EP1068445B1 - Dispositif d'injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
EP1068445B1
EP1068445B1 EP99964367A EP99964367A EP1068445B1 EP 1068445 B1 EP1068445 B1 EP 1068445B1 EP 99964367 A EP99964367 A EP 99964367A EP 99964367 A EP99964367 A EP 99964367A EP 1068445 B1 EP1068445 B1 EP 1068445B1
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EP
European Patent Office
Prior art keywords
valve
pressure
fuel
injection
space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99964367A
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German (de)
English (en)
Other versions
EP1068445A1 (fr
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1068445A1 publication Critical patent/EP1068445A1/fr
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Publication of EP1068445B1 publication Critical patent/EP1068445B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0068—Actuators specially adapted for partial and full opening of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention is based on a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • the fuel injection valve member supplied by a high-pressure fuel source is controlled by various hydraulic forces acting on it in the opening and closing directions. It has an injection valve member for controlling an injection opening and, on its side facing away from the injection opening, includes a control chamber which is supplied with high fuel pressure from a high-pressure fuel source via a throttled inflow channel and which can be relieved via the control valve, which is actuated by a piezo actuator , so that in this case the injection valve member is opened by the hydraulic pressure acting on the pressure shoulder of the injection valve member and in the absence of hydraulic high pressure in the control chamber.
  • the control valve is arranged in a drain channel of the control chamber.
  • a connection to the pressure chamber delimited by the pressure shoulder of the injection valve member which is constantly kept under high pressure, must also be provided in the known fuel injection device.
  • This known device is complex for the reason described, since in addition to the multiple connection between the high-pressure fuel source to the control chamber on the one hand and to the pressure chamber on the other hand, the inlet and outlet cross sections to the control chamber and the pressure-exposed surfaces on the injection valve member must be coordinated exactly with one another.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that the injection valve member of the fuel injection valve can be opened quickly and precisely via the piezo drive for a pre-injection with simple means, then closed again, in order to then be opened for the subsequent main injection. It is of major advantage that the control valve member only has to be moved back and forth for the entire process. In particular, very short high-pressure supply times can be achieved in order to achieve the pre-injection via the short phase of opening both valve seats on the control valve while the control valve member is moving in the same direction.
  • a further advantageous embodiment of the invention is that, according to claim 3, the high fuel pressure coming from the high-pressure fuel source when the control valve member is closed brings about a force equalization on the control valve member, since the same areas in both directions of movement of the control valve member are of equal size.
  • the area ratio of the areas exposed to pressure acting on the control valve member can be selected so that the control valve member is loaded slightly more by the high pressure of the high-pressure fuel source in the opening in the opening direction than in the closing direction. The closing takes place by resetting spring forces on the control valve member.
  • the pressurization of the control valve member according to claim 5 is chosen so that the supply of the pressure line to the valve chamber takes place coaxially to the valve tappet, so that the connection between the high-pressure fuel source and the valve chamber or to the pressure chamber of the fuel injector is closed when the valve head is in contact with its second valve seat is.
  • the control valve member is acted upon by relatively large opening forces, the valve tappet bore is only acted on by the low fuel, so that the leakage losses of the control valve are low.
  • the pressurization on the valve lifter or the latter leading valve tappet bore takes place only during the connection of the pressure line to the pressure chamber, that is to say during the injection phase of the fuel injection device.
  • FIG. 1 shows a schematic illustration of a fuel injection device with fuel supply from a high-pressure fuel reservoir and a fuel injection valve of a first exemplary embodiment
  • FIG. 2 shows the stroke profiles of the fuel injection valve and control valve member of the exemplary embodiment according to FIG. 1
  • FIG. 3 shows a modification of the exemplary embodiment according to FIG. 1 with interchanged connections of the pressure line leading from the high-pressure fuel reservoir to the fuel injector.
  • a fuel injection device with which a large variation of the fuel injection with respect to the injection quantity and injection timing is possible at high injection pressures but with little effort, is implemented by a so-called common rail system.
  • This provides a different type of high-pressure fuel source, from which fuel injection can take place than is specified in the usual high-pressure fuel injection pumps.
  • a high-pressure fuel reservoir 1 is provided as the high-pressure fuel source, which is supplied with fuel by a high-pressure fuel delivery pump 2 from a fuel reservoir 4, which is brought to the injection pressure.
  • the pressure in the high-pressure fuel reservoir is detected by a pressure sensor 6 and fed as a signal to an electrical control device 8, which controls the pressure in the high-pressure fuel reservoir via a pressure control valve 5.
  • the control device also controls the opening and closing of fuel injection valves 9, which are supplied for the injection of fuel from the high-pressure fuel reservoir.
  • a pressure line with the partial branches 10a, 10b leads from the high-pressure fuel reservoir 1 to a pressure chamber 11 in the fuel injection valve, which pressure chamber 11 surrounds the end of the fuel injection valve member 12 in a ring shape and penetrates up to a valve seat 13.
  • the injection valve member has in the area of the pressure chamber 11 a pressure shoulder 14 which is loaded by the pressure of the pressure chamber 11 in the opening direction of the injection valve member 12 against a closing spring 15 acting on the rear side of the injection valve member. If the hydraulic forces on the pressure shoulder 14 exceed the closing forces of the closing spring 15, the valve member lifts off with its sealing surface 16 from the valve seat 13 and establishes the connection between the pressure chamber 11 and the injection openings 17 so that the fuel injection can take place.
