EP0947690B1 - Fluid control valve - Google Patents

Fluid control valve Download PDF

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Publication number
EP0947690B1
EP0947690B1 EP98123744A EP98123744A EP0947690B1 EP 0947690 B1 EP0947690 B1 EP 0947690B1 EP 98123744 A EP98123744 A EP 98123744A EP 98123744 A EP98123744 A EP 98123744A EP 0947690 B1 EP0947690 B1 EP 0947690B1
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EP
European Patent Office
Prior art keywords
valve
pressure
piston
control
pressure 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
Application number
EP98123744A
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German (de)
French (fr)
Other versions
EP0947690A3 (en
EP0947690A2 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0947690A2 publication Critical patent/EP0947690A2/en
Publication of EP0947690A3 publication Critical patent/EP0947690A3/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
    • 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
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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 preamble of claim 1.
  • a valve for controlling liquids according to the preamble of claim 1.
  • Actuating piston of the valve member in one in diameter smaller part of a stepped bore is arranged so that it can be moved, whereas a piston with a larger diameter, with the piezo actuator is moved in a larger diameter Part of the stepped bore is arranged.
  • a piston with a larger diameter, with the piezo actuator is moved in a larger diameter Part of the stepped bore is arranged.
  • Between the two A hydraulic space is clamped in the piston, such that when the larger piston through the actuator by a certain Distance is moved, the actuating piston of the valve member one around the gear ratio of the stepped bore diameter enlarged stroke makes.
  • the piston and the piezo actuator lie on a common axis behind each other.
  • the valve according to the invention with the characteristic features of claim 1 has the advantage that the pressure chamber does not lose any liquid.
  • A is disadvantageous change in length of the entire device avoided, even if the piezo actuator, the valve or the housing its length changes, for example, when heated.
  • the facility has a simple structure, and it a safe and reliable seal is created.
  • the valve according to the invention is used in a Fuel injection valve, which in the main in Section is shown in Figure 1.
  • This injector has a valve housing 1, in which in a longitudinal bore 2 a valve needle 3 is guided. On her one The end is the valve needle with a conical sealing surface 4 provided at the tip 5 projecting into the combustion chamber of the valve housing cooperates with a seat from which Discharge injection openings that lead into the interior of the injection valve, here the valve needle 3 surrounding, below Injection standing fuel filled annular space 7 and connect it to the combustion chamber to create one To perform injection when the valve needle of her Has lifted the seat.
  • the annulus is with another Pressure chamber 8 connected, which is constantly in connection with a Pressure line 10 is through which the fuel injector from a high-pressure fuel reservoir not shown Fuel is supplied under injection pressure.
  • This high fuel pressure also acts in the pressure chamber 8 and there on a pressure shoulder 11, over which in known Way the valve needle in suitable conditions of their Valve seat can be lifted off.
  • valve needle At the other end of the valve needle is in a cylinder bore 12 out there and closes with its end face 14 a control pressure chamber 15, which via a throttle connection 16 is permanently connected to an annular space 17 which, like the pressure chamber 8, continuously with the high-pressure fuel accumulator communicates.
  • Axial leads from the control pressure chamber 15 a throttle bore 19 from to a valve seat 20 of a control valve 21.
  • the valve seat 20 acts Valve member 22 of the control valve 21 together, which is in the off State a connection between the control pressure chamber 15 and a spring chamber 18, which in turn constantly is connected to a relief room.
  • valve member 22 loading in the closing direction Compression spring 23 arranged, the valve member 22 on the Valve seat 20 acted out so that in the normal position of the Control valve 21 this connection of the control pressure chamber 15th is closed. Because the face of the valve needle 3 in the area of the control pressure chamber 15 is greater than that Surface of the pressure shoulder 11 holds the same fuel pressure in the control pressure chamber, which also prevails in the pressure chamber 8, now the valve needle 3 in the closed position. If the valve member 22 is lifted off, however, the pressure in the control pressure chamber decoupled via the throttle connection 16 15 relieved. With the now missing closing force opens the valve needle 3 quickly and on the other hand can be in the closed position be brought as soon as the valve member 22 again comes into the closed position. From that point on, it builds up then quickly over the throttle 16 of the original high Fuel pressure in the control pressure chamber 15 again.
  • the valve according to the invention has as an actuator a piezo actuator 24, which has a hydraulic Translator 25 with a hydraulic pressure chamber 26 engages on a shaft 27 of the valve member 22.
  • the Pressure chamber 26 is on the one hand by a piston 28 of the piezo actuator 24 limited, on the other hand it has a piston 29 as movable wall that communicates with the valve member shaft 27 stands.
  • control chamber 32 and 33 Seen from the pressure chamber 26 on the back 30 or 31 of each piston 28 and 29 form a control chamber 32 and 33, the actuator or valve side of a membrane 34 or 35 is tightly closed.
  • the pressure chamber 26 is in the Work of the injector under high pressure, which over the Piston guides of the two pistons 28 and 29 a small Leakage oil flow in the control rooms 32 and 33 causes. Thereby these control rooms 32 and 33 are filled with leak oil, which but the pressure chamber 26 must be returned to the hydraulic translator 25 to keep constant length.
  • each control room 32 or 33 there is one at its other Throttle bore 36 or 37 closed with a ball connected.
  • the throttle bores 36 and 37 have over a drain hole 40 connection to a not shown Low pressure source.
  • Each throttle bore 36 or 37 is in Relief direction with a sharp-edged transition 38 and provided with a rounded transition 39 in the filling direction. This measure ensures that a liquid flow, the entrance on the sharp-edged transition 38 hits, is throttled more than a liquid flow, the return flow over the rounded transition 39 flows, which means that a drain from the control rooms 32nd and 33 is more hampered than refilling the Pressure chamber 26 serving inflow.
  • the piezo actuator stroke is smaller, it generates depending on the larger the valve lift.
  • FIG. 5 shows an initial one using a pressure curve 41 great pressure in the control room 32, the one with the piezo stroke begins and then drops with the movement of the valve piston 29. If the piezo is switched off and thus enables one Return stroke, a pressure drop occurs at 42 until the Valve piston followed the piezo. About this pressure change the control chamber 32 is refilled.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Ventil zum Steuern von Flüssigkeiten gemäß der Gattung des Patentanspruches 1. Durch die EP 0 477 400 A1 ist ein solches Ventil bekannt, Dort ist der Betätigungskolben des Ventilgliedes in einem im Durchmesser kleineren Teil einer Stufenbohrung dicht verschiebbar angeordnet, wogegen ein im Durchmesser größerer Kolben, der mit dem Piezoaktor bewegt wird, in einem im Durchmesser größeren Teil der Stufenbohrung angeordnet ist. Zwischen den beiden Kolben ist ein hydraulischer Raum eingespannt, derart, daß, wenn der größere Kolben durch den Aktor um eine bestimmte Wegstrecke bewegt wird, der Betätigungskolben des Ventilgliedes einen um das Übersetzungsverhältnis des Stufenbohrungsdurchmesser vergrößerten Hub macht. Das Ventilglied, der Betätigungskolben, der im Durchmesser größere Kolben und der Piezoaktor liegen auf einer gemeinsamen Achse hintereinander.The invention relates to a valve for controlling liquids according to the preamble of claim 1. By the Such a valve is known from EP 0 477 400 A1 Actuating piston of the valve member in one in diameter smaller part of a stepped bore is arranged so that it can be moved, whereas a piston with a larger diameter, with the piezo actuator is moved in a larger diameter Part of the stepped bore is arranged. Between the two A hydraulic space is clamped in the piston, such that when the larger piston through the actuator by a certain Distance is moved, the actuating piston of the valve member one around the gear ratio of the stepped bore diameter enlarged stroke makes. The valve member, the actuating piston, the larger in diameter The piston and the piezo actuator lie on a common axis behind each other.

