EP2207955B1 - Soupape de décharge de carburant pour dispositif d'injection de carburant, et dispositif d'injection de carburant présentant une soupape de décharge de carburant - Google Patents

Soupape de décharge de carburant pour dispositif d'injection de carburant, et dispositif d'injection de carburant présentant une soupape de décharge de carburant Download PDF

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Publication number
EP2207955B1
EP2207955B1 EP20080848181 EP08848181A EP2207955B1 EP 2207955 B1 EP2207955 B1 EP 2207955B1 EP 20080848181 EP20080848181 EP 20080848181 EP 08848181 A EP08848181 A EP 08848181A EP 2207955 B1 EP2207955 B1 EP 2207955B1
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EP
European Patent Office
Prior art keywords
valve
fuel
pressure
region
valve element
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.)
Not-in-force
Application number
EP20080848181
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German (de)
English (en)
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EP2207955A1 (fr
Inventor
Volkhard Ammon
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2207955A1 publication Critical patent/EP2207955A1/fr
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Publication of EP2207955B1 publication Critical patent/EP2207955B1/fr
Not-in-force 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F02M37/0029—Pressure regulator in the low pressure fuel system
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7847—With leak passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/785—With retarder or dashpot

Definitions

  • the invention is based on a fuel spill valve for a fuel injector and a fuel injector with fuel spill valve according to the preamble of claim 1 and of claim 9.
  • Such a fuel spill valve and such a fuel injector is characterized by the DE 100 57 244 A1 known.
  • This fuel spill valve serves to limit the pressure in a low-pressure region of the fuel injection device.
  • the fuel overflow valve has a valve housing in which a valve member is arranged to be liftable.
  • the valve member is controlled in its stroke movement, the connection of an inlet from the low pressure area with a drain to a discharge area
  • the valve member is acted upon by a valve spring in the direction of a closed position in which the connection of the inlet is interrupted with the flow, and by the in the inlet prevailing pressure in the opening direction acted upon.
  • the connection of the inlet opens on the jacket of the valve member into the valve housing and the valve member forms with the connection of the inlet a slide valve.
  • the fuel injection device has a high-pressure pump through which fuel is conveyed under high pressure at least indirectly, for example via a reservoir, to at least one injector.
  • a feed pump delivers fuel to the high-pressure pump.
  • the high pressure pump has at least one in a drive region arranged drive in a lifting movement driven pump piston.
  • the low-pressure region of the fuel injection device extends between the feed pump and the high-pressure pump and in this there is a low pressure generated by the feed pump.
  • the low-pressure region is connected to the drive region of the high-pressure pump.
  • the volume of the drive range changes, since the outward stroke of the pump piston increases the volume of the drive portion and the inward stroke of the pump piston decreases the volume of the drive portion.
  • pressure fluctuations throughout the low pressure range are generated, which may affect the function of the fuel injection device.
  • the valve member of the fuel spill valve must be able to perform a large stroke, which also requires a large stroke of the valve spring. This in turn means that a large installation space for the valve spring is required and this is heavily loaded and therefore can break.
  • a valve which can be flowed through in two directions and in which there is no closed position.
  • a cylindrical part is provided which is slidably disposed in a first chamber and having a through opening.
  • a valve member is also provided, which is arranged in a second chamber and having a through opening.
  • the valve member is acted upon by a valve spring to a stop at the junction of the two chambers out.
  • the cylindrical part can come to rest on the valve member and cylindrical member and valve member are movable together against the valve spring.
  • the valve spring performs the same stroke as the valve member. Even if the cylindrical part bears against the valve member, the valve flows through the openings, so that this is not a closed position of the cylindrical part or of the valve member. This valve is thus not suitable as an overflow valve, since this has no closed position.
  • a feed pump which comprises a spring-loaded suction valve and a spring-loaded pressure valve.
  • valve springs By valve springs, the respective valve member of the suction valve or the pressure valve is acted upon in a closing direction to a valve seat.
  • the valve seats are each formed in a valve seat carrier. A movement of the valve member beyond its closed position determined by the system at the valve seat in the closing direction is not possible.
  • the conveying direction can be reversed by the normally acting as a suction valve acts as a pressure valve and the normally acting as a pressure valve valve acts as a suction valve.
  • valve springs are rendered ineffective by a displacement of the valve seat carrier and instead other valve springs are brought into abutment against the valve members.
  • the respective valve member of the suction valve and the pressure valve is acted upon in a closing direction to another valve seat.
