EP1491760B1 - Fuel injector - Google Patents

Fuel injector Download PDF

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Publication number
EP1491760B1
EP1491760B1 EP20040009262 EP04009262A EP1491760B1 EP 1491760 B1 EP1491760 B1 EP 1491760B1 EP 20040009262 EP20040009262 EP 20040009262 EP 04009262 A EP04009262 A EP 04009262A EP 1491760 B1 EP1491760 B1 EP 1491760B1
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EP
European Patent Office
Prior art keywords
injection valve
fuel injection
fuel
valve according
flexible
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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EP20040009262
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German (de)
French (fr)
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EP1491760A1 (en
Inventor
Dietmar Schmieder
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • From DE 199 54 537 A1 discloses a fuel injection valve with an actuating strand with an actuator, a valve needle, a hydraulic conversion device and a return spring, which actuate a valve closing body known.
  • the conversion device is used to implement a small Aktorhubs to a larger valve needle and to compensate for different, temperature-induced changes in length of components.
  • On the outflow side and on the upstream side of the actuator in each case at least one flexible section is arranged, which compensates for relative movements of the valve needle relative to the actuator or other components and keeps fuel away from the actuator. Due to the corrugated pipe-shaped design of the flexible sections is to prevent the one side acted upon by fuel with fuel pressure flexible portions exert axial forces on the actuation strand.
  • a disadvantage of this known prior art is that the flexible portions acting as a seal very need to be prepared consuming to achieve a satisfactory fatigue strength.
  • they in order to withstand the radially acting forces of fuel pressure, they must also have a corresponding radial stiffness.
  • This radial rigidity further increases the production costs and the production costs and has an unfavorable effect on the valve dynamics due to the associated axial rigidity. The space of such seals and the surface acted upon by the fuel pressure is increased.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that can be dispensed with unfavorably large, error-prone, the valve dynamics negatively influencing and consuming produced flexible sections or seals.
  • the manufacturing cost of the fuel injection valve is thereby substantially reduced, the size can be reduced without functional losses and the reliability of the fuel injection valve is increased.
  • the forces of fuel pressure acting in opposite axial directions can be advantageously used to assist or take over operations in the fuel injector.
  • a spring element biasing the actuator alone which extends, for example, as a Bourdon tube around the actuator, can be dimensioned with a lesser pretensioning force or, if appropriate, can be dispensed with altogether.
  • the actuator module can thus be more easily assembled and mounted.
  • the actuation strand has a hydraulic coupler for compensating temperature-induced changes in length of the actuator and / or other components and / or for Hubuma, wherein the coupler is arranged on the inflow side of the actuator in a further development.
  • the fuel injection valve can be designed particularly reliable and easy to set up.
  • the coupler cylinder can thus be arranged in a particularly simple manner, for example in the valve housing.
  • the hydraulic coupler has a compensation chamber, a leakage gap and a membrane space, the leakage gap connecting the compensation chamber with the membrane space, then the hydraulic coupler is constructed in a particularly simple manner.
  • the hydraulic coupler is completely filled with a hydraulic medium and a third flexible section separates the hydraulic medium from fuel.
  • the coupler can thus be designed in particular durable and reliable, since the properties of the hydraulic medium can be largely selected independently of the choice of fuel. As a result, for example, the viscosity and the lubricating properties of the hydraulic medium can be freely selected.
  • the third flexible portion is designed so that it transmits the fuel pressure applied to it on one side for the most part to the hydraulic medium.
  • the fuel pressure can be used in a particularly simple and advantageous manner to keep the expansion chamber filled with hydraulic fluid.
  • the flexible portions are perforated plate-shaped and formed in cross-section substantially U-shaped.
  • the flexibility will increased, thereby the flexible sections can be easily joined and are easy to manufacture.
  • the fuel injection valve can be made particularly compact.
  • the individual flexible sections are connected via flanges to the actuation line.
  • the flexible sections can be particularly easily connected to the actuation strand.
  • the first flexible portion and the second flexible portion are arranged so that the medium and directly acting on the valve closing body fuel pressure in terms of power, in the axial direction of the actuation strand, picks up. Due to the hydraulic force compensation achieved in this way, in particular the spring force of a biasing spring acting on the actuation strand can be selected to be much smaller. Due to the reduced spring force acting opposite to the confirmation direction of the actuator biasing spring, a smaller and less expensive actuator can be used. The power requirement of the actuator is reduced and the heat development in the actuator and in the control unit are reduced.
  • the coupler Due to the reduced spring force acting on the coupler, the coupler can very quickly compensate for temperature-related linear expansion even in cold start phases in which the valve opening times are generally extended, thereby also allowing cold start phases with reduced fuel pressure.
  • the fuel injection valve 1 according to the invention shown schematically in Fig. 1 is particularly suitable as a fuel injection valve 1 for fuel injection systems for mixture-compressing, spark-ignited internal combustion engines for direct injection of fuel into the combustion chamber of the internal combustion engine.
  • the fuel injection valve 1 comprises in particular a piezoelectric, magnetostrictive or electrostrictive actuator 2, which is arranged in an actuator module 22.
  • the actuator 2 or the actuator module 22 is part of a confirmation string, which in this embodiment also has a hydraulic coupler 3 arranged on the inflow side of the actuator module 22 and a valve needle 4 arranged downstream of the actuator module 22.
  • the actuator module 22, the hydraulic coupler 3 and the valve needle 4 are arranged coaxially in a valve housing 6.
