EP1276983B1 - Valve for controlling liquids - Google Patents

Valve for controlling liquids Download PDF

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Publication number
EP1276983B1
EP1276983B1 EP01921223A EP01921223A EP1276983B1 EP 1276983 B1 EP1276983 B1 EP 1276983B1 EP 01921223 A EP01921223 A EP 01921223A EP 01921223 A EP01921223 A EP 01921223A EP 1276983 B1 EP1276983 B1 EP 1276983B1
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EP
European Patent Office
Prior art keywords
valve
actuating piston
piston
actuating
bore
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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 - Lifetime
Application number
EP01921223A
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German (de)
French (fr)
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EP1276983A1 (en
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1276983A1 publication Critical patent/EP1276983A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/025—Hydraulically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention is based on a valve for controlling Liquids according to the detail defined in claim 1 Sort of out.
  • the hydraulic chamber is in such a way between the two Clamped piston, that the actuating piston of the Valve member one to the gear ratio of Piston diameter makes increased stroke when the larger piston by the piezoelectric actuator to a certain distance is moved.
  • the valve member, the pistons and the piezoelectric actuator are thereby on a common axis in a row.
  • valves in particular the great length, which extends through the longitudinal direction successively arranged piston results and at low available installation space very hindering is.
  • the inventive valve for controlling fluids according to the features of claim 1 with an actuating piston, which in a blind bore the adjusting piston is arranged, and with at least one Reduction element for the realization of the translation advantageously requires only a very small Installation space.
  • the leakage from the hydraulic chamber significantly reduce, as by the solution according to the invention parallel sealing gaps between control pistons, Actuating piston and reducing much less Liquid can escape than over the inevitable larger peripheral surfaces of serially one behind the other arranged actuating and actuating piston.
  • the transmission ratio is constructive in the inventive Valve in a particularly simple manner about the area ratios between the cross-sectional area of the actuator piston on the hydraulic chamber, i. the base area of the blind bore, and the cross-sectional area, which is the cross section of the actuating piston and the cross section of the at least one Reduzierettis composed, realized.
  • the actuating piston together with the at least one reducing element for a first part length of its maximum stroke displaceable is, and that the actuating piston from reaching the stop for the at least one reducing element in the Bore the valve body a remaining stroke performs.
  • the piezoelectric Although actuator provides a large reserve of power as long as the Aktorhub is small, but that the maximum Stroke piezoelectric actuators is also small. It is with a step ratio according to the invention but advantageously possible, a great force on the valve closure member for a first part length of maximum stroke, since the gear ratio 1: 1 relative to the actuating piston. In order to can the valve closure member against a very high Print to be opened. After the reducer its Stop has reached, the actuating piston depending on the dimensions of a remaining stroke with less Overcome power.
  • valve can also be the piezoelectric actuator on to be downsized as to the execution of the required Stroke the maximum actuator power only for a small stroke is required.
  • valve in a special way as a servo valve for control a fuel injection valve for internal combustion engines, in particular a common rail injector, in which a very limited space for Is available and in which the servo valve against a high rail pressure must be opened so that a through an injection needle predetermined flow through the Valve seat of the valve closure member is made possible.
  • valve according to the invention for controlling fluids is in the drawing and will become more apparent in the following description explained.
  • the single figure shows a schematic, fragmentary Representation of an embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section.
  • the embodiment shown in the figure shows a use of the valve according to the invention in a Fuel injection valve 1 for internal combustion engines of Motor vehicles.
  • the fuel injection valve 1 is presently designed as a common rail injector, the injection of diesel fuel over the Pressure level in a valve control chamber 12, which with a high pressure supply is connected, controlled becomes.
  • a multi-part valve member 2 via a piezoelectric actuator 3 formed as a piezoelectric Unit driven, the piezoelectric Actuator 3 on the valve control room and combustion chamber facing away Side of the valve member 2 is arranged.
  • the known per se of several layers constructed piezoelectric actuator 3 has on his the valve member 2 side facing an actuator head. 4 on and relies on the valve member facing away Side on a valve body 5 from.
  • On the actuator head 4 is via a support 6, a control piston 7 of the valve member 2 on.
  • the valve member 2 is in a longitudinal bore executed bore 8 of the Ventilkorpers. 5 axially displaceable and includes next to the actuating piston. 7 nor a valve closure member 9 actuated actuating piston 10, wherein the actuating piston 7 and the actuating piston 10 by means of a hydraulic transmission coupled together.
  • the hydraulic transmission is with a hydraulic chamber 11 formed over which the deflection of the piezoelectric Actuator 3 is transmitted.
  • the hydraulic chamber 11 is in an open in valve seat direction Blind bore 13 of the actuating piston 7 is formed in which the actuating piston 10 slidably mounted is and the hydraulic chamber 11 in the valve seat direction limited.
  • the gear ratio results thereby from the relationship between the to the hydraulic chamber 11 adjacent cross-sectional area A0 of the actuating piston 7 on the one hand and the smaller cross-sectional area A1 of the actuating piston 10 on the other.
  • Length of the bolt 14 is greater than the length of an area 10A of the actuating piston 10 with the at the compensation volume the hydraulic chamber 11 adjacent cross-sectional area A1 selected.
  • the cross section of the actuating piston 10 tapers from this area 10A against a contact surface 16 for the valve closure member 9th
  • the reducing element 14 in the valve seat direction be made a little shorter, so that a stepped translation is possible, in which the actuating piston 10 initially together with the Reduzierelement 14 for a first part length of its maximum stroke is displaceable, namely until the reducing element at which preferably divided at a dividing surface of executed valve body 5 trained stop 15th comes to the concern.
  • 1 Coupling can be a great force on the valve closure member 9 are applied, while in the subsequent sole movement of the actuating piston 10 a large residual stroke can be performed, the one stable operation of the fuel injection valve 1 ensures, on the one hand the valve position clearly and on the other a typical for common rail injectors Outflow throttle 18 can safely cavitate.
  • valve closure member 9 which in the present case with spherical caps is formed and on the valve control chamber side End of the valve member 2 is provided acts with formed on the valve body 5 valve seats 19, 20 together, the lower valve seat 20 a Spring device 21 is associated with the valve closing member 9 at discharge of the valve control chamber 12th at the upper valve seat 19 stops.
  • the valve seats 19, 20 are in a first formed in the valve body 5
  • Valve chamber 22 is formed, which with a leakage drainage channel 23 and with one to a valve system pressure chamber 24 leading equalization channel 25 a filling device 26 is connected.
  • valve closure member 9 which in an alternative Of course, also with only one valve seat can interact, separates a low pressure area 27 with a system pressure from a high pressure area 28 with a high pressure or rail pressure.
  • a second valve chamber 29 which on the one hand by the valve body 5 and on the other by a with the adjusting piston 7 and the valve body 5 connected sealing element 30 is limited wherein the sealing element 30 in the present case as a bellows-like Membrane is formed and prevents the piezoelectric actuator 3 with the in the low pressure region 27 contained fuel comes into contact.
  • the fuel injection valve 1 works in the manner described below.
  • valve closing member For fuel injection, the valve closing member must be 9 against the flow direction and thus against the Rail pressure in the high pressure area 28 are opened.
  • valve closure member 9 in a middle position placed between the two valve seats 19, 20 and then in a closed position to the lower Valve seat 20 moves, causing no more fuel the valve control chamber 12 into the first valve chamber 22 passes.
  • Valve closure member 9 When the energization of the piezoelectric actuator 3 is interrupted becomes shorter again, and that Valve closure member 9 is in the middle position between brought the two valve seats 19, 20, wherein a re-fuel injection takes place. After this Pressure reduction in the valve chamber 22 through the leakage drainage channel 23, the valve closing member 9 moves in its closed position to the upper valve seat 19, in the it is held by the spring means 21.
  • the embodiment is not a power balanced fuel injector, Of course, the invention can also be balanced with force designed valves are used.
  • the invention is not limited to fuel injectors limited, but it is suitable for everyone Valves with a piezoelectric actuator, at where a valve closure member is a high pressure area of separates a low pressure region, such as in pumps.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Control Of Non-Electrical Variables (AREA)

