EP1544454B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1544454B1
EP1544454B1 EP20040105054 EP04105054A EP1544454B1 EP 1544454 B1 EP1544454 B1 EP 1544454B1 EP 20040105054 EP20040105054 EP 20040105054 EP 04105054 A EP04105054 A EP 04105054A EP 1544454 B1 EP1544454 B1 EP 1544454B1
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EP
European Patent Office
Prior art keywords
fuel injection
injection valve
valve according
coupler
coupler portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
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EP20040105054
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German (de)
French (fr)
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EP1544454A1 (en
Inventor
Walter Maeurer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1544454A1 publication Critical patent/EP1544454A1/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
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim (WO-A-01/29403).
  • Couplers in particular hydraulically operating couplers in fuel injection valves with piezo drive, for compensation of temperature and pressure-related changes in length of components, in particular of the actuator, and length changes due to wear, are known from the prior art.
  • DE 101 37 210 A1 discloses a fuel injection valve with a piezoelectric actuator which is in operative connection with a valve needle.
  • the valve needle has at its discharge end a valve closing body which cooperates with a valve seat surface to a sealing seat.
  • a coupler which serves to compensate for changes in length of components of the fuel injection valve, in particular temperature-induced changes in length of the actuator, is disposed between the valve needle and the actuator.
  • the coupler has two mutually axially movable sections or pistons, which form two annular gaps and a hydraulic volume.
  • the annular gaps connect the hydraulic volume with the fuel-filled interior of the valve body.
  • fuel is added or discharged through the annular gaps.
  • a disadvantage of the above-mentioned prior art is in particular that high internal coupler pressures can only be achieved by correspondingly high biasing forces. At low coupler internal pressures, the cavitation tendency of the hydraulic medium used increases, strong preload forces are unfavorable for the valve dynamics and the setting accuracy. In addition, components must be sized larger in order to withstand the increased forces permanently.
  • the fuel injection valve according to the invention with the features of the main claim has the advantage that at relatively low preload high Kopplerinnendschreibe can be achieved.
  • the Kavitationsne Trent of the hydraulic medium is very low while good valve dynamics and small component dimensions.
  • the durability and reliability as well as the valve dynamics of the fuel injection valve are thereby also improved.
  • the preload forces can be adjusted more accurately and easily.
  • the pressure element is formed spirally and permanently elastic.
  • the pressure element can be advantageously arranged compact and the biasing force can permanently hold constant.
  • the first coupler section and the second coupler section are cylindrical, the gap is formed as an annular gap and the recess is formed as a hollow cylinder.
  • the coupler can be particularly simple, compact and easy to build.
  • the first section tapers in a cylindrical extension away from the hydraulic volume.
  • the pressure element can be placed particularly favorable, wherein it is particularly favorable for the extension also to be tapered by a step at the level of the upper edge of the recess and the extension is arranged coaxially to the first section.
  • the extension has an axially extending channel, which is connected via a thereto extending with a radial direction portion opening with the compensation chamber.
  • the coupler can thereby be filled with hydraulic medium in a particularly simple manner and closed by a spherical body.
  • the compensation space can be particularly easily formed and advantageously placed. This can be further improved by clamping one end of the flexible portion between the first portion and the first holder and / or the other end of the flexible portion between the second portion and the second holder.
  • the pressure element presses with the interposition of an intermediate layer element on the flexible portion.
  • the pressure prevailing in the equalization chamber This makes it particularly easy to set and adjust.
  • the intermediate layer element is annular or perforated disk-shaped, wherein the area resting on the flexible section is circular-segment-shaped or rounded in cross-section.
  • the pressure acting on the flexible portion pressure can thereby distribute more evenly and the coupler can be made more compact, as well as the sleeve-shaped design of at least one of the holders.
  • the second holder tapers step-like. This makes a very compact and simple construction of the coupler possible.
  • the hydraulic volume in addition to the gap, connected to the expansion chamber through at least one throttle bore.
  • the hydraulic properties of the coupler can be characterized advantageous and easy influence and easy to adjust.
  • An inventive fuel injection valve 1 shown in an axial sectional view in FIG. 1 is used in particular for the direct injection of fuel into a combustion chamber of a mixture-compressing, spark-ignited internal combustion engine.
  • a valve needle 8 In a hollow cylindrical valve housing 38, which tapers stepwise downward in the direction of discharge, a valve needle 8, an actuator 2 and a hydraulic coupler 3 are arranged coaxially to one another.
  • the housing 38 On the inflow side, the housing 38 is hermetically sealed by a housing cover 4. On the housing cover 4 is supported on the inside of the actuator 2 with its inflow end.
  • the actuator 2 On the outflow side, the actuator 2 has a disk-shaped actuator head 10.
  • the actuator head 10 is axially movably guided in a hollow cylindrical actuator module housing 9.