  • the valve housing 6 has at its downstream end a nozzle body 5, through which the valve needle 4 coaxially engages and at its downstream end an integrally formed with the nozzle body 5 valve seat body 10 having a spray opening 7 is arranged.
  • a valve seat surface 9 formed on the valve seat body 10 cooperates with a valve closing body 8 formed on the discharge end of the valve needle 4 to form a sealing seat.
  • the fuel injection valve 1 opens to the outside.
  • the valve housing 6 On the inflow side, the valve housing 6 has a valve top 33.
  • the upper valve part 33 is hermetically sealed on the inflow-side end of the valve housing 6 with a first shoulder 34, where it is joined to the valve housing 6, for example by a material fit, and engages with its downstream end into the valve housing 6.
  • Coaxially formed in the upper valve part 33 is a coupler cylinder 23 which is open towards the actuator module 22 and into which a compensating piston 21 engages.
  • the side of the balance piston 21 is located between the balance piston 21 and the coupler cylinder 23, a leakage gap 24.
  • the leakage gap 24 connects a top formed between the coupler cylinder 23 and the balance piston 21 equalization chamber 31 and a bottom, the actuator module 22 oriented toward the membrane space 32nd Die Membranraum 32nd is completed by a third flexible portion 28 downstream or sealed.
  • the membrane-like and hole-plate-shaped third flexible section 28 in the exemplary embodiment is hermetically sealed in the region of the outer circumference with the downstream end of the valve top part 33 engaging below a diameter-reducing second shoulder 35, for example by welding or other cohesive joining methods.
  • the third flexible section 28 is joined hermetically sealed and cohesively on the compensating piston 21, which tapers toward the actuator module 22 and passes through the third flexible section 28.
  • the steel or a steel government existing third flexible section 28 in cross-section on a U-shaped, or wave-shaped course is thereby not claimed to train, but advantageously to bending.
  • the coupler cylinder 23, the balance piston 21, the compensation chamber 31, the leakage gap 24 and the diaphragm space 32 in this embodiment form the hydraulic coupler 3.
  • the hydraulic coupler 3, or the compensation chamber 31, the leakage gap 24 and the diaphragm space 32 are completely with a Hydraulic medium 30 filled.
  • the hydraulic medium 30 is in this embodiment, a good heat-conducting and highly viscous oil.
  • an electrical connection 15 and a fuel inlet 16 which divides into a first fuel channel 17 and a second fuel channel 18.
  • the electrical connection 15 extends further in the valve housing 6 in order to enter the height of the actuator module 22 in this.
  • a hole-plate-shaped first flexible section 25 of substantially U-shaped design and consisting of steel is joined to its outer circumference with a material fit and hermetically sealed.
  • this is on the upper side of a third flange 29, which surrounds the diameter-tapered, downstream end of the balance piston 21, cohesively and hermetically sealed.
  • the third flange 29 engages with its downstream end in a arranged in the top of the actuator module 22 in an actuator base 13 conical recess 27 with which he is ideally in constant contact.
  • annular groove 36 is arranged.
  • the space located between the first flexible section 25 and the third flexible section 28 is completely filled with fuel via the first fuel channel 17.
  • the fuel presses in each case on one side of the first flexible portion 25 and third flexible portion 28.
  • Fuel pressure acts in this way on the compared to the first flexible portion 25 softer, in particular thinner, third flexible portion 28 on the hydraulic medium 30.
  • the between the The third flexible portion 28 and the first flexible portion 25 prevailing fuel pressure also acts on the first flexible portion 25 so that the actuator module 22 is loaded from above via the third flange 29 on the actuator base 13 with a force acting in the ejection direction bias.
  • the valve needle 4 is biased by a biasing spring 11, which acts on the valve needle 4 via a second flange 20, against the discharge direction.
  • the valve closing body 8 is thereby pulled into the sealing seat and the conically shaped, inflow-side end of the valve needle 4 is pressed into a second recess 37 arranged in an actuator head 12.
  • a first flange 19 is materially connected, for example by welding, with the valve needle 4.
  • a second flexible portion 26 with the underside of the first flange 19 is firmly bonded and hermetically sealed. In the region of the outer periphery of the second flexible portion 26, this is connected to the nozzle body 5 cohesively and hermetically sealed.
  • the second flexible portion 26 may be joined in the region of its outer periphery with the valve housing 6.
  • the one-sided to the second flexible section 26 acting fuel pressure pushes the valve needle 4 in the axial direction to the actuator module 22 through the first flange 19, against the Abspritzraum.
  • a belonging to the actuator module 22 spring element 14 biases the actuator foot 13 against the actuator head 12, so that the actuator 2 is under bias.
  • the actuator 2 If the actuator 2 is excited via the electrical connection 15, then it expands in the axial direction and acts on the compensating piston 21 via the actuator foot 13. Due to the speed of movement of the actuator 2 and the relatively narrow leakage gap 24, the hydraulic medium 30 behaves similar to a solid. The changes in length of the actuator 2 can be transmitted almost completely to the valve needle 4, whereby the valve closing body 8 lifts off from the valve seat surface 9 and fuel is injected into the combustion chamber, not shown, of the internal combustion engine, not shown. During slow movements of the actuator 2, for example due to thermal influences, the hydraulic medium 30 is displaced through the leakage gap 24 into the membrane space 32, whereby an arbitrary opening of the fuel injection valve 1 is prevented.
  • the first flexible portion 25 and the second flexible portion 26 are dimensioned and arranged so that the forces of the fuel pressure acting axially, indirectly and directly on the valve closing body 8 cancel each other out substantially.
  • the fuel injection valve 1 can thereby be operated at different fuel pressures without, for example, the spring force of the biasing spring 11 must be made adaptive by consuming measures.
  • FIG. 2 shows a schematic illustration of a second exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the actuator head 12, similar to the first exemplary embodiment from FIG There is no difference between the third flexible section 28 used in the first exemplary embodiment.
  • the fuel passed through the first fuel channel 17 and the annular groove 36 fills the hydraulic coupler 3, with which the hydraulic medium 30 consists of fuel.
  • the structure of the fuel injection valve 1 is thereby simplified.

