EP1135593B1 - Valve for controlling fluids - Google Patents

Valve for controlling fluids Download PDF

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Publication number
EP1135593B1
EP1135593B1 EP00974318A EP00974318A EP1135593B1 EP 1135593 B1 EP1135593 B1 EP 1135593B1 EP 00974318 A EP00974318 A EP 00974318A EP 00974318 A EP00974318 A EP 00974318A EP 1135593 B1 EP1135593 B1 EP 1135593B1
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EP
European Patent Office
Prior art keywords
valve
pressure
low
piston
chamber
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EP00974318A
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German (de)
French (fr)
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EP1135593A1 (en
Inventor
Wolfgang Stoecklein
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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention is based on a valve for controlling Liquids according to the preamble of claim 1.
  • the hydraulic chamber closes between two limiting them Pistons, one of which is a piston with a smaller diameter is formed and with a valve member to be controlled is connected and the other piston with a larger diameter is formed and with the piezoelectric Actuator is connected, a common compensation volume one.
  • the hydraulic chamber is so between the clamped two pistons that the actuating piston of the Valve member, in its rest position by means of a or several springs relative to a predetermined position is held, 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 actuators lie on a common Axis in a row.
  • About the equalization volume of Hydraulic chamber can tolerances due to temperature gradients in the component or different thermal expansion coefficients the materials used as well any settling effects are compensated without thereby changing the position of the to be controlled Valve member occurs.
  • the hydraulic coupler requires a system pressure which drops due to leakage, if not sufficient Refilling with hydraulic fluid takes place.
  • the invention has for its object to provide a valve for To create control of liquids with which the Leakage losses with increasing pressure in the high pressure range be limited.
  • the valve according to the invention for controlling fluids with the features of claim 1 has the advantage that for generating the minimum leak rate from the high pressure area in the low pressure area with system pressure one Throttle bore is used, whereby the leakage loss at high pressures in the high pressure area compared to the system pressure supply by a conventional leakage gap or Filling pen is reduced by a multiple.
  • FIG. 1 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 in the present case designed as a common rail injector, wherein the fuel injection over the pressure level in one Valve control chamber 12, which with a high pressure supply connected, is controlled.
  • a valve member 2 For setting an injection start, an injection duration and an injection amount about balance of power in the Fuel injection valve 1, a valve member 2 via a piezoelectric actuator 3 formed as a piezoelectric Unit controlled, which operates on the valve control and combustion chamber side facing away from the valve member. 2 is arranged.
  • the piezoelectric actuator 3 is composed of several layers constructed and has on its the valve member 2 facing Side an actuator head 4 and on its the valve member side facing away from an actuator base 5, which is located at a wall of a valve body 9 is supported. At the actuator head 4 is located above a support 6, a first piston 7 of the Valve member 2, which is stepped in its diameter is executed.
  • the valve member 2 is axially displaceable in a Longitudinal bore executed bore 8 of the valve body. 9 arranged and includes in addition to the first piston 7 a Valve closure member 13 actuated second piston 10, wherein the pistons 7 and 10 by means of a hydraulic transmission coupled together.
  • the hydraulic transmission is as a hydraulic chamber 11th formed, which is the deflection of the piezoelectric Actuator 3 transmits.
  • the hydraulic chamber 11 closes between the two limiting pistons 7 and 10, of those of the second piston 10 with a smaller diameter and the first piston 7 with a larger diameter is formed, a common compensation volume.
  • the hydraulic chamber 11 is between the piston 7 and 10 clamped, that the second piston 10 of the valve member 2 one to the ratio of the piston diameter increased stroke makes when the larger first piston 7 by the piezoelectric actuator 3 to a certain Distance is moved.
  • the valve member 2, the piston 7, 10th and the piezoelectric actuator 3 lie on one common axis in a row.
  • valve closing member 13 acts on the Valve body 9 formed valve seats 14, 15 together, wherein the valve closing member 13 is a low-pressure region 16 with a system pressure p_sys from a high pressure area 17 with a high pressure or rail pressure p_R separates.
  • valve seats 14, 15 are in one of the valve body. 9 formed valve low-pressure chamber 18 formed by the a leakage drain passage 19 and one to a valve system pressure chamber 20 on the piezoelectric actuator 3 facing Side of the valve member 2 leading opening 21st dissipates.
  • valve low-pressure chamber 18 has a formed by the lower valve seat 15 connection to the in Figure 1 only indicated valve control chamber 12 in the high pressure area 17.
  • valve control chamber 12 is a movable valve spool disposed in the Drawing is not shown.
  • the valve system pressure chamber 20 connects to the piezo glove End of the bore 8 and is on the one hand by the valve body 9 and on the other hand by a with the first piston. 7 the valve member 2 and the valve body 9 connected Sealing element 22 limited, with a leakage line 23 from the valve system pressure chamber 20 discharges.
  • the sealing element 22nd is presently designed as a bellows-like membrane and prevents the piezoelectric actuator 3 with the in the Valve system pressure chamber 20 contained fuel in contact comes.
  • a first piston 7 surrounding the gap 24 and a gap 25 surrounding the second piston 10 is one Leakage from the hydraulic chamber 11 in the valve low-pressure chamber 18 and in particular in the valve system pressure chamber 20 given.
  • the high pressure area 17 is provided.
  • the channel 27 of the filling device 26 opens on the Low pressure region 16 facing side of the throttle bore 28 in the first piston 7 surrounding gap 24, wherein in Mouth area an annular groove 29 is provided.
  • the channel 27 opens into the valve low pressure chamber 18th
  • the diameter of the throttle bore 28 is designed such that that a throttle bore 28 passing volume flow the high pressure area 17 at a defined minimum High pressure p_R_min the leakage quantity of the low pressure range 16 compensates.
  • the Orifice 28 has a diameter of 50 microns.
  • a connection between the throttle bore 28 and the Mouth of the channel 27 in the annular gap 29 a connection between the channel 27 of the filling device 28 and the Valve low pressure chamber 18 via a pressure relief valve 30th provided, which is spring loaded.
  • This pressure relief valve 30 is used to set a constant system pressure p_sys in the valve system pressure chamber 20, so that the system pressure for all contiguous common rail injectors can be kept the same.
  • the fuel injection valve 1 according to FIG. 1 operates in this case in the manner described below.
  • valve closure member 13 at the upper valve seat 14 by a spring 31st Upon discharge of the valve control chamber 12, the valve closure member 13 at the upper valve seat 14 by a spring 31st held.
  • the piezoelectric actuator 3 When an injection through the fuel injector 1, the piezoelectric actuator 3 is energized, making this his axial extent abruptly increased. In such a quick operation of the piezoelectric actuator 3 is based on the Valve body 9 from, whereby the second piston 10, the Valve closure member 13 of the valve member 2 from its upper Valve seat 14 in a middle position between the two Valve seats 14, 15 moves.
  • the moving membrane 22 By the adjusting movement of the Valve member 2 is due to the moving membrane 22 reduces the volume of the valve system pressure chamber 20, wherein a pressure reduction by leakage from the hydraulic chamber into the valve system pressure chamber 20 and the valve low-pressure chamber 18 and from these via the leakage line 23 and the Leakage drainage channel 19 and via the pressure relief valve 30th takes place.
  • each control (energizing or terminating the energizing) of the piezoelectric unit is a fuel injection allows.
  • the throttle bore 28 must be dimensioned so that the Provision of system pressure p_sys also at one minimum high pressure p_R_min is still secured. on the other hand also decreases with increasing high or rail pressure p_R the leakage in the low pressure area 16 too. That's why it opens the pressure relief valve 30 the more, the higher the channel 27 supplied high pressure p_R is to comply with the constant system pressure p_sys excess hydraulic fluid or to drain fuel.
  • FIG. 3 is a diagram can be seen, which shows that the throttle bore 28 while significant advantages over the realization of the filling of the low-pressure region 16 with a conventional filling pen has.

