WO2002053958A1 - Valve for controlling liquids - Google Patents

Valve for controlling liquids Download PDF

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Publication number
WO2002053958A1
WO2002053958A1 PCT/DE2001/004754 DE0104754W WO02053958A1 WO 2002053958 A1 WO2002053958 A1 WO 2002053958A1 DE 0104754 W DE0104754 W DE 0104754W WO 02053958 A1 WO02053958 A1 WO 02053958A1
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WO
WIPO (PCT)
Prior art keywords
valve
piston
actuating piston
actuating
valve body
Prior art date
Application number
PCT/DE2001/004754
Other languages
German (de)
French (fr)
Inventor
Patrick Mattes
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 WO2002053958A1 publication Critical patent/WO2002053958A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/004—Actuating devices; Operating means; Releasing devices actuated by piezoelectric means
    • F16K31/007—Piezo-electric stacks
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N2/00—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction
    • H02N2/02—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction producing linear motion, e.g. actuators; Linear positioners ; Linear motors
    • H02N2/04—Constructional details
    • H02N2/043—Mechanical transmission means, e.g. for stroke amplification
    • 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 relates to a valve for controlling liquids according to the kind defined in the preamble of claim 1.
  • Such a valve is for example from the
  • EP 0 477 400 AI known.
  • This valve has a piezoelectric actuator, the deflection of which is transmitted to a valve closing element via an actuating piston, a hydraulic chamber and an actuating piston.
  • the hydraulic actuator has a piezoelectric actuator, the deflection of which is transmitted to a valve closing element via an actuating piston, a hydraulic chamber and an actuating piston.
  • 25 chamber works here on the one hand as a hydraulic transmission and on the other hand as a tolerance compensation element. It closes between the two pistons, one of which is designed with a smaller diameter and is connected to the valve closing element to be controlled and the other
  • the 30 right piston has a larger diameter and is connected to the piezoelectric actuator, a common removal equal volume.
  • the hydraulic chamber is clamped between the two pistons in such a way that the actuating piston makes a stroke that is increased by the ratio of the piston diameter when the piston of larger diameter is moved by a certain distance by means of the piezoelectric actuator.
  • the valve closing member, the pistons, the hydraulic chamber and the piezoelectric actuator are arranged one behind the other in the axial direction of the valve, which requires a corresponding overall length.
  • the valve body of the known valve has a plurality of axially adjacent components, the actuating piston and the actuating piston each being guided in a bore in a separate valve body component.
  • these bores can be arranged so as to be axially offset from one another so that the hydraulic chamber is formed in the region of the common diameter sectional area of the bores for the pistons and in the region of the parting plane between the components containing the bores.
  • the surface pressure between these components must not exceed a certain limit. Due to a relatively low surface pressure, however, there is a risk that leakage losses occur when the forces are transferred from the actuating piston to the actuating piston, which in turn lead to loss of power in the hydraulic transmission. Due to this fact, there is disadvantageously a large number of copies in a series.
  • the proposed valve for the control of liquids with the features according to the preamble of claim 1, in which the actuating piston and the actuating piston in L0 side by side holes in the valve body are guided, has the advantage that a considerable reduction in component and space is possible.
  • valve body in which the valve body is constructed in several parts and the two bores, which are assigned to the actuating piston or the actuating piston, lie in a common valve body component, which is, for example, disk-shaped, there is the advantage that internal leaks
  • the bores can each be designed as a cylindrical through-bore.
  • Such a bore can be treated by means of through grinding. This leads to a high quality of the bores assigned to the pistons and thus of the entire valve.
  • the hydraulic chamber 30 are connected to one another, preferably via a so-called hydraulic channel, which is assigned to the hydraulic chamber. is not.
  • the hydraulic chamber is then preferably designed such that it comprises a part of the area of the piston bore facing away from the actuator unit, which is provided for receiving the actuating piston, the hydraulic channel and a part of the area of the piston bore associated with the actuating piston facing away from the valve closing member.
  • the cross section of the hydraulic channel can have a diameter of approximately 0.8 mm, for example.
  • the diameter of the cross section of the hydraulic channel can have a diameter of approximately 0.8 mm, for example.
  • the adjusting piston is, for example, approximately 2.5 mm and that of the actuating piston is approximately 1.5 mm.
  • valve body component having the piston bores can be clamped to the adjacent valve body component, for example, by means of a clamping screw. Due to the fact that the coupler is integrated in the valve body component, which is designed, for example, as an intermediate plate, a good seal of the coupler can be achieved by introducing large axial forces by means of the clamping screw.
  • FIG. 1 is a sectional view of a valve for controlling liquids in connection with a fuel injection valve for internal combustion engines in longitudinal section; and FIG. 2 shows a section along the line II-II in FIG. 1.
  • .0 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 shown here is a common rail injector, which is used for the injection of preferably diesel fuel and at
  • L5 which controls the fuel injection via the pressure level into a valve control chamber 2, which is connected to a high-pressure supply line 5, which is connected to a high-pressure reservoir, a so-called common rail, which is common to several injectors.
  • a valve member 3 is actuated via an actuator input designed as a piezoelectric actuator 4.
