EP2282045B1 - Fuel injector valve - Google Patents

Fuel injector valve Download PDF

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Publication number
EP2282045B1
EP2282045B1 EP10161556A EP10161556A EP2282045B1 EP 2282045 B1 EP2282045 B1 EP 2282045B1 EP 10161556 A EP10161556 A EP 10161556A EP 10161556 A EP10161556 A EP 10161556A EP 2282045 B1 EP2282045 B1 EP 2282045B1
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EP
European Patent Office
Prior art keywords
valve
coupler
sleeve
fuel injection
closing body
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
EP10161556A
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German (de)
French (fr)
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EP2282045A1 (en
Inventor
Michael Kurz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2282045A1 publication Critical patent/EP2282045A1/en
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Publication of EP2282045B1 publication Critical patent/EP2282045B1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M47/025—Hydraulically 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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

Definitions

  • the invention relates to a fuel injection valve for fuel injection systems of internal combustion engines. Specifically, the invention relates to an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a fuel injector for direct injection of diesel fuel into an internal combustion engine is known.
  • the known fuel injection valve has a valve housing consisting of a plurality of housing parts, wherein a fuel inlet nozzle is provided.
  • a channel for the passage of fuel is formed within the valve housing, which opens into a pressure chamber, which is seen in Abspritzides below a hydraulic coupler of the fuel injection valve, provided within the valve housing. From this channel branches off at the level of Hubüber GmbHs adopted an inlet throttle, is passed through the fuel from the channel into a control chamber of the hydraulic coupler.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that a high performance, in particular a high efficiency, even at high pressures is possible. Specifically, there is the advantage that an at least largely pressure-balanced switching concept can be realized.
  • valve closing body is designed as a spherical valve closing body and / or that the valve seat surface is designed as a cone-shaped valve seat surface.
  • the valve closing body is designed as a spherical valve closing body and / or that the valve seat surface is designed as a cone-shaped valve seat surface.
  • a robust behavior against wear by particles or the like can be achieved. This is particularly advantageous in a pressure-balanced design since it is sensitive to wear.
  • a valve pin is provided which receives the valve closing body at a first end of the valve pin, that the valve pin is supported at a second end of the valve pin at least indirectly on a valve cage and that the valve sleeve is guided in the valve cage.
  • valve cage has at least one connecting bore, via which a coupler volume variable by the actuating element is connected to the valve control chamber of the coupler.
  • the actuator may be selected depending on the application.
  • the actuating field can be designed as a piezoelectric actuator or as an electromagnetic actuator.
  • valve sleeve has a guide bore, in which the guide lug is at least partially inserted, and that a guide diameter of the guide bore is at least approximately equal to a seat diameter of the sealing seat, which is formed between the valve closing body and the valve seat surface of the valve sleeve.
  • the coupler comprises a valve spring, which acts on the valve sleeve in the direction of the valve control chamber.
  • a valve spring which acts on the valve sleeve in the direction of the valve control chamber.
  • the guide lug is formed integrally with the throttle plate, wherein through the guide approach a throttle bore leads, which opens into a limited by an end face of the nozzle needle nozzle control chamber.
  • valve sleeve has a stop which is remote from the end face of the valve sleeve, and that the stop of the valve sleeve cooperates with the throttle plate to limit a slidability of the valve sleeve made possible by the guidance of the valve sleeve on the guide projection, wherein the stop the valve sleeve is formed for example by a stop surface, which faces one side of the throttle plate.
  • the displaceability of the valve sleeve can in this case be limited in the other direction by the valve cage or the like. This ensures a robust and compact design.
  • the valve pin may be supported at its second end directly on the valve cage.
  • an adjusting body is provided and that the valve pin is supported at its second end by means of the adjusting body on the valve cage.
  • the adjusting body can be formed for example by one or more shims. As a result, a precise adjustment of a valve lift of the valve closing body with respect to the valve seat surface of the valve sleeve of the coupler is possible.
  • Fig. 1 shows an embodiment of a fuel injection valve 1 in a schematic, axial 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.
  • the fuel injection valve 1 is suitable for a fuel injection system with a fuel rail 2, which stores diesel fuel under high pressure and to the several fuel injection valves can be connected.
  • the fuel-saving valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a multi-part housing 3.
  • the housing 3 comprises a holding body 4, a throttle plate 5 and a nozzle body 6, which are connected to each other in a suitable manner.
  • a high-pressure channel is guided, which is connected by means of a fuel line 8 to the fuel rail 2.
  • high-pressure fuel is conducted via the high-pressure channel 7 to a fuel chamber 9 in the nozzle body 6.
  • the fuel chamber 9 is connected via a passage opening 10, which is formed in the nozzle body 6, with a further fuel chamber 11 of the nozzle body 6.
  • a nozzle needle 12 is arranged, which is guided in this embodiment within the nozzle body 6.
  • an actuating device 13 which has a piezoelectric actuator in this embodiment.
  • the actuator 13 may also be configured as an electromagnetic actuator.
  • the actuating device 13 actuates the nozzle needle 12 by means of a coupler 14.
  • the nozzle needle 12 cooperates with a valve seat surface 15, which is formed on the nozzle body 6, to form a sealing seat. Upon actuation of the nozzle needle 12, this lifts from its seat, whereby the sealing seat is opened and fuel is sprayed from the fuel chamber 11 via nozzle openings 16.
  • the actuation of the nozzle needle 12 takes place here by means of a pressure of a fuel in a nozzle control chamber 17 which is bounded by an end face 18 of the nozzle needle 12 and separated by a control chamber sleeve 19 of the fuel chamber 9.