  • the valve springs always execute the same stroke as the valve members.
  • An overflow valve is also known, which is designed as a seat valve, in which the valve member in its closed position acted upon by the valve spring comes into contact with a valve seat and can not move further in the closing direction beyond the valve seat.
  • the valve spring performs the same stroke as the valve member.
  • the fuel spill valve according to the invention with the features according to claim 1 has the advantage that the valve member can perform a larger stroke independently of the valve spring, whereby a better balance of the pressure fluctuations is possible.
  • the valve spring needs to perform only a limited stroke to move the valve member in its closed position, whereby the space of the Kraftstoffüberströmventils and the load of the valve spring can be kept low.
  • Corresponding advantages arise for the fuel injection device according to claim 9 whose function is improved by the reduced pressure fluctuations in the low-pressure region.
  • the embodiment according to claim 2 allows in a simple manner compared to the valve spring stroke enlarged stroke of the valve member. Due to the construction according to claim 3 damping of the lifting movement of the support member and thus the valve member and the valve spring is achieved, whereby the load on the valve spring is reduced.
  • the embodiment of claim 5 also allows damping of the lifting movement of the support member and thus the valve member and the valve spring.
  • the embodiment of claim 7 or 8 allows without changes to the valve housing a two-stage design of the fuel spill valve.
  • FIG. 1 a fuel injection device in a simplified schematic representation
  • FIG. 2 a fuel overflow valve of the fuel injection device according to a first embodiment in the closed state in a longitudinal section with a valve member in a first position
  • FIG. 3 the fuel spill valve in the closed state with the valve member in a second position
  • FIG. 4 the fuel spill valve in the open state
  • FIG. 5 the fuel spill valve according to a second embodiment in the closed state.
  • FIG. 1 a fuel injection device for an internal combustion engine is shown.
  • the fuel injection device has a feed pump 10, which draws fuel from a fuel reservoir 12 and conveys it to the suction side of a high-pressure pump 14. From the feed pump 10, the fuel is compressed to a delivery pressure of, for example, about 4 to 6 bar.
  • the feed pump 10 may be driven electrically or mechanically.
  • a fuel metering device 16 may be arranged, through which the of the High pressure pump 14 sucked and funded under high pressure fuel quantity can be variably adjusted.
  • the fuel metering device 16 may be a proportional valve that can set different flow cross sections, or a clocked valve and is controlled mechanically or electrically by an electronic control device 17.
  • the high-pressure pump 14 has a housing 18 in which a rotationally driven drive shaft 20 is arranged in an interior 19.
  • the interior 19 of the housing 18 with the drive shaft 20 forms a drive region of the high pressure pump 14.
  • the drive shaft 20 has at least one cam 22 or eccentric, wherein the cam 22 may be formed as a multiple cam.
  • the high-pressure pump has at least one or more pump elements 24, each having a pump piston 26, which is indirectly driven by the cam 22 of the drive shaft 20 in a lifting movement in at least approximately radial direction to the axis of rotation of the drive shaft 20.
  • the pump piston 26 is tightly guided in a cylinder bore 28 and bounded with its side facing away from the drive shaft 20 a pump working space 30.
  • the pump working chamber 30 has via an opening into the pump working chamber 30 inlet valve 32 a connection with the fuel inlet from the feed pump 10 ago.
  • the pump working chamber 30 also has, via an outlet valve 34 opening out of the pump working chamber 30, a connection to an outlet, which is connected, for example, to a high-pressure accumulator 110.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • the high-pressure accumulator 110 can also be dispensed with, with the high-pressure pump 14 then being connected to the injectors 120 via hydraulic lines.
  • the pump piston 26 moves into the interior 19 and sucks in fuel from the feed pump 10 via the open inlet valve 32 forth in the pump work chamber 30 at.
  • the pump piston 26 moves out of the interior 19 and delivers fuel under high pressure from the pump working chamber 30 via the open outlet valve 34 into the high-pressure accumulator 110 or to the injectors 120.
  • the region between the feed pump 10 and the fuel metering device 16 forms a low-pressure region in which the pressure generated by the feed pump 10 prevails.
  • a fuel overflow valve 36 is provided, by which the pressure in the low-pressure region is limited.
  • the fuel spill valve 36 opens when the pressure in the low pressure region exceeds its opening pressure and via the open Kraftstoffüberströmventil 36 funded by the feed pump 10, but not sucked by the high pressure pump 14 fuel quantity is diverted into a discharge area, which is for example a return 11 to the fuel tank 12.
