EP2898212B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP2898212B1
EP2898212B1 EP13739736.0A EP13739736A EP2898212B1 EP 2898212 B1 EP2898212 B1 EP 2898212B1 EP 13739736 A EP13739736 A EP 13739736A EP 2898212 B1 EP2898212 B1 EP 2898212B1
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EP
European Patent Office
Prior art keywords
actuator
stroke
nozzle needle
compensation device
nozzle
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EP13739736.0A
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German (de)
French (fr)
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EP2898212A1 (en
Inventor
Hans-Christoph Magel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2898212A1 publication Critical patent/EP2898212A1/en
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    • 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
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • F02M2200/702—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to a fuel injection valve, in particular an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. Specifically, the invention relates to the field of fuel injector injectors having a fuel rail that stores high pressure fuel and distributes it to a plurality of fuel injectors.
  • an injector with a directly driven register nozzle needle for fuel injection into an internal combustion engine is known.
  • the register nozzle needle is arranged in an axial bore of a nozzle body. In the non-activated state, the register nozzle needle closes spray holes of the nozzle body by means of a pressure spring.
  • a piezoelectric actuator arranged above the register nozzle needle is directly mechanically coupled to the register nozzle needle.
  • a deflection device with levers which are supported against the nozzle body is provided. The levers are actuated by a sleeve which is connected to the movable end of the actuator. In addition, the levers press from below against a colored plate of the register nozzle needle.
  • the from the DE 102 54 186 A1 known injector has the disadvantage that it comes due to temperature changes occurring during operation to length changes of the individual components, which do not compensate. This concerns, for example, a steel housing and a piezoelectric actuator. Furthermore, there is the disadvantage that production-related tolerances adversely affect the function, which leads to increased production costs.
  • a fuel injector with a longitudinally displaceably arranged in a housing valve needle known which closes in a closed position at least one arranged in a high-pressure chamber of the housing injection hole and in an open position releases the at least one injection hole for dispensing fuel into a combustion chamber of an internal combustion engine.
  • the valve needle is subjected to force by means of at least one compression spring in the direction of its closed position, wherein an actuator for actuating the valve needle is provided, which is connected to the valve needle via a mechanically acting coupling device.
  • the valve needle is formed in the closed position as at least almost force-balanced valve needle.
  • the actuator is designed as a magnetic actuator.
  • the magnetic actuator acts directly on the mechanically acting coupler.
  • the mechanically acting coupler includes rocker arms, one end portions of which are disposed in abutting engagement with a bottom surface of a coupler sleeve, while the other end portions of the rocker arms cooperate with the underside of the end portion of the valve needle.
  • a fuel injection valve in particular an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, in which an actuator, a nozzle needle and a mechanical translator are provided, wherein the mechanical translator translates a stroke of the actuator into a stroke of the nozzle needle, wherein a hydraulic Temperature compensation device provided and wherein, when translating the stroke of the actuator into the stroke of the nozzle needle, the actuator acts via the hydraulic temperature compensation device on the mechanical translator.
  • the hydraulic temperature compensation device is formed in the high pressure region and arranged between the actuator and the mechanical translator. As a result, the entire actuator force must be transmitted through the hydraulic temperature compensation device.
  • the from the DE102005020366 known fuel injector shows that by means of a lever mechanism of the booster piston and thus also the nozzle needle are coupled in the opposite direction with the piezoelectric actuator. Via a coupling space filled with fuel, the nozzle needle is hydraulically coupled with the booster piston.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is possible. Specifically, a temperature and / or tolerance compensation can be realized in an improved manner.
  • the hydraulic compensation device is arranged between the mechanical translator and the nozzle needle.
  • the preferably already reduced by the translation actuator power must be transmitted.
  • an advantageous ratio of, for example, two to five the transmission losses and the gap losses compared to a configuration in which the entire actuator force must be transmitted through the hydraulic device, thereby significantly reduced.
  • the compensation device between the mechanical translator and the nozzle needle is located.
  • the mechanical translator has at least one lever element
  • the compensation device has a base body, wherein when the stroke of the actuator is translated into the stroke of the nozzle needle, the at least one lever element acts on the base body.
  • the base body of the compensating device on a transmission part and a plate-shaped lifting part, acts on the at least one lever element when translating the stroke of the actuator in the stroke of the nozzle needle.
  • a stationary arranged to a housing plate is provided, wherein the transmission part of the compensation device extends through the plate.
  • the plate can create a certain spatial separation between a fuel space in which the mechanical translator is arranged and a fuel space in which the compensation device and, if appropriate, the nozzle needle are arranged.
  • the plate has a guide bore, in which the transmission part of the compensation device is axially guided.
  • the plate it is also possible for the plate to have a passage opening through which the transmission part extends with radial play. As a result, a guide on the plate can be avoided. As a result, an overdetermination can be avoided in particular.
  • a sealing sleeve is provided, which is acted upon by a spring element against a nozzle distal end of the nozzle needle side facing the plate, that within the sealing sleeve a compensation chamber of the compensation device is formed and that the nozzle-distal end of the nozzle needle and the nozzle distant End of the nozzle needle facing end face of the transmission part limit the expansion chamber.
  • a compensation chamber of the compensation device is formed and that the nozzle-distal end of the nozzle needle and the nozzle distant End of the nozzle needle facing end face of the transmission part limit the expansion chamber.
  • the mechanical translator has an actuating part, by means of which the actuator actuates the at least one lever element when translating the stroke of the actuator into the stroke of the nozzle needle, and that a prestressed rest position spring element is provided, on the one hand the actuating part of the mechanical translator and on the other hand supported on the lifting part of the base body of the compensating device.
  • the prestressed rest position spring element causes a play-free rest position of the transmission components, in particular of the actuating part of the mechanical translator, the at least one lever element of the mechanical translator and the base body of the compensating device.
  • the mechanical translator allows a fixed or variable stroke ratio of the stroke of the actuator in an x-fold stroke of the nozzle needle, wherein x is greater than one or not less than two or from a range of about two to about five.
  • x is greater than one or not less than two or from a range of about two to about five.
  • a force acting on the mechanical translator with respect to the force of the actuator can thus be reduced.
  • Loss of actuator force due to an optionally limited hydraulic stiffness of the hydraulic Compensation device can thus be reduced.
  • clearance losses in the hydraulic balancer that require refilling may be reduced due to reduced forces relative to the force of the actuator.
  • the preferred stroke ratio which can be in particular in the range of about two to about five, the transmission losses and the gap losses of the hydraulic balancer can be significantly reduced.
  • a body component which separates an actuator space in which the actuator is arranged from a fuel space in which the mechanical translator is arranged, that the body component has a through hole in which a transmission pin is guided, and that the actuator acts by means of the transmission pin on an actuating part of the mechanical translator.
  • a high-pressure-tight guide of the transmission pin can be provided in the body component, so that the actuator lies in the low-pressure region.
  • the actuator can be suitably protected against the fuel.
  • the actuator can be designed as a wet actuator in the low-pressure region or as a dry actuator by means of a corresponding seal, for example by means of a metal sleeve and membrane.
  • a biasing spring is provided for the actuator, which may be formed, for example, as the actuator surrounding pipe spring.
  • Fig. 1 shows a non-inventive fuel injection valve 1 in a schematic, partial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injector 1 is for a fuel injection system having a fuel rail that stores diesel fuel under high pressure and distributes it to a plurality of fuel injectors 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications in a correspondingly modified embodiment.
  • the fuel injection valve 1 comprises a multi-part housing 2 with a holding body 3, a nozzle body 4 and a clamping nut 5.
  • a nozzle needle 6 is arranged in the nozzle body 4.
  • the nozzle needle 6 may be axially guided in the nozzle body 4 along an axis 7 of the nozzle needle 6.
  • the nozzle needle 6 is designed as an inwardly opening nozzle needle 6.
  • an actuator chamber 8 is configured, which is relieved of pressure via a low-pressure line 9.
  • an actuator 10 is arranged, which is designed in this embodiment as a piezoelectric actuator 10.
  • the actuator 10 is supported on the one hand via an actuator base 11 on the holding body 3.
  • an actuator head 12 is attached to the actuator 10.
  • the actuator head 12 and the actuator base 11 are interconnected by a component 13. If the actuator 10 is designed as a dry actuator 10, then a seal relative to the actuator chamber 8 can be achieved in that the component 13 is designed as a sealing sleeve 13. It can also be a bias of the actuator 10 can be achieved in that the component 13 is designed as a surrounding the actuator 10 Bourdon tube 13.
  • a fuel chamber 14 is also provided, which can be filled via a high-pressure line 15 with fuel under high pressure.
  • a body component 16 of the holding body 3 separates the actuator space
  • a biasing spring is arranged for biasing the actuator 10 in a correspondingly modified embodiment between the body member 16 and the actuator head 12.
  • the body member 16 is configured in this embodiment 16 as a plate-shaped body member 16.
  • the body member 16 has a through hole 17 through which a transmission pin 18 extends.
  • the transfer pin 18 is here guided in the through hole 17, in particular guided pressure-tight.
  • a mechanical translator 19 is arranged in the fuel chamber 14.
  • the mechanical translator 19 has an actuating part 20 and lever elements 21, 22.
  • the actuator 10 acts via the transmission pin 18 on the actuating part 20 of the mechanical translator 19 a.
  • a compensation device 30 is provided, which in this embodiment has a base body 31 with a transmission part 32, a lifting part 33 and a guide part 34.
  • the compensation device 30 is located in the chain of action from the actuator 10 to the nozzle needle 6.
  • the compensation device 30 is in the chain of effects from the actuator 10 to the nozzle needle 6 between the mechanical translator 19 and the nozzle needle. 6
  • the mechanical translator 19 translates a stroke of the actuator 10 into a stroke of the nozzle needle 6.
  • the compensation device 30 is already subjected to the translated stroke.
  • the stroke of the balancing device 30 thus coincides with the stroke of the nozzle needle 6.
  • the fuel injection valve 1 also has a plate 35 which is arranged fixedly relative to the housing 2 and through which the transmission part 32 of the main body 31 of the compensation device 30 extends.
  • a through hole 36 of the plate 35, through which the transmission part 32 extends be designed as a guide bore 36, in which the transmission part 32 is axially guided.
  • the through-bore 36 can also be designed as a passage opening 36, through which the transmission part 32 extends with radial play.
  • the nozzle needle 6 can be guided axially within the nozzle body 4.
  • a further fuel chamber 37 is configured, in which the nozzle needle 6 is arranged.
  • the plate-shaped lifting part 33 of the main body 31 is located in the fuel chamber 14.
  • the guide part 34 of the main body 31 is located in the further fuel chamber 37.
  • the transmission part 32 of the main body 31 extends from the fuel chamber 14 into the further fuel chamber 37 and connects the lifting part 33 with the guide member 34.
  • the guide member 34 has a blind hole-shaped guide bore 38 in which a nozzle distal end 39 of the nozzle needle 6 is arranged.
  • the nozzle-distal end 39 of the nozzle needle 6 bounded in the blind hole-shaped guide bore 38 a compensation chamber 40 of the hydraulic balancer 30.
  • the compensation chamber 40 is filled in operation via the smallest possible leakage between the guide member 34 and the nozzle needle 6 with high pressure fuel.
  • the nozzle needle 6 may be guided in a shaft of the nozzle body 4, wherein in the guide region, a flow connection is provided. Via a nozzle closing spring 41 arranged in the fuel chamber 37, a closing of the nozzle needle 6 is made possible and a closed position predetermined. Due to the hydraulic compensation chamber 40 of the hydraulic compensation device 30 tolerances and occurring during operation, temperature expansions between the nozzle needle 6 and the actuator 10 can be compensated. In particular, different thermal length changes between the housing 2 and the actuator 10, the nozzle needle 6 and the individual components in the chain of effects between the actuator 10 and the nozzle needle 6 can be compensated for in this way.
  • the lever elements 21, 22 are on the one hand in contact with the actuating part 20 and on the other hand with the base body 31, wherein the lever elements 21, 22 are supported on the plate 35.
  • a biased rest-bearing spring element which causes a play-free rest position of the transmission components, especially the lever members 21, 22 of the base body 31 and the actuating member 20 between the actuating member 20 and the plate-shaped lifting part 33 of the base body 31.
  • the actuating member 20 for this purpose a blind hole-shaped recess which receives the rest position spring element 45 partially.
  • the transfer pin 18 is guided high pressure-tight and has a small diameter. As a result, the pressure force on the actuator 10 is kept low.
  • the actuator 10 is charged in this embodiment, whereby it expands.
  • the lever elements 21, 22 are actuated, so that in turn the main body 31 is actuated.
  • This requires a reversal of movement.
  • the pressure in the expansion chamber 40 drops and the nozzle needle 6 opens.
  • the mechanical translator 19 may be configured with a fixed or a variable Hubüber GmbH.
  • the mechanical translator 19 preferably translates the stroke of the actuator 10 into an x-fold stroke of the nozzle needle 6, where x is greater than one.
  • x is not less than two, that is greater than or equal to two.
  • x is from a range of about two to about five. Transmission losses and gap losses of the hydraulic balancing device 30 can thereby be kept low.
  • the actuator 10 is discharged in this embodiment, causing it to contract again.
  • no force is exerted on the actuating part 20, so that the lever elements 21, 22 are relieved by the operating part 20.
  • the nozzle needle 6 is then closed by the nozzle closing spring 41.
  • Fig. 2 shows an embodiment of a fuel injection valve 1 according to the invention in a schematic, excerpted sectional view.
  • the transmission part 32 is in this case guided in the guide bore 36 designed as a through hole 36.
  • the nozzle needle 6 is guided in the nozzle body 4.
  • a sealing sleeve 50 is provided in the fuel chamber 37.
  • the sealing sleeve 50 is in this case arranged at the nozzle-distal end 39 of the nozzle needle 6.
  • the sealing sleeve 50 has a sealing edge 51, with which the sealing sleeve 50 bears against the plate 35.
  • a compensation chamber 40 of the compensation device 30 is formed in this embodiment, which is enclosed by the sealing sleeve 50.
  • the sealing sleeve 50 is acted upon by the nozzle closing spring 41 against the plate 35.
  • the transmission part 32 protrudes into the inner region of the sealing sleeve 50, whereby the sealing sleeve 50 effectively separates the compensation chamber 40 in its interior from the outer part of the further fuel chamber 37.
  • the compensation chamber 40 is limited in this embodiment by the nozzle-distal end 39 of the nozzle needle 6, a nozzle-distal end 39 facing end face 52 of the transmission part 32 and the sealing sleeve 50.
  • a diameter of the transmission part 32 is smaller than a diameter of the nozzle-distal end 39 of the nozzle needle 6.
  • other embodiments are possible.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Brennstoffeinspritzventil, insbesondere einen Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen mit einer Brennstoffverteilerleiste, die unter hohem Druck stehenden Brennstoff speichert und auf mehrere Brennstoffeinspritzventile verteilt.The invention relates to a fuel injection valve, in particular an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. Specifically, the invention relates to the field of fuel injector injectors having a fuel rail that stores high pressure fuel and distributes it to a plurality of fuel injectors.

