EP1135594A1 - Valve for controlling liquids - Google Patents

Valve for controlling liquids

Info

Publication number
EP1135594A1
EP1135594A1 EP00974319A EP00974319A EP1135594A1 EP 1135594 A1 EP1135594 A1 EP 1135594A1 EP 00974319 A EP00974319 A EP 00974319A EP 00974319 A EP00974319 A EP 00974319A EP 1135594 A1 EP1135594 A1 EP 1135594A1
Authority
EP
European Patent Office
Prior art keywords
valve
piezoelectric actuator
hydraulic
chamber
hydraulic chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP00974319A
Other languages
German (de)
French (fr)
Other versions
EP1135594B1 (en
Inventor
Patrick Mattes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1135594A1 publication Critical patent/EP1135594A1/en
Application granted granted Critical
Publication of EP1135594B1 publication Critical patent/EP1135594B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S137/00—Fluid handling
    • Y10S137/906—Valves biased by fluid "springs"

Definitions

  • the invention is based on a valve for controlling liquids in accordance with the preamble of patent claim 1.
  • a valve which can be actuated via a piezoelectric actuator, is already known from EP 0 477 400 A1.
  • This known valve has an arrangement for an adaptive, mechanical tolerance compensation acting in the stroke direction for a displacement transformer of the piezoelectric actuator, in which the deflection of the piezoelectric actuator is transmitted via a hydraulic chamber.
  • the hydraulic chamber which works as a so-called hydraulic ratio, closes between two pistons delimiting it, one of which is designed with a smaller diameter and is connected to a valve member to be actuated and the other piston is designed with a larger diameter and with the piezoelectric actuator is connected, a common compensation volume.
  • the hydraulic chamber is clamped between the two pistons in such a way that the actuating piston of the valve member, which is held in its rest position by means of one or more springs relative to a predetermined position, one stroke increased by the ratio of the piston diameter when the larger piston is moved by the piezoelectric actuator by a certain distance.
  • the valve member, the pistons and the piezoelectric actuator lie one behind the other on a common axis.
  • the compensation volume of the hydraulic chamber can be used to compensate for tolerances due to temperature gradients in the component or different coefficients of thermal expansion of the materials used, as well as any setting effects, without a change in the position of the valve member to be controlled.
  • a piezoelectric actuator is constructed from several thin layers in order to achieve the largest possible stroke. So that these layers do not come apart from one another when the piezoelectric actuator is energized, the piezoelectric actuator must be pretensioned, the force to be applied in this case being approximately 1000 N.
  • the invention has for its object to provide a valve for controlling liquids, in which the bias of a piezoelectric actuator and tolerance compensation is implemented with a small space requirement with a simple structure with as few components as possible.
  • the valve according to the invention for the control of liquids with the characterizing features of claim 1 has the advantage that with the hydraulic chamber designed as a hydraulic spring, a biasing element for the piezoelectric actuator and a compensating element for temperature-related elongation tolerances in particular is realized at the same time.
  • the prestressing is represented hydraulically and with a small space requirement, a desired slim design of the entire valve being possible by dispensing with springs or other mechanical prestressing elements.
  • the manufacturing costs and the assembly effort can be significantly reduced.
  • Another important advantage of the invention is that the overall rigidity of the system can be increased by dimensioning the hydraulic chamber, the hydraulic spring and the piston immersed in it. Since the rigidity of the hydraulic spring depends on the cross-sectional area of the piston, the rigidity of the hydraulic spring and thus the preload force on the piezoelectric actuator can be increased at the same pressure if the cross-sectional area of the piston immersed in the hydraulic chamber is increased accordingly.
  • Figure 1 is a schematic, partial representation of a first embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section
  • Figure 2 is a schematic, partial representation of a second embodiment in a fuel injector in longitudinal section.
  • the first exemplary embodiment shown in FIG. 1 shows the use of the valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles.
  • fuel injection valve 1 is designed as a common rail injector.
  • a valve member 2 is controlled via a piezoelectric actuator 3, which is arranged in a piezo chamber 4 on the side of the valve member 2 facing away from the combustion chamber.
  • the piston-shaped valve member 2 is arranged in an axially displaceable manner in a bore 5 of a valve body 6 designed as a longitudinal bore and has a ball-like valve head 7 forming a valve closing member at its combustion chamber end.
  • the valve head 7 interacts with a seat 8 formed on the valve body 6, a connection to a spring chamber 9 having a spring force exerting a restoring force on the outwardly opening valve head 7 being produced in the lifted state of the valve head 7.
  • an outlet throttle 11 connects to the spring chamber 9, which leads to a valve control chamber 12, into which an injection line 13, which is only symbolically indicated in FIG. 1, flows, which in turn leads away from a high-pressure storage chamber (common rail) 14 common to all fuel injection valves ,
  • the high-pressure storage space 14 filled in a known manner by a high pressure fuel pump with high pressure fuel from a storage tank.
  • the piezoelectric actuator 3 is constructed from several layers and has an actuator head 15 on its side facing the combustion chamber and an actuator foot 16 on its side facing away from the combustion chamber.
  • An actuating piston 17 is attached to the actuator head 15, which extends from the piezo chamber 4 through a support 18 for the actuator head 15 on the combustion chamber-side wall of the piezo chamber 4 into the longitudinal bore 5, in which the valve member 2 is mounted.
  • the piezo chamber 4 is sealed in the area of the actuating piston 17 with a sealing device 19 in relation to the longitudinal bore 5.
  • the actuator foot 16 is fixedly connected to a further piston 20, which is immersed in a hydraulic chamber 21, which is arranged on the side of the piezoelectric actuator 3 facing away from the valve member 2 in the installed position of the fuel injection valve 1 above the piezo chamber 4.