  • the piezoelectric actuator 4 is constructed in the usual manner from a plurality of layers and has an actuator head 6 on its side facing the valve member 3, which is connected to
  • the actuating piston 7 is guided in a bore 8 of a component 9B, which is part of a valve body 9.
  • the component 9B of the valve body 9 borders in the axial direction 5 of the injection valve, ie parallel to the axis of the bore 8, on the one hand on a component 9A and on the other hand on a component 9C of the valve body . rs 9 and is pressed with this via a clamping nut, not shown here.
  • the valve member 3 comprises, in addition to the actuating piston 7, a second piston 10 which is arranged axially displaceably in a second bore 11 of the valve body component 9B.
  • This piston 10 is connected to a valve closing member 12 and serves to actuate the latter, which is why it
  • L5 is also referred to as an actuating piston.
  • the actuating piston 7 and the actuating piston 10 are coupled to one another via a hydraulic transmission.
  • the hydraulic transmission is designed as a hydraulic chamber 13.
  • a first area 14 which is arranged within the bore 8 and is arranged on the side of the actuating piston 7 facing away from the piezoelectric actuator 4, a second area designed as a hydraulic channel 15, which here has a
  • 25 NEN has a diameter of about 0.8 mm, and a third region 16 which is arranged within the bore 11 and adjoins the same on the side of the actuating piston 10 facing away from the valve closing member 12.
  • the diameter dl of the actuating piston 7 is larger than the diameter d2 of the actuating piston 10. Therefore, the Actuating piston 10, when the actuating piston 7 is moved a certain distance by means of the piezoelectric actuator 4, a stroke increased by the ratio of the piston diameters. 5
  • the diameter dl of the adjusting piston 7 is about 2.5 mm in the present case.
  • the diameter d2 of the actuating piston 10 is approximately 1.5 mm here.
  • the hydraulic chamber 13 consisting of the partial area 14, the hydraulic channel 15 and the partial area 16 also forms a compensation volume, by means of which tolerances due to temperature gradients in the component or different temperature expansion coefficients of the material used
  • the piston bores 11 and 8, which are assigned to the actuating piston 10 20 and the actuating piston 7, are each arranged in the component 9B of the valve body, which is designed in the manner of an intermediate disk.
  • the component 9B designed as an intermediate disk also has the hydraulic channel 15, which connects the bore 8 to the bore 11, and a further 25 bore 17, which is preferably aligned parallel to the axially parallel piston bores 11 and 8 and is part of the high-pressure inlet channel 5.
  • valve closing member 12 which here is hemispherical, acts with a valve member 9C formed on the valve body component 9C. tilsitz 18 together.
  • the valve seat 18 is formed in a valve chamber 19 enclosed by the valve body component 9C, into which a duct 22 branching off from the valve control chamber 2 opens with a so-called discharge throttle.
  • valve closing member 12 which is loaded by means of at least one spring 20 in the direction of the actuating piston 10, ie in the blocking direction.
  • valve closing member 12 separates the valve chamber 19 from a so-called outlet chamber 21, from which a leakage outlet channel (not shown here) branches off, which leads to a fuel storage tank (also not shown here).
  • valve control chamber 2 the valve chamber 19, the valve closing member 12, the piston bore 11 and the actuating piston 10 lie in a common axis.
  • the piezoelectric actuator also lies in a common axis.
  • valve body component 9B which is designed as a 25 intermediate washer
  • a good seal of the coupler is possible because, for example, by means of the mentioned clamping nut, a high axial force can be introduced into the valve body to brace the individual valve body components.
  • the fuel injection valve 1 shown in FIGS. 1 and 2 operates in the manner described below.
  • valve closing member 12 When the fuel injector 1 is closed, i.e. if there is no voltage at the piezoelectric actuator 4, the valve closing member 12 is against the valve seat 18. In this position, the valve closing member 12 seals the drain chamber 21 against the valve chamber 19. The valve closing member 12 is pressed against the valve seat 18 on the one hand by means of the spring 20 and on the other hand by means of the fluid pressure acting via the channel provided with a discharge throttle, which essentially corresponds to the common rail pressure.
  • the fuel injection valve 1 is to be opened, ie if an injection nozzle which is closed by a valve control piston (not shown here) and is also not shown here is to be opened, an electrical voltage is applied to the piezoelectric actuator 4, whereupon the latter suddenly changes in the axial direction , ie extends in the direction of the actuating piston 7.
  • the latter is thereby displaced in the direction of the valve body component 9C, as a result of which fluid located in the hydraulic chamber region 14 is displaced into the hydraulic chamber region 16 via the hydraulic channel 15.
  • the actuating piston 10 and thus also the valve closing member 12 are moved in the direction of the valve control chamber 2, so that a connection is established between the valve chamber 19 and the outlet chamber 21.
  • valve closing member 12 In this position of the valve closing member 12, fuel located in the valve chamber 19 flows into the outlet chamber 21 and from there via the leakage outlet channel, not shown.
  • the valve control chamber 2 is thus relieved of load via the channel 22 and the discharge throttle arranged in it, so that the pressure in the latter decreases and the valve control piston (not shown here) shifts in the direction of the channel 22.
  • the opening L0 leading to the combustion chamber of the internal combustion engine is opened and high-pressure fuel which is brought in via the high-pressure supply channel 5 is injected into the combustion chamber of the internal combustion engine.
  • the invention is not limited to the described preferred use for fuel injection valves. Rather, it is suitable for all valves with a piezoelectric actuator system, in which a valve closing element
  • the invention separates a high pressure area from a low pressure area, such as in pumps.
  • the invention can also be used in a so-called double-seat valve, that is to say in a valve with a valve closing element which interacts with two valve seats.

