EP1836385B1 - Soupape d'injection de combustible a multiplication de pression - Google Patents

Soupape d'injection de combustible a multiplication de pression Download PDF

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Publication number
EP1836385B1
EP1836385B1 EP05798800A EP05798800A EP1836385B1 EP 1836385 B1 EP1836385 B1 EP 1836385B1 EP 05798800 A EP05798800 A EP 05798800A EP 05798800 A EP05798800 A EP 05798800A EP 1836385 B1 EP1836385 B1 EP 1836385B1
Authority
EP
European Patent Office
Prior art keywords
control valve
pressure
injection valve
chamber
piston
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
EP05798800A
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German (de)
English (en)
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EP1836385A1 (fr
Inventor
Marco Ganser
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Ganser Hydromag AG
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Ganser Hydromag AG
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Publication of EP1836385A1 publication Critical patent/EP1836385A1/fr
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Publication of EP1836385B1 publication Critical patent/EP1836385B1/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
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification

Definitions

  • the present invention relates to a fuel injection valve for intermittent fuel injection in the Brenriraum a Verbrennungskraftmasffleine according to the preamble of patent claim 1.
  • the document DE 101 46 532 A1 discloses a fuel injector of this type.
  • the control valve may be formed as a 2/2-way valve or as a 3/2-way valve.
  • a fuel injector in which an electromagnetic actuator drives a 3/2 or 6/3 way valve.
  • an intensifier piston designed as a differential piston and the supply of fuel into a fuel high-pressure space adjacent to an injection valve seat are controlled by means of this control valve such that a pressure-controlled or stroke-controlled injection takes place.
  • the control valve member must each put a long way back to get from one switching position to another switching position. Typically, this path is several 1/10 mm. Further, the multiple injection with such control valves is very demanding and the structure of the fuel injection valve is extremely expensive.
  • the control valve is designed as a flat seat valve.
  • Flat seat valves have the property that they release large flow cross sections at a very small stroke.
  • the control valve member of a fuel injection valve according to the invention requires a stroke of only about 2/100 to 10/100 mm.
  • the control of the control valve member can thus also be effected by means of a piezoelectric actuator.
  • multiple injections are feasible without problems; this in the use of piezoelectric actuators as well as in the use of very fast electromagnetic actuators.
  • An Indian Fig. 1 shown fuel injector is intended to inject fuel intermittently in a well-known combustion chamber of an internal combustion engine. It has a substantially circular-cylindrical, stepped housing 10, on the front side - on that side with the smaller outer diameter - in a known manner, a valve seat member 12 is fixed by means of a cap nut 14.
  • the axis of the housing 10, the valve seat member 12 and the cap nut 14 coincide in the present example and is designated 16.
  • the axis of the housing, the valve seat member and the cap nut could also be desaxed or at an angle to each other.
  • an actuator arrangement 20 is arranged in a recess 18.
  • a piezoelectric actuator 22 of the actuator assembly 20 is intended to drive a control valve 24. This connects in the open position, a control pressure inlet 26 for the fuel on the housing 10 with the control pressure side of a designed as a differential piston booster piston 28.
  • the high pressure side of the booster piston 28 is provided with a in the valve seat member 12 arranged high-pressure fuel chamber 30 is connected, which adjoins a formed on the valve seat member 12, a cone-shaped like injection valve seat 32.
  • a needle-like injection valve member 34 is arranged centrally movable relative to the axis 16 and in the direction of this axis 16, which is intended on the one hand to cooperate with the injection valve seat 32, and the other piston-like limits a cylinder chamber 36 connected to the control pressure inlet 26.
  • the control pressure - or feed pressure - is about 200 - 1600 bar.
  • the control valve 24, the booster piston 28 and all necessary connection passages are arranged in the housing 10, or formed thereon.
  • the housing 10 is shown in one piece; However, it may be composed of several parts in order to easily form the necessary recesses and connecting passages in the production can.
  • the piezoelectric actuator 22 is accommodated in an actuator housing 38, which rests on the one hand on a shoulder 40 of the recess 18 on the housing 10 and on the other hand by means of a sleeve-shaped fastening screw 42, which is threaded into the housing 10 and is supported on a support shoulder 44 of the actuator 38, held in abutment against the shoulder 40.
  • Electrical control lines via which the actuator 22 is controlled in a known manner by a controller, are designated 46.
  • the actuator 22 has an actuator shaft 48, which upon excitation or de-excitation of the actuator 22 in the direction of the axis 16 about a stroke of about 0.02 - 0.1 mm in the one or the opposite direction is moved.
