EP0898650B1 - 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
EP0898650B1
EP0898650B1 EP97943768A EP97943768A EP0898650B1 EP 0898650 B1 EP0898650 B1 EP 0898650B1 EP 97943768 A EP97943768 A EP 97943768A EP 97943768 A EP97943768 A EP 97943768A EP 0898650 B1 EP0898650 B1 EP 0898650B1
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EP
European Patent Office
Prior art keywords
control valve
pressure
injection
valve member
fuel
Prior art date
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Expired - Lifetime
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EP97943768A
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German (de)
English (en)
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EP0898650A1 (fr
Inventor
Franz Guggenbichler
Jaroslaw Hlousek
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0898650A1 publication Critical patent/EP0898650A1/fr
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    • 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
    • F02M63/0005—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 valves actuated by fluid 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
    • 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
    • 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
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 27 59 255 A.
  • This fuel injection device has an injection line supplied with high-pressure fuel, which is connected to a respective injection valve whose opening and closing movements are controlled by an electrically controlled, arranged on the injection valve control valve, which is designed as a 3/2-way valve.
  • the 3/2-way valve has a control valve member with a spherical closing body, on which two sealing surfaces are formed.
  • the control valve member connects a high-pressure passage opening into an injection port of the injection valve to the injection passage or to a relief passage.
  • the control valve member is actuated by a prevailing in a working space pressure against a restoring force, wherein the working space is designed as a fillable with high pressure hydraulic hydraulic working space on the control valve member of the 3/2-way valve.
  • the control valve member has a piston-shaped portion which is acted upon by the pressure prevailing in the working space against a force acting on the spherical closing body hydraulic opening force in the closing direction of a flow cross-section between the injection line and the high-pressure passage and the working space can be opened in a discharge chamber.
  • the hydraulic opening force on the control valve member is generated by acting on the closing body fuel high pressure of the injection line.
  • a further 3/2 control valve is provided, through which the working space is connected to the injection line or to the discharge space.
  • a fuel injection device in which a high-pressure pump can be filled with fuel common high-pressure accumulation chamber is provided, which is connected via injection lines with injection valves.
  • the opening and closing movements of the injection valves are each controlled by an electrically controlled, arranged on the injection valve control valve.
  • the control valve is designed as a 2/2-way valve and has a piston-shaped control valve member with a sealing surface which connects a opening to an injection port of the injection valve high-pressure channel with the injection line or separates from the injection line.
  • the high-pressure channel is constantly connected via a throttle point with a discharge line, so that even when connected to the injection line high-pressure channel fuel flows into the discharge line and thus large leakage quantities are present.
  • the control valve member can be actuated by a prevailing in a working space pressure against a restoring force, wherein the working space is designed as a fillable with high pressure hydraulic hydraulic working space on the control valve member of the 2/2-way valve.
  • the control valve member is acted upon by the prevailing pressure in the working chamber against an opening force acting on this in the closing direction of a flow cross-section between the injection line and the high-pressure channel and the working space can be opened in a discharge chamber.
  • the opening force on the control valve member is generated by a spring.
  • the pressure in the working space is controlled by a constant inflow and a controlled outflow.
  • the working space is bounded by an upper end face of the control valve member.
  • the working space is constantly connected via a throttle cross-section with the injection line and from the working space leads from a closable discharge channel whose cross-section is greater than the throttle cross section to the injection line.
  • the discharge channel is openable and controllable by means of an electric control valve.
  • At the control valve member an annular groove is provided in the region of the overlap with the injection line, are formed by the opposing annular end faces on the control valve member, where the high fuel pressure acts. Due to the opposing annular end faces of the high fuel pressure does not generate a resultant force on the control valve member when this is in its closed position in which the high pressure passage is separated from the injection line. An opening movement of the control valve member is only possible by the opening force generating spring.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that it has a simple structure with the piston-shaped control valve member and the hydraulically generated opening force, for which no spring is required.
  • the illustrated in Figure 1 first embodiment of the fuel injection device for internal combustion engines has a high-pressure fuel pump 1, which is connected on the suction side via a fuel delivery line 3 with a fuel-filled low-pressure chamber 5 and the pressure side via the delivery line 3 with a high-pressure accumulator 7. From this high-pressure accumulation chamber 7 lead injection lines 9 to the individual, projecting into the combustion chamber of the engine to be supplied injection valves 11, wherein the Control of the injection process in each case an electrically actuated, designed as a 3/2-way valve control valve 13 is provided on each injection valve 11.