  • the fuel spill valve 36 includes a tubular valve housing 38 that includes a smaller diameter tubular portion 39 and a larger diameter tubular portion 40.
  • a piston-shaped valve member 42 is slidably guided in a longitudinal bore 41.
  • In section 39 of the valve housing 38 at least one opening 43 is provided, which connects the longitudinal bore 41 with the outer jacket of the portion 39.
  • the opening 43 is preferably formed as a bore, wherein, for example, two diametrically opposite holes 43 are provided. Via the openings 43, the longitudinal bore 41 with a discharge area, for example, a return to the fuel tank 12 connectable.
  • the pressure prevailing in the low-pressure region acts via its open end also in the longitudinal bore 41 of the valve housing 38 and thus on the end face of the valve member 42.
  • the open end of the longitudinal bore 41 thus forms an inlet from the low-pressure region into the fuel spill valve 36.
  • the valve member 42 the openings Covered 43, so the inlet, so the low pressure area is separated from the discharge area and when the valve member 42, the openings 43 at least partially releases, so is the inlet, so the low pressure area, with connected to the discharge area.
  • the valve member 42 thus forms with the openings 43 a slide valve.
  • a filter screen 44 can be arranged on the valve housing 38, by which it is prevented that dirt particles can enter the longitudinal bore 41 from the low-pressure region.
  • the filter screen 44 may be fixed by means of an annular fastening element 45 on the valve housing 38, wherein the fastening element may be connected, for example by a flange with the valve housing 38.
  • a valve spring 48 is arranged, which acts via a support member 50 on the valve member 42.
  • the support member 50 is cup-shaped, with its bottom 52 facing the valve member 42 and the open side facing away from the valve member 42.
  • the support member 50 is slidably guided in the longitudinal bore 46 and projects into this from the open side thereof designed as a helical compression spring valve spring 48, which rests against the bottom 52.
  • the valve member 42 remote from the end of the longitudinal bore 46 of the valve housing 38 is closed by means of an insert member 54, which also serves as a support for the valve spring 48.
  • the insert member 54 may be like the support member 50 cup-shaped, with its open end facing the valve member 42 and the valve spring 48 protrudes into the insert member 54 and is supported on the bottom thereof.
  • the insert 54 is fixed in the longitudinal bore 46, for example, pressed into this.
  • the support member 50 and / or the insert 54 may be formed as a sheet metal part.
  • the support member 50 is not connected to the valve member 42 but comes only by the action of the valve spring 48 on the valve member 42 with its bottom 52 to the plant.
  • the support element 50 can perform a maximum stroke towards the valve member 42 which is limited by abutment of the support element 50 at an annular shoulder 56 formed at the transition from the longitudinal bore 46 to the smaller longitudinal bore 41.
  • In the bottom 52 of the support element 50 there is at least one opening 58 available with large cross section.
  • the Longitudinal bore 46 can be connected via at least one opening 62 opening onto the outer jacket of section 40 of valve housing 38 to a relief region, which can be, for example, a return to fuel tank 12.
  • a relief region which can be, for example, a return to fuel tank 12.
  • the support member 50 When the support member 50 is in abutment with the annular shoulder 56, it does not cover the opening 62, so that the longitudinal bore 46 is connected to the relief region.
  • the support member 50 moves from its abutment against the annular shoulder 56 into the longitudinal bore 46, it progressively covers the opening 62 and thus reduces the cross-section and possibly completely closed so that the longitudinal bore 46 only has a small throttling action Flow cross-section is connected to the discharge area or is separated from this.
  • the fuel spill valve 36 with the valve housing 38, the valve member 42, the valve spring 48, the support member 50 and the insert member 54 and the filter screen 44 forms a preassembled module which is inserted into a receiving housing 70.
  • the receiving housing 70 may be a separate housing or a part of the housing 18 of the high-pressure pump 14.
  • the function of the fuel overflow valve 36 will be explained in more detail below.
  • the length of the valve member 42 and the position of the annular shoulder 56 in the valve housing 38 to limit the stroke of the support member 50 are coordinated so that the valve member 42 at the voltage applied to the annular shoulder 56 support member 50, the openings 43 just covers and thus the connection of the low pressure area separates the discharge area.
  • the valve member 42 in FIG. 2 shown. Starting from this position, the valve member 42 can move even further towards the open end of the longitudinal bore 41, wherein the valve member 42 is no longer in contact with the support member 50 and the valve spring 48 thus no longer acts on the valve member 42.
