EP1925812B1 - Soupape d'injection de carburant pour moteurs à combustion interne - Google Patents

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

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Publication number
EP1925812B1
EP1925812B1 EP07118225A EP07118225A EP1925812B1 EP 1925812 B1 EP1925812 B1 EP 1925812B1 EP 07118225 A EP07118225 A EP 07118225A EP 07118225 A EP07118225 A EP 07118225A EP 1925812 B1 EP1925812 B1 EP 1925812B1
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EP
European Patent Office
Prior art keywords
control
valve
pressure
chamber
control chamber
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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.)
Not-in-force
Application number
EP07118225A
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German (de)
English (en)
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EP1925812A1 (fr
Inventor
Jochen Mertens
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1925812A1 publication Critical patent/EP1925812A1/fr
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Publication of EP1925812B1 publication Critical patent/EP1925812B1/fr
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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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0047—Four-way valves or valves with more than four ways

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve according to the preamble of claim 1 is in DE 10 2005 060 655.5 proposed.
  • a second valve seat near guide bore is formed in the nozzle body for the valve needle, which forms a substantially hydraulically sealing guide for a second guide portion of the valve needle, the hydraulically sealing guides realized a hydraulic limitation of the valve needle pressure chamber on the valve seat side end face with open valve needle.
  • closing of the valve needle is characterized in that a closing space is provided in the rail or system pressure constantly acts in the closing direction on the valve needle, and that an acting on the valve needle control chamber is provided, which is controlled by a control valve and the Opening the valve needle connected to a low pressure / return system and is acted upon to close the valve needle with rail or system pressure.
  • a similar fuel injection valve, however, with a valve needle assembly with two valve pins is in DE 10 2005 060 656.3 proposed.
  • a similar fuel injector shows EP 1 589 217 A .
  • Object of the present invention is to provide a fuel injection valve in which there is a closing, resulting pressure force at unpressurized control chambers on the valve needle.
  • the object of the invention is achieved with the characterizing features of claim 1.
  • the opening forces are generated at the valve needle of the force acting in the opening direction of the valve needle pressure surface and the applied pressure in the second control chamber.
  • These pressure surfaces are the pressure surface facing the tip of the valve needle in the valve needle pressure chamber and the pressure shoulder on the valve needle pointing into the second control chamber.
  • the opening of the valve needle from the closed state is thereby realized only by pressurization of the second control chamber, wherein the second control chamber thereby forms an opening control chamber.
  • the valve needle is closed due to the closing pressure acting on the closing surface.
  • a trained at the top of the valve needle valve needle pressure chamber is realized by the valve seat near guide bore in the nozzle body forms a hydraulically tight guide for the second guide portion of the valve needle, so that the hydraulic tight guide forms a hydraulic boundary of the valve needle pressure chamber on the valve seat side end face with open valve needle.
  • valve needle In an opening-acting control of the valve needle without closing control of the valve needle is in accordance with FIG. 1 and 2 to close the valve needle, only the pressure in the second control chamber lowered again. Due to the pressure reduction in the second control chamber, the valve needle closes automatically.
  • the first control chamber and the second control chamber is permanently hydraulically connected to the low pressure / return system.
  • the second control chamber is connected via a control bore to the control valve, wherein the control bore by means of switching positions of the control valve with the system pressure or with the low-pressure / return system is hydraulically connected.
  • the second control chamber is permanently connected to the system pressure and connected via a control bore to the control valve, wherein the control bore by means of switching positions of the control valve with the low-pressure / return system is hydraulically connected.
  • FIG. 3 An opening-acting control and a closing acting control of the valve needle is provided with a third embodiment according to Fig. 3 achieved.
  • the first control chamber and the second control chamber is hydraulically permanently connected to the low pressure / return system
  • the first control chamber and the second control chamber are additionally connected by means of a respective control bore to the control valve, so that via the control valve of the first control chamber or the second control chamber alternately can be acted upon via one of the two control bores via a high-pressure connection to the system pressure. Due to the double connection by means of the two control bores and by the condition d3> d2, the second control chamber only needs to be subjected to system pressure for a short time to open the valve needle.