Abstract

A valve (1) for controlling liquids is proposed, having a piezoelectric unit (3) for actuating a valve member (2), which member is axially displaceable in a bore (8) of a valve body (9) and on one end has a valve closing member (13) that cooperates with at least one seat (14, 15), provided on the valve body (9), for opening and closing the valve (1). The valve closing member (13) divides a low-pressure region (16) having a system pressure (p_sys) from a high-pressure region (17). To compensate for a leakage quantity from the low-pressure region (16) by drawing hydraulic liquid from the high-pressure region (17), a filling device (26) is provided, which is embodied with a conduit (27) having a throttle bore (28). The diameter of the throttle bore is designed such that a volumetric flow that from the high-pressure region (17), which flow passes through the throttle bore (28), at a defined minimum high pressure (p_R_min) compensates for the leakage quantity from the low-pressure region (16) (FIG. 1).

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Ventil zum Steuern von Flüssigkeiten gemäß der Gattung des Patentanspruchs 1 aus.The invention is based on a valve for controlling Liquids according to the preamble of claim 1.

Aus der EP 0 477 400 A1 ist ein derartiges Ventil, welches über einen piezoelektrischen Aktor betätigbar ist, bereits bekannt. Dieses bekannte Ventil weist eine Anordnung für einen in Hubrichtung wirkenden Wegtransformator des piezoelektrischen Aktors auf, bei der die Auslenkung des piezoelektrischen Aktors über eine Hydraulikkammer übertragen wird, welche als hydraulische Übersetzung bzw. Kopplung und Toleranzausgleichselement arbeitet.From EP 0 477 400 A1 is such a valve, which is already actuated via a piezoelectric actuator known. This known valve has an arrangement for a displacement transformer acting in the stroke direction of the piezoelectric actuator, in which the deflection of the transmitted piezoelectric actuator via a hydraulic chamber is, which as a hydraulic translation or coupling and tolerance compensation element works.

Die Hydraulikkammer schließt zwischen zwei sie begrenzenden Kolben, von denen ein Kolben mit einem kleineren Durchmesser ausgebildet ist und mit einem anzusteuernden Ventilglied verbunden ist und der andere Kolben mit einem größeren Durchmesser ausgebildet ist und mit dem piezoelektrischen Aktor verbunden ist, ein gemeinsames Ausgleichsvolumen ein. Die Hydraulikkammer ist derart zwischen den beiden Kolben eingespannt, daß der Betätigungskolben des Ventilgliedes, das in seiner Ruhelage mittels einer oder mehrerer Federn relativ zu einer vorgegebenen Position gehalten ist, 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. Über das Ausgleichsvolumen der Hydraulikkammer können Toleranzen aufgrund von Temperaturgradienten im Bauteil oder unterschiedlichen Temperaturausdehnungskoeffizienten der verwendeten Materialien sowie eventuelle Setzeffekte ausgeglichen werden, ohne daß dadurch eine Änderung der Position des anzusteuernden Ventilgliedes auftritt.The hydraulic chamber closes between two limiting them Pistons, one of which is a piston with a smaller diameter is formed and with a valve member to be controlled is connected and the other piston with a larger diameter is formed and with the piezoelectric Actuator is connected, a common compensation volume one. The hydraulic chamber is so between the clamped two pistons that the actuating piston of the Valve member, in its rest position by means of a or several springs relative to a predetermined position is held, 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 actuators lie on a common Axis in a row. About the equalization volume of Hydraulic chamber can tolerances due to temperature gradients in the component or different thermal expansion coefficients the materials used as well any settling effects are compensated without thereby changing the position of the to be controlled Valve member occurs.

Der hydraulische Koppler benötigt einen Systemdruck, welcher aufgrund von Leckage abfällt, falls keine ausreichende Nachfüllung mit Hydraulikflüssigkeit stattfindet.The hydraulic coupler requires a system pressure which drops due to leakage, if not sufficient Refilling with hydraulic fluid takes place.