  • This fuel injection is controlled by the supply of high fuel pressure via the pressure line 10a, 10b to the pressure chamber 11.
  • a control valve 18 is provided in this pressure line for controlling it.
  • This has a control valve member 20, with a valve tappet 21 which is guided in a valve tappet bore 22 and has at its end a valve head 23 which is movable within a valve space 24.
  • the latter carries a spring plate 26, between which and the housing a clamping spring 27 is clamped, which strives to connect the valve head with a valve head sealing surface 29 on one side thereof to a correspondingly conical first valve seat Bring 30.
  • the first valve seat 30 is located at the transition between the valve chamber 24 with a larger diameter to the tappet bore 22.
  • valve seat 31 On the side of the valve chamber 24 opposite the first valve seat 30 there is a second, likewise conical valve seat 31 at the outlet of the part 10b of the pressure line from the valve chamber 24, which pressure line part 10b leads to the pressure chamber 11.
  • a second valve head sealing surface 32 cooperates on the valve head 37, so that the connection between the valve chamber 24 and the pressure line 10b is closed when the control valve member 20 is moved from the first valve seat against the force of the closing spring 27 to the second valve seat 31.
  • the tappet 21 has an annular recess 33, which together with the valve head 23 resting on the first valve seat 30 the tappet bore 22 includes an annular space 34.
  • the pressure line part 10a which leads from the high-pressure fuel reservoir 1, opens into this. If the control valve member 20 is in the closed position shown in FIG. 1, the connection between the high-pressure fuel reservoir 1 and the pressure chamber 11 is closed. The forces acting on the control valve member 20 due to the high pressure loading of the annular space 34 are substantially balanced in the axial direction of the control valve member.
  • the pressurized surface on the control valve member 20, which points in the direction of the valve chamber 24, can be slightly larger than the surface on the tappet acting in the direction of the spring plate 24.
  • the closing spring 27 applies the closing force necessary for securely closing the control valve 18, which is greater than the resulting hydraulic force acting in the opening direction. This has the advantage that low actuating forces for the control valve member 20 are necessary.
  • the control valve member 20 is actuated by means of a piezo actuator, the actuator 36 of which is partially shown in FIG. 1.
  • the actuator 36 delimits with its end face 37 a part of a closed transmission space 38, to which an end face 39 of a tappet actuating piston 40 also adjoins, which is tightly guided in a guide bore 41 which adjoins the valve tappet bore 22 coaxially.
  • the end face 37 of the actuator 36 is substantially larger than the end face 39 of the tappet actuating piston 40.
  • the piezo actuator is excited by the control device 8 and the actuator 36 is moved into the transmission space 38, the small stroke of the Actuator 36 enlarged by the area ratio of the end faces 37 and 39 into a larger stroke of the tappet actuating piston 40, which correspondingly moves the control valve member 20 to a relatively large opening stroke when it is in contact with the end of the valve tappet 21.
  • FIGS. 2a and 2b The movements of the control valve member 20 and the injection valve member 12 one above the other are shown in FIGS. 2a and 2b.
  • the piezo is excited in such a way that the valve head lifts off its contact with the first valve seat 30 until it comes to contact the second valve seat 31.
  • the two sub-lines 10a and 10b of the pressure line are connected to one another via the valve chamber 24, so that high fuel pressure can reach the pressure chamber 11 and cause the injection valve member 12 to rise there.
  • FIG. 2a with the stroke V.
  • the corresponding stroke of the control valve member is shown in Figure 2b over the area V s .
  • the connection of the pressure line parts 10a and 10b of the pressure line is interrupted again, which leads to a drop in the injection V according to FIG. 2a.
  • the control valve member 20 is then returned by appropriate actuation of the piezo actuator such that the valve head 23 assumes a stroke h Hs at which it is spaced both from the first valve seat 30 and from the second valve seat 31 and thus the connection of the sub-lines 10a and 10b of the pressure line.
  • the main injection H then takes place over the duration of the control valve member remaining in this position.
  • the control valve member 20 becomes the end of the main injection fully returned again, so that the first valve head sealing surface 29 in turn comes close to the first valve seat 30.
  • control valve member 20 In this embodiment of the control valve member, only small switching forces are required for the control valve member 20, since it is essentially force-balanced between the injections in the starting position shown in FIG. 1 when subjected to high pressure. However, the high fuel pressure is present on the valve tappet 21, so that leakage losses along the valve tappet bore 22 can occur. A corresponding procedure must be ensured.
  • control valve is used in the essentially identical configuration as in Figure 1.
  • the only difference here is that the pressure line with its pressure line part 10a does not open into the annular space 34, but opens into the valve space 24 at the second valve seat.
  • the pressure line part 10b of the pressure line then points from the annular space 34.
  • the control valve can be controlled in the same way as in the first embodiment. In the starting position, the valve head 23 rests with its first valve head sealing surface 29 on the first valve seat 30, so that the valve chamber 24 is exposed to the high pressure supplied by the pressure line 10a. This pressure holds the valve closing member 20 in the closed position.
  • the control valve member 20 is moved away from the first valve seat 30, as before, to the second valve seat 31 and the connection between the pressure line parts 10a and 10b is established briefly, over a time that is sufficient, one Trigger pre-injection V according to Figure 2a.
  • this pre-injection is then ended and after a pause P, the control valve member 20 is brought into an intermediate position between the two valve seats 30 and 31, as before, for carrying out the main injection H. Then this return movement is continued until the Valve head 23 rests against first valve seat 30 and the main injection ends.
  • the amount of leakage along the valve tappet 21 is reduced since the high fuel pressure is only applied to it during the injection phases.
  • larger actuation forces of the control valve member are required, but this can easily be achieved by a piezo actuator with hydraulic transmission.
  • the hydraulic ratio advantageously enables the large opening strokes h vs.