Aus der DE 102 54 186 A1 ist ein Injektor mit einer direkt angetriebenen Register-Düsennadel für die Kraftstoffeinspritzung in einen Verbrennungsmotor bekannt. Die Register-Düsennadel ist in einer axialen Bohrung eines Düsenkörpers angeordnet. Im nicht angesteuerten Zustand verschließt die Register-Düsennadel mittels einer Druckfeder Spritzlöcher des Düsenkörpers. Ein oberhalb der Register-Düsennadel angeordneter piezoelektrischer Aktor ist mit der Register-Düsennadel direkt mechanisch gekoppelt. Zwischen der nach innen öffnenden Register-Düsennadel und dem Aktor ist eine Umlenkeinrichtung mit Hebeln, die gegen den Düsenkörper abgestützt sind, vorgesehen. Die Hebel sind von einer Hülse betätigbar, die mit dem beweglichen Ende des Aktors verbunden ist. Außerdem drücken die Hebel von unten gegen eine Buntplatte der Register-Düsennadel.From the DE 102 54 186 A1 For example, an injector with a directly driven register nozzle needle for fuel injection into an internal combustion engine is known. The register nozzle needle is arranged in an axial bore of a nozzle body. In the non-activated state, the register nozzle needle closes spray holes of the nozzle body by means of a pressure spring. A piezoelectric actuator arranged above the register nozzle needle is directly mechanically coupled to the register nozzle needle. Between the inwardly opening register nozzle needle and the actuator, a deflection device with levers which are supported against the nozzle body is provided. The levers are actuated by a sleeve which is connected to the movable end of the actuator. In addition, the levers press from below against a colored plate of the register nozzle needle.

