EP2052148B1 - Injecteur de carburant avec commande directe du pointeau et servosoupape d'assistance - Google Patents

Injecteur de carburant avec commande directe du pointeau et servosoupape d'assistance Download PDF

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Publication number
EP2052148B1
EP2052148B1 EP07730183A EP07730183A EP2052148B1 EP 2052148 B1 EP2052148 B1 EP 2052148B1 EP 07730183 A EP07730183 A EP 07730183A EP 07730183 A EP07730183 A EP 07730183A EP 2052148 B1 EP2052148 B1 EP 2052148B1
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EP
European Patent Office
Prior art keywords
control
piston
valve member
chamber
injection valve
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
EP07730183A
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German (de)
English (en)
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EP2052148A1 (fr
Inventor
Friedrich Boecking
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2052148A1 publication Critical patent/EP2052148A1/fr
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Publication of EP2052148B1 publication Critical patent/EP2052148B1/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
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1 (US Pat. WO-A-96/37698 ).
  • a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having an injector housing having a fuel inlet communicating with a central fuel high pressure source outside the injector housing and with a pressure space within the injector housing depending on the position a control valve is injected with high pressure fuel.
  • the control valve is actuated by means of a piezoelectric actuator.
  • a coupling space is formed between the control valve and the piezoelectric actuator. This acts as a hydraulic translator on the valve piston of the control valve.
  • An inventively designed injector for injecting fuel into a combustion chamber of an internal combustion engine is actuated by means of an actuator and is connected to a fuel inlet, is supplied via the standing under system pressure fuel.
  • at least one injection opening can be opened or closed by an injection valve member, wherein the injection valve member by means of a control piston is controlled via a control chamber, which is exposed to the control piston and a piston portion of the injection valve member with respective pressure surfaces.
  • the control piston is also a valve piston of a control valve.
  • the valve piston and the piston portion of the injection valve member enclose a further control chamber, which is connected with the control valve open with a fuel return and with the control valve closed to the fuel inlet.
  • a first opening phase of the injection valve member the control piston acts via the first control chamber according to the principle of direct control of the injection valve member.
  • a further opening phase of the injection valve member begins when the control piston acts as a valve piston of a servo valve and controls the further control chamber.
  • the essence of the invention lies in a combination of direct control and servo control of the injection valve member, wherein the opening of the injection valve member takes place when the actuator moves the control piston in the direction of the injection openings.
  • a further advantage of the inventively embodied injector is that the stroke of the actuator is translated so that even a short actuator is sufficient to produce a sufficiently large stroke of the injection valve member. This makes it possible to reduce the height of the injector.
  • the opening speed of the injection valve member is increased at the beginning of the opening process in comparison to the fuel injectors known from the prior art by the inventive design of the injector.
  • an annular portion is formed on the control piston, in which the piston portion of the injection valve member is guided.
  • the additional control chamber is limited by the injection valve member and the annular portion.
  • the aring-shaped portion is formed on the piston portion of the injection valve member. In the annular portion of the control piston is guided and the other control chamber is limited by the control piston and the annular portion.
  • the actuator is connected to a booster piston, wherein the booster piston defines with an end face a booster chamber, which is bounded on the opposite side by an upper end face of the control piston.