  • the actuator housing 5 is connected downstream of the valve needle 8 via a corrugated bellows 39, which hermetically seals the actuator chamber 42 from the fuel.
  • a second spring element 22 is clamped between the actuator head 10 and the second flange 15 with a bias voltage and holds the actuator head 10 in constant contact with the actuator 2.
  • the hydraulic coupler 3 is disposed between the actuator 2 and the valve needle 8, wherein a first cylindrical coupler section 23 upstream and a second cylindrical coupler section 24 are arranged downstream.
  • the first smaller diameter coupler section 23 engages in a coaxially in the second section 24 on the upstream side arranged hollow cylindrical recess 16 partially.
  • the gap 27 connects a hydraulic volume 17 lying between the opposing axial inner surfaces of first and second coupler sections 23, 24 and a compensation chamber 21.
  • the size of the hydraulic volume 17 can be varied by the mutually axially displaceable two coupler sections 23, 24.
  • the first coupler section 23 has a coaxially arranged cylindrical or rod-shaped extension 32.
  • the extension 32 is arranged on the axial side of the first coupler section 23 directed away from the hydraulic volume 17, that is to say towards the actuator 2.
  • the first coupler section 23 tapers through a lying approximately at the level of the upper edge of the recess 16 stage 33 to the extension 32.
  • a axially extending coaxially in the extension 32 and channel 26, which is prepared for example by drilling is through a in the wall of the extension 32 arranged opening 34 connected to the compensation chamber 21.
  • On the inflow side of the extension 32 engages the actuator head 10 partially into the actuator housing 9 and is joined to the actuator head 10, for example, material or non-positive.
  • a first sleeve-shaped holder 29 is slipped over the extension 32 and clamps the flexible portion 25 in the region of its inner circumference between itself and the extension 32 form-fitting. and / or non-positively and hermetically tight.
  • the flexible section 25 facing and resting on it end of the first holder 29 is rounded.
  • the first holder 29 is immovably connected to the extension 32, for example by a weld.
  • a second sleeve-shaped holder 30 engages with a downstream axial portion of the second coupler portion 24 and here is joined to the radial outer surface of the second coupler portion 24, for example by welding.
  • the portion of the outer periphery of the flexible portion 25 is hermetically clamped between the downstream axial portion of the second holder 30 and the second coupler portion 24.
  • a circumferential around the extension 32 axial portion of the second holder 30 tapers in steps, wherein the inflow-side end is reduced diameter reducing to a retraction 37 and thereby surrounds the extension 32 radially.
  • the flexible section 25 and thus the compensation chamber 21 or the hydraulic medium located in the compensation chamber 21 is pressurized by a pressure element 28 under a bias.
  • the spiral-shaped and permanently elastic pressure element 28 in the illustrated embodiment presses with one end via an intermediate layer element 31 on the flexible portion 25 from outside the compensation space 21 and supports with the other end on the second holder 30 immovably connected to the second coupler section 24 Indent 37 off.
  • the other end of the pressure element 28 is supported on the first holder 29 that is fixedly connected to the first coupler section 23.
  • the intermediate layer element 31 is annular in this embodiment, surrounds the extension 32 radially and is rounded at the surfaces in contact with the flexible portion 25.
  • the compensation chamber 21 is connected to the hydraulic volume 17 adjacent to the gap 27 by a throttle bore 36 arranged axially in the second coupler section 24.
  • the compensation chamber 21, the gap 27, the opening 34 and the channel 26 are completely filled with the hydraulic medium, which is filled through the channel 26.
  • the channel 26 is closed pressure-tight after filling by a spherical body 35.
  • the valve needle 8 On the discharge side, the valve needle 8 has a valve closing body 7 and engages through a valve seat body 6 arranged at the discharge end of the housing 38.
  • the valve seat body 6 has a centrally disposed injection opening 12 and a valve seat surface 13 which cooperates with the valve closing body 7 to form a sealing seat.
  • the valve needle 8 On the inflow side, the valve needle 8 has a first flange 14. Between the first flange 14 and the valve seat body 6, a first spring element 20 is clamped, which pulls the valve closing body 7 in the sealing seat and how the second spring element 22 is formed spirally.
  • the fuel injection valve 1 opens to the outside.
  • the actuator 2 If the actuator 2 is energized via an electrical line, not shown, it expands quickly. Since the hydraulic medium can not drain fast enough through the gap 27 and the throttle bore 36 from the hydraulic volume 17, the coupler 3 behaves very hard, whereby the length of the actuator 2 acts almost completely on the valve needle 8. The valve needle 8 is moved axially against the biasing force of the first spring element 20 in the discharge direction. As a result, the sealing seat opens and the pressure-fed fuel is sprayed via the injection opening 12 into the combustion chamber, not shown. Slow changes in length of the actuator 2 are compensated by the exchange of hydraulic fluid between the hydraulic volume 17 and the compensation chamber 21.
  • the restoring force of the coupler 3 results from the pressure in the compensation chamber 21 multiplied by the effectively directed towards the actuator 2 surface, the.
  • In the compensation chamber 21 results from the effectively acting on the flexible portion 25 divided spring force of the pressure element pressurized by the hydraulic medium.
  • the invention is not limited to the illustrated embodiments and may, for. B. also be used for inward-opening fuel injectors.

