EP1335128B1 - Soupape hydraulique à haute pression, notamment pour un dispositif d'injection de carburant d'un moteur - Google Patents

Soupape hydraulique à haute pression, notamment pour un dispositif d'injection de carburant d'un moteur Download PDF

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Publication number
EP1335128B1
EP1335128B1 EP03001990A EP03001990A EP1335128B1 EP 1335128 B1 EP1335128 B1 EP 1335128B1 EP 03001990 A EP03001990 A EP 03001990A EP 03001990 A EP03001990 A EP 03001990A EP 1335128 B1 EP1335128 B1 EP 1335128B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
pressure
sealing surface
valve seat
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
EP03001990A
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German (de)
English (en)
Other versions
EP1335128A3 (fr
EP1335128A2 (fr
Inventor
Nestor Rodriguez-Amaya
Walter Egler
Christoph Hollmann
Hubert Greif
Godehard Nentwig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1335128A2 publication Critical patent/EP1335128A2/fr
Publication of EP1335128A3 publication Critical patent/EP1335128A3/fr
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Publication of EP1335128B1 publication Critical patent/EP1335128B1/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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Definitions

  • the invention relates to a valve for controlling a connection in a high-pressure fluid system, in particular a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a valve is known from EP 0 840 003 A.
  • This valve is for controlling a connection in a fuel injection device for an internal combustion engine.
  • the valve has a valve member, which is displaceably guided in the direction of its longitudinal axis, which projects into a pressure chamber and which has a sealing surface in the pressure chamber at an end face arranged transversely to its longitudinal axis.
  • the valve member cooperates with its sealing surface with a valve seat arranged transversely to its longitudinal axis for closing an opening, which is surrounded by the valve seat, with respect to the pressure chamber.
  • In the pressure chamber while there is high pressure and the opening leads to a discharge space, wherein the connection of the pressure chamber with the discharge chamber and thus the pressure in the pressure chamber is controlled by the valve member.
  • the valve according to the invention with the features of claim 1 has the advantage that the operability of the valve is ensured even over a long period of use of the valve. Through the passages on the valve member targeted low leakage is caused, which is irrelevant to the function of the valve, and by the annular surface is achieved that only a low flow velocity occurs during the outflow of liquid from the pressure chamber, so that no erosion on the valve member or occurs at the valve seat.
  • the valve thus has a total of low leakage, but remains at least approximately constant over the duration of use.
  • the embodiment according to claim 3 allows a simple design of the passages.
  • the embodiment according to claim 4 allows a low flow velocity of the effluent from the pressure chamber liquid.
  • the embodiment according to claim 6 ensures that the flow velocity of the outflowing liquid is at least approximately constant.
  • the embodiment of claim 7 allows easy production of the valve member.
  • FIG. 1 shows a fuel injection device for an internal combustion engine in a longitudinal section in a simplified representation with a valve
  • Figure 2 shows an enlarged view of the valve in a longitudinal section
  • Figure 3 shows the valve in a cross section along line III-III in Figure 2
  • Figure 4 is a in Figure 2 with IV designated section of the valve in an enlarged view.
  • FIG. 1 shows a fuel injection device for an internal combustion engine of a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the fuel injection device is preferably designed as a so-called pump-nozzle unit and has for each cylinder of the internal combustion engine in each case a high-pressure fuel pump 10 and a fuel injection valve 12 connected thereto, the one forming a common structural unit.
  • the fuel injector may be formed as a so-called pump-line-nozzle system in which the high-pressure fuel pump and the fuel injection valve of each cylinder are arranged separately from each other and connected to each other via a line.
  • the high-pressure fuel pump 10 has a pump body 14 with a cylinder bore 16 in which a pump piston 18 is tightly guided, which is driven at least indirectly by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19 in a lifting movement.
  • the pump piston 18 defines in the cylinder bore 16 a pump working chamber 22, in which the delivery stroke of the pump piston 18 compresses fuel under high pressure.
  • the pump working chamber 22 is supplied with fuel from a fuel tank 24 of the motor vehicle.
  • the fuel injection valve 12 has a valve body 26 connected to the valve body 14, which may be formed in several parts, and in which an injection valve member 28 is guided longitudinally displaceably in a bore 30.
  • the valve body 26 At its end region facing the combustion chamber of the cylinder of the internal combustion engine, the valve body 26 has at least one, preferably a plurality of injection openings 32.
  • the injection valve member 28 has, at its end region facing the combustion chamber, an approximately conical sealing surface 34, for example, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the injection openings 32 are discharged.
  • valve body 26 is between the injection valve member 28 and the bore 30 to the valve seat 36 toward an annular space 38, 38 present in its valve seat 36 facing away from the end portion by a radial extension of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 passes.