  • the injection valve 11 is clamped by means of a clamping nut 15 axially against a valve holding body 17 on which a lateral high pressure port 19 is provided, in which a pipe socket 21 of the corresponding injection line 9 is inserted.
  • the valve holding body 17 has an axial through hole 23 into which a piston-shaped control valve member 25 of the control valve 13 is inserted on the side facing away from the injection valve 11.
  • This formed as a double-seat valve control valve 13 connects a discharge from the injection line 9 in the pipe socket 21 connecting channel 27 with a valve holding body 17 axially penetrating the high-pressure channel 29 at the injection valve 11 facing the end face of the valve holding body 17 in a known manner to a not shown pressure line in Injection valve 11 opens, on the other hand opens up to a Jerusalem speakbaren by a valve needle 31 of the injection valve 11 injection cross section of the injection valve 11.
  • the high pressure passage 29 via the control valve 13 is alternately connected to the injection line 9 or a discharge line 33, which is formed from the injection valve side part of the through hole 23 and a laxative from this return line and which opens into the low pressure chamber 5.
  • the adjusting movement of the control valve member 25 of the control valve 13 is controlled by a solenoid valve 35 which is inserted on the side facing away from the injector 11 in the valve holding body 17 and which is controlled by an electrical control unit 37, which processes a variety of operating parameters of the engine to be supplied ,
  • the control valve member 25 of the control valve 13, shown enlarged in FIG. 2, is designed as a stepped piston whose cross-section points downwards in the direction of the injection valve. 11 tapered over two conical annular surfaces.
  • a first upper annular end face 39 is provided in the region of the junction of the connecting channel 27 to the injection line 9.
  • a second annular end surface forms a first conical valve sealing surface 41, which cooperates with a first conical valve seat 43, said first sealing seat formed between the valve sealing surface 41 and the valve seat 43 closes the injection line 9 with respect to the high-pressure channel 29.
  • the control valve member 25 has a sleeve 45 to which a second, the first valve sealing surface 41 facing valve sealing surface 47 is provided, which cooperates with a second valve seat 49 on the wall of the through hole 23.
  • the valve seat surfaces 43 and 49 are formed so that they limit the adjustment movement of the control valve member 25 in both stroke directions.
  • the second sealing cross-section formed between the second valve sealing surface 47 and the second valve seat surface 49 closes the connection between the high-pressure channel 29 and the relief line 33 formed in part through the through-bore 23 into the low-pressure space 5.
  • a hydraulic working chamber 51 is provided, which is limited by the upper, the injection valve 11 facing away from face 53 of the control valve member 25 in the bore 23.
  • the hydraulic working space 51 is delimited by an intermediate disk 55 to the solenoid valve 35.
  • a discharge channel 57 discharging from the working chamber 51 is provided, which leads into a return channel opening into the low-pressure chamber 5 59 opens and which can be closed by a valve member of the solenoid valve 35.
  • This valve member of the solenoid valve 35 is formed as a valve ball 61, which is guided in a valve seat adjacent to the discharge channel 57 and the discharge port 57 is held closed by the force of a solenoid valve spring 63 at de-energized solenoid valve 35.
  • the valve ball 61 is articulated to an armature 65 of the solenoid valve 35, which is displaced against the restoring force of the spring 63 in energized solenoid valve 35 in the direction away from the working space 51, so that the valve ball 61 is lifted from the pending in the working space 51 pressure from its seat and the discharge channel 57 is opened to the return line 59.
  • a filling bore 67 is provided in the control valve member 25, which has a throttle point 69 whose cross section is smaller than the cross section of the discharge channel 57.
  • this filling bore 67 opening into the end face 53 leads below the first annular end face 39 of the control valve member 25, so that the hydraulic working chamber 51 is connected at all times to the injection line 9 via the filling bore 67.
  • a portion of the high-pressure fuel passes through the remaining between the control valve member 25 and the wall of the bore 23 annular gap 71 throttled into the hydraulic working chamber 51, so that even with a possible closure of the filling bore 67 is an emergency operation of the control valve 13th is guaranteed.
  • the fuel injection device for internal combustion engines shown in Figures 1 and 2 in a first embodiment operates in the following manner.