Bei solchen Ventilen besteht das Problem, Längenänderungen des Piezoaktors, des Ventils oder des Ventilgehäuses durch den hydraulischen Kopplungsraum, der im folgenden kurz Druckraum genannt wird, auszugleichen. Da der Piezoaktor zum Öffnen des Ventils im Druckraum einen Druck erzeugt, führt dieser Druck auch zu einem Verlust an Druckraum-Flüssigkeit. Um ein Leerpumpen des Druckraumes zu verhindern, ist eine Wiederbefüllung notwendig. Einrichtungen, die dieses Problem lösen, sind zwar bereits bekannt, dabei ist aber weder ein Ventil zur Überwachung der Nachfüllung vorgesehen, noch ist ausgesagt, ob das Vorratsmittel nachlieferbar ist.The problem with such valves is length changes of the piezo actuator, the valve or the valve housing the hydraulic coupling space, briefly below Pressure room is called to balance. Since the piezo actuator for Opening the valve in the pressure chamber creates a pressure, leads this pressure also leads to a loss of pressure chamber fluid. To prevent the pressure chamber from being emptied, one is Refill necessary. Bodies that have this problem solve, are already known, but there is neither Valve for monitoring the refill is still provided stated whether the inventory can be replenished.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Ventil mit den kennzeichnenden Merkmalen des Patentanspruches 1 hat demgegenüber den Vorteil, daß der Druckraum keinen Flüssigkeitsverlust erleidet. Eine nachteilige Längenänderung der Gesamteinrichtung ist damit vermieden, auch wenn der Piezoaktor, das Ventil oder das Gehäuse seine Länge zum Beispiel bei Erwärmung ändert. Des weiteren hat die Einrichtung einen einfachen Aufbau, und es ist eine sichere und zuverlässige Abdichtung geschaffen.The valve according to the invention with the characteristic features of claim 1 has the advantage that the pressure chamber does not lose any liquid. A is disadvantageous change in length of the entire device avoided, even if the piezo actuator, the valve or the housing its length changes, for example, when heated. Of further, the facility has a simple structure, and it a safe and reliable seal is created.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen

  • Figur 1 ein Kraftstoffeinspritzventil im Schnitt,
  • Figur 2 ein Ausführungsbeispiel eines hydraulischen Druckübersetzers mit Flüssigkeitsnachspeiseventil,
  • Figur 3 eine Einzelheit aus Figur 2 in vergrößertem Maßstab,
  • Figur 4 ein Diagramm der Hübe über der Zeit und
  • Figuren 5 bis 7 drei Diagramme über die Druckverläufe.
    • An embodiment of the invention is shown in the drawing and explained in more detail in the following description. Show it
  • FIG. 1 shows a fuel injector in section,
  • FIG. 2 shows an exemplary embodiment of a hydraulic pressure intensifier with a liquid make-up valve,
  • FIG. 3 shows a detail from FIG. 2 on an enlarged scale,
  • Figure 4 is a diagram of the strokes over time and
  • Figures 5 to 7 three diagrams of the pressure profiles.

    • Beschreibung des AusführungsbeispielsDescription of the embodiment

    Das erfindungsgemäße Ventil findet Anwendung bei einem Kraftstoffeinspritzventil, das in wesentlichen Teilen im Schnitt in der Figur 1 wiedergegeben ist. Dieses Einspritzventil weist ein Ventilgehäuse 1 auf, in dem in einer Längsbohrung 2 eine Ventilnadel 3 geführt ist. An ihrem einen Ende ist die Ventilnadel mit einer kegelförmigen Dichtfläche 4 versehen, die an der in den Brennraum ragenden Spitze 5 des Ventilgehäuses mit einem Sitz zusammenwirkt, von dem aus Einspritzöffnungen abführen, die in das Innere des Einspritzventils, hier den die Ventilnadel 3 umgebenden, unter Einspritzdruck stehendem Kraftstoff gefüllten Ringraum 7 führen und diesen mit dem Brennraum verbinden, um so eine Einspritzung zu vollziehen, wenn die Ventilnadel von ihrem Sitz abgehoben hat. Der Ringraum ist mit einem weiteren Druckraum 8 verbunden, der ständig in Verbindung mit einer Druckleitung 10 steht, über die dem Kraftstoffeinspritzventil von einem nicht weiter gezeigten Kraftstoffhochdruckspeicher Kraftstoff unter Einspritzdruck zugeführt wird. Dieser hohe Kraftstoffdruck wirkt auch in dem Druckraum 8 und dort auf eine Druckschulter 11, über die in bekannter Weise die Ventilnadel bei geeigneten Bedingungen von ihrem Ventilsitz abgehoben werden kann.The valve according to the invention is used in a Fuel injection valve, which in the main in Section is shown in Figure 1. This injector has a valve housing 1, in which in a longitudinal bore 2 a valve needle 3 is guided. On her one The end is the valve needle with a conical sealing surface 4 provided at the tip 5 projecting into the combustion chamber of the valve housing cooperates with a seat from which Discharge injection openings that lead into the interior of the injection valve, here the valve needle 3 surrounding, below Injection standing fuel filled annular space 7 and connect it to the combustion chamber to create one To perform injection when the valve needle of her Has lifted the seat. The annulus is with another Pressure chamber 8 connected, which is constantly in connection with a Pressure line 10 is through which the fuel injector from a high-pressure fuel reservoir not shown Fuel is supplied under injection pressure. This high fuel pressure also acts in the pressure chamber 8 and there on a pressure shoulder 11, over which in known Way the valve needle in suitable conditions of their Valve seat can be lifted off.