  • the piezo chamber 4 is sealed from this by a further sealing device 22 in the region of the piston 20 leading into the hydraulic chamber 21.
  • the essentially closed hydraulic chamber 21 is designed with the pressure medium contained therein, which is supplied from a low-pressure source with a pressure that is relaxed compared to the pressure level of the high-pressure storage chamber 14, as a hydraulic spring which communicates via a hydraulic line 23 formed in the valve body 6 with which the Longitudinal bore 5 containing valve member 2 is connected.
  • the hydraulic spring performs a double function, because on the one hand it serves as a biasing element of the piezoelectric actuator 3 and on the other hand it is a tolerance compensation element.
  • the fuel injection valve 1 according to FIG. 1 operates in the manner described below.
  • the valve head 7 of the valve member 2 is held in contact with the seat 8 assigned to it, so that no fuel can get into the region of the longitudinal bore 5 from the valve control chamber 12 connected to the high-pressure storage chamber 14. Due to a slightly increased system pressure in the hydraulic chamber 21 of approximately 65 bar in the present embodiment, the piezoelectric actuator 3 is clamped between the hydraulic spring and the support 18 on the combustion chamber side.
  • the pretensioning force of the piezoelectric actuator 3 can be adjusted via the diameter of the piston 20, with the largest possible piston diameter being advantageous.
  • a piston diameter of 14 mm is sufficient to achieve a pretensioning force of 1000 N at a system pressure of 65 bar.
  • those skilled in the art can choose different values that are adapted to the individual case.
  • the piezoelectric actuator 3 When an injection is to take place through the fuel injection valve 1, the piezoelectric actuator 3 is energized, as a result of which its axial expansion increases abruptly. With such a rapid actuation of the piezoelectric actuator 3, it is supported on the support 18 and with the piston 20 projecting into the hydraulic chamber 21 on the hydraulic spring, as a result of which hydraulic medium is displaced from the hydraulic chamber 21 via the hydraulic line 23 into the longitudinal bore 5 of the valve member 2 is, whereby the valve head 7 of the valve member 2 lifts from its seat 8 in an open position.
  • the increased rigidity due to a relatively large diameter of the piston 20 has a positive effect.
  • FIG. 2 a second exemplary embodiment of fuel injector 1 is shown, in which, for the sake of clarity, functionally identical components are identified by the reference numerals used in FIG. 1.
  • the fuel injection valve 1 shown here differs in that the volume of the hydraulic chamber 21 cooperating with the piezoelectric actuator 3 can be changed externally.
  • a schematically illustrated adjusting screw is provided in a bore 25 as an adjusting device 24 in the present exemplary embodiment, which is positioned in such a way that the adjusting screw 24 can be screwed into the hydraulic chamber 21 in a protruding manner, as a result of which the compensation volume, depending on the change in the position of the adjusting screw 24, is reduced or is enlarged.
  • quantity tolerances can be compensated to a limited extent, since the Stiffness of the compensation volume is inversely proportional to the volume.
  • the opening behavior of the fuel injection valve 1 and thus the injection quantity can be influenced.
  • the adjusting screw 24 thus enables the injection quantity to be readjusted externally by correcting the compensation volume in the hydraulic chamber 21.
  • the sealing device 22 for separating the hydraulic chamber 21 from the piezo chamber 4 is arranged in a region of the piston 20 protruding into the hydraulic chamber 21, which lies within the piezo chamber 4, so that an annular chamber 26 thereof is separated with the diameter of the piezo chamber 4.
  • the sealing device 22 also has the function here of protecting the piezoelectric actuator 3 from any water content and harmful particles such as e.g. Protect Span.
  • the hydraulic line 23 opens into the annular chamber 26, which is connected to the hydraulic chamber 21 via an annular gap 27.
  • a filling surface 28 is formed on the piston 20 in the area of the annular gap 27.
  • the hydraulic medium for filling the hydraulic chamber 21 is the fuel, which is also injected into a combustion chamber of an internal combustion engine.

Abstract

A valve for controlling fluids is embodied with a piezoelectric actuator (3) for actuating a valve member (2) that on one end has a valve head (7), forming a valve closing member, that cooperates with a seat (8) provided on the valve body (6) for opening and closing the valve (1). On a side of the piezoelectric actuator (3) remote from the valve member (2), a hydraulic chamber (21) is provided, which communicates, via at least one hydraulic line (23), with a bore (5) of the valve member (2) that is sealed from the piezoelectric actuator (3), and into which bore a piston (20) connected to the piezoelectric actuator (3) can plunge; the hydraulic chamber (21) is embodied as a hydraulic spring, which with its spring force on the piston (20) connected to the piezoelectric actuator (3) act as the prestressing element and the tolerance compensating element. The valve is intended in particular as a component of a fuel injection valve.

Description

Ventil zum Steuern von FlüssigkeitenValve for controlling liquids
Stand der TechnikState of the art
Die Erfindung geht von einem Ventil zum Steuern von Flussig- keiten gemäß der Gattung des Patentanspruchs 1 aus. Aus der EP 0 477 400 AI ist ein derartiges Ventil, welches über einen piezoelektrischen Aktor betatigbar ist, bereits bekannt. Dieses bekannte Ventil weist eine Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranz- ausgleich für einen Wegtransformator des piezoelektrischen Aktors auf, bei der die Auslenkung des piezoelektrischen Aktors über eine Hydraulikkammer übertragen wird.The invention is based on a valve for controlling liquids in accordance with the preamble of patent claim 1. Such a valve, which can be actuated via a piezoelectric actuator, is already known from EP 0 477 400 A1. This known valve has an arrangement for an adaptive, mechanical tolerance compensation acting in the stroke direction for a displacement transformer of the piezoelectric actuator, in which the deflection of the piezoelectric actuator is transmitted via a hydraulic chamber.