  • An opening-acting control with variable opening speed of the valve needle is provided with a fourth embodiment according to FIG. 4 achieved.
  • the first control room and the other control room is constantly hydraulically connected to the low pressure / return system.
  • the second control chamber is connected via a first and a second control bore to the control valve.
  • the second control chamber via the first control bore and, alternatively, also via the second control bore via a high-pressure connection to the system pressure. Due to the double connection by means of the two control bores, the opening speed of the valve needle can be made variable.
  • fuel injection valves have a housing with a nozzle body 2 and a throttle body 3 and a control valve 4. Both parts of the housing are held together hydraulically tight by a device, not shown.
  • a stepped bore 10 is formed, which forms with a top portion a first, valve seat remote guide bore 11 and a lower portion, a second valve seat near guide bore 12.
  • a longitudinally displaceably arranged valve needle 5 is guided, which has a first, valve seat remote guide portion 13 and a second, valve seat near guide portion 14.
  • the valve seat remote guide portion 13 is guided in the valve seat remote guide bore 11 and the valve seat near guide portion 14 in the valve seat near guide bore 12, wherein these holes each form a substantially hydraulically tight guide.
  • the valve seat near guide section 14 terminates at the tip of the valve needle 5 with a valve seat-side end face 8, which forms within the valve seat 18 acting in the opening direction of the valve needle 5 pressure surface 81.
  • the valve needle 5 is traversed over its entire length by a coaxial fuel channel 6, which opens at the valve seat side end face 8 in a valve needle pressure chamber 15.
  • the stepped bore 10 is delimited at one end of the nozzle body 2 by a nozzle body seat 16 formed on the nozzle body 2.
  • the nozzle body seat 16 cooperates with a valve seat 18 formed on the valve needle 5.
  • the nozzle body seat 16 injection openings 17 are connected downstream, which open into the mounting position of the fuel injection valve in a combustion chamber of an internal combustion engine.
  • the valve needle 5 is in the closed state with the valve seat 18 on the nozzle body seat 16.
  • the valve seat 18 has a diameter d4.
  • valve seat 18 When the valve seat 18 rests on the nozzle body seat 16, a sealing seat is formed, which separates the injection openings 17 from the valve needle pressure chamber 15, whereby the injection openings 17 are decoupled from the valve needle pressure chamber 15 acted upon by rail or system pressure. Lifting the valve needle 5 with the valve seat 18 from the nozzle body seat 16, the injection ports are released and fuel is with the in the Valve needle pressure chamber 15 prevailing pressure corresponding to the system pressure, for example, a common rail system of a diesel fuel injector, injected.
  • the fuel injection valves further have a sliding sleeve 20, which is guided axially displaceably in a guide bore 21 with a diameter d2.
  • the sliding sleeve 20 further has an annular surface 22 which presses against an end face 23 of the throttle body 2 and thereby forms a cooperating with the end face 23 sealing surface.
  • the guide bore 21 forms below the slide sleeve 20 a closing space 24 with a closing surface 25 acting in the closing direction of the valve needle 5.
  • a closing spring 29 is arranged, which presses the sliding sleeve 20 against the end face 23.
  • the closing spring 29 simultaneously acts as a closing spring on the valve needle 5, which supports the force acting on the valve needle 5 hydraulic closing force.
  • valve needle 5 ends with an annular surface 28 which is exposed to a first control chamber 30.
  • the first control chamber 30 is thereby hydraulically limited by said annular surface 28 of the valve needle 5, by the end face 23 of the throttle body 3 and by the sliding sleeve 20.
  • the valve needle 5 is at the valve seat remote guide portion 13 outside the valve seat remote guide bore 11 surrounded by an annular space 27 which forms a second control chamber 31.
  • annular space 27 and in the second control chamber 31 opens an inlet channel 271 and a drain channel 272.
  • the valve seat remote guide portion 13 with the diameter d1 tapers towards the valve seat near guide portion 14 out with a diameter d3, wherein between the diameters d1 and d3 at the Valve needle 5 forms a pressure shoulder 32 which is exposed to the second control chamber 31.
  • the operation of the second control chamber 31 will be explained later.