Aus der Praxis sind bei Common-Rail-Injektoren Lösungen bekannt, bei denen der Systemdruck zweckmäßig im Ventil selbst erzeugt wird, wobei ein konstanter Systemdruck auch bei einem Systemstart sichergestellt ist. Hierzu wird Hydraulikflüssigkeit aus einem Hochdruckbereich des zu steuernden Kraftstoffs entnommen und dem Niederdruckbereich mit dem Systemdruck zugeführt. Dies geschieht mit Hilfe von Leckspalten, die durch Leck- bzw. Befüllstifte dargestellt werden. In practice, common rail injectors are solutions known in which the system pressure appropriate in the valve self-generated, being a constant system pressure too is ensured at a system start. For this purpose is Hydraulic fluid from a high pressure area of the taken from controlling fuel and the low pressure area supplied with the system pressure. This is done with the help of Leak gaps represented by leak or filling pins become.

Wenn jedoch der Druck im Hochdruckbereich ansteigt, nimmt automatisch die Leckrate in den Systembereich zu. Dies führt unter Umständen zu einem nicht zulässigen hohen Leckverlust des Ventils, wobei der Wirkungsgrad des Systems stark abnimmt.However, when the pressure in the high pressure area increases, decreases automatically the leak rate in the system area too. This may result in an unacceptable high Leakage of the valve, the efficiency of the system decreases sharply.

Der Erfindung liegt die Aufgabe zugrunde, ein Ventil zur Steuerung von Flüssigkeiten zu schaffen, mit dem die Leckverluste bei steigendem Druck im Hochdruckbereich begrenzt werden.The invention has for its object to provide a valve for To create control of liquids with which the Leakage losses with increasing pressure in the high pressure range be limited.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Ventil zur Steuerung von Flüssigkeiten mit den Merkmalen des Patentanspruchs 1 hat den Vorteil, daß zur Erzeugung der Mindestleckrate von dem Hochdruckbereich in den Niederdruckbereich mit Systemdruck eine Drosselbohrung benutzt wird, womit der Leckageverlust bei hohen Drücken im Hochdruckbereich gegenüber der Systemdruckversorgung durch einen herkömmlichen Leckspalt bzw. Befüllstift um ein Vielfaches reduziert wird.The valve according to the invention for controlling fluids with the features of claim 1 has the advantage that for generating the minimum leak rate from the high pressure area in the low pressure area with system pressure one Throttle bore is used, whereby the leakage loss at high pressures in the high pressure area compared to the system pressure supply by a conventional leakage gap or Filling pen is reduced by a multiple.

Dabei werden auf einfache Art und Weise die grundlegend unterschiedlichen stömungsphysikalischen Effekte zwischen der turbulenten Durchströmung einer Drosselbohrung und der laminaren Spaltströmung um einen Befüllstift zur Realisierung der Befüllung des Niederdruckbereiches genutzt.This is the basic way in a simple way different flow physical effects between the turbulent flow through a throttle bore and the laminar flow around a filling pen for realization the filling of the low pressure area used.

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. Es zeigen

  • Figur 1 eine schematische, ausschnittsweise Darstellung eines Ausführungsbeispiels der Erfindung bei einem Kraftstoffeinspritzventil für Brennkraftmaschinen im Längsschnitt, und
  • Figur 2 ein Diagramm mit einem stark vereinfachten Verlauf einer druckabhängigen Leckmenge bei einer erfindungsgemäßen Drosselbohrung im Vergleich zu der druckabhängigen Leckmenge bei einem Befüllstift.
    • An embodiment of the inventive valve for controlling fluids is shown in the drawing and will be explained in more detail in the following description. Show it
  • Figure 1 is a schematic, fragmentary view of an embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section, and
  • FIG. 2 shows a diagram with a greatly simplified course of a pressure-dependent leakage quantity in the case of a throttle bore according to the invention in comparison to the pressure-dependent leakage quantity in the case of a filling pen.

    • Beschreibung des AusführungsbeispielsDescription of the embodiment

    Das in der Figur 1 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 Kraftstoffeinspritzung über das Druckniveau in einem Ventilsteuerraum 12, welcher mit einer Hochdruckversorgung verbunden ist, gesteuert wird.The embodiment shown in Figure 1 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 in the present case designed as a common rail injector, wherein the fuel injection over the pressure level in one Valve control chamber 12, which with a high pressure supply connected, is controlled.

    Zur Einstellung eines Einspritzbeginns, einer Einspritzdauer und einer Einspritzmenge über Kräfteverhältnisse in dem Kraftstoffeinspritzventil 1 wird ein Ventilglied 2 über eine als piezoelektrischer Aktor 3 ausgebildete piezoelektrische Einheit angesteuert, welche auf der ventilsteuerraum- und brennraumabgewandten Seite des Ventilgliedes 2 angeordnet ist.For setting an injection start, an injection duration and an injection amount about balance of power in the Fuel injection valve 1, a valve member 2 via a piezoelectric actuator 3 formed as a piezoelectric Unit controlled, which operates on the valve control and combustion chamber side facing away from the valve member. 2 is arranged.

    Der piezoelektrische Aktor 3 ist aus mehreren Schichten aufgebaut und weist auf seiner dem Ventilglied 2 zugewandten Seite einen Aktorkopf 4 sowie auf seiner dem Ventilglied abgewandten Seite einen Aktorfuß 5 auf, der sich an einer Wand eines Ventilkörpers 9 abstützt. An dem Aktorkopf 4 liegt über ein Auflager 6 ein erster Kolben 7 des Ventilgliedes 2 an, welcher in seinem Durchmesser gestuft ausgeführt ist.The piezoelectric actuator 3 is composed of several layers constructed and has on its the valve member 2 facing Side an actuator head 4 and on its the valve member side facing away from an actuator base 5, which is located at a wall of a valve body 9 is supported. At the actuator head 4 is located above a support 6, a first piston 7 of the Valve member 2, which is stepped in its diameter is executed.