Die Hydraulikkammer, welche als eine sogenannte hydraulische Übersetzung arbeitet, 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 Betatigungskolben 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.The hydraulic chamber, which works as a so-called hydraulic ratio, closes between two pistons delimiting it, one of which is designed with a smaller diameter and is connected to a valve member to be actuated and the other piston is designed with a larger diameter and with the piezoelectric actuator is connected, a common compensation volume. The hydraulic chamber is clamped between the two pistons in such a way that the actuating piston of the valve member, which is held in its rest position by means of one or more springs relative to a predetermined position, one stroke increased by the ratio of the piston diameter when the larger piston is moved by the piezoelectric actuator by a certain distance. The valve member, the pistons and the piezoelectric actuator lie one behind the other on a common axis.
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 compensation volume of the hydraulic chamber can be used to compensate for tolerances due to temperature gradients in the component or different coefficients of thermal expansion of the materials used, as well as any setting effects, without a change in the position of the valve member to be controlled.
Ein Ausgleich von Langenanderungen des piezoelektrischen Aktors, des Ventilgliedes oder des Ventilgehauses durch die zwischen zwei Kolben angeordnete Hydraulikkammer erfordert jedoch eine aufwendige Konstruktion und ist hinsichtlich der auftretenden Leckageverluste und der Wiederbefullung der Hydraulikkammer problematisch.Compensating changes in length of the piezoelectric actuator, the valve member or the valve housing by the hydraulic chamber arranged between two pistons, however, requires a complex construction and is problematic with regard to the leakage losses that occur and the refilling of the hydraulic chamber.
Des weiteren ist es hinlänglich bekannt, daß ein piezoelektrischer Aktor aus mehreren dünnen Schichten aufgebaut ist, um einen möglichst großen Hub zu erzielen. Damit sich diese Schichten bei einer Bestromung des piezoelektrischen Aktors nicht voneinander losen, muß der piezoelektrische Aktor vorgespannt werden, wobei die dabei aufzubringende Kraft annähernd 1000 N betragen kann.Furthermore, it is well known that a piezoelectric actuator is constructed from several thin layers in order to achieve the largest possible stroke. So that these layers do not come apart from one another when the piezoelectric actuator is energized, the piezoelectric actuator must be pretensioned, the force to be applied in this case being approximately 1000 N.
In der Praxis werden zur Vorspannung des piezoelektrischen Aktors entweder Tellerfedern oder Bandfedern eingesetzt. Nachteilig ist dabei, daß die zur Vorspannung benotigten Federn einen aufwendigen Aufbau bedingen und einen großen Bauraum benotigen, wobei letzteres zu einem entsprechend großen Durchmesser des gesamten Ventils fuhrt, wodurch die Einbau oglichkeiten des Ventils begrenzt werden. Des weiteren hat die Verwendung von Federn als Vorspannelemente den Nachteil, daß diese über die Dauer ihrer Benutzung Reibrost verursachen.In practice, either disc springs or band springs are used to preload the piezoelectric actuator. The disadvantage here is that the springs required for pretensioning require a complex structure and require a large installation space, the latter leading to a correspondingly large diameter of the entire valve, as a result of which the Installation possibilities of the valve are limited. Furthermore, the use of springs as prestressing elements has the disadvantage that they cause rubbing rust over the duration of their use.
Der Erfindung liegt die Aufgabe zugrunde, ein Ventil zur Steuerung von Flüssigkeiten zu schaffen, bei dem die Vorspannung eines piezoelektrischen Aktors und ein Toleranzausgleich mit geringem Bauraumbedarf bei einem einfachen Aufbau mit möglichst wenigen Bauteilen realisiert ist.The invention has for its object to provide a valve for controlling liquids, in which the bias of a piezoelectric actuator and tolerance compensation is implemented with a small space requirement with a simple structure with as few components as possible.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemaße Ventil zur Steuerung von Flüssigkeiten mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat den Vorteil, daß mit der als hydraulische Feder ausgebildeten Hydraulikkammer gleichzeitig ein Vorspannelement für den piezoelektrischen Aktor und ein Ausgleichselment für insbesondere temperaturbedingte Langungstoleranzen realisiert ist.The valve according to the invention for the control of liquids with the characterizing features of claim 1 has the advantage that with the hydraulic chamber designed as a hydraulic spring, a biasing element for the piezoelectric actuator and a compensating element for temperature-related elongation tolerances in particular is realized at the same time.
Bei dem erfindungsgemaßen hydraulischen Vorspannelement mit integriertem Toleranzausgleich für den piezoelektrischen Aktor wird die Vorspannung hydraulisch und mit geringem Raumbedarf dargestellt, wobei durch den Verzicht auf Federn oder sonstige mechanische Vorspannelemente eine gewünschte schlanke Bauform des gesamten Ventils möglich ist.In the case of the hydraulic prestressing element according to the invention with integrated tolerance compensation for the piezoelectric actuator, the prestressing is represented hydraulically and with a small space requirement, a desired slim design of the entire valve being possible by dispensing with springs or other mechanical prestressing elements.