  • the system starts up, it first starts with the high-pressure fuel pump 1, a high-pressure fuel in common high-pressure accumulator 7 (common rail) constructed, which continues through the various injection lines 9 to the respective valve holding body 17 of the injectors 11.
  • the solenoid valve 35 is de-energized prior to the start of the injection phase, so that the valve ball 61 of the solenoid valve 35 keeps the discharge channel 57 closed.
  • the hydraulic working chamber 51 is filled via the filling bore 67 with high pressure fuel and presses the control valve member 25 due to the area ratio between the end face 53 and the first annular end face 39 with the first valve sealing surface 41 against the first valve seat 43.
  • the illustrated in Figure 3 second embodiment of the fuel injection device according to the invention differs from the first embodiment in the manner of forming the control valve member 25 of the control valve 13.
  • the control valve member 25 is now integrally formed and guided in a cylinder sleeve 73 inserted into the through hole 23 of the valve holding body 17 ,
  • a lower, the solenoid valve 35 facing away from cross-sectional part of the control valve member 25 forms a guide member 75 of the control valve member 25, which slides with little clearance in the inner diameter of the cylinder sleeve 73.
  • the filling of the hydraulic working chamber 51 in the second embodiment takes place only via the annular gap 71 between the control valve member 25 and the inner wall of the cylinder liner 73.
  • the annular gap 71 is designed as a throttle point such that the entire flow area is smaller than the cross section of the discharge channel 57 of the hydraulic working chamber 51.
  • the fuel discharge from a, the second sealing seat between the valve sealing surface 47 and the valve seat 49 downstream relief space 77 in the discharge line 23, 33 takes place via a remote from the upper end face 53 lower end face 79 in the control valve member 25 outgoing blind hole 81, from which a trained as a throttle bore transverse bore 83 dissipates, which opens into the discharge chamber 77.
  • the illustrated in Figure 5 fourth embodiment of the fuel injection device is analogous to that in the figure 3 illustrated second embodiment and additionally has a stroke-controlled throttle between the first and second sealing seat.
  • This stroke-controlled throttle is formed by an annular collar 89 on the control valve member 25, whose transition regions to the adjacent shaft portion of the control valve member 25 are conical.
  • This annular collar 89 acts together with an annular web 91 on the wall of the through hole 23 such that it is in the first valve seat 43 abutting first valve sealing surface 41 with this in coverage.
  • the fifth embodiment of the fuel injection device shown in Figure 6 in a simplified overall illustration also differs from the previous embodiments by the design of the control valve member 25.
  • the throttle cross-section between the injection line 9 and the working chamber 51 defining annular gap 71 by an annular groove 93 in a upper throttle gap 95 and a lower throttle gap 97 divided.
  • the second sealing seat controlling the overflow cross section between the high-pressure channel 29 and the discharge line 33 is designed as a slide valve seat in the fifth exemplary embodiment.
  • the control valve member 25 at its lower the Injection valve 11 facing the end of a slide head 99, whose outer diameter corresponds to the diameter of the through hole 23 in the guide portion 75 except for a very small clearance.
  • the upper, the solenoid valve 35 facing the boundary edge of the slide head 99 forms a valve control edge 101, which cooperates with the guide portion 75 of the through hole 23 and their immersion in the overlap with the guide portion 75 of the through hole 23 controlling the connection between the high pressure passage 29 and relief line 33 controls
  • the valve control edge 101 of the slide head 99 is preceded by a further annular collar 103 on the control valve member 25, which forms a Abflußdrosselstelle for flowing out of the high-pressure passage 29 in the discharge line 33 high-pressure fuel.
  • the stroke limit of the control valve member 25 in the direction of the solenoid valve 35 is effected in the fifth embodiment by the contact of the upper end face 53 of the control valve member 25 on a hydraulic working space 51 delimiting end wall 105th
  • the sixth exemplary embodiment of the fuel injection device shown in FIG. 7 is constructed analogously to the second exemplary embodiment shown in FIG. 3 and has, in addition to this, a further throttle point in the relief line 33.
  • This throttle point is formed by a throttle insert 107 inserted into the relief line 33, whose flow area is designed so that at the injection end, the closing of the injector supported and possible Nacheinspritzen is prevented.
  • the fuel from the through hole 23 via the discharge line 33 is first led to the solenoid valve 35 and from there via the return passage 59th derived to the low pressure chamber 5.