    Das Ventilglied 2 ist axial verschiebbar in einer als Längsbohrung ausgeführten Bohrung 8 des Ventilkörpers 9 angeordnet und umfaßt neben dem ersten Kolben 7 einen ein Ventilschließglied 13 betätigenden zweiten Kolben 10, wobei die Kolben 7 und 10 mittels einer hydraulischen Übersetzung miteinander gekoppelt sind.The valve member 2 is axially displaceable in a Longitudinal bore executed bore 8 of the valve body. 9 arranged and includes in addition to the first piston 7 a Valve closure member 13 actuated second piston 10, wherein the pistons 7 and 10 by means of a hydraulic transmission coupled together.

    Die hydraulische Übersetzung ist als Hydraulikkammer 11 ausgebildet, die die Auslenkung des piezoelektrischen Aktors 3 überträgt. Die Hydraulikkammer 11 schließt zwischen den beiden sie begrenzenden Kolben 7 und 10, von denen der zweite Kolben 10 mit einem kleineren Durchmesser und der erste Kolben 7 mit einem größeren Durchmesser ausgebildet ist, ein gemeinsames Ausgleichsvolumen ein.The hydraulic transmission is as a hydraulic chamber 11th formed, which is the deflection of the piezoelectric Actuator 3 transmits. The hydraulic chamber 11 closes between the two limiting pistons 7 and 10, of those of the second piston 10 with a smaller diameter and the first piston 7 with a larger diameter is formed, a common compensation volume.

    Die Hydraulikkammer 11 ist derart zwischen den Kolben 7 und 10 eingespannt, daß der zweite Kolben 10 des Ventilgliedes 2 einen um das Übersetzungsverhältnis des Kolbendurchmessers vergrößerten Hub macht, wenn der größere erste Kolben 7 durch den piezoelektrischen Aktor 3 um eine bestimmte Wegstrecke bewegt wird. Das Ventilglied 2, die Kolben 7, 10 und der piezoelektrische Aktor 3 liegen dabei auf einer gemeinsamen Achse hintereinander.The hydraulic chamber 11 is between the piston 7 and 10 clamped, that the second piston 10 of the valve member 2 one to the ratio of the piston diameter increased stroke makes when the larger first piston 7 by the piezoelectric actuator 3 to a certain Distance is moved. The valve member 2, the piston 7, 10th and the piezoelectric actuator 3 lie on one common axis in a row.

    Über das Ausgleichsvolumen der Hydraulikkammer 11 können Toleranzen aufgrund von Temperaturgradienten im Bauteil oder unterschiedlichen Temperaturausdehnungskoeffizienten der verwendeten Materialien sowie eventuelle Setzeffekte ausgeglichen werden, ohne daß dadurch eine Änderung der Position des anzusteuernden Ventilschließgliedes 13 auftritt.About the compensating volume of the hydraulic chamber 11 can Tolerances due to temperature gradients in the component or different coefficients of thermal expansion the materials used as well as possible setting effects be compensated, without thereby changing the Position of the valve closing member 13 to be controlled occurs.

    An dem ventilsteuerraumseitigen Ende des Ventilgliedes 2 wirkt das kugelartige Ventilschließglied 13 mit an dem Ventilkörper 9 ausgebildeten Ventilsitzen 14, 15 zusammen, wobei das Ventilschließglied 13 einen Niederdruckbereich 16 mit einem Systemdruck p_sys von einem Hochdruckbereich 17 mit einem Hochdruck bzw. Raildruck p_R trennt.At the valve control chamber end of the valve member. 2 the ball-like valve closing member 13 acts on the Valve body 9 formed valve seats 14, 15 together, wherein the valve closing member 13 is a low-pressure region 16 with a system pressure p_sys from a high pressure area 17 with a high pressure or rail pressure p_R separates.

    Die Ventilsitze 14, 15 sind in einem von dem Ventilkörper 9 gebildeten Ventilniederdruckraum 18 ausgebildet, von dem ein Leckageablaufkanal 19 und eine zu einem Ventilsystemdruckraum 20 auf der dem piezoelektrischen Aktor 3 zugewandten Seite des Ventilgliedes 2 führende Öffnung 21 abführt.The valve seats 14, 15 are in one of the valve body. 9 formed valve low-pressure chamber 18 formed by the a leakage drain passage 19 and one to a valve system pressure chamber 20 on the piezoelectric actuator 3 facing Side of the valve member 2 leading opening 21st dissipates.

    Darüber hinaus weist der Ventilniederdruckraum 18 eine durch den unteren Ventilsitz 15 gebildete Verbindung zu dem in Figur 1 lediglich angedeuteten Ventilsteuerraum 12 in dem Hochdruckbereich 17 auf. In dem Ventilsteuerraum 12 ist ein bewegbarer Ventilsteuerkolben angeordnet, der in der Zeichnung nicht weiter dargestellt ist. Durch axiale Bewegungen des Ventilsteuerkolbens in dem Ventilsteuerraum 12, der in üblicher Weise mit einer Einspritzleitung verbunden ist, welche mit einem für mehrere Kraftstoffeinspritzventile gemeinsamen Hochdruckspeicherraum (Common-Rail) verbunden ist und eine Einspritzdüse mit Kraftstoff versorgt, wird das Einspritzverhalten des Kraftstoffeinspritzventils 1 auf an sich bekannte Art gesteuert.In addition, the valve low-pressure chamber 18 has a formed by the lower valve seat 15 connection to the in Figure 1 only indicated valve control chamber 12 in the high pressure area 17. In the valve control chamber 12 is a movable valve spool disposed in the Drawing is not shown. By axial Movements of the valve spool in the valve control chamber 12, in the usual way with an injection line connected, which with one for several fuel injection valves common high-pressure storage space (common rail) is connected and an injector with fuel supplied, the injection behavior of the fuel injection valve 1 controlled in a known per se.