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

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs (WO-A-01/29403).The invention relates to a fuel injection valve according to the preamble of the main claim (WO-A-01/29403).

Koppler, insbesondere hydraulisch arbeitende Koppler in Brennstoffeinspritzventilen mit Piezo-Antrieb, zur Kompensation von temperatur- und druckbedingten Längenänderungen von Bauteilen, insbesondere des Aktors, sowie Längenänderungen aufgrund von Verschleiß, sind aus dem Stand der Technik bekannt.Couplers, in particular hydraulically operating couplers in fuel injection valves with piezo drive, for compensation of temperature and pressure-related changes in length of components, in particular of the actuator, and length changes due to wear, are known from the prior art.

Beispielsweise ist aus der DE 101 37 210 A1 ein Brennstoffeinspritzventil mit einem piezoelektrischen Aktor bekannt, welcher in Wirkverbindung mit einer Ventilnadel steht. Die Ventilnadel weist an ihrem abspritzseitigen Ende einen Ventilschließkörper auf, der mit einer Ventilsitzfläche zu einem Dichtsitz zusammenwirkt. Ein Koppler, welcher zum Ausgleich von Längenänderungen von Bauteilen des Brennstoffeinspritzventils, insbesondere von temperaturbedingten Längenänderungen des Aktors, dient, ist zwischen der Ventilnadel und dem Aktor angeordnet. Der Koppler weist zwei gegeneinander axial bewegliche Abschnitte bzw. Kolben auf, die zwei Ringspalte und ein Hydraulik-Volumen bilden. Die Ringspalte verbinden das Hydraulik-Volumen mit dem brennstoffbefüllten Inneren des Ventilkörpers. Zum Ausgleich von Längenänderungen des Aktors wird Brennstoff über die Ringspalte zu- oder abgegeben. Durch eine um die Ventilnadel spiralförmig herum verlaufende Schließfeder wird die Vorspannung, mit der die beiden Kolben auf das Hydraulik-Volumen wirken, eingestellt.For example, DE 101 37 210 A1 discloses a fuel injection valve with a piezoelectric actuator which is in operative connection with a valve needle. The valve needle has at its discharge end a valve closing body which cooperates with a valve seat surface to a sealing seat. A coupler, which serves to compensate for changes in length of components of the fuel injection valve, in particular temperature-induced changes in length of the actuator, is disposed between the valve needle and the actuator. The coupler has two mutually axially movable sections or pistons, which form two annular gaps and a hydraulic volume. The annular gaps connect the hydraulic volume with the fuel-filled interior of the valve body. To compensate for changes in length of the actuator fuel is added or discharged through the annular gaps. By a spiral around the valve needle extending around the closing spring, the bias voltage with which the two pistons act on the hydraulic volume set.

Nachteilig bei dem obengenannten Stand der Technik ist insbesondere, daß hohe Kopplerinnendrücke nur durch entsprechend hohe Vorspannkräfte erreicht werden können. Bei geringen Kopplerinnendrücken steigt die Kavitationsneigung des verwendeten Hydraulikmediums, starke Vorspannkräfte sind ungünstig für die Ventildynamik und die Einstellgenauigkeit. Außerdem müssen Bauteile größer bemessen werden, um den erhöhten Kräften dauerhaft standzuhalten.A disadvantage of the above-mentioned prior art is in particular that high internal coupler pressures can only be achieved by correspondingly high biasing forces. At low coupler internal pressures, the cavitation tendency of the hydraulic medium used increases, strong preload forces are unfavorable for the valve dynamics and the setting accuracy. In addition, components must be sized larger in order to withstand the increased forces permanently.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß bei relativ niedrigen Vorspannkräften hohe Kopplerinnendrücke erzielt werden können. Die Kavitationsneigung des Hydraulikmediums ist bei gleichzeitiger guter Ventildynamik und geringen Bauteilabmessungen sehr gering. Die Dauerhaltbarkeit und Zuverlässigkeit sowie die Ventildynamik des Brennstoffeinspritzventils werden dadurch ebenfalls verbessert. Außerdem können die Vorspannkräfte genauer und leichter eingestellt werden.The fuel injection valve according to the invention with the features of the main claim has the advantage that at relatively low preload high Kopplerinnendrücke can be achieved. The Kavitationsneigung of the hydraulic medium is very low while good valve dynamics and small component dimensions. The durability and reliability as well as the valve dynamics of the fuel injection valve are thereby also improved. In addition, the preload forces can be adjusted more accurately and easily.

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

In ersten Weiterbildungen des erfindungsgemäßen Brennstoffeinspritzventils ist das Druckelement spiralförmig und dauerelastisch ausgebildet. Das Druckelement kann dadurch vorteilhaft kompakt angeordnet werden und die Vorspannkraft kann dauerhaft konstant halten.In first developments of the fuel injection valve according to the invention, the pressure element is formed spirally and permanently elastic. The pressure element can be advantageously arranged compact and the biasing force can permanently hold constant.

Vorteilhaft ist es zudem, wenn der erste Koppler-Abschnitt und der zweite Koppler-Abschnitt zylinderförmig ausgebildet sind, der Spalt als Ringspalt ausgebildet ist und die Ausnehmung hohlzylindrisch geformt ist. Dadurch läßt sich der Koppler besonders einfach, kompakt und leicht aufbauen.It is also advantageous if the first coupler section and the second coupler section are cylindrical, the gap is formed as an annular gap and the recess is formed as a hollow cylinder. As a result, the coupler can be particularly simple, compact and easy to build.

In einer weiteren Weiterbildungen des erfindungsgemäßen Brennstoffeinspritzventils verjüngt sich der erste Abschnitt in einem zylindrischen Fortsatz vom Hydraulik-Volumen weggerichtet. Auch dadurch ist eine sehr kompakte Bauweise möglich. Insbesondere läßt sich das Druckelement besonders günstig platzieren, wobei es dafür besonders günstig ist, daß sich der Fortsatz zudem durch eine Stufe auf Höhe der Oberkante der Ausnehmung verjüngt und der Fortsatz koaxial zum ersten Abschnitt angeordnet ist.In a further development of the fuel injection valve according to the invention, the first section tapers in a cylindrical extension away from the hydraulic volume. This also makes a very compact design possible. In particular, the pressure element can be placed particularly favorable, wherein it is particularly favorable for the extension also to be tapered by a step at the level of the upper edge of the recess and the extension is arranged coaxially to the first section.

