EP1135594B1 - Valve for controlling liquids - Google Patents
Valve for controlling liquids Download PDFInfo
- Publication number
- EP1135594B1 EP1135594B1 EP00974319A EP00974319A EP1135594B1 EP 1135594 B1 EP1135594 B1 EP 1135594B1 EP 00974319 A EP00974319 A EP 00974319A EP 00974319 A EP00974319 A EP 00974319A EP 1135594 B1 EP1135594 B1 EP 1135594B1
- 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.)
- Expired - Lifetime
Links
Images
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 relates to a valve for controlling liquids according to the preamble of claim 1.
- a valve of this type which via a piezoelectric actuator is actuated, already known.
- This known valve has an arrangement for one adaptive mechanical tolerance compensation acting in the stroke direction for a path transformer of the piezoelectric Actuator on which the deflection of the piezoelectric Actuator is transmitted via a hydraulic chamber.
- the hydraulic chamber which is called a hydraulic Translation works, closes between two bounding it Pistons, one of which is a piston with a smaller diameter is formed and with a valve member to be controlled is connected and the other piston with a larger one Diameter is formed and with the piezoelectric Actuator is connected, a common compensation volume.
- the hydraulic chamber is between the two pistons clamped that the actuating piston of the valve member, in its rest position using one or more springs is held relative to a predetermined position, a increased by the ratio of the piston diameter Stroke makes when the larger piston by the piezoelectric Actuator is moved by a certain distance.
- the valve member, the pistons and the piezoelectric actuator lie one behind the other on a common axis.
- Tolerances can be set via the compensation volume of the hydraulic chamber due to temperature gradients in the component or different coefficients of thermal expansion of the used materials and any setting effects compensated without changing the position of the valve element to be controlled occurs.
- a piezoelectric Actuator is made up of several thin layers, to achieve the largest possible stroke. So that this Layers when the piezoelectric actuator is energized the piezoelectric actuator must not separate be biased, the force to be applied can be approximately 1000 N.
- the invention has for its object a valve for Control of liquids by creating the preload of a piezoelectric actuator and tolerance compensation with little space requirement with a simple construction is realized with as few components as possible.
- valve according to the invention for controlling liquids with the characterizing features of claim 1 the advantage that with the trained as a hydraulic spring Hydraulic chamber is also a biasing element for the piezoelectric actuator and a compensation element for in particular Temperature-related elongation tolerances realized is.
- the preload is hydraulic and with low actuator Space requirements shown, with the omission of springs or other mechanical biasing elements a desired slim design of the entire valve is possible.
- An important advantage of the invention is furthermore in that by dimensioning the hydraulic chamber, the hydraulic spring and the piston immersed in it Overall system rigidity can be increased. Since the Rigidity of the hydraulic spring from the cross-sectional area of the piston is dependent on the same pressure Rigidity of the hydraulic spring and thus the preload be increased to the piezoelectric actuator if the cross-sectional area of the immersed in the hydraulic chamber Piston is increased accordingly.
- a disadvantageous change in length can also occur with a high spring rate of the entire facility can be avoided if the piezoelectric actuator, the valve member or the valve body its length e.g. changes when heated.
- Second is in the case of dynamic actuation, the rigidity of the hydraulic Spring on which the piston is supported, the larger, the larger the diameter of the piston is chosen. This also has the advantage that the stroke losses of Remove the piston with increasing diameter.
- the first embodiment shown in Figure 1 shows a use of the valve according to the invention a fuel injection valve 1 for internal combustion engines of motor vehicles.
- the fuel injection valve 1 is designed here as a common rail injector.
- an injection duration and an injection quantity over force relationships in the Fuel injection valve 1 becomes a valve member 2 controlled a piezoelectric actuator 3, which on the Combustion chamber side of the valve member 2 in one Piezo chamber 4 is arranged.
- the piston-shaped valve member 2 is axially displaceable in a bore 5 of a valve body designed as a longitudinal bore 6 arranged and has on its combustion chamber side End a spherical, forming a valve closing member Valve head 7 on.
- the valve head 7 acts with one on the Valve body 6 formed seat 8 together, in the lifted State of the valve head 7 a connection to one Spring chamber 9 with a restoring force on the outside opening valve head 7 exerting spring 10 is produced.