  • a control chamber sleeve 19 of the fuel chamber 9. opens into the nozzle control chamber 17, an inlet throttle 20, which is configured in the throttle plate 5 and branches off from the high pressure passage 7.
  • the coupler 14 has a valve cage 25, a valve sleeve 26 and a valve closing body 27.
  • the valve sleeve 26 is disposed in the valve cage 25.
  • a valve pin 28 arranged in the valve cage 25 is provided.
  • the valve closing body 27 is supported on the valve cage 25 via the valve pin 28.
  • a first end 29 of the valve pin 28 receives the valve closing body 27.
  • the valve pin 28 is supported on the valve cage 25 from.
  • the throttle plate 5 has a guide projection 31, on which the valve sleeve 26 is guided along an axis 32 of the coupler 14.
  • the valve pin 28 is also guided along the axis 32 in the valve sleeve 26.
  • the valve closing body 27 is designed as a spherical valve closing body 27.
  • the first end 29 is adapted to the configuration of the valve closing body 27.
  • the valve-closure member 27 cooperates with a valve seat 33 configured on the valve sleeve to form a sealing seat.
  • the valve seat surface 33 is designed cone-shaped.
  • the coupler 14 has a coupler sleeve 35, which is supported for example by means of a biting edge on a plate-shaped part 36 of the valve cage 25.
  • a piston portion 37 of a transition piece 38 is guided, which is attached to the actuator of the actuator 13.
  • the piston section 37, the coupler sleeve 35 and the plate-shaped part 36 of the valve cage 25 delimit a coupler space 39.
  • the coupler space 39 has a variable coupler volume which can be changed by actuation of the actuation element 13.
  • the coupler volume of the coupler space 39 communicates via connecting bores 40, 41, which are configured in the plate-shaped part 36 of the valve cage 25, with a valve control space 42 within the valve cage 25.
  • the valve sleeve 26 has an end face 43.
  • the valve control chamber 42 is configured in this embodiment as an annular valve control chamber 42.
  • the valve control chamber 42 is defined by the end face 43 of the valve sleeve 26, the valve cage 25 and the second end 30 of the valve pin 28.
  • the volume of the valve control chamber 42 depends on the instantaneous position of the valve sleeve 26 within the valve cage 25.
  • the coupler 14 has a valve spring 45, which acts on the valve sleeve 26 in the direction of the valve control chamber 42.
  • the force of the valve spring 45 is therefore directed so that it acts in the direction of a reduction of the volume of the valve control chamber 42.
  • Another spring 46 acts on the coupler sleeve 35.
  • the actuating device 13 that is to say the piezoelectric actuator 13 is charged via electrical lines 47.
  • the actuator 13 expands along the axis 32.
  • the coupler volume of the coupler space 39 is thereby reduced.
  • the pressure in the coupler chamber 39 increases.
  • an increase in pressure in the valve control chamber 42 is thus achieved, with the volume of the valve control chamber 42 also increasing in relation to the reduction of the volume of the coupler chamber 39.
  • a guide diameter d of a guide bore 48 of the valve sleeve 26, in which the guide lug 31 is guided, is at least approximately the same size as a seat diameter of the sealing seat between the valve closing body 27 and the valve seat surface 33 of the valve sleeve 26.
  • the valve assembly with respect to the seat combination of the conical valve closing body 27 and the valve seat surface 33 of the valve sleeve 26 is thus at least approximately pressure balanced.
  • the hydraulic force produced by the pressure on the surface xd 2/4 is supported on the plate-shaped part 36 of the valve cage 25 via the spherical valve closing body 27, the dome-shaped first end 29 of the valve pin 28 and the valve pin 28 itself.
  • the seat diameter d of the seal seat is equal to the guide diameter d of the guide bore 48.
  • valve spring force of the valve spring 45 which presses the valve sleeve 26 against the spherical valve closing body 27, is smaller than a hydraulic force which is generated by the pressure in the valve control chamber 42 on the end face 43 of the valve sleeve 26, moves the valve sleeve 26 from that in the Fig. 1 shown position in the direction of the throttle plate 5.
  • This opens the formed between the valve closing body 27 and the valve seat surface 33 of the valve sleeve 26 sealing seat.
  • the displacement of the valve sleeve 26 is limited by abutting a stop surface 49 which forms a stop on the valve sleeve 26 against one side 50 of the throttle plate 5.
  • the valve sleeve 26 can be adjusted so far in the direction of the throttle plate 5 until the stop surface 49 rests against the side 50 of the throttle plate 5.
  • the actuator 13 is charged again, so that the volume of the coupler chamber 39 is increased again and thus reduces the pressure in the valve control chamber 42 and the volume of the valve control chamber 42 can be reduced. Due to the excess of force on the valve sleeve 26 in this case a provision of the valve sleeve 26 takes place in the in the Fig. 1 illustrated starting position in which the sealing seat formed between the valve closing body 27 and the valve seat surface 33 of the valve sleeve 26 is closed again.
  • the force for closing is here on the one hand from the valve spring force of the valve spring 45 and the other from the hydraulic force in the coupler 14, which acts on the surface (D 2 -B 2 ) x / 4, is composed.
  • the diameter D of the valve closing body 27 is equal to the inner diameter of the valve cage 25 for guiding.
  • Fig. 2 shows a partial representation of a fuel injection valve 1 in a schematic sectional view according to a second embodiment.
  • the valve pin 28 is supported in contrast to that in the Fig. 1 illustrated first embodiment not directly on the plate-shaped part 36 of the valve cage 25 from.
  • the support of the valve pin 28 on the plate-shaped part 36 of the valve cage 25 is effected indirectly, wherein between the second end 30 of the valve pin 28 and the plate-shaped part 36, an adjusting body 60 is arranged.
  • the adjusting body 60 is formed by a shim 60 partially inserted in a recess 61 in the plate-shaped member 36.
  • adjusting body 60 By selecting the adjusting body 60 from differently configured Einstellkörpem 60, a desired valve lift when operating the coupler 14 can be specified by the actuator 13. Thus, a precise adjustment of the valve lift is possible. This allows for a manufacturing tolerances are compensated. On the other hand, a simple adaptation to different applications is possible.