    Am anderen Ende der Ventilnadel ist diese in einer Zylinderbohrung 12 geführt und schließt dort mit ihrer Stirnseite 14 einen Steuerdruckraum 15 ein, der über eine Drosselverbindung 16 ständig mit einem Ringraum 17 verbunden ist, der, wie auch der Druckraum 8, fortwährend mit dem Kraftstoffhochdruckspeicher in Verbindung steht. Axial führt vom Steuerdruckraum 15 eine Drosselbohrung 19 ab zu einem Ventilsitz 20 eines Steuerventils 21. Mit dem Ventilsitz 20 wirkt ein Ventilglied 22 des Steuerventils 21 zusammen, das in abgehobenem Zustand eine Verbindung zwischen dem Steuerdruckraum 15 und einem Federraum 18 herstellt, der wiederum ständig mit einem Entlastungsraum verbunden ist. In dem Federraum 18 ist eine das Ventilglied 22 in Schließrichtung belastende Druckfeder 23 angeordnet, die das Ventilglied 22 auf den Ventilsitz 20 hin beaufschlagt, so daß in Normalstellung des Steuerventils 21 diese Verbindung des Steuerdruckraumes 15 verschlossen ist. Da die stirnseitige Fläche der Ventilnadel 3 im Bereich des Steuerdruckraumes 15 größer ist als die Fläche der Druckschulter 11, hält derselbe Kraftstoffdruck im Steuerdruckraum, der auch in dem Druckraum 8 vorherrscht, nun die Ventilnadel 3 in geschlossener Stellung. Ist das Ventilglied 22 jedoch abgehoben, so wird der Druck im über die Drosselverbindung 16 abgekoppelten Steuerdruckraum 15 entlastet. Bei der nun fehlenden Schließkraft öffnet die Ventilnadel 3 schnell und kann andererseits in Schließstellung gebracht werden, sobald das Ventilglied 22 wieder in Schließstellung kommt. Von diesem Zeitpunkt an baut sich dann schnell über die Drossel 16 der ursprüngliche hohe Kraftstoffdruck im Steuerdruckraum 15 wieder auf.At the other end of the valve needle is in a cylinder bore 12 out there and closes with its end face 14 a control pressure chamber 15, which via a throttle connection 16 is permanently connected to an annular space 17 which, like the pressure chamber 8, continuously with the high-pressure fuel accumulator communicates. Axial leads from the control pressure chamber 15 a throttle bore 19 from to a valve seat 20 of a control valve 21. The valve seat 20 acts Valve member 22 of the control valve 21 together, which is in the off State a connection between the control pressure chamber 15 and a spring chamber 18, which in turn constantly is connected to a relief room. In the spring chamber 18 is a valve member 22 loading in the closing direction Compression spring 23 arranged, the valve member 22 on the Valve seat 20 acted out so that in the normal position of the Control valve 21 this connection of the control pressure chamber 15th is closed. Because the face of the valve needle 3 in the area of the control pressure chamber 15 is greater than that Surface of the pressure shoulder 11 holds the same fuel pressure in the control pressure chamber, which also prevails in the pressure chamber 8, now the valve needle 3 in the closed position. If the valve member 22 is lifted off, however, the pressure in the control pressure chamber decoupled via the throttle connection 16 15 relieved. With the now missing closing force opens the valve needle 3 quickly and on the other hand can be in the closed position be brought as soon as the valve member 22 again comes into the closed position. From that point on, it builds up then quickly over the throttle 16 of the original high Fuel pressure in the control pressure chamber 15 again.

