EP1911966B1 - Fuel injector for a combustion engine - Google Patents

Fuel injector for a combustion engine Download PDF

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Publication number
EP1911966B1
EP1911966B1 EP07114360A EP07114360A EP1911966B1 EP 1911966 B1 EP1911966 B1 EP 1911966B1 EP 07114360 A EP07114360 A EP 07114360A EP 07114360 A EP07114360 A EP 07114360A EP 1911966 B1 EP1911966 B1 EP 1911966B1
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EP
European Patent Office
Prior art keywords
nozzle needle
chamber
coupler
control
pressure
Prior art date
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Application number
EP07114360A
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German (de)
French (fr)
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EP1911966A2 (en
EP1911966A3 (en
Inventor
Hans-Christoph Magel
Dirk Vahle
Matthias Burger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1911966A2 publication Critical patent/EP1911966A2/en
Publication of EP1911966A3 publication Critical patent/EP1911966A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injector is from the EP 1 989 436 A1 the applicant known. It comprises a guide element with a flange-like base plate and a molded guide bush in which the coupler rod of a coupler piston is guided axially displaceable.
  • a control chamber to which a coupler piston is exposed with a control surface, is actuated by a control valve.
  • the coupler piston acts on the nozzle needle via a hydraulic coupler chamber.
  • the control chamber is partially connected to a low-pressure / reflux system by means of the control valve. whereby the pressure in the control chamber decreases and the pressure forces acting in the opening direction on the nozzle needle exceed the pressure force acting on the control surface of the coupler piston.
  • a fuel injector is for example off DE 101 15 215 A1
  • the coupler piston is guided in a housing.
  • the high pressure supply line for supplying the fuel with rail or system pressure in a Düsennadeldruckrsum which is exposed to the nozzle needle acting in the opening direction pressure shoulders, via a parallel to the coupler piston extending bore within the housing.
  • the object of the present invention is to provide a fuel injector in which pressure vibrations are effectively damped and which has an improved wear behavior on the coupler guide. In addition, the production cost is to be reduced.
  • the object of the invention is achieved with the characterizing features of claim 1.
  • a solid guide is provided which exhibits improved wear behavior on the coupler guide.
  • a position separation of the coupler guide is made possible by the injector body. As a result, complex processing for a double guide can be avoided.
  • the guide element is combined with the guide bush for the coupler piston with a nozzle needle with control sleeve to the nozzle needle side boundary of the coupler space.
  • the nozzle needle can be arranged without guidance on the nozzle needle-side end face of the guide element in the nozzle needle pressure chamber.
  • the control sleeve is biased by a compression spring and is pressed with an annular surface by the biasing force of the compression spring against a nozzle needle-side end face, forming between the annular surface and nozzle needle end face a sealing seat which separates the coupler space from the nozzle needle pressure chamberVorteilhaft the biasing force of the compression spring is designed so that the control sleeve stands at overpressure in the coupler space with respect to the pressure in the nozzle needle pressure chamber from the sealing seat and so a pressure and flow compensation can take place between the rooms.
  • the control sleeve also exerts a switching function, so that an additional check valve for the relaxation of the coupler space can be omitted.
  • the nozzle needle-side end face is in this case of the pointing to the nozzle needle end face of the base plate of Guides formed, so that the sealing surface is also formed on the pointing to the nozzle needle end face of the base plate.
  • the guide element expediently has an opening which connects a first annulus exposed to the nozzle needle and a second annulus exposed to the coupler piston. It is also expedient if connection channels are formed in the base plate, via which a high-pressure connection between the internal storage space and the nozzle needle pressure chamber takes place. This eliminates a separate high-pressure bore in the injector body.
  • the in FIG. 1 and 2 illustrated fuel injector has a housing with an injector body 10 and a nozzle body 11.
  • a control valve 12 with an electromagnetic actuator 13 and a valve element 14 is arranged in the injector body 10.
  • the adjusting element 13 is connected to a connection part 15, which is clamped hydraulically tight with a first clamping nut 16, with the injector body 10.
  • a guide element 20 is further arranged between the injector body 12 and the nozzle body 11, a guide element 20 is further arranged.
  • the nozzle body 11 and the guide member 20 are clamped hydraulically tight with the injector body 10 by means of another clamping nut 19.
  • an injection valve member with an axially displaceable in the nozzle body 11 guided nozzle needle 21 is arranged.
  • injection openings 22 are introduced, which is preceded by a nozzle needle seat 23 on the nozzle body 11, on which the nozzle needle 21 rests with a sealing surface.
  • the nozzle needle seat 23 is preceded by a nozzle needle pressure chamber 24 in the nozzle body 11, to which the nozzle needle 21 is exposed with an upper pressure shoulder 25 and a lower pressure shoulder 26.
  • the nozzle needle 21 further has a nozzle needle piston 27 with a kopplerraum practicalen end face 28.
  • a control sleeve 30 is guided axially biased with a compression spring 31.
  • the control sleeve 30 further comprises an annular surface 32 which is pressed by means of the biasing force of the compression spring 31 against a later explained in more detail surface and thus forms a sealing seat.
  • the nozzle needle piston 27 and the control sleeve 30 is surrounded by an annular space 29 which is hydraulically connected via a formed on the nozzle needle 21 flattening with the nozzle needle pressure chamber 24.
  • the annular space 29 and the nozzle needle pressure chamber 24 form a common hydraulic space in which rail or system pressure is present as the injection pressure.
  • a through hole 35 is formed, which forms an internal storage space 36 for the fuel.