Abstract

The invention relates to a valve for controlling liquid. Said valve comprises an actuator unit (4), in particular a piezoelectric actuator for operating a valve member (3) that is located in a valve body, a valve closing member (12) that co-operates with at least one valve seat (18) being allocated to said valve member. The valve also has a control piston (7), which is connected to the actuator unit (4) and an actuator piston (10), which co-operates with the control piston (7) by means of a hydraulic chamber (13) and is connected to the valve closing member (12). To reduce construction space requirements and component size, the control piston (7) and the actuating piston (10) are configured in adjacent bores (8, 11) of the valve body.

Description

Ventil zum Steuern von Flüssigkeiten Valve for controlling liquids
Stand der Technik L5State of the art L5
Die Erfindung betrifft ein Ventil zum Steuern von Flüssigkeiten gemäß der im Oberbegriff des Patentanspruches 1 näher definierten Art.The invention relates to a valve for controlling liquids according to the kind defined in the preamble of claim 1.
20 Ein derartiges Ventil ist beispielsweise aus der20 Such a valve is for example from the
EP 0 477 400 AI bekannt. Dieses Ventil weist einen piezoelektrischen Aktor auf, dessen Auslenkung über einen Stell- kolben, eine Hydraulikkammer sowie einen Betätigungskolben auf ein Ventilschließglied übertragen wird. Die Hydraulik-EP 0 477 400 AI known. This valve has a piezoelectric actuator, the deflection of which is transmitted to a valve closing element via an actuating piston, a hydraulic chamber and an actuating piston. The hydraulic
25 kammer arbeitet hier einerseits als hydraulische Übersetzung und andererseits als Toleranzausgleichselement. Sie schließt zwischen den beiden Kolben, von denen einer mit einem kleineren Durchmesser ausgebildet ist und mit dem anzusteuernden Ventilschließglied verbunden ist und der ande-25 chamber works here on the one hand as a hydraulic transmission and on the other hand as a tolerance compensation element. It closes between the two pistons, one of which is designed with a smaller diameter and is connected to the valve closing element to be controlled and the other
30 re Kolben einen größeren Durchmesser aufweist und mit dem piezoelektrischen Aktor verbunden ist, ein gemeinsames Aus- gleichsvolumen ein. Die Hydraulikkammer ist derart zwischen den beiden Kolben eingespannt, daß der Bet tigungskolben einen um das Übersetzungsverhältnis der Kolbendurchmesser vergrößerten Hub macht, wenn der Kolben größeren Durchmessers mittels des piezoelektrischen Aktors um eine bestimmte Wegstrecke verfahren wird. Das Ventilschließglied, die Kolben, die Hydraulikkammer sowie der piezoelektrische Aktor sind dabei in axialer Richtung des Ventils hintereinander angeordnet, was eine entsprechende Baulänge bedingt.30 right piston has a larger diameter and is connected to the piezoelectric actuator, a common removal equal volume. The hydraulic chamber is clamped between the two pistons in such a way that the actuating piston makes a stroke that is increased by the ratio of the piston diameter when the piston of larger diameter is moved by a certain distance by means of the piezoelectric actuator. The valve closing member, the pistons, the hydraulic chamber and the piezoelectric actuator are arranged one behind the other in the axial direction of the valve, which requires a corresponding overall length.
Der Ventilkörper des bekannten Ventils weist mehrere axial aneinandergrenzende Bauteile auf, wobei der Betätigungskolben und der Stellkolben jeweils in einer Bohrung eines separaten Ventilkörperbauteils geführt sind. Diese Bohrungen können je nach Ausführung achsversetzt zueinander angeordnet sein, so daß die Hydraulikkammer im Bereich der gemeinsamen Durchmesserschnittfläche der Bohrungen für die Kolben und im Bereich der Trennebene zwischen den die Bohrungen enthaltenden Bauteilen gebildet wird. Die Flächenpressung zwischen diesen Bauteilen darf einen bestimmten Grenzwert nicht überschreiten. Durch eine relativ geringe Flächenpressung besteht jedoch die Gefahr, daß beim Übertragen der Kräfte von dem Stellkolben auf den Betätigungskolben Leckverluste auftreten, die wiederum zu Kraftverlusten bei der hydraulischen Übersetzung führen. Nachteilhafterweise bestehen aufgrund dieser Tatsache große Exemplarstreuungen bei einer Serie.The valve body of the known valve has a plurality of axially adjacent components, the actuating piston and the actuating piston each being guided in a bore in a separate valve body component. Depending on the design, these bores can be arranged so as to be axially offset from one another so that the hydraulic chamber is formed in the region of the common diameter sectional area of the bores for the pistons and in the region of the parting plane between the components containing the bores. The surface pressure between these components must not exceed a certain limit. Due to a relatively low surface pressure, however, there is a risk that leakage losses occur when the forces are transferred from the actuating piston to the actuating piston, which in turn lead to loss of power in the hydraulic transmission. Due to this fact, there is disadvantageously a large number of copies in a series.
Die beschriebenen Nachteile der bekannten Lösung treffen vor allem auf Servoventile zur Ansteuerung von als Common- Rail-Inj ektoren ausgebildeten Kraftstoffeinspritzventilen zu, bei denen eine hocheffiziente und präzise Funktion erwünscht ist sowie ein nur begrenzter Bauraum zur Verfügung steht .The disadvantages of the known solution described above apply in particular to servo valves for controlling fuel injection valves designed as common rail injectors for which a highly efficient and precise function is desired and only a limited space is available.