Weiterhin ist es vorteilhaft, wenn der Fortsatz einen axial verlaufenden Kanal aufweist, der über eine dazu mit einem radialen Richtungsanteil verlaufende Öffnung mit dem Ausgleichsraum verbunden ist. Der Koppler läßt sich dadurch in besonders einfacher Weise mit Hydraulikmedium befüllen und durch einen Kugelkörper verschließen.Furthermore, it is advantageous if the extension has an axially extending channel, which is connected via a thereto extending with a radial direction portion opening with the compensation chamber. The coupler can thereby be filled with hydraulic medium in a particularly simple manner and closed by a spherical body.

Wird ein Ende des flexiblen Abschnitts an der radialen Außenfläche des ersten Abschnitts und das andere Ende des flexiblen Abschnitts an der radialen Außenfläche des zweiten Koppler-Abschnitts hermetisch dicht gefügt, kann der Ausgleichsraum besonders einfach gebildet und vorteilhaft platziert werden. Dies läßt sich weiter verbessern, indem ein Ende des flexiblen Abschnitts zwischen dem ersten Abschnitt und dem ersten Halter und/oder das andere Ende des flexiblen Abschnitts zwischen dem zweiten Abschnitt und dem zweiten Halter geklemmt ist.If one end of the flexible portion on the radially outer surface of the first portion and the other end of the flexible portion on the radially outer surface of the second coupler portion hermetically sealed, the compensation space can be particularly easily formed and advantageously placed. This can be further improved by clamping one end of the flexible portion between the first portion and the first holder and / or the other end of the flexible portion between the second portion and the second holder.

Vorteilhaft ist es weiterhin, wenn das Druckelement unter Zwischenlage eines Zwischenlageelements auf den flexiblen Abschnitt drückt. Der im Ausgleichsraum herrschende Druck kann dadurch besonders einfach eingestellt und angepasst werden.It is also advantageous if the pressure element presses with the interposition of an intermediate layer element on the flexible portion. The pressure prevailing in the equalization chamber This makes it particularly easy to set and adjust.

Vorteilhaft ist es zudem, wenn das Zwischenlageelement ringförmig oder lochscheibenförmig ist, wobei die auf dem flexiblen Abschnitt aufliegende Fläche im Querschnitt kreissegmentförmig bzw. abgerundet ist. Der auf den flexiblen Abschnitt wirkende Druck läßt sich dadurch gleichmäßiger verteilen und der Koppler läßt sich kompakter gestalten, wie auch durch die hülsenförmige Ausbildung zumindest einer der Halter.In addition, it is advantageous if the intermediate layer element is annular or perforated disk-shaped, wherein the area resting on the flexible section is circular-segment-shaped or rounded in cross-section. The pressure acting on the flexible portion pressure can thereby distribute more evenly and the coupler can be made more compact, as well as the sleeve-shaped design of at least one of the holders.

Vorteilhafterweise verjüngt sich der zweite Halter stufenförmig. Dadurch ist eine sehr kompakte und einfache Bauweise des Kopplers möglich.Advantageously, the second holder tapers step-like. This makes a very compact and simple construction of the coupler possible.

Weiterhin ist es vorteilhaft, den ersten Halter an seinem dem ersten Abschnitt zugewandten Ende abzurunden. Der flexible Abschnitt wird dadurch weniger belastet und dauerhaltbarer.Furthermore, it is advantageous to round off the first holder at its end facing the first portion. The flexible section is thus less burdened and durable.

In einer weiteren Weiterbildung ist das Hydraulik-Volumen, zusätzlich zum Spalt, mit dem Ausgleichsraum durch zumindest eine Drosselbohrung verbunden. Die hydraulischen Eigenschaften des Kopplers lassen sich dadurch vorteilhaft und einfach beeinflussen und leicht einstellen.In a further development, the hydraulic volume, in addition to the gap, connected to the expansion chamber through at least one throttle bore. The hydraulic properties of the coupler can be characterized advantageous and easy influence and easy to adjust.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigt:

Fig. 1
eine vereinfachte schematische axiale Schnittdarstellung durch das Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils.
An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. It shows:
Fig. 1
a simplified schematic axial sectional view through the embodiment of a fuel injection valve according to the invention.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Nachfolgend wird ein Ausführungsbeispiel der Erfindung beispielhaft beschrieben.Hereinafter, an embodiment of the invention will be described by way of example.

Ein in Fig. 1 in einer axialen Schnittdarstellung gezeigtes erfindungsgemäßes Brennstoffeinspritzventil 1 dient insbesondere zum direkten Einspritzen von Brennstoff in einen Brennraum einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine.An inventive fuel injection valve 1 shown in an axial sectional view in FIG. 1 is used in particular for the direct injection of fuel into a combustion chamber of a mixture-compressing, spark-ignited internal combustion engine.