Durch die Verringerung der erforderlichen Bauteile zur Dar- Stellung eines Vorspannelementes und eines Toleranzausgleichselementes, welches erfindungsgemaß in das Vorspannelement integriert ist, können die Herstellungskosten und der Montageaufwand deutlich reduziert werden. Ein bedeutender Vorteil der Erfindung besteht des weiteren darin, daß durch Dimensionierung der Hydraulikkammer, der hydraulischen Feder und des in sie eintauchenden Kolbens die Gesamtsteifigkeit des Systems erhöht werden kann. Da die Steifigkeit der hydraulischen Feder von der Querschnittsflache des Kolbens abhangig ist, kann bei gleichem Druck die Steifigkeit der hydraulischen Feder und damit die Vorspannkraft auf den piezoelektrischen Aktor erhöht werden, wenn die Querschnittsflache des in die Hydraulikkammer eintau- chenden Kolbens entsprechend vergrößert wird. Im statischen Fall kann auch bei hoher Federrate eine nachteilige Lange- nanderung der Gesamteinrichtung vermieden werden, wenn der piezoelektrische Aktor, das Ventilglied oder der Ventilkor- per seine Lange z.B. bei Erwärmung ändert. Zum anderen ist bei einer dynamischen Betätigung die Steifigkeit der hydraulischen Feder, an der sich der Kolben abstutzt, um so großer, je großer der Durchmesser des Kolbens gewählt wird. Dabei ergibt sich zudem der Vorteil, daß die Hubverluste des Kolbens mit zunehmendem Durchmesser abnehmen.By reducing the number of components required to display a pretensioning element and a tolerance compensation element, which is integrated into the pretensioning element according to the invention, the manufacturing costs and the assembly effort can be significantly reduced. Another important advantage of the invention is that the overall rigidity of the system can be increased by dimensioning the hydraulic chamber, the hydraulic spring and the piston immersed in it. Since the rigidity of the hydraulic spring depends on the cross-sectional area of the piston, the rigidity of the hydraulic spring and thus the preload force on the piezoelectric actuator can be increased at the same pressure if the cross-sectional area of the piston immersed in the hydraulic chamber is increased accordingly. In the static case, a disadvantageous change in length of the entire device can be avoided even when the spring rate is high, if the piezoelectric actuator, the valve member or the valve body changes its length, for example when heated. On the other hand, in the case of dynamic actuation, the rigidity of the hydraulic spring against which the piston is supported is greater, the larger the diameter of the piston is chosen. This also has the advantage that the stroke losses of the piston decrease with increasing diameter.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the subject matter of the invention can be gathered from the description, the drawing and the patent claims.
Zeichnungdrawing
Zwei Ausfuhrungsbeispiele des erfindungsgemaßen Ventils zur Steuerung von Flüssigkeiten sind in der Zeichnung dargestellt und werden in der folgenden Beschreibung naher erlau- tert. Es zeigenTwo exemplary embodiments of the valve according to the invention for controlling liquids are shown in the drawing and will be explained in more detail in the following description. Show it
Figur 1 eine schematische, ausschnittsweise Darstellung eines erstes Ausfuhrungsbeispiels der Erfindung bei einem Kraftstoffeinspritzventil für Brennkraftmaschinen im Längsschnitt, und Figur 2 eine schematische, ausschnittsweise Darstellung eines zweiten Ausfuhrungsbeispiels bei einem Kraftstoffeinspritzventil im Längsschnitt.Figure 1 is a schematic, partial representation of a first embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section, and Figure 2 is a schematic, partial representation of a second embodiment in a fuel injector in longitudinal section.
Beschreibung der AusfuhrungsbeispieleDescription of the exemplary embodiments
Das in der Figur 1 dargestellte erste Ausfuhrungsbeispiel zeigt eine Verwendung des erfindungsgemaßen Ventils bei einem Kraftstoffeinspritzventil 1 für Brennkraftmaschinen von Kraftfahrzeugen. Das Kraftstoffeinspritzventil 1 ist vorliegend als ein Common-Rail-Injektor ausgebildet.The first exemplary embodiment shown in FIG. 1 shows the use of the valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles. In the present case, fuel injection valve 1 is designed as a common rail injector.
Zur Einstellung eines Einspritzbeginns, einer Einspritzdauer und einer Einspritzmenge über Kräfteverhältnisse in dem Kraftstoffeinspritzventil 1 wird ein Ventilglied 2 über einen piezoelektrischen Aktor 3 angesteuert, welcher auf der brennraumabgewandten Seite des Ventilgliedes 2 in einer Piezokammer 4 angeordnet ist.In order to set an injection start, an injection duration and an injection quantity via force relationships in the fuel injection valve 1, a valve member 2 is controlled via a piezoelectric actuator 3, which is arranged in a piezo chamber 4 on the side of the valve member 2 facing away from the combustion chamber.