  • the storage space 36 performs a transverse bore 37 which is provided with a connection 38 which is connected to a high pressure line of a common rail system, not shown. Via the connection 38 and the transverse bore 37, the fuel is supplied to the internal storage space 36 with the rail or system pressure applied in the common rail system.
  • a coupler rod 40 is arranged so that the coupler rod 40 is surrounded by the system pressure.
  • the coupler rod 40 includes a needle piston side coupler piston 41 and solenoid valve side, a control piston 42.
  • the coupler rod 40 is biased by a compression spring 43 in the direction of the nozzle needle 21.
  • the control piston 42 is guided in a valve piece 44, so that a control chamber 45 is formed within the valve piece 44, to which the control piston 42 is exposed with a control surface 46.
  • the valve piece 44 On the opposite side of the control chamber 45, the valve piece 44 has a valve seat for a valve ball.
  • the valve element 14 further comprises a valve piston 47, which communicates with a magnet armature 48, which in turn is actuated by the electromagnetic actuator 13.
  • the Valve element 14 separates via the valve seat the control chamber 45 from a low pressure chamber 50 in which the actuator 12 is arranged and which is connected via hydraulic channels, not shown, with the hydraulic port 18, which leads to a low pressure / return system.
  • the compression spring 43 of the coupler piston 40 is supported via an annular disc on the valve piece 44.
  • From the control chamber 45 performs a hydraulic discharge line 49 with an outlet throttle, not shown in the low pressure chamber 50 via the valve seat of the valve member 14 from the internal storage space 36 performs another hydraulic supply line 52 with an inlet throttle also not shown in the control chamber 45.
  • the outlet throttle and the inlet throttle are dimensioned so that more fuel can flow out via the drain line 49 with the outlet throttle when the valve element 14 is open than can flow via the inlet line 52 with the inlet throttle.
  • the guide element 20 comprises a flange-like base plate 61 and a guide bushing 62 formed thereon with a guide bore 63.
  • an opening 64 is formed in alignment with the guide bore 63 and leads into the guide bore 63.
  • a nozzle needle side annular space 71 and a coupler piston side annular space 72 is formed, wherein the opening 64 and the two annular spaces 71, 72 form a coupler space 70.
  • the base plate 61 is designed on the side facing the nozzle needle 21 side with an end face 65. Against the end face 65 presses the annular surface 32 of the control sleeve 30 by means of the biasing force of the compression spring 31, so that forms between the annular surface and the end face 65 of the sealing seat with which the control sleeve 30 surrounds the nozzle needle side annular space 71 and thereby the coupler space 70 to the nozzle needle pressure chamber 24th essentially hydraulically seals.
  • the biasing force of the compression spring 31 is designed so that the control sleeve 30 additionally exerts a switching function, wherein the control sleeve 30 lifts at overpressure in the coupler chamber 70 against the pressure in the nozzle needle pressure chamber 24 from the sealing seat and so a pressure and flow compensation between the coupler chamber 70 and the Nozzle needle pressure chamber 24 can take place.
  • the end face 65 can be designed as a stroke stop for the end face 28 of the nozzle needle 27 which is on the coupler-space-side.
  • the guide element 20 On the side facing the coupler rod 40, the guide element 20 has a further annular end face 66, which runs radially around the guide bushing 62.
  • a guide collar 67 is formed which serves to center the guide element 20.
  • a plurality of connecting channels 68 are guided through the base plate 61, which lead at the annular end face 66 by the guide collar 67 so that they surround the guide bush 63 radially. Via the connecting channels 68, a hydraulic connection of the internal storage space 36 with the nozzle needle pressure chamber 24 takes place.
  • a Hubeinstell Giant 75 is arranged, which is dimensioned in diameter so that the annular spaces formed on the nozzle needle piston 27 and the coupler piston 41 via the opening 64 are hydraulically connected.
  • the base plate 61 on the side of the nozzle needle side sealing surface 65 to be provided with a stop surface, while the coupler rod 40 can move freely and thus ensures a constant pressure level in the coupler chamber 70 .
  • the advantages of a Hubanschlages lie in the mutual sealing of the two annular spaces 71, 72 from each other.
  • the fuel injector operates as follows: If the electromagnetic actuator 13 of the control valve 12 is energized, the armature 48 is pulled against the actuator 13 and thus lifts the valve element 14 from the valve seat. This results in a hydraulic connection of the control chamber 45 via the connection 49 with the low-pressure chamber 50, which in turn via the hydraulic port 18 with the low-pressure return system is connected. As a result, the pressure in the control chamber 45 drops and the opening force acting in the opening direction of the nozzle needle 21 on the pressure shoulders 25, 26 exceeds the closing force acting on the control surface 46 in the control chamber 45. The nozzle needle 21 is thereby lifted from the nozzle needle seat 23 and the injectors 22 are released.
  • the fuel present in the nozzle needle pressure chamber 24 is injected at the system pressure of the common rail. If the electromagnetic actuator 13 is de-energized again, the armature 48 drops and the armature 48 presses the valve member 14 by means of a closing spring not shown in the valve seat. Thus, the control chamber 45 is decoupled again from the low pressure / return system. The control chamber 45 is now filled via the further hydraulic connection 52 again with system pressure from the internal storage space 36.
  • the coupler rod 40 moves back in the direction of the nozzle needle 21, wherein the movement is transmitted via the coupler chamber 70 to the nozzle needle 21, so that the nozzle needle 21 again is placed in the nozzle needle seat 23.
  • the control sleeve 30 exerts a switching function and lifts off with the annular surface 32 from the nozzle needle-side sealing surface 65. Over the gap between the annular surface 32 and the nozzle needle side sealing surface 65 excess leakage from the coupler chamber 70 is discharged into the nozzle needle pressure chamber 24. As a result, the injection nozzles 22 are decoupled from the system pressure at the nozzle needle pressure chamber 24 and the injection process is ended.