5 Vorteile der Erfindung5 advantages of the invention
Das vorgeschlagene Ventil zur Steuerung von Flüssigkeiten mit den Merkmalen nach dem Oberbegriff des Patentanspruches 1, bei welchem der Stellkolben und der Betätigungskolben in L0 nebeneinander angeordneten Bohrungen des Ventilkörpers geführt sind, hat den Vorteil, daß eine erhebliche Bauteil- und Bauraumreduzierung möglich ist.The proposed valve for the control of liquids with the features according to the preamble of claim 1, in which the actuating piston and the actuating piston in L0 side by side holes in the valve body are guided, has the advantage that a considerable reduction in component and space is possible.
Insbesondere bei einer vorteilhaften Ausführung der Erfin- L5 düng, bei welcher der Ventilkörper mehrteilig aufgebaut ist und die beiden Bohrungen, die dem Stellkolben bzw. dem Betätigungskolben zugeordnet sind, in einem gemeinsamen Ventilkörperbauteil liegen, das beispielsweise scheibenförmig ausgebildet ist, besteht der Vorteil, daß innere LeckagenIn particular in an advantageous embodiment of the inven- L5 fertilizer, in which the valve body is constructed in several parts and the two bores, which are assigned to the actuating piston or the actuating piston, lie in a common valve body component, which is, for example, disk-shaped, there is the advantage that internal leaks
20 vermieden werden können.20 can be avoided.
Des weiteren können die Bohrungen jeweils als zylindrische Durchgangsbohrung ausgebildet sein. Eine solche Bohrung kann mittels Durchgangsschleifen behandelt sein. Dies führt 25 zu einer hohen Qualität der den Kolben zugeordneten Bohrungen und damit des gesamten Ventils.Furthermore, the bores can each be designed as a cylindrical through-bore. Such a bore can be treated by means of through grinding. This leads to a high quality of the bores assigned to the pistons and thus of the entire valve.
Zur Übertragung der Kräfte von dem Stellkolben auf den Betätigungskolben sind die Bohrungen, in denen diese geführtTo transmit the forces from the actuating piston to the actuating piston, there are holes in which they are guided
30 sind, vorzugsweise über einen sogenannten Hydraulikkanal miteinander verbunden, welcher der Hydraulikkammer zugeord- net ist. Die Hydraulikkammer ist dann vorzugsweise so ausgebildet, daß sie einen Teil des der Aktuator-Einheit abgewandten Bereichs der Kolbenbohrung, die zur Aufnahme des Stellkolbens vorgesehen ist, den Hydraulikkanal sowie einen Teil des dem Ventilschließglied abgewandten Bereichs der dem Betätigungskolben zugeordneten Kolbenbohrung umfaßt.30 are connected to one another, preferably via a so-called hydraulic channel, which is assigned to the hydraulic chamber. is not. The hydraulic chamber is then preferably designed such that it comprises a part of the area of the piston bore facing away from the actuator unit, which is provided for receiving the actuating piston, the hydraulic channel and a part of the area of the piston bore associated with the actuating piston facing away from the valve closing member.
Der Querschnitt des Hydraulikkanals kann beispielsweise in einer vorteilhaften Ausführung der Erfindung einen Durch- messer von etwa 0,8 mm aufweisen. Der Durchmesser desIn an advantageous embodiment of the invention, the cross section of the hydraulic channel can have a diameter of approximately 0.8 mm, for example. The diameter of the
Stellkolbens beträgt beispielsweise etwa 2 , 5 mm und derjenige des Betätigungskolbens etwa 1,5 mm.The adjusting piston is, for example, approximately 2.5 mm and that of the actuating piston is approximately 1.5 mm.
Das die Kolbenbohrungen aufweisende Ventilkörperbauteil kann beispielsweise mittels einer Spannschraube mit dem angrenzenden Ventilkörperbauteil verspannt sein. Dadurch, daß der Koppler in das beispielsweise als Zwischenplatte ausgeführte Ventilkörperbauteil integriert ist, kann mittels der Spannschraube durch Einleiten großer Axialkräfte eine gute Abdichtung des Kopplers erreicht werden.The valve body component having the piston bores can be clamped to the adjacent valve body component, for example, by means of a clamping screw. Due to the fact that the coupler is integrated in the valve body component, which is designed, for example, as an intermediate plate, a good seal of the coupler can be achieved by introducing large axial forces by means of the clamping screw.
Weitere Vorteile und vorteilhafte Weiterbildungen des Gegenstandes nach der Erfindung ergeben sich aus der Beschreibung, der Zeichnung und den Patentansprüchen.Further advantages and advantageous developments of the object according to the invention result from the description, the drawing and the patent claims.
Zeichnungdrawing
Ein Ausführungsbeispiel des Ventils zum Steuern von Flüssigkeiten nach der Erfindung ist in der Zeichnung schema- tisch vereinfacht dargestellt und wird in der nachfolgenden Beschreibung näher erläutert . Es zeigen Figur 1 eine ausschnittsweise Darstellung eines Ventils zum Steuern von Flüssigkeiten in Verbindung mit einem Kraftstoffeinspritzventil für Brennkraftmaschinen im Längsschnitt; und 5 Figur 2 einen Schnitt entlang der Linie II-II in Figur 1.An embodiment of the valve for controlling liquids according to the invention is shown schematically simplified in the drawing and is explained in more detail in the following description. Show it Figure 1 is a sectional view of a valve for controlling liquids in connection with a fuel injection valve for internal combustion engines in longitudinal section; and FIG. 2 shows a section along the line II-II in FIG. 1.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Das in den Figuren 1 und 2 dargestellte AusführungsbeispielThe embodiment shown in Figures 1 and 2