Abstract

The valve (1) has a jet needle (12) actuated by an actuating device (13) e.g. piezoelectric actuator, by using a coupler (14). The coupler includes a valve sleeve (26) guided at a guide flange (31) of a throttle plate (5). The sleeve includes a conical envelope-like valve seat surface (33) combined together with a ball-like valve closing body (27) of the coupler to form a sealing seat. A front surface (43) of the sleeve limits a valve control chamber (42) of the coupler. The closing body is provided at an end (29) of a valve bolt (28) that is supported at a valve cage (25) by an adjustingbody.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen. Speziell betrifft die Erfindung einen Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a fuel injection valve for fuel injection systems of internal combustion engines. Specifically, the invention relates to an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.

Aus der DE 101 64 123 A1 ist ein Brennstoffeinspritzventil zur direkten Einspritzung von Dieselbrennstoff in eine Brennkraftmaschine bekannt. Das bekannte Brennstoffeinspritzventil weist ein aus mehreren Gehäuseteilen bestehendes Ventilgehäuse auf, wobei ein Brennstoffeinlassstutzen vorgesehen ist. Dabei ist innerhalb des Ventilgehäuses ein Kanal zur Durchleitung von Brennstoff ausgebildet, der in einen Druckraum mündet, welcher in Abspritzrichtung gesehen unterhalb eines hydraulischen Kopplers des Brennstoffeinspritzventils, innerhalb des Ventilgehäuses vorgesehen ist. Von diesem Kanal zweigt auf Höhe der Hubübersetzungseinrichtung eine Zulaufdrossel ab, über die Brennstoff aus dem Kanal in einen Steuerraum des hydraulischen Kopplers geleitet wird.From the DE 101 64 123 A1 For example, a fuel injector for direct injection of diesel fuel into an internal combustion engine is known. The known fuel injection valve has a valve housing consisting of a plurality of housing parts, wherein a fuel inlet nozzle is provided. In this case, a channel for the passage of fuel is formed within the valve housing, which opens into a pressure chamber, which is seen in Abspritzrichtung below a hydraulic coupler of the fuel injection valve, provided within the valve housing. From this channel branches off at the level of Hubübersetzungseinrichtung an inlet throttle, is passed through the fuel from the channel into a control chamber of the hydraulic coupler.

Das aus der DE 101 64 123 A1 bekannte Brennstoffeinspritzventil hat den Nachteil, dass eine Leistungsfähigkeit in Bezug auf den Einsatz bei sehr hohen Drücken begrenzt ist.That from the DE 101 64 123 A1 known fuel injector has the disadvantage that a performance in terms of use at very high pressures is limited.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine hohe Leistungsfähigkeit, insbesondere ein hoher Wirkungsgrad, auch bei hohen Drücken ermöglicht ist. Speziell besteht der Vorteil, dass ein zumindest weitgehend druckausgeglichenes Schaltkonzept realisiert werden kann.The fuel injection valve according to the invention with the features of claim 1 has the advantage that a high performance, in particular a high efficiency, even at high pressures is possible. Specifically, there is the advantage that an at least largely pressure-balanced switching concept can be realized.

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.

Vorteilhaft ist es, dass der Ventilschließkörper als kugelförmiger Ventilschließkörper ausgestaltet ist und/oder dass die Ventilsitzfläche als kegelmantelförmige Ventilsitzfläche ausgebildet ist. Speziell durch die Sitzkombination eines kugelförmigen Ventilschließkörpers mit einer kegelmantelförmigen Ventilsitzfläche kann ein robustes Verhalten gegenüber Verschleiß durch Partikel oder dergleichen erzielt werden. Dies ist speziell bei einer druckausgeglichenen Ausgestaltung von Vorteil, da diese verschleißempfindlich ist.It is advantageous that the valve closing body is designed as a spherical valve closing body and / or that the valve seat surface is designed as a cone-shaped valve seat surface. Especially by the seat combination of a spherical valve closing body with a cone-shaped valve seat surface, a robust behavior against wear by particles or the like can be achieved. This is particularly advantageous in a pressure-balanced design since it is sensitive to wear.

Vorteilhaft ist es, dass ein Ventilbolzen vorgesehen ist, der an einem ersten Ende des Ventilbolzens den Ventilschließkörper aufnimmt, dass der Ventilbolzen an einem zweiten Ende des Ventilbolzens zumindest mittelbar an einem Ventilkäfig abgestützt ist und dass die Ventilhülse in dem Ventilkäfig geführt ist. Hierdurch ist eine vorteilhafte Zentrierung der einzelnen Teile zueinander möglich, wobei der mit der Drosselplatte verbundene oder einstückig mit der Drosselplatte ausgestaltete Führungsansatz eine zuverlässige Positionierung in einem Gehäuse des Brennstoffeinspritzventils gewährleistet.It is advantageous that a valve pin is provided which receives the valve closing body at a first end of the valve pin, that the valve pin is supported at a second end of the valve pin at least indirectly on a valve cage and that the valve sleeve is guided in the valve cage. As a result, an advantageous centering of the individual parts is possible with each other, wherein the associated with the throttle plate or integrally configured with the throttle plate guide approach ensures reliable positioning in a housing of the fuel injection valve.

Vorteilhaft ist es dabei auch, dass der Ventilkäfig zumindest eine Verbindungsbohrung aufweist, über die ein von dem Betätigungselement veränderbares Kopplervolumen mit dem Ventilsteuerraum des Kopplers verbunden ist. Hierdurch ist eine kompakte Ausgestaltung möglich. Das Betätigungselement kann je nach Anwendungsfall gewählt sein. Insbesondere kann das Betätigungsfeld als piezoelektrischer Aktor oder als elektromagnetisches Betätigungselement ausgestaltet sein.It is also advantageous that the valve cage has at least one connecting bore, via which a coupler volume variable by the actuating element is connected to the valve control chamber of the coupler. As a result, a compact design is possible. The actuator may be selected depending on the application. In particular, the actuating field can be designed as a piezoelectric actuator or as an electromagnetic actuator.

Vorteilhaft ist es, dass die Ventilhülse eine Führungsbohrung aufweist, in die der Führungsansatz zumindest teilweise eingefügt ist, und dass ein Führungsdurchmesser der Führungsbohrung zumindest näherungsweise gleich einem Sitzdurchmesser des Dichtsitzes ist, der zwischen dem Ventilschließkörper und der Ventilsitzfläche der Ventilhülse gebildet ist. Hierdurch wirkt auf die Ventilhülse keine oder nur eine vernachlässigbare öffnende hydraulische Kraft. Dadurch ist eine druckausgeglichene Ausgestaltung möglich.It is advantageous that the valve sleeve has a guide bore, in which the guide lug is at least partially inserted, and that a guide diameter of the guide bore is at least approximately equal to a seat diameter of the sealing seat, which is formed between the valve closing body and the valve seat surface of the valve sleeve. As a result, no or only a negligible opening hydraulic force acts on the valve sleeve. As a result, a pressure-balanced design is possible.

In vorteilhafter Weise umfasst der Koppler eine Ventilfeder, die die Ventilhülse in Richtung auf den Ventilsteuerraum beaufschlagt. Dadurch kann zum Schließen des Dichtsitzes zwischen der Ventilsitzfläche der Ventilhülse und dem Ventilschließkörper des Kopplers ein in Schließrichtung wirkender Kraftüberschuss, der sich aus einer Ventilfederkraft der Ventilfeder und einer hydraulischen Kraft am Koppler zusammensetzt, durch die Vorgabe der Ventilfederkraft vorgegeben werden.Advantageously, the coupler comprises a valve spring, which acts on the valve sleeve in the direction of the valve control chamber. As a result, to close the sealing seat between the valve seat surface of the valve sleeve and the valve closing body of the coupler acting in the closing direction force surplus, which is composed of a valve spring force of the valve spring and a hydraulic force on the coupler, be specified by the specification of the valve spring force.