Der aus der DE 102 54 186 A1 bekannte Injektor hat den Nachteil, dass es auf Grund von im Betrieb auftretenden Temperaturänderungen zu Längenänderungen der einzelnen Komponenten kommt, welche sich nicht kompensieren. Dies betrifft beispielsweise ein aus Stahl bestehendes Gehäuse und einen piezoelektrischen Aktor. Ferner besteht der Nachteil, dass sich fertigungsbedingte Toleranzen ungünstig auf die Funktion auswirken, was zu erhöhten Herstellungskosten führt.The from the DE 102 54 186 A1 known injector has the disadvantage that it comes due to temperature changes occurring during operation to length changes of the individual components, which do not compensate. This concerns, for example, a steel housing and a piezoelectric actuator. Furthermore, there is the disadvantage that production-related tolerances adversely affect the function, which leads to increased production costs.

Denkbar ist jedoch der Ausgleich von Toleranzen und insbesondere von unterschiedlichen Temperaturdehnungen betreffend einen piezoelektrischen Aktor und ein Gehäuse des Injektors. Dies erfordert allerdings ein teures Material für das Gehäuse mit eingeschränkter Festigkeit, wodurch die Druckfestigkeit des Injektors eingeschränkt wird. Außerdem müssen dennoch hohe Fertigungstoleranzen eingehalten werden, was die Herstellung verteuert.Conceivable, however, is the compensation of tolerances and in particular of different thermal expansions relating to a piezoelectric actuator and a housing of the injector. However, this requires an expensive material for the housing with limited strength, whereby the compressive strength of the injector is limited. In addition, high manufacturing tolerances must still be met, which makes the production more expensive.

Aus der DE 10 2011 076 956 A1 ist ein Kraftstoffinjektor mit einer in einem Gehäuse längsverschiebbar angeordneten Ventilnadel bekannt, die in einer Schließstellung wenigstens ein in einem Hochdruckraum des Gehäuses angeordnetes Spritzloch verschließt und in einer Öffnungsstellung das wenigstens eine Spritzloch zum Abgeben von Kraftstoff in einen Brennraum einer Brennkraftmaschine freigibt. Hierbei ist die Ventilnadel mittels wenigstes einer Druckfeder in Richtung ihrer Schließstellung kraftbeaufschlagt, wobei ein Aktuator zur Betätigung der Ventilnadel vorgesehen ist, der mit der Ventilnadel über eine mechanisch wirkende Kopplereinrichtung verbunden ist. Die Ventilnadel ist in der Schließstellung als zumindest nahezu kraftausgeglichene Ventilnadel ausgebildet. Der Aktuator ist als Magnetaktor ausgebildet. Bei dieser Ausgestaltung wirkt der Magnetaktor direkt auf die mechanisch wirkende Kopplereinrichtung ein. Die mechanisch wirkende Kopplereinrichtung umfasst Kipphebel, deren einen Endbereiche in Anlagekontakt mit einer Unterseite eines Kopplerhuts angeordnet sind, während die anderen Endbereiche der Kipphebel mit der Unterseite des Abschlussbereichs der Ventilnadel zusammen wirken. Durch eine entsprechende geometrische Dimensionierung der einzelnen Abschnitte der Kipphebel kann eine variable Wegübersetzung der Kipphebel derart erzeugt werden, dass zum Abheben der Ventilnadel von ihrem Dichtsitz eine Bewegung einer Kopplerstange in einen zunächst geringen Hub mit relativ großer Öffnungskraft übersetzt wird, während nach dem Abheben der Ventilnadel von ihrem Dichtsitz bei dem gleichen Weg der Kopplerstange ein relativ hoher Öffnungshub bei entsprechend verringerter Öffnungskraft erzielt wird.From the DE 10 2011 076 956 A1 is a fuel injector with a longitudinally displaceably arranged in a housing valve needle known which closes in a closed position at least one arranged in a high-pressure chamber of the housing injection hole and in an open position releases the at least one injection hole for dispensing fuel into a combustion chamber of an internal combustion engine. In this case, the valve needle is subjected to force by means of at least one compression spring in the direction of its closed position, wherein an actuator for actuating the valve needle is provided, which is connected to the valve needle via a mechanically acting coupling device. The valve needle is formed in the closed position as at least almost force-balanced valve needle. The actuator is designed as a magnetic actuator. In this embodiment, the magnetic actuator acts directly on the mechanically acting coupler. The mechanically acting coupler includes rocker arms, one end portions of which are disposed in abutting engagement with a bottom surface of a coupler sleeve, while the other end portions of the rocker arms cooperate with the underside of the end portion of the valve needle. By a corresponding geometrical dimensioning of the individual sections of the rocker arms, a variable displacement of the rocker arm can be generated such that for lifting the valve needle from its sealing seat a movement of a coupler rod is translated into a first small stroke with a relatively large opening force, while after lifting the valve needle from its sealing seat in the same way the coupler bar a relatively high opening stroke is achieved with a correspondingly reduced opening force.

Ferner ist aus der DE 10 2012 211 233 A1 eine Ausgestaltung eines Brennstoffeinspritzventils, insbesondere eines Injektors für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen, bekannt, bei der ein Aktor, eine Düsennadel und ein mechanischer Übersetzer vorgesehen sind, wobei der mechanische Übersetzer einen Hub des Aktors in einen Hub der Düsennadel übersetzt, wobei eine hydraulische Temperaturausgleichseinrichtung vorgesehen ist und wobei beim Übersetzen des Hubs des Aktors in den Hub der Düsennadel der Aktor über die hydraulische Temperaturausgleichseinrichtung auf den mechanischen Übersetzer einwirkt. Bei dieser denkbaren Ausgestaltung des Brennstoffeinspritzventils ist die hydraulische Temperaturausgleichseinrichtung im Hochdruckbereich ausgebildet und zwischen dem Aktor und dem mechanischen Übersetzer angeordnet. Dadurch muss die gesamte Aktorkraft durch die hydraulische Temperaturausgleichseinrichtung übertragen werden. Anschließend wird im mechanischen Übersetzer die Kraft reduziert und der Hub erhöht. Die Übertragung der hohen Aktorkraft durch die hydraulische Temperaturausgleichseinrichtung führt wegen der geringen hydraulischen Steifigkeit zu großen Verlusten bei der Aktorkraft. Weiterhin ergeben sich durch die Übertragung großer Kräfte hohe Spaltverluste im Koppler, die eine Wiederbefüllung problematisch machen können.Furthermore, from the DE 10 2012 211 233 A1 an embodiment of a fuel injection valve, in particular an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, in which an actuator, a nozzle needle and a mechanical translator are provided, wherein the mechanical translator translates a stroke of the actuator into a stroke of the nozzle needle, wherein a hydraulic Temperature compensation device provided and wherein, when translating the stroke of the actuator into the stroke of the nozzle needle, the actuator acts via the hydraulic temperature compensation device on the mechanical translator. In this conceivable embodiment of the fuel injection valve, the hydraulic temperature compensation device is formed in the high pressure region and arranged between the actuator and the mechanical translator. As a result, the entire actuator force must be transmitted through the hydraulic temperature compensation device. Subsequently, in the mechanical translator, the force is reduced and the stroke is increased. The transmission of the high actuator force by the hydraulic temperature compensation device leads to large losses in the actuator force because of the low hydraulic stiffness. Furthermore, resulting from the transmission of large forces high gap losses in the coupler, which can make refilling problematic.

