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EP1478840B1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
EP1478840B1
EP1478840B1 EP03704252A EP03704252A EP1478840B1 EP 1478840 B1 EP1478840 B1 EP 1478840B1 EP 03704252 A EP03704252 A EP 03704252A EP 03704252 A EP03704252 A EP 03704252A EP 1478840 B1 EP1478840 B1 EP 1478840B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
chamber
control
valve needle
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
EP03704252A
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German (de)
English (en)
Other versions
EP1478840A1 (fr
Inventor
Detlev Potz
Peter Boehland
Thomas Kuegler
Andreas Koeninger
Predrag Nunic
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 EP1478840A1 publication Critical patent/EP1478840A1/fr
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Publication of EP1478840B1 publication Critical patent/EP1478840B1/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
    • 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
    • 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
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve is for example from the published patent application DE 41 15 477 A1 known.
  • a housing there is an outer valve needle and an inner valve needle guided therein. Both valve needles cooperate with their combustion chamber-side end with a valve seat surface in which two rows of injection openings are formed.
  • the outer injection opening row is controlled by the outer valve needle, the inner row of injection openings correspondingly by the inner valve needle.
  • fuel is supplied under high pressure to the injection openings, which discharges under the control of the valve needles through the injection openings and is injected from there into the combustion chamber of the internal combustion engine.
  • a control chamber In the housing of the fuel injection valve, a control chamber is formed, the pressure of which acts on the end face of a pressure piston which is connected to the inner valve needle. In this way, results from the pressure in the control chamber, a closing force on the inner valve needle, which holds them in contact with the valve seat surface.
  • the control room can over a control valve connected to the injection pressure or be relieved in a leakage oil space, so that in this way the pressure in the control room can be controlled.
  • the opening force on the inner and outer valve needle is generated in the cited prior art by application of fuel pressure of each formed on the valve needles pressure surface, wherein the pressure at which open the valve needles, is referred to as the opening pressure.
  • the known fuel injection valve has the disadvantage that the closing force on the outer valve needle is not generated hydraulically, but via a firmly biased closing spring. Therefore, the opening pressure of the outer valve needle is not controllable, and it can be injected through the outer Einspritzö réelles #2 only with a minimum pressure corresponding to the opening pressure of the outer valve needle.
  • the prior art has the disadvantage that the control valve, which regulates the pressure in the control chamber, is designed as a 3/2-way valve with slide seat, so that it is relatively complicated and therefore expensive to manufacture. It is thus not possible in the known fuel injection valve to control the injection cross section as desired.
  • an injection valve with an outer and an inner valve needle is known, which are guided into each other and each control an injection opening row.
  • a first control chamber which acts on the outer valve needle
  • a second control chamber which acts on the inner valve needle, formed, wherein both control chambers are interconnected.
  • the control chamber Via a solenoid valve, the control chamber can be connected to a leakage oil space, so that the pressure in the first control chamber is lowered and - depending on the duration that opens the solenoid valve - in the second control chamber.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that both the inner and the outer valve needle via only one control valve can be controlled.
  • a control chamber is formed, which is connected to the high pressure passage and beyond with a control pressure chamber. Due to the pressure in the control chamber, a closing force is exerted on the outer valve needle, at least indirectly.
  • a control valve is formed, through which the control chamber is connectable to a leakage oil chamber, so that the pressure in the control chamber and, because of the connection with the control chamber, also in the control pressure chamber via the control valve can be lowered well below the injection pressure, so that the closing force can be controlled to the inner and the outer valve needle.
  • the control valve has a valve space connected to the control space and a valve member which is controlled by an actuator.
  • the actuator is designed here as an electrical piezo actuator. As a result, the valve member can be precisely controlled and drive the valve member directly to the desired position.
  • valve member cooperates in a first switching position with a first valve seat and in a second switching position with a second valve seat, wherein the valve chamber is sealed in the first switching position against the leakage oil chamber and is connected in the second switching position with the leakage oil space.
  • valve chamber of the control valve can be connected to the high-pressure passage via a connecting channel, with the valve member closing the connecting channel when it rests against the second valve seat.
  • connection channel is ineffective and does not interfere with the further function of the pressure control in the control room.
  • the high-pressure passage is released, and it can flow fuel at the injection pressure in the valve chamber and from there into the control chamber.
  • an outer pressure piston is arranged in the housing, which is connected to the outer valve needle and whose end face defines the control chamber. In this way, a hydraulic force results from the pressure in the control chamber on the end face of the outer pressure piston, so that a closing force is exerted on the outer valve needle.