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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.The invention relates to a fuel injection valve according to the preamble of the main claim.

Aus der DE 199 54 537 A1 ist ein Brennstoffeinspritzventil mit einem Betätigungsstrang mit einem Aktor, einer Ventilnadel, einer hydraulische Umsetzeinrichtung und einer Rückstellfeder, die einen Ventilschließkörper betätigen, bekannt. Die Umsetzeinrichtung dient der Umsetzung eines kleinen Aktorhubs auf einen größeren Ventilnadelhub und zum Ausgleich von unterschiedlichen, temperaturbedingten Längenänderungen von Bauteilen. Abströmseitig und zuströmseitig des Aktors ist jeweils zumindest ein flexibler Abschnitt angeordnet, der Relativbewegungen der Ventilnadel gegenüber dem Aktor oder anderen Bauteilen ausgleicht und Brennstoff vom Aktor fernhält. Durch die wellrohrförmige Ausbildung der flexiblen Abschnitte soll verhindert werden, daß die einseitig von Brennstoff mit Brennstoffdruck beaufschlagten flexiblen Abschnitte axiale Kräfte am Betätigungsstrang ausüben.From DE 199 54 537 A1 discloses a fuel injection valve with an actuating strand with an actuator, a valve needle, a hydraulic conversion device and a return spring, which actuate a valve closing body known. The conversion device is used to implement a small Aktorhubs to a larger valve needle and to compensate for different, temperature-induced changes in length of components. On the outflow side and on the upstream side of the actuator, in each case at least one flexible section is arranged, which compensates for relative movements of the valve needle relative to the actuator or other components and keeps fuel away from the actuator. Due to the corrugated pipe-shaped design of the flexible sections is to prevent the one side acted upon by fuel with fuel pressure flexible portions exert axial forces on the actuation strand.

Nachteilig an diesem bekannten Stand der Technik ist, daß die als Dichtung wirkenden flexiblen Abschnitte sehr aufwendig hergestellt werden müssen, um eine befriedigende Dauerfestigkeit zu erreichen. Um den radial wirkenden Kräften des Brennstoffdrucks standzuhalten, müssen sie jedoch auch eine entsprechende radial Steifigkeit aufweisen. Diese radiale Steifigkeit erhöht den Fertigungsaufwand und die Fertigungskosten weiter und wirkt auf die Ventildynamik, durch die einhergehende axiale Steifigkeit, unvorteilhaft. Der Bauraum solcher Dichtungen und die vom Brennstoffdruck beaufschlagte Oberfläche ist erhöht.A disadvantage of this known prior art is that the flexible portions acting as a seal very need to be prepared consuming to achieve a satisfactory fatigue strength. However, in order to withstand the radially acting forces of fuel pressure, they must also have a corresponding radial stiffness. This radial rigidity further increases the production costs and the production costs and has an unfavorable effect on the valve dynamics due to the associated axial rigidity. The space of such seals and the surface acted upon by the fuel pressure is increased.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß auf unvorteilhaft große, fehleranfällige, die Ventildynamik negativ beeinflussende und aufwendig hergestellte flexible Abschnitte bzw. Dichtungen verzichtet werden kann. Der Herstellungsaufwand des Brennstoffeinspritzventils ist dadurch wesentlich reduziert, die Baugröße kann ohne funktionelle Einbußen verringert werden und die Zuverlässigkeit des Brennstoffeinspritzventils ist erhöht. Darüber hinaus können die in entgegengesetzten axialen Richtungen wirkenden Kräfte des Brennstoffdrucks vorteilhaft zur Unterstützung oder Übernahme von Funktionsvorgängen im Brennstoffeinspritzventil genutzt werden.The fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that can be dispensed with unfavorably large, error-prone, the valve dynamics negatively influencing and consuming produced flexible sections or seals. The manufacturing cost of the fuel injection valve is thereby substantially reduced, the size can be reduced without functional losses and the reliability of the fuel injection valve is increased. In addition, the forces of fuel pressure acting in opposite axial directions can be advantageously used to assist or take over operations in the fuel injector.

Insbesondere kann ein den Aktor alleinig vorspannendes Federelement, das beispielsweise als Rohrfeder um den Aktor verläuft, mit geringerer Vorspannkraft dimensioniert werden oder ggf. ganz entfallen. Das Aktormodul kann damit einfacher aufgebaut und montiert werden.In particular, a spring element biasing the actuator alone, which extends, for example, as a Bourdon tube around the actuator, can be dimensioned with a lesser pretensioning force or, if appropriate, can be dispensed with altogether. The actuator module can thus be more easily assembled and mounted.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous refinements and improvements of the main claim fuel injector are possible.

In einer ersten Weiterbildung weist der Betätigungsstrang einen hydraulischen Koppler zum Ausgleich von temperaturbedingten Längenänderungen des Aktors und/oder anderer Bauteile und/oder zur Hubumsetzung auf, wobei der Koppler in einer weiteren Weiterbildung zuströmseitig des Aktors angeordnet ist. Das Brennstoffeinspritzventil kann dadurch besonders zuverlässig gestaltet und einfach aufgebaut werden. Insbesondere kann so der Kopplerzylinder in besonders einfacher Weise beispielsweise im Ventilgehäuse angeordnet werden.In a first development, the actuation strand has a hydraulic coupler for compensating temperature-induced changes in length of the actuator and / or other components and / or for Hubumsetzung, wherein the coupler is arranged on the inflow side of the actuator in a further development. The fuel injection valve can be designed particularly reliable and easy to set up. In particular, the coupler cylinder can thus be arranged in a particularly simple manner, for example in the valve housing.

Weist der hydraulische Koppler einen Ausgleichsraum, einen Leckagespalt und einen Membranraum auf, wobei der Leckagespalt den Ausgleichsraum mit dem Membranraum verbindet, so ist der hydraulische Koppler in besonders einfache Weise aufgebaut.If the hydraulic coupler has a compensation chamber, a leakage gap and a membrane space, the leakage gap connecting the compensation chamber with the membrane space, then the hydraulic coupler is constructed in a particularly simple manner.

Vorteilhafterweise ist der hydraulische Koppler vollständig mit einem Hydraulikmedium gefüllt und ein dritter flexibler Abschnitt trennt bzw. dichtet das Hydraulikmedium von Brennstoff ab. Der Koppler kann dadurch insbesondere langlebiger und zuverlässiger gestaltet werden, da die Eigenschaften des Hydraulikmedium weitgehend unabhängig von der Wahl des Brennstoffes gewählt werden können. Dadurch können beispielsweise die Viskosität und die Schmiereigenschaften des Hydraulikmediums frei gewählt werden.Advantageously, the hydraulic coupler is completely filled with a hydraulic medium and a third flexible section separates the hydraulic medium from fuel. The coupler can thus be designed in particular durable and reliable, since the properties of the hydraulic medium can be largely selected independently of the choice of fuel. As a result, for example, the viscosity and the lubricating properties of the hydraulic medium can be freely selected.