  • the ratio of the strokes of the booster piston and the control piston is proportional to the ratio the diameter. The larger the diameter of the booster piston compared to the diameter of the control chamber limiting end face of the control piston, the larger the stroke of the control piston compared to the stroke of the booster piston.
  • the control chamber which is bounded by the injection valve member and the control piston, connected by a connecting channel with a valve chamber, the Control spool encloses.
  • the valve chamber is a valve chamber of the control valve.
  • a throttle element is received in the connecting channel, through which the control chamber, which is delimited by the injection valve member and the control piston, is connected to the valve chamber.
  • the throttle element acts as a tolerance limiter in the connecting channel.
  • valve chamber of the control valve which is connected to the further control chamber via the connecting channel, is connected by means of a throttle element to the fuel inlet.
  • the injection valve member in which the injection valve member is guided in an annular portion in the control piston, define a lower end face on the annular portion of the control piston and a shoulder on the piston portion of the injection valve member, the control space.
  • the injection valve member is pushed out of this during a movement of the control piston into the control chamber.
  • This configuration has the effect that, when the actuator is energized, that is to say with an extended actuator, the control piston is moved into the control chamber and the injection valve member moves out of the control chamber through this movement of the control piston, thus lifting it out of its seat and releasing the at least one injection opening.
  • the stroke of the injection valve member in dependence on the stroke of the control piston can be adjusted.
  • the piston portion of the injection valve member has an annular portion in which the control piston is guided, define an end face on the annular portion of the piston portion of the injection valve member and a shoulder on the control piston the control chamber.
  • the function here is the same as in the embodiment in which the annular portion is formed on the control piston, and an injection valve member is guided in this annular portion on the control piston.
  • control piston in an embodiment is connected directly to the actuator.
  • the actuator is preferably housed in a housing which is made of a material whose coefficient of thermal expansion corresponds to that of the actuator. Due to the almost same coefficient of thermal expansion, the housing in which the actuator is received, preferably made of Invar, when the actuator is a piezoelectric actuator.
  • a compensation element is added in a preferred embodiment between the actuator and the housing.
  • the compensating element is made of aluminum or aluminum alloys, for example.
  • the housing is made of a material whose coefficient of thermal expansion corresponds to that of the actuator and in which a compensating element is accommodated between the housings and the actuator, by which a residual error of the coefficient of thermal expansion between actuator and housing is compensated, is particularly preferred when the spool is directly connected to the actuator. This is therefore necessary to ensure a clean closing of the control valve.
  • An optionally occurring residual error in the stroke for generating the tightness at the control valve can be compensated for example electrically.
  • FIG. 1 a fuel injector designed according to the invention is shown in a first embodiment.
  • a fuel injector 1 comprises an injection valve member 3, which is guided in a guide 5 in a lower housing part 7. At the injection valve member 3, a sealing edge 9 is formed, which is in a seat 13 when the injection opening 11 is closed. In addition to the embodiment shown here, in which the fuel injector 1 has an injection opening 11, it is also possible that more than one injection opening 11 is provided.
  • the injection valve member 3 is enclosed by a nozzle chamber 15.
  • the nozzle chamber 15 is connected via an inlet channel 17 with a fuel inlet 19.
  • the fuel inlet 19 is in turn connected to a high-pressure accumulator, not shown here, of a common-rail system.