Abstract

The fuel injector has nozzle needle (21), a coupling rod (40), which is partly surrounded by an annular space, which forms an internal storage space (36) for the fuel. The guide element (20) has a flange-like base plate (61) with a formed guide bush (62), which is guided in the axially adjustable coupling rod with the coupling piston (41).

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Kraftstoffinjektor für eine Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injector for an internal combustion engine according to the preamble of claim 1.

Ein derartiger Kraftstoffinjektor ist aus der EP 1 989 436 A1 der Anmelderin bekannt. Er umfasst dabei ein Führungselement mit einer flanschartigen Basisplatte und einer angeformten Führungsbuchse, in der die Kopplerstange eines Kopplerkolbens axial verschieblich geführt ist.Such a fuel injector is from the EP 1 989 436 A1 the applicant known. It comprises a guide element with a flange-like base plate and a molded guide bush in which the coupler rod of a coupler piston is guided axially displaceable.

Bei hubgesteuerte Krafistoffinjeworen mit einer Düsennadel wird ein Steuerraum, dem ein Kopplerkolben mit einer Steuerfläche ausgesetzt ist, von einem Steuerventil angesteuert Der Kopplerkolben wirktüber einen hydraulischen Kopplerraum auf die Düsennadel ein- Zum Öffnen der Düsennadel wird der Steuerraum mitteildes Steuerventils mit einem Niederdruck/Rücklaufsystem verbunden, wodurch der Druck im Steuerraum sinkt und die in Öffnungsrichtung auf die Düsennadel wirkenden Druckkräfte die auf die Steuerfläche des Kopplerkolbens wirkende Druckkraft übersteigen. Ein derartiger Krafistoffinjektor ist beispielsweise aus DE 101 15 215 A1 bekannt Bei diesem Kraftstoffinjektor ist der Kopplerkolben in einem Gehäuse geführt. Die Hochdruckzuleitung zum Zuführen des Kraftstoffs mit Rail- bzw. Systemdruck in einen Düsennadeldruckrsum, dem die Düsennadel mit in Öffnungsrichtung wirkenden Druckschultern ausgesetzt ist, erfolgt über eine parallel zum Kopplerkolben verlaufende Bohrung innerhalb des Gehäuses.In stroke-controlled fuel injectors with a nozzle needle, a control chamber, to which a coupler piston is exposed with a control surface, is actuated by a control valve. The coupler piston acts on the nozzle needle via a hydraulic coupler chamber. To open the nozzle needle, the control chamber is partially connected to a low-pressure / reflux system by means of the control valve. whereby the pressure in the control chamber decreases and the pressure forces acting in the opening direction on the nozzle needle exceed the pressure force acting on the control surface of the coupler piston. Such a fuel injector is for example off DE 101 15 215 A1 In this fuel injector, the coupler piston is guided in a housing. The high pressure supply line for supplying the fuel with rail or system pressure in a Düsennadeldruckrsum, which is exposed to the nozzle needle acting in the opening direction pressure shoulders, via a parallel to the coupler piston extending bore within the housing.

Bei derartigen Kraftstoflinjektoren treten häufig hydraulische Schwingungen zwischen dem als Hochdruckspeicher ausgebildeten Common-Rail und dem Kraftstoffinjektor auf, die einen nachteiligen Einfluss auf den Einspritzverlauf, insbesondere bei Mehrfacheinspritzungen, und auf den InjektorveischleiB haben. Um diesen hydraulischen Schwingungen entgegenzuwirken, weisen neuere Kraftstoffinjektoren innerhalb des Gehäuses ein zusätzliches internes Speichervolumen auf, das auch als "Mini-Rail" bezeichnet wird. Mit diesem internen Speichervolumen werden die Druckschwingungen gedämpft. Ein derartiger Kraftstoffinjektor wurde bereits in der deutschen Patentanmeldung 10 2006 026 877.6 vorgeschlagen.With such fuel injectors, hydraulic vibrations frequently occur between the common rail designed as a high-pressure accumulator and the fuel injector, which have a disadvantageous influence on the course of the injection, in particular in the case of multiple injections, and on the injector discharge line. To counteract these hydraulic oscillations, newer fuel injectors within the housing have an additional internal storage volume, which is also referred to as "mini-rail". With this internal storage volume, the pressure oscillations attenuated. Such a fuel injector was already in the German patent application 10 2006 026 877.6 proposed.

Aufgabe der vorliegenden Erfindung ist es, einen Kraftstoffinjektor zu schaffen, bei dem Druckschwingungen effektiv gedämpft werden und der ein verbessertes Verschleißverhalten an der Kopplerführung aufweist. Darüber hinaus soll der Fertigungsaufwand reduziert werden.The object of the present invention is to provide a fuel injector in which pressure vibrations are effectively damped and which has an improved wear behavior on the coupler guide. In addition, the production cost is to be reduced.

Vorteile der ErfindungAdvantages of the invention

Die Aufgabe der Erfindung wird mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst. Durch die Führung der Kopplerstange mit dem Kopplerkolben innerhalb der Führungsbuchse wird eine massive Führung bereitgestellt, die ein verbessertes Verschleißverhalten an der Kopplerführung zeigt. Außerdem wird eine Positionstrennung der Kopplerführung vom Injektorkörper ermöglicht. Dadurch können aufwendige Bearbeitungen für eine Doppelführung vermieden werden.The object of the invention is achieved with the characterizing features of claim 1. By guiding the coupler rod with the coupler piston within the guide bushing, a solid guide is provided which exhibits improved wear behavior on the coupler guide. In addition, a position separation of the coupler guide is made possible by the injector body. As a result, complex processing for a double guide can be avoided.