Der aus der DE102005020366 bekannte Kraftstoffinjektor zeigt, daß mittels eines Hebelmechanismus der Übersetzerkolben und damit auch die Düsennadel in entgegen gesetzter Richtung mit dem piezoelektrischen Aktor bewegungsgekoppelt sind. Über einen mit Kraftstoff gefüllten Kopplungsraum ist die Düsennadel mit dem Übersetzerkolben hydraulisch bewegungsgekoppelt.The from the DE102005020366 known fuel injector shows that by means of a lever mechanism of the booster piston and thus also the nozzle needle are coupled in the opposite direction with the piezoelectric actuator. Via a coupling space filled with fuel, the nozzle needle is hydraulically coupled with the booster piston.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine verbesserte Ausgestaltung ermöglicht ist. Speziell kann ein Temperatur- und/oder Toleranzausgleich in verbesserter Weise realisiert werden.The fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is possible. Specifically, a temperature and / or tolerance compensation can be realized in an improved manner.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in claim 1 are possible.

Dabei ist die hydraulische Ausgleichseinrichtung zwischen dem mechanischen Übersetzer und der Düsennadel angeordnet. Hierbei muss lediglich die vorzugsweise bereits durch die Übersetzung reduzierten Aktorkraft übertragen werden. Bei einer vorteilhaften Übersetzung von beispielsweise zwei bis fünf können hierdurch die Übertragungsverluste und die Spaltverluste gegenüber einer Ausgestaltung, bei der die gesamte Aktorkraft durch die hydraulische Einrichtung übertragen werden muss, deutlich verringert werden.In this case, the hydraulic compensation device is arranged between the mechanical translator and the nozzle needle. Here, only the preferably already reduced by the translation actuator power must be transmitted. With an advantageous ratio of, for example, two to five, the transmission losses and the gap losses compared to a configuration in which the entire actuator force must be transmitted through the hydraulic device, thereby significantly reduced.

Somit ist es vorteilhaft, dass in der Wirkungskette vom Aktor auf die Düsennadel die Ausgleichseinrichtung zwischen dem mechanischen Übersetzer und der Düsennadel liegt.Thus, it is advantageous that in the chain of effects from the actuator to the nozzle needle, the compensation device between the mechanical translator and the nozzle needle is located.

Weiter weist der mechanische Übersetzer zumindest ein Hebelelement auf, und die Ausgleichseinrichtung einen Grundkörper , wobei beim Übersetzen des Hubs des Aktors in den Hub der Düsennadel das zumindest eine Hebelelement auf den Grundkörper einwirkt. Dabei weist der Grundkörper der Ausgleichseinrichtung ein Übertragungsteil und ein plattenförmiges Hubteil auf, auf das beim Übersetzen des Hubs des Aktors in den Hub der Düsennadel das zumindest eine Hebelelement einwirkt. Außerdem ist eine ortsfest zu einem Gehäuse angeordnete Platte vorgesehen, wobei sich das Übertragungsteil der Ausgleichseinrichtung durch die Platte erstreckt. Die Platte kann hierbei eine gewisse räumliche Trennung zwischen einem Brennstoffraum, in dem der mechanische Übersetzer angeordnet ist, und einem Brennstoffraum, in dem die Ausgleichseinrichtung sowie gegebenenfalls die Düsennadel angeordnet sind, schaffen. Ferner weist die Platte eine Führungsbohrung aufweisen, in der das Übertragungsteil der Ausgleichseinrichtung axial geführt ist. Hierdurch ist je nach Ausgestaltung der Ausgleichseinrichtung auch eine Führung der Düsennadel realisierbar.Furthermore, the mechanical translator has at least one lever element, and the compensation device has a base body, wherein when the stroke of the actuator is translated into the stroke of the nozzle needle, the at least one lever element acts on the base body. In this case, the base body of the compensating device on a transmission part and a plate-shaped lifting part, acts on the at least one lever element when translating the stroke of the actuator in the stroke of the nozzle needle. In addition, a stationary arranged to a housing plate is provided, wherein the transmission part of the compensation device extends through the plate. In this case, the plate can create a certain spatial separation between a fuel space in which the mechanical translator is arranged and a fuel space in which the compensation device and, if appropriate, the nozzle needle are arranged. Furthermore, the plate has a guide bore, in which the transmission part of the compensation device is axially guided. As a result, depending on the design of the compensating device, it is also possible to realize a guidance of the nozzle needle.

Je nach Ausgestaltung des Brennstoffeinspritzventils ist es allerdings auch möglich, dass die Platte eine Durchgangsöffnung aufweist, durch die sich das Übertragungsteil mit radialem Spiel erstreckt. Hierdurch kann eine Führung an der Platte vermieden werden. Dadurch kann insbesondere eine Überbestimmung vermieden werden.Depending on the configuration of the fuel injection valve, however, it is also possible for the plate to have a passage opening through which the transmission part extends with radial play. As a result, a guide on the plate can be avoided. As a result, an overdetermination can be avoided in particular.

Weiter ist es vorgesehen, dass eine Dichthülse vorgesehen ist, die von einem Federelement gegen eine einem düsenfernen Ende der Düsennadel zugewandte Seite der Platte beaufschlagt ist, dass innerhalb der Dichthülse ein Ausgleichsraum der Ausgleichseinrichtung gebildet ist und dass das düsenferne Ende der Düsennadel und eine dem düsenfernen Ende der Düsennadel zugewandte Stirnseite des Übertragungsteils den Ausgleichsraum begrenzen. Bei dieser Ausgestaltung können insbesondere radiale Toleranzen zwischen den Bauteilen der hydraulischen Ausgleichseinrichtung und der Düsennadel ausgeglichen werden. Außerdem vereinfacht sich die Ausgestaltung des Übertragungsteils.It is further provided that a sealing sleeve is provided, which is acted upon by a spring element against a nozzle distal end of the nozzle needle side facing the plate, that within the sealing sleeve a compensation chamber of the compensation device is formed and that the nozzle-distal end of the nozzle needle and the nozzle distant End of the nozzle needle facing end face of the transmission part limit the expansion chamber. In this embodiment, in particular radial tolerances between the components of the hydraulic compensation device and the nozzle needle can be compensated. In addition, simplifies the design of the transmission part.

Hierbei ist es ferner von Vorteil, dass der mechanische Übersetzer ein Betätigungsteil aufweist, über das der Aktor beim Übersetzen des Hubs des Aktors in den Hub der Düsennadel das zumindest eine Hebelelement betätigt, und dass ein vorgespanntes Ruhelage-Federelement vorgesehen ist, das sich einerseits an dem Betätigungsteil des mechanischen Übersetzers und andererseits an dem Hubteil des Grundkörpers der Ausgleichseinrichtung abstützt. Dadurch kann in vorteilhafter Weise ermöglicht werden, dass das vorgespannte Ruhelage-Federelement eine spielfreie Ruhelage der Übertragungsbauteile, insbesondere des Betätigungsteils des mechanischen Übersetzers, des zumindest einen Hebelelements des mechanischen Übersetzers und des Grundkörpers der Ausgleichseinrichtung, bewirkt.In this case, it is also advantageous that the mechanical translator has an actuating part, by means of which the actuator actuates the at least one lever element when translating the stroke of the actuator into the stroke of the nozzle needle, and that a prestressed rest position spring element is provided, on the one hand the actuating part of the mechanical translator and on the other hand supported on the lifting part of the base body of the compensating device. This can be advantageously made possible that the prestressed rest position spring element causes a play-free rest position of the transmission components, in particular of the actuating part of the mechanical translator, the at least one lever element of the mechanical translator and the base body of the compensating device.