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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)

Abstract

L'invention concerne un dispositif d'injection de carburant pour moteurs à combustion interne, alimenté en carburant par une source de carburant haute pression (1), et comportant une soupape d'injection de carburant (8) commandée par une unité de commande (10). La soupape d'injection de carburant présente un organe d'injection (12) qui est sollicité, via un épaulement de pression (14), par la haute pression de carburant alimenté et, de ce fait, peut s'ouvrir pour effectuer l'injection. L'alimentation en carburant s'effectue via un conduit de pression (10a, 10b) à passage commandé par une vanne de réglage (20) dont l'organe de commande est déplaçable, dans un logement de soupape (24), entre deux sièges de soupape (30, 31), et commande ainsi, pour une pré-injection et une injection principale, la connexion entre la source de carburant haute pression (1) et la soupape d'injection de carburant (9), via le logement de soupape (24).

Claims (5)

  1. Dispositif d'injection de carburant pour moteurs à combustion interne, doté d'une source de carburant haute pression (1) qui alimente en carburant à l'aide d'une conduite de refoulement (10a, 10b), un injecteur de carburant (9) qui présente un organe de soupape d'injection (12) pour commander une ouverture d'injection (17), doté d'un épaulement de pression (14) limitant une chambre de pression et contraint par la pression du carburant amené par la conduite de refoulement (10a, 10b), grâce auquel l'organe de soupape d'injection (12) peut être soulevé d'un siège de soupape d'injection (13) contre une force de rappel (15) pour ouvrir l'ouverture d'injection (17), et doté d'une soupape de commande (18) qui a un organe de soupape de commande (20) actionné par un piézo-actionneur (36), commandant le mouvement de l'organe de soupape d'injection (12), doté d'un poussoir de soupape (21) guidé dans un boîtier à l'extrémité duquel est prévue une tête de soupape (23) saillant dans une chambre de soupape (24), munie de deux surfaces d'étanchéité de tête de soupape (29, 32) opposées l'une à l'autre, laquelle tête coopère avec les surfaces d'étanchéité de la tête de soupape (29, 32) respectivement avec l'un des deux sièges de soupape (30, 31) de la soupape de commande, et commande à cet effet le passage d'une conduite (10a, 10b) provenant de la source de carburant haute pression , débouchant par le premier siège de soupape (30) de ces sièges de soupape dans la chambre de soupape (24), et quittant la chambre de soupape (24) par le deuxième siège de soupape (31) de ces sièges de soupapes, l'organe de soupape de commande (20) pouvant être actionné par le piézo-actionneur (36) de telle sorte qu'il est déplacé avec sa tête de soupape (23) de l'un à l'autre des sièges de soupape ou qu'il reste entre les deux sièges de soupape, dans une position intermédiaire dans laquelle les deux parties de conduite de la conduite (10a, 10b) provenant de la source de carburant haute pression sont raccordées entre elles par la chambre de soupape (24),
    caractérisé en ce que
    pour commander le mouvement de l'organe de soupape d'injection (12) la soupape de commande (20) est disposée dans la conduite de refoulement (10a, 10b) menant à la chambre de soupape (11) limitée par l'épaulement de pression (14).
  2. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe de soupape de commande (20) est actionné par le piézo-actionneur (36) à l'aide d'une transmission hydraulique (37, 38, 39).
  3. Dispositif d'injection de carburant selon la revendication 1 ou 2,
    caractérisé en ce que