    Der Ventilsystemdruckraum 20 schließt an das piezoseitige Ende der Bohrung 8 an und ist einerseits durch den Ventilkörper 9 und andererseits durch ein mit dem ersten Kolben 7 des Ventilgliedes 2 und dem Ventilkörper 9 verbundenes Dichtelement 22 begrenzt, wobei eine Leckageleitung 23 aus dem Ventilsystemdruckraum 20 abführt. Das Dichtelement 22 ist vorliegend als faltenbalgartige Membran ausgebildet und verhindert, daß der piezoelektrische Aktor 3 mit dem in dem Ventilsystemdruckraum 20 enthaltenen Kraftstoff in Kontakt kommt.The valve system pressure chamber 20 connects to the piezoseitige End of the bore 8 and is on the one hand by the valve body 9 and on the other hand by a with the first piston. 7 the valve member 2 and the valve body 9 connected Sealing element 22 limited, with a leakage line 23 from the valve system pressure chamber 20 discharges. The sealing element 22nd is presently designed as a bellows-like membrane and prevents the piezoelectric actuator 3 with the in the Valve system pressure chamber 20 contained fuel in contact comes.

    Über einen den ersten Kolben 7 umgebenden Spalt 24 und einen den zweiten Kolben 10 umgebenden Spalt 25 ist eine Leckage von der Hydraulikkammer 11 in den Ventilniederdruckraum 18 und insbesondere in den Ventilsystemdruckraum 20 gegeben.About a first piston 7 surrounding the gap 24 and a gap 25 surrounding the second piston 10 is one Leakage from the hydraulic chamber 11 in the valve low-pressure chamber 18 and in particular in the valve system pressure chamber 20 given.

    Da die Hydraulikkammer 11 während einer Ansteuer- bzw. Bestromungspause des piezoelektrischen Aktors 3 wiederbefüllt werden muß, ist ein Ausgleich einer Leckagemenge des Niederdruckbereiches 16 durch Entnahme von Hydraulikflüssigkeit des Hochdruckbereichs 17 vorgesehen. Hierzu dient eine Befülleinrichtung 26, welche mit einem Kanal 27, in dem eine Drosselbohrung 28 angeordnet ist, ausgebildet ist. Der Kanal 27 der Befülleinrichtung 26 mündet auf der dem Niederdruckbereich 16 zugewandten Seite der Drosselbohrung 28 in den den ersten Kolben 7 umgebenden Spalt 24, wobei im Mündungsbereich eine Ringnut 29 vorgesehen ist. Auf der dem Hochdruckbereich 17 zugewandten Seite der Drosselbohrung 28 mündet der Kanal 27 in den Ventilniederdruckraum 18.Since the hydraulic chamber 11 during a drive or Refreshment break of the piezoelectric actuator 3 refilled must be a compensation for a leakage amount of the Low pressure range 16 by removal of hydraulic fluid the high pressure area 17 is provided. Serves for this purpose a filling device 26, which with a channel 27, in a throttle bore 28 is arranged, is formed. The channel 27 of the filling device 26 opens on the Low pressure region 16 facing side of the throttle bore 28 in the first piston 7 surrounding gap 24, wherein in Mouth area an annular groove 29 is provided. On the High pressure region 17 facing side of the throttle bore 28th the channel 27 opens into the valve low pressure chamber 18th

    Selbstverständlich kann in einer alternativen Ausführung auch vorgesehen sein, daß der Kanal 27 der Befülleinrichtung 26 zu dem den zweiten Kolben 10 umgebenden Spalt 25 führt.Of course, in an alternative embodiment Also be provided that the channel 27 of the filling 26 to the second piston 10 surrounding gap 25th leads.

    Der Durchmesser der Drosselbohrung 28 ist derart ausgelegt, daß ein die Drosselbohrung 28 passierender Volumenstrom aus dem Hochdruckbereich 17 bei einem definierten minimalen Hochdruck p_R_min die Leckagemenge des Niederdruckbereiches 16 ausgleicht. In der gezeigten Ausführung weist die Drosselbohrung 28 einen Durchmesser von 50 Mikrometer auf.The diameter of the throttle bore 28 is designed such that that a throttle bore 28 passing volume flow the high pressure area 17 at a defined minimum High pressure p_R_min the leakage quantity of the low pressure range 16 compensates. In the embodiment shown, the Orifice 28 has a diameter of 50 microns.

    Des weiteren ist zwischen der Drosselbohrung 28 und der Mündung des Kanals 27 in den Ringspalt 29 eine Verbindung zwischen dem Kanal 27 der Befülleinrichtung 28 und dem Ventilniederdruckraum 18 über ein Überdruckventil 30 vorgesehen, welches federbelastet ist. Dieses Überdruckventil 30 dient zur Einstellung eines konstanten Systemdrucks p_sys in dem Ventilsystemdruckraum 20, so daß der Systemdruck bei allen zusammenhängenden Common-Rail-Injektoren gleich gehalten werden kann.Furthermore, between the throttle bore 28 and the Mouth of the channel 27 in the annular gap 29 a connection between the channel 27 of the filling device 28 and the Valve low pressure chamber 18 via a pressure relief valve 30th provided, which is spring loaded. This pressure relief valve 30 is used to set a constant system pressure p_sys in the valve system pressure chamber 20, so that the system pressure for all contiguous common rail injectors can be kept the same.

    Das Kraftstoffeinspritzventil 1 nach Figur 1 arbeitet dabei in nachfolgend beschriebener Weise.The fuel injection valve 1 according to FIG. 1 operates in this case in the manner described below.

    In geschlossenem Zustand des Kraftstoffeinspritzventils 1, d.h. bei unbestromtem piezoelektrischen Aktor 3 wird das Ventilschließglied 13 des Ventilglieds 2 durch den Hochdruck bzw. Raildruck p_R in dem Hochdruckbereich 17 in Anlage an dem ihm zugeordneten oberen Ventilsitz 14 gehalten, so daß kein Kraftstoff aus dem mit dem Hochdruckspeicherraum verbundenen Ventilsteuerraum 12 in den Ventilniederdruckraum 18 gelangen und dann durch den Leckageablaufkanal 19 entweichen kann.In the closed state of the fuel injection valve 1, i.e. when no current supplied piezoelectric actuator 3 is the Valve closure member 13 of the valve member 2 by the high pressure or rail pressure p_R in the high-pressure region 17 in FIG Attachment to the associated upper valve seat 14th held so that no fuel from the with the high-pressure reservoir connected valve control chamber 12 in the Valve low pressure chamber 18 and then pass through the Leak drainage channel 19 can escape.