  • the injection valve member 3 has a piston portion, which is guided in an annular portion 21 of a control piston 23.
  • an end face 57 is formed, which is exposed as a pressure surface of a control chamber 59.
  • a shoulder 61 is formed, which also limits the control space 59 as the other pressure surface on the same side as the end face 57 of the annular portion 21. This leads to that the injection valve member 3 is moved in a movement of the control piston 23 in the opposite direction, so that a stroke reversal of Aktorhubs based on the stroke of the injection valve member 3 is formed.
  • a further control chamber 27 is enclosed.
  • a spring element 29 is received, which is preferably designed as a compression spring coil spring.
  • the control piston 23 simultaneously acts as a valve piston of a control valve 31.
  • a sealing edge 33 is formed on the control piston 23.
  • the control piston 23 is enclosed on the side facing the injection valve member 3 by a valve chamber 37.
  • a connecting channel 39 is formed, through which the valve chamber 37 is connected to the other control chamber 27. Furthermore, a throttle element 41, which connects the valve chamber 37 with the inlet channel 17, opens into the valve chamber 37. As a result, when the control valve 31 is closed, the control chamber 27 is filled via the throttle element 41, the valve chamber 37 and the connecting channel 39 with fuel under system pressure.
  • a plate-shaped portion 43 is formed, which is connected to an actuator 45, preferably with a piezoelectric actuator.
  • an actuator 45 preferably with a piezoelectric actuator.
  • a piezoelectric actuator it is also possible to use any other actuator known to the person skilled in the art, which expands when energized and contracts when the current supply is terminated.
  • the actuator On the opposite side of the control piston 23, the actuator is connected to a disk 47. To achieve the necessary bias of the actuator is enclosed by a spring element 49.
  • the spring element 49 is preferably designed as a tension spring Bourdon tube.
  • the actuator 45 is housed in a housing 51 which is made of a material having a substantially same thermal expansion coefficient as the actuator 45. If the actuator 45 is a piezoelectric actuator is, the housing 51 is preferably made of Invar. To compensate for any residual error due to the different thermal expansion coefficients is in the in FIG. 1 illustrated embodiment between the disc 47, which is connected to the actuator 45, and the housing 51 a compensating element 53 added.
  • the compensating element 53 is made of aluminum, for example.
  • an actuator chamber 55 is formed, which is filled with fuel during operation of the fuel injector 1.
  • the actuator 45 is surrounded by fuel. Due to the good thermal conductivity of the fuel, the heat generated by the actuator 45 during operation is transmitted to the housing 51. Thus, the fuel with which the actuator 45 is lapped, at the same time for cooling the actuator 45th
  • the actuator 45 is energized. As a result, the actuator 45 expands. By expanding the actuator 45, the control piston 23 is moved in the direction of the injection valve member 3. The thus increasing pressure force acts on the shoulder 61 on the piston portion of the injection valve member 3, which moves the injection valve member 3 in the opposite direction to Aktorhub and the injection valve member 3 lifts from its seat 13 and thereby the at least one injection opening 11 releases.
  • the control piston 23 via the control chamber 59 acts directly on the injection valve member 3. At the same time lifts the sealing edge 33 of the control valve 31 from its seat 35 and thus gives a connection from the valve chamber 37 in a fuel return by the movement of the control piston 23 63 free.
  • the pressure in the valve chamber 37 drops to the return pressure. Due to the reduced pressure in the valve chamber 37, fuel flows from the further control chamber 27 via the connecting channel 39 into the valve chamber 37 and from there into the fuel return 63. The pressure in the further control chamber 27 decreases.
  • the control piston 23 acts as a valve piston of a servo-valve and controls the further control chamber 27 at. Due to the decreasing pressure in the control chamber 27, the movement of the injection valve member 3 is facilitated. A quick opening of the injection valve member 3 with a translated actuator stroke is thereby achieved.