    Wie die Figur 2 erkennen läßt, hat das erfindungsgemäße Ventil als Betätiger einen Piezoaktor 24, der über einen hydraulischen Übersetzer 25 mit einem hydraulischen Druckraum 26 an einem Schaft 27 des Ventilgliedes 22 angreift. Der Druckraum 26 wird einerseits von einem Kolben 28 des Piezoaktors 24 begrenzt, andererseits hat er einen Kolben 29 als bewegliche Wand, der mit dem Ventilgliedschaft 27 in Verbindung steht.As can be seen in FIG. 2, the valve according to the invention has as an actuator a piezo actuator 24, which has a hydraulic Translator 25 with a hydraulic pressure chamber 26 engages on a shaft 27 of the valve member 22. The Pressure chamber 26 is on the one hand by a piston 28 of the piezo actuator 24 limited, on the other hand it has a piston 29 as movable wall that communicates with the valve member shaft 27 stands.

    Vom Druckraum 26 aus gesehen ist auf der Rückseite 30 bzw. 31 jedes Kolbens 28 bzw. 29 ein Steuerraum 32 bzw. 33 gebildet, der aktor- bzw. ventilseitig von einer Membran 34 bzw. 35 dicht abgeschlossen ist. Der Druckraum 26 steht bei der Arbeit des Einspritzventils unter hohem Druck, der über die Kolbenführungen der beiden Kolben 28 und 29 einen geringen Leckölstrom in die Steuerräume 32 und 33 bewirkt. Dadurch sind diese Steuerräume 32 und 33 mit Lecköl gefüllt, das aber dem Druckraum 26 wieder zugeführt werden muß, um den hydraulischen Übersetzer 25 auf konstanter Länge zu halten.Seen from the pressure chamber 26 on the back 30 or 31 of each piston 28 and 29 form a control chamber 32 and 33, the actuator or valve side of a membrane 34 or 35 is tightly closed. The pressure chamber 26 is in the Work of the injector under high pressure, which over the Piston guides of the two pistons 28 and 29 a small Leakage oil flow in the control rooms 32 and 33 causes. Thereby these control rooms 32 and 33 are filled with leak oil, which but the pressure chamber 26 must be returned to the hydraulic translator 25 to keep constant length.

    An jeden Steuerraum 32 bzw. 33 ist eine an ihrem anderen Ende mit einer Kugel verschlossene Drosselbohrung 36 bzw. 37 angeschlossen. Die Drosselbohrungen 36 und 37 haben über eine Leckölbohrung 40 Verbindung zu einer nicht dargestellten Niederdruckquelle. Jede Drosselbohrung 36 bzw. 37 ist in Entlastungsrichtung mit einem scharfkantigen Übergang 38 und in Füllrichtung mit einem gerundeten Übergang 39 versehen. Durch diese Maßnahme wird erreicht, daß ein Flüssigkeitsstrom, der eingangsseitig auf den scharfkantigen Übergang 38 trifft, stärker gedrosselt wird als ein Flüssigkeitsstrom, der im Rückfluß über den gerundeten Übergang 39 fließt, was bedeutet, daß ein Abfluß aus den Steuerräumen 32 und 33 mehr behindert wird als ein der Wiederbefüllung des Druckraumes 26 dienender Zufluß.At each control room 32 or 33 there is one at its other Throttle bore 36 or 37 closed with a ball connected. The throttle bores 36 and 37 have over a drain hole 40 connection to a not shown Low pressure source. Each throttle bore 36 or 37 is in Relief direction with a sharp-edged transition 38 and provided with a rounded transition 39 in the filling direction. This measure ensures that a liquid flow, the entrance on the sharp-edged transition 38 hits, is throttled more than a liquid flow, the return flow over the rounded transition 39 flows, which means that a drain from the control rooms 32nd and 33 is more hampered than refilling the Pressure chamber 26 serving inflow.