Das Führungselement wird mit der Führungsbuchse für den Kopplerkolben mit einer Düsennadel mit Steuerhülse zur düsennadelseitigen Begrenzung des Kopplerraums kombiniert. Dadurch kann die Düsennadel an der düsennadelseitigen Stirnseite des Führungselements führungsfrei im Düsennadeldruckraum angeordnet werden. Die Steuerhülse ist dabei mittels einer Druckfeder vorgespannt und wird mit einer Ringfläche durch die Vorspannkraft der Druckfeder gegen eine düsennadelseitige Stirnfläche gedrückt, wobei sich zwischen Ringfläche und düsennadelseitiger Stirnfläche ein Dichtsitz ausbildet, der den Kopplerraum vom Düsenadeldruckraum trenntVorteilhaft ist die Vorspannkraft der Druckfeder dabei so ausgelegt, dass die Steuerhülse bei Überdruck im Kopplerraum gegenüber dem Druck im Düsenadeldruckraum vom Dichtsitz abhebt und so ein Druck- und Mengenausgleich zwischen den Räumen stattfinden kann. Dadurch übt die Steuerhülse zusätzlich eine Schaltfunktion aus, so dass ein zusätzliches Rückschlagventil zur Entspannung des Kopplerraums entfallen kann. Die düsenadelseitige Stirnfläche wird dabei von der zur Düsennadel weisenden Stirnfläche der Basisplatte des Führungselements gebildet, so dass die Dichtfläche ebenfalls an der zur Düsenadel weisenden Stirnfläche der Basisplatte ausgebildet ist.The guide element is combined with the guide bush for the coupler piston with a nozzle needle with control sleeve to the nozzle needle side boundary of the coupler space. As a result, the nozzle needle can be arranged without guidance on the nozzle needle-side end face of the guide element in the nozzle needle pressure chamber. The control sleeve is biased by a compression spring and is pressed with an annular surface by the biasing force of the compression spring against a nozzle needle-side end face, forming between the annular surface and nozzle needle end face a sealing seat which separates the coupler space from the nozzle needle pressure chamberVorteilhaft the biasing force of the compression spring is designed so that the control sleeve stands at overpressure in the coupler space with respect to the pressure in the nozzle needle pressure chamber from the sealing seat and so a pressure and flow compensation can take place between the rooms. As a result, the control sleeve also exerts a switching function, so that an additional check valve for the relaxation of the coupler space can be omitted. The nozzle needle-side end face is in this case of the pointing to the nozzle needle end face of the base plate of Guides formed, so that the sealing surface is also formed on the pointing to the nozzle needle end face of the base plate.

Zur Ausbildung eines Kopplerraums weist das Führungselement zweckmäßigerweise eine Öffnung auf, die einen der Düsennadel ausgesetzten ersten Ringraum und einen dem Kopplerkolben ausgesetzten zweiten Ringraum miteinander verbindet. Zweckmäßig ist es außerdem, wenn in der Basisplatte Verbindungskanäle ausgebildet sind, über die eine Hochdruckverbindung zwischen internem Speicherraum und Düsenadeldruckraum erfolgt. Dadurch entfällt eine separate Hochdruckbohrung im Injektorkörper.In order to form a coupler space, the guide element expediently has an opening which connects a first annulus exposed to the nozzle needle and a second annulus exposed to the coupler piston. It is also expedient if connection channels are formed in the base plate, via which a high-pressure connection between the internal storage space and the nozzle needle pressure chamber takes place. This eliminates a separate high-pressure bore in the injector body.

Ausführungsbeispielembodiment

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description.

Es zeigen:

Figur 1
eine Schnittdarstellung durch einen erfindungsgemäßen Kraftstoffinjektor,
Figur 2
einen düsennadelseitigen Ausschnitt X des Kraftstoffinjektors in Figur 1,
Figur 3a
eine perspektivische Darstellung des Führungselements mit Blick auf eine düsennadelseitigen Stirnfläche und
Figur 3b
eine perspektivische Darstellung des Führungselements mit Blick auf eine kopplerkolbenseitige Ringfläche.
Show it:
FIG. 1
a sectional view through a fuel injector according to the invention,
FIG. 2
a nozzle needle-side section X of the fuel injector in FIG. 1 .
FIG. 3a
a perspective view of the guide element with a view of a nozzle needle-side end face and
FIG. 3b
a perspective view of the guide member with a view of a coupler piston side annular surface.

Der in Figur 1 und 2 dargestellte Kraftstoffinjektor weist ein Gehäuse mit einem Injektorkörper 10 und einen Düsenkörper 11 auf. Im Injektorkörper 10 ist ein Steuerventil 12 mit einem elektromagnetischen Stellelement 13 und einem Ventilelement 14 angeordnet. Das Stellelement 13 ist mit einem Anschlussteil 15 verbunden, das mit einer ersten Spannmutter 16, mit dem Injektorkörper 10 hydraulisch dicht verspannt ist. Am Anschlussteil 15 sind die elektrischen Anschlüsse 17 für das magnetische Stellelement 13 und ein hydraulischer Anschluss 18, der zu einem nicht dargestellten Niederdruck/Rücklaufsystem führt, ausgebildet. Zwischen dem Injektorkörper 12 und dem Düsenkörper 11 ist weiterhin ein Führungselement 20 angeordnet. Der Düsenkörper 11 und das Führungselement 20 sind mit dem Injektorkörper 10 mittels einer weiteren Spannmutter 19 hydraulisch dicht verspannt.The in FIG. 1 and 2 illustrated fuel injector has a housing with an injector body 10 and a nozzle body 11. In the injector body 10, a control valve 12 with an electromagnetic actuator 13 and a valve element 14 is arranged. The adjusting element 13 is connected to a connection part 15, which is clamped hydraulically tight with a first clamping nut 16, with the injector body 10. At the connection part 15, the electrical connections 17 for the magnetic control element 13 and a hydraulic connection 18, which leads to a low-pressure / return system, not shown, formed. Between the injector body 12 and the nozzle body 11, a guide element 20 is further arranged. The nozzle body 11 and the guide member 20 are clamped hydraulically tight with the injector body 10 by means of another clamping nut 19.