  • the energization of the actuator 45 is stopped.
  • the actuator 45 contracts and thereby moves the control piston 23 in the direction of the actuator 45.
  • the end face 57 lifts out of the control chamber 59 and thus increases its volume.
  • the pressure in the control chamber 59 decreases. This results in a lower pressure force acting on the shoulder 61 on the injection valve member 3. Sobad the pressure force acting on the shoulder 61 of the injection valve member 3 is smaller than the pressure force acting on the upper end face 25 of the injection valve member 3, the injection valve member 3 moves into its seat 13 and thereby closes the injection port 11 is supported Movement of the injection valve member 3 characterized in that the sealing edge 33 is placed in its seat 35 by the movement of the control piston 23 and so the control valve 31 is closed.
  • control valve 31 Once the control valve 31 is closed, can under System pressure standing fuel from the inlet channel 17 via the throttle element 41, the valve chamber 37 and the connecting channel 39 in the other control chamber 27 flow.
  • the pressure in the further control chamber 27 increases to system pressure.
  • a further increased pressure force acts on the upper end face 25 of the injection valve member 3. The movement of the injection valve member 3 is accelerated.
  • the housing 51 is made of a material which has approximately the same coefficient of thermal expansion as the actuator 45. Differences in the coefficients of thermal expansion of the actuator 45 and the housing 51 are compensated, for example, by the compensation element 53. Should nevertheless a residual error occur in the stroke, through which the control valve 31 does not close tightly, it is possible to electrically compensate for this error.
  • the actuator is operated, for example bipolar. For this purpose, however, it is necessary to use a bipolar piezoelectric actuator.
  • bipolar piezoelectric actuator contracts when the voltage is reversed.
  • the control valve 31 does not close due to the thermal expansion of the actuator 45 to apply a negative voltage to the actuator 45 and thus cause a contraction of the actuator 45.
  • the control piston 23 is moved further in the direction of the actuator 45 and the sealing edge 33 placed in its seat 35.
  • FIG. 2 a fuel injector designed according to the invention is shown in a second embodiment.
  • FIG. 2 illustrated fuel injector differs from the in FIG. 1 shown fuel injector characterized in that the control piston 23 is not connected to the actuator 45, but limited with an upper end face 65 a booster chamber 67. At the upper end surface 65 opposite side of the booster chamber 67 is bounded by an end face 69 of a booster piston 71. At the booster piston 71, a plate-shaped extension 73 is formed, which is connected to the actuator 45.
  • control piston 23 Since the control piston 23 is not directly connected to the actuator 45, but a hydraulic transmission of the movement of the actuator 45 takes place on the control piston 23, it is in the in FIG. 2 illustrated embodiment, by providing a housing 51 made of a material having a thermal expansion coefficient which corresponds to that of the actuator 45, a occurring due to thermal expansion To compensate for lifting errors. At the same time it is possible to translate the stroke of the actuator 45 to the stroke of the control piston 23 through the translator chamber 67. The transmission ratio is dependent on the diameter d 1 of the booster piston 71 and the diameter d 2 of the control piston 23.
  • the operation of the fuel injector with the in FIG. 2 illustrated embodiment differs from the in FIG. 1 illustrated embodiment in that when power to the actuator 45, the actuator 45 expands and thereby the booster piston 71 is moved with the end face 69 in the booster chamber 67. As a result, the volume in the interpreter space 67 decreases. The pressure in the interpreter room 67 increases. Due to the increased pressure, an increased pressure force acts on the upper end surface 65 of the control piston 23. Due to this increased pressure force on the upper end face 65 of the control piston 23, the control piston 23 is moved in the direction of the injection valve member 3. By the movement of the control piston 23, the sealing edge 33 is lifted from its seat 35 and the control valve 31 opens.