Abstract

A valve for controlling fluids has a piezoelectric unit (3) for actuating a valve member (2) that is displaceable in a bore (8) of a valve body (9), having at least one control piston (7) and at least one actuating piston (10) for actuating a valve closing member (9). Between the control piston (7) and the actuating piston (10), a hydraulic chamber (11) functioning as a hydraulic coupler is embodied; the actuating piston (10), defining the hydraulic chamber (11), is supported displaceably in a blind bore (12) of the control piston (7), which bore is open in the valve seat direction. A cross-sectional area (A0), bordering the hydraulic chamber (11), of the control piston (7) on the one hand and a smaller cross-sectional area (A1) of the actuating piston (10) and a cross-sectional area (A2) of at least one reducing element (14) determine a boost for the stroke length of the actuating piston (10), during which the at least one reducing element (14) is braced on a stop (15) in the bore (8) (Drawing figure).

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Ventil zum Steuern von Flüssigkeiten gemäß der in Patentanspruch 1 näher definierten Art aus.The invention is based on a valve for controlling Liquids according to the detail defined in claim 1 Sort of out.

Aus der EP 0 477 400 A1 ist ein Ventil, welches über einen piezoelektrischen Aktor betätigbar ist, bereits bekannt. Dieses bekannte Ventil weist eine Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für einen Wegtransformator des piezoelektrischen Aktors auf, bei der die Auslenkung des piezoelektrischen Aktors über eine Hydraulikkammer übertragen wird. Die Hydraulikkammer, welche als eine sogenannte hydraulische Übersetzung arbeitet, schließt zwischen zwei sie begrenzenden Kolben, von denen einer als Betätigungskolben mit einem kleineren Durchmesser ausgebildet ist und mit einem anzusteuernden Ventilschließglied verbunden ist und der andere Kolben als Stellkolben mit einem größeren Durchmesser ausgebildet ist und mit dem piezoelektrischen Aktor verbunden ist, ein gemeinsames Ausgleichsvolumen ein. Über dieses können Toleranzen aufgrund von Temperaturgradienten im Bauteil sowie eventuelle Setzeffekte ausgeglichen werden, ohne daß dadurch eine Änderung der Position des anzusteuernden Ventilgliedes auftritt.From EP 0 477 400 A1 is a valve which over a piezoelectric actuator is actuated already known. This known valve has an arrangement for an adaptive, mechanical acting in the stroke direction Tolerance compensation for a path transformer of the piezoelectric actuator on, in which the deflection the piezoelectric actuator via a hydraulic chamber is transmitted. The hydraulic chamber, which as a so-called hydraulic translation works, closes between two limiting pistons, one of which as actuating piston with a smaller diameter is formed and with a valve closure member to be controlled is connected and the other piston than Control piston formed with a larger diameter is and is connected to the piezoelectric actuator, a common compensation volume. About this can Tolerances due to temperature gradients in the Component as well as possible setting effects are compensated without thereby changing the position of the to be controlled valve member occurs.

Die Hydraulikkammer ist dabei derart zwischen den beiden Kolben eingespannt, daß der Betätigungskolben des Ventilgliedes einen um das Übersetzungsverhältnis des Kolbendurchmessers vergrößerten Hub macht, wenn der größere Kolben durch den piezoelektrischen Aktor um eine bestimmte Wegstrecke bewegt wird. Das Ventilglied, die Kolben und der piezoelektrische Aktor liegen dabei auf einer gemeinsamen Achse hintereinander.The hydraulic chamber is in such a way between the two Clamped piston, that the actuating piston of the Valve member one to the gear ratio of Piston diameter makes increased stroke when the larger piston by the piezoelectric actuator to a certain distance is moved. The valve member, the pistons and the piezoelectric actuator are thereby on a common axis in a row.

Nachteilig ist bei derartigen Ventilen insbesondere die große Baulänge, welche sich durch die in Längsrichtung hintereinander angeordneten Kolben ergibt und bei geringem zur Verfügung stehenden Einbauraum sehr hinderlich ist.A disadvantage of such valves in particular the great length, which extends through the longitudinal direction successively arranged piston results and at low available installation space very hindering is.