Im Düsenkörper 11 ist ein Einspritzventilglied mit einer axial im Düsenkörper 11 verschiebbare geführten Düsennadel 21 angeordnet. An einer Kuppe des Düsenkörpers 11 sind Einspritzöffnungen 22 eingebracht, denen am Düsenkörper 11 ein Düsennadelsitz 23 vorgelagert ist, auf dem die Düsennadel 21 mit einer Dichtfläche aufliegt. Dem Düsennadelsitz 23 ist im Düsenkörper 11 ein Düsennadeldruckraum 24 vorgelagert, dem die Düsennadel 21 mit einer oberen Druckschulter 25 und einer unteren Druckschulter 26 ausgesetzt ist. Die Düsennadel 21 weist ferner einen Düsennadelkolben 27 mit einer kopplerraumseitigen Stirnfläche 28 auf. Am Düsennadelkolben 27 ist eine Steuerhülse 30 mit einer Druckfeder 31 axial vorgespannt geführt. Die Steuerhülse 30 weist ferner einer Ringfläche 32 auf, die mittels der Vorspannkraft der Druckfeder 31 gegen eine später noch näher erläuterte Fläche gedrückt wird und so einen Dichtsitz ausbildet. Der Düsennadelkolben 27 und die Steuerhülse 30 ist von einem Ringraum 29 umgeben, der über eine an der Düsennadel 21 ausgebildete Abflachung mit dem Düsennadeldruckraum 24 hydraulische verbunden ist. Dadurch bilden der Ringraum 29 und der Düsennadeldruckraum 24 einen gemeinsamen hydraulische Raum, in dem Rail- bzw. Systemdruck als Einspritzdruck vorliegt.In the nozzle body 11, an injection valve member with an axially displaceable in the nozzle body 11 guided nozzle needle 21 is arranged. At a tip of the nozzle body 11 injection openings 22 are introduced, which is preceded by a nozzle needle seat 23 on the nozzle body 11, on which the nozzle needle 21 rests with a sealing surface. The nozzle needle seat 23 is preceded by a nozzle needle pressure chamber 24 in the nozzle body 11, to which the nozzle needle 21 is exposed with an upper pressure shoulder 25 and a lower pressure shoulder 26. The nozzle needle 21 further has a nozzle needle piston 27 with a kopplerraumseitigen end face 28. At the nozzle needle piston 27, a control sleeve 30 is guided axially biased with a compression spring 31. The control sleeve 30 further comprises an annular surface 32 which is pressed by means of the biasing force of the compression spring 31 against a later explained in more detail surface and thus forms a sealing seat. The nozzle needle piston 27 and the control sleeve 30 is surrounded by an annular space 29 which is hydraulically connected via a formed on the nozzle needle 21 flattening with the nozzle needle pressure chamber 24. As a result, the annular space 29 and the nozzle needle pressure chamber 24 form a common hydraulic space in which rail or system pressure is present as the injection pressure.

Im Injektorkörper 10 ist eine Durchgangsbohrung 35 eingebracht, die einen internen Speicherraum 36 für den Kraftstoff ausbildet. In den Speicherraum 36 führt ein Querbohrung 37, die mit einem Anschluss 38 versehen ist, der an eine Hochdruckleitung eines nicht dargestellten Common-Rail-Systems angeschlossen ist. Über den Anschluss 38 und die Querbohrung 37 wird dem internen Speicheraum 36 der Kraftstoff mit dem im Common-Rail-System anliegenden Rail- bzw. Systemdruck zugeführt. Innerhalb des Speicherraums 36 ist eine Kopplerstange 40 angeordnet, so dass die Kopplerstange 40 vom Systemdruck umgeben ist. Die Kopplerstange 40 umfasst düsennadelseitig einen Kopplerkolben 41 und magnetventilseitig einen Steuerkolben 42. Die Kopplerstange 40 ist mittels einer Druckfeder 43 in Richtung der Düsennadel 21 vorgespannt.In the injector body 10, a through hole 35 is formed, which forms an internal storage space 36 for the fuel. In the storage space 36 performs a transverse bore 37 which is provided with a connection 38 which is connected to a high pressure line of a common rail system, not shown. Via the connection 38 and the transverse bore 37, the fuel is supplied to the internal storage space 36 with the rail or system pressure applied in the common rail system. Within the storage space 36, a coupler rod 40 is arranged so that the coupler rod 40 is surrounded by the system pressure. The coupler rod 40 includes a needle piston side coupler piston 41 and solenoid valve side, a control piston 42. The coupler rod 40 is biased by a compression spring 43 in the direction of the nozzle needle 21.

Der Steuerkolben 42 ist in einem Ventilstück 44 geführt, so dass sich innerhalb des Ventilstücks 44 ein Steuerraum 45 ausbildet, dem der Steuerkolben 42 mit einer Steuerfläche 46 ausgesetzt ist. An der gegenüberliegenden Seite des Steuerraums 45 weist das Ventilstück 44 einen Ventilsitz für eine Ventilkugel auf. Das Ventilelement 14 umfasst weiterhin einen Ventilkolben 47, der mit einem Magnetanker 48 in Verbindung steht, der wiederum vom elektromagnetischen Stellelement 13 betätigt wird. Das Ventilelement 14 trennt über den Ventilsitz den Steuerraum 45 von einem Niederdruckraum 50, in dem das Stellelement 12 angeordnet ist und der über nicht näher dargestellte hydraulische Kanäle mit dem hydraulischen Anschluss 18 verbunden ist, der in ein Niederdruck/Rücklaufsystem führt. Die Druckfeder 43 des Kopplerkolbens 40 stützt sich über eine Ringscheibe am Ventilstück 44 ab.The control piston 42 is guided in a valve piece 44, so that a control chamber 45 is formed within the valve piece 44, to which the control piston 42 is exposed with a control surface 46. On the opposite side of the control chamber 45, the valve piece 44 has a valve seat for a valve ball. The valve element 14 further comprises a valve piston 47, which communicates with a magnet armature 48, which in turn is actuated by the electromagnetic actuator 13. The Valve element 14 separates via the valve seat the control chamber 45 from a low pressure chamber 50 in which the actuator 12 is arranged and which is connected via hydraulic channels, not shown, with the hydraulic port 18, which leads to a low pressure / return system. The compression spring 43 of the coupler piston 40 is supported via an annular disc on the valve piece 44.