    Bei Entlastung des Ventilsteuerraums 12 wird das Ventilschließglied 13 am oberen Ventilsitz 14 durch eine Feder 31 gehalten.Upon discharge of the valve control chamber 12, the valve closure member 13 at the upper valve seat 14 by a spring 31st held.

    Im Falle einer langsamen Betätigung, wie sie bei einer temperaturbedingten Längenänderung des piezoelektrischen Aktors 3 oder weiterer Ventilbauteile wie z.B. des Ventilglieds 2 oder des Ventilkörper 9 auftritt, dringt der erste Kolben 7 mit Temperaturerhöhung in das Ausgleichsvolumen der Hydraulikkammer 11 ein oder zieht sich bei Temperaturabsenkung daraus zurück, ohne daß dies Auswirkungen auf die Schließ- und Öffnungsstellung des Ventilgliedes 2 und des Kraftstoffventils 1 insgesamt hat. In the case of a slow operation, as with a temperature-induced change in length of the piezoelectric Actuator 3 or other valve components such. of the valve member 2 or the valve body 9 occurs, the first penetrates Piston 7 with temperature increase in the compensation volume the hydraulic chamber 11 or retracts when the temperature is lowered from this, without affecting the Closing and opening position of the valve member 2 and the Fuel valve 1 has a total.

    Wenn eine Einspritzung durch das Kraftstoffeinspritzventil 1 erfolgen soll, wird der piezoelektrische Aktor 3 bestromt, wodurch dieser seine axiale Ausdehnung schlagartig vergrößert. Bei einer derartigen schnellen Betätigung des piezoelektrischen Aktors 3 stützt sich dieser an dem Ventilkörper 9 ab, wodurch der zweite Kolben 10 das Ventilschließglied 13 des Ventilgliedes 2 von seinem oberen Ventilsitz 14 in eine Mittelstellung zwischen den beiden Ventilsitzen 14, 15 bewegt. Durch die Stellbewegung des Ventilgliedes 2 wird aufgrund der sich bewegenden Membran 22 das Volumen des Ventilsystemdruckraumes 20 verringert, wobei ein Druckabbau durch Leckage von der Hydraulikkammer in den Ventilsystemdruckraum 20 und den Ventilniederdruckraum 18 und aus diesen über die Leckageleitung 23 und den Leckageablaufkanal 19 sowie über das Überdruckventil 30 stattfindet.When an injection through the fuel injector 1, the piezoelectric actuator 3 is energized, making this his axial extent abruptly increased. In such a quick operation of the piezoelectric actuator 3 is based on the Valve body 9 from, whereby the second piston 10, the Valve closure member 13 of the valve member 2 from its upper Valve seat 14 in a middle position between the two Valve seats 14, 15 moves. By the adjusting movement of the Valve member 2 is due to the moving membrane 22 reduces the volume of the valve system pressure chamber 20, wherein a pressure reduction by leakage from the hydraulic chamber into the valve system pressure chamber 20 and the valve low-pressure chamber 18 and from these via the leakage line 23 and the Leakage drainage channel 19 and via the pressure relief valve 30th takes place.

    Nach Ablassen des den Systemdruck p_sys übersteigenden Drucks in dem Niederdruckbereich 16 kann das Ventilschließglied 13 in seine Schließstellung an den unteren Ventilsitz 15 bewegt werden, wodurch kein Kraftstoff mehr aus dem Ventilsteuerraum 12 in den Ventilniederdruckraum 18 eindringen kann. Die Kraftstoffeinspritzung ist dann beendet.After releasing the system pressure p_sys exceeding Pressure in the low pressure region 16 may be the valve closure member 13 in its closed position to the lower valve seat 15 are moved, causing no more fuel from the Valve control chamber 12 in the valve low pressure chamber 18th can penetrate. The fuel injection is then completed.

    Danach wird die Bestromung des piezoelektrischen Aktors 3 unterbrochen, wodurch sich dieser wieder verkürzt und das Ventilschließglied 13 in die Mittelstellung zwischen die beiden Ventilsitze 14, 15 gebracht wird, wobei eine erneute Kraftstoffeinspritzung erfolgt. Durch den unteren Ventilsitz kann Kraftstoff in den Ventilniederdruckraum 18 eindringen. Dabei wird durch eine in dem Leckageablaufkanal 19 angeordnete Drossel 32 der Druck jedoch nicht sofort abgebaut. Die kurzzeitige Druckerhöhung in dem Ventilniederdruckraum 18 bewirkt eine hydraulische Gegenkraft, welche die Stellbewegung des Ventilgliedes 2 derart abbremst, daß das Ventilschließglied 13 in seiner Mittelstellung zwischen den beiden Ventilsitzen 14, 15 stabilisiert wird.Thereafter, the energization of the piezoelectric actuator 3rd interrupted, whereby this shortened again and the Valve closure member 13 in the middle position between the two valve seats 14, 15 is brought, with a renewed Fuel injection takes place. Through the lower valve seat can fuel in the valve low pressure chamber 18th penetration. It is characterized by a in the leakage drainage channel 19 arranged throttle 32, the pressure but not immediately reduced. The short-term pressure increase in the valve low pressure chamber 18 causes a hydraulic counterforce, which the adjusting movement of the valve member 2 so decelerates that the valve closing member 13 in its center position stabilized between the two valve seats 14, 15 becomes.

