EP1936180A2 - Fuel injector valve - Google Patents

Fuel injector valve Download PDF

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Publication number
EP1936180A2
EP1936180A2 EP07119028A EP07119028A EP1936180A2 EP 1936180 A2 EP1936180 A2 EP 1936180A2 EP 07119028 A EP07119028 A EP 07119028A EP 07119028 A EP07119028 A EP 07119028A EP 1936180 A2 EP1936180 A2 EP 1936180A2
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EP
European Patent Office
Prior art keywords
storage
volume
fuel
fuel injection
injection valve
Prior art date
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Granted
Application number
EP07119028A
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German (de)
French (fr)
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EP1936180A3 (en
EP1936180B1 (en
Inventor
Matthias Burger
Hans-Christoph Magel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1936180A2 publication Critical patent/EP1936180A2/en
Publication of EP1936180A3 publication Critical patent/EP1936180A3/en
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Publication of EP1936180B1 publication Critical patent/EP1936180B1/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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • 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.
  • the known injection valve has a multi-part valve housing which comprises a nozzle body, wherein within the nozzle body an onion-shaped nozzle volume is provided, in which there is high pressure fuel in operation, which is hosed when opening the valve needle via at least one nozzle opening. The filling of the nozzle volume takes place via a leading through the valve housing fuel channel.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that possible hydraulic vibrations are advantageously damped.
  • the fuel injector of the invention may have a relatively large storage volume, with adverse side effects associated with such a large storage volume being prevented or at least reduced.
  • a nozzle volume is formed within the valve housing, which is connected to the second storage volume, wherein upon actuation of the valve closing body fuel from the nozzle volume on the opened sealing seat is sprayed off.
  • the nozzle volume can be configured onion-shaped.
  • the inflow of fuel can be made directly into the second storage sub-volume.
  • at least one further throttle is provided between the nozzle volume and the second storage partial volume, in order to enable a faster closing of a nozzle needle.
  • the supply of fuel may also be done directly into the first storage sub-volume connected to the second storage sub-volume via the throttle.
  • the connection between the second storage partial volume and the nozzle volume can also be at least substantially unthrottled.
  • the actuating device actuates the valve closing body by means of a hydraulic coupler having a control rod which limits the storage volume, and that the throttle, which connects the first storage part volume with the second storage part volume, through a throttle gap between the control rod and a in the Valve housing inserted annular disc is formed.
  • This has the advantage that the spatial division of the storage volume into the first storage subvolume and the second storage subvolume can be done by the annular disc, whereby a cost-effective and easy to implement design of the fuel injector is possible.
  • the annular disc can be pressed into the valve housing.
  • the actuating device actuates the valve closing body by means of a hydraulic coupler having a control chamber, that the control chamber is connected by means of a drain throttle with a return, the connection of the drain throttle is controlled with the return by the actuator, and that an inlet throttle is provided, which connects the first storage part volume with the control room.
  • the hydraulic coupler has a further control chamber, that an end face of the control rod limits the control chamber, that a further end face of the control rod limits the further control chamber and that the valve closing body in dependence on a pressure difference between the pressure of a fuel in the further Control chamber and a pressure of a fuel in a nozzle chamber is actuated.
  • the first storage part volume is formed by a first storage space
  • the second storage part volume is formed by a second storage space and that the second storage space is connected to a limited by the valve seat surface nozzle space.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the fuel injection valve 1 is suitable for commercial vehicles or passenger cars.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1.
  • a mini-rail may be formed by the fuel injection valve 1, wherein the fuel injection valve 1 by a floating in the high pressure control rod 21, which may be designed needle-shaped, distinguished.
  • fuel injector 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a valve housing 3, which is generally designed in several parts and, for example, may have a nozzle body.
  • the valve housing 3 has a valve seat body 4, on which a valve seat surface 5 is formed.
  • the valve seat surface 5 cooperates with a valve closing body 6 to form a sealing seat.
  • the valve closing body 6 is actuated by a nozzle needle 7, wherein the valve closing body 6 is formed in one piece with the nozzle needle 7 in the illustrated embodiment.
  • the nozzle needle 7 is guided by a valve needle guide 8 of the valve housing 3 in the axial direction.
  • the nozzle needle 7 may additionally be acted upon by a valve spring in the direction of the sealing seat formed by the valve closing body 6 and the valve seat surface 5 with a spring force.
  • valve housing 3 has a fuel inlet nozzle 10, shown in simplified form, in order to lead fuel from a high-pressure pump 11 into the fuel injection valve 1.
  • the connection of the fuel injection valve 1 with the high-pressure pump 11 can take place via a common rail.
  • the fuel is conducted to the fuel inlet port 10 in a fuel channel 12, which opens into a first storage space 13.
  • the first storage space 13 is formed inside the valve housing 3.
  • a second storage space 14 is provided, which is also provided within the valve housing 3.
  • the first storage space 13 forms a first storage partial volume and the second storage space 14 forms second storage partial volume, wherein the two storage partial volumes formed by the storage spaces 13, 14 define a storage volume 15. Due to the storage volume 15, the fuel injection valve 1 can act as a mini-rail.
  • the storage spaces 13, 14 are connected to each other via a throttle 16. Further, an unthrottled fuel passage 17 is provided, which connects the second storage part volume defined by the second storage space 14 to a nozzle volume formed by a nozzle space 18.
  • the nozzle needle 7 has a piston portion 20, on which the nozzle needle 7 is guided in the valve needle guide 8.
  • the fuel injection valve 1 also has a control rod 21 arranged in the valve housing 3, which is arranged partly in the first storage space 13 and partly in the second storage space 14, so that the control rod 21, the first storage part volume and the second storage part volume and thus also the limited storage volume composed of the storage volume.
  • a control chamber 23 is provided, which is connected via a throttle 24 to the first storage volume of the first storage space 13.
  • a further control chamber 26 is formed, which is limited by the control rod 21, a control chamber sleeve 27 and the piston portion 20.
  • the control chamber sleeve 27 is arranged within the second storage space 14. Due to the pressure difference between a pressure of the fuel in the further control chamber 26 and a pressure of the fuel in the nozzle chamber 18, a control of the nozzle needle 7 is possible, wherein the pressure in the other control chamber 26 via the pressure in the control chamber 23 is controllable.
  • the control chamber 23 is limited by the control rod 21, a control chamber sleeve 28 and the valve housing 3. Further, valve springs 29, 30 are provided, which act on the control chamber sleeves 27, 28 each with a certain spring force.
  • the control rod 21, the control chamber sleeves 27, 28, the valve springs 29, 30 and the control chambers 23, 26 are part of a hydraulic coupler 31, which may be configured as a force or displacement amplifier.
  • an outlet throttle 32 is provided which defines a certain A / Z ratio with the throttle 24 acting as inlet throttle.
  • the flow through the outlet throttle 32 is controllable via an actuating device 33, wherein the actuating device 33 connects the outlet throttle 32 via a return 34 with a tank 35 or interrupts this connection.
  • valve closing body 6 can be operated by means of the hydraulic coupler 31 to control the opening and closing of the fuel injection valve 1.
  • the control rod 21 floats in the fuel under high pressure, wherein the control rod 21 limits both the first storage part volume of the first storage space 13 and the second storage partial volume of the second storage space 14.
  • the storage volume Due to the storage volume formed by the storage partial volume, vibrations between the high-pressure pump 11 or the common rail and the fuel injection valve 1 can be damped.
  • the storage volume form a substantially tubular storage volume 15, so that there is a risk that hydraulic pressure oscillations occur within the fuel injection valve, which are characterized by a particularly high frequency.
  • pressure oscillations with high frequency and respectable amplitude damage especially in the region of the sealing seat between the valve closing body 6 and the valve seat surface 5 during opening and closing of the fuel injection valve 1 are possible.
  • the storage volume 15 is divided by the storage spaces 13, 14 into two storage sub-volume, which are throttled connected to each other via the throttle 16.
  • the storage volume 15 it is also possible for the storage volume 15 to be subdivided into more than two storage sub-volumes, which are preferably connected to each other in a throttled manner. The advantages of the storage volume 15, in particular with respect to the vibration damping between the high pressure pump 11 and the common rail and the fuel injection valve 1, can be at least substantially obtained.
  • the throttle 16 is taken into account that the fuel channel 17, which connects the second storage space 14 with the nozzle chamber 18, is configured as an unthrottled fuel channel 17.
  • Fig. 2 shows a second embodiment of a fuel injection valve 1.
  • the supply of fuel from the high-pressure pump 11 via the fuel passage 12 takes place directly in the storage volume of the storage volume 15 formed by the second storage space 14.
  • the fuel passage 12 opens into the second storage space 14.
  • This embodiment is suitable, for example, for fuel injection valves 1, in which the fuel inlet nozzle 10 is to be arranged laterally on the valve housing 3. This is usually the case for medium or high load engines.
  • the division of the storage volume 15 into the storage sub-volume is made such that a direct introduction into the second storage space 14, which is arranged closer to the nozzle chamber 18 than the first storage space 13, takes place.
  • This has the further advantage that the throttle effect of the throttle 16 has a smaller influence on the function of the fuel injection valve 1.
  • This may for example relate to the injection pressure or the needle closing speed. This allows an optimization of the throttle 16 with regard to the damping of the pressure oscillations within the valve housing 13, in particular the storage space 15. In addition, there is a great insensitivity with respect to the tolerance of the throttle effect of the throttle 16.
  • the throttle 16 is formed in this embodiment by an annular gap 40 between an annular disc 41 and the control rod 21.
  • the annular disc 41 is in a recess 42 of the valve housing 3 is inserted.
  • the annular disk 41 can also be pressed into the valve housing 3.
  • the embodiment by means of the annular disc 41 allows a cost-effective production of the fuel injection valve 1, which can be easily implemented. Due to the low sensitivity of the equivalent throttle cross-section of the throttle 16 to the damping of the pressure oscillations within the fuel injection valve 1, it is not necessary that special tolerance ranges in the gap dimension of the annular gap 40 are maintained.
  • the size of the storage volume 15 is selected so that a certain amount of fuel can be absorbed, which allows effective damping of the high-frequency vibration components within the valve housing 3 below a certain threshold, so that wear especially in the region of the sealing seat between the valve closing body 6 and the valve seat surface 5 is prevented or at least reduced.
  • the fuel channel 17 is throttled by a throttle 43 in order to allow a faster closing of the nozzle needle 7.