In vorteilhafter Weise ist der Führungsansatz einstückig mit der Drosselplatte ausgebildet, wobei durch den Führungsansatz eine Drosselbohrung führt, die in einen von einer Stirnfläche der Düsennadel begrenzten Düsensteuerraum mündet. Hierdurch ist eine kompakte Ausgestaltung des Kopplers und somit der Schaltanordnung zum Betätigen der Düsennadel möglich.Advantageously, the guide lug is formed integrally with the throttle plate, wherein through the guide approach a throttle bore leads, which opens into a limited by an end face of the nozzle needle nozzle control chamber. As a result, a compact configuration of the coupler and thus the switching arrangement for actuating the nozzle needle is possible.

Vorteilhaft ist es auch, dass die Ventilhülse einen Anschlag aufweist, der von der Stirnfläche der Ventilhülse abgewandt ist, und dass der Anschlag der Ventilhülse mit der Drosselplatte zum Begrenzen einer durch die Führung der Ventilhülse an dem Führungsansatz ermöglichten Verschiebbarkeit der Ventilhülse zusammenwirkt, wobei der Anschlag der Ventilhülse beispielsweise durch eine Anschlagfläche gebildet ist, die einer Seite der Drosselplatte zugewandt ist. Die Verschiebbarkeit der Ventilhülse kann hierbei in der anderen Richtung durch den Ventilkäfig oder dergleichen begrenzt sein. Hierdurch ist eine robuste und kompakte Ausgestaltung gewährleistet.It is also advantageous that the valve sleeve has a stop which is remote from the end face of the valve sleeve, and that the stop of the valve sleeve cooperates with the throttle plate to limit a slidability of the valve sleeve made possible by the guidance of the valve sleeve on the guide projection, wherein the stop the valve sleeve is formed for example by a stop surface, which faces one side of the throttle plate. The displaceability of the valve sleeve can in this case be limited in the other direction by the valve cage or the like. This ensures a robust and compact design.

Der Ventilbolzen kann an seinem zweiten Ende direkt an dem Ventilkäfig abgestützt sein. Vorteilhaft ist es allerdings auch, dass ein Einstellkörper vorgesehen ist und dass der Ventilbolzen an seinem zweiten Ende mittels des Einstellkörpers an dem Ventilkäfig abgestützt ist. Der Einstellkörper kann beispielsweise durch eine oder mehrere Einstellscheiben gebildet sein. Hierdurch ist eine präzise Einstellung eines Ventilhubs des Ventilschließkörpers in Bezug auf die Ventilsitzfläche der Ventilhülse des Kopplers möglich.The valve pin may be supported at its second end directly on the valve cage. However, it is also advantageous that an adjusting body is provided and that the valve pin is supported at its second end by means of the adjusting body on the valve cage. The adjusting body can be formed for example by one or more shims. As a result, a precise adjustment of a valve lift of the valve closing body with respect to the valve seat surface of the valve sleeve of the coupler is possible.

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 erstes Ausführungsbeispiel eines Brennstoffeinspritzventils der Erfindung in einer auszugsweisen, axialen Schnittdarstellung und
  • Fig. 2 eine auszugsweise Darstellung des in Fig. 1 dargestellten Brennstoffeinspritzventils entsprechend einem zweiten 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 first embodiment of a fuel injection valve of the invention in an excerpt, axial sectional view and
  • Fig. 2 a partial representation of the in Fig. 1 illustrated fuel injection valve according to a second embodiment of the invention.

Fig. 1 zeigt ein Ausführungsbeispiel eines Brennstoffeinspritzventils 1 in einer schematischen, axialen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Speziell eignet sich das Brennstoffeinspritzventil 1 für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste 2, die Dieselbrennstoff unter hohem Druck speichert und an die mehrere Brennstoffeinspritzventile anschließbar sind. Das erfindungsgemäße Brennstofleinspätzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows an embodiment of a fuel injection valve 1 in a schematic, axial 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. Specifically, the fuel injection valve 1 is suitable for a fuel injection system with a fuel rail 2, which stores diesel fuel under high pressure and to the several fuel injection valves can be connected. However, the fuel-saving valve 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist ein mehrteiliges Gehäuse 3 auf. In diesem Ausführungsbeispiel umfasst das Gehäuse 3 einen Haltekörper 4, eine Drosselplatte 5 und einen Düsenkörper 6, die auf geeignete Weise miteinander verbunden sind. Durch das Gehäuse 3 ist ein Hochdruckkanal geführt, der mittels einer Brennstoffleitung 8 mit der Brennstoffverteilerleiste 2 verbunden ist. Über den Hochdruckkanal 7 wird im Betrieb unter hohem Druck stehender Brennstoff zu einem Brennstoffraum 9 im Düsenkörper 6 geführt. Der Brennstoffraum 9 ist über eine Durchgangsöffnung 10, die im Düsenkörper 6 ausgebildet ist, mit einem weiteren Brennstoffraum 11 des Düsenkörpers 6 verbunden.The fuel injection valve 1 has a multi-part housing 3. In this embodiment, the housing 3 comprises a holding body 4, a throttle plate 5 and a nozzle body 6, which are connected to each other in a suitable manner. Through the housing 3, a high-pressure channel is guided, which is connected by means of a fuel line 8 to the fuel rail 2. During operation, high-pressure fuel is conducted via the high-pressure channel 7 to a fuel chamber 9 in the nozzle body 6. The fuel chamber 9 is connected via a passage opening 10, which is formed in the nozzle body 6, with a further fuel chamber 11 of the nozzle body 6.

In dem Düsenkörper 6 ist eine Düsennadel 12 angeordnet, die in diesem Ausführungsbeispiel innerhalb des Düsenkörpers 6 geführt ist. Zur Betätigung der Düsennadel 12 dient eine Betätigungseinrichtung 13, die in diesem Ausführungsbeispiel einen piezoelektrischen Aktor aufweist. Die Betätigungseinrichtung 13 kann allerdings auch als elektromagnetische Betätigungseinrichtung ausgestaltet sein. Die Betätigungseinrichtung 13 betätigt die Düsennadel 12 mittels eines Kopplers 14.In the nozzle body 6, a nozzle needle 12 is arranged, which is guided in this embodiment within the nozzle body 6. For actuating the nozzle needle 12 is an actuating device 13 which has a piezoelectric actuator in this embodiment. However, the actuator 13 may also be configured as an electromagnetic actuator. The actuating device 13 actuates the nozzle needle 12 by means of a coupler 14.