In einem sich stufenartig nach unten in Abspritzrichtung verjüngenden hohlzylindrischen Ventilgehäuse 38 sind eine Ventilnadel 8, ein Aktor 2 und ein hydraulischer Koppler 3 jeweils zueinander koaxial angeordnet. Oben, zuströmseitig ist das Gehäuse 38 durch einen Gehäusedeckel 4 hermetisch dicht verschlossen. Am Gehäusedeckel 4 stützt sich an der Innenseite der Aktor 2 mit seinem zuströmseitigen Ende ab. Abströmseitig weist der Aktor 2 einen scheibenförmigen Aktorkopf 10 auf. Der Aktorkopf 10 ist in einem hohlzylindrischen Aktormodulgehäuse 9 axial beweglich geführt. Das Aktorgehäuse 5 ist abströmseitig mit der Ventilnadel 8 über einen Wellbalg 39 verbunden, der den Aktorraum 42 hermetisch vom Kraftstoff abdichtet. Ein zweites Federelement 22 ist zwischen dem Aktorkopf 10 und dem zweiten Flansch 15 mit einer Vorspannung eingespannt und hält den Aktorkopf 10 in ständiger Anlage an den Aktor 2.In a hollow cylindrical valve housing 38, which tapers stepwise downward in the direction of discharge, a valve needle 8, an actuator 2 and a hydraulic coupler 3 are arranged coaxially to one another. Above, on the inflow side, the housing 38 is hermetically sealed by a housing cover 4. On the housing cover 4 is supported on the inside of the actuator 2 with its inflow end. On the outflow side, the actuator 2 has a disk-shaped actuator head 10. The actuator head 10 is axially movably guided in a hollow cylindrical actuator module housing 9. The actuator housing 5 is connected downstream of the valve needle 8 via a corrugated bellows 39, which hermetically seals the actuator chamber 42 from the fuel. A second spring element 22 is clamped between the actuator head 10 and the second flange 15 with a bias voltage and holds the actuator head 10 in constant contact with the actuator 2.

Im gezeigten Ausführungsbeispiel ist der hydraulische Koppler 3 zwischen dem Aktor 2 und der Ventilnadel 8 angeordnet, wobei ein erster zylinderförmiger Koppler-Abschnitt 23 zuströmseitig und ein zweiter zylinderförmiger Koppler-Abschnitt 24 abströmseitig angeordnet sind. Der erste im Durchmesser kleinere Koppler-Abschnitt 23 greift in eine koaxial im zweiten Abschnitt 24 zuströmseitig angeordnete hohlzylinderförmige Ausnehmung 16 teilweise ein. Umfänglich des ersten Koppler-Abschnitts 23, zwischen dem ersten und zweiten Koppler-Abschnitt 23, 24, bildet sich dabei ein als Ringspalt ausgeführter Spalt 27 aus. Der Spalt 27 verbindet ein zwischen den sich gegenüberliegenden axialen Innenflächen von erstem und zweitem Koppler-Abschnitt 23, 24 liegendes Hydraulik-Volumen 17 und einen Ausgleichsraum 21.In the illustrated embodiment, the hydraulic coupler 3 is disposed between the actuator 2 and the valve needle 8, wherein a first cylindrical coupler section 23 upstream and a second cylindrical coupler section 24 are arranged downstream. The first smaller diameter coupler section 23 engages in a coaxially in the second section 24 on the upstream side arranged hollow cylindrical recess 16 partially. Surrounding the first coupler section 23, between the first and second coupler sections 23, 24, a gap 27 designed as an annular gap is formed. The gap 27 connects a hydraulic volume 17 lying between the opposing axial inner surfaces of first and second coupler sections 23, 24 and a compensation chamber 21.

Die Größe des Hydraulik-Volumens 17 ist durch die gegeneinander axial verschiebbaren beiden Koppler-Abschnitte 23, 24 variierbar. Der erste Koppler-Abschnitt 23 weist einen koaxial angeordneten zylinderförmigen bzw. stabförmigen Fortsatz 32 auf. Der Fortsatz 32 ist dabei auf der vom Hydraulik-Volumen 17 weggerichteten axialen Seite des ersten Koppler-Abschnitts 23, also zum Aktor 2 hin, angeordnet. Im gezeigten Ausführungsbeispiel verjüngt sich der erste Koppler-Abschnitt 23 durch eine etwa auf Höhe der Oberkante der Ausnehmung 16 liegende Stufe 33 zu dem Fortsatz 32. Ein im Fortsatz 32 axial und koaxial verlaufender Kanal 26, der beispielsweise durch Bohren hergestellt ist, ist durch eine in der Wandung des Fortsatzes 32 angeordnete Öffnung 34 mit dem Ausgleichsraum 21 verbunden. Zuströmseitig greift der Fortsatz 32 bis zum Aktorkopf 10 teilweise in das Aktorgehäuse 9 ein und ist mit dem Aktorkopf 10 gefügt, beispielsweise stoff- oder kraftschlüssig.The size of the hydraulic volume 17 can be varied by the mutually axially displaceable two coupler sections 23, 24. The first coupler section 23 has a coaxially arranged cylindrical or rod-shaped extension 32. In this case, the extension 32 is arranged on the axial side of the first coupler section 23 directed away from the hydraulic volume 17, that is to say towards the actuator 2. In the illustrated embodiment, the first coupler section 23 tapers through a lying approximately at the level of the upper edge of the recess 16 stage 33 to the extension 32. A axially extending coaxially in the extension 32 and channel 26, which is prepared for example by drilling is through a in the wall of the extension 32 arranged opening 34 connected to the compensation chamber 21. On the inflow side of the extension 32 engages the actuator head 10 partially into the actuator housing 9 and is joined to the actuator head 10, for example, material or non-positive.