Vorteilhaft ist es auch, dass der mechanische Übersetzer eine feste oder variable Hubübersetzung des Hubs des Aktors in einen x-fachen Hub der Düsennadel ermöglicht, wobei x größer als eins oder nicht kleiner als zwei oder aus einem Bereich von etwa zwei bis etwa fünf ist. Durch die feste oder variable Hubübersetzung kann somit eine auf den mechanischen Übersetzer wirkende Kraft in Bezug auf die Kraft des Aktors reduziert werden. Verluste der Aktorkraft auf Grund einer gegebenenfalls begrenzten hydraulischen Steifigkeit der hydraulischen Ausgleichseinrichtung können somit verringert werden. Außerdem können Spaltverluste in der hydraulischen Ausgleichseinrichtung, die eine Wiederbefüllung erforderlich machen, auf Grund der in Bezug auf die Kraft des Aktors reduzierten Kräfte verringert werden. Somit können durch die bevorzugte Hubübersetzung, die insbesondere im Bereich von etwa zwei bis etwa fünf liegen kann, die Übertragungsverluste und die Spaltverluste der hydraulischen Ausgleichseinrichtung deutlich verringert werden.It is also advantageous that the mechanical translator allows a fixed or variable stroke ratio of the stroke of the actuator in an x-fold stroke of the nozzle needle, wherein x is greater than one or not less than two or from a range of about two to about five. As a result of the fixed or variable stroke ratio, a force acting on the mechanical translator with respect to the force of the actuator can thus be reduced. Loss of actuator force due to an optionally limited hydraulic stiffness of the hydraulic Compensation device can thus be reduced. In addition, clearance losses in the hydraulic balancer that require refilling may be reduced due to reduced forces relative to the force of the actuator. Thus, by the preferred stroke ratio, which can be in particular in the range of about two to about five, the transmission losses and the gap losses of the hydraulic balancer can be significantly reduced.

Außerdem ist es vorteilhaft, dass ein Körperbauteil vorgesehen ist, das einen Aktorraum, in dem der Aktor angeordnet ist, von einem Brennstoffraum, in dem der mechanische Übersetzer angeordnet ist, trennt, dass das Körperbauteil eine Durchgangsbohrung aufweist, in der ein Übertragungsstift geführt ist, und dass der Aktor mittels des Übertragungsstiftes auf ein Betätigungsteil des mechanischen Übersetzers einwirkt. Speziell kann hierbei eine hochdruckdichte Führung des Übertragungsstiftes in dem Körperbauteil vorgesehen sein, so dass der Aktor im Niederdruckbereich liegt. Der Aktor kann gegenüber dem Brennstoff geeignet geschützt werden. Hierbei kann der Aktor als nasser Aktor im Niederdruckbereich oder als trockner Aktor durch eine entsprechende Abdichtung, beispielsweise mittels Metallhülse und Membran, ausgebildet sein. In vorteilhafter Weise ist ein Vorspannfeder für den Aktor vorgesehen, die zum Beispiel als den Aktor umgebende Rohrfeder ausgebildet sein kann.Moreover, it is advantageous that a body component is provided, which separates an actuator space in which the actuator is arranged from a fuel space in which the mechanical translator is arranged, that the body component has a through hole in which a transmission pin is guided, and that the actuator acts by means of the transmission pin on an actuating part of the mechanical translator. In particular, a high-pressure-tight guide of the transmission pin can be provided in the body component, so that the actuator lies in the low-pressure region. The actuator can be suitably protected against the fuel. In this case, the actuator can be designed as a wet actuator in the low-pressure region or as a dry actuator by means of a corresponding seal, for example by means of a metal sleeve and membrane. Advantageously, a biasing spring is provided for the actuator, which may be formed, for example, as the actuator surrounding pipe spring.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 ein nicht erfindungsgemäßes Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung und
  • Fig. 2 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with identical reference numerals. It shows:
  • Fig. 1 a non-inventive fuel injection valve in a partial, schematic sectional view and
  • Fig. 2 a fuel injection valve in a partial, schematic sectional view according to an embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein nicht erfindungsgemäßes Brennstoffeinspritzventils 1 in einer schematischen, auszugsweisen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste, die Dieselbrennstoff unter hohem Druck speichert und auf mehrere Brennstoffeinspritzventile 1 verteilt. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich in einer entsprechend abgewandelten Ausgestaltung jedoch auch für andere Anwendungsfälle. Fig. 1 shows a non-inventive fuel injection valve 1 in a schematic, partial sectional view. The fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the fuel injector 1 is for a fuel injection system having a fuel rail that stores diesel fuel under high pressure and distributes it to a plurality of fuel injectors 1. However, the fuel injection valve 1 according to the invention is also suitable for other applications in a correspondingly modified embodiment.

Das Brennstoffeinspritzventil 1 umfasst ein mehrteiliges Gehäuse 2 mit einem Haltekörper 3, einem Düsenkörper 4 und einer Spannmutter 5. In dem Düsenkörper 4 ist eine Düsennadel 6 angeordnet. Je nach Ausgestaltung des Brennstoffeinspritzventils 1 kann die Düsennadel 6 in dem Düsenkörper 4 entlang einer Achse 7 der Düsennadel 6 axial geführt sein. Die Düsennadel 6 ist als nach innen öffnende Düsennadel 6 ausgeführt.The fuel injection valve 1 comprises a multi-part housing 2 with a holding body 3, a nozzle body 4 and a clamping nut 5. In the nozzle body 4, a nozzle needle 6 is arranged. Depending on the configuration of the fuel injection valve 1, the nozzle needle 6 may be axially guided in the nozzle body 4 along an axis 7 of the nozzle needle 6. The nozzle needle 6 is designed as an inwardly opening nozzle needle 6.

Innerhalb des Haltekörpers 3 ist ein Aktorraum 8 ausgestaltet, der über eine Niederdruckleitung 9 druckentlastet ist. In dem Aktorraum 8 ist ein Aktor 10 angeordnet, der in diesem Ausführungsbeispiel als piezoelektrischer Aktor 10 ausgestaltet ist. Der Aktor 10 stützt sich einerseits über einen Aktorfuß 11 an dem Haltekörper 3 ab. Andererseits ist an den Aktor 10 ein Aktorkopf 12 angefügt. In diesem Ausführungsbeispiel sind der Aktorkopf 12 und der Aktorfuß 11 durch ein Bauteil 13 miteinander verbunden. Wenn der Aktor 10 als trockener Aktor 10 ausgeführt ist, dann kann eine Abdichtung gegenüber dem Aktorraum 8 dadurch erreicht werden, dass das Bauteil 13 als Dichthülse 13 ausgeführt ist. Es kann auch eine Vorspannung des Aktors 10 dadurch erreicht werden, dass das Bauteil 13 als eine den Aktor 10 umgebende Rohrfeder 13 ausgestaltet ist.Within the holding body 3, an actuator chamber 8 is configured, which is relieved of pressure via a low-pressure line 9. In the actuator chamber 8, an actuator 10 is arranged, which is designed in this embodiment as a piezoelectric actuator 10. The actuator 10 is supported on the one hand via an actuator base 11 on the holding body 3. On the other hand, an actuator head 12 is attached to the actuator 10. In this embodiment, the actuator head 12 and the actuator base 11 are interconnected by a component 13. If the actuator 10 is designed as a dry actuator 10, then a seal relative to the actuator chamber 8 can be achieved in that the component 13 is designed as a sealing sleeve 13. It can also be a bias of the actuator 10 can be achieved in that the component 13 is designed as a surrounding the actuator 10 Bourdon tube 13.