  • the energization of the actuator 45 is released.
  • the actuator 45 contracts.
  • the booster piston 71 is moved with the end face 69 from the booster chamber 67.
  • the volume in the translator room 67 increases.
  • the pressure drops in the booster chamber 67 and on the upper end face 65 of the control piston 23 acts a lower pressure force.
  • the control piston 23 is moved in the direction of the booster piston 71 in the booster chamber 67. This movement of the control piston 23 causes the sealing surface 33 is placed in the seat 35 and so the control valve 31 closes the connection from the valve chamber 37 in the fuel return 63.
  • FIG. 3 shows a fuel injector designed according to the invention in a third embodiment.
  • annular portion 75 is formed, in which the control piston 23 is guided.
  • the annular portion 75 and the control piston 23 surround the other control chamber 27.
  • the annular portion 75 on the piston portion of the injection valve member 3 bounded with a face 77 a control chamber 79.
  • a shoulder 81 is formed on the control piston 23, the control chamber 79 on the same Side bounded as the end face 77 of the annular portion 75.
  • a third control chamber 83 which is connected to the fuel inlet 19 via the inlet channel 17, the second control chamber 79 by a ring member 85, which encloses the annular portion 75 on the injection valve member 3, limited ,
  • the ring element 85 is provided with a biting edge 87 against a shoulder 89 on the middle housing part 91.
  • the force required for this purpose is exerted by a spring element 93, which is supported with one side against the ring member 85 and with the other side against the lower housing part 7.
  • the spring element 93 is preferably designed as a compression spring coil spring.
  • a throttle element 95 is formed in the connecting channel 39.
  • FIG. 3 shown fuel injector of the actuator 45 energized.
  • the actuator 45 expands.
  • the booster piston 71 connected to the actuator 45 is moved in the direction of the translator chamber 67.
  • the pressure in the interpreter room 67 increases.
  • an increased pressure force on the upper end surface 65 of the control piston 23 acts.
  • the control piston 23 is moved in the direction of the injection valve member 3.
  • the sealing edge 33 rises from its seat 35.
  • a connection from the other control chamber 27 via the connecting channel 39 with the throttle element 95 in the valve chamber 37 and from there into the fuel return 63 is released.
  • the pressure in the other control chamber 27 decreases.
  • the volume in the control chamber 79 is increased by the movement of the control piston 23, since the shoulder 81 is moved in the direction of the injection valve member. As a result, the pressure in the control chamber 79 decreases.
  • On the end face 77 of the annular portion 75 on the piston portion of the injection valve member 3 acts a lower pressure force. Due to the pressure force in the third control chamber 83, which acts on a second shoulder 99 on the injection valve member 3, the injection valve member is lifted out of its seat 13 and releases the at least one injection opening.
  • the energization of the actuator 45 is canceled.
  • the actuator 45 contracts.
  • the booster piston 71 is moved in the direction of the actuator 45.
  • the volume in the interpreter room 67 increases.
  • On the upper end face 65 of the control piston 23 acts a lower pressure force, whereby the control piston 23 is moved in the direction of the booster chamber 67.
  • the sealing edge 33 is placed back in its seat 35 and thus closes the control valve 31.
  • About the inlet throttle flows under system pressure fuel from the inlet channel into the valve chamber 37 and from there via the throttle element 95 and the connecting channel 39 in the other control chamber 27th Pressure in control room 27 increases.
  • the actuator chamber 55 is connected via a channel 101 to the inlet channel 17.
  • fuel in the actuator chamber 55 under system pressure. This fuel is used to dissipate the heat generated during operation of the actuator to the housing, since the heat transfer coefficient of the fuel is substantially greater than the heat transfer coefficient of a gas.