- An outlet throttle is connected to the spring chamber 9 on the combustion chamber side 11 leading to a valve control chamber 12, in which an injection line only indicated symbolically in FIG. 1 13 flows, which in turn from one for all Fuel injectors common high pressure storage space (Common Rail) 14 leads away.
- the high-pressure storage space 14 thereby in a known manner from a high-pressure fuel delivery pump with high pressure fuel from a storage tank filled.
- the piezoelectric actuator 3 is made of several layers built and points on its combustion chamber facing side an actuator head 15 and on its combustion chamber facing away Page up an actuator foot 16.
- On the actuator head 15 is a Adjusted piston 17 attached, which from the piezo chamber 4 by a support 18 for the actuator head 15 on the combustion chamber side Wall of the piezo chamber 4 in the longitudinal bore 5 enough in which the valve member 2 is mounted. It is the piezo chamber 4 in the area of the actuating piston 17 opposite the longitudinal bore 5 sealed with a sealing device 19.
- the actuator base 16 is fixed with a further piston 20 connected, which dips into a hydraulic chamber 21, which on the side of the piezoelectric element facing away from the valve member 2 Actuator 3 in the installed position of the fuel injector 1 is arranged above the piezo chamber 4. It is the piezo chamber 4 via a further sealing device 22 in the Area of the piston 20 leading into the hydraulic chamber 21 sealed against this.
- the substantially closed hydraulic chamber 21 is with the pressure medium contained in it, which consists of a Low pressure source with a compared to the pressure level of the High pressure storage space 14 is supplied relaxed pressure designed as a hydraulic spring, which has a the valve body 6 formed hydraulic line 23 with the the valve member 2 containing longitudinal bore 5 is connected.
- the hydraulic spring has a dual 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 works here in the manner described below.
- the preload of the piezoelectric actuator 3 on the diameter of the piston 20 can be set, the largest possible piston diameter is advantageous.
- a piston diameter of 14 mm is sufficient to a preload of 1000 N at a system pressure of 65 bar to achieve.
- the specialist can do this deviating values selected for the individual case can be selected.
- the piston 20 penetrates into the compensation volume with an increase in temperature the hydraulic chamber 21 or pulls when the temperature drops, it returns without the effects to the closing and opening position of the valve member 2 and the fuel valve 1 in total.
- the piezoelectric actuator 3 When an injection by the fuel injection valve 1 is to take place, the piezoelectric actuator 3 is energized, whereby this suddenly increases its axial extent. With such a rapid actuation of the piezoelectric Actuator 3 is based on the support 18th and with the piston 20 projecting into the hydraulic chamber 21 the hydraulic spring, consequently hydraulic medium from the hydraulic chamber 21 via the hydraulic line 23 in the longitudinal bore 5 of the valve member 2 is shifted, whereby the valve head 7 of the valve member 2 of his Seat 8 lifts off into an open position.
- the increased rigidity due to a relatively large dimension Diameter of the piston 20 positive.
- FIG. 2 is a second embodiment of the fuel injector 1 shown in the components that have the same function for reasons of clarity with the reference numerals used in Figure 1 are.
- the fuel injection valve 1 shown here that the volume of the interacting with the piezoelectric actuator 3 Hydraulic chamber 21 is externally changeable.
- a schematically illustrated screw in a bore 25 is provided, which is positioned such that the set screw 24 in the hydraulic chamber if necessary 21 can be screwed in so that the compensation volume depending on the change in the position of the adjusting screw 24 reduced or is enlarged.
- the Stiffness of the compensation volume is inversely proportional to volume.
- the adjusting screw 24 thus enables an external readjustment of the injection quantity by correction of the compensation volume in the hydraulic chamber 21.
- the sealing device 22 also here the function, the piezoelectric actuator 3 in front of one any water contained in the hydraulic medium and harmful particles such as To protect chips.
- the hydraulic line 23 opens here into the annular chamber 26, which communicates with the hydraulic chamber 21 via an annular gap 27 connected is.
- a filling surface 28 molded.