    Wirkungsweiseoperation

    In den beiden Steuerräumen 32 und 33 wird beim Hub der Kolben 28 und 29 über die Restflächen der Membranen 34 und 35 ein Gegendruck erzeugt. Beim Öffnen des Einspritzventils wirkt der Steuerraum 32, und beim Schließen des Einspritzventils wirkt der Steuerraum 33. Gleichzeitig werden in umgekehrter Arbeitsweise die Steuerräume 32 und 33 über die Drosselbohrungen 36 und 37 wieder befüllt. Über die lichte Weite des Drosselbohrungen 36 und 37 sowie über eine entsprechende Auslegung der scharfkantigen bzw. gerundeten Übergänge 38 und 39 kann in den Steuerräumen 32 und 33 der richtige Druck eingestellt werden, der gewährleistet, daß jeweils ein zum Wiederbefüllen des Druckraumes 26 ausreichender Mindestdruck zur Verfügung steht. Damit ist ein gleichbleibendes Volumen in dem Druckraum 26 sichergestellt, womit auch gewährleistet ist, daß beispielsweise durch Erwärmung auftretende Längeveränderungen ausgeglichen werden. Die Figuren 4 bis 7 zeigen zusammenhängende Diagramme, bei denen auf der Abzisse jeweils die Zeit aufgetragen ist. Und diese Zeitwerte sind mit gestrichelten Linien über die Gesamtdarstellung der Figuren 4 bis 7 vergleichend dargestellt.In the two control rooms 32 and 33, the piston is at the stroke 28 and 29 over the remaining surfaces of the membranes 34 and 35 creates a back pressure. When opening the injector acts the control chamber 32, and when closing the injection valve acts the control room 33. At the same time in reverse Operation of the control rooms 32 and 33 over the Throttle bores 36 and 37 refilled. About the light Width of the throttle bores 36 and 37 and a corresponding one Interpretation of the sharp-edged or rounded Transitions 38 and 39 can be in the control rooms 32 and 33 of the correct pressure is set to ensure that each sufficient to refill the pressure chamber 26 Minimum pressure is available. So that's a constant volume ensured in the pressure chamber 26, which also ensures that, for example, by heating occurring changes in length are compensated. Figures 4 to 7 show related diagrams, at which time is plotted on the abscissa. And these time values are with dashed lines across the overall display of Figures 4 to 7 shown comparably.

    In dem Diagramm nach der Figur 4 sind auf der Ordinaten die Hübe des Piezoaktors 24 und des Ventil-Kolbens 29 aufgetragen. Der Piezoaktor-Hub ist kleiner, er erzeugt abhängig von der Übersetzung den größeren Ventilhub.In the diagram according to FIG. 4, the are on the ordinate Strokes of the piezo actuator 24 and the valve piston 29 applied. The piezo actuator stroke is smaller, it generates depending on the larger the valve lift.

    Die Figur 5 zeigt anhand einer Druck-Kurve 41 einen anfänglichen großen Druck im Steuerraum 32, der mit dem Piezohub beginnt und dann mit der Bewegung des Ventilkolbens 29 abfällt. Wird der Piezo abgeschaltet und ermöglicht somit einen Rückhub, entsteht bei 42 eine Druckabsenkung bis der Ventilkolben dem Piezo gefolgt ist. Über diese Druckänderung wird die Wiederbefüllung des Steuerraumes 32 durchgeführt.FIG. 5 shows an initial one using a pressure curve 41 great pressure in the control room 32, the one with the piezo stroke begins and then drops with the movement of the valve piston 29. If the piezo is switched off and thus enables one Return stroke, a pressure drop occurs at 42 until the Valve piston followed the piezo. About this pressure change the control chamber 32 is refilled.