  • the injection valve member 28 has at the level of the pressure chamber 40 by a cross-sectional reduction on a pressure shoulder 42.
  • a prestressed closing spring 44 At the end remote from the combustion chamber of the injection valve member 28 engages a prestressed closing spring 44, through which the injection valve member 28 is pressed to the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of the valve body 26, which adjoins the bore 30.
  • a further bore 48 in which a control piston 50 is guided tightly, which is connected to the injection valve member 28.
  • the bore 48 forms a control pressure chamber 52, which is limited by the control piston 50 as a movable wall.
  • the control piston 50 is supported on the injection valve member 28 via a piston rod 51, which is smaller in diameter, and can be connected to the injection valve member 28.
  • the control piston 50 may be formed integrally with the injection valve member 28, but is preferably connected to the injection valve member 28 as a separate part for reasons of assembly.
  • a channel 60 to the pressure chamber 40 of the fuel injection valve 12.
  • a channel 62 to the control pressure chamber 52.
  • the control pressure chamber 52 is also a channel 64 connectable which forms a connection to a discharge space, as the at least indirectly can serve the fuel tank 24 or another area in which a low pressure prevails.
  • a connection 66 leads to a discharge space, which is replaced by a first electrically operated control valve 68 is controlled.
  • the control valve 68 may be formed as shown in Figure 1 as a 2/2-way valve.
  • the circuit of the control valve 68 between its two switching positions is effected by an actuator 69, which may for example be an electromagnet, against a return spring.
  • a second electrically operated control valve 70 is provided for controlling the pressure in the control pressure chamber 52.
  • the second control valve 70 is designed as a 3/2-way valve, which can be switched between two switching positions. In a first switching position of the control valve 70 is connected by this the control pressure chamber 52 to the pump chamber 22 and separated from the discharge chamber 24 and in a second switching position of the control valve 70 is separated by this the control pressure chamber 52 from the pump working chamber 22 and connected to the discharge chamber 24.
  • a throttle point 63 is provided in the connection 64 of the control pressure chamber 52 with the discharge chamber 24, a throttle point 65 is provided.
  • the orifice 63 may be located upstream of the control valve 70 in the connection 62 or downstream of the control valve 70 in the connection 62, as shown in FIG.
  • the control valve 70 has an actuator 71, which may be an electromagnet, and by means of which the control valve 70 can be switched over against a return spring between its two switching positions.
  • the two control valves 68,70 are controlled by an electronic control device 67.
  • the second control valve 70 will be explained in more detail with reference to Figures 2 and 3.
  • the control valve 70 has a valve member 72 which is displaceably guided in the direction of its longitudinal axis 73 via a shaft 74 and which protrudes into a valve pressure chamber 77 with an enlarged end portion 75 in diameter relative to the shaft 74.
  • In the valve pressure chamber 77 opens on the one hand, the connection 62 to the pump working chamber 22 and on the other hand, the connection 64 to the relief space 24.
  • the connection 62 extends as a formed between the shaft 74 and a surrounding hole 76 annular gap.
  • the bore 76 is formed smaller in diameter than the valve pressure chamber 77.
  • connection 64 opens into an opening 78 in the valve pressure chamber 77 and is surrounded by a surface 79 which extends transversely, preferably at least approximately perpendicular to the longitudinal axis 73 of the valve member 72 and the one Valve seat forms.
  • the valve member 72 has towards the valve seat 79 towards an at least approximately cylindrical projection 80, whose end face forms a sealing surface 81 which extends transversely, preferably at least approximately perpendicular to the longitudinal axis 73 of the valve member 72.
  • the projection 80 has a smaller diameter than the end portion 75 of the valve member 72, wherein the diameter of the projection 80, however, is greater than that of the opening 78.
  • a recess 82 is formed frontally, so that the sealing surface 81 is annular ,
  • the inner projection 81 of the valve member 72 is surrounded by a further at least approximately cylindrical outer projection 83 with a larger diameter.
  • a sealing surface 81 surrounding annular surface 84 is formed, which is arranged offset in the direction of the longitudinal axis 73 of the valve member 72 to the sealing surface 81, so that the sealing surface 81 relative to the annular surface 84 by a dimension A to the valve seat 79 out protrudes.
  • the Ring surface 84 extends transversely to the longitudinal axis 73 of the valve member 72, preferably at least approximately perpendicular to the longitudinal axis 73.
  • Between the inner shoulder 80 and the outer shoulder 83 is an end face also recessed against the annular surface 84 annular groove 85 is formed.
  • a plurality of openings 86 are provided distributed over the circumference, which preferably extend at least approximately radially to the longitudinal axis 73 of the valve member 72.
  • the apertures 86 establish a connection between the valve pressure chamber 77 surrounding the jacket of the inner projection 80 and the recess 82 within the projection 80.