  • This flow through the solenoid valve 35 has the advantage that the solenoid valve chamber can be cooled and vented during operation of the fuel injector.
  • FIG. 8 shows a seventh exemplary embodiment, the structure of which essentially corresponds to the third exemplary embodiment shown in FIG.
  • an additional throttle point 111 is provided between the high-pressure inlet channel 27 and the valve seat 43, via which the flow of the injection fuel in the ⁇ réelleshubphase, in particular at its beginning is controlled and by the Schinnehubterrorism the control valve member 25 can be attenuated .
  • This throttling point 111 is formed in the seventh embodiment as a narrow gap between the inner wall of the cylinder liner 73 and the control valve member 25, wherein the control valve member 25 a paragraph 113 is provided, through which the narrow gap is opened after a certain opening stroke of the control valve member 25 in a larger flow area.

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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)

Abstract

La présente invention porte sur un dispositif d'injection de carburant pour moteurs à combustion interne, avec une pompe haute pression (1) doté d'un collecteur commun haute pression (Common Rail) que l'on remplit de carburant. Ce collecteur est relié par des conduites d'injection (9) à des soupapes injectrices (11) émergeant dans la chambre de combustion du moteur à alimenter. Les mouvements d'ouverture et de fermeture de ces soupapes sont commandés par une soupape pilote à commande électrique (13), conçue comme une soupape à 3/2 voies qui relie un canal haute pression (29) débouchant sur une ouverture d'injection de la soupape injectrice (11) avec la conduite d'injection (9) ou une conduite de décharge (33). Sur la tige (25) de la soupape pilote (13) est prévue une chambre de travail hydraulique (51) que l'on remplit de carburant HP et que l'on peut manoeuvrer pour régler la position de la tige (25) de soupape pilote (13) dans un canal de décharge (57).

Claims (11)

  1. Dispositif d'injection de carburant pour des moteurs à combustion interne ayant une chambre collectrice à haute pression commune (7), rempli de carburant par une pompe à haute pression (1) raccordée par des conduites d'injection (9) à des injecteurs (11), dont les mouvements d'ouverture et de fermeture sont commandés par une soupape de commande (13) électrique disposée sur l'injecteur (11),
    la soupape de commande (13) étant une soupape à 3/2 voies, avec un organe de soupape de commande (25) présentant deux faces d'étanchéité (41, 47), reliant un canal à haute pression (29) débouchant sur une ouverture d'injection de l'injecteur (11) à la conduite d'injection (9) ou à une conduite de décharge (33),
    l'organe de soupape de commande (25) étant actionné par une pression régnant dans une chambre de travail (51) contre une force de rappel, la chambre de travail (51) étant une chambre de travail hydraulique (51) remplie avec une haute pression de carburant sur l'organe de soupape de commande (25) de la soupape à 3/2 voies (13), sollicitant l'organe de soupape de commande (25), contre une force d'ouverture hydraulique agissant sur celui-ci, dans le sens de fermeture d'une section transversale de passage entre la conduite d'injection (9) et le canal à haute pression (29) et commandée dans une chambre de décharge (59),
    caractérisé en ce que
    la pression dans la chambre de travail (51) est commandée par un flux entrant constant et un flux sortant réglable,
    la chambre de travail hydraulique (51) est délimitée par une face frontale supérieure (53) de l'organe de soupape de commande en forme de piston (25),
    la chambre de travail (51) est reliée en permanence à la conduite d'injection (9) par une section transversale d'étranglement (69, 71),
    un canal de décharge (57) pouvant se fermer, et dont la section transversale est plus grande que la section transversale d'étranglement (69, 71) vers la conduite d'injection (9), part de la chambre de travail (51),
    le canal de décharge (57) peut être ouvert ou fermé par une soupape de réglage électrique (35), et
    sur l'organe de soupape de commande (25), dans la zone du recouvrement avec la conduite d'injection (9), une face frontale annulaire (39), sur laquelle la haute pression de carburant agissant sur l'organe de soupape de commande (25) en sens inverse de la pression régnant dans la chambre de travail (51), génère la force hydraulique d'ouverture sur l'organe de soupape de commande (25) et le déplace lorsque le canal de décharge (57) est ouvert, dans la position dans laquelle la section transversale de passage entre la conduite d'injection (9) et le canal à haute pression (29) est ouverte.