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

Claims (12)

  1. Injecteur pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne, l'injecteur (1) étant actionné au moyen d'un actionneur (45) et étant connecté à une alimentation en carburant (19), par le biais de laquelle du carburant à la pression du système est injecté, et dans lequel au moins une ouverture d'injection (11) peut être ouverte ou fermée par le biais d'un organe de soupape d'injection (3), l'organe de soupape d'injection (3) étant commandé au moyen d'un piston de commande (23) par le biais d'un espace de commande (59, 79), auquel le piston de commande (23) et une portion de piston de l'organe de soupape d'injection (3) avec des surfaces de pression respectives (57, 81) et (61, 77) sont exposés, le piston de commande (23) étant un piston de soupape d'une soupape de commande (31) et la surface de pression (57, 81) du piston de commande (23) et la surface de pression (61, 77) de la portion de piston de l'organe de soupape d'injection (3) délimitant l'espace de commande (59, 79) du même côté, caractérisé en ce que le piston de commande (23) et la portion de piston de l'organe de soupape d'injection (3) entourent un espace de commande supplémentaire (27), qui, lorsque la soupape de commande (31) est ouverte, est connecté à une recirculation de carburant (63), et lorsque la soupape de commande (31) est fermée, est connecté à l'alimentation en carburant (19).
  2. Injecteur selon la revendication 1, caractérisé en ce qu'une portion (21) de forme annulaire est réalisée sur le piston de commande (23), dans laquelle la portion de piston de l'organe de soupape d'injection (3) est guidée, l'espace de commande supplémentaire (27) étant limité par la portion de piston de l'organe de soupape d'injection (3) et la portion de forme annulaire (21) du piston de commande (23).
  3. Injecteur selon la revendication 1 ou 2, caractérisé en ce que la surface de pression du piston de commande (23) est formée par une surface frontale inférieure (57) sur la portion de forme annulaire (21) et la surface de pression de la portion de piston de l'organe de soupape d'injection (3) est formée par un épaulement (61).
  4. Injecteur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'espace de commande supplémentaire (27), qui est limité par l'organe de soupape d'injection (3) et le piston de commande (23), est connecté par un canal de connexion (39) avec un espace de soupape (37), qui entoure le piston de commande (23).
  5. Injecteur selon la revendication 4, caractérisé en ce qu'un élément d'étranglement (95) est reçu dans le canal de connexion (39), qui relie l'espace de commande supplémentaire (27), qui est limité par l'organe de soupape d'injection (3) et le piston de commande (23), à l'espace de soupape (37).
  6. Injecteur selon la revendication 4 ou 5, caractérisé en ce que l'espace de soupape (37) est connecté à l'alimentation en carburant (19) au moyen d'un élément d'étranglement (41).
  7. Injecteur selon la revendication 1, caractérisé en ce qu'une portion de forme annulaire (75) est réalisée sur la portion de piston de l'organe de soupape d'injection (3), dans laquelle est guidé le piston de commande (23), l'espace de commande supplémentaire (27) étant limité par le piston de commande (23) et la portion de forme annulaire (75).
  8. Injecteur selon la revendication 7, caractérisé en ce qu'une surface frontale (77) sur la portion de forme annulaire (75) de la portion de piston de l'organe de soupape d'injection (3) et un épaulement (81) sur le piston de commande (23) limitent l'espace de commande (79) du même côté.
  9. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionneur (45) est connecté au piston de commande (23).
  10. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionneur (45) est connecté à un piston de multiplication (71), le piston de multiplication (71) délimitant, avec une face frontale (69), un espace de multiplication (67) qui est limité du côté opposé par une face frontale supérieure (65) du piston de commande (23).
  11. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un élément de compensation (53) est reçu entre l'actionneur (45) et le boîtier (51), lequel permet de compenser l'erreur résiduelle de coefficient de dilatation thermique entre l'actionneur (45) et le boîtier (51).
  12. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionneur (45) est reçu dans un boîtier (51) qui est fabriqué en un matériau dont le coefficient de dilatation thermique correspond à celui de l'actionneur (45).
EP07730183A 2006-08-07 2007-06-15 Injecteur de carburant avec commande directe du pointeau et servosoupape d'assistance Not-in-force EP2052148B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006036780A DE102006036780A1 (de) 2006-08-07 2006-08-07 Krafstoffinjektor mit direkter Nadelsteuerung und Servoventil-Unterstützung
PCT/EP2007/055939 WO2008017538A1 (fr) 2006-08-07 2007-06-15 Injecteur de carburant avec commande directe du pointeau et servosoupape d'assistance

Publications (2)

Publication Number Publication Date
EP2052148A1 EP2052148A1 (fr) 2009-04-29
EP2052148B1 true EP2052148B1 (fr) 2010-05-12

Family

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Family Applications (1)

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EP07730183A Not-in-force EP2052148B1 (fr) 2006-08-07 2007-06-15 Injecteur de carburant avec commande directe du pointeau et servosoupape d'assistance

Country Status (6)