Des weiteren sind bei solchen Ventilen die Leckageverluste aus der Hydraulikkammer entlang eines den Stellkolben bzw. den Betatigungskolben umgebenden Spaltes problematisch, da diese Verluste zu einer empfindlichen Verschlechterung des Wirkungsgrades führen können.Furthermore, in such valves, the leakage losses from the hydraulic chamber along a the actuator piston or the actuating piston surrounding gap problematic, since these losses become a sensitive one Deterioration of the efficiency can lead.

Die beschriebenen Nachteile der bekannten Lösungen treffen vor allem auf Servoventile zur Ansteuerung von als Common-Rail-Injektoren ausgebildeten Kraftstoffeinspritzventilen zu, bei denen ein hoher Wirkungsgrad erwünscht ist sowie ein nur sehr begrenzter Bauraum zur Verfügung steht.The described disadvantages of the known solutions especially on servo valves to control designed as common rail injectors fuel injection valves to, where a high efficiency desired is as well as a very limited space for Available.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Ventil zur Steuerung von Flussigkeiten gemäß den Merkmalen des Patentanspruchs 1 mit einem Betätigungskolben, welcher in einer Sackbohrung des Stellkolbens angeordnet ist, und mit wenigstens einem Reduzierelement zur Realisierung der Übersetzung benötigt in vorteilhafter Weise einen nur sehr kleinen Einbauraum.The inventive valve for controlling fluids according to the features of claim 1 with an actuating piston, which in a blind bore the adjusting piston is arranged, and with at least one Reduction element for the realization of the translation advantageously requires only a very small Installation space.

Des weiteren lassen sich mit dem erfindungsgemäßen Ventil die Leckverluste aus der Hydraulikkammer deutlich reduzieren, da durch die bei der erfindungsgemäßen Lösung parallel verlaufenden Dichtspalte zwischen Stellkolben, Betätigungskolben und Reduzierelement weit weniger Flüssigkeit entweichen kann als über die zwangsläufig größeren Umfangsflächen von seriell hintereinander angeordneten Stell- und Betätigungskolben.Furthermore, can be with the valve according to the invention the leakage from the hydraulic chamber significantly reduce, as by the solution according to the invention parallel sealing gaps between control pistons, Actuating piston and reducing much less Liquid can escape than over the inevitable larger peripheral surfaces of serially one behind the other arranged actuating and actuating piston.

Aufgrund der geringeren Leckverluste insbesondere bei kleinen Übersetzungen wird ein besserer Wirkungsgrad realisiert. Zudem kann ein kleinerer bzw. kürzerer piezoelektrischer Aktor eingesetzt werden, wodurch die Fertigungskosten für das erfindungsgemäße Ventil deutlich gesenkt werden können, da die Dimensionierung des piezoelektrischen Aktors ein bedeutender Kostenfaktor ist. Due to the lower leakage especially at small translations will be a better efficiency realized. In addition, a smaller or shorter piezoelectric Actuator be used, causing the Production costs for the valve according to the invention clearly can be lowered because the sizing of the piezoelectric actuator a significant cost factor is.

Das Übersetzungsverhältnis wird konstruktiv bei dem erfindungsgemäßen Ventil auf besonders einfache Weise über die Flächenverhältnisse zwischen der Querschnittsflache des Stellkolbens an der Hydraulikkammer, d.h. der Grundfläche der Sackbohrung, und der Querschnittsfläche, welche sich aus dem Querschnitt des Betätigungskolbens und dem Querschnitt des wenigstens einen Reduzierelementes zusammensetzt, realisiert.The transmission ratio is constructive in the inventive Valve in a particularly simple manner about the area ratios between the cross-sectional area of the actuator piston on the hydraulic chamber, i. the base area of the blind bore, and the cross-sectional area, which is the cross section of the actuating piston and the cross section of the at least one Reduzierelementes composed, realized.

In einer sehr vorteilhaften Weiterführung der Erfindung kann vorgesehen sein, daß der Betätigungskolben zusammen mit dem wenigstens einen Reduzierelement für eine erste Teillänge seines maximalen Hubweges verschiebbar ist, und daß der Betätigungskolben ab Erreichen des Anschlags fur das wenigstens eine Reduzierelement in der Bohrung des Ventilkörpers einen verbleibenden Hubweg ausführt.In a very advantageous continuation of the invention can be provided that the actuating piston together with the at least one reducing element for a first part length of its maximum stroke displaceable is, and that the actuating piston from reaching the stop for the at least one reducing element in the Bore the valve body a remaining stroke performs.

Damit wird die Erkenntnis berücksichtigt, daß der piezoelektrische Aktor zwar eine große Kraftreserve liefert solange der Aktorhub klein ist, daß aber der maximale Hub piezoelektrischer Aktoren ebenfalls klein ist. Mit einer erfindungsgemäßen Stufenübersetzung ist es aber in vorteilhafter Weise möglich, eine große Kraft auf das Ventilschließglied fur eine erste Teillänge des maximalen Hubweges aufzubringen, da das Übersetzungsverhältnis gegenüber dem Stellkolben 1:1 beträgt. Damit kann das Ventilschließglied gegen einen sehr hohen Druck geöffnet werden. Nachdem das Reduzierelement seinen Anschlag erreicht hat, kann der Betätigungskolben je nach Dimensionierung einen restlichen Hubweg mit geringerer Kraft überwinden.Thus, the knowledge is taken into account that the piezoelectric Although actuator provides a large reserve of power as long as the Aktorhub is small, but that the maximum Stroke piezoelectric actuators is also small. It is with a step ratio according to the invention but advantageously possible, a great force on the valve closure member for a first part length of maximum stroke, since the gear ratio 1: 1 relative to the actuating piston. In order to can the valve closure member against a very high Print to be opened. After the reducer its Stop has reached, the actuating piston depending on the dimensions of a remaining stroke with less Overcome power.