Vorteilhafterweise ist der dritte flexible Abschnitt so gestaltet, daß er den an ihm einseitig anliegenden Brennstoffdruck zum größten Teil an das Hydraulikmedium überträgt. Der Brennstoffdruck kann so in besonders einfacher und vorteilhafterweise dazu benutzt werden, den Ausgleichsraum mit Hydraulikmedium gefüllt zu halten.Advantageously, the third flexible portion is designed so that it transmits the fuel pressure applied to it on one side for the most part to the hydraulic medium. The fuel pressure can be used in a particularly simple and advantageous manner to keep the expansion chamber filled with hydraulic fluid.

In einer weiteren Weiterbildung sind die flexiblen Abschnitte lochplattenförmig und im Querschnitt im wesentlichen U-förmig ausgebildet. Die Flexibilität wird dadurch gesteigert, die flexiblen Abschnitte können dadurch einfacher gefügt werden und sind einfach herzustellen.In a further development, the flexible portions are perforated plate-shaped and formed in cross-section substantially U-shaped. The flexibility will increased, thereby the flexible sections can be easily joined and are easy to manufacture.

Greift der Betätigungsstrang durch zumindest einen der flexiblen Abschnitte, so kann das Brennstoffeinspritzventil besonders kompakt hergestellt werden.If the actuation strand engages through at least one of the flexible sections, the fuel injection valve can be made particularly compact.

Vorteilhafterweise stehen die einzelnen flexible Abschnitte über Flansche mit dem Betätigungsstrang in Verbindung. Die flexible Abschnitte können dadurch besonders einfach mit dem Betätigungsstrang verbunden werden. Insbesondere die Sicherheit und Langlebigkeit der Fügeverbindung zwischen den flexiblen Abschnitten und dem Betätigungsstrang, sowie die Montagefreundlichkeit der flexiblen Abschnitte, ist dadurch gesteigert.Advantageously, the individual flexible sections are connected via flanges to the actuation line. The flexible sections can be particularly easily connected to the actuation strand. In particular, the safety and longevity of the joint connection between the flexible sections and the actuation strand, as well as the ease of installation of the flexible sections, thereby increased.

Vorteilhafterweise sind der erste flexible Abschnitt und der zweite flexible Abschnitt so angeordnet, daß der mittel- und unmittelbar auf den Ventilschließkörper wirkende Brennstoffdruck sich kräftemäßig, in axialer Richtung des Betätigungsstrangs, aufhebt. Durch den dadurch erzielten hydraulischen Kraftausgleich kann insbesondere die Federkraft einer auf den Betätigungsstrang wirkende Vorspannfeder wesentlich kleiner gewählt werden. Durch die verringerte Federkraft der entgegen der Bestätigungsrichtung des Aktors wirkenden Vorspannfeder kann ein kleinerer und kostengünstigerer Aktor verwendet werden. Der Leistungsbedarf des Aktors ist verringert und die Wärmeentwicklung im Aktor und im Steuergerät sind vermindert.Advantageously, the first flexible portion and the second flexible portion are arranged so that the medium and directly acting on the valve closing body fuel pressure in terms of power, in the axial direction of the actuation strand, picks up. Due to the hydraulic force compensation achieved in this way, in particular the spring force of a biasing spring acting on the actuation strand can be selected to be much smaller. Due to the reduced spring force acting opposite to the confirmation direction of the actuator biasing spring, a smaller and less expensive actuator can be used. The power requirement of the actuator is reduced and the heat development in the actuator and in the control unit are reduced.

Durch die auf den Koppler wirkende verringerte Federkraft kann der Koppler auch in Kaltstartphasen, bei denen in der Regel die Ventilöffnungszeiten verlängert sind, sehr schnell temperaturbedingte Längenausdehnungen kompensieren, wodurch auch eine Kaltstartphasen mit reduziertem Brennstoffdruck ermöglicht wird.Due to the reduced spring force acting on the coupler, the coupler can very quickly compensate for temperature-related linear expansion even in cold start phases in which the valve opening times are generally extended, thereby also allowing cold start phases with reduced fuel pressure.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
eine schematische Darstellung eines ersten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils und
Fig. 2
eine schematische Darstellung eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich des Aktorkopfs.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
a schematic representation of a first embodiment of a fuel injection valve according to the invention and
Fig. 2
a schematic representation of a second embodiment of a fuel injection valve according to the invention in the region of the actuator head.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Das in Fig. 1 schematisch dargestellte erfindungsgemäße Brennstoffeinspritzventil 1 ist insbesondere als Brennstoffeinspritzventil 1 für Brennstoffeinspritzanlagen für gemischverdichtende, fremdgezündete Brennkraftmaschinen zum direkten Einspritzen von Brennstoff in den Brennraum der Brennkraftmaschine geeignet.The fuel injection valve 1 according to the invention shown schematically in Fig. 1 is particularly suitable as a fuel injection valve 1 for fuel injection systems for mixture-compressing, spark-ignited internal combustion engines for direct injection of fuel into the combustion chamber of the internal combustion engine.