    Umgekehrte Verhältnisse herrschen dabei - wie das Diagramm nach der Figur 6 belegt - in dem Steuerraum 33. Dort verläuft eine Druckkurve 43 zunächst in ein Tal 44, wo eine Befüllung des Steuerraumes 33 durchgeführt wird. Anschließend folgt eine Druckspitze am Ende des Ventilhubes. Zum Schluß verläuft die Druckkurve 43 im Lecköldruckniveau.The opposite is true - like the diagram according to FIG. 6 occupied - in the control room 33 a pressure curve 43 first in a valley 44, where a filling of the control room 33 is carried out. Subsequently a pressure peak follows at the end of the valve lift. Finally the pressure curve 43 runs in the leakage oil pressure level.

    Schließlich ist in dem Diagramm nach der Figur 7 die Druckübersetzung des hydraulischen Übersetzers 25 dargestellt, die bei großen Hüben auf hohem Niveau liegt und nach der Schaltarbeit des Ventils ein niedrigeres Niveau erreicht.Finally, in the diagram of Figure 7 is the pressure ratio of the hydraulic translator 25, which is at a high level for large strokes and after the Switching work of the valve reached a lower level.

    Obwohl beim Ausführungsbeispiel zwei Drosselbohrungen 36 und 37 und zwei Steuerräume 32 und 33 beschrieben sind, ist es auch denkbar, diese Einrichtungen nur auf einer Seite des Druckraumes 26 vorzusehen. Although in the exemplary embodiment two throttle bores 36 and 37 and two control rooms 32 and 33 are described, it is also conceivable, these facilities only on one side of the To provide pressure chamber 26.

    BezugszahlenlisteLIST OF REFERENCE NUMBERS

    11
    Ventilgehäusevalve housing
    22
    Längsbohrunglongitudinal bore
    33
    Ventilnadelvalve needle
    44
    Dichtflächesealing surface
    55
    Spitzetop
    66
    --
    77
    Ringraumannulus
    88th
    Druckraumpressure chamber
    99
    --
    1010
    Druckleitungpressure line
    1111
    Druckschulterpressure shoulder
    1212
    Zylinderbohrungbore
    1313
    --
    1414
    Stirnseitefront
    1515
    SteuerdruckraumControl pressure chamber
    1616
    Drosselverbindungthrottle connection
    1717
    Ringraumannulus
    1818
    --
    1919
    Drosselbohrungthrottle bore
    2020
    Ventilsitzvalve seat
    2121
    Steuerventilcontrol valve
    2222
    Ventilgliedvalve member
    2323
    Druckfedercompression spring
    2424
    Piezoaktorpiezo actuator
    2525
    hydraulischer Übersetzerhydraulic translator
    2626
    Druckraumpressure chamber
    2727
    Schaftshaft
    2828
    Kolbenpiston
    2929
    Kolbenpiston
    3030
    Rückseiteback
    3131
    Rückseiteback
    3232
    Steuerraumcontrol room
    3333
    Steuerraumcontrol room
    3434
    Membranmembrane
    3535
    Membranmembrane
    3636
    Drosselbohrungthrottle bore
    3737
    Drosselbohrungthrottle bore
    3838
    Übergangcrossing
    3939
    Übergangcrossing
    4040
    LeckölbohrungLeak oil bore
    4141
    Druckkurvepressure curve
    4242
    Talvalley
    4343
    Druckkurvepressure curve
    4444
    Talvalley

    Claims (2)

    1. Valve for the control of liquids, with a valve member (22) which is actuable via a hydraulic intensifier (25) and is loaded in the closing direction onto its valve seat (20) by a compression spring (23), the hydraulic intensifier (25) having a pressure space (26) which, on the one hand, is delimited by a piston (28) of a piezoelectric actuator (24), the movement of the said piston giving rise in the pressure space (26) to a pressure change which, on the other hand, acts on a piston (29), likewise delimiting the pressure space (26), of the valve member (22), by means of which piston (29) the valve member (22) can be adjusted in the opening direction counter to the force of the compression spring (23), characterized in that on the rear side of at least the one piston (28 or 29) is formed a control space (32 or 33) which is closed off sealingly on the actuator side and/or valve side by a diaphragm (34 or 35) and which is filled with leakage oil from the pressure space (26), and in that a throttle bore (36 or 37) connected to a low-pressure source issues into the control space (32 or 33).
    2. Valve according to Claim 1, characterized in that the throttle bore (36 or 37) has a sharp-edged transition (38) in the relieving direction and a rounded transition (39) in the filling direction.
    EP98123744A 1998-03-28 1998-12-14 Fluid control valve Expired - Lifetime EP0947690B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE19813983A DE19813983A1 (en) 1998-03-28 1998-03-28 Valve for controlling liquids
    DE19813983 1998-03-28