Das kolbenförmige Ventilglied 2 ist axial verschiebbar in einer als Langsbohrung ausgeführten Bohrung 5 eines Ventil- korpers 6 angeordnet und weist an seinem brennraumseitigen Ende einen kugelartigen, ein Ventilschließglied bildenden Ventilkopf 7 auf. Der Ventilkopf 7 wirkt mit einem an dem Ventilkorper 6 ausgebildeten Sitz 8 zusammen, wobei in abgehobenem Zustand des Ventilkopfes 7 eine Verbindung zu einem Federraum 9 mit einer eine Ruckstellkraft auf den nach außen öffnenden Ventilkopf 7 ausübenden Feder 10 hergestellt wird. An den Federraum 9 schließt sich brennraumseitig eine Ab- laufdrossel 11 an, die zu einem Ventilsteuerraum 12 fuhrt, in welchen eine in Figur 1 nur symbolisch angedeutete Einspritzleitung 13 mundet, die ihrerseits von einem für alle Kraftstoffeinspritzventile gemeinsamen Hochdruckspeicherraum (Common-Rail) 14 abfuhrt. Der Hochdruckspeicherraum 14 wird dabei in bekannter Weise von einer Kraftstoffhochdruckforderpumpe mit Kraftstoff hohen Druckes aus einem Vorratstank befullt.The piston-shaped valve member 2 is arranged in an axially displaceable manner in a bore 5 of a valve body 6 designed as a longitudinal bore and has a ball-like valve head 7 forming a valve closing member at its combustion chamber end. The valve head 7 interacts with a seat 8 formed on the valve body 6, a connection to a spring chamber 9 having a spring force exerting a restoring force on the outwardly opening valve head 7 being produced in the lifted state of the valve head 7. On the combustion chamber side, an outlet throttle 11 connects to the spring chamber 9, which leads to a valve control chamber 12, into which an injection line 13, which is only symbolically indicated in FIG. 1, flows, which in turn leads away from a high-pressure storage chamber (common rail) 14 common to all fuel injection valves , The high-pressure storage space 14 filled in a known manner by a high pressure fuel pump with high pressure fuel from a storage tank.
Der piezoelektrische Aktor 3 ist aus mehreren Schichten aufgebaut und weist auf seiner brennraumzugewandten Seite einen Aktorkopf 15 sowie auf seiner brennraumabgewandten Seite einen Aktorfuß 16 auf. An dem Aktorkopf 15 ist ein Stellkolben 17 befestigt, welcher von der Piezokammer 4 aus durch ein Auflager 18 für den Aktorkopf 15 an der brennraum- seitigen Wand der Piezokammer 4 in die Langsbohrung 5 reicht, in welcher das Ventilglied 2 gelagert ist. Dabei ist die Piezokammer 4 im Bereich des Stellkolbens 17 gegenüber der Langsbohrung 5 mit einer Dichteinrichtung 19 abgedich- tet. Der Aktorfuß 16 ist fest mit einem weiteren Kolben 20 verbunden, der in eine Hydraulikkammer 21 eintaucht, welche auf der dem Ventilglied 2 abgewandten Seite des piezoelektrischen Aktors 3 in Einbaulage des Kraftstoffeinspritzventils 1 oberhalb der Piezokammer 4 angeordnet ist. Dabei ist die Piezokammer 4 über eine weitere Dichteinrichtung 22 im Bereich des in die Hydraulikkammer 21 fuhrenden Kolbens 20 gegenüber dieser abgedichtet.The piezoelectric actuator 3 is constructed from several layers and has an actuator head 15 on its side facing the combustion chamber and an actuator foot 16 on its side facing away from the combustion chamber. An actuating piston 17 is attached to the actuator head 15, which extends from the piezo chamber 4 through a support 18 for the actuator head 15 on the combustion chamber-side wall of the piezo chamber 4 into the longitudinal bore 5, in which the valve member 2 is mounted. The piezo chamber 4 is sealed in the area of the actuating piston 17 with a sealing device 19 in relation to the longitudinal bore 5. The actuator foot 16 is fixedly connected to a further piston 20, which is immersed in a hydraulic chamber 21, which is arranged on the side of the piezoelectric actuator 3 facing away from the valve member 2 in the installed position of the fuel injection valve 1 above the piezo chamber 4. The piezo chamber 4 is sealed from this by a further sealing device 22 in the region of the piston 20 leading into the hydraulic chamber 21.
Die im wesentlichen abgeschlossene Hydraulikkammer 21 ist mit dem in ihr enthaltenen Druckmedium, welches aus einer Niederdruckquelle mit einem gegenüber dem Druckniveau des Hochdruckspeicherraums 14 entspannten Druck zugeführt wird, als eine hydraulische Feder konzipiert, welche über eine in dem Ventilkorper 6 ausgebildete Hydraulikleitung 23 mit der das Ventilglied 2 enthaltenden Langsbohrung 5 verbunden ist. Dabei übt die hydraulische Feder eine Doppelfunktion aus, denn zum einen dient sie als Vorspannelement des piezoelektrischen Aktors 3 und zum anderen ist sie ein Toleranzausgleichselement . Das Kraftstoffeinspritzventil 1 nach Figur 1 arbeitet dabei in nachfolgend beschriebener Weise.The essentially closed hydraulic chamber 21 is designed with the pressure medium contained therein, which is supplied from a low-pressure source with a pressure that is relaxed compared to the pressure level of the high-pressure storage chamber 14, as a hydraulic spring which communicates via a hydraulic line 23 formed in the valve body 6 with which the Longitudinal bore 5 containing valve member 2 is connected. The hydraulic spring performs a double function, because on the one hand it serves as a biasing element of the piezoelectric actuator 3 and on the other hand it is a tolerance compensation element. The fuel injection valve 1 according to FIG. 1 operates in the manner described below.
In geschlossenem Zustand des Kraftstoffeinspritzventils 1, d.h. bei unbestromten piezoelektrischen Aktor 3 wird der Ventilkopf 7 des Ventilglieds 2 in Anlage an dem ihm zugeordneten Sitz 8 gehalten, so daß kein Kraftstoff aus dem mit dem Hochdruckspeicherraum 14 verbundenen Ventilsteuerraum 12 in den Bereich der Langsbohrung 5 gelangen kann. Aufgrund eines leicht erhöhten Systemdrucks in der Hydraulikkammer 21 von annähernd 65 bar in der vorliegenden Ausfuhrung wird der piezoelektrische Aktor 3 zwischen der Hydraulikfeder und dem brennraumseitigen Auflager 18 eingespannt.When the fuel injector 1 is closed, i.e. when the piezoelectric actuator 3 is not energized, the valve head 7 of the valve member 2 is held in contact with the seat 8 assigned to it, so that no fuel can get into the region of the longitudinal bore 5 from the valve control chamber 12 connected to the high-pressure storage chamber 14. Due to a slightly increased system pressure in the hydraulic chamber 21 of approximately 65 bar in the present embodiment, the piezoelectric actuator 3 is clamped between the hydraulic spring and the support 18 on the combustion chamber side.