  • the outer pressure piston comes in the opening stroke of the outer valve needle to a wall of the control chamber to the system, so that the connection of the control chamber is interrupted to the high-pressure channel.
  • control pressure chamber is formed in the outer pressure piston and connected by a bore in the outer pressure piston with the control chamber.
  • the leakage oil space compared to the injection pressure significantly lower pressure, preferably atmospheric pressure.
  • FIG. 1 is a longitudinal section through an inventive fuel injection valve shown.
  • the fuel injection valve has a housing 1, which comprises a valve body 3, an intermediate body 7, an intermediate disk 9, a control body 12 and a holding body 14, wherein these components abut each other in the enumerated sequence. All these parts of the housing 1 are hereby pressed together by a clamping nut 5 with their contact surfaces.
  • a high-pressure passage 10 is formed, which is connected at one end to a high-pressure fuel source, not shown in the drawing and extends through the holding body 14, the control body 12, the washer 9 and the intermediate body 7 into the valve body 3.
  • the high pressure passage 10 opens into a pressure chamber 26, which is designed as a radial extension of a bore 16 formed in the valve body 3.
  • the bore 16 is closed at its combustion chamber end by a seat surface 24, wherein in the seat 24 injection openings 30 are formed, which connect the bore 16 with the combustion chamber of the internal combustion engine.
  • a piston-shaped, outer valve needle 20 is arranged, which is sealingly guided in a combustion chamber remote from the bore 16.
  • the outer valve needle 20 tapers from the guided portion to the combustion chamber to form a pressure shoulder 27 and merges at its combustion chamber end in a valve sealing surface 32, with which it bears against the seat surface 24 in the closed position.
  • annular channel 28 is formed, which connects the pressure chamber 26 with the seat surface 24, wherein the pressure shoulder 27 is disposed at the level of the pressure chamber 26.
  • the outer valve needle 20 closes the injection openings 30 against the fuel in the annular channel 28, so that fuel can flow into the injection openings 30 only when the outer valve needle 20 lifted from the seat surface 24.
  • the outer valve needle 20 is designed as a hollow needle and has a longitudinal bore 21.
  • an inner valve needle 22 is longitudinally displaceable, which also comes with its combustion chamber end end to the seat surface 24 in the closed position to the plant.
  • FIG. 2 is an enlargement of the section marked II FIG. 1 shown, so the area of the seat 24.
  • the injection openings 30 in the seat surface 24 are grouped in an outer injection opening row 130 and an inner injection opening row 230.
  • the outer valve needle 20 has at its combustion chamber end, a conical valve sealing surface 32, which has a larger opening angle than the likewise conical seat 24. As a result, at the outer edge of the sealing surface 32, a sealing edge 34 is formed in the closed position of the outer valve needle 20 at the seat 24 comes to rest.
  • the sealing edge 34 is in this case arranged upstream of the outer injection opening row 130, so that upon contact of the sealing edge 34 on the seat surface 24, the injection openings of the outer injection opening row 130 are sealed against the annular channel 28.
  • a conical pressure surface 36 is formed, which in turn adjoins an also conical conical surface 38, which forms the end of the inner valve needle 22.
  • a sealing edge 37 is formed, which comes into abutment in the closed position of the inner valve needle 22 on the seat surface 24.
  • the installation of the sealing edge 37 in this case takes place between the outer injection opening row 130 and the inner injection opening 230, so that when the inner valve needle 22 on the seat 24 only the inner row of injection openings 230 is sealed against the annular space 28, but not the outer row of injection openings 130th
  • FIG. 3 shows an enlargement of FIG. 1
  • a piston bore 45 is formed, in which a pressure piston 40 is arranged, which abuts with its end facing the combustion chamber on the outer valve needle 20 in the designated III section, ie in the region of the intermediate body 7, intermediate disc 9 and control body.
  • a spring chamber 43 is formed, in which between a contact surface 41 of the spring chamber 43 and an annular surface 39 of the outer pressure piston 40 a closing spring 44 is arranged under pressure bias, which surrounds the outer pressure piston 40 on a part of its length.
  • the outer pressure piston 40 is pressed in the direction of the valve body 3 and thus also the outer valve needle 20 in the direction of the seat 24.
  • a guide bore 47 is formed in the longitudinal direction, in which an inner pressure piston 42 is guided , which rests with its combustion chamber end on the inner valve needle 22.