Abstract
Description
Die Erfindung geht von einem Ventil zum Steuern von Flüssigkeiten gemäß der Gattung des Patentanspruchs 1 aus. Aus der EP 0 477 400 A1 ist ein derartiges Ventil, welches über einen piezoelektrischen Aktor betätigbar ist, bereits bekannt. Dieses bekannte Ventil weist eine Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für einen Wegtransformator des piezoelektrischen Aktors auf, bei der die Auslenkung des piezoelektrischen Aktors über eine Hydraulikkammer übertragen wird.The invention relates to a valve for controlling liquids according to the preamble of claim 1. From the EP 0 477 400 A1 is a valve of this type, which via a piezoelectric actuator is actuated, already known. This known valve has an arrangement for one adaptive mechanical tolerance compensation acting in the stroke direction for a path transformer of the piezoelectric Actuator on 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 Betätigungskolben des Ventilgliedes, das in seiner Ruhelage mittels einer oder mehrerer Federn relativ zu einer vorgegebenen Position gehalten ist, einen um das Übersetzungsverhältnis des Kolbendurchmessers vergrößerten Hub macht, wenn der größere Kolben durch den piezoelektrischen Aktor um eine bestimmte Wegstrecke bewegt wird. Das Ventilglied, die Kolben und der piezoelektrische Aktor liegen dabei auf einer gemeinsamen Achse hintereinander.The hydraulic chamber, which is called a hydraulic Translation works, closes between two bounding it Pistons, one of which is a piston with a smaller diameter is formed and with a valve member to be controlled is connected and the other piston with a larger one Diameter is formed and with the piezoelectric Actuator is connected, a common compensation volume. The hydraulic chamber is between the two pistons clamped that the actuating piston of the valve member, in its rest position using one or more springs is held relative to a predetermined position, a increased by the ratio of the piston diameter Stroke makes when the larger piston by the piezoelectric Actuator is moved 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.Tolerances can be set via the compensation volume of the hydraulic chamber due to temperature gradients in the component or different coefficients of thermal expansion of the used materials and any setting effects compensated without changing the position of the valve element to be controlled occurs.
Ein Ausgleich von Längenänderungen des piezoelektrischen Aktors, des Ventilgliedes oder des Ventilgehäuses durch die zwischen zwei Kolben angeordnete Hydraulikkammer erfordert jedoch eine aufwendige Konstruktion und ist hinsichtlich der auftretenden Leckageverluste und der Wiederbefüllung der Hydraulikkammer problematisch.Compensating for changes in length of the piezoelectric Actuator, the valve member or the valve housing through the Hydraulic chamber arranged between two pistons requires however, a complex construction and is in terms of Leakage losses that occur and the refilling of the Hydraulic chamber problematic.
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 lösen, 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 made up of several thin layers, to achieve the largest possible stroke. So that this Layers when the piezoelectric actuator is energized the piezoelectric actuator must not separate be biased, the force to be applied can be approximately 1000 N.
In der Praxis werden zur Vorspannung des piezoelektrischen Aktors entweder Tellerfedern oder Bandfedern eingesetzt. Nachteilig ist dabei, daß die zur Vorspannung benötigten Federn einen aufwendigen Aufbau bedingen und einen großen Bauraum benötigen, wobei letzteres zu einem entsprechend großen Durchmesser des gesamten Ventils führt, wodurch die Einbaumöglichkeiten 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, are used to bias the piezoelectric Actuator used either disc springs or band springs. The disadvantage here is that those required for pretensioning Springs require a complex structure and a large one Require installation space, the latter to a corresponding large diameter of the entire valve, which leads to the Installation options for the valve are limited. Furthermore has the use of springs as the biasing elements Disadvantage that this grating over the duration of their use cause.
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 a valve for Control of liquids by creating the preload of a piezoelectric actuator and tolerance compensation with little space requirement with a simple construction is realized with as few components as possible.
Das erfindungsgemäße 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 Längungstoleranzen realisiert ist.The valve according to the invention for controlling liquids with the characterizing features of claim 1 the advantage that with the trained as a hydraulic spring Hydraulic chamber is also a biasing element for the piezoelectric actuator and a compensation element for in particular Temperature-related elongation tolerances realized is.
Bei dem erfindungsgemäßen 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.With the hydraulic prestressing element according to the invention Integrated tolerance compensation for the piezoelectric The preload is hydraulic and with low actuator Space requirements shown, with the omission of springs or other mechanical biasing elements a desired slim design of the entire valve is possible.
Durch die Verringerung der erforderlichen Bauteile zur Darstellung eines Vorspannelementes und eines Toleranzausgleichselementes, welches erfindungsgemäß in das Vorspannelement integriert ist, können die Herstellungskosten und der Montageaufwand deutlich reduziert werden. By reducing the components required for display a prestressing element and a tolerance compensation element, which according to the invention in the biasing element is integrated, the manufacturing costs and the assembly effort can be significantly reduced.