Abstract

The valve (1) has an operating device (33), which is arranged in a valve housing (3). A valve closure body (6) is indirectly operable by the operating device, where the valve closure body works together with a valve seat surface for a seal seat. A storage volume (15), which is formed within the valve housing, serves for receiving certain amount of fuel. The storage volume is divided into two storage partial volumes, which are connected with one another by a throttle (16).

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 55 413 A1 ist ein Einspritzventil zum Einspritzen von Brennstoff in einen Brennraum einer Brennkraftmaschine bekannt. Das bekannte Einspritzventil weist ein mehrteiliges Ventilgehäuse auf, das einen Düsenkörper umfasst, wobei innerhalb des Düsenkörpers ein zwiebelförmiges Düsenvolumen vorgesehen ist, in dem sich im Betrieb unter hoher Druck stehender Brennstoff befindet, der beim Öffnen der Ventilnadel über wenigstens eine Düsenöffnung abgespritzt wird. Das Befüllen des Düsenvolumens erfolgt dabei über einen durch das Ventilgehäuse führenden Brennstoffkanal.From the DE 101 55 413 A1 An injection valve for injecting fuel into a combustion chamber of an internal combustion engine is known. The known injection valve has a multi-part valve housing which comprises a nozzle body, wherein within the nozzle body an onion-shaped nozzle volume is provided, in which there is high pressure fuel in operation, which is hosed when opening the valve needle via at least one nozzle opening. The filling of the nozzle volume takes place via a leading through the valve housing fuel channel.

Das aus der DE 101 55 413 A1 bekannte Einspritzventil hat den Nachteil, dass hydraulische Schwingungen zwischen einem Common-Rail, an das das Einspritzventil anschließbar ist, und dem Einspritzventil auftreten können. Dies wirkt sich ungünstig auf den Einspritzverlauf, die Mehrfacheinspritzfähigkeit und den Verschleiß des Brennstoffeinspritzventils, insbesondere im Bereich eines Dichtsitzes, aus.That from the DE 101 55 413 A1 known injection valve has the disadvantage that hydraulic vibrations between a common rail, to which the injection valve can be connected, and the injection valve can occur. This affects itself unfavorable to the course of injection, the multiple injection capability and the wear of the fuel injection valve, in particular in the region of a sealing seat from.