Da sich die Federrate der hydraulischen Feder mit zunehmendem Durchmesser des in die Hydraulikkammer 21 ragenden Kolbens 20 proportional erhöht, kann die Vorspannkraft des piezoelektrischen Aktors 3 über den Durchmesser des Kolbens 20 eingestellt werden, wobei ein möglichst großer Kolbendurchmesser vorteilhaft ist. Im vorliegenden Ausfuhrungsbeispiel ist ein Kolbendurchmesser von 14 mm ausreichend, um eine Vorspannkraft von 1000 N bei dem Systemdruck von 65 bar zu erzielen. Selbstverständlich können vom Fachmann hiervon abweichende, dem Einzelfall angepaßte Werte gewählt werden.Since the spring rate of the hydraulic spring increases proportionally with increasing diameter of the piston 20 projecting into the hydraulic chamber 21, the pretensioning force of the piezoelectric actuator 3 can be adjusted via the diameter of the piston 20, with the largest possible piston diameter being advantageous. In the present exemplary embodiment, a piston diameter of 14 mm is sufficient to achieve a pretensioning force of 1000 N at a system pressure of 65 bar. Of course, those skilled in the art can choose different values that are adapted to the individual case.
Im Falle einer langsamen Betätigung, wie sie bei einer temperaturbedingten Langenanderung des piezoelektrischen Aktors 3 oder weiterer Ventilbauteile wie z.B. des Ventilglieds 2 oder des Ventilgehauses bzw. Ventilkorpers 6 auftritt, dringt der Kolben 20 mit Temperaturerhöhung in das Ausgleichsvolumen der Hydraulikkammer 21 ein oder zieht sich bei Temperaturabsenkung daraus zurück, ohne daß die Auswir- kungen auf die Schließ- und Offnungsstellung des Ventilgliedes 2 und des Kraftstoffventils 1 insgesamt hat.In the case of slow actuation, as occurs when the piezoelectric actuator 3 or other valve components, such as the valve member 2 or the valve housing or valve body 6, change in length due to temperature, the piston 20 penetrates into the compensating volume of the hydraulic chamber 21 as the temperature rises or contracts Temperature reduction from this without the effects kungen on the closed and open position of the valve member 2 and the fuel valve 1 as a whole.
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 stutzt sich dieser auf dem Auflager 18 und mit dem in die Hydraulikkammer 21 ragenden Kolben 20 auf der hydraulischen Feder ab, infolgedessen Hydraulikmedium aus der Hydraulikkammer 21 über die Hydraulikleitung 23 in die Langsbohrung 5 des Ventilgliedes 2 verschoben wird, wodurch sich der Ventilkopf 7 des Ventilgliedes 2 von seinem Sitz 8 in eine geöffnete Stellung abhebt. Auch hier wirkt sich die erhöhte Steifigkeit durch einen relativ groß dimensionierten Durchmesser des Kolbens 20 positiv aus.When an injection is to take place through the fuel injection valve 1, the piezoelectric actuator 3 is energized, as a result of which its axial expansion increases abruptly. With such a rapid actuation of the piezoelectric actuator 3, it is supported on the support 18 and with the piston 20 projecting into the hydraulic chamber 21 on the hydraulic spring, as a result of which hydraulic medium is displaced from the hydraulic chamber 21 via the hydraulic line 23 into the longitudinal bore 5 of the valve member 2 is, whereby the valve head 7 of the valve member 2 lifts from its seat 8 in an open position. Here too, the increased rigidity due to a relatively large diameter of the piston 20 has a positive effect.
Bezug nehmend auf Figur 2 ist ein zweites Ausfuhrungsbeispiel des Kraftstoffeinspritzventils 1 dargestellt, bei der aus Gründen der Übersichtlichkeit funktionsgleiche Bauteile mit den in Figur 1 verwendeten Bezugszeichen bezeichnet sind. Gegenüber der Ausfuhrung nach Figur 1 unterscheidet sich das hier gezeigte Kraftstoffeinspritzventil 1 darin, daß das Volumen der mit dem piezoelektrischen Aktor 3 zusam- menwirkenden Hydraulikkammer 21 von extern veränderbar ist.Referring to FIG. 2, a second exemplary embodiment of fuel injector 1 is shown, in which, for the sake of clarity, functionally identical components are identified by the reference numerals used in FIG. 1. Compared to the embodiment according to FIG. 1, the fuel injection valve 1 shown here differs in that the volume of the hydraulic chamber 21 cooperating with the piezoelectric actuator 3 can be changed externally.