Die Düsennadel 12 wirkt mit einer Ventilsitzfläche 15, die an dem Düsenkörper 6 ausgebildet ist, zu einem Dichtsitz zusammen. Bei einer Betätigung der Düsennadel 12 hebt sich diese aus ihrem Sitz, wodurch der Dichtsitz geöffnet und Brennstoff aus dem Brennstoffraum 11 über Düsenöffnungen 16 abgespritzt wird.The nozzle needle 12 cooperates with a valve seat surface 15, which is formed on the nozzle body 6, to form a sealing seat. Upon actuation of the nozzle needle 12, this lifts from its seat, whereby the sealing seat is opened and fuel is sprayed from the fuel chamber 11 via nozzle openings 16.

Die Betätigung der Düsennadel 12 erfolgt hierbei mittels eines Drucks eines Brennstoffs in einem Düsensteuerraum 17, der von einer Stirnfläche 18 der Düsennadel 12 begrenzt und durch eine Steuerraumhülse 19 von dem Brennstoffraum 9 abgetrennt ist. Hierbei mündet in den Düsensteuerraum 17 eine Zulaufdrossel 20, die in der Drosselplatte 5 ausgestaltet ist und von dem Hochdruckkanal 7 abzweigt.The actuation of the nozzle needle 12 takes place here by means of a pressure of a fuel in a nozzle control chamber 17 which is bounded by an end face 18 of the nozzle needle 12 and separated by a control chamber sleeve 19 of the fuel chamber 9. In this case, opens into the nozzle control chamber 17, an inlet throttle 20, which is configured in the throttle plate 5 and branches off from the high pressure passage 7.

Der Koppler 14 weist einen Ventilkäfig 25, eine Ventilhülse 26 und einen Ventilschließkörper 27 auf. Die Ventilhülse 26 ist in dem Ventilkäfig 25 angeordnet. Ferner ist ein in dem Ventilkäfig 25 angeordneter Ventilbolzen 28 vorgesehen. Der Ventilschließkörper 27 ist über den Ventilbolzen 28 an dem Ventilkäfig 25 abgestützt. Hierbei nimmt ein erstes Ende 29 des Ventilbolzens 28 den Ventilschließkörper 27 auf. An einem zweiten Ende 30 des Ventilbolzens 28 stützt sich der Ventilbolzen 28 an dem Ventilkäfig 25 ab.The coupler 14 has a valve cage 25, a valve sleeve 26 and a valve closing body 27. The valve sleeve 26 is disposed in the valve cage 25. Furthermore, a valve pin 28 arranged in the valve cage 25 is provided. The valve closing body 27 is supported on the valve cage 25 via the valve pin 28. In this case, a first end 29 of the valve pin 28 receives the valve closing body 27. At a second end 30 of the valve pin 28, the valve pin 28 is supported on the valve cage 25 from.

Die Drosselplatte 5 weist einen Führungsansatz 31 auf, an dem die Ventilhülse 26 entlang einer Achse 32 des Kopplers 14 geführt ist. Der Ventilbolzen 28 ist ebenfalls entlang der Achse 32 in der Ventilhülse 26 geführt. Außerdem besteht eine Führung zwischen dem Ventilkäfig 25 und der Ventilhülse 26. Hierbei ist durch die Ventilhülse 26, die über den Führungsansatz 31 an der Achse 32 ausgerichtet ist, eine Ausrichtung des Ventilkäfigs 25 bezüglich der Achse 32 gewährleistet.The throttle plate 5 has a guide projection 31, on which the valve sleeve 26 is guided along an axis 32 of the coupler 14. The valve pin 28 is also guided along the axis 32 in the valve sleeve 26. In addition, there is a guide between the valve cage 25 and the valve sleeve 26. In this case, an orientation of the valve cage 25 with respect to the axis 32 is ensured by the valve sleeve 26 which is aligned on the guide projection 31 on the axis 32.

In diesem Ausführungsbeispiel ist der Ventilschließkörper 27 als kugelförmiger Ventilschließkörper 27 ausgestaltet. Das erste Ende 29 ist an die Ausgestaltung des Ventilschließkörpers 27 angepasst. Der Ventilschließkörper 27 wirkt mit einer an der Ventilhülse ausgestalteten Ventilsitzfläche 33 zu einem Dichtsitz zusammen. Die Ventilsitzfläche 33 ist kegelmantelförmig ausgestaltet. Durch die Sitzkombination, die aus dem kugelförmigen Ventilschließkörper 27 und der kegelmantelförmigen Ventilsitzfläche 33 gebildet ist, ist eine verschleißunempfindliche Ausgestaltung des Ventils des Kopplers 14 möglich.In this embodiment, the valve closing body 27 is designed as a spherical valve closing body 27. The first end 29 is adapted to the configuration of the valve closing body 27. The valve-closure member 27 cooperates with a valve seat 33 configured on the valve sleeve to form a sealing seat. The valve seat surface 33 is designed cone-shaped. By the seat combination, which is formed from the spherical valve closing body 27 and the cone-shaped valve seat surface 33, a wear-resistant design of the valve of the coupler 14 is possible.