Es ist denkbar, dass ein gewisses Speichervolumen innerhalb des Ventilgehäuses vorgesehen ist, um diesen hydraulischen Schwingungen entgegenzuwirken. Ein derartiges Speichervolumen bringt allerdings den Nachteil mit sich, dass zusätzliche, hochfrequente Druckschwingungen innerhalb des Einspritzventils entstehen können, die insbesondere zu einem höheren Verschleiß im Bereich eines Dichtsitzes führen.It is conceivable that a certain storage volume is provided within the valve housing to counteract these hydraulic vibrations. However, such a storage volume has the disadvantage that additional, high-frequency pressure oscillations can occur within the injection valve, leading in particular to a higher wear in the region of a sealing seat.

Offenbarung der ErfindungDisclosure of the invention Vorteilhafte WirkungenAdvantageous effects

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass mögliche hydraulische Schwingungen vorteilhaft gedämpft sind. Speziell kann das Brennstoffeinspritzventil der Erfindung ein relativ großes Speichervolumen aufweisen, wobei bei solch einem großen Speichervolumen auftretende ungünstige Nebeneffekte verhindert oder zumindest verringert sind.The fuel injection valve according to the invention with the features of claim 1 has the advantage that possible hydraulic vibrations are advantageously damped. Specifically, the fuel injector of the invention may have a relatively large storage volume, with adverse side effects associated with such a large storage volume being prevented or at least reduced.

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.

In vorteilhafter Weise ist innerhalb des Ventilgehäuses ein Düsenvolumen ausgebildet, das mit dem zweiten Speichervolumen verbunden ist, wobei bei der Betätigung des Ventilschließkörpers Brennstoff aus dem Düsenvolumen über den geöffneten Dichtsitz abspritzbar ist. Das Düsenvolumen kann dabei zwiebelförmig ausgestaltet sein. Der Zufluss von Brennstoff kann direkt in das zweite Speicherteilvolumen erfolgen. In solch einem Fall ist es vorteilhaft, dass zwischen dem Düsenvolumen und dem zweiten Speicherteilvolumen zumindest eine weitere Drossel vorgesehen ist, um ein schnelleres Schließen einer Düsennadel zu ermöglichen. Die Zuführung von Brennstoff kann auch direkt in das erste Speicherteilvolumen erfolgen, das mit dem zweiten Speicherteilvolumen über die Drossel verbunden ist. In diesem Fall kann die Verbindung zwischen dem zweiten Speicherteilvolumen und dem Düsenvolumen auch zumindest im Wesentlichen ungedrosselt erfolgen.Advantageously, a nozzle volume is formed within the valve housing, which is connected to the second storage volume, wherein upon actuation of the valve closing body fuel from the nozzle volume on the opened sealing seat is sprayed off. The nozzle volume can be configured onion-shaped. The inflow of fuel can be made directly into the second storage sub-volume. In such a case, it is advantageous that at least one further throttle is provided between the nozzle volume and the second storage partial volume, in order to enable a faster closing of a nozzle needle. The supply of fuel may also be done directly into the first storage sub-volume connected to the second storage sub-volume via the throttle. In this case, the connection between the second storage partial volume and the nozzle volume can also be at least substantially unthrottled.

Vorteilhaft ist es, dass die Betätigungseinrichtung den Ventilschließkörper mittels eines hydraulischen Kopplers betätigt, der eine Steuerstange aufweist, die das Speichervolumen begrenzt, und dass die Drossel, die das erste Speicherteilvolumen mit dem zweiten Speicherteilvolumen verbindet, durch einen Drosselspalt zwischen der Steuerstange und einer in das Ventilgehäuse eingesetzten Ringscheibe gebildet ist. Dies hat den Vorteil, dass die räumliche Aufteilung des Speichervolumen in das erste Speicherteilvolumen und das zweite Speicherteilvolumen durch die Ringscheibe erfolgen kann, wodurch eine kostengünstige und einfach umzusetzende Ausgestaltung des Brennstoffeinspritzventils ermöglicht ist. Die Ringscheibe kann dabei in das Ventilgehäuse eingepresst sein. In der Regel kann eine relativ geringe Empfindlichkeit des äquivalenten Drosselquerschnitts auf die Dämpfung der Druckschwingungen angenommen werden, so dass hinsichtlich des Spaltmaßes des Drosselspaltes keine besonderen Anforderungen an die Einhaltung eines engen Toleranzfeldes gestellt sind.It is advantageous that the actuating device actuates the valve closing body by means of a hydraulic coupler having a control rod which limits the storage volume, and that the throttle, which connects the first storage part volume with the second storage part volume, through a throttle gap between the control rod and a in the Valve housing inserted annular disc is formed. This has the advantage that the spatial division of the storage volume into the first storage subvolume and the second storage subvolume can be done by the annular disc, whereby a cost-effective and easy to implement design of the fuel injector is possible. The annular disc can be pressed into the valve housing. As a rule, a relatively low sensitivity of the equivalent throttle cross-section to the damping of the pressure oscillations can be assumed, so that with regard to the gap dimension of the throttle gap, no special requirements are imposed on compliance with a narrow tolerance field.

Vorteilhaft ist es, dass die Betätigungseinrichtung den Ventilschließkörper mittels eines hydraulischen Kopplers betätigt, der einen Steuerraum aufweist, dass der Steuerraum mittels einer Ablaufdrossel mit einem Rücklauf verbunden ist, wobei die Verbindung der Ablaufdrossel mit dem Rücklauf durch die Betätigungseinrichtung gesteuert ist, und dass eine Zulaufdrossel vorgesehen ist, die das erste Speicherteilvolumen mit dem Steuerraum verbindet. Dies hat den Vorteil, dass eine Ansteuerung mit einer im Hochdruck schwimmenden Steuerstange, die auch nadelförmig ausgestaltet sein kann, erfolgen kann, wobei Druckschwingungen hinsichtlich ihrer Amplitude reduziert sind. Dabei ist es ferner vorteilhaft, dass der hydraulische Koppler einen weiteren Steuerraum aufweist, dass eine Stirnseite der Steuerstange den Steuerraum begrenzt, dass eine weitere Stirnseite der Steuerstange den weiteren Steuerraum begrenzt und dass der Ventilschließkörper in Abhängigkeit von einer Druckdifferenz zwischen dem Druck eines Brennstoffs im weiteren Steuerraum und einem Druck eines Brennstoffs in einem Düsenraum betätigbar ist.It is advantageous that the actuating device actuates the valve closing body by means of a hydraulic coupler having a control chamber, that the control chamber is connected by means of a drain throttle with a return, the connection of the drain throttle is controlled with the return by the actuator, and that an inlet throttle is provided, which connects the first storage part volume with the control room. This has the advantage that a control with a floating in the high pressure control rod, which may also be configured needle-shaped, can take place, wherein pressure oscillations are reduced in amplitude. In this case, it is also advantageous that the hydraulic coupler has a further control chamber, that an end face of the control rod limits the control chamber, that a further end face of the control rod limits the further control chamber and that the valve closing body in dependence on a pressure difference between the pressure of a fuel in the further Control chamber and a pressure of a fuel in a nozzle chamber is actuated.