    Publications (3)

    Publication Number Publication Date
    EP0947690A2 EP0947690A2 (en) 1999-10-06
    EP0947690A3 EP0947690A3 (en) 2002-06-12
    EP0947690B1 true EP0947690B1 (en) 2003-10-01

    Family

    ID=7862828

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP98123744A Expired - Lifetime EP0947690B1 (en) 1998-03-28 1998-12-14 Fluid control valve

    Country Status (4)

    Country Link
    US (1) US6089529A (en)
    EP (1) EP0947690B1 (en)
    JP (1) JP2000046220A (en)
    DE (2) DE19813983A1 (en)

    Families Citing this family (14)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE19743669A1 (en) * 1997-10-02 1999-04-08 Bosch Gmbh Robert Fuel injection valve for motor vehicle IC engine
    DE19951964A1 (en) 1999-10-28 2001-05-03 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
    DE19954288A1 (en) 1999-11-11 2001-05-17 Bosch Gmbh Robert Fuel injection valve for fitting to internal combustion engines has an injection valve element to control injection openings, a control valve to affect movement in injection valve elements and a valve element for regulating pressure
    DE10002270C1 (en) 2000-01-20 2001-06-28 Bosch Gmbh Robert Valve for controlling liquids has electronic control unit that defines piezoelectric valve element actuating unit drive voltage depending on leakage loss in low pressure region
    DE10007175B9 (en) * 2000-02-17 2004-11-04 Siemens Ag Injection valve for injecting fuel into an internal combustion engine
    DE10006785A1 (en) * 2000-02-18 2001-09-27 Bosch Gmbh Robert Injector, control valve and method for injecting fluid
    DE10023952A1 (en) * 2000-05-16 2001-11-29 Bosch Gmbh Robert Valve for controlling liquids
    DE10024702A1 (en) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Fuel injector for storage injection system includes bypass channel injecting into outlet path at valve chamber
    DE10029297A1 (en) * 2000-06-14 2001-10-18 Bosch Gmbh Robert Valve for controling liquids has piezo actuator, dual piston hydraulic converter, valve closure element and spring element directly coupled to second piston of hydraulic converter
    DE10030232A1 (en) * 2000-06-20 2002-01-17 Siemens Ag Device for transmitting a movement with play compensation
    DE10037388A1 (en) * 2000-08-01 2002-02-21 Bosch Gmbh Robert Valve arrangement, in particular for a fuel injection system of an internal combustion engine
    DE10107222C1 (en) * 2001-02-16 2002-08-29 Bosch Gmbh Robert Device for controlling liquids
    DE10230089A1 (en) * 2002-07-04 2004-01-15 Robert Bosch Gmbh Fuel injector
    DE102017202310A1 (en) * 2017-02-14 2018-08-16 Robert Bosch Gmbh Throttle element and low-pressure circuit of a fuel injection system with a throttle element

    Family Cites Families (5)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    JPS62107265A (en) * 1985-11-02 1987-05-18 Nippon Soken Inc Electrostriction type oil pressure control valve
    JPH0656162B2 (en) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 Variable stroke 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
    DE4306072C2 (en) * 1993-02-26 1994-12-08 Siemens Ag Device for opening and closing a passage opening in a housing
    DE19519192C1 (en) * 1995-05-24 1996-06-05 Siemens Ag Injector

    Also Published As

    Publication number Publication date
    DE59809801D1 (en) 2003-11-06
    US6089529A (en) 2000-07-18
    EP0947690A3 (en) 2002-06-12
    DE19813983A1 (en) 1999-09-30
    JP2000046220A (en) 2000-02-18
    EP0947690A2 (en) 1999-10-06

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