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 Querschnittsfläche des Kolbens abhängig ist, kann bei gleichem Druck die Steifigkeit der hydraulischen Feder und damit die Vorspannkraft auf den piezoelektrischen Aktor erhöht werden, wenn die Querschnittsfläche des in die Hydraulikkammer eintauchenden Kolbens entsprechend vergrößert wird. Im statischen Fall kann auch bei hoher Federrate eine nachteilige Längenänderung der Gesamteinrichtung vermieden werden, wenn der piezoelektrische Aktor, das Ventilglied oder der Ventilkörper seine Länge z.B. bei Erwärmung ändert. Zum anderen ist bei einer dynamischen Betätigung die Steifigkeit der hydraulischen Feder, an der sich der Kolben abstützt, um so größer, je größer der Durchmesser des Kolbens gewählt wird. Dabei ergibt sich zudem der Vorteil, daß die Hubverluste des Kolbens mit zunehmendem Durchmesser abnehmen.An important advantage of the invention is furthermore in that by dimensioning the hydraulic chamber, the hydraulic spring and the piston immersed in it Overall system rigidity can be increased. Since the Rigidity of the hydraulic spring from the cross-sectional area of the piston is dependent on the same pressure Rigidity of the hydraulic spring and thus the preload be increased to the piezoelectric actuator if the cross-sectional area of the immersed in the hydraulic chamber Piston is increased accordingly. In static A disadvantageous change in length can also occur with a high spring rate of the entire facility can be avoided if the piezoelectric actuator, the valve member or the valve body its length e.g. changes when heated. Second is in the case of dynamic actuation, the rigidity of the hydraulic Spring on which the piston is supported, the larger, the larger the diameter of the piston is chosen. This also has the advantage that the stroke losses of Remove the piston 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 object the invention are the description, the drawing and the patent claims.
Zwei Ausführungsbeispiele des erfindungsgemäßen Ventils zur
Steuerung von Flüssigkeiten sind in der Zeichnung dargestellt
und werden in der folgenden Beschreibung näher erläutert.
Es zeigen
Das in der Figur 1 dargestellte erste Ausführungsbeispiel zeigt eine Verwendung des erfindungsgemäßen Ventils bei einem Kraftstoffeinspritzventil 1 für Brennkraftmaschinen von Kraftfahrzeugen. Das Kraftstoffeinspritzventil 1 ist vorliegend als ein Common-Rail-Injektor ausgebildet.The first embodiment shown in Figure 1 shows a use of the valve according to the invention a fuel injection valve 1 for internal combustion engines of motor vehicles. The fuel injection valve 1 is designed here 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.For setting an injection start, an injection duration
and an injection quantity over force relationships in the
Fuel injection valve 1 becomes a
Das kolbenförmige Ventilglied 2 ist axial verschiebbar in
einer als Längsbohrung ausgeführten Bohrung 5 eines Ventilkörpers
6 angeordnet und weist an seinem brennraumseitigen
Ende einen kugelartigen, ein Ventilschließglied bildenden
Ventilkopf 7 auf. Der Ventilkopf 7 wirkt mit einem an dem
Ventilkörper 6 ausgebildeten Sitz 8 zusammen, wobei in abgehobenem
Zustand des Ventilkopfes 7 eine Verbindung zu einem
Federraum 9 mit einer eine Rückstellkraft auf den nach außen
öffnenden Ventilkopf 7 ausübenden Feder 10 hergestellt wird.
An den Federraum 9 schließt sich brennraumseitig eine Ablaufdrossel
11 an, die zu einem Ventilsteuerraum 12 führt,
in welchen eine in Figur 1 nur symbolisch angedeutete Einspritzleitung
13 mündet, die ihrerseits von einem für alle
Kraftstoffeinspritzventile gemeinsamen Hochdruckspeicherraum
(Common-Rail) 14 abführt. Der Hochdruckspeicherraum 14 wird
dabei in bekannter Weise von einer Kraftstoffhochdruckförderpumpe
mit Kraftstoff hohen Druckes aus einem Vorratstank
befüllt.The piston-
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 brennraumseitigen
Wand der Piezokammer 4 in die Längsbohrung 5
reicht, in welcher das Ventilglied 2 gelagert ist. Dabei ist
die Piezokammer 4 im Bereich des Stellkolbens 17 gegenüber
der Längsbohrung 5 mit einer Dichteinrichtung 19 abgedichtet.