Das Brennstoffeinspritzventil 1 umfaßt insbesondere einen piezoelektrischen, magnetostriktiven oder elektrostriktiven Aktor 2, welcher in einem Aktormodul 22 angeordnet ist. Der Aktor 2 bzw. das Aktormodul 22 ist Bestandteil eines Bestätigungsstrangs, der in diesem Ausführungsbeispiel außerdem einen zuströmseitig des Aktormoduls 22 angeordneten hydraulischen Koppler 3 und eine abströmseitig des Aktormoduls 22 angeordnete Ventilnadel 4 aufweist. Das Aktormodul 22, der hydraulische Koppler 3 und die Ventilnadel 4 sind in einem Ventilgehäuses 6 koaxial angeordnet. Das Ventilgehäuses 6 weist an seinem abströmseitigen Ende einen Düsenkörper 5 auf, durch welchen die Ventilnadel 4 koaxial greift und an dessen abströmseitigen Ende ein einstückig mit dem Düsenkörper 5 ausgebildeter Ventilsitzkörper 10 mit einer Abspritzöffnung 7 angeordnet ist. Eine am Ventilsitzkörper 10 ausgebildete Ventilsitzfläche 9 wirkt mit einem am abspritzseitigen Ende der Ventilnadel 4 ausgebildeten Ventilschließkörper 8 zu einem Dichtsitz zusammen. Das Brennstoffeinspritzventil 1 öffnet nach außen.The fuel injection valve 1 comprises in particular a piezoelectric, magnetostrictive or electrostrictive actuator 2, which is arranged in an actuator module 22. The actuator 2 or the actuator module 22 is part of a confirmation string, which in this embodiment also has a hydraulic coupler 3 arranged on the inflow side of the actuator module 22 and a valve needle 4 arranged downstream of the actuator module 22. The actuator module 22, the hydraulic coupler 3 and the valve needle 4 are arranged coaxially in a valve housing 6. The valve housing 6 has at its downstream end a nozzle body 5, through which the valve needle 4 coaxially engages and at its downstream end an integrally formed with the nozzle body 5 valve seat body 10 having a spray opening 7 is arranged. A valve seat surface 9 formed on the valve seat body 10 cooperates with a valve closing body 8 formed on the discharge end of the valve needle 4 to form a sealing seat. The fuel injection valve 1 opens to the outside.

Zuströmseitig weist das Ventilgehäuses 6 ein Ventiloberteil 33 auf. Das Ventiloberteil 33 liegt auf dem zuströmseitigen Ende des Ventilgehäuses 6 hermetisch dicht mit einer ersten Schulter 34 auf, ist dort mit dem Ventilgehäuses 6 beispielsweise stoffschlüssig gefügt, und greift mit seinem abströmseitigen Ende in das Ventilgehäuses 6 ein. Koaxial im Ventiloberteil 33 ausgebildet befindet sich ein zum Aktormodul 22 hin geöffneter Kopplerzylinder 23, in den ein Ausgleichskolben 21 eingreift. Seitlich des Ausgleichskolbens 21 befindet sich zwischen dem Ausgleichskolbens 21 und dem Kopplerzylinder 23 ein Leckagespalt 24. Der Leckagespalt 24 verbindet einen oben zwischen dem Kopplerzylinder 23 und dem Ausgleichskolbens 21 gebildeten Ausgleichsraum 31 und einen unten, zum Aktormodul 22 hin orientierten Membranraum 32. Der Membranraum 32 wird durch einen dritten flexiblen Abschnitt 28 abströmseitig abgeschlossen bzw. abgedichtet.On the inflow side, the valve housing 6 has a valve top 33. The upper valve part 33 is hermetically sealed on the inflow-side end of the valve housing 6 with a first shoulder 34, where it is joined to the valve housing 6, for example by a material fit, and engages with its downstream end into the valve housing 6. Coaxially formed in the upper valve part 33 is a coupler cylinder 23 which is open towards the actuator module 22 and into which a compensating piston 21 engages. The side of the balance piston 21 is located between the balance piston 21 and the coupler cylinder 23, a leakage gap 24. The leakage gap 24 connects a top formed between the coupler cylinder 23 and the balance piston 21 equalization chamber 31 and a bottom, the actuator module 22 oriented toward the membrane space 32nd Die Membranraum 32nd is completed by a third flexible portion 28 downstream or sealed.

Der in diesem Ausführungsbeispiel membranartige und lochplattenförmige dritte flexible Abschnitt 28 ist im Bereich des Außenumfangs mit dem in das Aktorgehäuses 6 eingreifenden abströmseitigen Ende des Ventiloberteils 33 unterhalb einer durchmesserreduzierenden zweiten Schulter 35 hermetisch dicht, beispielsweise durch Schweißen oder andere stoffschlüssigen Fügeverfahren, gefügt. Im Bereich seines Innenumfangs ist der dritte flexible Abschnitt 28 an dem sich zum Aktormodul 22 hin verjüngenden, den dritten flexiblen Abschnitt 28 durchgreifenden Ausgleichskolben 21 hermetisch dicht und stoffschlüssig gefügt. In radialer Richtung weist der aus Stahl oder einer Stahlregierung bestehende dritte flexible Abschnitt 28 im Querschnitt einen U-förmigen, bzw. wellenförmigen Verlauf auf. Der dritte flexible Abschnitt 28 wird dadurch nicht auf Zug, sondern vorteilhafterweise auf Biegung beansprucht.The membrane-like and hole-plate-shaped third flexible section 28 in the exemplary embodiment is hermetically sealed in the region of the outer circumference with the downstream end of the valve top part 33 engaging below a diameter-reducing second shoulder 35, for example by welding or other cohesive joining methods. In the region of its inner circumference, the third flexible section 28 is joined hermetically sealed and cohesively on the compensating piston 21, which tapers toward the actuator module 22 and passes through the third flexible section 28. In the radial direction, the steel or a steel government existing third flexible section 28 in cross-section on a U-shaped, or wave-shaped course. The third flexible section 28 is thereby not claimed to train, but advantageously to bending.

Der Kopplerzylinder 23, der Ausgleichskolbens 21, der Ausgleichsraum 31, der Leckagespalt 24 und der Membranraum 32 bilden in diesem Ausführungsbeispiel den hydraulischen Koppler 3. Der hydraulischen Koppler 3, bzw. der Ausgleichsraum 31, der Leckagespalt 24 und der Membranraum 32 sind vollständig mit einem Hydraulikmedium 30 gefüllt. Das Hydraulikmedium 30 ist in diesem Ausführungsbeispiel ein gut wärmeleitendes und hochviskoses Öl.The coupler cylinder 23, the balance piston 21, the compensation chamber 31, the leakage gap 24 and the diaphragm space 32 in this embodiment form the hydraulic coupler 3. The hydraulic coupler 3, or the compensation chamber 31, the leakage gap 24 and the diaphragm space 32 are completely with a Hydraulic medium 30 filled. The hydraulic medium 30 is in this embodiment, a good heat-conducting and highly viscous oil.