  • the fuel channel 6 of the valve needle 5 leading into the valve needle pressure chamber 15 communicates via the closing space 24, a central bore 26 in the valve sleeve 20 and via a central inlet bore 33 formed in the throttle body 3 to a high-pressure line 34 is connected, which in turn is connected to a high pressure source of a common rail system.
  • a first control concept I in which the injection process is initiated with an opening-acting control.
  • the condition for this control concept is that the following diameter ratios are present: d1>d2>d3> d4.
  • FIG. 1 is in addition to the inlet bore 33, a control bore 35 with a first throttle 36 and a drain hole 37 with a second throttle 38 is formed.
  • the inlet bore 35 is hydraulically connected to the inlet channel 271 and the drain hole 37 to the drain channel 272. From the drain hole 37, which is connected to the low pressure / return system, branches off a hydraulic connecting channel 39 which leads into the first control chamber 30.
  • the control bore 35 is connected to a control line 41 which is connected to the control valve 4.
  • the control valve 4 is according to the embodiment FIG. 1 a 3/2-way valve, which is connected to one connection to the control line 41 with the other connection to a low-pressure / return system and to the third connection via a further, optional throttle with the high-pressure line 34. With the control valve 4 while the control line 41 is connected to activate the valve needle 5 in the second switching position with the high pressure line 34.
  • the closing force acting on the closing surface 25 with the diameter d2 in the closing space 24 is greater than the opening force acting on the end face 8 with the diameter d3 in the valve needle pressure chamber 5 with the valve needle open. Therefore, the valve needle 5 closes automatically.
  • the first control chamber 30 is permanently connected to the low-pressure return system via a separate second drainage bore 311 with a further, optional drainage throttle 312.
  • the second control chamber 31 is permanently connected via a further inlet bore 371 with a further inlet throttle 381 with the system pressure.
  • a control valve 4 in this case a 2/2-way valve is used, which connects or disconnects the second control chamber 31 via the control bore 35 with the low-pressure / return system.
  • a pressure level in the second control chamber 31 is set, which is so low that it is not sufficient to open the valve needle 5 in the first switching position.
  • FIG. 2 is therefore of particular interest for cam-driven systems or non-constant pressure systems, such as the pump nozzle.
  • a second control concept II with an opening and closing control is off FIG. 3 out.
  • closed valve needle 5 acts here, as in the embodiment in FIG. 1
  • the resulting pressure force in the closing space 24 closing The opening movement takes place by pressurization of the second control chamber 31 according to the second switching position of the control valve 4.
  • a resulting pressure force exists, which only 5 opens in the open state of the valve needle. Therefore, after opening, the pressurization of the second control room 31 can be canceled. This is especially through FIG.
  • valve needle 5a according to the center position of the control valve 4 is provided.
  • the first control chamber 30 must be coupled according to the first switching position of the control valve 4 to the high-pressure line 34. If the valve needle 5 is placed in its valve seat 18 after the closing operation, then the opening acting pressure surface on the end face 8 reduces to the size of the pressure surface 81 within the diameter d4. After closing the valve needle 5 is thus again a closing acting resulting pressure force in the closing chamber 24.
  • control valve 4 operates as a 3/2-way valve.
  • the fuel injection valve according to FIG. 3 but also with other control valve variants according to Figure 5a and Figure 5b operate.
  • the control valve 4 according to FIG. 5a is a 3/3-way valve, which represents the described decoupling of the first control chamber 30 and the second control chamber 31 of the high pressure line 34 in the closed position of the valve needle 5 in the second switching position.
  • the control valve 4 according to FIG. 5b it is a 4/2-way valve.
  • the second control chamber 31 via the drain hole 37 is hydraulically permanently connected to the low pressure / return system.
  • the second control chamber 31 is connected via the first control bore 35 and the first control chamber 30 via a second control bore 321 with a further throttle 322 to the control valve 4. Furthermore, the first control chamber 30 via a further inlet bore 341 with a further inlet throttle 342 hydraulically permanently connected to the pressurized with system pressure high pressure line 34.
  • the second control chamber 31 In the illustrated first switching position of the control valve 4, the second control chamber 31 is separated from the system pressure and the first control chamber 30 from the low pressure / return system.