Ein flexibler Abschnitt 25, der lochscheibenähnlich als Membran ausgebildet ist, sich jedoch an seinen Enden auch axial erstreckt, ist im Bereich seines Außenumfangs an der radialen Außenfläche des zweiten Abschnitts 24 hermetisch dicht gefügt. Im Bereich seines Innenumfangs ist der flexible Abschnitt 25 an der radialen Außenfläche des Fortsatzes 32 hermetisch dicht gefügt, wobei der Fortsatz 32 den flexiblen Abschnitt 25 mittig durchgreift. Der flexible Abschnitt 25, der erste Koppler-Abschnitt 23 mit dem Fortsatz 32 und der zweite Koppler-Abschnitt 24 begrenzen in dieser Weise den Ausgleichsraum 21.A flexible portion 25, which is formed as a membrane-like hole plate, but also extends axially at its ends, is hermetically sealed in the region of its outer periphery on the radially outer surface of the second portion 24. In the region of its inner circumference, the flexible portion 25 is hermetically sealed to the radially outer surface of the extension 32, wherein the extension 32 passes through the flexible portion 25 in the center. The flexible portion 25, the first coupler portion 23 with the extension 32 and the second coupler portion 24 limit in this way the compensation space 21st

Ein erster hülsenförmiger Halter 29 ist über den Fortsatz 32 gestülpt und klemmt den flexiblen Abschnitt 25 im Bereich seines Innenumfangs zwischen sich und dem Fortsatz 32 form- und/oder kraftschlüssig und hermetisch dicht fest. Das dem flexiblen Abschnitt 25 zugewandte und an ihm aufliegende Ende des ersten Halters 29 ist abgerundet. Der erste Halter 29 ist bewegungsfest mit dem Fortsatz 32 beispielsweise durch eine Schweißung verbunden.A first sleeve-shaped holder 29 is slipped over the extension 32 and clamps the flexible portion 25 in the region of its inner circumference between itself and the extension 32 form-fitting. and / or non-positively and hermetically tight. The flexible section 25 facing and resting on it end of the first holder 29 is rounded. The first holder 29 is immovably connected to the extension 32, for example by a weld.

Ein zweiter hülsenförmiger Halter 30 umgreift mit einem abströmseitigen axialen Teilabschnitt den zweiten Koppler-Abschnitt 24 und ist hier mit der radialen Außenfläche des zweiten Koppler-Abschnitts 24 beispielsweise durch eine Schweißung gefügt. Der Bereich des Außenumfangs des flexiblen Abschnitts 25 ist zwischen dem abströmseitigen axialen Teilabschnitt des zweiten Halters 30 und dem zweiten Koppler-Abschnitt 24 hermetisch dicht geklemmt. Ein um den Fortsatz 32 umlaufender axialer Teilbereich des zweiten Halter 30 verjüngt sich stufenförmig, wobei das zuströmseitige Ende durchmesserverkleinernd zu einem Einzug 37 eingezogen ist und dabei den Fortsatz 32 radial umgibt.A second sleeve-shaped holder 30 engages with a downstream axial portion of the second coupler portion 24 and here is joined to the radial outer surface of the second coupler portion 24, for example by welding. The portion of the outer periphery of the flexible portion 25 is hermetically clamped between the downstream axial portion of the second holder 30 and the second coupler portion 24. A circumferential around the extension 32 axial portion of the second holder 30 tapers in steps, wherein the inflow-side end is reduced diameter reducing to a retraction 37 and thereby surrounds the extension 32 radially.

Der flexible Abschnitt 25 und damit der Ausgleichsraum 21 bzw. das im Ausgleichsraum 21 befindliche Hydraulikmedium ist durch ein unter einer Vorspannung stehendes Druckelement 28 mit Druck beaufschlagt. Das im gezeigten Ausführungsbeispiel spiralförmige und dauerelastische Druckelement 28 drückt mit einem Ende über ein Zwischenlageelement 31 auf den flexiblen Abschnitt 25 von außerhalb des Ausgleichsraums 21 und stützt sich dabei mit dem anderen Ende an dem mit dem zweiten Koppler-Abschnitt 24 bewegungsfest verbundenen zweiten Halter 30 am Einzug 37 ab. In anderen Ausführungsbeispielen stützt sich das andere Ende des Druckelements 28 am mit dem ersten Koppler-Abschnitt 23 bewegungsfest verbundenen ersten Halter 29 ab.The flexible section 25 and thus the compensation chamber 21 or the hydraulic medium located in the compensation chamber 21 is pressurized by a pressure element 28 under a bias. The spiral-shaped and permanently elastic pressure element 28 in the illustrated embodiment presses with one end via an intermediate layer element 31 on the flexible portion 25 from outside the compensation space 21 and supports with the other end on the second holder 30 immovably connected to the second coupler section 24 Indent 37 off. In other exemplary embodiments, the other end of the pressure element 28 is supported on the first holder 29 that is fixedly connected to the first coupler section 23.