Vorteilhaft ist es, dass das erste Speicherteilvolumen durch einen ersten Speicherraum gebildet ist, dass das zweite Speicherteilvolumen durch einen zweiten Speicherraum gebildet ist und dass der zweite Speicherraum mit einem durch die Ventilsitzfläche begrenzten Düsenraum verbunden ist. Dadurch ergibt sich eine kompakte Ausgestaltung, bei der ein im Wesentlichen rohrförmiger Speicherraum realisiert werden kann, wobei die Amplitude von hochfrequenten Druckschwingungen zuverlässig gedämpft ist.It is advantageous that the first storage part volume is formed by a first storage space, that the second storage part volume is formed by a second storage space and that the second storage space is connected to a limited by the valve seat surface nozzle space. This results in a compact design, in which a substantially tubular storage space can be realized, wherein the amplitude of high-frequency pressure oscillations is reliably damped.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

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

  • Fig. 1 ein erstes Ausführungsbeispiel eines Brennstoffeinspritzventils der Erfindung in einer auszugsweisen, axialen Schnittdarstellung und
  • Fig. 2 ein zweites Ausführungsbeispiels eines Brennstoffeinspritzventils der Erfindung in einer auszugsweisen, axialen Schnittdarstellung.
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 second embodiment of a fuel injection valve of the invention in an excerpt, axial sectional view.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein erstes Ausführungsbeispiel eines Brennstoffeinspritzventils 1 der Erfindung in einer schematischen, auszugsweisen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Speziell eignet sich das Brennstoffeinspritzventil 1 für Nutzkraftwagen oder Personenkraftwagen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine Brennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck zu mehreren Brennstoffeinspritzventilen 1 führt. Dabei kann durch das Brennstoffeinspritzventil 1 ein Mini-Rail gebildet sein, wobei sich das Brennstoffeinspritzventil 1 durch eine im Hochdruck schwimmende Steuerstange 21, die nadelförmig ausgestaltet sein kann, auszeichnen kann. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view. The fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. Specifically, the fuel injection valve 1 is suitable for commercial vehicles or passenger cars. A preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1. In this case, a mini-rail may be formed by the fuel injection valve 1, wherein the fuel injection valve 1 by a floating in the high pressure control rod 21, which may be designed needle-shaped, distinguished. The However, fuel injector 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist ein Ventilgehäuse 3 auf, das in der Regel mehrteilig ausgestaltet ist und beispielsweise einen Düsenkörper aufweisen kann. Das Ventilgehäuse 3 weist einen Ventilsitzkörper 4 auf, an dem eine Ventilsitzfläche 5 ausgebildet ist. Die Ventilsitzfläche 5 wirkt mit einem Ventilschließkörper 6 zu einem Dichtsitz zusammen. Der Ventilschließkörper 6 ist dabei von einer Düsennadel 7 betätigbar, wobei der Ventilschließkörper 6 in dem dargestellten Ausführungsbeispiel einstückig mit der Düsennadel 7 ausgebildet ist. Die Düsennadel 7 ist von einer Ventilnadelführung 8 des Ventilgehäuses 3 in axialer Richtung geführt. Die Düsennadel 7 kann dabei zusätzlich von einer Ventilfeder in Richtung des durch den Ventilschließkörper 6 und die Ventilsitzfläche 5 gebildeten Dichtsitzes mit einer Federkraft beaufschlagt sein. Außerdem weist das Ventilgehäuse 3 einen vereinfacht dargestellten Brennstoffeinlassstutzen 10 auf, um Brennstoff von einer Hochdruckpumpe 11 in das Brennstoffeinspritzventil 1 zu führen. Die Verbindung des Brennstoffeinspritzventils 1 mit der Hochdruckpumpe 11 kann dabei über ein Common-Rail erfolgen.The fuel injection valve 1 has a valve housing 3, which is generally designed in several parts and, for example, may have a nozzle body. The valve housing 3 has a valve seat body 4, on which a valve seat surface 5 is formed. The valve seat surface 5 cooperates with a valve closing body 6 to form a sealing seat. The valve closing body 6 is actuated by a nozzle needle 7, wherein the valve closing body 6 is formed in one piece with the nozzle needle 7 in the illustrated embodiment. The nozzle needle 7 is guided by a valve needle guide 8 of the valve housing 3 in the axial direction. The nozzle needle 7 may additionally be acted upon by a valve spring in the direction of the sealing seat formed by the valve closing body 6 and the valve seat surface 5 with a spring force. In addition, the valve housing 3 has a fuel inlet nozzle 10, shown in simplified form, in order to lead fuel from a high-pressure pump 11 into the fuel injection valve 1. The connection of the fuel injection valve 1 with the high-pressure pump 11 can take place via a common rail.