Mit einer derartigen erfindungsgemäßen Ausgestaltung des Ventils kann zudem der piezoelektrische Aktor weiter verkleinert werden, da zur Ausführung des erforderlichen Hubweges die maximale Aktorkraft nur noch für einen geringen Hubweg erforderlich ist.With such an inventive embodiment the valve can also be the piezoelectric actuator on to be downsized as to the execution of the required Stroke the maximum actuator power only for a small stroke is required.

Mit seiner erfindungsgemäßen Ausgestaltung eignet sich das Ventil in besonderer Weise als Servoventil zur Ansteuerung eines Kraftstoffeinspritzventils für Brennkraftmaschinen, insbesondere eines Common-Rail-Injektors, bei dem ein nur sehr begrenzter Bauraum zur Verfügung steht und bei dem das Servoventil gegen einen hohen Raildruck geöffnet werden muß, damit ein durch eine Einspritznadel vorgegebener Durchfluß durch den Ventilsitz des Ventilschließgliedes ermöglicht wird.With its inventive design is suitable the valve in a special way as a servo valve for control a fuel injection valve for internal combustion engines, in particular a common rail injector, in which a very limited space for Is available and in which the servo valve against a high rail pressure must be opened so that a through an injection needle predetermined flow through the Valve seat of the valve closure member is made possible.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of Subject of the invention are the description that Drawing and claims removed.

Zeichnungdrawing

Ein Ausführungsbeispiel des erfindungsgemäßen Ventils zur Steuerung von Flüssigkeiten ist in der Zeichnung dargestellt und wird in der folgenden Beschreibung näher erläutert. An embodiment of the valve according to the invention for controlling fluids is in the drawing and will become more apparent in the following description explained.

Die einzige Figur zeigt eine schematische, ausschnittsweise Darstellung eines Ausführungsbeispiels der Erfindung bei einem Kraftstoffeinspritzventil für Brennkraftmaschinen im Längsschnitt.The single figure shows a schematic, fragmentary Representation of an embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in der Figur dargestellte Ausführungsbeispiel zeigt eine Verwendung des erfindungsgemäßen Ventils bei einem Kraftstoffeinspritzventil 1 für Brennkraftmaschinen von Kraftfahrzeugen. Das Kraftstoffeinspritzventil 1 ist vorliegend als ein Common-Rail-Injektor ausgebildet, wobei die Einspritzung von Dieselkraftstoff über das Druckniveau in einem Ventilsteuerraum 12, welcher mit einer Hochdruckversorgung verbunden ist, gesteuert wird.The embodiment shown in the figure shows a use of the valve according to the invention in a Fuel injection valve 1 for internal combustion engines of Motor vehicles. The fuel injection valve 1 is presently designed as a common rail injector, the injection of diesel fuel over the Pressure level in a valve control chamber 12, which with a high pressure supply is connected, controlled becomes.

Zur Einstellung eines Einspritzbeginns, einer Einspritzdauer und einer Einspritzmenge in dem vorliegend nicht kraftausgeglichen ausgestalteten Kraftstoffeinspritzventil 1 wird ein mehrteiliges Ventilglied 2 über eine als piezoelektrischer Aktor 3 ausgebildete piezoelektrische Einheit angesteuert, wobei der piezoelektrische Aktor 3 auf der ventilsteuerraum- und brennraumabgewandten Seite des Ventilgliedes 2 angeordnet ist.For setting an injection start, an injection duration and an injection amount in the present not force balanced designed fuel injector 1, a multi-part valve member 2 via a piezoelectric actuator 3 formed as a piezoelectric Unit driven, the piezoelectric Actuator 3 on the valve control room and combustion chamber facing away Side of the valve member 2 is arranged.

Der auf an sich bekannte Weise aus mehreren Schichten aufgebaute piezoelektrische Aktor 3 weist auf seiner dem Ventilglied 2 zugewandten Seite einen Aktorkopf 4 auf und stützt sich auf der dem Ventilglied abgewandten Seite an einem Ventilkörper 5 ab. An dem Aktorkopf 4 liegt über ein Auflager 6 ein Stellkolben 7 des Ventilgliedes 2 an. Das Ventilglied 2 ist in einer als Längsbohrung ausgeführten Bohrung 8 des Ventilkorpers 5 axial verschiebbar und umfaßt neben dem Stellkolben 7 noch einen ein Ventilschließglied 9 betätigenden Betätigungskolben 10, wobei der Stellkolben 7 und der Betätigungskolben 10 mittels einer hydraulischen Übersetzung miteinander gekoppelt sind.The known per se of several layers constructed piezoelectric actuator 3 has on his the valve member 2 side facing an actuator head. 4 on and relies on the valve member facing away Side on a valve body 5 from. On the actuator head 4 is via a support 6, a control piston 7 of the valve member 2 on. The valve member 2 is in a longitudinal bore executed bore 8 of the Ventilkorpers. 5 axially displaceable and includes next to the actuating piston. 7 nor a valve closure member 9 actuated actuating piston 10, wherein the actuating piston 7 and the actuating piston 10 by means of a hydraulic transmission coupled together.

Die hydraulische Übersetzung ist mit einer Hydraulikkammer 11 ausgebildet, über die die Auslenkung des piezoelektrischen Aktors 3 übertragen wird. Die Hydraulikkammer 11 ist dabei in einer in Ventilsitzrichtung offenen Sackbohrung 13 des Stellkolbens 7 ausgebildet, in welcher der Betätigungskolben 10 verschiebbar gelagert ist und dabei die Hydraulikkammer 11 in Ventilsitzrichtung begrenzt. Das Übersetzungsverhältnis ergibt sich dabei aus dem Verhältnis zwischen der an die Hydraulikkammer 11 grenzenden Querschnittsfläche A0 des Stellkolbens 7 einerseits und der kleineren Querschnittsfläche A1 des Betätigungskolbens 10 andererseits.The hydraulic transmission is with a hydraulic chamber 11 formed over which the deflection of the piezoelectric Actuator 3 is transmitted. The hydraulic chamber 11 is in an open in valve seat direction Blind bore 13 of the actuating piston 7 is formed in which the actuating piston 10 slidably mounted is and the hydraulic chamber 11 in the valve seat direction limited. The gear ratio results thereby from the relationship between the to the hydraulic chamber 11 adjacent cross-sectional area A0 of the actuating piston 7 on the one hand and the smaller cross-sectional area A1 of the actuating piston 10 on the other.