Hierzu ist als Justiereinrichtung 24 im vorliegenden Ausfuhrungsbeispiel eine schematisch dargestellte Stellschraube in einer Bohrung 25 vorgesehen, welche derart positioniert ist, daß die Stellschraube 24 bei Bedarf in die Hydraulikkammer 21 ragend einschraubbar ist, wodurch das Ausgleichsvolumen je nach Veränderung der Stellung der Stellschraube 24 verkleinert oder vergrößert wird. Mit dieser Maßnahme können in begrenztem Maße Mengentoleranzen ausgeglichen werden, da die Steifigkeit des Ausgleichsvolumens umgekehrt proportional zum Volumen ist. Je nach Steifigkeit der hydraulischen Feder in der Hydraulikkammer 21 kann das Offnungsverhalten des Kraftstoffeinspritzventils 1 und damit die Einspritzmenge beeinflußt werden. Somit ermöglicht die Stellschraube 24 eine externe Nachjustage der Einspritzmenge durch Korrektur des Ausgleichsvolumens in der Hydraulikkammer 21.For this purpose, a schematically illustrated adjusting screw is provided in a bore 25 as an adjusting device 24 in the present exemplary embodiment, which is positioned in such a way that the adjusting screw 24 can be screwed into the hydraulic chamber 21 in a protruding manner, as a result of which the compensation volume, depending on the change in the position of the adjusting screw 24, is reduced or is enlarged. With this measure, quantity tolerances can be compensated to a limited extent, since the Stiffness of the compensation volume is inversely proportional to the volume. Depending on the rigidity of the hydraulic spring in the hydraulic chamber 21, the opening behavior of the fuel injection valve 1 and thus the injection quantity can be influenced. The adjusting screw 24 thus enables the injection quantity to be readjusted externally by correcting the compensation volume in the hydraulic chamber 21.
Des weiteren ist bei der Ausfuhrung nach Figur 2 die Dicht- einrichtung 22 zur Abtrennung der Hydraulikkammer 21 von der Piezokammer 4 in einem Bereich des in die Hydraulikkammer 21 ragenden Kolbens 20 angeordnet, welcher innerhalb der Piezokammer 4 liegt, so daß von dieser eine Ringkammer 26 mit dem Durchmesser der Piezokammer 4 abgetrennt ist. Wie bei der Ausfuhrung nach Figur 1 hat die Dichteinrichtung 22 auch hier die Funktion, den piezoelektrischen Aktor 3 vor einem eventuell in dem Hydraulikmedium enthaltenen Wasseranteil und schädlichen Partikeln wie z.B. Spanen zu schützen.Furthermore, in the embodiment according to FIG. 2, the sealing device 22 for separating the hydraulic chamber 21 from the piezo chamber 4 is arranged in a region of the piston 20 protruding into the hydraulic chamber 21, which lies within the piezo chamber 4, so that an annular chamber 26 thereof is separated with the diameter of the piezo chamber 4. As in the embodiment according to FIG. 1, the sealing device 22 also has the function here of protecting the piezoelectric actuator 3 from any water content and harmful particles such as e.g. Protect Span.
Die Hydraulikleitung 23 mundet hier in die Ringkammer 26, welche über einen Ringspalt 27 mit der Hydraulikkammer 21 verbunden ist. Zur Verbesserung des Befullverhaltens ist im Bereich des Ringspalts 27 an dem Kolben 20 eine Befullflache 28 ausgeformt.The hydraulic line 23 opens into the annular chamber 26, which is connected to the hydraulic chamber 21 via an annular gap 27. To improve the filling behavior, a filling surface 28 is formed on the piston 20 in the area of the annular gap 27.
In beiden beschriebenen Ausfuhrungen ist das Hydraulikmedium zur Befullung der Hydraulikkammer 21 der Kraftstoff, welcher auch in einen Brennraum einer Brennkraftmaschine eingespritzt wird.In both embodiments described, the hydraulic medium for filling the hydraulic chamber 21 is the fuel, which is also injected into a combustion chamber of an internal combustion engine.
Bei einer geeigneten Trennung zwischen der Kraftstoffzufuhrung und der Abfuhrung des an dem Sitz 8 des Ventilkopfes 7 austretenden Hydraulikmediums sowie einer Nachfuhrung von Leckageverlusten ist es auch möglich, separates 01 wie z.B. Motorol als Hydraulikmedium einzusetzen. With a suitable separation between the fuel supply and the discharge of the hydraulic medium escaping from the seat 8 of the valve head 7 and a tracking of Leakage losses, it is also possible to use separate 01 such as Motorol as the hydraulic medium.

Claims

Ansprüche Expectations
1. Ventil zum Steuern von Flüssigkeiten, mit einem in einer Bohrung (5) eines Ventilkorpers (6) axial verschiebbaren Ventilglied (2), das an einem Ende einen ein Ventilschließ- glied bildenden Ventilkopf (7) aufweist, der mit einem an dem Ventilkorper (6) vorgesehenen Sitz (8) zum Offnen und Schließen des Ventils (1) zusammenwirkt, und mit einem piezoelektrischen Aktor (3) zur Betätigung des Ventilglieds (2), wobei ein Vorspannelement (21) für den piezoelektri- sehen Aktor (3) und ein Toleranzausgleichselement (21) zum1. Valve for controlling liquids, with a valve member (2) which is axially displaceable in a bore (5) of a valve body (6) and which has at one end a valve head (7) which forms a valve closing member and which is connected to the valve body (6) provided seat (8) for opening and closing the valve (1) cooperates, and with a piezoelectric actuator (3) for actuating the valve member (2), a biasing element (21) for the piezoelectric actuator (3) and a tolerance compensation element (21) for
Ausgleich von Langungstoleranzen des piezolektrischen Aktors (3) und/oder weiterer Ventilbauteile (2, 6) vorgesehen ist, dadurch gekennzeichnet, daß auf einer dem Ventilglied (2) abgewandten Seite des piezoelektrischen Aktors (3) eine Hydraulikkammer (21) vorgesehen ist, die über wenigstens eine Hydraulikleitung (23) mit der gegenüber dem piezoelektrischen Aktor (3) abgedichteten Bohrung (5) des Ventilglieds (2) verbunden ist und in die ein mit dem piezoelektrischen Aktor (3) verbundener Kolben (20) eintauchbar ist, wobei die Hydraulikkammer (21) als hydraulische Feder ausgebildet ist, welche mit ihrer Federkraft auf den mit dem piezoelektrischen Aktor (3) verbundenen Kolben (20) das Vorspannelement und das Toleranzausgleichselement darstellt. Compensation of elongation tolerances of the piezoelectric actuator (3) and / or further valve components (2, 6) is provided, characterized in that a hydraulic chamber (21) is provided on a side of the piezoelectric actuator (3) facing away from the valve member (2) Via at least one hydraulic line (23) is connected to the bore (5) of the valve member (2) sealed from the piezoelectric actuator (3) and into which a piston (20) connected to the piezoelectric actuator (3) can be immersed, the hydraulic chamber (21) is designed as a hydraulic spring which, with its spring force on the piston (20) connected to the piezoelectric actuator (3), represents the prestressing element and the tolerance compensation element.