Innerhalb des Haltekörpers 3 ist außerdem ein Brennstoffraum 14 vorgesehen, der über eine Hochdruckleitung 15 mit unter hohem Druck stehenden Brennstoff befüllbar ist. Ein Körperbauteil 16 des Haltekörpers 3 trennt den Aktorraum 8 von dem Brennstoffraum 14. Zur Vorspannung des Aktors 10 ist es beispielsweise auch denkbar, dass bei einer entsprechend abgewandelten Ausgestaltung zwischen dem Körperbauteil 16 und dem Aktorkopf 12 eine Vorspannfeder angeordnet ist.Within the holding body 3, a fuel chamber 14 is also provided, which can be filled via a high-pressure line 15 with fuel under high pressure. A body component 16 of the holding body 3 separates the actuator space For biasing the actuator 10, it is for example also conceivable that in a correspondingly modified embodiment between the body member 16 and the actuator head 12, a biasing spring is arranged.

Das Körperbauteil 16 ist in diesem Ausführungsbeispiel 16 als plattenförmiges Körperbauteil 16 ausgestaltet. Das Körperbauteil 16 weist eine Durchgangsbohrung 17 auf, durch die sich ein Übertragungsstift 18 erstreckt. Der Übertragungsstift 18 ist hierbei in der Durchgangsbohrung 17 geführt, insbesondere druckdicht geführt.The body member 16 is configured in this embodiment 16 as a plate-shaped body member 16. The body member 16 has a through hole 17 through which a transmission pin 18 extends. The transfer pin 18 is here guided in the through hole 17, in particular guided pressure-tight.

In dem Brennstoffraum 14 ist ein mechanischer Übersetzer 19 angeordnet. Der mechanische Übersetzer 19 weist ein Betätigungsteil 20 und Hebelelemente 21, 22 auf. Der Aktor 10 wirkt über den Übertragungsstift 18 auf das Betätigungsteil 20 des mechanischen Übersetzers 19 ein.In the fuel chamber 14, a mechanical translator 19 is arranged. The mechanical translator 19 has an actuating part 20 and lever elements 21, 22. The actuator 10 acts via the transmission pin 18 on the actuating part 20 of the mechanical translator 19 a.

Ferner ist eine Ausgleichseinrichtung 30 vorgesehen, die in diesem Ausführungsbeispiel einen Grundkörper 31 mit einem Übertragungsteil 32, einem Hubteil 33 und einem Führungsteil 34 aufweist. Die Ausgleichseinrichtung 30 liegt in der Wirkungskette vom Aktor 10 auf die Düsennadel 6. Hierbei liegt die Ausgleichseinrichtung 30 in der Wirkungskette vom Aktor 10 auf die Düsennadel 6 zwischen dem mechanischen Übersetzer 19 und der Düsennadel 6.Further, a compensation device 30 is provided, which in this embodiment has a base body 31 with a transmission part 32, a lifting part 33 and a guide part 34. The compensation device 30 is located in the chain of action from the actuator 10 to the nozzle needle 6. Here, the compensation device 30 is in the chain of effects from the actuator 10 to the nozzle needle 6 between the mechanical translator 19 and the nozzle needle. 6

Der mechanische Übersetzer 19 übersetzt einen Hub des Aktors 10 in einen Hub der Düsennadel 6. Hierbei wird die Ausgleichseinrichtung 30 bereits mit dem übersetzten Hub beaufschlagt. Der Hub der Ausgleichseinrichtung 30 stimmt somit mit dem Hub der Düsennadel 6 überein. Beim Übersetzen des Hubs des Aktors 10 in den Hub der Düsennadel 6 wirken die Hebelelemente 21, 22, die von dem Betätigungsteil 20 betätigt werden, auf das plattenförmige Hubteil 33 des Grundkörpers 31 der Ausgleichseinrichtung 30 ein. Hierdurch kommt es zu einem axialen Hub des Grundkörpers 31.The mechanical translator 19 translates a stroke of the actuator 10 into a stroke of the nozzle needle 6. In this case, the compensation device 30 is already subjected to the translated stroke. The stroke of the balancing device 30 thus coincides with the stroke of the nozzle needle 6. When translating the stroke of the actuator 10 into the stroke of the nozzle needle 6, the lever elements 21, 22, which are actuated by the actuating part 20, act on the plate-shaped lifting part 33 of the main body 31 of the compensating device 30. This results in an axial stroke of the main body 31st

Das Brennstoffeinspritzventil 1 weist außerdem eine ortsfest zu dem Gehäuse 2 angeordnete Platte 35 auf, durch die sich das Übertragungsteil 32 des Grundkörpers 31 der Ausgleichseinrichtung 30 erstreckt. Je nach Ausgestaltung des Brennstoffeinspritzventils 1 kann eine Durchgangsbohrung 36 der Platte 35, durch die sich das Übertragungsteil 32 erstreckt, als Führungsbohrung 36 ausgestaltet sein, in der das Übertragungsteil 32 axial geführt ist. Hierdurch kann über den Grundkörper 31 eine Führung der Düsennadel 6 erzielt werden. Allerdings kann die Durchgangsbohrung 36 auch als Durchgangsöffnung 36 ausgestaltet sein, durch die sich das Übertragungsteil 32 mit radialem Spiel erstreckt. Speziell bei dieser Ausgestaltung kann die Düsennadel 6 innerhalb des Düsenkörpers 4 axial geführt sein.The fuel injection valve 1 also has a plate 35 which is arranged fixedly relative to the housing 2 and through which the transmission part 32 of the main body 31 of the compensation device 30 extends. Depending on the configuration of the fuel injection valve 1, a through hole 36 of the plate 35, through which the transmission part 32 extends, be designed as a guide bore 36, in which the transmission part 32 is axially guided. As a result, a guidance of the nozzle needle 6 can be achieved via the main body 31. However, the through-bore 36 can also be designed as a passage opening 36, through which the transmission part 32 extends with radial play. Especially in this embodiment, the nozzle needle 6 can be guided axially within the nozzle body 4.

Innerhalb des Gehäuses 2 ist ein weiterer Brennstoffraum 37 ausgestaltet, in dem die Düsennadel 6 angeordnet ist. Das plattenförmige Hubteil 33 des Grundkörpers 31 befindet sich in dem Brennstoffraum 14. Das Führungsteil 34 des Grundkörpers 31 befindet sich in dem weiteren Brennstoffraum 37. Das Übertragungsteil 32 des Grundkörpers 31 erstreckt sich von dem Brennstoffraum 14 in den weiteren Brennstoffraum 37 und verbindet das Hubteil 33 mit dem Führungsteil 34. Das Führungsteil 34 weist eine sacklochförmige Führungsbohrung 38 auf, in der ein düsenfernes Ende 39 der Düsennadel 6 angeordnet ist. Das düsenferne Ende 39 der Düsennadel 6 begrenzt in der sacklochförmigen Führungsbohrung 38 einen Ausgleichsraum 40 der hydraulischen Ausgleichseinrichtung 30. Der Ausgleichsraum 40 wird im Betrieb über eine möglichst geringe Leckage zwischen dem Führungsteil 34 und der Düsennadel 6 mit unter hohem Druck stehenden Brennstoff gefüllt.Within the housing 2, a further fuel chamber 37 is configured, in which the nozzle needle 6 is arranged. The plate-shaped lifting part 33 of the main body 31 is located in the fuel chamber 14. The guide part 34 of the main body 31 is located in the further fuel chamber 37. The transmission part 32 of the main body 31 extends from the fuel chamber 14 into the further fuel chamber 37 and connects the lifting part 33 with the guide member 34. The guide member 34 has a blind hole-shaped guide bore 38 in which a nozzle distal end 39 of the nozzle needle 6 is arranged. The nozzle-distal end 39 of the nozzle needle 6 bounded in the blind hole-shaped guide bore 38 a compensation chamber 40 of the hydraulic balancer 30. The compensation chamber 40 is filled in operation via the smallest possible leakage between the guide member 34 and the nozzle needle 6 with high pressure fuel.