Zum Ausgleich der Differenz zwischen der Querschnittsfläche A1 des Betätigungskolbens 10 und der größeren Querschnittsfläche A0 an dem Stellkolben 7 ist seitens des Betätigungskolbens 10 ein als Bolzen ausgebildetes Reduzierelement 14 vorgesehen, welches in eine axial in dem Betätigungskolben 10 ausgebildeten Durchgangsbohrung 17 eingesetzt ist und mit einer Querschnittsfläche A2 an die Hydraulikkammer 11 grenzt. Die Querschnittsfläche A1 des Betätigungskolbens 10 und die Querschnittsfläche A2 des Reduzierelementes 14 ergeben zusammen unter Vernachlässigung von Spaltflächen die an die Hydraulikkammer 11 grenzende Querschnittsfläche A0 des Stellkolbens 7. Damit ist bei Betätigung des Stellkolbens 7 über die Hydraulikkammer 11 ein Verschieben des Betätigungskolbens 10 in Ventilsitzrichtung über wenigstens eine Teillänge seines maximalen Hubweges moglich, während der als Reduzierelement vorgesehene Bolzen 14 an einem Anschlag 15 in der Bohrung 8 abgestützt ist.To compensate for the difference between the cross-sectional area A1 of the actuating piston 10 and the larger Cross-sectional area A0 on the actuating piston 7 is the side of the actuating piston 10 designed as a bolt Reduction element 14 is provided, which in an axially in the actuating piston 10 formed through hole 17 is inserted and with a cross-sectional area A2 is adjacent to the hydraulic chamber 11. The cross-sectional area A1 of the actuating piston 10 and the cross-sectional area A2 of the Reduzierelementes 14 together neglecting cleavage surfaces on the hydraulic chamber 11 adjacent cross-sectional area A0 of the actuating piston 7. This is upon actuation of the actuating piston 7 via the hydraulic chamber 11 a move of the actuating piston 10 in the valve seat direction at least a part of its maximum stroke possible, while intended as a Reduzierelement Bolt 14 supported on a stop 15 in the bore 8 is.

Bei der in der Figur dargestellten Ausführung ist die Länge des Bolzens 14 größer als die Länge eines Bereiches 10A des Betätigungskolbens 10 mit der an das Ausgleichsvolumen der Hydraulikkammer 11 grenzenden Querschnittsfläche A1 gewahlt. Der Querschnitt des Betätigungskolbens 10 verjüngt sich von diesem Bereich 10A entgegen einer Anlagefläche 16 für das Ventilschließglied 9.In the embodiment shown in the figure is the Length of the bolt 14 is greater than the length of an area 10A of the actuating piston 10 with the at the compensation volume the hydraulic chamber 11 adjacent cross-sectional area A1 selected. The cross section of the actuating piston 10 tapers from this area 10A against a contact surface 16 for the valve closure member 9th

In weiteren erfindungsgemäßen Ausführungen kann selbstverständlich auch vorgesehen sein, daß als Reduzierelement mehrere Bolzen vorhanden sind oder daß das Reduzierelement eine andere Form, wie z.B. eine Ringform, aufweist.In other embodiments of the invention may of course also be provided that as a reducing several bolts are present or that the reducing element another form, e.g. a ring shape, having.

Des weiteren kann das Reduzierelement 14 in Ventilsitzrichtung auch etwas kürzer ausgeführt sein, so daß eine gestufte Übersetzung möglich ist, bei der der Betätigungskolben 10 zunächst zusammen mit dem Reduzierelement 14 für eine erste Teillänge seines maximalen Hubweges verschiebbar ist, nämlich bis das Reduzierelement an dem vorzugsweise an einer Teilungsfläche des geteilt ausgeführten Ventilkörpers 5 ausgebildeten Anschlag 15 zum Anliegen kommt. Mit der bis dahin wirkenden 1:1 Kopplung kann eine große Kraft auf das Ventilschließglied 9 aufgebracht werden, während bei der anschließenden alleinigen Fortbewegung des Betätigungskolbens 10 ein großer Resthub durchgeführt werden kann, der einen stabilen Betrieb des Kraftstoffeinspritzventils 1 sicherstellt, da zum einen die Ventilstellung eindeutig ist und zum anderen eine für Common-Rail-Injektoren typische Ablaufdrossel 18 sicher kavitieren kann.Furthermore, the reducing element 14 in the valve seat direction be made a little shorter, so that a stepped translation is possible, in which the actuating piston 10 initially together with the Reduzierelement 14 for a first part length of its maximum stroke is displaceable, namely until the reducing element at which preferably divided at a dividing surface of executed valve body 5 trained stop 15th comes to the concern. With the until then acting 1: 1 Coupling can be a great force on the valve closure member 9 are applied, while in the subsequent sole movement of the actuating piston 10 a large residual stroke can be performed, the one stable operation of the fuel injection valve 1 ensures, on the one hand the valve position clearly and on the other a typical for common rail injectors Outflow throttle 18 can safely cavitate.

Zur Erzielung dieses Effekts kann es ausreichend sein, das Reduzierelement 14 gegenuber der zuvor beschriebenen Ausführung in einer so geringen Größenordnung zu verkürzen, daß sich diese Variante bei den gegebenen Größenverhältnissen von der in der Figur gezeigten Ausführung zeichnerisch unmerklich unterscheidet.To achieve this effect, it may be sufficient the reducing element 14 compared to the previously described Execution on such a small scale too shorten that this variant with the given Size ratios of the embodiment shown in the figure Drawn unnoticed.