Vom Steuerraum 45 führt eine hydraulische Ablaufleitung 49 mit einer nicht näher dargestellten Ablaufdrossel über den Ventilsitz des Ventilelements 14 in den Niederdruckraum 50. Vom internen Speicherraum 36 führt eine weitere hydraulische Zulaufleitung 52 mit einer ebenfalls nicht näher dargestellten Zulaufdrossel in den Steuerraum 45. Die Ablaufdrossel und die Zulaufdrossel sind so dimensioniert, dass über die Ablaufleitung 49 mit der Ablaufdrossel bei geöffnetem Ventilelement 14 mehr Kraftstoff abfließen kann als über die Zulaufleitung 52 mit der Zulaufdrossel zufließen kann.From the control chamber 45 performs a hydraulic discharge line 49 with an outlet throttle, not shown in the low pressure chamber 50 via the valve seat of the valve member 14 from the internal storage space 36 performs another hydraulic supply line 52 with an inlet throttle also not shown in the control chamber 45. The outlet throttle and the inlet throttle are dimensioned so that more fuel can flow out via the drain line 49 with the outlet throttle when the valve element 14 is open than can flow via the inlet line 52 with the inlet throttle.

Das Führungselement 20 umfasst eine flanschartige Basisplatte 61 und eine daran angeformte Führungsbuchse 62 mit einer Führungsbohrung 63. In der Basisplatte 61 ist fluchtend zur Führungsbohrung 63, eine Öffnung 64 ausgebildet, die in die Führungsbohrung 63 führt. An der Öffnung 64 ist ein düsennadelseitiger Ringraum 71 und ein kopplerkolbenseitiger Ringraum 72 ausgebildet, wobei die Öffnung 64 und die beiden Ringräume 71, 72 einen Kopplerraum 70 ausbilden.The guide element 20 comprises a flange-like base plate 61 and a guide bushing 62 formed thereon with a guide bore 63. In the base plate 61, an opening 64 is formed in alignment with the guide bore 63 and leads into the guide bore 63. At the opening 64, a nozzle needle side annular space 71 and a coupler piston side annular space 72 is formed, wherein the opening 64 and the two annular spaces 71, 72 form a coupler space 70.

Die Basisplatte 61 ist an der zur Düsennadel 21 weisenden Seite mit einer Stirnfläche 65 ausgeführt. Gegen die Stirnfläche 65 drückt die Ringfläche 32 der Steuerhülse 30 mittels der Vorspannkraft der Druckfeder 31, so dass sich zwischen der Ringfläche und der Stirnfläche 65 der Dichtsitz ausbildet, mit der die Steuerhülse 30 den düsennadelseitigen Ringraum 71 umgibt und dadurch den Kopplerraum 70 zum Düsennadeldruckraum 24 hin im Wesentlichen hydraulisch abdichtet. Die Vorspannkraft der Druckfeder 31 ist dabei so ausgelegt, dass die Steuerhülse 30 zusätzlich eine Schaltfunktion ausübt, wobei die Steuerhülse 30 bei Überdruck im Kopplerraum 70 gegenüber dem Druck im Düsenadeldruckraum 24 vom Dichtsitz abhebt und so ein Druck- und Mengenausgleich zwischen dem Kopplerraum 70 und dem Düsenadeldruckraum 24 stattfinden kann.The base plate 61 is designed on the side facing the nozzle needle 21 side with an end face 65. Against the end face 65 presses the annular surface 32 of the control sleeve 30 by means of the biasing force of the compression spring 31, so that forms between the annular surface and the end face 65 of the sealing seat with which the control sleeve 30 surrounds the nozzle needle side annular space 71 and thereby the coupler space 70 to the nozzle needle pressure chamber 24th essentially hydraulically seals. The biasing force of the compression spring 31 is designed so that the control sleeve 30 additionally exerts a switching function, wherein the control sleeve 30 lifts at overpressure in the coupler chamber 70 against the pressure in the nozzle needle pressure chamber 24 from the sealing seat and so a pressure and flow compensation between the coupler chamber 70 and the Nozzle needle pressure chamber 24 can take place.

Gleichzeitig kann die Stirnfläche 65 als Hubanschlag für die die kopplerraumseitige Stirnfläche 28 der Düsennadel 27 ausgebildet sein. An der zur Kopplerstange 40 weisenden Seite weist das Führungselement 20 eine weitere ringförmige Stirnfläche 66 auf, die radial um die Führungsbuchse 62 verläuft. An der weiteren ringförmigen Stirnfläche 66 ist gemäß Figur 3b ein Führungsbund 67 ausgebildet, der zum Zentrieren des Führungselements 20 dient. Radial um die Öffnung 64 sind mehrere Verbindungskanäle 68 durch die Basisplatte 61 geführt, die an der ringförmigen Stirnfläche 66 durch den Führungsbund 67 führen, so dass sie die Führungsbuchse 63 radial umgeben. Über die Verbindungskanäle 68 erfolgt eine hydraulische Verbindung des internen Speicherraums 36 mit dem Düsennadeldruckraum 24.At the same time, the end face 65 can be designed as a stroke stop for the end face 28 of the nozzle needle 27 which is on the coupler-space-side. On the side facing the coupler rod 40, the guide element 20 has a further annular end face 66, which runs radially around the guide bushing 62. At the other annular end surface 66 is according to FIG. 3b a guide collar 67 is formed which serves to center the guide element 20. Radially around the opening 64 a plurality of connecting channels 68 are guided through the base plate 61, which lead at the annular end face 66 by the guide collar 67 so that they surround the guide bush 63 radially. Via the connecting channels 68, a hydraulic connection of the internal storage space 36 with the nozzle needle pressure chamber 24 takes place.