    Nach dem Druckabbau in dem Ventilniederdruckraum 18 durch den Leckageablaufkanal 19 bewegt sich das Ventilschließglied 13 in seine Schließstellung zum oberen Ventilsitz 14. Somit wird durch jede Ansteuerung (Bestromen oder Beenden des Bestromens) der piezoelektrischen Einheit eine Kraftstoffeinspritzung ermöglicht.After the pressure reduction in the valve low-pressure chamber 18 through the leakage drain passage 19, the valve closing member moves 13 in its closed position to the upper valve seat 14th Thus, by each control (energizing or terminating the energizing) of the piezoelectric unit is a fuel injection allows.

    Wenn das Ventilschließglied 13 von seinem unteren Ventilsitz 15 abgehoben ist, wird dem Kanal 27 der Befülleinrichtung 26 Hochdruck p_R aus dem Ventilsteuerraum 12 zugeführt, so daß die Leckageverluste in dem Niederdruckbereich 16 ausgeglichen werden können.When the valve closing member 13 from its lower valve seat 15 is lifted, the channel 27 of the filling device 26 high-pressure p_R supplied from the valve control chamber 12, so that the leakage losses in the low pressure area 16 can be compensated.

    Da stets ein bestimmter Systemdruck p_sys benötigt wird, muß die Drosselbohrung 28 so dimensioniert sein, daß die Bereitstellung des Systemdrucks p_sys auch bei einem minimalen Hochdruck p_R_min noch gesichert ist. Andererseits nimmt mit steigendem Hoch- bzw. Raildruck p_R auch die Leckage in den Niederdruckbereich 16 zu. Deshalb öffnet das Überdruckventil 30 um so mehr, je höher der dem Kanal 27 zugeführte Hochdruck p_R ist, um zur Einhaltung des konstanten Systemdrucks p_sys überschüssige Hydraulikflüssigkeit bzw. Kraftstoff abzulassen.Since a certain system pressure p_sys is always required, the throttle bore 28 must be dimensioned so that the Provision of system pressure p_sys also at one minimum high pressure p_R_min is still secured. on the other hand also decreases with increasing high or rail pressure p_R the leakage in the low pressure area 16 too. That's why it opens the pressure relief valve 30 the more, the higher the channel 27 supplied high pressure p_R is to comply with the constant system pressure p_sys excess hydraulic fluid or to drain fuel.

    In Figur 3 ist ein Diagramm ersichtlich, welches zeigt, daß die Drosselbohrung 28 dabei deutliche Vorteile gegenüber der Realisierung der Befüllung des Niederdruckbereiches 16 mit einem herkömmlichen Befüllstift hat.In Figure 3 is a diagram can be seen, which shows that the throttle bore 28 while significant advantages over the realization of the filling of the low-pressure region 16 with a conventional filling pen has.

    Dabei ist ein Verlauf einer druckabhängigen Leckmenge Q_d bei der erfindungsgemäßen Drosselbohrung 28 im Vergleich zu einer druckabhängigen Leckmenge Q_s1 bei einem Befüllstift ohne Spaltaufweitung und einer druckabhängigen Leckmenge Q_s2 bei einem Befüllstift mit Spaltaufweitung dargestellt.Here is a course of a pressure-dependent leakage quantity Q_d in the throttle bore 28 according to the invention compared to a pressure-dependent leakage amount Q_s1 at a Befüllstift without gap widening and a pressure-dependent leakage quantity Q_s2 shown at a filling pin with gap widening.

    Damit der Systemdruck p_sys gehalten werden kann, muß schon bei einem relativ niedrigen Hochdruck p_R von z.B. 200 bar die Leckage durch die Drosselbohrung 28 größer sein als die Verluste aus dem Niederdruckbereich 16, wodurch sich ein minimaler Durchfluß Q_min von hier 5 Liter/Std. ergibt.So that the system pressure p_sys can be kept, already at a relatively low pressure p_R of e.g. 200 bar the leakage through the throttle bore 28 will be greater than that Losses from the low pressure area 16, which causes a minimum flow Q_min from here 5 liters / hr. results.

    Die Verläufe der Durchflußmengen zeigen, daß die Durchflußmenge Q_d durch die Drosselbohrung 28 mit ansteigendem Druck p_R nicht in dem Maße zunimmt wie bei einem Befüllstift. Betrachtet man die Unterschiede der Durchflußmengen formelmäßig, so kann der Volumenstrom Q_d durch die Drosselbohrung 28 bei Vereinfachung der zahlreichen neben der Druckdifferenz zu berücksichtigenden Faktoren auf einen Durchflußfaktor A folgendermaßen beschrieben werden: Q_d(p) = A (p_R - p_sys) The curves of the flow rates show that the flow Q_d through the throttle bore 28 with increasing pressure p_R does not increase to the extent as in a Befüllstift. Considering the differences in the flow rates formulaically, the volume flow Q_d through the throttle bore 28 in simplifying the numerous factors to be considered in addition to the pressure difference on a flow factor A can be described as follows: q_d ( p ) = A ( p_R - p_sys )

    Mit steigendem Hoch- bzw. Raildruck p_R nimmt der Durchfluß und damit die überschüssige Menge, die durch das Überdruckventil 30 abgelassen wird, nur in der Wurzel zu. Eine Befüllung des Niederdruckbereichs 16 mit einem Befüllstift kann hingegen mit vereinfachtem Durchflußfaktor B durch nachfolgenden Zusammenhang beschrieben werden: Q_s(p) = B(p_R - p_sys) With increasing high or rail pressure p_R, the flow and thus the excess amount discharged by the relief valve 30 increases only in the root. A filling of the low-pressure region 16 with a Befüllstift, however, can be described with simplified flow factor B by the following context: Q_s ( p ) = B ( p_R - p_sys )

    Die Gleichung ist linear bezüglich der Druckdifferenz. Der Durchfluß Q_s nimmt somit bei hohem Raildruck p_R linear zu.The equation is linear with respect to the pressure difference. Of the Flow Q_s thus decreases linearly at high rail pressure p_R to.