.0 zeigt eine Verwendung des Ventils nach der Erfindung bei einem Kraftstoffeinspritzventil 1 für Brennkraftmaschinen von Kraftfahrzeugen. Das hier dargestellte Kraftstoffein- spritzventil 1 ist ein Common-Rail-Inj ektor, der zur Einspritzung von vorzugsweise Dieselkraftstoff dient und bei.0 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 shown here is a common rail injector, which is used for the injection of preferably diesel fuel and at
L5 dem die Kraftstoffeinspritzung über das Druckniveau in einen Ventilsteuerraum 2 gesteuert wird, der mit einer Hochdruckzufuhrleitung 5 verbunden ist, welche mit einem für mehrere Einspritzventile gemeinsamen Hochdruckspeicher, einem sogenannten Common-Rail, in Verbindung steht.L5, which controls the fuel injection via the pressure level into a valve control chamber 2, which is connected to a high-pressure supply line 5, which is connected to a high-pressure reservoir, a so-called common rail, which is common to several injectors.
2020
Zur Einstellung eines Einspritzbeginns, einer Einspritzdauer und einer Einspritzmenge über Kräf everhältnisse in dem Kraftstoffeinspritzventil 1 wird ein Ventilglied 3 über eine als piezoelektrischer Aktor 4 ausgebildete Aktuator-Ein-In order to set an injection start, an injection duration and an injection quantity via force ratios in the fuel injection valve 1, a valve member 3 is actuated via an actuator input designed as a piezoelectric actuator 4.
25 heit angesteuert, welche auf der ventilsteuerraum- und brennraumabgewandten Seite des Ventilgliedes 3 angeordnet ist. Der piezoelektrische Aktor 4 ist in üblicher Weise aus mehreren Schichten aufgebaut und weist auf seiner dem Ventilglied 3 zugewandten Seite einen Aktorkopf 6 auf, der mit25 driven, which is arranged on the valve control chamber and the combustion chamber remote side of the valve member 3. The piezoelectric actuator 4 is constructed in the usual manner from a plurality of layers and has an actuator head 6 on its side facing the valve member 3, which is connected to
30 einem dem Ventilglied 3 zugeordneten sogenannten Stellkolben 7 verbunden ist. Der Stellkolben 7 ist in einer Bohrung 8 eines Bauteiles 9B, welches Teil eines Ventilkörpers 9 ist, geführt. Das Bauteil 9B des Ventilkörpers 9 grenzt in axialer Richtung 5 des Einspritzventils, d.h. parallel zur Achse der Bohrung 8, einerseits an ein Bauteil 9A und andererseits an ein Bauteil 9C des Ventilkörpe.rs 9 an und ist mit diesen über eine hier nicht dargestellte Spannmutter verpreßt.30 is connected to a so-called control piston 7 assigned to the valve member 3. The actuating piston 7 is guided in a bore 8 of a component 9B, which is part of a valve body 9. The component 9B of the valve body 9 borders in the axial direction 5 of the injection valve, ie parallel to the axis of the bore 8, on the one hand on a component 9A and on the other hand on a component 9C of the valve body . rs 9 and is pressed with this via a clamping nut, not shown here.
L0 Das Ventilglied 3 umfaßt neben dem Stellkolben 7 einen zweiten Kolben 10, der in einer zweiten Bohrung 11 des Ventilkörperbauteils 9B axial verschiebbar angeordnet ist. Dieser Kolben 10 ist mit einem Ventilschließglied 12 verbunden und dient zur Betätigung des letzteren, weshalb erL0 The valve member 3 comprises, in addition to the actuating piston 7, a second piston 10 which is arranged axially displaceably in a second bore 11 of the valve body component 9B. This piston 10 is connected to a valve closing member 12 and serves to actuate the latter, which is why it
L5 auch als Betätigungskolben bezeichnet wird.L5 is also referred to as an actuating piston.
Der Stellkolben 7 und der Betätigungskolben 10 sind über eine hydraulische Übersetzung miteinander gekoppelt. Die hydraulische Übersetzung ist als Hydraulikkammer 13 ausge-The actuating piston 7 and the actuating piston 10 are coupled to one another via a hydraulic transmission. The hydraulic transmission is designed as a hydraulic chamber 13.
20 bildet, welche aus drei Teilbereichen besteht, nämlich einem ersten Bereich 14, der innerhalb der Bohrung 8 angeordnet ist und auf der dem piezoelektrischen Aktor 4 abgewandten Seite des Stellkolbens 7 angeordnet ist, einem als Hydraulikkanal 15 ausgebildeten zweiten Bereich, der hier ei-20, which consists of three sub-areas, namely a first area 14, which is arranged within the bore 8 and is arranged on the side of the actuating piston 7 facing away from the piezoelectric actuator 4, a second area designed as a hydraulic channel 15, which here has a
25 nen Durchmesser von etwa 0,8 mm aufweist, sowie einem dritten Bereich 16, der innerhalb der Bohrung 11 angeordnet ist und auf der dem Ventilschließglied 12 abgewandten Seite des Betätigungskolbens 10 an denselben angrenzt.25 NEN has a diameter of about 0.8 mm, and a third region 16 which is arranged within the bore 11 and adjoins the same on the side of the actuating piston 10 facing away from the valve closing member 12.
30 Der Durchmesser dl des Stellkolbens 7 ist größer als der Durchmesser d2 des Betätigungskolbens 10. Daher macht der Betätigungskolben 10, wenn der Stellkolben 7 mittels des piezoelektrischen Aktors 4 um eine bestimmte Wegstrecke verfahren wird, einen um das Übersetzungsverhältnis der Kolbendurchmesser vergrößerten Hub. 530 The diameter dl of the actuating piston 7 is larger than the diameter d2 of the actuating piston 10. Therefore, the Actuating piston 10, when the actuating piston 7 is moved a certain distance by means of the piezoelectric actuator 4, a stroke increased by the ratio of the piston diameters. 5
Der Durchmesser dl des Stellkolbens 7 beträgt im vorliegenden Fall etwa 2,5 mm. Der Durchmesser d2 des Betätigungskolbens 10 beträgt hier etwa 1,5 mm.The diameter dl of the adjusting piston 7 is about 2.5 mm in the present case. The diameter d2 of the actuating piston 10 is approximately 1.5 mm here.