Im Ventiloberteil 33 verlaufen ein elektrischer Anschluß 15 und ein Brennstoffeinlaß 16, der sich in einen ersten Brennstoffkanal 17 und einen zweiten Brennstoffkanal 18 teilt. Der elektrische Anschluß 15 verläuft im weiteren im Ventilgehäuses 6, um auf Höhe des Aktormoduls 22 in dieses einzutreten.In the upper valve part 33 extend an electrical connection 15 and a fuel inlet 16 which divides into a first fuel channel 17 and a second fuel channel 18. The electrical connection 15 extends further in the valve housing 6 in order to enter the height of the actuator module 22 in this.

Im Bereich oberhalb der den Durchmesser des abströmseitigen Endes des Ventiloberteils 33 nach unten reduzierenden zweiten Schulter 35, ist ein lochplattenförmiger, im Querschnitt im wesentlichen U-förmig geformter und aus Stahl bestehender erster flexibler Abschnitt 25 mit seinem Außenumfang stoffschlüssig und hermetisch dicht gefügt. Im Bereich des Innenumfangs des ersten flexiblen Abschnitts 25 ist dieser auf der Oberseite eines dritten Flansches 29, der das im Durchmesser verjüngte, abströmseitige Ende des Ausgleichskolbens 21 umschließt, stoffschlüssig und hermetisch dicht verbunden. Der dritte Flansch 29 greift mit seinem abströmseitigen Ende in eine in der Oberseite des Aktormoduls 22 in einem Aktorfuß 13 angeordnete konische Ausnehmung 27 ein, mit der er idealerweise in ständigem Kontakt steht.In the area above the second shoulder 35, which reduces the diameter of the downstream end of the upper valve part 33, a hole-plate-shaped first flexible section 25 of substantially U-shaped design and consisting of steel is joined to its outer circumference with a material fit and hermetically sealed. In the region of the inner circumference of the first flexible portion 25, this is on the upper side of a third flange 29, which surrounds the diameter-tapered, downstream end of the balance piston 21, cohesively and hermetically sealed. The third flange 29 engages with its downstream end in a arranged in the top of the actuator module 22 in an actuator base 13 conical recess 27 with which he is ideally in constant contact.

Unmittelbar unterhalb der zweiten Schulter 35 und oberhalb des Außenumfangs des dritten flexiblen Abschnitts 28 ist eine zum ersten Brennstoffkanal 17 gehörende Ringnut 36 angeordnet. Im Betrieb des Brennstoffeinspritzventils 1 ist der zwischen dem ersten flexiblen Abschnitt 25 und dem dritten flexiblen Abschnitt 28 befindliche Raum über den ersten Brennstoffkanal 17 vollständig mit Brennstoff gefüllt. Der Brennstoff drückt dabei auf jeweils eine Seite des ersten flexiblen Abschnitts 25 und dritten flexiblen Abschnitts 28. Brennstoffdruck wirkt in dieser Weise auf den im Vergleich zum ersten flexiblen Abschnitt 25 weicheren, insbesondere dünneren, dritten flexiblen Abschnitt 28 auf das Hydraulikmedium 30. Der zwischen dem dritten flexiblen Abschnitt 28 und dem ersten flexiblen Abschnitt 25 herrschende Brennstoffdruck wirkt außerdem auf den ersten flexiblen Abschnitt 25 so, daß das Aktormodul 22 von oben über den dritten Flansch 29 auf dem Aktorfuß 13 mit einer in Abspritzrichtung wirkenden Vorspannung belastet wird.Immediately below the second shoulder 35 and above the outer periphery of the third flexible portion 28 is a belonging to the first fuel passage 17 annular groove 36 is arranged. In operation of the fuel injection valve 1 is the space located between the first flexible section 25 and the third flexible section 28 is completely filled with fuel via the first fuel channel 17. The fuel presses in each case on one side of the first flexible portion 25 and third flexible portion 28. Fuel pressure acts in this way on the compared to the first flexible portion 25 softer, in particular thinner, third flexible portion 28 on the hydraulic medium 30. The between the The third flexible portion 28 and the first flexible portion 25 prevailing fuel pressure also acts on the first flexible portion 25 so that the actuator module 22 is loaded from above via the third flange 29 on the actuator base 13 with a force acting in the ejection direction bias.

Die Ventilnadel 4 wird durch eine Vorspannfeder 11, welche über einen zweiten Flansch 20 an der Ventilnadel 4 angreift, entgegen der Abspritzrichtung vorspannt. Der Ventilschließkörper 8 wird dadurch in den Dichtsitz gezogen und das konisch geformte, zuströmseitige Ende der Ventilnadel 4 wird in eine in einem Aktorkopf 12 angeordnete zweite Ausnehmung 37 gedrückt. Zwischen dem zweiten Flansch 20 und dem zuströmseitigen Ende der Ventilnadel 4 ist ein erster Flansch 19 stoffschlüssig, beispielsweise durch Schweißen, mit der Ventilnadel 4 verbunden. Im Bereich seines Innenumfangs ist ein zweiter flexibler Abschnitt 26 mit der Unterseite des ersten Flansches 19 stoffschlüssig und hermetisch dicht verbunden. Im Bereich des Außenumfangs des zweiten flexiblen Abschnitts 26 ist dieser mit dem Düsenkörper 5 stoffschlüssig und hermetisch dicht verbunden.The valve needle 4 is biased by a biasing spring 11, which acts on the valve needle 4 via a second flange 20, against the discharge direction. The valve closing body 8 is thereby pulled into the sealing seat and the conically shaped, inflow-side end of the valve needle 4 is pressed into a second recess 37 arranged in an actuator head 12. Between the second flange 20 and the inflow end of the valve needle 4, a first flange 19 is materially connected, for example by welding, with the valve needle 4. In the region of its inner circumference, a second flexible portion 26 with the underside of the first flange 19 is firmly bonded and hermetically sealed. In the region of the outer periphery of the second flexible portion 26, this is connected to the nozzle body 5 cohesively and hermetically sealed.