Das Ventilschließglied 9, welches vorliegend mit Kugelkappen ausgebildet ist und an dem ventilsteuerraumseitigen Ende des Ventilgliedes 2 vorgesehen ist, wirkt mit an dem Ventilkörper 5 ausgebildeten Ventilsitzen 19, 20 zusammen, wobei dem unteren Ventilsitz 20 eine Federeinrichtung 21 zugeordnet ist, die das Ventilschließglied 9 bei Entlastung des Ventilsteuerraumes 12 am oberen Ventilsitz 19 hält. Die Ventilsitze 19, 20 sind in einem in dem Ventilkörper 5 gebildeten ersten Ventilraum 22 ausgebildet, der mit einem Leckageablaufkanal 23 und mit einem zu einem Ventilsystemdruckraum 24 führenden Ausgleichkanal 25 einer Befülleinrichtung 26 verbunden ist.The valve closure member 9, which in the present case with spherical caps is formed and on the valve control chamber side End of the valve member 2 is provided acts with formed on the valve body 5 valve seats 19, 20 together, the lower valve seat 20 a Spring device 21 is associated with the valve closing member 9 at discharge of the valve control chamber 12th at the upper valve seat 19 stops. The valve seats 19, 20 are in a first formed in the valve body 5 Valve chamber 22 is formed, which with a leakage drainage channel 23 and with one to a valve system pressure chamber 24 leading equalization channel 25 a filling device 26 is connected.

Das Ventilschließglied 9, welches in einer alternativen Ausführung selbstverständlich auch mit nur einem Ventilsitz zusammenwirken kann, trennt einen Niederdruckbereich 27 mit einem Systemdruck von einem Hochdruckbereich 28 mit einem Hochdruck bzw. Raildruck.The valve closure member 9, which in an alternative Of course, also with only one valve seat can interact, separates a low pressure area 27 with a system pressure from a high pressure area 28 with a high pressure or rail pressure.

An dem piezoseitigen Ende des Ventilglieds 2 schließt sich an die Anbohrung 8 ein zweiter Ventilraum 29 an, welcher einerseits durch den Ventilkörper 5 und andererseits durch ein mit dem Stellkolben 7 und dem Ventilkörper 5 verbundenes Dichtelement 30 begrenzt ist, wobei das Dichtelement 30 vorliegend als faltenbalgartige Membran ausgebildet ist und verhindert, daß der piezoelektrische Aktor 3 mit dem in dem Niederdruckbereich 27 enthaltenen Kraftstoff in Kontakt kommt.At the piezoseitigen end of the valve member 2 closes to the tapping 8 a second valve chamber 29, which on the one hand by the valve body 5 and on the other by a with the adjusting piston 7 and the valve body 5 connected sealing element 30 is limited wherein the sealing element 30 in the present case as a bellows-like Membrane is formed and prevents the piezoelectric actuator 3 with the in the low pressure region 27 contained fuel comes into contact.

Über die Befülleinrichtung 26 wird die Hydraulikkammer 11 während einer Ansteuer- bzw. Bestromungspause des piezoelektrischen Aktors 3 zum Ausgleich einer Leckagemenge des Niederdruckbereiches 27 mit Hydraulikflüssigkeit aus dem Hochdruckbereich 28 wiederbefüllt. Hierzu mündet ein kanalartiger Hohlraum 31 in den Systemdruckraum 24 des Niederdruckbereiches 27, welcher als Bohrung in einem den Betätigungskolben 10 umgebenden Bereich 7A des Stellkolbens 7 zwischen einem den Stellkolben 7 umgebenden Spalt 32 und einem den Betätigungskolben 10 umgebenden Spalt 33 ausgeführt ist. About the filling device 26, the hydraulic chamber 11 during a driving or Bestromungspause the piezoelectric actuator 3 to compensate for a leakage amount the low-pressure region 27 with hydraulic fluid refilled from the high pressure area 28. For this opens a channel-like cavity 31 in the system pressure chamber 24 of the low pressure region 27, which as a bore in a region surrounding the actuating piston 10 7A of the adjusting piston 7 between a the adjusting piston 7 surrounding gap 32 and an actuating piston 10 surrounding gap 33 is executed.

Es versteht sich, daß auch andere konstruktive Ausgestaltungen des Systemdruckraumes denkbar sind und daß die Befülleinrichtung 26 eine geeignete Drosselung gegenüber dem Hochdruckbereich 28 sowie eine geeignete Vorrichtung zum Ablassen eines Überdruckes aufweisen kann.It is understood that other structural configurations the system pressure chamber are conceivable and that the filling device 26 faces a suitable throttling the high pressure area 28 and a suitable Have device for releasing an overpressure can.

Das Kraftstoffeinspritzventil 1 gemäß der Figur arbeitet in nachfolgend beschriebener Weise.The fuel injection valve 1 according to the figure works in the manner described below.

In geschlossenem Zustand des Kraftstoffeinspritzventils 1, d.h. bei unbestromtem piezoelektrischen Aktor 3, wird das Ventilschließglied 9 des Ventilglieds 2 durch den Hochdruck bzw. Raildruck in dem Hochdruckbereich 28 in Anlage an dem oberen Ventilsitz 19 gehalten, so daß kein Kraftstoff aus dem mit einem für mehrere Kraftstoffeinspritzventile gemeinsamen Hochdruckspeicherraum (Common-Rail) verbundenen Ventilsteuerraum 12 in den ersten Ventilraum 22 gelangen und dann durch den Leckageablaufkanal 23 entweichen kann.In the closed state of the fuel injection valve 1, i. with no-current piezoelectric actuator 3, the valve closing member 9 of the valve member 2 by the high pressure or rail pressure in the high pressure area 28th held in contact with the upper valve seat 19, so that no fuel from the one with multiple fuel injectors common high pressure storage room (Common Rail) connected valve control chamber 12 in the pass first valve chamber 22 and then through the leakage drainage channel 23 can escape.

Bei einer langsamen Betätigung, wie sie bei einer temperaturbedingten Langenänderung des piezoelektrischen Aktors 3 oder weiterer Ventilbauteile auftritt, drückt der Stellkolben 7 unter Verkleinerung des Ausgleichsvolumens der Hydraulikkammer 11 in Ventilsitzrichtung und zieht sich bei Temperaturabsenkung entsprechend zurück, ohne daß dies Auswirkungen auf die Schließ- und Öffnungsstellung des Ventilgliedes 2 und des Kraftstoffventils 1 insgesamt hat. In a slow operation, as in a temperature-related Longitudinal change of the piezoelectric Actuator 3 or other valve components occurs, presses the adjusting piston 7 with reduction of the compensation volume the hydraulic chamber 11 in the valve seat direction and retracts accordingly when the temperature drops without affecting the closing and opening position the valve member 2 and the fuel valve 1 in total.