  • the second control chamber 31 is acted upon by the first control bore 35 with the system pressure and the first control chamber 30 connected to the low pressure / return system.
  • there are in the first switching position at FIG. 5b no system pressure leakage through the throttles and the valve needle 5 is kept closed.
  • valve needle 5 can each be opened and closed and essentially only leakage losses in the control phase during opening during the opening pulse or during closing during the Close pulse occurs.
  • the high pressure supply of the high-pressure pump for the common rail storage or other systems is therefore required only by the pilot leakage and the injection quantity.
  • the control is in accordance with FIG. 5a used.
  • a third taxation concept III is out FIG. 4 and 5c out.
  • a fuel injection with variable opening and / or closing speed of the valve needle 5 is possible.
  • the condition for this control concept is: d1>d2>d3> d4.
  • a closing pressure acting on resulting force is closed when the valve needle 5 is open and also when the pressure relief first and second control chambers 30, 31 are present.
  • the movement of the valve needle 5 can be chosen variable. This is done according to FIG. 4 a 3/3-way valve used as a control valve 4.
  • a second control line 412 is present, which leads to a second control bore 331 with a second control throttle 332.
  • the connecting channel 39 to the first control chamber 30 is optionally provided with a further outlet throttle 391.
  • switching position of the control valve 4 are all inlet holes separated from the high pressure line 34. In the second switching position (middle position), only the first control bore 35 is connected via the control line 41 and the first throttle 36 to the high-pressure line 34.
  • the pressure in the second control chamber 31 slowly builds up and the valve needle 5 opens correspondingly slowly according to the mass flow rates.
  • the optional throttle 391 also influences the opening speed.
  • a targeted pilot injection with less fuel is possible.
  • the third switching position is additionally the second control bore 331 coupled to the second control throttle 332 via the second control line 412 to the high-pressure line 34.
  • the pressure build-up in the second control chamber 31 is correspondingly larger, so that the opening movement of the valve needle 5 is also faster. But it is also conceivable to go directly to the third switching position, so as to obtain the shortest opening time of the valve needle 5.
  • the stroke of the valve needle 5 is set to "fast", so that a correspondingly larger amount of fuel can be injected.
  • FIG. 5c out A further embodiment for controlling the fuel injection valve in FIG. 4 comes from FIG. 5c out.
  • the control valve 4 is here a 4/3-way valve.
  • the first control chamber 30 is permanently connected via the drain hole 39 with a drain throttle 391 to the low pressure / return system.
  • the further control bore 331 is placed on the one port of the control valve 4, which is the low-pressure / return system can be activated.
  • the control bore 35 for the second control chamber 31 is placed on the further connection of the control valve 4, which is the high-pressure line 34 can be connected. In the first switching position of the control valve 4, the control bore 35 without pressure connection and the further control bore 331 with return connection, whereby the valve needle 5 closes.
  • the control bore 35 with pressure connection and the further control bore 331 is blocked, ie, without connection neither to return nor to system pressure.
  • About the throttle ratio of the restrictors 36 and 332 results in a moderate pressure level or a slow opening of the valve needle 5.
  • the control bores 35 and 332 with pressure connection so that a higher pressure level in the second control chamber 31 leads to a fast opening.