  • valve member 42 is thus free to move in the longitudinal bore 41 according to the difference of acting on one end face pressure in the low pressure region and acting on the other end face pressure in the cylinder bore 46.
  • valve spring 48 By the valve spring 48, the valve member 42 can be moved to its closed position and Independently of the valve spring 48, the valve member 42 beyond its closed position still another run further stroke, which may be limited, for example by the filter screen 44 or the fastener 45, to prevent the valve member 42 moves out of the longitudinal bore 41 out. In this end position, the valve member 42 is in FIG. 3 shown.
  • the low-pressure region is separated from the relief region.
  • the valve member 42 is displaced against the force of the valve spring 48 in the longitudinal bore 41 so that the openings 43 are opened by the valve member 42 and the low-pressure region is connected to the relief region, so that from the low pressure area fuel can flow into the discharge area. In this open position, the valve member 42 is in FIG. 4 shown.
  • valve member 42 can nevertheless carry out a further stroke towards the open end of the longitudinal bore 41 and thus at least partially compensate for pressure and volume fluctuations in the low-pressure region.
  • the stroke that the support element 50 and the valve spring 48 perform is smaller than the possible stroke of the valve member 42. This leads to lower loads on the valve spring 48, which can be dimensioned correspondingly weaker.
  • the maximum stroke of the support member 50 and the valve member 42 and thus the maximum travel of the valve spring 48 is limited by the fact that the support member 50 comes to rest on the insert 54.
  • the valve spring 48 is preferably not yet compressed to block.
  • the at least one opening 58 in the bottom 52 of the support member 50 it is ensured that the valve member 42 can be easily detached from the support member 50 and again come to rest on this.
  • the at least one opening 60 in the support member 50 a pressure equalization between the two sides of the support member 50 is ensured so that it is in the fuel-filled Can move longitudinal bore 46.
  • a damping of the ⁇ réelleshubiolo the valve member 42 and the support member 50 is also achieved, whereby the load on the valve spring 48 is reduced, since the opening stroke is damped by the building up in the longitudinal bore 46 fuel pressure.
  • the fuel spill valve 36 is shown according to a second embodiment in which it opens in two stages and controls two connections of the low-pressure area.
  • the valve housing 38, the support member 50, the valve spring 48, the insert member 54 and the filter screen 44 and its fastening element 45 are formed identically as in the first embodiment.
  • the valve member 142 is deviating from the first embodiment, but the outer dimensions of the valve member 142, ie diameter and length, are identical to the first embodiment.
  • the valve member 142 is hollow and has a blind bore 176 extending from its end facing away from the valve spring 48, wherein the bottom 178 of the valve member 142 coming to rest on the support element 50 is designed to be closed.
  • At least one opening 180 for example in the form of a bore, through which the blind bore 176 is connected to the outer jacket of the valve member 142.
  • the opening 180 is preferably designed as a throttle bore with a defined cross-section.
  • the interior of the blind bore 176 is constantly acted upon by the pressure prevailing in the low-pressure region.
  • the valve member 142 effected by the valve spring 48 When the valve member 142 effected by the valve spring 48 is in its closed position, so are the openings 43 covered by this and the mouth of the opening 180 is located within the longitudinal bore 41 and is covered by this The low-pressure region is thus separated from the discharge areas. If the pressure in the low-pressure region is sufficient to move the valve member 142 against the force of the valve spring 48, the opening 180 initially emerges from the longitudinal bore 41 with a slight opening stroke of the valve member 142, so that the low-pressure region via the blind bore 176, the opening 180 and the at least one opening 60 in the support member 50 is connected to the opening 62 and can flow through this opening 62 fuel from the low pressure region.
  • the openings 43 are further covered by this small opening stroke of the valve member 142 through this and remain closed, so that no fuel can flow out of the low pressure region via the openings 43.
  • the openings 43 are released by this, so that fuel can flow from the low-pressure region via the openings 43 in the return line 11.
  • a use of the two-stage embodiment of the Kraftstoffüberströmventils 36 is advantageous in a fuel injection device in which only a portion of the funded by the feed pump 10 amount of fuel is supplied to the interior 19 of the high-pressure pump 14 for the lubrication and cooling of the drive. If the pressure prevailing in the low-pressure region is insufficient to open the fuel spill valve 36, the entire amount of fuel delivered by the feed pump 10 is supplied via the fuel metering device 16 to the high-pressure pump 14 for delivery.