Der Koppler 14 weist eine Kopplerhülse 35 auf, die sich beispielsweise mittels einer Beißkante an einem plattenförmigen Teil 36 des Ventilkäfigs 25 abstützt. In der Kopplerhülse 35 ist ein Kolbenabschnitt 37 eines Übergangsstücks 38 geführt, das an den Aktor der Betätigungseinrichtung 13 angefügt ist. Der Kolbenabschnitt 37, die Kopplerhülse 35 und der plattenförmige Teil 36 des Ventilkäfigs 25 begrenzen einen Kopplerraum 39. Hierbei weist der Kopplerraum 39 ein veränderbares Kopplervolumen auf, das über eine Betätigung des Betätigungselements 13 veränderbar ist. Das Kopplervolumen des Kopplerraums 39 steht über Verbindungsbohrungen 40, 41, die in dem plattenförmigen Teil 36 des Ventilkäfigs 25 ausgestaltet sind, mit einem Ventilsteuerraum 42 innerhalb des Ventilkäfigs 25 in Verbindung. Die Ventilhülse 26 weist eine Stirnfläche 43 auf. Der Ventilsteuerraum 42 ist in diesem Ausführungsbeispiel als ringförmiger Ventilsteuerraum 42 ausgestaltet. Hierbei ist der Ventilsteuerraum 42 durch die Stirnfläche 43 der Ventilhülse 26, den Ventilkäfig 25 und das zweite Ende 30 des Ventilbolzens 28 definiert. Das Volumen des Ventilsteuerraums 42 hängt allerdings von der momentanen Stellung der Ventilhülse 26 innerhalb des Ventilkäfigs 25 ab.The coupler 14 has a coupler sleeve 35, which is supported for example by means of a biting edge on a plate-shaped part 36 of the valve cage 25. In the coupler sleeve 35, a piston portion 37 of a transition piece 38 is guided, which is attached to the actuator of the actuator 13. The piston section 37, the coupler sleeve 35 and the plate-shaped part 36 of the valve cage 25 delimit a coupler space 39. In this case, the coupler space 39 has a variable coupler volume which can be changed by actuation of the actuation element 13. The coupler volume of the coupler space 39 communicates via connecting bores 40, 41, which are configured in the plate-shaped part 36 of the valve cage 25, with a valve control space 42 within the valve cage 25. The valve sleeve 26 has an end face 43. The valve control chamber 42 is configured in this embodiment as an annular valve control chamber 42. In this case, the valve control chamber 42 is defined by the end face 43 of the valve sleeve 26, the valve cage 25 and the second end 30 of the valve pin 28. However, the volume of the valve control chamber 42 depends on the instantaneous position of the valve sleeve 26 within the valve cage 25.

Der Koppler 14 weist eine Ventilfeder 45 auf, die die Ventilhülse 26 in Richtung auf den Ventilsteuerraum 42 beaufschlagt. Die Kraft der Ventilfeder 45 ist daher so gerichtet, dass diese in Richtung einer Verkleinerung des Volumens des Ventilsteuerraums 42 wirkt. Eine weitere Feder 46 beaufschlagt die Kopplerhülse 35.The coupler 14 has a valve spring 45, which acts on the valve sleeve 26 in the direction of the valve control chamber 42. The force of the valve spring 45 is therefore directed so that it acts in the direction of a reduction of the volume of the valve control chamber 42. Another spring 46 acts on the coupler sleeve 35.

Zum Einleiten einer Einspritzung von Brennstoff über die Düsenöffnungen 16 in den Brennraum-einer Brennkraftmaschine wird die Betätigungseinrichtung 13, das heißt der piezoelektrische Aktor 13, über elektrische Leitungen 47 geladen. Dadurch dehnt sich der Aktor 13 entlang der Achse 32 aus. Das Kopplervolumen des Kopplerraums 39 wird dadurch reduziert. Dadurch erhöht sich der Druck im Kopplerraum 39. Über die Verbindungsbohrungen 40, 41 wird somit auch eine Druckerhöhung im Ventilsteuerraum 42 erreicht, wobei sich außerdem in Bezug auf die Reduzierung des Volumens des Kopplerraums 39 das Volumen des Ventilsteuerraums 42 vergrößert.To initiate an injection of fuel via the nozzle openings 16 into the combustion chamber of an internal combustion engine, the actuating device 13, that is to say the piezoelectric actuator 13, is charged via electrical lines 47. As a result, the actuator 13 expands along the axis 32. The coupler volume of the coupler space 39 is thereby reduced. As a result, the pressure in the coupler chamber 39 increases. Via the connecting bores 40, 41, an increase in pressure in the valve control chamber 42 is thus achieved, with the volume of the valve control chamber 42 also increasing in relation to the reduction of the volume of the coupler chamber 39.

Ein Führungsdurchmesser d einer Führungsbohrung 48 der Ventilhülse 26, in der der Führungsansatz 31 geführt ist, ist zumindest näherungsweise gleich groß wie ein Sitzdurchmesser des Dichtsitzes zwischen dem Ventilschließkörper 27 und der Ventilsitzfläche 33 der Ventilhülse 26. Somit wirkt auf die Ventilhülse 26 diesbezüglich keine öffnende hydraulische Kraft. Die Ventilanordnung in Bezug auf die Sitzkombination des kegelförmigen Ventilschließkörpers 27 und der Ventilsitzfläche 33 der Ventilhülse 26 ist somit zumindest näherungsweise druckausgeglichen. Die hydraulische Kraft, die durch den Druck auf die Fläche xd2/4 entsteht, wird über den kugelförmigen Ventilschließkörper 27, das kalottenförmige erste Ende 29 des Ventilbolzens 28 und den Ventilbolzen 28 selbst an dem plattenförmigen Teil 36 des Ventilkäfigs 25 abgestützt. Hierbei ist der Sitzdurchmesser d des Dichsitzes gleich dem Führungsdurchmesser d der Führungsbohrung 48.A guide diameter d of a guide bore 48 of the valve sleeve 26, in which the guide lug 31 is guided, is at least approximately the same size as a seat diameter of the sealing seat between the valve closing body 27 and the valve seat surface 33 of the valve sleeve 26. Thus acts on the valve sleeve 26 in this respect no opening hydraulic Force. The valve assembly with respect to the seat combination of the conical valve closing body 27 and the valve seat surface 33 of the valve sleeve 26 is thus at least approximately pressure balanced. The hydraulic force produced by the pressure on the surface xd 2/4 is supported on the plate-shaped part 36 of the valve cage 25 via the spherical valve closing body 27, the dome-shaped first end 29 of the valve pin 28 and the valve pin 28 itself. Here, the seat diameter d of the seal seat is equal to the guide diameter d of the guide bore 48.