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 führenden Kolbens 20
gegenüber dieser abgedichtet.The
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 Ventilkörper 6 ausgebildete Hydraulikleitung 23 mit der
das Ventilglied 2 enthaltenden Längsbohrung 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. The substantially closed
Das Kraftstoffeinspritzventil 1 nach Figur 1 arbeitet dabei in nachfolgend beschriebener Weise.The fuel injection valve 1 according to FIG. 1 works here 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 Längsbohrung 5 gelangen kann. Aufgrund
eines leicht erhöhten Systemdrucks in der Hydraulikkammer 21
von annähernd 65 bar in der vorliegenden Ausführung wird der
piezoelektrische Aktor 3 zwischen der Hydraulikfeder und dem
brennraumseitigen Auflager 18 eingespannt.When the fuel injection valve 1 is closed,
i.e. when the
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 Ausführungsbeispiel
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.As the spring rate of the hydraulic spring increases with increasing
Diameter of the piston projecting into the
Im Falle einer langsamen Betätigung, wie sie bei einer temperaturbedingten
Längenänderung des piezoelektrischen Aktors
3 oder weiterer Ventilbauteile wie z.B. des Ventilglieds 2
oder des Ventilgehäuses bzw. Ventilkörpers 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 Auswirkungen
auf die Schließ- und Öffnungsstellung des Ventilgliedes
2 und des Kraftstoffventils 1 insgesamt hat.In the case of a slow actuation, as in a temperature-related
Change in length of the
Wenn eine Einspritzung durch das Kraftstoffeinspritzventil 1
erfolgen soll, wird der piezoelektrische Aktor 3 bestromt,
wodurch dieser seine axiale Ausdehnung schlagartig vergrößert.
Bei einer derartigen schnellen Betätigung des piezoelektrischen
Aktors 3 stützt sich dieser 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 Längsbohrung 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 by the fuel injection valve 1
is to take place, the
Bezug nehmend auf Figur 2 ist ein zweites Ausführungsbeispiel
des Kraftstoffeinspritzventils 1 dargestellt, bei der
aus Gründen der Übersichtlichkeit funktionsgleiche Bauteile
mit den in Figur 1 verwendeten Bezugszeichen bezeichnet
sind. Gegenüber der Ausführung nach Figur 1 unterscheidet
sich das hier gezeigte Kraftstoffeinspritzventil 1 darin,
daß das Volumen der mit dem piezoelektrischen Aktor 3 zusammenwirkenden
Hydraulikkammer 21 von extern veränderbar ist.Referring to Figure 2 is a second embodiment
of the fuel injector 1 shown in the
components that have the same function for reasons of clarity
with the reference numerals used in Figure 1
are. Compared to the embodiment according to FIG. 1
the fuel injection valve 1 shown here
that the volume of the interacting with the
Hierzu ist als Justiereinrichtung 24 im vorliegenden Ausführungsbeispiel
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 Öffnungsverhalten 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.This is done as an
Des weiteren ist bei der Ausführung nach Figur 2 die Dichteinrichtung
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
Ausführung 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. Spänen zu schützen.Furthermore, in the embodiment according to FIG. 2, the
Die Hydraulikleitung 23 mündet hier in die Ringkammer 26,
welche über einen Ringspalt 27 mit der Hydraulikkammer 21
verbunden ist. Zur Verbesserung des Befüllverhaltens ist im
Bereich des Ringspalts 27 an dem Kolben 20 eine Befüllfläche
28 ausgeformt.The
In beiden beschriebenen Ausführungen ist das Hydraulikmedium
zur Befüllung der Hydraulikkammer 21 der Kraftstoff, welcher
auch in einen Brennraum einer Brennkraftmaschine eingespritzt
wird.In both versions described, the hydraulic medium
for filling the
Bei einer geeigneten Trennung zwischen der Kraftstoffzuführung
und der Abführung des an dem Sitz 8 des Ventilkopfes 7
austretenden Hydraulikmediums sowie einer Nachführung von
Leckageverlusten ist es auch möglich, separates Öl wie z.B.