Das Zwischenlageelement 31 ist in diesem Ausführungsbeispiel ringförmig, umgibt den Fortsatz 32 radial und ist an den mit dem flexiblen Abschnitt 25 berührenden Flächen abgerundet.The intermediate layer element 31 is annular in this embodiment, surrounds the extension 32 radially and is rounded at the surfaces in contact with the flexible portion 25.

Der Ausgleichsraum 21 ist neben dem Spalt 27 durch eine axial im zweiten Koppler-Abschnitt 24 angeordnete Drosselbohrung 36 mit dem Hydraulik-Volumen 17 verbunden.The compensation chamber 21 is connected to the hydraulic volume 17 adjacent to the gap 27 by a throttle bore 36 arranged axially in the second coupler section 24.

Der Ausgleichsraum 21, der Spalt 27, die Öffnung 34 und der Kanal 26 sind vollständig mit dem Hydraulikmedium gefüllt, welches durch den Kanal 26 eingefüllt ist. Der Kanal 26 ist nach dem Einfüllen durch einen Kugelkörper 35 druckfest verschlossen.The compensation chamber 21, the gap 27, the opening 34 and the channel 26 are completely filled with the hydraulic medium, which is filled through the channel 26. The channel 26 is closed pressure-tight after filling by a spherical body 35.

Abspritzseitig weist die Ventilnadel 8 einen Ventilschließkörper 7 auf und greift durch einen am abspritzseitigen Ende des Gehäuses 38 angeordneten Ventilsitzkörper 6. Der Ventilsitzkörper 6 weist eine zentriert angeordnete Abspritzöffnung 12 und eine Ventilsitzfläche 13 auf, die mit dem Ventilschließkörper 7 zu einem Dichtsitz zusammenwirkt. Zuströmseitig weist die Ventilnadel 8 einen ersten Flansch 14 auf. Zwischen dem ersten Flansch 14 und dem Ventilsitzkörper 6 ist ein erstes Federelement 20 eingespannt, das den Ventilschließkörper 7 in den Dichtsitz zieht und wie das zweite Federelement 22 spiralförmig ausgebildet ist. Das Brennstoffeinspritzventil 1 öffnet nach außen.On the discharge side, the valve needle 8 has a valve closing body 7 and engages through a valve seat body 6 arranged at the discharge end of the housing 38. The valve seat body 6 has a centrally disposed injection opening 12 and a valve seat surface 13 which cooperates with the valve closing body 7 to form a sealing seat. On the inflow side, the valve needle 8 has a first flange 14. Between the first flange 14 and the valve seat body 6, a first spring element 20 is clamped, which pulls the valve closing body 7 in the sealing seat and how the second spring element 22 is formed spirally. The fuel injection valve 1 opens to the outside.

Wird der Aktor 2 über eine nicht dargestellte elektrische Leitung erregt, so dehnt er sich schnell aus. Da das Hydraulikmedium nicht schnell genug durch den Spalt 27 und die Drosselbohrung 36 aus dem Hydraulik-Volumen 17 abfließen kann, verhält sich der Koppler 3 sehr hart, wodurch die Längenausdehnung des Aktors 2 fast vollständig auf die Ventilnadel 8 wirkt. Die Ventilnadel 8 wird entgegen der Vorspannkraft des ersten Federelements 20 axial in Abspritzrichtung bewegt. Dadurch öffnet der Dichtsitz und der druckbehaftet zugeleitete Brennstoff wird über die Abspritzöffnung 12 in den nicht dargestellten Brennraum abgespritzt. Langsame Längenänderungen des Aktors 2 werden durch den Austausch von Hydraulikmedium zwischen dem Hydraulik-Volumen 17 und dem Ausgleichsraum 21 ausgeglichen.If the actuator 2 is energized via an electrical line, not shown, it expands quickly. Since the hydraulic medium can not drain fast enough through the gap 27 and the throttle bore 36 from the hydraulic volume 17, the coupler 3 behaves very hard, whereby the length of the actuator 2 acts almost completely on the valve needle 8. The valve needle 8 is moved axially against the biasing force of the first spring element 20 in the discharge direction. As a result, the sealing seat opens and the pressure-fed fuel is sprayed via the injection opening 12 into the combustion chamber, not shown. Slow changes in length of the actuator 2 are compensated by the exchange of hydraulic fluid between the hydraulic volume 17 and the compensation chamber 21.

Der Druck im Ausgleichsraum 21 ergibt sich dabei aus der durch die effektiv auf den flexiblen Abschnitt 25 wirkende geteilte Federkraft des Druckelements 28. Die Rückstellkraft des Kopplers 3 ergibt sich aus dem Druck im Ausgleichsraum 21 multipliziert mit der effektiv zum Aktor 2 hin gerichteten Fläche, die mit Druck durch das Hydraulikmedium beaufschlagt ist.The restoring force of the coupler 3 results from the pressure in the compensation chamber 21 multiplied by the effectively directed towards the actuator 2 surface, the. In the compensation chamber 21 results from the effectively acting on the flexible portion 25 divided spring force of the pressure element pressurized by the hydraulic medium.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und kann z. B. auch für nach innen öffnende Brennstoffeinspritzventile verwendet werden.The invention is not limited to the illustrated embodiments and may, for. B. also be used for inward-opening fuel injectors.