    Während die Befüllung mit Befüllstift und mit Drosselbohrung bei einem Hochdruck p_R von 200 bar noch dieselbe nötige Mindestmenge Zulauf zum Niederdruckbereich 16 ergeben, erzeugt der Befüllstift bereits ohne Spaltaufweitung mit steigendem Hochdruck p_R eine erheblich größere Leckmenge Q_s1 als die Drosselbohrung. Wird am Befüllstift weiterhin berücksichtigt, daß sich der Leckspalt durch den Hochdruck p_R zusätzlich aufweitet, wie es der Verlauf des Volumenstroms Q_s2 zeigt, erweist sich die Befüllung mit der Drosselbohrung 28 als noch günstiger hinsichtlich des Wirkungsgrades des gesamten Systems.While filling with filling pen and with throttle bore at a high pressure p_R of 200 bar still the same required minimum quantity inlet to the low pressure area 16 result, the Befüllstift already generated without gap widening with increasing high pressure p_R a much larger Leakage Q_s1 as the throttle bore. Is at the filling pen further takes into account that the leakage gap through the High pressure p_R additionally expands, as is the course of the Volume flow Q_s2 shows, the filling proves to be the throttle bore 28 as even more favorable in terms of Efficiency of the entire system.

    Claims (10)

    1. Valve for controlling fluids, having a piezoelectric unit (3) for actuating a valve member (2), which is axially displaceable in a bore (8) in a valve body (9) and has at one end a valve closing member (13), which co-operates with at least one seat (14, 15) provided on the valve body (9) for opening and closing the valve (1), the valve closing member (13) separating a low-pressure region (16) at a system pressure (p_sys) from a high-pressure region (17), and a filling device (26) being provided to compensate for a leakage quantity from the low-pressure region (16) by removal of hydraulic fluid from the high-pressure region (17), characterized in that the filling device (26) is formed with a channel (27) with a throttle bore (28), the diameter of which is designed in such a way that a volumetric flow passing the throttle bore (28) from the high-pressure region (17) at a defined minimum high pressure (p_R_min) compensates for the leakage quantity of the low-pressure region (16).
    2. Valve according to Claim 1, characterized in that the valve member (2) is formed in a divided manner, having at least one first piston (7) and a second piston (10), which are separated from each other by a hydraulic chamber (11), the first piston (7) bordering the piezoelectric unit (3) and being surrounded by a valve system pressure chamber (20) in a region adjoining the bore (8) in the valve body (9), and the second piston (10) bordering a valve low-pressure chamber (18) having at least one valve seat (14, 15) and a leakage draining channel (19), the channel (27) of the filling device (26) opening out on the side of the throttle bore (28) that is facing the low-pressure region (16) into a gap (24, 25) surrounding the first piston (7) or the second piston (10), and opening out on the side of the throttle bore (28) that is facing the high-pressure region (17) into the valve low-pressure chamber (18).
    3. Valve according to Claim 2, characterized in that the channel (27) of the filling device (26) opens out on the side of the throttle bore (28) that is facing the low-pressure region (16) into the gap (24) surrounding the first piston (7).
    4. Valve according to either of Claims 2 and 3, characterized in that, for opening and closing the valve (1), the valve closing member (13) co-operates with two valve seats (14, 15), arranged in the valve low-pressure chamber (18), in such a way that, in a closed position, it separates the valve low-pressure chamber (18) from a valve control chamber (12) that is under high pressure and, in an intermediate position between the valve seats (14, 15), it fluidically connects the valve low-pressure chamber (18) to the valve control chamber (12).
    5. Valve according to one of Claims 2 to 4, characterized in that a pressure relief valve (30) for setting the system pressure (p_sys) is provided between a region of the channel (27) that is facing the low-pressure region (16) and the valve low-pressure chamber (18).
    6. Valve according to one of Claims 2 to 5, characterized in that the hydraulic chamber (11) at system pressure (p_sys) is formed as a tolerance compensating element to compensate for elongational tolerances of the piezoelectric unit (3) and/or further valve components (9) and as a hydraulic transmission.
    7. Valve according to one of Claims 2 to 6, characterized in that the valve system pressure chamber (20) is delimited by a sealing element (25).
    8. Valve according to Claim 7, characterized in that the sealing element delimiting the valve system pressure chamber (20) is formed as a bellows-like diaphragm (25), which is connected to the valve member (2) and to the valve body (9) in such a way that the piezoelectric unit (3) is protected against contact with the fluid to be controlled.
    9. Valve according to one of Claims 1 to 8, characterized in that the throttle bore (28) has a diameter of at least approximately 40 micrometres to 60 micrometres, preferably 50 micrometres.
    10. Valve according to one of Claims 1 to 9, characterized by its use as a component part of a fuel injection valve for internal combustion engines, in particular a common-rail injector (1).
    EP00974318A 1999-09-30 2000-09-09 Valve for controlling fluids Expired - Lifetime EP1135593B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE19946833 1999-09-30
    DE19946833A DE19946833C2 (en) 1999-09-30 1999-09-30 Valve for controlling liquids
    PCT/DE2000/003138 WO2001023743A1 (en) 1999-09-30 2000-09-09 Valve for controlling fluids

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    EP1135593A1 EP1135593A1 (en) 2001-09-26
    EP1135593B1 true EP1135593B1 (en) 2005-01-12

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    EP (1) EP1135593B1 (en)
    JP (1) JP2003510506A (en)
    KR (1) KR20010101059A (en)
    AT (1) ATE287039T1 (en)
    CZ (1) CZ20011879A3 (en)
    DE (2) DE19946833C2 (en)
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    Also Published As

    Publication number Publication date
    ATE287039T1 (en) 2005-01-15
    DE19946833A1 (en) 2001-05-03
    DE50009213D1 (en) 2005-02-17
    US6530555B1 (en) 2003-03-11
    KR20010101059A (en) 2001-11-14
    CZ20011879A3 (en) 2002-04-17
    JP2003510506A (en) 2003-03-18
    EP1135593A1 (en) 2001-09-26
    DE19946833C2 (en) 2002-02-21
    WO2001023743A1 (en) 2001-04-05

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