L0 Die aus dem Teilbereich 14, dem Hydraulikkanal 15 und dem Teilbereich 16 bestehende Hydraulikkammer 13 bildet zudem ein Ausgleichsvolumen, mittels dem Toleranzen aufgrund von Temperaturgradienten im Bauteil oder unterschiedlicher Temperaturausdehnungskoeffizienten der eingesetzten Materiali-L0 The hydraulic chamber 13 consisting of the partial area 14, the hydraulic channel 15 and the partial area 16 also forms a compensation volume, by means of which tolerances due to temperature gradients in the component or different temperature expansion coefficients of the material used
L5 en sowie eventuelle Setzeffekte ausgeglichen werden können, ohne daß dadurch eine Änderung der Position des anzusteuernden Ventilschließglieds 12 erfolgen würde.L5 s as well as possible setting effects can be compensated for without a change in the position of the valve closing element 12 to be controlled.
Die Kolbenbohrungen 11 und 8, die dem Betätigungskolben 10 20 bzw. dem Stellkolben 7 zugeordnet sind, sind jeweils in dem nach Art einer Zwischenscheibe ausgebildeten Bauteil 9B des Ventilkörpers angeordnet. Das als Zwischenscheibe ausgebildete Bauteil 9B weist zudem den Hydraulikkanal 15, der die Bohrung 8 mit der Bohrung 11 verbindet, sowie eine weitere 25 Bohrung 17 auf, die vorzugsweise parallel zu den achsparallel ausgerichteten Kolbenbohrungen 11 und 8 ausgerichtet ist und Teil des Hochdruckzulaufkanals 5 ist.The piston bores 11 and 8, which are assigned to the actuating piston 10 20 and the actuating piston 7, are each arranged in the component 9B of the valve body, which is designed in the manner of an intermediate disk. The component 9B designed as an intermediate disk also has the hydraulic channel 15, which connects the bore 8 to the bore 11, and a further 25 bore 17, which is preferably aligned parallel to the axially parallel piston bores 11 and 8 and is part of the high-pressure inlet channel 5.
An dem ventilsteuerraumseiten Ende des Ventilglieds 3 wirkt 30 das hier halbkugelartig ausgebildete Ventilschließglied 12 mit einem an dem Ventilkörperbauteil 9C ausgebildeten Ven- tilsitz 18 zusammen. Der Ventilsitz 18 ist in einem von dem Ventilkörperbauteil 9C umschlossenen Ventilraum 19 ausgebildet, in den ein von dem Ventilsteuerraum 2 abzweigender Kanal 22 mit einer sogenannten Ablau drossel mündet. In dem 5 Ventilraum 19 ist auch das Ventilschließglied 12 angeordnet, welches mittels mindestens einer Feder 20 in Richtung des Betätigungskolbens 10, d.h. in Sperrichtung, belastet ist .At the valve control chamber side end of the valve member 3, the valve closing member 12, which here is hemispherical, acts with a valve member 9C formed on the valve body component 9C. tilsitz 18 together. The valve seat 18 is formed in a valve chamber 19 enclosed by the valve body component 9C, into which a duct 22 branching off from the valve control chamber 2 opens with a so-called discharge throttle. In the 5 valve chamber 19 there is also the valve closing member 12, which is loaded by means of at least one spring 20 in the direction of the actuating piston 10, ie in the blocking direction.
L0 In Sperrstellung trennt das Ventilschließglied 12 den Ventilraum 19 von einem sogenannten Ablaufräum 21, von welchem ein hier nicht dargestellter Leckageablaufkanal abzweigt, der zu einem hier ebenfalls nicht dargestellten Kraftstoffvorratstank führt .L0 In the blocking position, the valve closing member 12 separates the valve chamber 19 from a so-called outlet chamber 21, from which a leakage outlet channel (not shown here) branches off, which leads to a fuel storage tank (also not shown here).
L5L5
Der Ventilsteuerraum 2, der Ventilraum 19, das Ventilschließglied 12, die Kolbenbohrung 11 sowie der Bet tigungskolben 10 liegen in einer gemeinsamen Achse. Ebenfalls in einer gemeinsamen Achse liegen der piezoelektrische Ak-The valve control chamber 2, the valve chamber 19, the valve closing member 12, the piston bore 11 and the actuating piston 10 lie in a common axis. The piezoelectric actuator also lies in a common axis.
20 tor 4, die Kolbenbohrung 8 sowie der Stellkolben 7. Diese beiden Achsen sind im vorliegenden Fall parallel zueinander ausgerichtet .20 gate 4, the piston bore 8 and the actuating piston 7. These two axes are aligned parallel to each other in the present case.
Dadurch, daß der gesamte hydraulische Koppler in dem als 25 Zwischenscheibe ausgebildeten Ventilkörperbauteil 9B integriert ist, ist eine gute Abdichtung des Kopplers möglich, denn beispielsweise mittels der erwähnten Spannmutter kann hier zur Verspannung der einzelnen Ventilkδrperbauteile miteinander eine hohe Axialkraft in den Ventilkδrper einge-Due to the fact that the entire hydraulic coupler is integrated in the valve body component 9B, which is designed as a 25 intermediate washer, a good seal of the coupler is possible because, for example, by means of the mentioned clamping nut, a high axial force can be introduced into the valve body to brace the individual valve body components.
30 leitet werden. Das in den Figuren 1 und 2 dargestellte Kraftstoffein- spritzventil 1 arbeitet in nachfolgend beschriebener Weise.30 heads. The fuel injection valve 1 shown in FIGS. 1 and 2 operates in the manner described below.