Somit kann die Düsennadel 6 in einem Schaft des Düsenkörpers 4 geführt sein, wobei im Führungsbereich eine Strömungsverbindung vorgesehen ist. Über eine im Brennstoffraum 37 angeordnete Düsenschließfeder 41 wird ein Schließen der Düsennadel 6 ermöglicht und eine geschlossene Stellung vorgegeben. Durch den hydraulischen Ausgleichsraum 40 der hydraulischen Ausgleichseinrichtung 30 können Toleranzen und im Betrieb auftretende Temperaturdehnungen zwischen der Düsennadel 6 und dem Aktor 10 ausgeglichen werden. Speziell können hierdurch unterschiedliche thermische Längenänderungen zwischen dem Gehäuse 2 und dem Aktor 10, der Düsennadel 6 sowie den einzelnen Bauteilen in der Wirkungskette zwischen dem Aktor 10 und der Düsennadel 6 ausgeglichen werden.Thus, the nozzle needle 6 may be guided in a shaft of the nozzle body 4, wherein in the guide region, a flow connection is provided. Via a nozzle closing spring 41 arranged in the fuel chamber 37, a closing of the nozzle needle 6 is made possible and a closed position predetermined. Due to the hydraulic compensation chamber 40 of the hydraulic compensation device 30 tolerances and occurring during operation, temperature expansions between the nozzle needle 6 and the actuator 10 can be compensated. In particular, different thermal length changes between the housing 2 and the actuator 10, the nozzle needle 6 and the individual components in the chain of effects between the actuator 10 and the nozzle needle 6 can be compensated for in this way.

Die Hebelelemente 21, 22 stehen einerseits in Kontakt mit dem Betätigungsteil 20 und andererseits mit dem Grundkörper 31, wobei sich die Hebelelemente 21, 22 an der Platte 35 abstützen. Zwischen dem Betätigungsteil 20 und dem plattenförmigen Hubteil 33 des Grundkörpers 31 befindet sich ein vorgespanntes Ruhelager-Federelement, das eine spielfreie Ruhelage der Übertragungsbauteile, speziell der Hebelelemente 21, 22, des Grundkörpers 31 und des Betätigungsteils 20 bewirkt. In diesem Ausführungsbeispiel weist das Betätigungsteil 20 hierfür eine sacklochförmige Ausnehmung auf, die das Ruhelage-Federelement 45 teilweise aufnimmt.The lever elements 21, 22 are on the one hand in contact with the actuating part 20 and on the other hand with the base body 31, wherein the lever elements 21, 22 are supported on the plate 35. There is a biased rest-bearing spring element, which causes a play-free rest position of the transmission components, especially the lever members 21, 22 of the base body 31 and the actuating member 20 between the actuating member 20 and the plate-shaped lifting part 33 of the base body 31. In this embodiment, the actuating member 20 for this purpose a blind hole-shaped recess which receives the rest position spring element 45 partially.

Um eine Leckage von dem Brennstoffraum 14 über die Führung des Übertragungsstiftes 18 in der Durchgangsbohrung 17 des Körperbauteils 16 in den Aktorraum 8 gering zu halten, ist der Übertragungsstift 18 hochdruckdicht geführt und weist einen kleinen Durchmesser auf. Dadurch wird auch die Druckkraft auf den Aktor 10 gering gehalten.In order to keep leakage from the fuel chamber 14 via the guide of the transfer pin 18 in the through hole 17 of the body member 16 in the actuator chamber 8 low, the transfer pin 18 is guided high pressure-tight and has a small diameter. As a result, the pressure force on the actuator 10 is kept low.

Zum Öffnen der Düsennadel 6 wird in diesem Ausführungsbeispiel der Aktor 10 geladen, wodurch sich dieser ausdehnt. Durch die Bewegung des Übertragungsstiftes 18 und des Betätigungsteils 20 werden die Hebelelemente 21, 22 betätigt, so dass wiederum der Grundkörper 31 betätigt wird. Dies bedingt eine Bewegungsumkehr. Dadurch fällt der Druck im Ausgleichsraum 40 ab und die Düsennadel 6 öffnet sich.To open the nozzle needle 6, the actuator 10 is charged in this embodiment, whereby it expands. By the movement of the transmission pin 18 and the actuating part 20, the lever elements 21, 22 are actuated, so that in turn the main body 31 is actuated. This requires a reversal of movement. As a result, the pressure in the expansion chamber 40 drops and the nozzle needle 6 opens.

Der mechanische Übersetzer 19 kann mit einer festen oder einer variablen Hubübersetzung ausgestaltet sein. Hierbei übersetzt der mechanische Übersetzer 19 den Hub des Aktors 10 vorzugsweise in einen x-fachen Hub der Düsennadel 6, wobei x größer als eins ist. Dadurch reduziert sich in Bezug auf die Kraft des Aktors 10 die Betätigungskraft auf den Grundkörper 31, während der Weg beziehungsweise Hub zunimmt. Vorzugsweise ist x nicht kleiner als zwei, das heißt größer oder gleich zwei. Bevorzugt ist x aus einem Bereich von etwa zwei bis etwa fünf. Übertragungsverluste und Spaltverluste der hydraulischen Ausgleichungseinrichtung 30 können hierdurch gering gehalten werden.The mechanical translator 19 may be configured with a fixed or a variable Hubübersetzung. In this case, the mechanical translator 19 preferably translates the stroke of the actuator 10 into an x-fold stroke of the nozzle needle 6, where x is greater than one. As a result, with respect to the force of the actuator 10, the actuating force is reduced to the main body 31 as the travel or stroke increases. Preferably, x is not less than two, that is greater than or equal to two. Preferably, x is from a range of about two to about five. Transmission losses and gap losses of the hydraulic balancing device 30 can thereby be kept low.

Zum Beenden der Einspritzung wird der Aktor 10 in diesem Ausführungsbeispiel entladen, wodurch sich dieser wieder zusammenzieht. Dadurch wird keine Kraft mehr auf das Betätigungsteil 20 ausgeübt, so dass die Hebelelemente 21, 22 seitens des Betätigungsteils 20 entlastet werden. Die Düsennadel 6 wird dann durch die Düsenschließfeder 41 geschlossen.To end the injection, the actuator 10 is discharged in this embodiment, causing it to contract again. As a result, no force is exerted on the actuating part 20, so that the lever elements 21, 22 are relieved by the operating part 20. The nozzle needle 6 is then closed by the nozzle closing spring 41.

Fig. 2 zeigt ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 in einer schematischen, auszugsweisen Schnittdarstellung. In diesem Ausführungsbeispiel weist der Grundkörper 31 der Ausgleichseinrichtung 30 das plattenförmige Hubteil 33 und das Übertragungsteil 32 auf. Das Übertragungsteil 32 ist hierbei in der als Führungsbohrung 36 ausgestalteten Durchgangsbohrung 36 geführt. Die Düsennadel 6 ist in dem Düsenkörper 4 geführt. Außerdem ist in dem Brennstoffraum 37 eine Dichthülse 50 vorgesehen. Die Dichthülse 50 ist hierbei an dem düsenfernen Ende 39 der Düsennadel 6 angeordnet. Die Dichthülse 50 weist eine Dichtkante 51 auf, mit der die Dichthülse 50 an der Platte 35 anliegt. Hierdurch ist in diesem Ausführungsbeispiel ein Ausgleichsraum 40 der Ausgleichseinrichtung 30 gebildet, der von der Dichthülse 50 umschlossen ist. Die Dichthülse 50 wird von der Düsenschließfeder 41 gegen die Platte 35 beaufschlagt. Fig. 2 shows an embodiment of a fuel injection valve 1 according to the invention in a schematic, excerpted sectional view. In this embodiment, the main body 31 of the balancer 30, the plate-shaped lifting part 33 and the transmission part 32 on. The transmission part 32 is in this case guided in the guide bore 36 designed as a through hole 36. The nozzle needle 6 is guided in the nozzle body 4. In addition, a sealing sleeve 50 is provided in the fuel chamber 37. The sealing sleeve 50 is in this case arranged at the nozzle-distal end 39 of the nozzle needle 6. The sealing sleeve 50 has a sealing edge 51, with which the sealing sleeve 50 bears against the plate 35. As a result, a compensation chamber 40 of the compensation device 30 is formed in this embodiment, which is enclosed by the sealing sleeve 50. The sealing sleeve 50 is acted upon by the nozzle closing spring 41 against the plate 35.

