EP1631746B1 - Hydraulic drive for displacing an actuator - Google Patents

Hydraulic drive for displacing an actuator Download PDF

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Publication number
EP1631746B1
EP1631746B1 EP04736733A EP04736733A EP1631746B1 EP 1631746 B1 EP1631746 B1 EP 1631746B1 EP 04736733 A EP04736733 A EP 04736733A EP 04736733 A EP04736733 A EP 04736733A EP 1631746 B1 EP1631746 B1 EP 1631746B1
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EP
European Patent Office
Prior art keywords
piston
unit
hydraulic
cylinder
cylindrical
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Expired - Lifetime
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EP04736733A
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German (de)
French (fr)
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EP1631746A1 (en
Inventor
Norbert Krimbacher
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Linz Center of Mechatronics GmbH
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Linz Center of Mechatronics GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices

Definitions

  • the invention relates to a hydraulic drive for displacing an actuator between two predetermined end positions with a two separate cylinder chambers forming cylinder unit, with an over the cylinder spaces in the opposite direction acted upon by hydraulic springs piston unit and with a control device for alternately counteracting the piston unit.
  • a control valve is used in an admission line connecting the cylinder to a pressure accumulator of a hydraulic spring.
  • the control valve In the two end positions of the piston, the control valve is closed to move when opening the piston via the respectively tensioned hydraulic spring under tension of the other hydraulic spring in the opposite end position in which the control valve is closed to hold the piston again.
  • a working cylinder is known ( DE 196 02 390 A1 ), in which the radial distance in a cylinder chamber guided working piston in an end position cooperates with a switching ring which seals the working piston relative to the rest of the cylinder chamber, so that the working piston is acted upon interaction with the switching ring by the pressure of the hydraulic fluid in the cylinder chamber at the release of the switching ring but despite a high hydraulic fluid pressure in the cylinder chamber is freely displaced.
  • the invention is therefore based on the object with simple structural means to improve a hydraulic drive of the type described so that an independent of the actuating speed of the control device movement of the actuator can be ensured and that for holding the piston unit in the reversal positions no separate control intervention required becomes.
  • the invention solves the problem set by the fact that the cylinder chambers of the cylinder unit have a respective end face of the piston unit in the associated end position sealingly receiving end portion of smaller cross-section than the remaining cylinder space that connected via a throttle to a return line for the hydraulic fluid end portions opposite the rest Cylinder space are limited by one control edge and that the Control device consists of an actuator for an axial relative movement of the control edge relative to the piston end face.
  • the offset end portion of the cylinder unit forms a control edge, which must be axially displaced relative to the piston end face in order to pressurize the piston end face with the cylinder pressure.
  • the abruptly building up in such a relative displacement of the piston end face relative to the control edge in the region of the end portion of the cylinder chamber hydraulic medium pressure accelerates the piston unit against the opposite end position, in which the piston unit is caught on the engaging in the local end portion of the cylinder unit face.
  • the connected to the end portion return line for the hydraulic fluid comprises a throttle, although the pressure in the end portion of the cylinder chamber when retracting the piston end accordingly reduce, but the throttle prevents the sudden acceleration of the piston unit obstructing the pressure of the piston unit obstructing the end of the piston unit.
  • the connected to the end portion of the cylinder unit return line for the hydraulic fluid can be additionally blocked via a switching valve.
  • the control device for the hydraulic drive must bring about an axial relative displacement between the piston end side and the control edge delimiting the end portion of the cylinder unit.
  • the control edge of the end portions of the cylinder unit may be formed on an axially displaceably mounted, connected to the adjusting drive of the control device sleeve which is displaced over the adjusting drive of the control device.
  • Another possibility to displace the piston end face with respect to the control edge of the end portion of the cylinder unit, is to abut the piston unit, so that the piston end face is moved over the cylinder-fixed control edge.
  • the adjusting drive of the control device act on the piston end face engaging in the end section of the cylinder unit, which can be carried out hydraulically, mechanically or electromagnetically.
  • the pressure in the cylinder space can be used for holding in the end position or for releasing from the end position, because the piston unit then stepped on via the hydraulic means, even after intervention the end face remains axially loaded in the end portion of the cylinder chamber, regardless of the application of the opposite piston end face.
  • the piston unit 4 comprises two cooperating with the cylinder blocks 1 and 2 piston body 5 and 6, which is to be adjusted between two end positions actuator 7 are connected.
  • the cylinder blocks 1 and 2 form in the region of their mutually averted end walls 8 remote from the rest of the cylinder chamber 9 end portions 10 with a smaller cross-section than the remaining cylinder chamber 9.
  • These end portions 10 are compared to the rest of the cylinder chamber 9 limited by a control edge 11 and take in the respective end position the piston unit 4, the end face 12 of the respective piston body 5 and 6 respectively.
  • the end portions 10 of the cylinder blocks 1 and 2 are connected via throttles 13 to a respective return line 14 for the hydraulic medium.