  • the recess 18 has, adjacent to the actuator arrangement 20, a low-pressure space 50, which is connected to a low-pressure outlet connection 54 on the housing 10 via a low-pressure passage 52 extending radially through the housing 10, from which loss of fuel caused by leakage or the control a fuel storage tank is passed.
  • control valve 24 and the pressure boosting device with the booster piston 28 is under the inclusion of FIG. 2 described in more detail.
  • a circular cylindrical control valve chamber 56 is recessed centrally to the axis 16, in which a disc-shaped control valve member 58 is movably received in the direction of the axis 16.
  • a guide passage 60 which is penetrated in close sliding fit by an actuating shaft 62 which rests on the one hand on the control valve member 58 and on the other hand at the free end of the Aktuatorschafts 48.
  • the control valve chamber 56 is connected to the low pressure chamber 50 via a throttle channel 64.
  • planar control valve seat 66 On the side facing away from the operating shaft 62 of the control valve member 58 of the control valve chamber 56 is limited by a formed on the housing 10, planar control valve seat 66. With this the plate-like control valve member 58 cooperates, which is also formed flat on the control valve seat 66 side facing with high precision. In Fig. 2 the control valve member 58 is located in one of Control valve seat 66 spaced open position, whereas it is in Fig. 1 is shown in its resting on the control valve seat 66 closed position.
  • an annular inlet groove 68 extending around the axis 16 is formed in the housing 10 and is open in the direction of the control valve chamber 56 and closed by the control valve member 58 when the control valve 24 is closed.
  • the inlet groove 68 is fluidly connected to the control pressure inlet 26 via a control pressure channel 70 in the housing 10. Further, it is formed with the largest possible radial outer diameter, so that when opening the control valve 24 very quickly a large flow cross section is free.
  • a circular cylindrical piston guide chamber 74 is formed, in which a control pressure side piston part 28 'of the booster piston 28 is received and guided in close sliding fit in the direction of the axis 16 back and forth.
  • the free cross sections of the control pressure channel 70 and the connecting channel 78 are much larger than the narrowest cross section of the throttle channel 64.
  • the check valve 92 designed as a spring-loaded ball valve allows fuel to flow from the control pressure inlet 26 into the piston output space 84, but prevents fuel from flowing out of the piston output space 84 into the control pressure branch line 90.
  • the fuel high-pressure space 30 formed by a recess in the valve seat element 12 is graduated in a circular cylindrical manner and limited on the one hand by the injection valve seat 32 and on the other hand by the end face of the housing 10.
  • a sleeve-like design needle guide element 94 is arranged, the on the one hand via three radially outwardly projecting ribs 94 'on the valve seat member 12 is supported centering and by on the other hand radially inwardly this side end portion of the injection valve member 34 is guided in tight sliding fit.
  • the ribs 94 ' may also be omitted (guidance of the needle guide element 94 would be assumed by ribs 100, see below).
  • the needle guide element 94 circumferentially bounded the cylinder chamber 36 and is under the force of a closing spring 96 sealingly against the end face of the housing 10.
  • the closing spring 96 is supported on the one hand at the free end of the needle guide element 94 and on the other hand via an annular disc 98 and a support element 98 'in a known manner on the injection valve member 34 from.
  • the closing spring 96 presses the fuel injection valve member 34 in the direction against the injection valve seat 32. Between the valve seat member 12 and the needle guide member 94, the closing spring 96 and the injection valve member 34 remains a large flow area for the fuel free.
  • the injection valve member 34 has in the radial direction three projecting guide ribs 100, via which it is guided on the valve seat member 12, in the region of the narrower in cross section part of the high-pressure fuel chamber 30, in the axial direction. In the region between the three guide ribs 100, a large flow cross-section is present so that fuel can flow unhindered to the injection valve seat 32.
  • nozzle passages 102 are excluded, by means of which an injection of the fuel is injected under very high pressure in the combustion chamber.
  • valve control valve 34 acts as a 2/2-way valve.
  • a circular cylindrical recess is formed in the region of the control valve seat 66, centric to the axis 16, which forms an outlet opening 104 encompassed by a distance from the inlet groove 68.
  • This is flow-connected to the piston drive chamber 76 via a further connecting channel 78 '.
  • the injection valve member 34 is again plate-shaped or disk-shaped, but now firmly connected to the operating shaft 62, preferably with this integrally formed.
  • the control valve member 58 bears sealingly against an annular sealing surface of the control valve seat 66 which adjoins the inlet groove 68 radially on the one hand, and against a further annular sealing face of the control valve seat 66 between the inlet groove 68 and the outlet opening 104.