Claims (13)

  1. Soupape d'injection de carburant pour moteurs à combustion interne, comprenant un corps de buse (12), dans lequel une aiguille de soupape (5) commandée par une soupape de commande (4) est guidée de manière déplaçable axialement avec une première portion de guidage (13) dans un alésage de guidage (11) éloigné du siège de soupape et avec une deuxième portion de guidage (14) dans un alésage de guidage (12) proche du siège de soupape, un canal de carburant (6) réalisé à l'intérieur de l'aiguille de soupape (5), par le biais duquel canal de carburant (6) du carburant est acheminé à un espace de pression de l'aiguille de soupape (15), l'aiguille de soupape (5) étant associée à cet espace de pression d'aiguille de soupape (15) par une face frontale (8) du côté du siège de soupape, qui forme une face de pression (81) agissant dans la direction de l'ouverture de l'aiguille de soupape (5), au moins une face de fermeture (25) agissant dans la direction de la fermeture de l'aiguille de soupape (5), qui est exposée à un espace de fermeture (24), et qui est soumise à la pression du système, un premier espace de commande (30), auquel l'aiguille de soupape (5) est exposée par une surface de commande (28) agissant dans la direction de fermeture, et un deuxième espace de commande (31) auquel l'aiguille de soupape (5) est exposée au moyen d'un épaulement de pression (32) agissant dans la direction de l'ouverture, au moins un siège de soupape (16) étant réalisé sur la face frontale (8), du côté du siège de soupape, de l'aiguille de soupape (5), lequel sépare l'espace de pression d'aiguille de soupape (15) d'au moins une ouverture d'injection (17), caractérisée en ce que les faces de pression agissant dans la direction de l'ouverture de l'aiguille de soupape (5) sont formées par la face de pression (81) réalisée sur la face frontale (8) et par l'épaulement de pression (32) tourné vers le deuxième espace de commande (31), et en ce que pour l'ouverture de l'aiguille de soupape (5), la pression dans le deuxième espace de commande (31) peut être commandée au moyen de la soupape de commande (4).
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce qu'une face de commande (28) exposée au premier espace de commande (30) présente un diamètre extérieur d1, la face de fermeture (25) exposée à l'espace de fermeture (24) présente un diamètre d2 et la portion de guidage (14) de l'aiguille de soupape (5) proche du siège de soupape, avec laquelle l'aiguille de soupape (5) est guidée de manière hydrauliquement hermétique dans l'alésage de guidage (12) proche du siège de soupape, présente un diamètre d3, et en ce que le siège de soupape (16) limite l'espace de pression d'aiguille de soupape (15) dans l'état fermé de l'aiguille de soupape (5) avec un diamètre d4, de sorte que la face de pression (81) présente dans cet état le même diamètre d4.
  3. Soupape d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que le deuxième espace de commande (31) est raccordé par le biais d'un alésage de commande (35) à la soupape de commande (4) et en ce que l'alésage de commande (35) peut être sollicité au moyen de positions de commutation de la soupape de commande (4) par la pression du système, ou peut être connecté hydrauliquement au système basse pression / de retour.
  4. Soupape d'injection de carburant selon la revendication 2, caractérisée en ce que le premier espace de commande (30) et le deuxième espace de commande (31) sont connectés hydrauliquement de manière permanente au système basse pression / de retour.
  5. Soupape d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que le premier espace de commande (30) est connecté hydrauliquement de manière permanente au système basse pression / de retour, en ce que le deuxième espace de commande (31) est raccordé par le biais d'un premier alésage de commande (35) à la soupape de commande (4) et est connecté par le biais d'un alésage d'afflux (371) de manière permanente à la pression du système, et en ce que la conduite de commande (35) peut être connectée hydrauliquement au moyen de positions de commutation de la soupape de commande (4) au système basse pression / de retour, ou peut être séparée hydrauliquement du système basse pression / de retour.
  6. Soupape d'injection de carburant selon l'une quelconque des revendications 1 à 5, caractérisée en ce que lesdits diamètres sont dimensionnés de telle sorte que d1 > d2 > d3 > d4.
  7. Soupape d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que l'on prévoit au moins deux alésages de commande (35, 321, 331) qui conduisent dans un espace de commande respectif (30, 31) ou ensemble dans l'un des deux espaces de commande (30, 31), et en ce que les au moins deux alésages de commande (35, 321, 331) sont connectés à la soupape de commande (4).
  8. Soupape d'injection de carburant selon la revendication 7, caractérisée en ce que le premier espace de commande (30) et le deuxième espace de commande (31) sont connectés hydrauliquement de manière permanente au système basse pression / de retour, en ce que le deuxième espace de commande (31) est raccordé par le biais du premier alésage de commande (35), et le premier espace de commande (30) est raccordé par le biais du deuxième alésage de commande (321), à la soupape de commande (4), et en ce que le premier espace de commande (30) ou le deuxième espace de commande (31), en alternance ou au choix, peut être sollicité par le biais de l'un des deux alésages de commande (35, 321) au moyen de la soupape de commande (4) par la pression du système.