  • the inner pressure piston 42 is longitudinally displaceable in the outer pressure piston 40 and moves synchronously with the inner valve needle 22.
  • a control chamber 50 is limited, via a in the outer pressure piston 40th formed connecting bore 55 is connected to a control pressure chamber 52 which is bounded by the guide bore 47 and the combustion chamber facing away from end face 53 of the inner pressure piston 42.
  • the control chamber 50 is connected via an inlet throttle 70 to the high-pressure passage 10 and via an outlet throttle 72 with a formed in the control body 12 valve chamber 68.
  • a valve member 60 is arranged, which is formed substantially hemispherical and forms a control valve 58.
  • the flattened side faces the intermediate disk 9, while the hemispherical side of the valve member 60 is connected to a pressure piece 48, which is guided in a receiving body 13 arranged in the holding body 14.
  • the pressure piece 48 is in this case longitudinally displaceable by an actuator 46 and thereby also moves the valve member 60 in the valve chamber 68, wherein the actuator is designed here as a piezoelectric actuator.
  • the pressure member 48 is surrounded by a leakage oil chamber 78, which always has a low pressure because of its connection with a drain oil system, not shown in the drawing.
  • the intermediate disc 9 faces away in the valve chamber 68 a first valve seat 62 is formed, on which the valve member 60 can come with its spherical valve sealing surface 66 to the plant.
  • FIG. 4 shows a cross section through FIG. 3 along the line IV-IV.
  • the course of the transverse channel 76 as a semicircular groove on the abutment surface 7 of the intermediate disc 9 facing the intermediate body 7 becomes clear here.
  • the inlet throttle 70, the outlet throttle 72, the connecting channel 74 and the high-pressure passage 10 are also visible.
  • the function of the fuel injection valve is as follows: At the beginning of the injection cycle, the fuel injection valve is in the closed position, ie both the outer valve needle 20 and the inner valve needle 22 are in contact with the seat surface 24 and close both the inner injection opening row 230 and the outer injection opening row 130. Since the valve member 60 rests against the first valve seat 62, both the control chamber 50 and the control pressure chamber 52 are connected via the inlet throttle 70 to the high pressure passage 10, so that both the control chamber 50 and the control pressure chamber 52, the high fuel pressure of the high pressure passage 10 prevails which corresponds to the injection pressure.
  • the end face 51 of the outer pressure piston 40 has a larger hydraulically effective area than the pressure shoulder 27 of the outer valve needle 20, so that the outer valve needle 20 remains in the closed position.
  • the force of the closing spring 44 plays only a minor role; the closing spring 44 is mainly used to hold the outer valve needle 20 in the closed position, when the internal combustion engine is not working. Also in the valve chamber 68 prevails through the connection via the connecting channel 74 and also via the outlet throttle 72, the pressure in the high-pressure passage 10. In the leakage oil chamber 78, however, there is a low pressure, which generally corresponds approximately to the atmospheric pressure.
  • the actuator 46 is actuated, and the valve member 60 moves together with the pressure piece 48 from the first valve seat 62 away to the second valve seat 64.
  • the valve chamber 68 is connected to the leakage oil chamber 78, so that the valve chamber 68 and also the control chamber 50 are relieved of pressure via the outlet throttle 72.
  • the connecting channel 74 is closed, so that no more fuel can flow into the valve chamber 68 via the transverse channel 76.
  • the inlet throttle 70 and the outlet throttle 72 are dimensioned such that the pressure in the control chamber 50 drops, but not to the level of the leakage oil chamber 78.
  • valve member 60 If it is intended, for example for a pilot injection, to inject fuel into the combustion chamber of the internal combustion engine only through the outer injection opening row 130, then, by actuating the actuator 46, the valve member 60 must be moved again so that the connection of the valve space 68 to the leakage oil space 78 is interrupted. As a result, the connection of the high-pressure passage 10 via the connecting channel 74 to the valve chamber 68 is restored, so that fuel flows with injection pressure from the high-pressure passage 10 via the outlet throttle 72 and via the inlet throttle 70 into the control chamber 50. There again, a high fuel pressure level builds up, which presses the outer pressure piston 40 and thus also the outer valve needle 20 back into the closed position.
  • valve member 60 remains in abutment with the second valve seat 64.
  • the feed throttle 70 is closed by abutment of the end face 51 of the outer pressure piston 40 on the intermediate disk 9.