  • the control valve member 58 In the Fig. 4 shown open position of the control valve 34, the control valve member 58, the connection from the inlet groove 68 to the connecting channel 78 and further connecting channel 78 'free.
  • the control valve member 58 has on the side facing away from the control valve seat 66 an annular sealing shoulder 106 which protrudes in the axial direction with respect to the adjoining operating shaft 62 in the radial direction and with respect to the remaining part of the control valve member 58.
  • the sealing shoulder 106 is in the open position of the control valve 24 sealingly on the housing 10.
  • the guide passage 60 in which the operating shaft 62 is guided in sliding fit, is widened in its, the control valve chamber 56 facing end portion to a circumferential relief groove 108, which via a discharge channel 64 'permanently - and without throttle - with the low-pressure chamber 50 and thus the Low pressure outlet 54 is connected.
  • FIGS. 5 and 6 show an embodiment of a fuel injection valve according to the invention, in which this problem is resolved and which the control of the control valve 24 also by means of an electromagnetic actuator 22 allows this by at least partially compensating the forces caused by the pressure differences forces on the control valve member 58th
  • FIGS. 5 and 6 embodiment shown is that of in Fig. 4 similar embodiment shown. In the following, only the differences will be discussed.
  • a shaft 62 ' At the disk-like control valve member 58 is on the side facing away from the operating shaft 62, a shaft 62 ', preferably integrally arranged, which is guided in a shaft passage 110 in the housing 10 in close sliding fit and carries in its free end a compensating piston 112.
  • the compensation piston 112 is guided in a cylinder recess 114, also in close sliding fit.
  • the cylinder recess 114 and the compensating piston 112 delimit, on the side of the compensation piston 112 facing the control valve member 58, a compensation pressure chamber 116, which is flow-connected to the control pressure channel 70 and thus to the control pressure inlet 26.
  • the circumferential inlet groove 68 in comparison to those in the Fig. 1 - 4th shown embodiments, measured in their radial width narrow, ie slot-shaped, whereby the force acting on the control valve member 58 when the control valve 24 is closed is reduced.
  • the inlet groove 68 is fed via a cross-sectionally larger annular channel 68 ', which communicates with the control pressure channel 70.
  • the further connecting channel 78' opens radially outward from the outlet opening 104 and leads into the connecting channel 78.
  • control valve 24 is in the open position.
  • the control valve member 58 acts on the control valve member 58, as indicated by the thick arrow directed against the actuator 22 force, which the pressure difference between the pressure of the fuel in the control pressure inlet 26 connected to the control valve chamber 56 and the low-pressure outlet 54 connected to the relief groove 108, multiplied by the difference of the area of the compensating piston 112 - diameter D2 - and the surface of the sealing shoulder 106 - diameter D1 - corresponds.
  • the control valve 104 of the Actuator 48 thus apply a force opposing this force.
  • control valve 24 In the Fig. 6 the control valve 24 is in the closed position, wherein the control valve member 58 abuts the control valve seat 66 and the inlet groove 68 seals.
  • D3 is in Fig. 6 the diameter of the outlet opening 104 is characterized.
  • D4 the diameter of the control valve member 58 is indicated, and D5 denotes the diameter of the shaft 62 '.
  • Fig. 7 shows a further embodiment of the inventive injection valve, which is formed with respect to the control valve 24 is the same as those according to Fig. 4 , However, the C-shaped connecting channel does not open directly into the piston drive chamber 76, but in the concentric with the axis 16 arranged further connecting channel 78 '.
  • control-pressure-side piston part 28 'of the booster piston 28 is formed like a step. He has on its the piston drive chamber 76 side facing a circular cylindrical, central to the axis 16 piston projection 122 whose designated Da diameter is slightly larger than the designated Db diameter of the high-pressure side piston member 28 ".
  • the piston guide space 74 has an extension 124, in which the piston projection 122 is immersed by the length designated L, when the booster piston 28 in the in the Fig. 7 is shown in rest position. In this stop the lugs 80 at the bottom of the extension 124 at.
  • the 8 and 9 show an embodiment with pressure compensation, which those in the FIGS. 5 and 6 shown embodiment is very similar.
  • the structural design is shown with more details.
  • a pill-like control valve seat body 130 is inserted in a graduated recess 16 to the axis of the housing recess 128 - this connects to the recess 18 - a pill-like control valve seat body 130 is inserted. With one end face of this sealingly against the bottom of the housing recess 128 and at the other end face of the control valve seat 66, the inlet groove 68 and the outlet opening 104 are formed.
  • a bore passing through the control valve seat body 130 parallel to the axis 16 forms part of the connection channel 78 which is fluidly connected to the bottom of the housing recess 128 with a further part of the connection channel 78 formed on the housing 10 leading to the piston drive chamber 76.