In anderen Ausführungsbeispielen kann der zweite flexible Abschnitt 26 im Bereich seines Außenumfangs auch mit dem Ventilgehäuses 6 gefügt sein. Der druckbehaftet in dem zweiten Brennstoffkanal 18 im Ventilgehäuse 6 an dem Aktormodul 22 und der Vorspannfeder 11 vorbeigeführte Brennstoff wird, von unten kommend, die Vorspannfeder 11 und den zweiten Flansch 20 umspülend, an den zweiten flexiblen Abschnitt 26 geführt. Der einseitig auf den zweiten flexiblen Abschnitt 26 wirkende Brennstoffdruck drückt über den ersten Flansch 19 die Ventilnadel 4 in axialer Richtung zum Aktormodul 22 hin, entgegen der Abspritzrichtung.In other embodiments, the second flexible portion 26 may be joined in the region of its outer periphery with the valve housing 6. The pressurized in the second fuel channel 18 in the valve housing 6 on the actuator module 22 and the biasing spring 11 guided past fuel, coming from below, the biasing spring 11 and the second flange 20 flushing, guided to the second flexible portion 26. The one-sided to the second flexible section 26 acting fuel pressure pushes the valve needle 4 in the axial direction to the actuator module 22 through the first flange 19, against the Abspritzrichtung.

Ein zum Aktormodul 22 gehörendes Federelement 14 spannt den Aktorfuß 13 gegen den Aktorkopf 12, so daß der Aktor 2 unter Vorspannung steht.A belonging to the actuator module 22 spring element 14 biases the actuator foot 13 against the actuator head 12, so that the actuator 2 is under bias.

Wird über den elektrischen Anschluß 15 der Aktor 2 angeregt, so dehnt dieser sich in axialer Richtung aus und wirkt über den Aktorfuß 13 auf den Ausgleichskolben 21 ein. Bedingt durch die Schnelligkeit der Bewegung des Aktors 2 und des relativ schmalen Leckagespaltes 24 verhält sich das Hydraulikmedium 30 ähnlich wie ein Festkörper. Die Längenänderungen des Aktors 2 können dadurch fast vollständig auf die Ventilnadel 4 übertragen werden, wodurch der Ventilschließkörper 8 von der Ventilsitzfläche 9 abhebt und Brennstoff in den nicht dargestellten Brennraum der nicht dargestellten Brennkraftmaschine eingespritzt wird. Bei langsamen Bewegungen des Aktors 2, beispielsweise durch thermische Einflüsse, wird das Hydraulikmedium 30 durch den Leckagespalt 24 in den Membranraum 32 verdrängt, wodurch ein willkürliches Öffnen des Brennstoffeinspritzventils 1 verhindert wird.If the actuator 2 is excited via the electrical connection 15, then it expands in the axial direction and acts on the compensating piston 21 via the actuator foot 13. Due to the speed of movement of the actuator 2 and the relatively narrow leakage gap 24, the hydraulic medium 30 behaves similar to a solid. The changes in length of the actuator 2 can be transmitted almost completely to the valve needle 4, whereby the valve closing body 8 lifts off from the valve seat surface 9 and fuel is injected into the combustion chamber, not shown, of the internal combustion engine, not shown. During slow movements of the actuator 2, for example due to thermal influences, the hydraulic medium 30 is displaced through the leakage gap 24 into the membrane space 32, whereby an arbitrary opening of the fuel injection valve 1 is prevented.

Der erste flexible Abschnitt 25 und der zweite flexible Abschnitt 26 sind so dimensioniert und angeordnet, daß sich die axial, mittel- und unmittelbar auf den Ventilschließkörper 8 wirkenden Kräfte des Brennstoffdrucks sich im wesentlichen aufheben. Insbesondere kann das Brennstoffeinspritzventil 1 dadurch bei unterschiedlichen Brennstoffdrücken betrieben werden, ohne das beispielsweise die Federkraft der Vorspannfeder 11 durch aufwendige Maßnahmen adaptiv gestaltet werden muß.The first flexible portion 25 and the second flexible portion 26 are dimensioned and arranged so that the forces of the fuel pressure acting axially, indirectly and directly on the valve closing body 8 cancel each other out substantially. In particular, the fuel injection valve 1 can thereby be operated at different fuel pressures without, for example, the spring force of the biasing spring 11 must be made adaptive by consuming measures.

Fig. 2 zeigt eine schematische Darstellung eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils 1 im Bereich des Aktorkopfs 12, ähnlich dem ersten Ausführungsbeispiel aus Fig. 1. Im Unterschied fehlt der im ersten Ausführungsbeispiel verwendete dritte flexible Abschnitt 28. Der durch den ersten Brennstoffkanal 17 und die Ringnut 36 geleitete Brennstoff füllt in diesem Ausführungsbeispiel den hydraulischen Koppler 3, womit das Hydraulikmedium 30 aus Brennstoff besteht. Der Aufbau des Brennstoffeinspritzventils 1 wird dadurch vereinfacht.FIG. 2 shows a schematic illustration of a second exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the actuator head 12, similar to the first exemplary embodiment from FIG There is no difference between the third flexible section 28 used in the first exemplary embodiment. In this exemplary embodiment, the fuel passed through the first fuel channel 17 and the annular groove 36 fills the hydraulic coupler 3, with which the hydraulic medium 30 consists of fuel. The structure of the fuel injection valve 1 is thereby simplified.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt sondern gilt auch für andere Bauweisen von Brennstoffeinspritzventilen, die unter dem Schutz der Ansprüche liegen.The invention is not limited to the illustrated embodiments but also applies to other designs of fuel injection valves, which are under the protection of the claims.