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der piezoelektrische Aktor (3) zwischen der hydraulischen Feder, die mittels eines Hydraulikmediums aus einer Niederdruckquelle in der Hydraulikkammer (21) gebildet ist, und einem Auflager (18) an einer der Hydraulikkammer (21) abgewandten Seite einer den piezoelektrischen Aktor (3) aufnehmenden Piezokammer (4) verspannt ist.2. Valve according to claim 1, characterized in that the piezoelectric actuator (3) between the hydraulic spring, which is formed by means of a hydraulic medium from a low pressure source in the hydraulic chamber (21), and a support (18) on one of the hydraulic chamber (21 ) facing away from a piezoelectric chamber (4) receiving the piezoelectric actuator (3) is clamped.
3. Ventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der piezoelektrische Aktor (3) mit einem an einem Aktorkopf (15) befestigten Stellkolben (17) in die gegenüber dem piezoelektrischen Aktor (3) abgedichtete, das Ventilglied (2) aufnehmende Bohrung (5) reicht.3. Valve according to claim 1 or 2, characterized in that the piezoelectric actuator (3) with an actuator head (15) attached to the actuating piston (17) in the sealed against the piezoelectric actuator (3), the valve member (2) receiving bore (5) is enough.
4. Ventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß die Hydraulikkammer (21) gegenüber dem piezoelektrischen Aktor (3) im Bereich des Kolbens (20) mittels einer Dichteinrichtung (22) abgedichtet ist, welche in einem Ringspalt (27) zwischen der Hydaulikkammer (21) und der Piezokammer (4) angeordnet ist.4. Valve according to claim 2 or 3, characterized in that the hydraulic chamber (21) with respect to the piezoelectric actuator (3) in the region of the piston (20) is sealed by means of a sealing device (22) which in an annular gap (27) between the Hydraulic chamber (21) and the piezo chamber (4) is arranged.
5. Ventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß die Hydraulikkammer (21) gegenüber dem piezoelektrischen Aktor (3) mittels einer Dichteinrichtung (22) abgedichtet ist, welche im Bereich der Piezokammer (4) angeordnet ist und eine Ringkammer (26) mit dem Durchmesser der Piezokammer (4) von dieser abtrennt, wobei die Hydraulikleitung (23) in die über einen Ringspalt (27) mit der Hydraulikkammer (21) verbundene Ringkammer (26) mundet.5. Valve according to claim 2 or 3, characterized in that the hydraulic chamber (21) with respect to the piezoelectric actuator (3) is sealed by a sealing device (22) which is arranged in the region of the piezo chamber (4) and an annular chamber (26) with the diameter of the piezo chamber (4) from the latter, the hydraulic line (23) opening into the annular chamber (26) connected to the hydraulic chamber (21) via an annular gap (27).
6. Ventil nach Anspruch 5, dadurch gekennzeichnet, daß im Bereich des Ringspaltes (27) an dem Kolben (20) eine Befüll- flache (28) ausgebildet ist. 6. Valve according to claim 5, characterized in that a filling flat (28) is formed in the region of the annular gap (27) on the piston (20).
7. Ventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das Volumen der Hydraulikkammer (21) mittels einer extern bedienbaren Justiereinrichtung (24) veränderbar ist.7. Valve according to one of claims 1 to 6, characterized in that the volume of the hydraulic chamber (21) can be changed by means of an externally operable adjusting device (24).
8. Ventil nach Anspruch 7, dadurch gekennzeichnet, daß die Justiereinrichtung als eine Stellschraube (24) ausgebildet ist, welche in das Hydraulikmedium der Hydraulikkammer (21) eintauchend schraubbar ist.8. Valve according to claim 7, characterized in that the adjusting device is designed as an adjusting screw (24) which can be screwed into the hydraulic medium of the hydraulic chamber (21).
9. Ventil nach einem der Ansprüche 1 bis 8, gekennzeichnet durch seine Verwendung als Bestandteil eines Kraftstoffein- spritzventils für Brennkraftmaschinen, insbesondere eines Common-Rail-Injektors (1).9. Valve according to one of claims 1 to 8, characterized by its use as part of a fuel injection valve for internal combustion engines, in particular a common rail injector (1).
10. Ventil nach Anspruch 9, dadurch gekennzeichnet, daß das Hydraulikmedium zur Befullung der Hydraulikkammer (21) Kraftstoff darstellt. 10. Valve according to claim 9, characterized in that the hydraulic medium for filling the hydraulic chamber (21) represents fuel.
EP00974319A 1999-09-30 2000-09-14 Valve for controlling liquids Expired - Lifetime EP1135594B1 (en)

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KR20010101060A (en) 2001-11-14
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