  • the openings 86 are preferably designed as outgoing from the sealing surface 81, introduced into the neck 80 grooves.
  • a conical transition surface 87 is provided, which forms a second valve seat.
  • a second, conical sealing surface 88 is arranged on the valve member 72, which cooperates with the valve seat 87 for controlling the connection 62.
  • the valve member 72 In the first switching position of the control valve 70, the valve member 72 abuts with its second sealing surface 88 on the second valve seat 87, so that the connection 62 is separated to the pump working chamber 22.
  • the valve member 72 In the second switching position of the control valve 70, the valve member 72 is arranged with its second sealing surface 88 at a distance from the second valve seat 87, so that the connection 62 is open to the pump working chamber 22.
  • the end region 75 of the valve member 72 in the valve pressure chamber 77 is preferably at least approximately pressure-balanced, so that the valve member 72 results in substantially no resultant pressure force in the direction of its longitudinal axis 73.
  • valve member 72 In the second switching position of the control valve 70, the valve member 72 is located with its sealing surface 81 on the valve seat 79, wherein the annular surface 84 is disposed at the distance A from the valve seat 79, so that between this and the valve seat 79 an annular gap-shaped flow area remains free.
  • the second sealing surface 88 of the valve member 72 is arranged in the second switching position at a distance from the second valve seat 87, so that in the valve pressure chamber 77 there is high pressure. From the valve pressure chamber 77 fuel can flow through the flow area and the openings 86 in the valve member 72 in the recess 82 and from this through the opening 78 and the connection 64 in the discharge chamber 24.
  • the control valve 70 thus has a defined leakage, wherein the leakage is kept low by appropriate selection of the number and the cross-sectional area of the apertures 86.
  • the flow of the fuel flowing out of the valve pressure chamber 77 through the flow area between the annular surface 84 and the valve seat 79 is carried out at a low flow rate, preferably forming a laminar flow.
  • the flow velocity at the openings 86 is also low, so that no erosion occurs on the valve member 72 or the valve seat.
  • FIG 4 a modified embodiment of the control valve 70 is shown, in which the annular surface 84 of the valve member 72 is not perpendicular to the longitudinal axis 73 of the valve member 72 but such that it, starting from its radially inner edge to its radially outer edge toward the valve seat 79th approaches and thus the distance A decreases.
  • the annular surface 84 may be formed at least approximately conical.
  • the annular surface 84 is conical in such a way that the flow area between the annular surface 84 and the valve seat 79 at with its sealing surface 81 on the valve seat 79th abutting valve member 72 is at least approximately constant over the radial course of the annular surface 84.
  • the flow area is formed by a cylindrical surface, which results as a product of the circumference, which is the product of twice the radius and n, and the distance A. This ensures that the flow rate of the fuel is at least approximately constant and no acceleration of the flow occurs.
  • the annular surface 84 may alternatively be curved.
  • the fuel injector During the suction stroke of the pump piston 18, this fuel is supplied from the fuel tank 24.
  • the fuel injection begins with a pilot injection, wherein the first control valve 68 is closed by the control device 67, so that the pump working chamber 22 is separated from the discharge chamber 24.
  • the control device 67 also the second control valve 70 is brought into its first switching position, so that the control pressure chamber 52 is connected to the discharge chamber 24 and separated from the pump working chamber 22. In this case, no high pressure can build up in the control pressure chamber 52.
  • the second control valve 70 is brought into its second switching position by the control device, so that the control pressure chamber 52 is separated from the discharge chamber 24 and connected to the pump working chamber 22.
  • the first control valve 68 remains in its closed position. High pressure builds up in the control pressure chamber 52 as in the pump working chamber 22, so that a large pressure force in the closing direction acts on the control piston 50 and the injection valve member 28 is moved into its closed position.
  • the second control valve 70 is brought by the control device 67 in its first switching position, so that the control pressure chamber 52 is connected to the discharge chamber 24 and separated from the pump working chamber 22.
  • the fuel injection valve 12 then opens due to the reduced pressure force on the control piston 50 and the injection valve member 28 moves to its open position.
  • the second control valve 70 is brought by the control device 67 in its second switching position, so that the control pressure chamber 52 is separated from the discharge chamber 24 and connected to the pump working chamber 22 and builds up in this high pressure and acting on the control piston 50 force the fuel injection valve 12 is closed.
  • a post-injection to which the second control valve 70 is brought into its first switching position.
  • the second control valve 70 is returned to its second switching position and / or the first control valve 68 is opened.
  • a control valve 70 configured as described above may also be used in other fuel injectors or high pressure fluid systems to control a connection.
  • the control valve 70 may also be designed as a 2/2-way valve, a 2/3-way valve or a 3/3-way valve.