Das Übertragungsteil 32 ragt in diesem Ausführungsbeispiel in den Innenbereich der Dichthülse 50, wobei die Dichthülse 50 den Ausgleichsraum 40 in ihrem Inneren gewissermaßen von dem außenliegenden Teil des weiteren Brennstoffraums 37 abtrennt. Somit wird der Ausgleichsraum 40 in diesem Ausführungsbeispiel durch das düsenferne Ende 39 der Düsennadel 6, eine dem düsenfernen Ende 39 zugewandte Stirnseite 52 des Übertragungsteils 32 und der Dichthülse 50 begrenzt. In diesem Ausführungsbeispiel ist ein Durchmesser des Übertragungsteils 32 kleiner als ein Durchmesser des düsenfernen Endes 39 der Düsennadel 6. Jedoch sind auch andere Ausgestaltungen möglich.In this exemplary embodiment, the transmission part 32 protrudes into the inner region of the sealing sleeve 50, whereby the sealing sleeve 50 effectively separates the compensation chamber 40 in its interior from the outer part of the further fuel chamber 37. Thus, the compensation chamber 40 is limited in this embodiment by the nozzle-distal end 39 of the nozzle needle 6, a nozzle-distal end 39 facing end face 52 of the transmission part 32 and the sealing sleeve 50. In this embodiment, a diameter of the transmission part 32 is smaller than a diameter of the nozzle-distal end 39 of the nozzle needle 6. However, other embodiments are possible.

In diesem Ausführungsbeispiel besteht ein radialer Toleranzausgleich zwischen der Düsennadel 6 und dem Übertragungsteil 32, da die Düsennadel 6 unabhängig von dem Übertragungsteil 32 geführt ist.In this embodiment, there is a radial tolerance compensation between the nozzle needle 6 and the transmission part 32, since the nozzle needle 6 is guided independently of the transmission part 32.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (4)

  1. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, autoignition internal combustion engines, having an actuator (10), having a nozzle needle (6) and having a mechanical booster (19), wherein the mechanical booster (19) boosts a stroke of the actuator (10) into a stroke of the nozzle needle (6),
    wherein a hydraulic compensation device (30) is provided, and wherein, during the boosting of the stroke of the actuator (10) into the stroke of the nozzle needle (6), the actuator (10) acts via the mechanical booster (19) on the compensation device (30), and the mechanical booster (19) acts via the compensation device (30) on the nozzle needle (6), wherein the mechanical booster (19) has at least one lever element (21, 22), the compensation device (30) has a main body (31), and, during the boosting of the stroke of the actuator (10) into the stroke of the nozzle needle (6), the at least one lever element (21, 22) acts on the main body (31),
    wherein the main body (31) of the compensation device (30) has a transmission part (32) and a plate-like stroke part (33) which, during the boosting of the stroke of the actuator (10) into the stroke of the nozzle needle (6), acts on the at least one lever element (21, 22),
    and wherein a plate (35) which is arranged in positionally static fashion relative to a housing (2) is provided, and the transmission part (32) of the compensation device (30) extends through the plate (35), and wherein the plate (35) has a guide bore (36) in which the transmission part (32) of the compensation device (30) is guided axially,
    characterized in that
    a sealing sleeve (50) is provided which is forced by a spring element (41) against a side of the plate (35), said side facing toward an end (39), which is remote from the nozzle, of the nozzle needle (6), in that a compensation chamber (40) of the compensation device (30) is formed within the sealing sleeve (50), and in that the compensation chamber (40) is delimited by that end (39) of the nozzle needle (6) which is remote from the nozzle and by a face side (52) of the transmission part (32), said face side facing toward that end (39) of the nozzle needle (6) which is remote from the nozzle.
  2. Fuel injection valve according to Claim 1, characterized
    in that the mechanical booster (19) has an actuation part (20) by way of which the actuator (10), during the boosting of the stroke of the actuator (10) into the stroke of the nozzle needle (6), actuates the at least one lever element (21, 22), and in that a prestressed rest-position spring element (45) is provided which is supported at one side on the actuation part (20) of the mechanical booster (19) and at the other side on the stroke part (33) of the main body (31) of the compensation device (30).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the mechanical booster (19) permits fixed or variable stroke boosting of the stroke of the actuator (10) into an x-fold stroke of the nozzle needle (6), wherein x is greater than one or no less than two or lies in a range from approximately two to approximately five.
  4. Fuel injection valve according to one of Claims 1 to 3,
    characterized
    in that a body component (16) is provided which divides an actuator chamber (8), in which the actuator (10) is arranged, from a fuel chamber (14), in which the mechanical booster (19) is arranged, in that the body component (16) has a passage bore (17) in which a transmission pin (18) is guided, and in that the actuator (10) acts by way of the transmission pin (18) on an actuation part (20) of the mechanical booster (19).
EP13739736.0A 2012-09-18 2013-07-24 Fuel injection valve Active EP2898212B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012216688.2A DE102012216688A1 (en) 2012-09-18 2012-09-18 Fuel injector
PCT/EP2013/065594 WO2014044437A1 (en) 2012-09-18 2013-07-24 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP2898212A1 EP2898212A1 (en) 2015-07-29
EP2898212B1 true EP2898212B1 (en) 2016-06-08

Family

ID=48832944

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13739736.0A Active EP2898212B1 (en) 2012-09-18 2013-07-24 Fuel injection valve

Country Status (4)

Country Link
EP (1) EP2898212B1 (en)
CN (1) CN104641100B (en)
DE (1) DE102012216688A1 (en)
WO (1) WO2014044437A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014206969A1 (en) * 2014-04-10 2015-10-15 Robert Bosch Gmbh fuel injector
CN108035812B (en) * 2017-11-03 2019-11-26 中国航发北京航科发动机控制系统科技有限责任公司 It is a kind of it is adjustable away from control with changed scale temperature compensation means and method

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10254186A1 (en) 2002-11-20 2004-06-17 Siemens Ag Injector with a directly driven register nozzle needle for fuel injection into an internal combustion engine
DE10326707B3 (en) * 2003-06-11 2005-01-27 Westport Germany Gmbh Valve device and method for injecting gaseous fuel
DE102005020366A1 (en) * 2005-05-02 2006-11-09 Robert Bosch Gmbh Injector for motor vehicle internal combustion engine fuel system has nozzle with axially slidable piston connected to needle via connecting volume
DE102005024707A1 (en) * 2005-05-30 2006-12-07 Robert Bosch Gmbh fuel Injector
DE102006031567A1 (en) * 2006-07-07 2008-01-10 Siemens Ag Injection system and method for manufacturing an injection system
DE102007036571B3 (en) * 2007-08-03 2009-04-02 Continental Automotive Gmbh Injector and device with a vessel and a housing enclosing the vessel
DE102007040510A1 (en) * 2007-08-28 2009-03-05 Robert Bosch Gmbh Actuator head for piezo actuator module, has recess that does not restrict functionality of actuator head or cavity to reduce mass of actuator head as compared to solid material design
DE102011076956A1 (en) 2011-06-06 2012-12-06 Robert Bosch Gmbh Fuel injector for internal combustion engine, has valve needle arranged in housing in longitudinally displaceable manner, where valve needle closes scum hole arranged in high-pressure space of housing
KR101382282B1 (en) 2012-02-29 2014-04-08 현대자동차(주) Variable intake device of engine
DE102012211233A1 (en) 2012-06-29 2014-01-02 Robert Bosch Gmbh Fuel injection valve for fuel injection system of internal combustion engine, has actuator that affects mechanical translator over hydraulic temperature equalizing device when translating stroke of actuator into stroke of nozzle needle

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Title
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Also Published As

Publication number Publication date
CN104641100B (en) 2017-10-13
CN104641100A (en) 2015-05-20
EP2898212A1 (en) 2015-07-29
DE102012216688A1 (en) 2014-03-20
WO2014044437A1 (en) 2014-03-27

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