Zur Kraftstoffeinspritzung muß das Ventilschließglied 9 gegen die Strömungsrichtung und damit gegen den Raildruck im Hochdruckbereich 28 geöffnet werden. Die hierzu erforderliche Aktorkraft wird durch den piezoelektrischen Aktor 3 erzeugt, welcher sich bei Bestromung schlagartig axial ausdehnt und durch Verschiebung des Stellkolbens 7 in Ventilsitzrichtung einen bestimmten Druck in der Hydraulikkammer 11 aufbaut. Damit wird über die Hydraulikkammer 11 auf den Betätigungskolben 10 sowie das Reduzierelement bzw. den Bolzen 14 eine hydraulische Kraft ausgeübt, welche der Kraft des piezoelektrischen Aktors 3 entspricht. Da bei der gezeigten Ausführung das Reduzierelement 14 an dem Absatz 15 in der Bohrung 8 des Ventilkörpers 5 abgestützt ist, wird lediglich der Betätigungskolben 10 um einen umso größeren Hub bewegt, je größer die Querschnittsfläche A2 des Reduzierelements 14 im Vergleich zu der Querschnittsfläche A1 des Betätigungskolbens 10 ist.For fuel injection, the valve closing member must be 9 against the flow direction and thus against the Rail pressure in the high pressure area 28 are opened. The This actuator force required by the piezoelectric Actuator 3 generated, which is energized abruptly expands axially and by displacement the actuating piston 7 in the valve seat direction a certain Pressure in the hydraulic chamber 11 builds. This will be via the hydraulic chamber 11 to the actuating piston 10 and the reducing element or the bolt 14 a exerted hydraulic force, which is the force of the piezoelectric Actuator 3 corresponds. As shown at the Execution of the reducing element 14 on the paragraph 15th is supported in the bore 8 of the valve body 5, only the actuating piston 10 is the more larger stroke moves, the larger the cross-sectional area A2 of the reducing element 14 in comparison to the cross-sectional area A1 of the actuating piston 10 is.

Bei dem in der Figur gezeigten Doppelsitzventil wird dabei das Ventilschließglied 9 in eine Mittelstellung zwischen den beiden Ventilsitzen 19, 20 gebracht und anschließend in eine Schließstellung an den unteren Ventilsitz 20 bewegt, wodurch kein Kraftstoff mehr aus dem Ventilsteuerraum 12 in den ersten Ventilraum 22 gelangt.In the double-seat valve shown in the figure while the valve closure member 9 in a middle position placed between the two valve seats 19, 20 and then in a closed position to the lower Valve seat 20 moves, causing no more fuel the valve control chamber 12 into the first valve chamber 22 passes.

Wenn die Bestromung des piezoelektrischen Aktors 3 unterbrochen wird, verkürzt sich dieser wieder, und das Ventilschließglied 9 wird in die Mittelstellung zwischen die beiden Ventilsitze 19, 20 gebracht, wobei eine erneute Kraftstoffeinspritzung erfolgt. Nach dem Druckabbau in dem Ventilraum 22 durch den Leckageablaufkanal 23 bewegt sich das Ventilschließglied 9 in seine Schließstellung zum oberen Ventilsitz 19, in der es durch die Federeinrichtung 21 gehalten wird.When the energization of the piezoelectric actuator 3 is interrupted becomes shorter again, and that Valve closure member 9 is in the middle position between brought the two valve seats 19, 20, wherein a re-fuel injection takes place. After this Pressure reduction in the valve chamber 22 through the leakage drainage channel 23, the valve closing member 9 moves in its closed position to the upper valve seat 19, in the it is held by the spring means 21.

Bei jeder Ansteuerung des piezoelektrischen Aktors 3 wird eine Kraftstoffeinspritzung und eine erforderliche Wiederbefüllung der Hydraulikkammer 11 bei dem erfindungsgemäßen Ventil 1 durchgeführt, wobei im Hochdruckbereich 28 durch axiale Bewegungen eines Ventilsteuerkolbens in dem Ventilsteuerraum 12 eine Einspritzdüse auf an sich bekannte Art mit Kraftstoff versorgt wird.Each time the piezoelectric actuator 3 is activated becomes a fuel injection and a required Refilling the hydraulic chamber 11 in the inventive Valve 1 performed, being in the high pressure area 28 by axial movements of a valve spool in the valve control chamber 12, an injection nozzle is supplied in a known per se with fuel.

Wenngleich sich das Ausführungsbeispiel auf ein nicht kraftausgegliches Kraftstoffeinspritzventil bezieht, kann die Erfindung selbstverständlich auch bei kraftausgeglichen gestalteten Ventilen Verwendung finden. Die Erfindung ist auch nicht auf Kraftstoffeinspritzventile beschränkt, sondern sie eignet sich bei allen Ventilen mit einer piezoelektrischen Aktuatorik, bei denen ein Ventilschließglied einen Hochdruckbereich von einem Niederdruckbereich trennt, wie z.B. in Pumpen.Although the embodiment is not a power balanced fuel injector, Of course, the invention can also be balanced with force designed valves are used. The invention is not limited to fuel injectors limited, but it is suitable for everyone Valves with a piezoelectric actuator, at where a valve closure member is a high pressure area of separates a low pressure region, such as in pumps.