  • These webs 132 connect with respect to the annular channel 68 'radially inner part of the control valve seat body 130 with the radially outer part; see in particular Fig. 9 , In one of these webs 132, an inclined bore forming the further connecting channel 78 'extends from the outlet opening 104 to the connecting channel 78.
  • the compensating low-pressure passage 120 extends through a further web 132. This opens out of the cylindrical recess 114, which is blind-like on the control valve seat body 130 and on the other hand Bottom of the housing recess 128 is closed.
  • the compensation pressure chamber 116 is connected via a radially extending passage with the annular channel 68 ', which in turn at the bottom of the housing recess 128 with the recessed on the housing 10 control pressure channel 70 is fluidly connected.
  • control valve seat body 130 two positioning pins 134 are inserted, which engage in corresponding blind holes in the bottom of the housing recess 128 for fixing the rotational position of the control valve seat body 130 with respect to the housing 10.
  • annular disc 136 On the bottom of the housing recess 128 facing away from the end face of the control valve seat body 130 sits an annular disc 136, which limits the control valve chamber 56 circumferentially and the inner diameter is selected such that the connecting channel 78 is fluidly connected to the control valve chamber 56.
  • control valve chamber 56 On the side facing away from the control valve seat body 130, the control valve chamber 56 is delimited by a disc 138, which rests on the annular disc 136 and is provided with a central bore 140 which is penetrated by the operating shaft 62 with radial play. The annular gap between the operating shaft 62 and the disc 138 forms the discharge channel 64 '. In the control valve chamber 56 sits the disk-like control valve member 58 on the operating shaft 62nd
  • an annular, provided with a hexagon screw 142 is arranged, which is threaded with its external thread in an internal thread in the region of the housing recess 128. This acts on the disc 138, the washer 136 and the control valve seat body 130 with an axial force, so that these sealingly against each other and the control valve seat body 130 sealingly abut the bottom of the housing recess 128.
  • the hexagon socket screw 142 bounded inside a partial space of the housing recess 128, which adjoins the low pressure chamber 50.
  • the low pressure passage 52 is formed by a radial bore in the housing 10.
  • the actuator housing 38 which together with the actuator 22 inserted therein defines the low-pressure space 50, sits on the downstream end of the housing 10.
  • the operating shaft 62 is fixedly connected to the actuator shaft 48.
  • the compensating piston 112 may be configured to fully compensate for the forces acting on the control valve member 58.
  • the disc 138 also forms the seat for the sealing shoulder 106 of the control valve member 58 in order to separate the control valve chamber 56 from the low-pressure chamber 50 when the control valve 24 is open.
  • the disc 138 in cooperation with the control valve member 58 also forms the stop for the actuator or its armature. Further, in this embodiment, by selecting the thickness of the washer 136 and the axial dimension of the control valve member 58, the stroke of the actuator 22 can be adjusted.
  • the in the Fig. 1-9 shown fuel injectors operate as follows. Starting from the in the Fig. 1 and 6 shown state with closed control valve 24 and the injection valve seat 32 adjacent injection valve member 34 is so controlled for a fuel injection of the actuator 22, the actuator shaft 48 moves away from the control valve seat 66. As a result, the control valve member 58 moves away from the control valve seat member 66 in the in the Fig. 2 . 4 . 5 . 7 and 8th shown open position, whereby the piston drive chamber 76 is subjected to control pressure.
  • the actuator 22 is driven such that the actuator shaft 48 moves in the direction against the control valve seat 66 and thereby the control valve 24 is closed.
  • the differential piston By connecting the control valve chamber 56 and thus the piston drive chamber 76 through the throttle channel 64 and discharge channel 64 'with the low-pressure chamber 50, the differential piston now moves in the opposite direction, causing the pressure of the fuel in the high-pressure fuel chamber 30 drops rapidly and the injection valve member 34th moved toward the injection valve seat 32 and thereby terminates the injection process.
  • Is between the control pressure inlet 26 and the Kolbenabtriebsraum 84th Given pressure equalization, flows - by the check valve 92 opens - fuel in the Kolbenabtriebsraum 84 until the booster piston 28 rests with its stop lug 80 on the housing 10.
  • the fuel injection valve is now ready for another injection process.
  • the booster piston 28 need not necessarily move back or even all the way toward the end of the piston drive chamber 76 in the short pauses between each injection.
  • Flat seat valves have, as explained with reference to the exemplary embodiments shown, the property of releasing a very large flow cross-section even at a very small opening stroke.
  • the fuel injection valve according to the invention is also suitable for multiple injections.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (13)