  • the pressure in the control pressure chamber 52 can thus further drop via the outlet throttle 72 and the connection of the valve chamber 68 to the leakage oil chamber 78 until the hydraulic force on the pressure surface 36 of the inner valve needle 22 is greater than the hydraulic force on the end face 53 of the inner pressure piston 42nd
  • the inner valve needle 22 now lifts with the sealing edge 37 from the seat surface 24, and fuel is additionally injected through the inner injection port row 230.
  • a selective opening can also be achieved by means of a middle position of the control valve 58.
  • the valve member 60 is moved by means of the piezo-actuator 48 in a middle position between the first valve seat 62 and the second valve seat 64, so that all connections to the valve chamber 68 are opened.
  • fuel flows from the valve chamber 68 into the leakage oil chamber 78, on the other hand via the connecting channel 74 constantly in the valve chamber 68, so that only a certain pressure drop in the valve chamber 68 sets, which is still significantly above the pressure of the leakage oil chamber 78.
  • This pressure is sufficient to hold the inner valve needle 22 in its closed position, but the closing force on the outer valve needle 20 is reduced to the extent that it opens.
  • the injection is also terminated here again in the manner already described above by switching the control valve 58.
  • the actuator 46 is a piezoelectric actuator in this embodiment.
  • the valve member 60 in the valve chamber 68 requires only a small stroke for its function, as it can usually be applied by a piezoelectric actuator. If necessary, a hydraulic translator can be provided with which larger strokes can be realized and which is well known from the prior art.
  • piezo actuators have the advantage that they can switch extremely fast. It is thus possible without any problems in the manner described above to carry out a precise pre-injection only through the outer injection opening row 130.

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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 (8)

  1. Soupape d'injection de carburant pour moteurs à combustion interne, comprenant un boîtier (1), dans lequel sont disposées, dans un alésage (16), une aiguille de soupape extérieure (20) et une aiguille de soupape intérieure (22) guidée dans celle-ci, l'aiguille de soupape extérieure (20) venant en appui dans une position de fermeture contre un siège de soupape (24) disposé à une extrémité du boîtier (1) du côté de la chambre de combustion, et commandant une rangée extérieure d'ouvertures d'injection (130) par un mouvement longitudinal dans une direction d'ouverture, et l'aiguille de soupape intérieure (22) s'appliquant également contre le siège de soupape (24) dans une position de fermeture et commandant une rangée intérieure d'ouvertures d'injection (230) par un mouvement longitudinal dans une direction d'ouverture, lesquelles rangées d'ouvertures d'injection (130 ; 230), dans l'état commandé des aiguilles de soupape (20 ; 22), recevant du carburant sous pression d'un espace de pression (26) réalisé dans le boîtier (1), lequel carburant est de là injecté dans la chambre de combustion du moteur à combustion interne, et comprenant un épaulement de pression (27) qui est réalisé sur l'aiguille de soupape extérieure (20) et qui est sollicité par la pression de carburant dans l'espace de pression (26) de telle sorte qu'il se produise ainsi une force agissant dans la direction d'ouverture sur l'aiguille de soupape extérieure (20), et comprenant une surface de pression (36) sur l'aiguille de soupape intérieure (22), qui, après le soulèvement de l'aiguille de soupape extérieure (20) du siège de soupape (24), est sollicitée par la pression de carburant dans la direction d'ouverture, et comprenant un canal haute pression (10) s'étendant dans le boîtier (1), lequel débouche dans l'espace de pression (26) et dans lequel règne toujours du carburant sous haute pression, et comprenant un espace de commande de pression (52) rempli de carburant dont la pression peut être commandée et dont la pression permet d'exercer au moins de manière indirecte une force de fermeture sur l'aiguille de soupape intérieure (22), un espace de commande (50) rempli de carburant étant réalisé dans le boîtier (1), dont la pression permet d'exercer au moins de manière indirecte une force de fermeture sur l'aiguille de soupape extérieure (20), et comprenant un étranglement d'afflux (70), par lequel l'espace de commande (50) est connecté au canal haute pression (10), et comprenant un étranglement de sortie (72), par le biais duquel l'espace de commande (50) peut être connecté à un espace d'huile de fuite sans pression (78), l'étranglement de sortie (72) pouvant être fermé par une soupape de commande (58) et l'étranglement de sortie (72) et l'étranglement d'afflux (70) étant dimensionnés de telle sorte que lorsque l'étranglement de sortie (72) est ouvert, plus de carburant sorte de l'espace de commande (50) que n'entre par l'étranglement d'afflux (70), et comprenant une connexion (55) entre l'espace de commande (50) et l'espace de pression de commande (52), l'espace de pression de commande (52) étant fermé à l'exception de la connexion (55), et la connexion (55) étant dimensionnée de telle sorte que lors de l'ouverture de l'étranglement de sortie (72) par la soupape de commande (58), d'abord la pression diminue dans l'espace de commande (50) et seulement avec un retard dans le temps, diminue aussi dans l'espace de pression de commande (52), la soupape de commande (58) présentant un espace de soupape (68) connecté à l'espace de commande (50) et un organe de soupape (60) pouvant être commandé par un actionneur piézoélectrique (46).