  • the fuel overflow valve 36 opens in the first stage and that over the opening of the first stage from the blind bore 176, the opening 180, the at least one opening 60 in the support element 50 and the opening 62 outflowing fuel quantity is according to FIG. 1 fed via a line 13 to the interior 19.
  • the second stage opens at the fuel overflow valve 36, in that the valve member 142 releases the openings 43 and fuel can flow out of the low-pressure region via the return 11 into the fuel tank 12.

Claims (10)

  1. Soupape de décharge de carburant pour un dispositif d'injection de carburant, en particulier pour la limitation de pression dans une zone basse pression du dispositif d'injection de carburant, comprenant un boîtier de soupape (38), comprenant un organe de soupape (42 ; 142) disposé de manière à pouvoir effectuer un mouvement de va-et-vient dans le boîtier de soupape (38), au moyen duquel organe de soupape, grâce à son mouvement de va-et-vient, une connexion (43) d'une entrée dans le boîtier de soupape (38) à une zone de décharge est commandée, l'organe de soupape (42 ; 142) étant sollicité, par un ressort de soupape (48), en direction d'une position de fermeture dans laquelle la connexion (43) de l'entrée à la zone de décharge est interrompue, et l'organe de soupape (42 ; 142) étant sollicité dans la direction d'ouverture par la pression régnant dans l'entrée, la connexion (43) de l'entrée à la zone de décharge dans le boîtier de soupape (38) débouchant au niveau de l'organe de soupape (42 ; 142), l'organe de soupape (42 ; 142) formant, avec la connexion (43) de l'entrée à la zone de décharge, une soupape à tiroir, caractérisée en ce que l'organe de soupape (42 ; 142) peut effectuer, dans la direction de fermeture, une course supplémentaire au-delà de sa position de fermeture dans le boîtier de soupape (38), lors de laquelle course le ressort de soupape (48) n'agit pas sur l'organe de soupape (42 ; 142).
  2. Soupape de décharge de carburant selon la revendication 1, caractérisée en ce que le ressort de soupape (48) agit, par le biais d'un élément d'appui (50), sur l'organe de soupape (42 ; 142), lequel élément d'appui n'est pas connecté à l'organe de soupape (42 ; 142), et en ce que l'élément d'appui (50) vient s'appliquer contre une butée (56) dans le boîtier de soupape (38) dans la direction de fermeture dans la zone de la position de fermeture de l'organe de soupape (42 ; 142).
  3. Soupape de décharge de carburant selon la revendication 2, caractérisée en ce que l'élément d'appui (50) est guidé de manière coulissante dans le boîtier de soupape (38) et délimite dans le boîtier de soupape (38) un espace (46) dans lequel est disposé le ressort de soupape (48), en ce que cet espace (46) présente une connexion (62) à une zone de décharge, et en ce que cette connexion (62) est commandée au moyen de l'élément d'appui (50) indépendamment de sa course.
  4. Soupape de décharge de carburant selon la revendication 3, caractérisée en ce que la connexion (62) de l'espace (46) à la zone de décharge est ouverte lorsque l'élément d'appui (50) s'applique contre la butée (56) et est fermée par l'élément d'appui (50) lors du déplacement de l'élément d'appui (50) en direction de la position d'ouverture de l'organe de soupape (42 ; 142).
  5. Soupape de décharge de carburant selon l'une quelconque des revendications 2 à 4, caractérisée en ce que l'élément d'appui (50) est réalisé en forme de pot, en ce que le ressort de soupape (48) pénètre dans l'élément d'appui (50) et s'applique contre son fond (52), et en ce que l'élément d'appui (50) vient s'appliquer, par son fond (52), contre l'organe de soupape (42 ; 142).
  6. Soupape de décharge de carburant selon la revendication 5, caractérisée en ce que l'élément d'appui (50) présente, dans une zone de son fond (52) dans laquelle celui-ci vient s'appliquer contre l'organe de soupape (42 ; 142), au moins une première ouverture (58) de grande section transversale et présente, dans une zone de son fond (52) à l'extérieur de l'appui contre l'organe de soupape (42 ; 142), au moins une deuxième ouverture (60) de petite section transversale.