  1. Soupape d'injection de combustible pour l'injection de combustible intermittente dans la chambre de combustion d'un moteur à combustion interne, comprenant un siège de soupape d'injection (32) contigu à une chambre à haute pression de combustible (30), un élément de soupape d'injection (34) en forme d'aiguille, qui d'une part coopère avec le siège de soupape d'injection (32) et d'autre part délimite à la façon d'un piston une chambre de cylindre (36) reliée à une entrée de pression de commande (26) pour le combustible, un piston amplificateur (28) agissant comme piston différentiel, lequel piston amplificateur délimite côté pression de commande une chambre d'entraînement de piston (76) pouvant être reliée à l'entrée de pression de commande (26) au moyen d'une soupape de commande (24) commandée au moyen d'un actionneur (22) commandé électriquement et pouvant être dissociée de cette entrée et côté haute pression une chambre de sortie de piston (84) reliée à la chambre à haute pression de combustible (30), caractérisée en ce que la soupape de commande (24) est conçue comme soupape à siège plat.
  2. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que la soupape de commande (24) présente un élément de soupape de commande (58), qui est disposé dans une chambre de soupape de commande (56), qui est reliée à une chambre à basse pression (50) au moins lorsque la soupape de commande (24) est fermée.
  3. Soupape d'injection de combustible selon la revendication 2, caractérisée en ce que l'élément de soupape de commande (58) est conçu en forme de disque et coopère avec un siège de soupape de commande (66), dans la zone duquel est disposée une rainure d'entrée (68) reliée à l'entrée de pression de commande (26) et au moins approximativement en forme d'anneau circulaire.
  4. Soupape d'injection de combustible selon la revendication 3, caractérisée en ce qu'une ouverture de sortie (104) reliée à la chambre d'entraînement de piston (76) est disposée dans la zone du siège de soupape de commande (66), de façon centrée et à une certaine distance de la rainure d'entrée (68).
  5. Soupape d'injection de combustible selon la revendication 3 ou 4, caractérisée en ce que l'élément de soupape de commande (58) est disposé sur une tige d'actionnement (62) coopérant avec l'actionneur (22) et guidée dans un ajustement de glissement.
  6. Soupape d'injection de combustible selon l'une quelconque des revendications 3 à 5, caractérisée en ce que l'élément de soupape de commande (58) est relié à un piston de compensation (28) délimitant une chambre de pression de compensation (116) reliée à l'entrée de pression de commande (26).
  7. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 6, caractérisée en ce que la chambre de sortie de piston (84) est reliée à l'entrée de haute pression (26) par un clapet anti-retour (92).
  8. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 6, caractérisée en ce que la chambre de sortie de piston (84) est reliée par un clapet anti-retour (92) à une entrée pour le combustible à injecter.
  9. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 8, caractérisée en ce que la chambre d'entraînement de piston (76) est reliée par un passage d'étranglement (64) à une sortie de basse pression (54).
  10. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 8, caractérisée en ce que la chambre d'entraînement de piston (76) est reliée par un passage (64') à une sortie de basse pression (54) et en ce que la sortie de basse pression (54) est fermée, de préférence par l'élément de soupape de commande (58), lorsque la soupape de commande (24) est ouverte.
  11. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 10, caractérisée en ce que le piston amplificateur (28) est conçu de façon échelonnée côté pression de commande et la chambre d'entraînement de piston (76) est délimitée au moins approximativement dans le sens opposé de façon échelonnée.
  12. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 11, caractérisée en ce que l'actionneur (22) est conçu comme un actionneur piézoélectrique.
  13. Soupape d'injection de combustible selon l'une quelconque des revendications 1 à 12, caractérisée en ce que la soupape de commande (24) présente un siège de soupape de commande (66) conçu sur une face frontale d'un corps de siège de soupape de commande (130) et un disque annulaire (136) d'épaisseur pouvant être choisie est disposé entre l'actionneur (22) et le corps de siège de soupape de commande (130).
EP05798800A 2004-12-03 2005-11-08 Soupape d'injection de combustible a multiplication de pression Not-in-force EP1836385B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH20062004 2004-12-03
PCT/CH2005/000656 WO2006058444A1 (fr) 2004-12-03 2005-11-08 Soupape d'injection de combustible a multiplication de pression