Motoröl als Hydraulikmedium einzusetzen.With a suitable separation between the fuel supply
and the removal of the on the
Claims (10)
- Valve for controlling liquids, having a valve element (2), which can be moved axially in a bore (5) in a valve body (6) and at one end has a valve head (7) which forms a valve closing element and interacts with a seat (8), which is provided on the valve body (6), in order to open and close the valve (1), and having a piezoelectric actuator (3) for operation of the valve element (2), with a prestressing element (21) being provided for the piezoelectric actuator (3) and a tolerance compensation element (21) being provided in order to compensate for length tolerances of the piezoelectric actuator (3) and/or of further valve components (2, 6), characterized in that a hydraulic chamber (21) is provided on one side of the piezoelectric actuator (3), facing away from the valve element (2), is connected via at least one hydraulic line (23) to the bore (5), which is sealed with respect to the piezoelectric actuator (3), in the valve element (2) and can enter the piston (20) which is connected to the piezoelectric actuator (3), with the hydraulic chamber (21) being in the form of a hydraulic spring, whose spring force on the piston (20) which is connected to the piezoelectric actuator (3) represents the prestressing element and the tolerance compensation element.
- Valve according to Claim 1, characterized in that the piezoelectric actuator (3) is clamped in 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 bearing surface (18) on one side, facing away from the hydraulic chamber (21), of a piezo chamber (4) which holds the piezoelectric actuator (3).
- Valve according to Claim 1 or 2, characterized in that the piezoelectric actuator (3) has an actuating piston (17) which is attached to an actuator head (15) and extends into the bore (5) which is sealed with respect to the piezoelectric actuator (3) and holds the valve element (2).
- Valve according to Claim 2 or 3, characterized in that the hydraulic chamber (21) is sealed with respect to the piezoelectric actuator (3) in the area of the piston (20) by means of a sealing device (22), which is arranged in an annular gap (27) between the hydraulic chamber (21) and the piezo chamber (4).
- Valve according to Claim 2 or 3, characterized in that the hydraulic chamber (21) is sealed with respect to the piezoelectric actuator (3) by means of a sealing device (22) which is arranged in the area of the piezo chamber (4) and separates an annular chamber (26) with the same diameter as the piezo chamber (4) from this, with the hydraulic line (23) opening into the annular chamber (26), which is connected via an annular gap (27) to the hydraulic chamber (21).
- Valve according to Claim 5, characterized in that a filling surface (28) is formed on the piston (20) in the area of the annular gap (27).
- Valve according to one of Claims 1 to 6, characterized in that the volume of the hydraulic chamber (21) can be varied by means of an adjusting device (24), which can be controlled externally.
- Valve according to Claim 7, characterized in that the adjusting device is in the form of an adjusting screw (24) which can be screwed into the hydraulic medium in the hydraulic chamber (21) such that it is immersed.
- Valve according to one of Claims 1 to 8,
characterized by the valve being used as a component of a fuel injection valve for internal combustion engines, in particular for a common rail injector (1). - Valve according to Claim 9, characterized in that the hydraulic medium for filling the hydraulic chamber (21) is fuel.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19946840A DE19946840A1 (en) | 1999-09-30 | 1999-09-30 | Valve for controlling liquids |
| DE19946840 | 1999-09-30 | ||
| PCT/DE2000/003200 WO2001023744A1 (en) | 1999-09-30 | 2000-09-14 | Valve for controlling liquids |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1135594A1 EP1135594A1 (en) | 2001-09-26 |
| EP1135594B1 true EP1135594B1 (en) | 2004-12-01 |
Family
ID=7923821
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP00974319A Expired - Lifetime EP1135594B1 (en) | 1999-09-30 | 2000-09-14 | Valve for controlling liquids |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US6502803B1 (en) |
| EP (1) | EP1135594B1 (en) |
| JP (1) | JP2003510507A (en) |
| KR (1) | KR20010101060A (en) |
| AT (1) | ATE283973T1 (en) |
| CZ (1) | CZ20011881A3 (en) |
| DE (2) | DE19946840A1 (en) |
| WO (1) | WO2001023744A1 (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19946869A1 (en) * | 1999-09-30 | 2001-04-05 | Bosch Gmbh Robert | Fuel injector |