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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)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (11)

  1. Soupape pour la commande d'une liaison dans un système de liquide à haute pression, en particulier dans un dispositif d'injection de carburant pour un moteur à combustion interne, comprenant un organe de soupape (72) guidé de façon mobile en translation selon la direction de son axe longitudinal (73), faisant saillie dans une chambre de pression de soupape (77) dans laquelle règne au moins temporairement une haute pression et présentant, dans la chambre de pression de soupape (77), au niveau d'un côté frontal s'étendant transversalement à son axe longitudinal (73), une surface d'étanchéité (81) par laquelle il coopère avec un siège de soupape (79) s'étendant transversalement à son axe longitudinal (73) pour isoler de la chambre de pression de soupape (77),au moins dans une large mesure, une ouverture (78) entourée par le siège de soupape (79),
    caractérisée en ce qu'
    au niveau de la surface frontale de l'organe de soupape (72), la surface d'étanchéité (81) est entourée d'une surface annulaire (84) disposée à petite distance (A) du siège de soupape (79) lorsque l'organe de soupape (72) est appuyé sur le siège de soupape (79) par sa surface d'étanchéité (81), et l'organe de soupape (72), en direction de son axe longitudinal (73), présente plusieurs passages (86) répartis sur sa périphérie, à travers lesquels l'ouverture (78) est reliée à la chambre de pression de soupape (77) lorsque l'organe de soupape (72) est appuyé sur le siège de soupape (79) par sa surface d'étanchéité (81).
  2. Soupape selon la revendication 1,
    caractérisée en ce que
    les passages (86) s'étendent au moins à peu près radialement à l'axe longitudinal (73) de l'organe de soupape (72):
  3. Soupape selon la revendication 1 ou 2,
    caractérisée en ce que
    les passages (86) sont formés par des rainures ménagées dans la surface d'étanchéité (81), qui s'ouvrent vers le siège de soupape (79).
  4. Soupape selon une des revendications 1 à 3.
    caractérisée en ce que
    dans son extension radiale, de la surface annulaire (84) se rapproche du siège de soupape (79) son bord radialement intérieur à son bord radialement extérieur.
  5. Soupape selon la revendication 4,
    caractérisée en ce que
    la surface annulaire (84) est au moins approximativement conique.
  6. Soupape selon la revendication 4 ou 5.
    caractérisée en ce que
    la surface annulaire (84) est conformée de manière que la dimension d'une section de passage libre existant entre cette surface et le siège de soupape (79) soit au moins approximativement constante sur l'extension radiale de la surface annulaire (84).
  7. Soupape selon une des revendications précédentes,
    caractérisée en ce qu'
    au niveau du côté frontal de l'organe de soupape (72) est disposée, entre la surface d'étanchéité (81) et la surface annulaire (84), une gorge annulaire (85) approfondie comparativement à la surface annulaire (84).
  8. Soupape selon une des revendications précédentes,
    caractérisée en ce que
    la surface d'étanchéité (81) est formée sur un bossage intérieur (80) au moins approximativement cylindrique de l'organe de soupape (72), et la surface annulaire (84) est formée sur un bossage extérieur (83), au moins approximativement cylindrique, de l'organe de soupape (72) avec un diamètre supérieur à celui du bossage intérieur (80).
  9. Soupape selon une des revendications précédentes,