Publications (2)

Publication Number Publication Date
EP1836385A1 EP1836385A1 (fr) 2007-09-26
EP1836385B1 true EP1836385B1 (fr) 2010-12-29

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EP05798800A Not-in-force EP1836385B1 (fr) 2004-12-03 2005-11-08 Soupape d'injection de combustible a multiplication de pression

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Country Link
US (1) US7513241B2 (fr)
EP (1) EP1836385B1 (fr)
AT (1) ATE493577T1 (fr)
DE (1) DE502005010779D1 (fr)
WO (1) WO2006058444A1 (fr)

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ATE455952T1 (de) * 2006-10-16 2010-02-15 Ganser Hydromag Brennstoffeinspritzventil für verbrennungskraftmaschinen
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DE19939450A1 (de) 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19939452C2 (de) 1999-08-20 2003-04-17 Bosch Gmbh Robert Vorrichtung zur Einspritzung von Kraftstoff
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DE10222196A1 (de) * 2002-05-18 2003-11-27 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US6739575B2 (en) * 2002-06-06 2004-05-25 Caterpillar Inc Piezoelectric valve system
DE10229418A1 (de) * 2002-06-29 2004-01-29 Robert Bosch Gmbh Einrichtung zur Dämpfung des Nadelhubes an Kraftstoffinjektoren
US6854446B2 (en) * 2002-07-11 2005-02-15 Toyota Jidosha Kabushiki Kaisha Fuel injection apparatus
DE10250130A1 (de) 2002-10-28 2004-03-04 Robert Bosch Gmbh Hochdruckeinspritzeinrichtung mit Druck- und Hubsteuerung
US7320310B2 (en) * 2003-04-02 2008-01-22 Robert Bosch Gmbh Fuel injector provided with provided with a pressure transmitter controlled by a servo valve
DE10335059A1 (de) * 2003-07-31 2005-02-17 Robert Bosch Gmbh Schaltventil für einen Kraftstoffinjektor mit Druckübersetzer
JP3997983B2 (ja) * 2003-11-10 2007-10-24 株式会社デンソー 圧電素子駆動による３方向切替弁およびその３方向切替弁を用いた燃料噴射弁
DE102004015744A1 (de) * 2004-03-31 2005-10-13 Robert Bosch Gmbh Common-Rail-Injektor
DE102004022267A1 (de) * 2004-05-06 2005-12-01 Robert Bosch Gmbh Verfahren und Vorrichtung zur Formung des Einspritzdruckes an einem Kraftstoffinjektor
DE102004022270A1 (de) * 2004-05-06 2005-12-01 Robert Bosch Gmbh Kraftstoffinjektor für Verbrennungskraftmaschinen mit mehrstufigem Steuerventil
AT501727B1 (de) * 2005-09-14 2006-11-15 Hoerbiger Valvetec Gmbh Gasventil

Also Published As

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WO2006058444A1 (fr) 2006-06-08
ATE493577T1 (de) 2011-01-15
US7513241B2 (en) 2009-04-07
US20080115765A1 (en) 2008-05-22
DE502005010779D1 (de) 2011-02-10
EP1836385A1 (fr) 2007-09-26

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