Da eine Ventilfederkraft der Ventilfeder 45, die die Ventilhülse 26 gegen den kugelförmigen Ventilschließkörper 27 drückt, kleiner ist als eine hydraulische Kraft, die durch den Druck im Ventilsteuerraum 42 auf die Stirnfläche 43 der Ventilhülse 26 erzeugt ist, verfährt die Ventilhülse 26 aus der in der Fig. 1 dargestellten Stellung in Richtung auf die Drosselplatte 5. Hierbei öffnet sich der zwischen dem Ventilschließkörper 27 und der Ventilsitzfläche 33 der Ventilhülse 26 gebildete Dichtsitz. Die Verschiebung der Ventilhülse 26 ist durch Anschlagen einer Anschlagfläche 49, die einen Anschlag an der Ventilhülse 26 bildet, gegen eine Seite 50 der Drosselplatte 5 begrenzt. Somit kann die Ventilhülse 26 so weit in Richtung auf die Drosselplatte 5 verstellt werden, bis die Anschlagfläche 49 an der Seite 50 der Drosselplatte 5 anliegt.Since a valve spring force of the valve spring 45, which presses the valve sleeve 26 against the spherical valve closing body 27, is smaller than a hydraulic force which is generated by the pressure in the valve control chamber 42 on the end face 43 of the valve sleeve 26, moves the valve sleeve 26 from that in the Fig. 1 shown position in the direction of the throttle plate 5. This opens the formed between the valve closing body 27 and the valve seat surface 33 of the valve sleeve 26 sealing seat. The displacement of the valve sleeve 26 is limited by abutting a stop surface 49 which forms a stop on the valve sleeve 26 against one side 50 of the throttle plate 5. Thus, the valve sleeve 26 can be adjusted so far in the direction of the throttle plate 5 until the stop surface 49 rests against the side 50 of the throttle plate 5.

Über den geöffneten Dichtsitz wird der Brennstoff zwischen dem Führungsansatz 31 und dem Ventilschließkörper 27 entlastet. Durch den Führungsansatz 31 führt eine Drosselbohrung 51, die in den Düsensteuerraum 17 mündet. Auf Grund des geöffneten Dichtsitzes bricht deshalb der Druck im Düsensteuerraum 17 zusammen, so dass sich die Düsennadel 12 auf Grund des an der Düsennadel 12 angreifenden hohen Drucks des Brennstoffs im Brennstoffraum 9 sowie im Brennstoffraum 11 aus ihrem Sitz hebt und Brennstoff aus dem Brennstoffraum 11 abgespritzt wird. Die beim Betätigen der Düsennadel 12 über die Drosselbohrung 51 in den Koppler 14 gelangende Steuermenge wird über Entlastungsbohrungen 52 in der Ventilhülse 26 und Entlastungsbohrungen 53 in dem Ventilkäfig 25 in einen Niederdruckraum 54 des Brennstoffeinspritzventils 1 geführt. Aus dem Niederdruckraum 54 gelangt der Brennstoff über einen gedrosselten Rücklauf 55 zu einem Tank 56 der Brennstoffeinspritzanlage.About the open sealing seat of the fuel between the guide lug 31 and the valve closing body 27 is relieved. Through the guide projection 31 performs a throttle bore 51, which opens into the nozzle control chamber 17. Due to the open sealing seat, therefore, the pressure in the nozzle control chamber 17 collapses, so that the nozzle needle 12 due to the acting on the nozzle needle 12 high pressure of Fuel in the fuel chamber 9 and in the fuel chamber 11 lifts from its seat and fuel is sprayed from the fuel chamber 11. The reaching upon actuation of the nozzle needle 12 via the throttle bore 51 in the coupler 14 control amount is performed via relief holes 52 in the valve sleeve 26 and relief holes 53 in the valve cage 25 in a low-pressure chamber 54 of the fuel injection valve 1. From the low-pressure space 54, the fuel passes through a throttled return line 55 to a tank 56 of the fuel injection system.

Zum Beenden des Einspritzvorgangs wird der Aktor 13 wieder geladen, so dass sich das Volumen des Kopplerraums 39 wieder vergrößert und somit der Druck im Ventilsteuerraum 42 verringert und das Volumen des Ventilsteuerraums 42 reduziert werden. Auf Grund des Kraftüberschusses auf die Ventilhülse 26 erfolgt hierbei eine Rückstellung der Ventilhülse 26 in die in der Fig. 1 dargestellte Ausgangslage, bei der der zwischen dem Ventilschließkörper 27 und der Ventilsitzfläche 33 der Ventilhülse 26 gebildete Dichtsitz wieder geschlossen ist. Die Kraft zum Schließen setzt sich hierbei zum einen aus der Ventilfederkraft der Ventilfeder 45 und zum anderen aus der hydraulischen Kraft im Koppler 14, die auf die Fläche (D2-B2)x /4 wirkt, zusammengesetzt ist. Hierbei ist der Durchmesser D des Ventilschließkörpers 27 gleich dem Innendurchmesser des Ventilkäfigs 25 zur Führung.To end the injection process, the actuator 13 is charged again, so that the volume of the coupler chamber 39 is increased again and thus reduces the pressure in the valve control chamber 42 and the volume of the valve control chamber 42 can be reduced. Due to the excess of force on the valve sleeve 26 in this case a provision of the valve sleeve 26 takes place in the in the Fig. 1 illustrated starting position in which the sealing seat formed between the valve closing body 27 and the valve seat surface 33 of the valve sleeve 26 is closed again. The force for closing is here on the one hand from the valve spring force of the valve spring 45 and the other from the hydraulic force in the coupler 14, which acts on the surface (D 2 -B 2 ) x / 4, is composed. Here, the diameter D of the valve closing body 27 is equal to the inner diameter of the valve cage 25 for guiding.

Der Druckaufbau im Düsensteuerraum 17 erfolgt über den Zulauf von unter hohem Druck stehenden Brennstoff über die Zulaufdrossel 20. Dadurch ist eine zuverlässige Rückstellung der Düsennadel 12 in ihrer Ausgangsstellung gewährleistet.The pressure build-up in the nozzle control chamber 17 via the inlet of high pressure fuel via the inlet throttle 20. This ensures a reliable return of the nozzle needle 12 in its initial position.