Claims (11)

  1. Valve for controlling liquids, having a piezoelectric unit (3) for actuating a valve member (2), which can be displaced in a bore (8) of a valve body (5) and has at least one adjusting piston (7) and at least one actuating piston (10) for actuating a valve-closing member (9), which interacts with at least one valve seat (19, 20), which is provided on the valve body (5), in order to open and close the valve (1), and having a hydraulic chamber (11), which operates as a tolerance-compensating member and as a hydraulic transmission, between the adjusting piston (7) and actuating piston (10), characterized in that the adjusting piston (7) has a blind bore (12), which is open in the valve seat direction and in which the actuating piston (10) is mounted displaceably and bound in the hydraulic chamber (11), a cross-sectional surface (A0) of the adjusting piston (7), which surface is adjacent in each case to the hydraulic chamber (11), corresponding at least approximately to a smaller cross-sectional surface (A1) of the actuating piston (10) together with a cross-sectional surface (A2) of at least one reducing member (14), and a transmission being provided in such a manner that the actuating piston (10) can be displaced in the valve seat direction for at least a partial length of its maximum stroke travel while the at least one reducing member (14) is supported on a stop (15) in the bore (8).
  2. Valve according to Claim 1, characterized in that a stepped transmission is provided in such a manner that the actuating piston (10) together with the at least one reducing member (14) can be displaced for a first partial length of its maximum stroke travel, and in that the actuating piston (10), after reaching the stop (15) for the at least one reducing member (14), executes a remaining stroke travel.
  3. Valve according to Claim 1 or 2, characterized in that the at least one reducing member is designed as a pin (14) which is inserted into a passage bore (17) formed axially in the actuating piston (10).
  4. Valve according to Claim 3, characterized in that the length of the pin or of the pins (14) is greater than the length of the region (10A) of the actuating piston (10) with its cross-sectional surface (A1).
  5. Valve according to one of Claims 1 to 4, characterized in that the cross section of the actuating piston (10) tapers counter to a bearing surface (16) for the valve-closing member (9).
  6. Valve according to one of Claims 1 to 5, characterized in that the stop (15) for the reducing member or the reducing members (14) is designed as a step in the bore (8) of the valve body (5), preferably on a dividing surface of the valve body (5).
  7. Valve according to one of Claims 1 to 6, characterized in that the actuating piston (10) is adjacent to a first valve space (22), in which the at least one seat (19, 20) for the valve-closing member (9) is provided, the valve-closing member (9) separating a low-pressure region (27) in the valve (1) from a high-pressure region (28), and in that the adjusting piston (7) is surrounded by a second valve space (29) in a region adjoining the bore (8) of the valve body (5).
  8. Valve according to Claim 7, characterized in that a filling device (26) is provided to compensate for an amount of leakage from the low-pressure region (27) due to removal of hydraulic fluid from the high-pressure region (28), the filling device (26) being formed in the valve body (5) with a channel-like cavity (31) which opens into a system pressure space (24) of the low-pressure region (27), preferably into a gap (32, 33) surrounding the adjusting piston (7) and/or the actuating piston (10), and which, on the high-pressure side, preferably opens into the first valve space (22).
  9. Valve according to Claim 8, characterized in that the system pressure space (24) is designed as a bore in a region (7A) of the adjusting piston (7), which region surrounds the actuating piston (10), the system pressure space (24) opening into the gap (33) surrounding the actuating piston (10).
  10. Valve according to one of Claims 1 to 9, characterized in that it is designed to be inherently not force-compensated.
  11. Valve according to one of Claims 1 to 10, characterized by its use as part of a fuel injection valve for internal combustion engines, in particular of a common-rail injector (1).
EP01921223A 2000-04-20 2001-03-21 Valve for controlling liquids Expired - Lifetime EP1276983B1 (en)

Applications Claiming Priority (3)

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DE10019767 2000-04-20
DE10019767A DE10019767A1 (en) 2000-04-20 2000-04-20 Valve for controlling liquids
PCT/DE2001/001074 WO2001081751A1 (en) 2000-04-20 2001-03-21 Valve for controlling liquids

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EP1276983B1 true EP1276983B1 (en) 2005-07-06

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JP (1) JP2003532000A (en)
AT (1) ATE299239T1 (en)
CZ (1) CZ20014520A3 (en)
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WO (1) WO2001081751A1 (en)

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DE10145620B4 (en) * 2001-09-15 2006-03-02 Robert Bosch Gmbh Valve for controlling fluids
DE102004005456A1 (en) * 2004-02-04 2005-08-25 Robert Bosch Gmbh Fuel injector with direct-acting injection valve member
US7100577B2 (en) * 2004-06-14 2006-09-05 Westport Research Inc. Common rail directly actuated fuel injection valve with a pressurized hydraulic transmission device and a method of operating same
DE102009027187A1 (en) * 2009-06-25 2010-12-30 Robert Bosch Gmbh fuel injector

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WO2001023754A1 (en) * 1999-09-30 2001-04-05 Robert Bosch Gmbh Valve for controlling a liquid

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ATE192263T1 (en) * 1990-09-25 2000-05-15 Siemens Ag ARRANGEMENT FOR AN ADAPTIVE, MECHANICAL TOLERANCE COMPENSATION FOR THE DISTANCE TRANSFORMER OF A PIEZOELECTRIC ACTUATOR, ACTING IN THE STROKE DIRECTION
DE4406522C1 (en) * 1994-02-28 1995-07-13 Siemens Ag Electrohydraulic drive element for e.g. injection valve
DE19500706C2 (en) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Metering valve for dosing liquids or gases
DE19732802A1 (en) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19821768C2 (en) * 1998-05-14 2000-09-07 Siemens Ag Dosing device and dosing method
DE19946830A1 (en) * 1999-09-30 2001-05-03 Bosch Gmbh Robert Valve for controlling liquids
DE19946833C2 (en) * 1999-09-30 2002-02-21 Bosch Gmbh Robert Valve for controlling liquids
DE19946838C1 (en) * 1999-09-30 2000-10-19 Bosch Gmbh Robert Fluid control valve e.g. fuel injection valve for IC engine, has piezoelectric unit coupled to sliding valve element via lever arm setting element for length tolerance compensation

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Publication number Priority date Publication date Assignee Title
WO2001023754A1 (en) * 1999-09-30 2001-04-05 Robert Bosch Gmbh Valve for controlling a liquid

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ATE299239T1 (en) 2005-07-15
DE50106694D1 (en) 2005-08-11
US20030098429A1 (en) 2003-05-29
JP2003532000A (en) 2003-10-28
EP1276983A1 (en) 2003-01-22
CZ20014520A3 (en) 2003-03-12
WO2001081751A1 (en) 2001-11-01
DE10019767A1 (en) 2001-10-31
US6651950B2 (en) 2003-11-25

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