  9. Soupape d'injection de carburant selon la revendication 7, caractérisée en ce que le deuxième espace de commande (31) est connecté hydrauliquement de manière permanente au système basse pression / de retour, en ce que le deuxième espace de commande (31) est raccordé par le biais du premier alésage de commande (35) et le premier espace de commande (30) est raccordé par le biais du deuxième alésage de commande (321) à la soupape de commande (4), et en ce que le premier espace de commande (30) est raccordé par le biais d'un autre alésage d'afflux (341) hydrauliquement de manière permanente à une conduite haute pression (34) sollicitée par la pression du système, en ce que dans une deuxième position de commutation de la soupape de commande (4), le deuxième espace de pression (31) est connecté par le biais du premier alésage de commande (35) à la pression du système et le premier espace de commande (30) est connecté par le biais du deuxième alésage de commande (321) au système basse pression / de retour, et en ce que dans une première position de commutation de la soupape de commande (4), le deuxième espace de commande (31) est séparé de la pression du système et le premier espace de commande (30) est séparé du système basse pression / de retour.
  10. Soupape d'injection de carburant selon la revendication 1, 2, 7, 8 ou 9, caractérisée en ce que lesdits diamètres sont dimensionnés de telle sorte que d1 > d2 > d3 > d4.
  11. Soupape d'injection de carburant selon la revendication 7, caractérisée en ce que le premier espace de commande (30) et le deuxième espace de commande (31) sont connectés hydrauliquement de manière permanente au système basse pression / de retour, et en ce que le deuxième espace de commande (31) peut être sollicité par le biais du premier alésage de commande (35) ou par le biais des deux alésages de commande (35, 321) au moyen de la soupape de commande (4) par la pression du système.
  12. Soupape d'injection de carburant selon la revendication 7, caractérisée en ce que le premier espace de commande (30) est connecté hydrauliquement de manière permanente au système basse pression / de retour, en ce que le deuxième espace de commande (31) est connecté par le biais d'un premier alésage de commande (35) et d'un deuxième alésage de commande (331) à la soupape de commande (4), en ce que le deuxième espace de commande (31) peut être sollicité par le biais du premier alésage de commande (35) ou par le biais des deux alésages de commande (35, 331) au moyen de la soupape de commande (4) par la pression du système, et en ce que la soupape de commande (4) présente une autre position de commutation, dans laquelle le deuxième espace de commande (31) dans l'état désaccouplé de la pression du système, peut être connecté par le biais de l'un des deux alésages de commande (35, 331) au moyen de la soupape de commande (4) au système basse pression / de retour.
  13. Soupape d'injection de carburant selon la revendication 1, 2, 7 ou 12, caractérisée en ce que lesdits diamètres sont dimensionnés de telle sorte que d1 > d2 > d3 > d4.
EP07118225A 2006-11-27 2007-10-10 Soupape d'injection de carburant pour moteurs à combustion interne Not-in-force EP1925812B1 (fr)

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DE102006055792A DE102006055792A1 (de) 2006-11-27 2006-11-27 Kraftstoffeinspritzventil für Brennkraftmaschinen

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DE102008000702A1 (de) * 2008-03-17 2009-09-24 Robert Bosch Gmbh Injektor
DE102010002205A1 (de) * 2009-03-25 2010-09-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE102013009378A1 (de) 2013-05-28 2014-12-04 Jochen Mertens Vorrichtung zur Einspritzung eines Kraftstoffs und zur optionalen Nutzung innerhalb der Vorrichtung zur Speicherung und Verwendung von Bremsenergie
KR101638815B1 (ko) * 2016-01-07 2016-07-25 한빛정공(주) 4 행정용 인젝션 밸브
CN105756830B (zh) * 2016-04-21 2018-04-24 哈尔滨工程大学 组合式机械喷油-增压电磁喷气混合燃料喷射装置

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DE10160490B4 (de) * 2001-12-08 2005-10-06 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, Kraftstoffsystem sowie Brennkraftmaschine
DE102004019836A1 (de) * 2004-04-23 2005-11-17 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

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DE102006055792A1 (de) 2008-05-29
ATE466186T1 (de) 2010-05-15
EP1925812A1 (fr) 2008-05-28

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