| DE10003863B4 (en) * | 2000-01-28 | 2004-11-18 | Robert Bosch Gmbh | injection |
| US6789965B2 (en) * | 2002-05-31 | 2004-09-14 | Agilent Technologies, Inc. | Dot printer with off-axis loading |
| DE10254985A1 (en) * | 2002-11-26 | 2004-06-03 | Robert Bosch Gmbh | Valve for controlling liquids with a nozzle and a control module |
| DE10326259A1 (en) * | 2003-06-11 | 2005-01-05 | Robert Bosch Gmbh | Injector for fuel injection systems of internal combustion engines, in particular direct injection diesel engines |
| DE102004002299A1 (en) * | 2004-01-16 | 2005-08-04 | Robert Bosch Gmbh | Fuel injector with directly controlled injection valve member |
| DE102007002758A1 (en) * | 2006-04-04 | 2007-10-11 | Robert Bosch Gmbh | fuel injector |
| KR20100053536A (en) | 2007-06-29 | 2010-05-20 | 아트피셜 머슬, 인코퍼레이션 | Electroactive polymer transducers for sensory feedback applications |
| US20090250021A1 (en) * | 2007-10-02 | 2009-10-08 | Artificial Muscle, Inc. | Fluid control systems employing compliant electroactive materials |
| EP2239793A1 (en) | 2009-04-11 | 2010-10-13 | Bayer MaterialScience AG | Electrically switchable polymer film structure and use thereof |
| US8500036B2 (en) | 2010-05-07 | 2013-08-06 | Caterpillar Inc. | Hydraulically amplified mechanical coupling |
| CA2828809A1 (en) | 2011-03-01 | 2012-09-07 | Francois EGRON | Automated manufacturing processes for producing deformable polymer devices and films |
| JP2014517331A (en) | 2011-03-22 | 2014-07-17 | バイエル・インテレクチュアル・プロパティ・ゲゼルシャフト・ミット・ベシュレンクテル・ハフツング | Electric field responsive polymer actuator lenticular system |
| JP2012202251A (en) * | 2011-03-24 | 2012-10-22 | Denso Corp | Injector |
| EP2828901B1 (en) | 2012-03-21 | 2017-01-04 | Parker Hannifin Corporation | Roll-to-roll manufacturing processes for producing self-healing electroactive polymer devices |
| WO2013192143A1 (en) | 2012-06-18 | 2013-12-27 | Bayer Intellectual Property Gmbh | Stretch frame for stretching process |
| US9590193B2 (en) | 2012-10-24 | 2017-03-07 | Parker-Hannifin Corporation | Polymer diode |
| US10281055B2 (en) * | 2016-02-09 | 2019-05-07 | Parker-Hannifin Corporation | Hydraulic servo valve |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4529164A (en) * | 1982-03-05 | 1985-07-16 | Nippon Soken, Inc. | Piezo-type valve |
| DE3237258C1 (en) * | 1982-10-08 | 1983-12-22 | Daimler-Benz Ag, 7000 Stuttgart | Electrically pilot operated valve arrangement |
| DE3533085A1 (en) * | 1985-09-17 | 1987-03-26 | Bosch Gmbh Robert | METERING VALVE FOR DOSING LIQUIDS OR GASES |
| DE3713697A1 (en) * | 1987-04-24 | 1988-11-10 | Licentia Gmbh | Ultra-fast control valve |
| US4907748A (en) * | 1988-08-12 | 1990-03-13 | Ford Motor Company | Fuel injector with silicon nozzle |
| US5092360A (en) * | 1989-11-14 | 1992-03-03 | Hitachi Metals, Ltd. | Flow rated control valve using a high-temperature stacked-type displacement device |
| EP0477400B1 (en) * | 1990-09-25 | 2000-04-26 | Siemens Aktiengesellschaft | Device for compensating the tolerance in the lift direction of the displacement transformer of a piezoelectric actuator |
| US5779149A (en) * | 1996-07-02 | 1998-07-14 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
| DE19702066C2 (en) * | 1997-01-22 | 1998-10-29 | Daimler Benz Ag | Piezoelectric injector for fuel injection systems of internal combustion engines |
| DE19727992C2 (en) * | 1997-07-01 | 1999-05-20 | Siemens Ag | Compensation element for compensation of temperature-related changes in length of electromechanical control systems |
-
1999
- 1999-09-30 DE DE19946840A patent/DE19946840A1/en not_active Ceased
-
2000
- 2000-09-14 DE DE50008830T patent/DE50008830D1/en not_active Expired - Lifetime
- 2000-09-14 JP JP2001527102A patent/JP2003510507A/en active Pending
- 2000-09-14 CZ CZ20011881A patent/CZ20011881A3/en unknown
- 2000-09-14 US US09/856,837 patent/US6502803B1/en not_active Expired - Fee Related
- 2000-09-14 KR KR1020017006491A patent/KR20010101060A/en not_active Application Discontinuation
- 2000-09-14 WO PCT/DE2000/003200 patent/WO2001023744A1/en not_active Application Discontinuation
- 2000-09-14 EP EP00974319A patent/EP1135594B1/en not_active Expired - Lifetime
- 2000-09-14 AT AT00974319T patent/ATE283973T1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| ATE283973T1 (en) | 2004-12-15 |
| US6502803B1 (en) | 2003-01-07 |
| CZ20011881A3 (en) | 2002-04-17 |
| JP2003510507A (en) | 2003-03-18 |
| DE50008830D1 (en) | 2005-01-05 |
| WO2001023744A1 (en) | 2001-04-05 |
| KR20010101060A (en) | 2001-11-14 |
| DE19946840A1 (en) | 2001-05-03 |