In geschlossenem Zustand des Kraftstoffeinspritzventils 1, d.h. wenn keine Spannung an dem piezoelektrischen Aktor 4 anliegt, liegt das Ventilschließglied 12 an dem Ventilsitz 18 an. In dieser Stellung dichtet das Ventilschließglied 12 den Ablaufraum 21 gegen den Ventilraum 19 ab. Das Ventilschließglied 12 wird zum einen mittels der Feder 20 und zum andern mittels des über den mit einer Ablaufdrossel versehenen Kanal wirkenden Fluiddrucks, der im wesentlichen dem Common-Rail-Druck entspricht, gegen den Ventilsitz 18 gepreßt .When the fuel injector 1 is closed, i.e. if there is no voltage at the piezoelectric actuator 4, the valve closing member 12 is against the valve seat 18. In this position, the valve closing member 12 seals the drain chamber 21 against the valve chamber 19. The valve closing member 12 is pressed against the valve seat 18 on the one hand by means of the spring 20 and on the other hand by means of the fluid pressure acting via the channel provided with a discharge throttle, which essentially corresponds to the common rail pressure.
Wenn das Kraftstoffeinspritzventil 1 geöffnet werden soll, d.h. wenn ein durch einen hier nicht dargestellten Ventil - steuerkolben verschlossene, hier ebenfalls nicht dargestellte Einspritzdüse geöffnet werden soll, wird an dem piezoelektrischen Aktor 4 eine elektrische Spannung ange- legt, worauf sich dieser schlagartig in axialer Richtung, d.h. in Richtung des Stellkolbens 7, ausdehnt. Letzterer wird dadurch in Richtung des Ventilkörperbauteils 9C verschoben, wodurch in dem Hydraulikkammerbereich 14 befindliches Fluid über den Hydraulikkanal 15 in den Hydraulikkam- merbereich 16 verdrängt wird. Dadurch wird wiederum der Betätigungskolben 10 und damit auch das Ventilschließglied 12 in Richtung des Ventilsteuerraums 2 verfahren, so daß eine Verbindung zwischen dem Ventilraum 19 und dem Ablaufräum 21 hergestellt wird. In dieser Stellung des Ventilschließglieds 12 strömt sich in dem Ventilraum 19 befindlicher Kraftstoff in den Ablaufraum 21 und von dort über den nicht dargestellten Leckageablaufkanal ab. Über den Kanal 22 und die in diesem ange- 5 ordnete Ablaufdrossel wird dadurch der Ventilsteuerraum 2 entlastet, so daß sich der Druck in demselben abbaut und sich der hier nicht dargestellte Ventilsteuerkolben in Richtung des Kanals 22 verschiebt. Dadurch wird die zu dem Verbrennungsraum der Verbrennungsmaschine führende Öffnung L0 freigegeben und unter Hochdruck stehender, über den Hochdruckzufuhrkanal 5 herangeführter Kraftstoff wird in den Verbrennungsraum der Verbrennungsmaschine eingespritzt.If the fuel injection valve 1 is to be opened, ie if an injection nozzle which is closed by a valve control piston (not shown here) and is also not shown here is to be opened, an electrical voltage is applied to the piezoelectric actuator 4, whereupon the latter suddenly changes in the axial direction , ie extends in the direction of the actuating piston 7. The latter is thereby displaced in the direction of the valve body component 9C, as a result of which fluid located in the hydraulic chamber region 14 is displaced into the hydraulic chamber region 16 via the hydraulic channel 15. As a result, the actuating piston 10 and thus also the valve closing member 12 are moved in the direction of the valve control chamber 2, so that a connection is established between the valve chamber 19 and the outlet chamber 21. In this position of the valve closing member 12, fuel located in the valve chamber 19 flows into the outlet chamber 21 and from there via the leakage outlet channel, not shown. The valve control chamber 2 is thus relieved of load via the channel 22 and the discharge throttle arranged in it, so that the pressure in the latter decreases and the valve control piston (not shown here) shifts in the direction of the channel 22. As a result, the opening L0 leading to the combustion chamber of the internal combustion engine is opened and high-pressure fuel which is brought in via the high-pressure supply channel 5 is injected into the combustion chamber of the internal combustion engine.
Wird nun die an dem piezoelektrischen Aktor 4 angelegte L5 Spannung unterbrochen, so wird der Stellkolben 7 in Richtung des Aktors 4 zurückgefahren, wodurch der Druck, der in der zwischen dem Stellkolben 7 und dem Betätigungskolben 10 liegenden Hydraulikkammer herrscht, reduziert wird. Das Ventilschließglied 12 und der Betätigungskolben 10 werdenIf the L5 voltage applied to the piezoelectric actuator 4 is now interrupted, the actuating piston 7 is retracted in the direction of the actuator 4, whereby the pressure prevailing in the hydraulic chamber between the actuating piston 7 and the actuating piston 10 is reduced. The valve closing member 12 and the actuating piston 10 are
20 dann mittels der Feder 20 und des über den Kanal 22 auf die freie Stirnfläche des Ventilschließglieds 12 wirkenden Drucks in Richtung des Ventilkörperbauteils 9A verfahren, bis das Ventilschließglied 12 an dem Ventilsitz 18 zum Anliegen kommt . 2520 then move in the direction of the valve body component 9A by means of the spring 20 and the pressure acting on the free end face of the valve closing member 12 via the channel 22 until the valve closing member 12 comes into contact with the valve seat 18. 25
Die Erfindung ist nicht nur auf die beschriebene bevorzugte Verwendung bei Kraftstoffeinspritzventilen beschränkt. Vielmehr eignet sie sich bei allen Ventilen mit einer piezoelektrischen Aktuatorik, bei denen ein VentilschließgliedThe invention is not limited to the described preferred use for fuel injection valves. Rather, it is suitable for all valves with a piezoelectric actuator system, in which a valve closing element
30 einen Hochdruckbereich von einem Niederdruckbereich trennt, wie z.B. in Pumpen. Die Erfindung ist auch bei einem sogenannten Doppelsitzventil, d.h. bei einem Ventil mit einem mit zwei Ventilsitzen zusammenwirkenden Ventilschiießglied, anwendbar. 30 separates a high pressure area from a low pressure area, such as in pumps. The invention can also be used in a so-called double-seat valve, that is to say in a valve with a valve closing element which interacts with two valve seats.

