pressure booster 20 is separated from the return line 71 and again pressurized via the valve chamber 47, the connecting channel 44 and the pressure chamber 40 with system pressure.
  • the system pressure is also passed via the return line 65 into the rear space 26, whereby the pressure booster piston 21 is returned by the return spring 18 in its initial position.
  • the pressure in the high-pressure chamber 25 drops to system pressure, as a result of which system pressure is likewise applied again in the pressure chamber 14, the high-pressure chamber 25 being filled via the connecting line 63 from the fuel source 5.
  • the provision of the closing piston 12 is realized by the system pressure also applied via the second pressure line 62, supported by the closing spring 17 arranged in the closing pressure chamber 16.

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

Claims (10)

  1. Injecteur de carburant pour un moteur à combustion interne avec un injecteur de carburant (10) raccordé à une source haute pression et une soupape de commande (30) comprenant dans un corps de soupape (31) un piston de commande (34) mobile longitudinalement et présentant un segment de piston de pression (35) guidé dans un manchon (33) avec une première surface de pression (38), et un segment de piston de commande (36) ayant une étanchéité de coulisseau avec une arête de commande (45), dans lequel le manchon (33) disposé dans une chambre de pression (40) du corps de soupape (41) est sollicité au moins en partie de l'extérieur avec une pression du système, le piston de commande (34) dans une première position de soupape sépare une chambre de soupape (47) d'un système basse pression ou d'un système de retour à l'aide d'un siège d'étanchéité (46) sollicité par la surface de pression (38), alors que dans une seconde position de soupape le piston de commande (34) sépare la chambre de pression (40) de la chambre de soupape (47) à l'aide de l'arête de commande (45) en établissant en même temps une liaison de la chambre de soupape (47) au système basse pression ou au système de retour, en amorçant en même temps un actionnement de l'injecteur de carburant (10),
    caractérisé en ce que
    le segment de commande (36) du piston (34) avec l'arête de commande (45) est guidé dans un cylindre de commande (41) séparé du manchon (33) dans la chambre de pression (40) du corps de soupape (31).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    un canal de liaison (44) coopérant avec l'arête de commande (45) est formé dans une zone de guidage du segment de piston de commande (36), pour avoir une liaison hydraulique entre une chambre de pression (40) et la chambre de soupape (47) à l'état désactivé lorsque le siège d'étanchéité (46) du piston de commande (34) est fermé.
  3. Injecteur de carburant selon la revendication 1 ou 2,
    caractérisé en ce que
    le cylindre de commande (41) présente un autre siège d'étanchéité (42) qui sépare la chambre de pression (40) de la chambre de soupape (47) à l'état décompressé de la chambre de soupape (47).
  4. Injecteur de carburant selon la revendication 1, 2 ou 3,
    caractérisé en ce qu'
    un ressort de pression (49) agit sur le cylindre de commande (41) dans la direction de fermeture de l'autre siège d'étanchéité (42).
  5. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le piston de commande (34) présente une surface de pression (39) exposée à la chambre de pression (40), sollicitée par la pression du système et s'ouvrant constamment dans la direction d'ouverture en agissant sur le siège d'étanchéité (46).
  6. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la surface de pression (38) dans le manchon délimite une chambre de commande (37), qui peut à l'aide d'une soupape de commutation (50) être commutée entre un moyen de raccordement à la pression du système et le système basse pression ou le système de retour.
  7. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le siège d'étanchéité (46) du piston de commande (34) est réalisé avec un siège plat.
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le cylindre de commande (41) au moins en partie à l'intérieur de la chambre de pression (40) est sollicité de l'extérieur par la pression du système.
  9. Installation d'injection de carburant selon la revendication 1,
    caractérisé en ce qu'
    une installation de d'amplification de pression (20) commandée par la soupape de commande (30) et présentant un piston d'amplification de pression (21) est commutée entre la source à haute pression (5) et un injecteur (10).
  10. Installation d'injection de carburant selon la revendication 9,
    caractérisé en ce que
    l'installation de d'amplification de pression (20) possède une chambre de retour (26) coopérant avec le piston amplificateur de pression (21), et commandée par la soupape de commande (30), pour avoir une amplification de pression agissant sur l'injecteur (10) par une modification de pression dans la chambre de pression (26).
EP05100659A 2004-04-08 2005-02-01 Injecteur de carburant commandé par une soupape asservie Expired - Fee Related EP1584814B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004017304 2004-04-08
DE102004017304A DE102004017304A1 (de) 2004-04-08 2004-04-08 Servoventilangesteuerter Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP1584814A1 EP1584814A1 (fr) 2005-10-12
EP1584814B1 true EP1584814B1 (fr) 2007-05-16

Family

ID=34895517

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05100659A Expired - Fee Related EP1584814B1 (fr) 2004-04-08 2005-02-01 Injecteur de carburant commandé par une soupape asservie

Country Status (4)

Country Link
US (1) US7210639B2 (fr)
EP (1) EP1584814B1 (fr)
DE (2) DE102004017304A1 (fr)
ES (1) ES2284123T3 (fr)

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JP3994990B2 (ja) * 2004-07-21 2007-10-24 株式会社豊田中央研究所 燃料噴射装置
JP4305394B2 (ja) * 2005-01-25 2009-07-29 株式会社デンソー 内燃機関用燃料噴射装置
DE102006038840A1 (de) * 2006-08-18 2008-02-21 Robert Bosch Gmbh Kraftstoffinjektor mit Kolbenrückholung eines Druckübersetzerkolbens
US7568632B2 (en) * 2006-10-17 2009-08-04 Sturman Digital Systems, Llc Fuel injector with boosted needle closure
JP2009103080A (ja) * 2007-10-24 2009-05-14 Denso Corp 燃料噴射弁
DK177456B1 (en) * 2011-06-27 2013-06-17 Man Diesel & Turbo Deutschland A fuel valve for large turbocharged two stroke diesel engines
GB201518923D0 (en) * 2015-10-27 2015-12-09 Delphi Internat Operations Luxembourg S À R L Control valve arrangement of a fuel injector
CN114405764B (zh) * 2022-02-23 2022-11-29 无锡冰平自动化技术有限公司 一种阀座型腔开合行程相同的注胶管体

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WO2004088122A1 (fr) * 2003-04-02 2004-10-14 Robert Bosch Gmbh Injecteur de carburant comportant un transmetteur de pression commande par une soupape asservie
DE10337574A1 (de) * 2003-08-14 2005-03-10 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen

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Also Published As

Publication number Publication date
EP1584814A1 (fr) 2005-10-12
US7210639B2 (en) 2007-05-01
DE102004017304A1 (de) 2005-10-27
ES2284123T3 (es) 2007-11-01
DE502005000719D1 (de) 2007-06-28
US20050224599A1 (en) 2005-10-13

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