| EP1135594A1 (en) | 2001-09-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP1135594B1 (en) | Valve for controlling liquids | |
| DE19946828C1 (en) | Valve for controlling liquids | |
| EP1714025B1 (en) | Fuel injector with a direct controlled injection valve member | |
| EP1135595B1 (en) | Valve for controlling liquids | |
| EP1185787B1 (en) | Valve for controlling liquids | |
| DE10139857A1 (en) | Valve for controlling liquids | |
| EP0218895A1 (en) | Measure valve for determining the quantity of fluids or gases | |
| EP2310662B1 (en) | Fuel injector | |
| DE102006017034B4 (en) | Piezo actuator, method for producing a piezo actuator and injection system with such | |
| DE19946831C1 (en) | Valve for controlling liquids | |
| DE10019764B4 (en) | Length measuring device for measuring dimensions of bodies, particularly inner- and outer diameters, used in mechanical drive- and transmission elements and in circular body, has carrier element, which is adapted to body to be measured | |
| EP1276985A1 (en) | Valve for controlling liquids | |
| DE10147483B4 (en) | Valve for controlling fluids | |
| DE102009039647A1 (en) | Fuel injector, particularly common rail fuel injector, for injecting fuel into combustion chamber of internal combustion engine, has servo valve that is controlled by piezoelectric actuator | |
| DE10139871B4 (en) | Valve for controlling fluids | |
| EP1137876A1 (en) | Valve for controlling liquids | |
| WO2001081755A1 (en) | Valve for regulating fluids | |
| DE102006055555A1 (en) | Fuel injector for internal combustion engine, has actuator mounted in low pressure area in housing part or retaining body and force-balanced under formation of piston stroke directly or indirectly on valve, where actuator has support | |
| EP1916412B1 (en) | Actuator with fluid isolation | |
| WO2002020978A1 (en) | Hydraulically translated valve | |
| WO2005050001A1 (en) | Fuel-injection valve | |
| DE10032924A1 (en) | Fuel injection device for internal combustion engines | |
| EP1276983A1 (en) | Valve for controlling liquids | |
| DE102005045892A1 (en) | Directly driven fuel injector, comprises outwards opening jet needle moved by piezoelectric multi-layer device | |
| EP1165956A1 (en) | Valve for controlling liquids |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
| 17P | Request for examination filed |
Effective date: 20011005 |
|
| GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
| GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20041201 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20041201 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20041201 Ref country code: GB Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20041201 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20041201 Ref country code: IE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20041201 |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
| REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
| REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: GERMAN |
|
| REF | Corresponds to: |
Ref document number: 50008830 Country of ref document: DE Date of ref document: 20050105 Kind code of ref document: P |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20050301 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20050301 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20050301 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20050312 |
|
| NLV1 | Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act | ||
| GBV | Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed] |
Effective date: 20041201 |
|
| REG | Reference to a national code |
Ref country code: IE Ref legal event code: FD4D |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050914 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20050914 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050930 Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050930 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050930 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050930 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050930 |
|
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed |
Effective date: 20050902 |
|
| EN | Fr: translation not filed | ||
| REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
| BERE | Be: lapsed |
Owner name: ROBERT *BOSCH G.M.B.H. Effective date: 20050930 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050501 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20161125 Year of fee payment: 17 |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50008830 Country of ref document: DE |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180404 |