In dem dargestellten Ausführungsbeispiel wird der Brennstoff an dem Brennstoffeinlassstutzen 10 in einen Brennstoffkanal 12 geleitet, der in einen ersten Speicherraum 13 mündet. Der erste Speicherraum 13 ist innerhalb des Ventilgehäuses 3 ausgebildet. Ferner ist ein zweiter Speicherraum 14 vorgesehen, der ebenfalls innerhalb des Ventilgehäuses 3 vorgesehen ist. Der erste Speicherraum 13 bildet ein erstes Speicherteilvolumen und der zweite Speicherraum 14 bildet ein zweites Speicherteilvolumen, wobei die beiden von den Speicherräumen 13, 14 gebildeten Speicherteilvolumen ein Speichervolumen 15 vorgeben. Durch das Speichervolumen 15 kann das Brennstoffeinspritzventil 1 als Mini-Rail wirken. Die Speicherräume 13, 14 sind über eine Drossel 16 miteinander verbunden. Ferner ist ein ungedrosselter Brennstoffkanal 17 vorgesehen, der das zweite Speicherteilvolumen, das durch den zweiten Speicherraum 14 definiert ist, mit einem Düsenvolumen verbindet, das durch einen Düsenraum 18 gebildet ist. Bei einer Betätigung der Düsennadel 7 wird Brennstoff aus dem Düsenraum 18 über den geöffneten Dichtsitz, der zwischen dem Ventilschließkörper 6 und der Ventilsitzfläche 5 gebildet ist, und eine Düsenöffnung 19 in dem Ventilsitzkörper in einen Brennraum oder dergleichen der Brennkraftmaschine eingespritzt.In the illustrated embodiment, the fuel is conducted to the fuel inlet port 10 in a fuel channel 12, which opens into a first storage space 13. The first storage space 13 is formed inside the valve housing 3. Furthermore, a second storage space 14 is provided, which is also provided within the valve housing 3. The first storage space 13 forms a first storage partial volume and the second storage space 14 forms second storage partial volume, wherein the two storage partial volumes formed by the storage spaces 13, 14 define a storage volume 15. Due to the storage volume 15, the fuel injection valve 1 can act as a mini-rail. The storage spaces 13, 14 are connected to each other via a throttle 16. Further, an unthrottled fuel passage 17 is provided, which connects the second storage part volume defined by the second storage space 14 to a nozzle volume formed by a nozzle space 18. Upon actuation of the nozzle needle 7, fuel is injected from the nozzle chamber 18 via the open sealing seat formed between the valve closing body 6 and the valve seat surface 5 and a nozzle opening 19 in the valve seat body into a combustion chamber or the like of the internal combustion engine.

Die Düsennadel 7 weist einen Kolbenabschnitt 20 auf, an dem die Düsennadel 7 in der Ventilnadelführung 8 geführt ist. Das Brennstoffeinspritzventil 1 weist außerdem eine in dem Ventilgehäuse 3 angeordnete Steuerstange 21 auf, die zum Teil in dem ersten Speicherraum 13 und zum Teil in dem zweiten Speicherraum 14 angeordnet ist, so dass die Steuerstange 21 das erste Speicherteilvolumen und das zweite Speicherteilvolumen und somit auch das aus den Speicherteilvolumen zusammengesetzte Speichervolumen begrenzt. An einer ersten Stirnseite 22 der Steuerstange 21 ist ein Steuerraum 23 vorgesehen, der über eine Drossel 24 mit dem ersten Speichervolumen des ersten Speicherraums 13 verbunden ist. Ferner ist an einer weiteren Stirnseite 25 der Steuerstange 21, die der Stirnseite 22 abgewandt ist, ein weiterer Steuerraum 26 ausgebildet, der durch die Steuerstange 21 eine Steuerraumhülse 27 und den Kolbenabschnitt 20 begrenzt ist. Die Steuerraumhülse 27 ist dabei innerhalb des zweiten Speicherraums 14 angeordnet. Durch die Druckdifferenz zwischen einem Druck des Brennstoffs im weiteren Steuerraum 26 und einem Druck des Brennstoffs im Düsenraum 18 ist eine Steuerung der Düsennadel 7 möglich, wobei der Druck im weiteren Steuerraum 26 über den Druck im Steuerraum 23 steuerbar ist. Der Steuerraum 23 ist dabei durch die Steuerstange 21, eine Steuerraumhülse 28 und das Ventilgehäuse 3 begrenzt. Ferner sind Ventilfedern 29, 30 vorgesehen, die die Steuerraumhülsen 27, 28 jeweils mit einer gewissen Federkraft beaufschlagen.The nozzle needle 7 has a piston portion 20, on which the nozzle needle 7 is guided in the valve needle guide 8. The fuel injection valve 1 also has a control rod 21 arranged in the valve housing 3, which is arranged partly in the first storage space 13 and partly in the second storage space 14, so that the control rod 21, the first storage part volume and the second storage part volume and thus also the limited storage volume composed of the storage volume. At a first end face 22 of the control rod 21, a control chamber 23 is provided, which is connected via a throttle 24 to the first storage volume of the first storage space 13. Further, on another end face 25 of the control rod 21, which faces away from the end face 22, a further control chamber 26 is formed, which is limited by the control rod 21, a control chamber sleeve 27 and the piston portion 20. The control chamber sleeve 27 is arranged within the second storage space 14. Due to the pressure difference between a pressure of the fuel in the further control chamber 26 and a pressure of the fuel in the nozzle chamber 18, a control of the nozzle needle 7 is possible, wherein the pressure in the other control chamber 26 via the pressure in the control chamber 23 is controllable. The control chamber 23 is limited by the control rod 21, a control chamber sleeve 28 and the valve housing 3. Further, valve springs 29, 30 are provided, which act on the control chamber sleeves 27, 28 each with a certain spring force.

Die Steuerstange 21, die Steuerraumhülsen 27, 28, die Ventilfedern 29, 30 sowie die Steuerräume 23, 26 sind Teil eines hydraulischen Kopplers 31, der als Kraft- oder Wegverstärker ausgestaltet sein kann. Dabei ist eine Ablaufdrossel 32 vorgesehen, die mit der als Zulaufdrossel wirkenden Drossel 24 ein gewisses A/Z-Verhältnis vorgibt. Der Fluss durch die Ablaufdrossel 32 ist über eine Betätigungseinrichtung 33 steuerbar, wobei die Betätigungseinrichtung 33 die Ablaufdrossel 32 über eine Rücklauf 34 mit einem Tank 35 verbindet oder diese Verbindung unterbricht.The control rod 21, the control chamber sleeves 27, 28, the valve springs 29, 30 and the control chambers 23, 26 are part of a hydraulic coupler 31, which may be configured as a force or displacement amplifier. In this case, an outlet throttle 32 is provided which defines a certain A / Z ratio with the throttle 24 acting as inlet throttle. The flow through the outlet throttle 32 is controllable via an actuating device 33, wherein the actuating device 33 connects the outlet throttle 32 via a return 34 with a tank 35 or interrupts this connection.