Im Kopplerraum 70 ist gemäß Figur 2 beispielsweise ein Hubeinstellstück 75 angeordnet, das im Durchmesser so dimensioniert ist, dass die am Düsennadelkolben 27 und am Kopplerkolben 41 ausgebildeten Ringräume über die Öffnung 64 hydraulisch verbunden sind. Zur Begrenzung der Einspritzmenge ist es aber genauso denkbar, anstelle des Hubeinstellstücks 72 die Basisplatte 61 an der Seite der düsennadelseitigen Dichtfläche 65 mit einer Anschlagfläche zu versehen, während die Kopplerstange 40 sich weiter frei bewegen kann und somit für ein gleich bleibendes Druckniveau im Kopplerraum 70 sorgt. Die Vorteile eines Hubanschlages liegen im gegenseitigen Abdichten der beiden Ringräume 71, 72 voneinander. Dadurch wird die Leckage über die Führung zwischen Düsennadelkolben 27 und Steuerhülse 30 vermindert. Eine selbständige Schließbewegung der Düsennadel 21 während der Phase des Hubanschlages durch einen schleichenden Druckausgleich zwischen dem Kopplerraum 70 mit den Druckräumen 24, 35 wird somit außerdem ausgeschlossen.In the coupler space 70 is according to FIG. 2 For example, a Hubeinstellstück 75 is arranged, which is dimensioned in diameter so that the annular spaces formed on the nozzle needle piston 27 and the coupler piston 41 via the opening 64 are hydraulically connected. To limit the injection quantity, it is just as conceivable, instead of Hubeinstellstücks 72, the base plate 61 on the side of the nozzle needle side sealing surface 65 to be provided with a stop surface, while the coupler rod 40 can move freely and thus ensures a constant pressure level in the coupler chamber 70 , The advantages of a Hubanschlages lie in the mutual sealing of the two annular spaces 71, 72 from each other. As a result, the leakage is reduced via the guide between the nozzle needle piston 27 and the control sleeve 30. An independent closing movement of the nozzle needle 21 during the phase of Hubanschlages by a creeping pressure equalization between the coupler chamber 70 with the pressure chambers 24, 35 is thus also excluded.

Während der Öffnungsbewegung von Kopplerstange 40 und Düsenadel 21 gelangt über die Führung 63 und über die Führung zwischen Düsenadel 21 und der Steuerhülse 30 Kraftstoff aus dem Hochdruckräumen 36 bzw. aus dem Düsennadeldruckraum 24 in den Kopplerraum 70.During the opening movement of Kopplerstange 40 and nozzle needle 21 passes through the guide 63 and via the guide between the nozzle needle 21 and the control sleeve 30 fuel from the high-pressure chambers 36 and from the nozzle needle pressure chamber 24 in the coupler 70th

Der Kraftstoffinjektor arbeitet folgendermaßen: Wird das elektromagnetische Stellelement 13 des Steuerventils 12 bestromt, wird der Magnetanker 48 gegen das Stellelement 13 gezogen und hebt somit das Ventilelement 14 vom Ventilsitz ab. Dadurch entsteht eine hydraulische Verbindung des Steuerraums 45 über die Verbindung 49 mit dem Niederdruckraum 50, der wiederum über den hydraulischen Anschluss 18 mit dem Niederdruck-Rücklaufsystem verbunden ist. Dadurch fällt der Druck im Steuerraum 45 ab und die in Öffnungsrichtung der Düsennadel 21 an den Druckschultern 25, 26 wirkende Öffnungskraft übersteigen die im Steuerraum 45 auf die Steuerfläche 46 wirkende Schließkraft. Die Düsennadel 21 wird dadurch aus dem Düsennadelsitz 23 gehoben und die Einspritzdüsen 22 werden freigegeben. Dadurch wird der im Düsennadeldruckraum 24 anliegende Kraftstoff mit dem Systemdruck des Common-Rails eingespritzt. Wird das elektromagnetische Stellelement 13 wieder stromlos geschaltet, fällt der Magnetanker 48 ab und der Magnetanker 48 drückt mittels einer nicht näher dargestellten Schließfeder das Ventilelement 14 in den Ventilsitz. Damit ist der Steuerraum 45 wieder vom Niederdruck/Rücklaufsystem entkoppelt. Der Steuerraum 45 wird nun über die weitere hydraulische Verbindung 52 wieder mit Systemdruck aus dem internen Speicherraum 36 befüllt. Bedingt durch die Vorspannkräfte der Druckfeder 43 und dem Druckausgleich zwischen dem Steuerraum 45 und dem Kopplerraum 70 bewegt sich die Kopplerstange 40 wieder in Richtung der Düsennadel 21, wobei die Bewegung über den Kopplerraum 70 auf die Düsennadel 21 übertragen wird, so dass die Düsennadel 21 wieder in den Düsennadelsitz 23 gestellt wird. In der Schließphase übt die Steuerhülse 30 eine Schaltfunktion aus und hebt dabei mit der Ringfläche 32 von der düsenadelseitiger Dichtfläche 65 ab. Über den Spalt zwischen der Ringfläche 32 und der düsenadelseitiger Dichtfläche 65 wird überschüssige Leckage aus dem Kopplerraum 70 in den Düsenadeldruckraum 24 abgelassen. Dadurch sind die Einspritzdüsen 22 vom Systemdruck am Düsennadeldruckraum 24 entkoppelt und der Einspritzvorgang ist beendet.The fuel injector operates as follows: If the electromagnetic actuator 13 of the control valve 12 is energized, the armature 48 is pulled against the actuator 13 and thus lifts the valve element 14 from the valve seat. This results in a hydraulic connection of the control chamber 45 via the connection 49 with the low-pressure chamber 50, which in turn via the hydraulic port 18 with the low-pressure return system is connected. As a result, the pressure in the control chamber 45 drops and the opening force acting in the opening direction of the nozzle needle 21 on the pressure shoulders 25, 26 exceeds the closing force acting on the control surface 46 in the control chamber 45. The nozzle needle 21 is thereby lifted from the nozzle needle seat 23 and the injectors 22 are released. As a result, the fuel present in the nozzle needle pressure chamber 24 is injected at the system pressure of the common rail. If the electromagnetic actuator 13 is de-energized again, the armature 48 drops and the armature 48 presses the valve member 14 by means of a closing spring not shown in the valve seat. Thus, the control chamber 45 is decoupled again from the low pressure / return system. The control chamber 45 is now filled via the further hydraulic connection 52 again with system pressure from the internal storage space 36. Due to the biasing forces of the compression spring 43 and the pressure balance between the control chamber 45 and the coupler chamber 70, the coupler rod 40 moves back in the direction of the nozzle needle 21, wherein the movement is transmitted via the coupler chamber 70 to the nozzle needle 21, so that the nozzle needle 21 again is placed in the nozzle needle seat 23. In the closing phase, the control sleeve 30 exerts a switching function and lifts off with the annular surface 32 from the nozzle needle-side sealing surface 65. Over the gap between the annular surface 32 and the nozzle needle side sealing surface 65 excess leakage from the coupler chamber 70 is discharged into the nozzle needle pressure chamber 24. As a result, the injection nozzles 22 are decoupled from the system pressure at the nozzle needle pressure chamber 24 and the injection process is ended.