  7. Soupape de décharge de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une connexion étranglée (180) de l'entrée à une sortie (62) est en outre commandée par l'organe de soupape (142), et lors de la course de l'organe de soupape (142) dans la direction d'ouverture, au moyen de cet organe de soupape, la connexion étranglée (180) de l'entrée à la sortie (62) étant tout d'abord ouverte lors d'une petite course d'ouverture et la connexion (43) de l'entrée à la zone de décharge étant ouverte lors d'une course d'ouverture plus grande.
  8. Soupape de décharge de carburant selon la revendication 7, caractérisée en ce que l'organe de soupape (142) est réalisé en forme de piston, est guidé de manière étanche dans un alésage longitudinal (41) du boîtier de soupape (38) et comprend un alésage borgne (176) ouvert en direction de son extrémité opposée au ressort de soupape (48), lequel alésage borgne est connecté en permanence à l'entrée, en ce que la connexion (43) à la zone de décharge part de l'alésage borgne (41) au niveau de l'enveloppe de l'organe de soupape (142) et cette connexion (43) est commandée par l'extrémité frontale ouverte de l'organe de soupape (142), en ce que la connexion étranglée comporte au moins une ouverture (180) partant de l'alésage borgne (176) à proximité du fond (178) fermé de l'organe de soupape (142) tourné vers le ressort de soupape (48) et débouchant au niveau de l'enveloppe de l'organe de soupape (142), au moyen du recouvrement de laquelle ouverture par l'alésage longitudinal (41) la connexion à la sortie (62) est commandée.
  9. Dispositif d'injection de carburant pour un moteur à combustion interne comprenant une pompe haute pression (14) au moyen de laquelle du carburant sous haute pression est refoulé au moins indirectement jusqu'à au moins un injecteur (120), comprenant une pompe de refoulement (10) au moyen de laquelle du carburant est refoulé jusqu'à la pompe haute pression (14), la pompe haute pression (14) comprenant au moins un piston de pompe (26) qui est entraîné suivant un mouvement de va-et-vient par un entraînement (20, 22) disposé dans une zone d'entraînement (19), une zone basse pression étant formée entre la pompe de refoulement (10) et la pompe haute pression (14), la zone d'entraînement (19) de la pompe haute pression (14) étant connectée à la zone basse pression, et une soupape de décharge de carburant (36) étant prévue dans la zone basse pression, caractérisé en ce que la soupape de décharge de carburant (36) est réalisée selon l'une quelconque des revendications précédentes.
  10. Dispositif d'injection de carburant selon la revendication 9, caractérisé en ce qu'un dispositif de dosage de carburant (16) est prévu entre la pompe de refoulement (10) et la pompe haute pression (14), au moyen duquel la quantité de carburant refoulée par la pompe haute pression (14) peut être réglée de manière variable, et en ce que la zone basse pression s'étend entre la pompe de refoulement (10) et le dispositif de dosage de carburant (16).
EP20080848181 2007-11-05 2008-09-18 Soupape de décharge de carburant pour dispositif d'injection de carburant, et dispositif d'injection de carburant présentant une soupape de décharge de carburant Not-in-force EP2207955B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710052665 DE102007052665A1 (de) 2007-11-05 2007-11-05 Kraftstoffüberströmventil für eine Kraftstoffeinspritzeinrichtung und Kraftstoffeinspritzeinrichtung mit Kraftstoffüberströmventil
PCT/EP2008/062443 WO2009059833A1 (fr) 2007-11-05 2008-09-18 Soupape de décharge de carburant pour dispositif d'injection de carburant, et dispositif d'injection de carburant présentant une soupape de décharge de carburant

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EP2207955A1 EP2207955A1 (fr) 2010-07-21
EP2207955B1 true EP2207955B1 (fr) 2014-11-12

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US (1) US8973557B2 (fr)
EP (1) EP2207955B1 (fr)
JP (1) JP5222368B2 (fr)
KR (1) KR101481206B1 (fr)
CN (1) CN101849096B (fr)
DE (1) DE102007052665A1 (fr)
WO (1) WO2009059833A1 (fr)

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KR101481206B1 (ko) 2015-01-09
US8973557B2 (en) 2015-03-10
JP5222368B2 (ja) 2013-06-26
EP2207955A1 (fr) 2010-07-21
JP2011503413A (ja) 2011-01-27
US20100258092A1 (en) 2010-10-14
KR20100072338A (ko) 2010-06-30
CN101849096A (zh) 2010-09-29
DE102007052665A1 (de) 2009-05-07
WO2009059833A1 (fr) 2009-05-14
CN101849096B (zh) 2013-06-19

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