Somit kann mit der in dem Ventilgehäuse 3 angeordneten Betätigungseinrichtung 33 der Ventilschließkörper 6 mittels des hydraulischen Kopplers 31 betätigt werden, um das Öffnen und Schließen des Brennstoffeinspritzventils 1 zu steuern. Die Steuerstange 21 schwimmt dabei im unter hohem Druck stehenden Brennstoff, wobei die Steuerstange 21 sowohl das erste Speicherteilvolumen des ersten Speicherraums 13 als auch das zweite Speicherteilvolumen des zweiten Speicherraums 14 begrenzt.Thus, with the actuator 33 disposed in the valve housing 3, the valve closing body 6 can be operated by means of the hydraulic coupler 31 to control the opening and closing of the fuel injection valve 1. The control rod 21 floats in the fuel under high pressure, wherein the control rod 21 limits both the first storage part volume of the first storage space 13 and the second storage partial volume of the second storage space 14.

Durch das durch die Speicherteilvolumen gebildete Speichervolumen können Schwingungen zwischen der Hochdruckpumpe 11 beziehungsweise dem Common-Rail und dem Brennstoffeinspritzventil 1 gedämpft. In dem in der Fig. 1 dargestellten Ausführungsbeispiel bilden die Speichervolumen ein im Wesentlichen rohrförmiges Speichervolumen 15, so dass die Gefahr besteht, dass hydraulische Druckschwingungen innerhalb des Brennstoffeinspritzventils auftreten, die sich durch eine besonders hohe Frequenz auszeichnen. Durch solche Druckschwingungen mit hoher Frequenz und respektabler Amplitude sind Beschädigungen speziell im Bereich des Dichtsitzes zwischen dem Ventilschließkörper 6 und der Ventilsitzfläche 5 beim Öffnen und Schließen des Brennstoffeinspritzventils 1 möglich. Allerdings ist das Speichervolumen 15 durch die Speicherräume 13, 14 in zwei Speicherteilvolumen aufgeteilt, die über die Drossel 16 gedrosselt miteinander verbunden sind. Dadurch kommt es zu einer Dämpfung, bei einer entsprechend ausgelegten Drossel 16 insbesondere zu einer starken Dämpfung, dieser hochfrequenten Schwingungen, so dass die Amplitude der hochfrequenten Schwingungen in kurzer Zeit unter einen für den Verschleiß unkritischen Wert gesenkt werden kann. Somit kann eine hohe Verschleißsicherheit des Brennstoffeinspritzventils 1 gewährleistet werden. Hierbei ist es auch möglich, dass das Speichervolumen 15 in mehr als zwei Speicherteilvolumen unterteilt wird, die vorzugsweise gedrosselt miteinander verbunden sind. Die Vorteile des Speichervolumens 15, insbesondere in Bezug auf die Schwingungsdämpfung zwischen der Hochdruckpumpe 11 beziehungsweise dem Common-Rail und dem Brennstoffeinspritzventil 1, können dabei zumindest im Wesentlichen erhalten werden.Due to the storage volume formed by the storage partial volume, vibrations between the high-pressure pump 11 or the common rail and the fuel injection valve 1 can be damped. In the in the Fig. 1 illustrated embodiment, the storage volume form a substantially tubular storage volume 15, so that there is a risk that hydraulic pressure oscillations occur within the fuel injection valve, which are characterized by a particularly high frequency. By such pressure oscillations with high frequency and respectable amplitude damage especially in the region of the sealing seat between the valve closing body 6 and the valve seat surface 5 during opening and closing of the fuel injection valve 1 are possible. However, the storage volume 15 is divided by the storage spaces 13, 14 into two storage sub-volume, which are throttled connected to each other via the throttle 16. This results in a damping, with a correspondingly designed throttle 16 in particular to a strong damping, this high-frequency oscillations, so that the amplitude of the high-frequency vibrations in a short time can be reduced below a value uncritical for the wear. Thus, a high wear resistance of the fuel injection valve 1 can be ensured. In this case, it is also possible for the storage volume 15 to be subdivided into more than two storage sub-volumes, which are preferably connected to each other in a throttled manner. The advantages of the storage volume 15, in particular with respect to the vibration damping between the high pressure pump 11 and the common rail and the fuel injection valve 1, can be at least substantially obtained.

Ferner ist anzumerken, dass bei der Wahl der Drosselwirkung der Drossel 16 berücksichtigt ist, dass der Brennstoffkanal 17, der den zweiten Speicherraum 14 mit dem Düsenraum 18 verbindet, als ungedrosselter Brennstoffkanal 17 ausgestaltet ist.It should also be noted that in the choice of throttle effect the throttle 16 is taken into account that the fuel channel 17, which connects the second storage space 14 with the nozzle chamber 18, is configured as an unthrottled fuel channel 17.

Fig. 2 zeigt ein zweites Ausführungsbeispiel eines Brennstoffeinspritzventils 1. In diesem Ausführungsbeispiel erfolgt die Zufuhr von Brennstoff aus der Hochdruckpumpe 11 über den Brennstoffkanal 12 direkt in das durch den zweiten Speicherraum 14 gebildete Speicherteilvolumen des Speichervolumens 15. Der Brennstoffkanal 12 mündet in den zweiten Speicherraum 14. Diese Ausgestaltung eignet sich beispielsweise für Brennstoffeinspritzventile 1, bei denen der Brennstoffeinlassstutzen 10 seitlich am Ventilgehäuse 3 angeordnet sein soll. Dies ist in der Regel bei Brennkraftmaschinen für mittlere oder hohe Last der Fall. Die Aufteilung des Speichervolumens 15 in die Speicherteilvolumen ist so vorgenommen, dass eine direkte Einleitung in den zweiten Speicherraum 14, der näher an dem Düsenraum 18 angeordnet ist als der erste Speicherraum 13, erfolgt. Dies hat den weiteren Vorteil, dass die Drosselwirkung der Drossel 16 einen geringeren Einfluss auf die Funktion des Brennstoffeinspritzventils 1 hat. Dies kann beispielsweise den Einspritzdruck oder die Nadelschließgeschwindigkeit betreffen. Dies ermöglicht eine Optimierung der Drossel 16 im Hinblick auf die Dämpfung der Druckschwingungen innerhalb des Ventilgehäuses 13, insbesondere des Speicherraums 15. Außerdem ergibt sich eine große Unempfindlichkeit in Bezug auf die Toleranz der Drosselwirkung der Drossel 16. Fig. 2 shows a second embodiment of a fuel injection valve 1. In this embodiment, the supply of fuel from the high-pressure pump 11 via the fuel passage 12 takes place directly in the storage volume of the storage volume 15 formed by the second storage space 14. The fuel passage 12 opens into the second storage space 14. This embodiment is suitable, for example, for fuel injection valves 1, in which the fuel inlet nozzle 10 is to be arranged laterally on the valve housing 3. This is usually the case for medium or high load engines. The division of the storage volume 15 into the storage sub-volume is made such that a direct introduction into the second storage space 14, which is arranged closer to the nozzle chamber 18 than the first storage space 13, takes place. This has the further advantage that the throttle effect of the throttle 16 has a smaller influence on the function of the fuel injection valve 1. This may for example relate to the injection pressure or the needle closing speed. This allows an optimization of the throttle 16 with regard to the damping of the pressure oscillations within the valve housing 13, in particular the storage space 15. In addition, there is a great insensitivity with respect to the tolerance of the throttle effect of the throttle 16.