Claims (10)

  1. Fuel injector for an internal combustion engine, having a nozzle needle (21), having a coupler rod (40) which is at least partially surrounded by an annular chamber which forms an internal storage chamber (36) for the fuel, and having a control valve (12), wherein the coupler rod (40) has a coupler piston (41) at the nozzle needle side and has a control piston (42) at the control valve side, wherein the coupler piston (41) is guided axially in a guide element (20), wherein the control piston (42) is exposed to a control chamber (45), which control chamber (45) can be connected, in a manner controlled by the control valve (12), to a low-pressure/return system and in this way the nozzle needle (21) is lifted from a nozzle needle seat (23) and fuel is injected from a nozzle needle pressure chamber (24) which is charged with injection pressure, and wherein the guide element (20) has a flange-like base plate (61) with an integrally formed guide bush (62) in which the coupler rod (40) is axially movably guided via the coupler piston (41),
    characterized
    in that an axially movably guided control sleeve (30) is arranged on the nozzle needle (21), which control sleeve (30) presses with an annular surface (32) against an end surface (65) at the nozzle needle side and thereby forms a sealing seat, such that the control sleeve (30) separates a coupler chamber (70) from a nozzle needle pressure chamber (24) which is charged with injection pressure.
  2. Fuel injector according to Claim 1, characterized in that the control sleeve (30) is preloaded by means of a compression spring (31) and presses via the annular surface (32) against the nozzle-needle-side end surface (65), and in that the preload force of the compression spring (31) is configured such that the control sleeve (30) is lifted from the sealing seat when there is a positive pressure in the coupler chamber (70) in relation to the pressure in the nozzle needle pressure chamber (24).
  3. Fuel injector according to Claim 1 or 2, characterized in that the end surface (65) at the nozzle needle side is formed on that side of the base plate (61) which points towards the nozzle needle (21).
  4. Fuel injector according to Claim 3, characterized in that a stop surface for the nozzle needle (21) is formed on the end surface (65) at the nozzle needle side.
  5. Fuel injector according to Claim 1, characterized in that, to form the coupler chamber (70), the guide element (20) has an opening (64) with a first annular chamber (71), which is exposed to the nozzle needle (21), and a second annular chamber (72), which is exposed to the coupler piston (41).
  6. Fuel injector according to Claim 1, characterized in that at least one connecting duct (68) is formed in the base plate (61) so as to lead from one side to the other, which at least one connecting duct hydraulically connects the internal storage chamber (36) to the nozzle needle pressure chamber (24).
  7. Fuel injector according to one of the preceding claims, characterized in that the guide element (20) is hydraulically sealingly clamped via the base plate (61) between an injector body (10) and a nozzle body (11).
  8. Fuel injector according to one of the preceding claims, characterized in that a stroke setting piece (75) is arranged in the coupler chamber (70), by means of which stroke setting piece the stroke of the nozzle needle (21) can be set.
  9. Fuel injector according to one of the preceding claims, characterized in that the base plate (61) has, on the end surface (66) at the coupler rod side, a guide collar (67) for centering the guide element (20).
  10. Fuel injector according to Claim 1, characterized in that the control piston (42) is guided in an axially movable manner in a valve piece (44), in that the valve piece (44) delimits the control chamber (45), in that an outflow line (49) with an outflow throttle and an inflow line (52) with an inflow throttle are guided through the valve piece (44), and in that the outflow line (49) connects the control chamber (45), via a valve seat of a valve element (14) of the control valve (12), to a low-pressure chamber (50) connected to the low-pressure/return system, and the inflow line (52) connects the control chamber (45) to the internal storage chamber (36).
EP07114360A 2006-10-10 2007-08-15 Fuel injector for a combustion engine Active EP1911966B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006047935A DE102006047935A1 (en) 2006-10-10 2006-10-10 Fuel injector for an internal combustion engine

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EP1911966A2 EP1911966A2 (en) 2008-04-16
EP1911966A3 EP1911966A3 (en) 2009-07-01
EP1911966B1 true EP1911966B1 (en) 2011-10-19

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AT (1) ATE529625T1 (en)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008044093A1 (en) 2008-11-26 2010-05-27 Robert Bosch Gmbh Fuel injector for internal combustion engine, has throttle plate arranged between inner storage chamber and pressure chamber and remaining in nozzle needle-side sealing seat in stop position when nozzle needle is placed in needle seat
DE102009007095A1 (en) * 2009-02-02 2010-08-05 Continental Automotive Gmbh Injector
DE102010030383A1 (en) * 2010-06-23 2011-12-29 Robert Bosch Gmbh Fuel injection device with hydraulic coupler

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115215A1 (en) 2001-03-28 2002-10-10 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE102006008648A1 (en) 2006-02-24 2007-08-30 Robert Bosch Gmbh Fuel e.g. diesel or petrol, injecting device for internal combustion engine, has valve unit including control piston and nozzle needle that are coupled with each other by hydraulic coupler, and guiding unit guiding fluid outlet of piston

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EP1911966A2 (en) 2008-04-16
EP1911966A3 (en) 2009-07-01
ATE529625T1 (en) 2011-11-15
DE102006047935A1 (en) 2008-04-17

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