  2. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé en ce que
    la soupape de réglage (35) est une soupape magnétique dont l'organe de réglage est formé par une bille de soupape (61) coopérant avec un siège de soupape adjacent au canal de décharge (57).
  3. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé en ce que
    la section transversale d'étranglement vers la conduite d'injection (9) est formée par un alésage d'étranglement (69) dans l'organe de soupape de commande (25).
  4. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé en ce que
    la soupape de commande à 3/2 voies (13) est une soupape à double siège, avec un premier siège d'étanchéité (41, 43) régissant l'écoulement entre la conduite d'injection (9) et le canal à haute pression (29) et un deuxième siège d'étanchéité (47, 49) régissant l'écoulement entre le canal à haute pression (29) et la conduite de décharge (33), les deux faces des sièges d'étanchéité (43, 49) se faisant face et limitant le mouvement de réglage de l'organe de soupape de commande (25) dans une direction de levée.
  5. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé en ce que
    la section transversale d'étranglement entre la chambre de travail (51) et la conduite d'injection (9) est une fente annulaire (71) entre la surface latérale de l'organe de soupape de commande en forme de piston (25) et la paroi d'un alésage cylindrique (23) guidant celui-ci.
  6. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé par
    l'organe de soupape de commande (25) réalisé d'une seule pièce.
  7. Dispositif d'injection de carburant selon la revendication 4,
    caractérisé par
    une ouverture de passage sur l'organe de soupape de commande (25) entre le deuxième siège d'étanchéité (47, 49) et la conduite de décharge (33).
  8. Dispositif d'injection de carburant selon la revendication 7,
    caractérisé en ce que
    l'ouverture de passage est un alésage à trou borgne (81) débouchant dans la conduite de décharge (23, 33), dans laquelle débouche un alésage transversal (83).
  9. Dispositif d'injection de carburant selon la revendication 7,
    caractérisé en ce que
    l'ouverture de passage est une entaille de surface (85) sur l'organe de soupape de commande (25), qui n'est commandée qu'après la fermeture de la section transversale de transfert entre la conduite d'injection (9) vers le canal à haute pression (29).
  10. Dispositif d'injection de carburant selon la revendication 4, caractérisé en ce que
    dans une première phase de l'opération d'injection, un étranglement commandé par levée (89, 91), entre les deux sièges d'étanchéité (43, 49), étrangle la quantité de carburant débordant de la conduite d'injection (9) vers le canal à haute pression (29).
  11. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé par
    un point d'étranglement (107) inséré dans la conduite de décharge (33) commandée par la soupape de commande (13).
EP97943768A 1997-01-21 1997-09-13 Dispositif d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0898650B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19701879A DE19701879A1 (de) 1997-01-21 1997-01-21 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19701879 1997-01-21
PCT/DE1997/002053 WO1998031933A1 (fr) 1997-01-21 1997-09-13 Dispositif d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0898650A1 EP0898650A1 (fr) 1999-03-03
EP0898650B1 true EP0898650B1 (fr) 2006-11-22

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EP97943768A Expired - Lifetime EP0898650B1 (fr) 1997-01-21 1997-09-13 Dispositif d'injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US6431148B1 (fr)
EP (1) EP0898650B1 (fr)
JP (1) JP3980069B2 (fr)
DE (2) DE19701879A1 (fr)
WO (1) WO1998031933A1 (fr)

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DE19921878C2 (de) * 1999-05-12 2001-03-15 Daimler Chrysler Ag Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE19923421C2 (de) * 1999-05-21 2003-03-27 Bosch Gmbh Robert Injektor
DE19928846A1 (de) * 1999-06-24 2001-03-08 Bosch Gmbh Robert Common-Rail-Injektor
DE19937713C1 (de) 1999-08-10 2001-03-15 Siemens Ag Steuerventilanordnung zum Einsatz in einem Kraftstoffinjektor für Verbrennungsmotoren
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DE59712768D1 (de) 2007-01-04
EP0898650A1 (fr) 1999-03-03
US6431148B1 (en) 2002-08-13
JP2000507327A (ja) 2000-06-13
WO1998031933A1 (fr) 1998-07-23
JP3980069B2 (ja) 2007-09-19
DE19701879A1 (de) 1998-07-23

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