Claims (14)

  1. Fuel injection valve (1), in particular for directly injecting fuel into a combustion chamber of an internal combustion engine, having an actuating mechanism which has a piezoelectric, electrostrictive or magnetostrictive actuator (2) which is operatively connected to a valve closing body (8) which interacts with a valve seat face (9) to form a sealing seat, at least one first flexible section (25), which is acted on with fuel pressure at one side by the fuel, being arranged at the inflow side of the actuator (2), and at least one second flexible section (26), which is acted on with fuel pressure at one side by the fuel, being arranged at the outflow side of the actuator (2),
    characterized
    in that the first flexible section (25) and the second flexible section (26) are arranged in such a way that the flexible sections (25, 26), or the fuel pressure acting on the flexible sections (25, 26), exert opposing axial forces on the actuator (2) or actuating mechanism, the flexible sections (25, 26) being substantially U-shaped in cross section.
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the actuating mechanism (2) has a hydraulic coupler (3).
  3. Fuel injection valve according to Claim 2,
    characterized
    in that the coupler (3) is arranged at the inflow side of the actuator (2).
  4. Fuel injection valve according to Claim 2 or 3,
    characterized
    in that the hydraulic coupler (3) has at least one equalizing space (31), at least one leakage gap (24) and a diaphragm space (32), the leakage gap (24) connecting the equalizing space (31) to the diaphragm space (32).
  5. Fuel injection valve according to one of Claims 2 to 4,
    characterized
    in that the hydraulic coupler (3) is completely filled with a hydraulic medium (30), at least one third flexible section (28) separating or sealing off the hydraulic medium (30) from fuel.
  6. Fuel injection valve according to Claim 5,
    characterized
    in that the third flexible section (28) seals off or separates the diaphragm space (32) from fuel.
  7. Fuel injection valve according to Claim 5 or 6,
    characterized
    in that the third flexible section (28) transmits most of the fuel pressure to the hydraulic medium (30).
  8. Fuel injection valve according to one of Claims 5 to 7,
    characterized
    in that the hydraulic medium (30) is an oil.
  9. Fuel injection valve according to one of the preceding claims,
    characterized
    in that at least one of the flexible sections (25, 26, 28) is formed in the manner of a perforated plate.
  10. Fuel injection valve according to one of the preceding claims,
    characterized
    in that the actuating mechanism (2, 3) engages through at least one of the flexible sections (25, 26, 28).
  11. Fuel injection valve according to one of the preceding claims,
    characterized
    in that the inner circumference of at least one of the flexible sections (25, 26, 28) is connected to the actuating mechanism (2, 3) in a cohesive and hermetically sealed manner.
  12. Fuel injection valve according to one of the preceding claims,
    characterized
    in that the flexible sections (25, 26, 28) consist of steel or a steel alloy.
  13. Fuel injection valve according to one of the preceding claims,
    characterized
    in that at least one of the flexible sections (25, 26, 28) is connected to the actuating mechanism (2, 3) by means of a first flange (19), a second flange (20) or a third flange (29).
  14. Fuel injection valve according to one of the preceding claims,
    characterized
    in that the first flexible section (25) and the second flexible section (26) are arranged and dimensioned such that the axial forces of the fuel pressure which act indirectly and directly on the valve closing body (8) substantially cancel one another out.
EP20040009262 2003-06-25 2004-04-20 Fuel injector Expired - Fee Related EP1491760B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10328573 2003-06-25
DE10328573A DE10328573A1 (en) 2003-06-25 2003-06-25 Fuel injector

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EP1491760A1 EP1491760A1 (en) 2004-12-29
EP1491760B1 true EP1491760B1 (en) 2006-09-27

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008041544B4 (en) * 2008-08-26 2016-05-12 Robert Bosch Gmbh Valve for metering a liquid or gaseous medium

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3533085A1 (en) * 1985-09-17 1987-03-26 Bosch Gmbh Robert METERING VALVE FOR DOSING LIQUIDS OR GASES
JPH09287511A (en) * 1996-04-19 1997-11-04 Futaba Corp Model engine and its controlling method
DE19901711A1 (en) * 1999-01-18 2000-07-20 Bosch Gmbh Robert Fuel injector and method for operating a fuel injector
DE19912665A1 (en) * 1999-03-20 2000-09-21 Bosch Gmbh Robert Fuel injector
DE19928916B4 (en) * 1999-06-24 2017-12-14 Robert Bosch Gmbh Fuel injector
DE19940054C2 (en) * 1999-08-24 2003-11-27 Siemens Ag Dosing valve for a pressurized fluid
DE19946869A1 (en) * 1999-09-30 2001-04-05 Bosch Gmbh Robert Fuel injector
DE19954537A1 (en) * 1999-11-12 2001-05-17 Bosch Gmbh Robert Fuel injector
DE19962177A1 (en) * 1999-12-22 2001-07-12 Siemens Ag Hydraulic device for transmitting an actuator movement
DE10003863B4 (en) * 2000-01-28 2004-11-18 Robert Bosch Gmbh injection
DE10007733A1 (en) * 2000-02-19 2001-08-23 Daimler Chrysler Ag Injection valve has actuator is sealed with respect to fuel under high pressure using metallic corrugated tube between fuel chamber and actuator
DE10039543C2 (en) * 2000-08-12 2003-06-18 Conti Temic Microelectronic Injector
DE10141136A1 (en) * 2001-04-07 2002-10-10 Continental Teves Ag & Co Ohg Hydraulic valve with smooth piezoelectric actuation, for anti-skid vehicle braking system, includes resiliently-deformable thrust transmission system
DE10129375B4 (en) * 2001-06-20 2005-10-06 Mtu Friedrichshafen Gmbh Injector with piezo actuator
DE10158789A1 (en) * 2001-11-30 2003-07-10 Bosch Gmbh Robert Fuel injector
DE10159749A1 (en) * 2001-12-05 2003-06-12 Bosch Gmbh Robert Fuel injection valve for an internal combustion engine comprises a pressure space which contains a hydraulic fluid and, by means of sealing units, is separated from the actuator and fuel spaces

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DE502004001567D1 (en) 2006-11-09
EP1491760A1 (en) 2004-12-29

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