Die Drossel 16 ist in diesem Ausführungsbeispiel durch einen Ringspalt 40 zwischen einer Ringscheibe 41 und der Steuerstange 21 gebildet. Die Ringscheibe 41 ist dabei in eine Aussparung 42 des Ventilgehäuses 3 eingesetzt. Die Ringscheibe 41 kann auch in das Ventilgehäuse 3 eingepresst sein. Die Ausgestaltung mittels der Ringscheibe 41 ermöglicht eine kostengünstige Herstellung des Brennstoffeinspritzventils 1, die einfach umgesetzt werden kann. Aufgrund der geringen Empfindlichkeit des äquivalenten Drosselquerschnitts der Drossel 16 auf die Dämpfung der Druckschwingungen innerhalb des Brennstoffeinspritzventils 1 ist es nicht erforderlich, dass besondere Toleranzfelder beim Spaltmaß des Ringspalts 40 eingehalten werden.The throttle 16 is formed in this embodiment by an annular gap 40 between an annular disc 41 and the control rod 21. The annular disc 41 is in a recess 42 of the valve housing 3 is inserted. The annular disk 41 can also be pressed into the valve housing 3. The embodiment by means of the annular disc 41 allows a cost-effective production of the fuel injection valve 1, which can be easily implemented. Due to the low sensitivity of the equivalent throttle cross-section of the throttle 16 to the damping of the pressure oscillations within the fuel injection valve 1, it is not necessary that special tolerance ranges in the gap dimension of the annular gap 40 are maintained.

Die Größe des Speichervolumens 15 ist so gewählt, dass eine gewisse Brennstoffmenge aufgenommen werden kann, die eine wirksame Dämpfung der hochfrequenten Schwingungsanteile innerhalb des Ventilgehäuses 3 unter einen gewissen Schwellwert ermöglicht, so dass ein Verschleiß speziell im Bereich des Dichtsitzes zwischen dem Ventilschließkörper 6 und der Ventilsitzfläche 5 verhindert oder zumindest verringert ist.The size of the storage volume 15 is selected so that a certain amount of fuel can be absorbed, which allows effective damping of the high-frequency vibration components within the valve housing 3 below a certain threshold, so that wear especially in the region of the sealing seat between the valve closing body 6 and the valve seat surface 5 is prevented or at least reduced.

Bei dem in der Fig. 2 dargestellten Ausführungsbeispiel mündet der Brennstoffkanal 12 direkt in den zweiten Speicherraum 14. In diesem Fall kann es vorteilhaft sein, dass der Brennstoffkanal 17 durch eine Drossel 43 gedrosselt ist, um ein schnelleres Schließen der Düsennadel 7 zu ermöglichen.In the in the Fig. 2 In this case, it may be advantageous that the fuel channel 17 is throttled by a throttle 43 in order to allow a faster closing of the nozzle needle 7.

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

Claims (10)