Claims

L 0 Ansprüche L 0 claims
1. Ventil zum Steuern von Flüssigkeiten, mit einer Aktuator-Einheit (4), insbesondere mit einem piezoelektrischen Aktuator, zur Betätigung eines in einem Ventilkör-1. Valve for controlling liquids, with an actuator unit (4), in particular with a piezoelectric actuator, for actuating one in a valve body.
.5 per (9) angeordneten Ventilglieds (3) , dem ein mit mindestens einem Ventilsitz (18) zusammenwirkendes Ventil - schließglied (12) zugeordnet ist und das einen Stellkolben (7) , der mit der Aktuator-Einheit (4) verbunden ist, und einen Betätigungskolben (10) aufweist, der über eine.5 valve member (3) arranged with (9), to which a valve-closing member (12) cooperating with at least one valve seat (18) is assigned and the one actuating piston (7), which is connected to the actuator unit (4), and an actuating piston (10) which via a
>0 Hydraulikkammer (13) mit dem Stellkolben (7) in Wirkverbindung steht und mit dem Ventilschließglied (12) verbunden ist, dadurch gekennzeichnet, daß der Stellkolben (7) und der Betätigungskolben (10) in nebeneinander angeordneten Bohrungen (8, 11) des Ventilkörpers (9) ge-> 0 hydraulic chamber (13) is operatively connected to the actuating piston (7) and is connected to the valve closing member (12), characterized in that the actuating piston (7) and the actuating piston (10) are arranged in bores (8, 11) of the Valve body (9)
!5 führt sind.! 5 leads.
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Ventilkörper (9) mehrteilig aufgebaut ist und die beiden Bohrungen (11, 8), die dem Stellkolben (7) bzw. dem Be-2. Valve according to claim 1, characterized in that the valve body (9) is constructed in several parts and the two bores (11, 8) which the actuating piston (7) or the loading
10 tätigungskolben (10) zugeordnet sind, in einem gemeinsamen Ventilkörperbauteil (9B) liegen. 10 actuating pistons (10) are assigned to lie in a common valve body component (9B).
3. Ventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Achsen der Kolbenbohrungen (8, 11) parallel ausgerichtet sind.3. Valve according to claim 1 or 2, characterized in that the axes of the piston bores (8, 11) are aligned in parallel.
4. Ventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Durchmesser (dl) des Stellkolbens (7) größer ist als der Durchmesser (d2) des Betätigungskolbens (10) .4. Valve according to one of claims 1 to 3, characterized in that the diameter (dl) of the actuating piston (7) is larger than the diameter (d2) of the actuating piston (10).
L0L0
5. Ventil nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Kolbenbohrungen (8, 11) über einen Hydraulikkanal (15) miteinander in Verbindung stehen, welcher der Hydraulikkammer (13) zugeordnet ist.5. Valve according to one of claims 1 to 4, characterized in that the piston bores (8, 11) are connected to one another via a hydraulic channel (15) which is assigned to the hydraulic chamber (13).
L5L5
6. Ventil nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Hydraulikkanal (15) von dem der Aktuator-Einheit (4) abgewandten Bereich der dem Stellkolben6. Valve according to one of claims 1 to 4, characterized in that the hydraulic channel (15) from that of the actuator unit (4) facing away from the area of the actuating piston
(7) zugeordneten Kolbenbohrung (8) zu dem dem Ventil- 20 schließglied (12) abgewandten Bereich der dem Betätigungskolben (10) zugeordneten Kolbenbohrung (11) führt.(7) assigned piston bore (8) leads to the region of the piston bore (11) assigned to the actuating piston (10) facing away from the valve closing member (12).
7. Ventil nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß der Querschnitt des Hydraulikkanals (15) einen7. Valve according to claim 5 or 6, characterized in that the cross section of the hydraulic channel (15) one
25 Durchmesser von wenigstens annähernd 0,8 mm .hat .25 diameter of at least approximately 0.8 mm.
8. Ventil nach einem der Ansprüche 2 bis 7, dadurch gekennzeichnet, daß das die Kolbenbohrungen (8, 11) aufweisende Ventilkörperbauteil (9B) mittels einer Spannschraube8. Valve according to one of claims 2 to 7, characterized in that the valve body component (9B) having the piston bores (8, 11) by means of a clamping screw
30 mit den angrenzenden Ventilkörperbauteilen (9A, 9C) verspannt ist. 30 is clamped to the adjacent valve body components (9A, 9C).
PCT/DE2001/004754 2001-01-05 2001-12-14 Valve for controlling liquids WO2002053958A1 (en)

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DE10100392.7 2001-01-05
DE2001100392 DE10100392C1 (en) 2001-01-05 2001-01-05 Fluid control valve for IC engine fuel injection has setting piston and operating piston received in adjacent bores in valve body

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110440046A (en) * 2019-09-06 2019-11-12 厦门赛尔特电子有限公司 A kind of liquid transmitting stroke amplifying type Piezoelectric switches valve
FR3122053A1 (en) * 2021-04-15 2022-10-21 Psa Automobiles Sa piezo-hydraulic device for multiplying a force from a piezoelectric element

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006012078A1 (en) * 2005-11-15 2007-05-16 Bosch Gmbh Robert Fuel injection device for an internal combustion engine with direct fuel injection
DE102010047940B4 (en) * 2010-10-08 2019-03-14 Tdk Electronics Ag Arrangement of a piezoelectric actuator
DE102011088282A1 (en) * 2011-12-12 2013-06-13 Continental Automotive Gmbh Injector
WO2015044420A2 (en) * 2013-09-27 2015-04-02 Siemens Aktiengesellschaft Lifting system, method for electrical testing, vibration damper, and machine assembly
DE102014219604A1 (en) * 2014-09-26 2016-03-31 Siemens Aktiengesellschaft Lifting system, electrical testing method, vibration damper and machine unit
DE102015225749A1 (en) 2015-12-17 2017-06-22 Robert Bosch Gmbh fuel injector

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0477400A1 (en) 1990-09-25 1992-04-01 Siemens Aktiengesellschaft Device for compensating the tolerance in the lift direction of the displacement transformer of a piezoelectric actuator
EP0864743A2 (en) * 1997-03-10 1998-09-16 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE19709794A1 (en) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Valve for controlling liquids
DE19835494A1 (en) * 1998-08-06 2000-02-10 Bosch Gmbh Robert Pump-nozzle unit for supplying fuel to a combustion chamber of a direct-injection control valve
DE19906266A1 (en) * 1999-02-15 2000-08-17 Bosch Gmbh Robert Fuel injection valve has actuation arrangement that enables second opening force to be introduced for opening valve element that acts in addition to first opening force

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0477400A1 (en) 1990-09-25 1992-04-01 Siemens Aktiengesellschaft Device for compensating the tolerance in the lift direction of the displacement transformer of a piezoelectric actuator
EP0864743A2 (en) * 1997-03-10 1998-09-16 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE19709794A1 (en) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Valve for controlling liquids
DE19835494A1 (en) * 1998-08-06 2000-02-10 Bosch Gmbh Robert Pump-nozzle unit for supplying fuel to a combustion chamber of a direct-injection control valve
DE19906266A1 (en) * 1999-02-15 2000-08-17 Bosch Gmbh Robert Fuel injection valve has actuation arrangement that enables second opening force to be introduced for opening valve element that acts in addition to first opening force

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110440046A (en) * 2019-09-06 2019-11-12 厦门赛尔特电子有限公司 A kind of liquid transmitting stroke amplifying type Piezoelectric switches valve
FR3122053A1 (en) * 2021-04-15 2022-10-21 Psa Automobiles Sa piezo-hydraulic device for multiplying a force from a piezoelectric element

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