Country Link
US (1) US7946509B2 (fr)
EP (1) EP2052148B1 (fr)
CN (1) CN101501324A (fr)
AT (1) ATE467758T1 (fr)
DE (2) DE102006036780A1 (fr)
WO (1) WO2008017538A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000181A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoff-Injektor
FR2941746A1 (fr) * 2009-02-02 2010-08-06 Renault Sas Dispositif d'injection de liquide, notamment de carburant, a actionneur electroactif.
FR2941745A3 (fr) * 2009-02-02 2010-08-06 Renault Sas Dispositif d'injection de liquide, notamment de carburant.
DE102009002897A1 (de) * 2009-05-07 2010-11-11 Robert Bosch Gmbh Kraftstoffinjektor
FR2947200B1 (fr) * 2009-06-25 2011-08-19 Prospection & Inventions Outil de pose d'elements de fixation a injecteur de combustible
DE102010023698A1 (de) 2010-06-14 2011-12-15 Continental Automotive Gmbh Einspritzventil mit Direkt- und Servoantrieb
DE102012005319A1 (de) * 2012-03-19 2013-09-19 L'orange Gmbh Injektorbaugruppe
US9309846B2 (en) * 2012-11-12 2016-04-12 Mcalister Technologies, Llc Motion modifiers for fuel injection systems
DK177782B1 (en) * 2013-05-29 2014-06-30 Man Diesel & Turbo Deutschland Internal combustion engine and a water-in-fuel emulsion creation and injection pump for it
DE102014209961A1 (de) * 2014-05-26 2015-11-26 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor
DE102014215774B4 (de) * 2014-08-08 2016-06-30 Continental Automotive Gmbh Vorrichtung für eine Hochdruckpumpe für ein Kraftfahrzeug
JP6674799B2 (ja) * 2015-06-05 2020-04-01 株式会社Ｓｏｋｅｎ 燃料噴射弁、及び燃料噴射弁の制御装置
JP6926693B2 (ja) * 2017-06-06 2021-08-25 株式会社Ｓｏｋｅｎ 燃料噴射装置、制御装置及び燃料噴射システム
JP7014637B2 (ja) * 2018-02-26 2022-02-01 株式会社Soken 燃料噴射装置
JP6993900B2 (ja) * 2018-02-26 2022-01-14 株式会社Soken 燃料噴射装置
CN114151255B (zh) * 2021-11-19 2023-02-14 哈尔滨工程大学 电磁阀直驱喷油-增压双作用喷油器

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8407579D0 (en) * 1984-03-23 1984-05-02 Lucas Ind Plc Fuel injection unit
DE19519191C2 (de) * 1995-05-24 1997-04-10 Siemens Ag Einspritzventil
US6915789B2 (en) * 1997-01-13 2005-07-12 Royce Walker & Co., Ltd. Fuel conditioning assembly
ATE228614T1 (de) * 1998-11-10 2002-12-15 Ganser Hydromag Brennstoffeinspritzventil für verbrennungskraftmaschinen
DE19950760A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
JP4007202B2 (ja) * 2003-01-23 2007-11-14 株式会社デンソー 軸部材の摺動構造およびインジェクタ
DE10326259A1 (de) 2003-06-11 2005-01-05 Robert Bosch Gmbh Injektor für Kraftstoff-Einspritzsysteme von Brennkraftmaschinen, insbesondere von direkteinspritzenden Dieselmotoren
DE10353045A1 (de) * 2003-11-13 2005-06-23 Siemens Ag Kraftstoffeinspritzventil
DE102004005456A1 (de) 2004-02-04 2005-08-25 Robert Bosch Gmbh Kraftstoffinjektor mit direktgesteuertem Einspritzventilglied
DE102004035313A1 (de) * 2004-07-21 2006-02-16 Robert Bosch Gmbh Kraftstoffinjektor mit zweistufigem Übersetzer

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EP2052148A1 (fr) 2009-04-29
CN101501324A (zh) 2009-08-05
DE102006036780A1 (de) 2008-02-21
US20090179086A1 (en) 2009-07-16
DE502007003775D1 (de) 2010-06-24
US7946509B2 (en) 2011-05-24
ATE467758T1 (de) 2010-05-15
WO2008017538A1 (fr) 2008-02-14

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