Brennstoffeinspritzventil (1), insbesondere Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen, mit einer in einem Ventilgehäuse (3) angeordneten Betätigungseinrichtung (33) und einem von der Betätigungseinrichtung (33) zumindest mittelbar betätigbaren Ventilschließkörper (6), der mit einer Ventilsitzfläche (5) zu einem Dichtsitz zusammenwirkt,
wobei innerhalb des Ventilgehäuses (3) ein Speichervolumen (15) ausgebildet ist, das zum Aufnehmen einer gewissen Brennstoffmenge dient, und wobei das Speichervolumen (15) in ein erstes Speicherteilvolumen und zumindest ein zweites Speicherteilvolumen aufgeteilt ist, die mittels zumindest einer Drossel (16) miteinander verbunden sind.Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, with an actuating device (33) arranged in a valve housing (3) and a valve closing body (6) which can be actuated at least indirectly by the actuating device (33) and which is provided with a valve seat surface (5 ) cooperates to a sealing seat,
wherein within the valve housing (3) a storage volume (15) is formed, which serves for receiving a certain amount of fuel, and wherein the storage volume (15) is divided into a first storage partial volume and at least a second storage partial volume, which by means of at least one throttle (16) connected to each other. Brennstoffeinspritzventil nach Anspruch 1,
dadurch gekennzeichnet,
dass innerhalb des Ventilgehäuses (3) ein Düsenvolumen ausgebildet ist, das mit dem zweiten Speicherteilvolumen verbunden ist, und dass bei der Betätigung des Ventilschließkörpers (6) Brennstoff aus dem Düsenvolumen über den geöffneten Dichtsitz abspritzbar ist.Fuel injection valve according to claim 1,
characterized,
in that a nozzle volume is formed within the valve housing (3), which is connected to the second storage subvolume, and in that, upon actuation of the valve closing body (6), fuel can be ejected from the nozzle volume via the opened sealing seat. Brennstoffeinspritzventil nach Anspruch 2,
dadurch gekennzeichnet,
dass das Düsenvolumen mittels einer weiteren Drossel (43) mit dem zweiten Speicherteilvolumen verbunden ist.Fuel injection valve according to claim 2,
characterized,
that the nozzle volume is connected via a further throttle (43) to the second storage part volume. Brennstoffeinspritzventil nach Anspruch 2,
dadurch gekennzeichnet,
dass das Düsenvolumen zumindest im Wesentlichen ungedrosselt mit zweiten Speicherteilvolumen verbunden ist.Fuel injection valve according to claim 2,
characterized,
that the nozzle volume is at least substantially unthrottled connected to the second storage sub-volume. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet,
dass ein Brennstoffeinlassstutzen (10) vorgesehen ist, über den Brennstoff in das erste Speicherteilvolumen einführbar ist.Fuel injection valve according to one of claims 1 to 4,
characterized,
that a fuel inlet port (10) is provided which is insertable through the fuel in the first storage part volume. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet,
dass ein Brennstoffeinlassstutzen (10) vorgesehen ist, über den Brennstoff in das zweite Speicherteilvolumen einführbar ist.Fuel injection valve according to one of claims 1 to 4,
characterized,
that a fuel inlet port (10) is provided which is insertable through the fuel in the second storage sub-volume. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet,
dass die Betätigungseinrichtung (33) den Ventilschließkörper (6) mittels eines hydraulischen Kopplers (31) betätigt, der eine Steuerstange (21) aufweist, dass die Steuerstange (21) zumindest teilweise das Speichervolumen (15) begrenzt und
dass die Drossel (16), die das erste Speicherteilvolumen mit dem zweiten Speicherteilvolumen verbindet, durch einen Drosselspalt (40) zwischen der Steuerstange (21) und einer in das Ventilgehäuse (3) eingesetzten Ringscheibe (41) gebildet ist.Fuel injection valve according to one of claims 1 to 6,
characterized,
in that the actuating device (33) actuates the valve closing body (6) by means of a hydraulic coupler (31) having a control rod (21), that the control rod (21) at least partially limits the storage volume (15) and
in that the throttle (16), which connects the first storage partial volume to the second storage partial volume, is formed by a throttle gap (40) between the control rod (21) and an annular disc (41) inserted into the valve housing (3). Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet,
dass die Betätigungseinrichtung (33) den Ventilschließkörper (6) mittels eines hydraulischen Kopplers (31) betätigt, der einen Steuerraum (23) aufweist, dass der Steuerraum (23) mittels einer Ablaufdrossel (32) mit einem Rücklauf (34) verbunden ist, wobei die Verbindung der Ablaufdrossel (32) mit dem Rücklauf (34) mittels der Betätigungseinrichtung (33) gesteuert ist, und dass eine Zulaufdrossel (24) vorgesehen ist, die das erste Speicherteilvolumen mit dem Steuerraum (23) verbindet.Fuel injection valve according to one of claims 1 to 7,
characterized,
in that the actuating device (33) actuates the valve closing body (6) by means of a hydraulic coupler (31) having a control chamber (23), that the control chamber (23) is connected to a return (34) by means of an outlet throttle (32) the connection of the outlet throttle (32) with the return (34) by means of the actuating device (33) is controlled, and that an inlet throttle (24) is provided, which connects the first storage part volume with the control chamber (23). Brennstoffeinspritzventil nach Anspruch 8,
dadurch gekennzeichnet,
dass der hydraulische Koppler einen weiteren Steuerraum (26) aufweist, dass eine Steuerstange (21) vorgesehen ist, wobei eine Stirnseite (22) der Steuerstange (21) den Steuerraum (23) begrenzt und eine weitere Stirnseite (25) der Steuerstange (21) den weiteren Steuerraum (26) begrenzt, und
dass der Ventilschließkörper (6) in Abhängigkeit von einer Druckdifferenz zwischen einem Druck eines Brennstoffes im weiteren Steuerraum (26) und einem Druck eines Brennstoffes in einem Düsenraum betätigbar ist.Fuel injection valve according to claim 8,
characterized,
in that the hydraulic coupler has a further control chamber (26), that a control rod (21) is provided, wherein an end face (22) of the control rod (21) delimits the control chamber (23) and a further end face (25) of the control rod (21) the other control room (26) limited, and
that the valve closing body (6) in response to a pressure difference between a pressure of a fuel in a further control chamber (26) and a pressure of a fuel in a nozzle chamber can be actuated. Brennstoffeinspritzventil nach Anspruch 9,
dadurch gekennzeichnet,
dass ein erster Speicherraum (13) vorgesehen ist, der das erste Speicherteilvolumen aufweist, dass ein zweiter Speicherraum (14) vorgesehen ist, der das zweite Speicherteilvolumen aufweist, und dass der zweite Speicherraum (14) mit einem Düsenraum (18) verbunden ist, der zumindest teilweise durch die Ventilsitzfläche (5) begrenzt ist.Fuel injection valve according to claim 9,
characterized,
in that a first storage space (13) is provided which has the first storage partial volume, a second storage space (14) is provided which has the second storage partial volume, and the second storage space (14) is connected to a nozzle space (18) is limited at least partially by the valve seat surface (5).
EP20070119028 2006-12-21 2007-10-23 Fuel injector valve Active EP1936180B1 (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
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EP2187034A1 (en) * 2008-11-14 2010-05-19 Robert Bosch Gmbh A fuel injector with axial sealing element
WO2011160900A1 (en) * 2010-06-23 2011-12-29 Robert Bosch Gmbh Fuel injection device comprising a hydraulic coupler
WO2012085186A1 (en) * 2010-12-23 2012-06-28 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
CN114135430A (en) * 2021-12-08 2022-03-04 一汽解放汽车有限公司 Fuel injection valve

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DE10060812A1 (en) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Fuel injection system for internal combustion engines
DE10121892A1 (en) * 2001-05-05 2002-11-07 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10348929A1 (en) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Fuel injection valve for automobile internal combustion engine has jet control space between valve control piston and jet needle coupled via flow channel to valve space for regulation of fuel pressure

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DE10155413A1 (en) 2001-11-10 2003-05-22 Bosch Gmbh Robert Valve for controlling liquids

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2187034A1 (en) * 2008-11-14 2010-05-19 Robert Bosch Gmbh A fuel injector with axial sealing element
WO2011160900A1 (en) * 2010-06-23 2011-12-29 Robert Bosch Gmbh Fuel injection device comprising a hydraulic coupler
WO2012085186A1 (en) * 2010-12-23 2012-06-28 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
CN103261660A (en) * 2010-12-23 2013-08-21 罗伯特·博世有限公司 Fuel injection valve for internal combustion engines
CN103261660B (en) * 2010-12-23 2016-01-13 罗伯特·博世有限公司 For the Fuelinjection nozzle of internal-combustion engine
CN114135430A (en) * 2021-12-08 2022-03-04 一汽解放汽车有限公司 Fuel injection valve

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DE102006060657A1 (en) 2008-07-03
EP1936180A3 (en) 2009-09-16
EP1936180B1 (en) 2013-09-11

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