    la tête de soupape (23) présente deux surfaces d'étanchéité de tête de soupape (29, 32) coniques, qui coopèrent avec des sièges de soupape (30, 31) coniques, et le poussoir de soupape (21) présente un évidement (33) adjacent à la surface d'étanchéité de la tête de soupape (29), lequel évidement forme avec un alésage (22) de poussoir de soupape se terminant au premier siège de soupape, un espace annulaire (34) raccordé en permanence avec la conduite de refoulement (10a) menant à la source de carburant haute pression (1), laquelle conduite de refoulement (10b) mène du deuxième siège de soupape (31) vers la chambre de pression (11).
  4. Dispositif d'injection de carburant selon la revendication 3,
    caractérisé en ce qu'
    une surface de l'organe de soupape de commande, contrainte en pression, tournée dans la direction de la chambre de soupape, est plus grande qu'une surface contrainte en pression tournée à l'opposé du poussoir.
  5. Dispositif d'injection de carburant selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    la tête de soupape (23) présente deux surfaces d'étanchéité de tête de soupape (29, 32) coniques qui coopèrent avec des sièges de soupape (30, 31) coniques, et le poussoir de soupape (21) présente un évidement (33) adjacent à la surface d'étanchéité de la tête de soupape (29), lequel évidement forme avec un alésage (22) de poussoir de soupape se terminant au premier siège de soupape (30), un espace annulaire (34) raccordé en permanence avec la conduite de refoulement (10b) menant à la chambre de pression (11), et la conduite de pression (10a) provenant de la source de carburant haute pression (1) débouche dans la chambre de soupape (24) par le deuxième siège de soupape (31).
EP99964367A 1998-12-29 1999-11-24 Dispositif d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP1068445B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19860678A DE19860678A1 (de) 1998-12-29 1998-12-29 Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19860678 1998-12-29
PCT/DE1999/003721 WO2000039451A1 (fr) 1998-12-29 1999-11-24 Dispositif d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1068445A1 EP1068445A1 (fr) 2001-01-17
EP1068445B1 true EP1068445B1 (fr) 2004-03-31

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99964367A Expired - Lifetime EP1068445B1 (fr) 1998-12-29 1999-11-24 Dispositif d'injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US6422211B1 (fr)
EP (1) EP1068445B1 (fr)
JP (1) JP2002533613A (fr)
DE (2) DE19860678A1 (fr)
WO (1) WO2000039451A1 (fr)

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DE10019766A1 (de) 2000-04-20 2001-10-31 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10031570C2 (de) * 2000-06-29 2002-09-26 Bosch Gmbh Robert Leckage reduzierter Hochdruckinjektor
DE10031574B4 (de) * 2000-06-29 2008-12-04 Robert Bosch Gmbh Druckgesteuerter doppelschaltender Hochdruckinjektor
DE10032923A1 (de) 2000-07-06 2002-01-24 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10032924A1 (de) * 2000-07-06 2002-01-24 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10033428C2 (de) * 2000-07-10 2002-07-11 Bosch Gmbh Robert Druckgesteuerter Injektor zum Einspritzen von Kraftstoff
DE10127932A1 (de) * 2001-06-08 2002-12-19 Bosch Gmbh Robert Ventil zum Steuern von Fluiden sowie Verfahren zur Bestimmung von Drücken
US7278593B2 (en) * 2002-09-25 2007-10-09 Caterpillar Inc. Common rail fuel injector
US7124746B2 (en) * 2002-07-16 2006-10-24 Brocco Douglas S Method and apparatus for controlling a fuel injector
DE10333695A1 (de) * 2003-07-24 2005-03-03 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333696A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
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JP2002533613A (ja) 2002-10-08
WO2000039451A1 (fr) 2000-07-06
DE19860678A1 (de) 2000-07-06
US6422211B1 (en) 2002-07-23
DE59909039D1 (de) 2004-05-06
EP1068445A1 (fr) 2001-01-17

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