Fig. 2 zeigt eine auszugsweise Darstellung eines Brennstoffeinspritzventils 1 in einer schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel. In diesem Ausführungsbeispiel stützt sich der Ventilbolzen 28 im Unterschied zu dem in der Fig. 1 dargestellten ersten Ausführungsbeispiel nicht direkt an dem plattenförmigen Teil 36 des Ventilkäfigs 25 ab. Die Abstützung des Ventilbolzens 28 an dem plattenförmigen Teil 36 des Ventilkäfigs 25 erfolgt mittelbar, wobei zwischen dem zweiten Ende 30 des Ventilbolzens 28 und dem plattenförmigen Teil 36 ein Einstellkörper 60 angeordnet ist. In diesem Ausführungsbeispiel ist der Einstellkörper 60 durch eine Einstellscheibe 60 gebildet, die teilweise in eine Vertiefung 61 in dem plattenförmigen Teil 36 eingesetzt ist. Durch die Auswahl des Einstellkörpers 60 aus unterschiedlich ausgestalteten Einstellkörpem 60 kann ein gewünschter Ventilhub beim Betätigen des Kopplers 14 durch den Aktor 13 vorgegeben werden. Somit ist eine genaue Einstellung des Ventilhubs möglich. Hierdurch können zum einen Fertigungstoleranzen ausgeglichen werden. Zum anderen ist eine einfache Anpassung an unterschiedliche Anwendungsfälle möglich. Fig. 2 shows a partial representation of a fuel injection valve 1 in a schematic sectional view according to a second embodiment. In this embodiment, the valve pin 28 is supported in contrast to that in the Fig. 1 illustrated first embodiment not directly on the plate-shaped part 36 of the valve cage 25 from. The support of the valve pin 28 on the plate-shaped part 36 of the valve cage 25 is effected indirectly, wherein between the second end 30 of the valve pin 28 and the plate-shaped part 36, an adjusting body 60 is arranged. In this embodiment, the adjusting body 60 is formed by a shim 60 partially inserted in a recess 61 in the plate-shaped member 36. By selecting the adjusting body 60 from differently configured Einstellkörpem 60, a desired valve lift when operating the coupler 14 can be specified by the actuator 13. Thus, a precise adjustment of the valve lift is possible. This allows for a manufacturing tolerances are compensated. On the other hand, a simple adaptation to different applications is possible.

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

Claims (11)

  1. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, autoignition internal combustion engines, having an actuating device (13), having a coupler (14) and having a nozzle needle (12) which can be actuated by the actuating device (13) via the coupler (14),
    characterized
    in that the coupler (14) has a valve sleeve (26) which is guided on a guide projection (31) of a throttle plate (5), in that the valve sleeve (26) has a valve seat surface (33) which interacts with a valve closing body (27) of the coupler (14) to form a sealing seat, and in that the valve sleeve (26) has an end surface (43) which delimits a valve control chamber (42) of the coupler (14).
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the valve closing body (27) is designed as a spherical valve closing body (27) and/or in that the valve seat surface (33) is designed as a cone-surface-shaped valve seat surface (33).
  3. Fuel injection valve according to Claim 1 or 2,
    characterized
    in that a valve pin (28) is provided which, at a first end (29) of the valve pin (28), receives the valve closing body (27), in that the valve pin (28), at a second end (30) of the valve pin (28), is supported at least indirectly on a valve cage (25), and in that the valve sleeve (26) is guided in the valve cage (25).
  4. Fuel injection valve according to Claim 3,
    characterized
    in that the valve pin (28) is supported at its second end (30) on the valve cage (25) via a setting body (60).
  5. Fuel injection valve according to Claim 3 or 4,
    characterized
    in that the valve cage (25) has at least one connecting bore (40, 41) via which a coupler volume (39), which can be varied by the actuating device (13), is connected to the valve control chamber (42) of the coupler (14).
  6. Fuel injection valve according to one of Claims 1 to 5,
    characterized
    in that the valve sleeve (26) has a guide bore (48) into which the guide projection (31) is at least partially inserted, and in that a guide diameter (d) of the guide bore (48) is at least approximately identical to a seat diameter of the sealing seat formed between the valve closing body (27) and the valve seat surface (33) of the valve sleeve (26).
  7. Fuel injection valve according to one of Claims 1 to 6, characterized in that the coupler (14) has a valve spring (45) which loads the valve sleeve (26) in the direction of the valve control chamber (42).
  8. Fuel injection valve according to one of Claims 1 to 7, characterized in that the guide projection (31) is formed in one piece with the throttle plate (5).
  9. Fuel injection valve according to one of Claims 1 to 8,
    characterized
    in that a throttle bore (51) leads through the guide projection (31) and opens into a nozzle control chamber (17) which is delimited by an end surface (18) of the nozzle needle (12).
  10. Fuel injection valve according to one of Claims 1 to 9,
    characterized
    in that the valve sleeve (26) has a stop (49) which faces away from the end surface (43) of the valve sleeve (26), and in that the stop (49) of the valve sleeve (26) interacts with the throttle plate (5) so as to limit a displaceability of the valve sleeve (26) afforded by the guidance of the valve sleeve (26) on the guide projection (31).
  11. Fuel injection valve according to Claim 10,
    characterized
    in that the stop of the valve sleeve (26) is formed by a stop surface (49) which faces toward a side (50) of the throttle plate (5).
EP10161556A 2009-06-29 2010-04-30 Fuel injector valve Not-in-force EP2282045B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009027261A DE102009027261A1 (en) 2009-06-29 2009-06-29 Fuel injector

Publications (2)

Publication Number Publication Date
EP2282045A1 EP2282045A1 (en) 2011-02-09
EP2282045B1 true EP2282045B1 (en) 2012-04-25

Family

ID=42732885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10161556A Not-in-force EP2282045B1 (en) 2009-06-29 2010-04-30 Fuel injector valve

Country Status (3)

Country Link
EP (1) EP2282045B1 (en)
AT (1) ATE555302T1 (en)
DE (1) DE102009027261A1 (en)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9526522D0 (en) * 1995-12-23 1996-02-28 Lucas Ind Plc Valve arrangement
DE10118053A1 (en) * 2001-04-11 2002-10-24 Bosch Gmbh Robert Valve for controlling liquids e.g. for vehicle fuel injection system, has hydraulic chamber that transfers control piston movement to actuating piston, which is in hydraulic force equilibrium with valve element closed
DE10164123A1 (en) 2001-12-24 2003-01-30 Bosch Gmbh Robert Fuel injection device for direct injection internal combustion engine with valve device having elastic delay element between valve seat and control space at its opposite ends
EP1612403B1 (en) * 2004-06-30 2007-01-10 C.R.F. Società Consortile per Azioni Servo valve for controlling an internal combustion engine fuel injector
DE102007018042A1 (en) * 2007-04-13 2008-10-16 Robert Bosch Gmbh Fuel injector i.e. common-rail-injector, for internal combustion engine, has valve element including control rod and needle, which are hydraulically coupled with each other, where coupler area is temporarily connected with low-pressure area

Also Published As

Publication number Publication date
ATE555302T1 (en) 2012-05-15
DE102009027261A1 (en) 2010-12-30
EP2282045A1 (en) 2011-02-09

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