    caractérisée en ce que
    l'organe de soupape (72) est au moins approximativement équilibré en pression dans la chambre de pression de soupape (77) de sorte qu'au moins approximativement aucune force de pression résultante n'agit sur cet organe en direction de son axe longitudinal (73).
  10. Soupape selon l'une des revendications précédentes;
    caractérisée en ce que,
    lorsque l'organe de soupape (72) est appuyé sur le siège de soupape (79) par sa surface d'étanchéité (81), il s'établit un écoulement au moins approximativement laminaire à faible vitesse d'écoulement entre la surface annulaire (84) et le siège de soupape (79).
  11. Dispositif d'injection de carburant pour un moteur à combustion interne, comprenant une pompe à carburant à haute pression (10) et un injecteur de carburant (12) relié à cette pompe pour chaque cylindre du moteur à combustion interne, la pompe à carburant à haute pression (10) présentant un piston de pompe (18) entraîné en un mouvement alternatif par le moteur à combustion interne et qui délimite une chambre de travail de pompe (22), reliée à une chambre de pression (40) de l'injecteur de carburant (12), lequel présente un organe de soupape (28) qui commande au moins une ouverture d'injection (32) et qui peut être déplacé dans une direction d'ouverture (29) par la pression régnant dans la chambre de pression (40) à l'encontre d'une force de fermeture (44), pour libérer l'au moins une ouverture d'injection (32), une première soupape de commande (68) commandée électriquement, qui commande au moins indirectement une liaison (66) entre la chambre de travail de pompe (22) et une chambre de décharge (24), et une deuxième soupape de commande actionnée électriquement (70) qui commande au moins une liaison (64) entre une chambre de pression de commande (52) et une chambre de décharge (24), l'organe de soupape d'injection (28) étant sollicité au moins indirectement dans une direction de fermeture par la pression régnant dans la chambre de pression de commande (52),
    caractérisé en ce que,
    comme première soupape de commande (68) et/ou comme deuxième soupape de commande (70), on utilise une soupape selon une des revendications précédentes.
EP03001990A 2002-02-08 2003-01-31 Soupape hydraulique à haute pression, notamment pour un dispositif d'injection de carburant d'un moteur Expired - Lifetime EP1335128B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10205218 2002-02-08
DE10205218A DE10205218A1 (de) 2002-02-08 2002-02-08 Ventil zur Steuerung einer Verbindung in einem Hochdruckflüssigkeitssystem, insbesondere einer Kraftstoffeinspitzeinrichtung für eine Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1335128A2 EP1335128A2 (fr) 2003-08-13
EP1335128A3 EP1335128A3 (fr) 2004-10-20
EP1335128B1 true EP1335128B1 (fr) 2006-01-04

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Application Number Title Priority Date Filing Date
EP03001990A Expired - Lifetime EP1335128B1 (fr) 2002-02-08 2003-01-31 Soupape hydraulique à haute pression, notamment pour un dispositif d'injection de carburant d'un moteur

Country Status (4)

Country Link
US (1) US6820594B2 (fr)
EP (1) EP1335128B1 (fr)
JP (1) JP4335544B2 (fr)
DE (2) DE10205218A1 (fr)

Cited By (1)

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US20040079335A1 (en) 2004-04-29
EP1335128A3 (fr) 2004-10-20
DE50302088D1 (de) 2006-03-30
US6820594B2 (en) 2004-11-23
JP2003239822A (ja) 2003-08-27
EP1335128A2 (fr) 2003-08-13
JP4335544B2 (ja) 2009-09-30
DE10205218A1 (de) 2003-10-30

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