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que l'organe de soupape (60) coopère dans une première position de commutation avec un premier siège de soupape (62) et dans une deuxième position de commutation avec un deuxième siège de soupape (64), l'espace de soupape (68) dans la première position de commutation étant rendu étanche vis-à-vis de l'espace d'huile de fuite (78) et étant connecté à l'espace d'huile de fuite (78) dans la deuxième position de commutation.
  3. Soupape d'injection de carburant selon la revendication 2, caractérisée en ce que l'espace de soupape (68) peut être connecté par le biais d'un canal de connexion (74 ; 76) au canal haute pression (10), l'organe de soupape (60) fermant le canal de connexion (74) lors de son application contre le deuxième siège de soupape (64).
  4. Soupape d'injection de carburant selon la revendication 2, caractérisée en ce que l'organe de soupape (60) peut être amené dans une position centrale de sorte que l'organe de soupape (60) ne s'applique ni contre le premier siège de soupape (62) ni contre le deuxième siège de soupape (64).
  5. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que dans le boîtier (1) est disposé un piston de pression extérieur (40), qui est connecté à l'aiguille de soupape extérieure (20) et dont la surface frontale (51) limite l'espace de commande (50), de sorte qu'une force de fermeture soit exercée sur l'aiguille de soupape extérieure (20) par la force hydraulique appliquée à cette surface frontale (51).
  6. Soupape d'injection de carburant selon la revendication 5, caractérisée en ce que le piston de pression extérieur (40), lors du mouvement d'ouverture de l'aiguille de soupape extérieure (20), vient en appui contre une paroi de l'espace de commande (50) et interrompt de ce fait l'étranglement d'entrée (70) qui relie l'espace de commande (50) au canal haute pression (10).
  7. Soupape d'injection de carburant selon la revendication 5, caractérisée en ce que l'espace de commande de pression (52) est réalisé dans le piston de pression extérieur (40) et en ce que la connexion à l'espace de commande (50) est réalisée sous la forme d'un alésage de connexion (55) dans le piston de pression extérieur (40).
  8. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce qu'il règne dans l'espace d'huile de fuite (78) toujours une pression nettement inférieure par rapport à la pression d'injection, de préférence la pression atmosphérique.
EP03704252A 2002-02-14 2003-01-27 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP1478840B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10205970A DE10205970A1 (de) 2002-02-14 2002-02-14 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10205970 2002-02-14
PCT/DE2003/000210 WO2003069151A1 (fr) 2002-02-14 2003-01-27 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1478840A1 EP1478840A1 (fr) 2004-11-24
EP1478840B1 true EP1478840B1 (fr) 2009-12-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03704252A Expired - Lifetime EP1478840B1 (fr) 2002-02-14 2003-01-27 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (9)

Country Link
US (1) US7051958B2 (fr)
EP (1) EP1478840B1 (fr)
JP (1) JP2005517858A (fr)
KR (1) KR20040091522A (fr)
CN (1) CN100366889C (fr)
AT (1) ATE453798T1 (fr)
DE (2) DE10205970A1 (fr)
PL (1) PL201040B1 (fr)
WO (1) WO2003069151A1 (fr)

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ATE453798T1 (de) 2010-01-15
PL201040B1 (pl) 2009-02-27
PL363037A1 (en) 2004-11-15
KR20040091522A (ko) 2004-10-28
DE50312286D1 (de) 2010-02-11
JP2005517858A (ja) 2005-06-16
CN1533474A (zh) 2004-09-29
DE10205970A1 (de) 2003-09-04
EP1478840A1 (fr) 2004-11-24
US7051958B2 (en) 2006-05-30
CN100366889C (zh) 2008-02-06
WO2003069151A1 (fr) 2003-08-21
US20040129804A1 (en) 2004-07-08

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