Claims (18)

  1. Fuel injection valve (1), in particular for the direct injection of fuel into a combustion space of an internal combustion engine, with a piezoelectric, electrostrictive or magnetostrictive actuator (2), with a valve-closing body (7) which is operatively connected to the actuator (2) and co-operates with a valve-seat surface (13) to form a sealing seat, and with a coupler (3) which has a first coupler portion (23) and a second coupler portion (24), the first coupler portion (23) engaging axially displaceably into a recess (16) of the second coupler portion (24), so as to maintain a gap (27) designed as a throttle point and so as to form hydraulic volume (17), and the two coupler portions (23, 24) being operatively connected via a hydraulic medium, and the gap (27) connecting the hydraulic volume (17) to a compensation space (21), characterized in that the compensation space (21) is delimited by the first and the second coupler portion (23, 24) and a flexible portion (25), and the flexible portion (25) is acted upon with pressure by one end of a pressure element (28), the other end of the pressure element (28) being supported on a first holder (29), which is connected to the first coupler portion (23), or on a second holder (30), which is connected to the second coupler portion (24).
  2. Fuel injection valve according to Claim 1, characterized in that the pressure element (28) is of helical design.
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the pressure element (28) is permanently elastic.
  4. Fuel injection valve according to one of the preceding claims, characterized in that the first coupler portion (23) and the second coupler portion (24) are of cylindrical design and the gap (27) is designed as an annular gap, the recess (16) being of hollow-cylindrical shape.
  5. Fuel injection valve according to Claim 4, characterized in that the first coupler portion (23) narrows in the axial direction pointing away from the hydraulic volume (17), to form a cylindrical extension (32).
  6. Fuel injection valve according to Claim 5, characterized in that the first coupler portion (23) narrows, level with a top edge of the recess (16), by means of a step (33), to form the cylindrical extension (32).
  7. Fuel injection valve according to Claim 5 or 6, characterized in that the extension (32) is arranged coaxially with respect to the first coupler portion (23) .
  8. Fuel injection valve according to one of Claims 5 to 7, characterized in that the extension (32) has an axially running duct (26) which is connected, via an orifice (34) running in relation to the latter with a radial direction fraction, to the compensation space (21).
  9. Fuel injection valve according to Claim 8, characterized in that the duct (26) is closed by means of a spherical body (35).
  10. Fuel injection valve according to one of Claims 5 to 9, characterized in that the flexible portion (25) is designed as a diaphragm and is in the form of a perforated disc or of a hose.
  11. Fuel injection valve according to Claim 10, characterized in that in each case one end of the flexible portion (25) is joined in a hermetically sealed manner to the radial outer surface of the first coupler portion (23) and to the second coupler portion (24).
  12. Fuel injection valve according to Claim 11, characterized in that one end of the flexible portion (25) is clamped between the first coupler portion (24) and the first holder (29) and/or the other end of the flexible portion (25) is clamped between the second coupler portion (24) and the second holder (30).
  13. Fuel injection valve according to one of the preceding claims, characterized in that the pressure element (28) presses onto the flexible portion (25), with an intermediate element (31) being interposed.
  14. Fuel injection valve according to Claim 13, characterized in that the intermediate element (31) is annular and/or is in the form of a perforated disc, that surface of the intermediate element (31) which lies on the flexible portion (25) being in the form of a segment of a circle and/or being rounded.
  15. Fuel injection valve according to one of the preceding claims, characterized in that at least one of the holders (29, 30) is of sleeve-shaped design.
  16. Fuel injection valve according to one of the preceding claims, characterized in that the second holder (30) narrows in the form of a step.
  17. Fuel injection valve according to one of the preceding claims, characterized in that the first holder (29) is rounded at an end facing the flexible portion (25).
  18. Fuel injection valve according to one of the preceding claims, characterized in that the hydraulic volume (17) is connected to the compensation space (21) by means of at least one throttle bore.
EP20040105054 2003-12-15 2004-10-14 Fuel injection valve Expired - Fee Related EP1544454B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10358723 2003-12-15
DE2003158723 DE10358723A1 (en) 2003-12-15 2003-12-15 Fuel injector

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EP1544454B1 true EP1544454B1 (en) 2007-01-24

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007053426A1 (en) * 2007-11-09 2009-05-14 Robert Bosch Gmbh Piezoelectric actuator module
WO2011045298A1 (en) * 2009-10-12 2011-04-21 Ulrich Stieler Kunststoff Service E.K. Fluid injector

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0656162B2 (en) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 Variable stroke device
DE4306072C2 (en) * 1993-02-26 1994-12-08 Siemens Ag Device for opening and closing a passage opening in a housing
DE19708304C2 (en) * 1997-02-28 1999-09-30 Siemens Ag Movement transmission device and injection valve with a movement transmission device
DE19940054C2 (en) * 1999-08-24 2003-11-27 Siemens Ag Dosing valve for a pressurized fluid
DE19950760A1 (en) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Fuel injection valve esp. for fuel injection systems of IC engines with piezo-electric or magneto-strictive actuator and valve closing body operable by valve needle working with valve
DE19959704A1 (en) * 1999-12-10 2001-06-21 Tenovis Gmbh & Co Kg Processes for processing data packets
DE19962177A1 (en) * 1999-12-22 2001-07-12 Siemens Ag Hydraulic device for transmitting an actuator movement
DE10162045B4 (en) * 2001-12-17 2005-06-23 Siemens Ag Device for translating a deflection of an actuator, in particular for an injection valve

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DE502004002759D1 (en) 2007-03-15
DE10358723A1 (en) 2005-07-07

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