  • the pressure chambers 9 of the cylinder blocks 1, 2 optionally form a hydraulic accumulator 15 shown as a block with external auxiliary accumulators.
  • These hydraulic accumulators 15 constitute hydraulic springs due to the compressibility of the hydraulic medium, by means of which the piston bodies 5 and 6 can be charged in opposite directions.
  • the hydraulic accumulators 15 are connected via switching valves 16 to a pressure line 17.
  • the hydraulic accumulator 15 are connected via check valves 18 to a pressure line 19, which ensures a predetermined minimum pressure for the hydraulic accumulator 15.
  • the piston body 5 engages in the end portion 10 of the cylinder block 1 with its end face 12 sealing, so that the pressure prevailing in the pressure chamber 9 of the cylinder block 1 hydraulic fluid pressure can exert no axial compressive forces on the piston unit 4, which is thus held by the biasing pressure in the range of Zylinderblokkes 2 in this end position.
  • the end portion 10 In order to pressurize the piston body 5 with the hydraulic fluid pressure in the cylinder chamber 9, the end portion 10 must be hydraulically connected to the rest of the cylinder chamber 9. For this purpose, the end portion 10 is enclosed by a sleeve 20 which forms the control edge 11.
  • This sleeve 20 is mounted axially displaceable and can be axially displaced over an adjusting drive of a control device relative to the end face 12 of the piston body 5 to release the end face 12 which is abruptly acted on the passing of the control edge 11 with the pressure of the hydraulic fluid in the cylinder chamber 9 and the Piston unit 4 accelerates with the actuator 7 against the pressure in the cylinder chamber 9 of the cylinder block 2.
  • the throttle 13 in the return line 14 prevents a corresponding pressure drop in the end portion 10.
  • the hydraulic accumulator 15 for the cylinder block 2 receiving the piston unit 4 in the end position By opening the associated switching valve 16, the hydraulic accumulator 15 for the cylinder block 2 receiving the piston unit 4 in the end position to compensate for friction and leakage losses be charged via the pressure line 17 to a predetermined system pressure to have the full system pressure for actuation of the piston body 6 against the pressure of the cylinder block 1 associated, partially relaxed hydraulic accumulator 15 at a control of the cylinder block 2 via the sleeve 20.
  • the cooperating with the cylinder block 1 piston body 5, as already in connection with the opposite piston body 6 was described, when reaching the end position on the engaging in the end portion 10 of the cylinder block 1 and thereby withdrawn the application pressure piston end face 12 against a free swinging motion until it is released by a renewed displacement of the sleeve 20 again.
  • Fig. 2 one of the two cylinder blocks 1, 2 of the cylinder unit 3 is shown in more detail, wherein the pressure chamber 9 forms the essential for the hydraulic spring hydraulic accumulator.
  • the end wall 8 has a coaxial projection 21, on which the required for controlling the piston body 5, 6 sleeve 20 is mounted axially displaceable.
  • This approach is also provided with a receiving bore 22 for a over the end face 12 of the piston body 5, 6 projecting guide extension 23 which has a control edge 24 for an annular connecting groove 25 of the return line 14.
  • the resulting in the drawn end position of the piston body 5, 6 between the control edge 24 of the guide extension 23 and the connecting groove 25 throttle position serves as a throttle 13, as indicated in the block diagram of FIG. 1.
  • the return line 14 is opened only for the engagement of the end face 12 of the piston body 5, 6 in the end portion 10 of the cylinder blocks 1, 2, whereby larger leakage losses are avoided.
  • admission lines 26 for the pressure chambers 9 of the cylinder blocks 1, 2 can be opened and closed by control edges 27 of the piston bodies 5, 6 as a function of the piston position.
  • these Beauftschungs effet 26 serve to connect the pressure chamber 9 to the pressure line 17, wherein the control edge 27 takes over the task of the switching valve 16.
  • the connection of the pressure chamber 9 with the acted upon only with a partial pressure, a check valve 18 having pressure line 19 requires no control.
  • the sleeve 20 is acted upon by an actuator 28, which adjusts the sleeve 20 hydraulically, mechanically or electromagnetically on the coaxial projection 21 of the cylinder block 1 and 2 axially.
  • this actuator 28 does not need to be provided outside of the cylinder unit 3.
  • Such actuators can also be installed in the cylinder unit 3.
  • the hydraulic drive of FIG. 3 differs from that of FIG. 1 only by the control of the piston body 5, 6.
  • the end portion 10 of the cylinder blocks 1, 2 with the control edge 11 is not by a movable sleeve, but by a recess formed in the end wall 8 so that the axial relative movement of the control edge 11 relative to the end face 12 of the piston body 5, 6 of these must be displaced.
  • an actuating drive 28 is provided, by means of which the end portion 10 engaging end face 12 of the piston body can be acted upon to abut the piston body and the end face 12 over the control edge 11 away, so that the hydraulic pressure in the cylinder chamber 9 for acting on the respective Piston body 5, 6 can be used.
  • the actuator can also abut the respective piston body 5, 6 mechanically or electromagnetically.
  • the hydraulic drive works the same as that shown in FIG.
  • Hydraulic drives according to the invention are therefore suitable for actuators with short switching times, as required, for example, for switching and safety valves.
  • the invention is not limited to the illustrated embodiments.
  • the cylinder blocks 1, 2 could be combined to form a common cylinder, in which a single piston is mounted as a piston unit.
  • a drive connection in the form of a piston rod is to be established between the actuator and the piston unit.
  • gas bubbles can be enclosed in the hydraulic medium or the hydraulic accumulators can additionally be acted upon by springs.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A hydraulic drive is described for displacing an actuator ( 7 ) between two predetermined end positions, comprising a piston unit ( 4 ) which can be pressurized in a cylinder unit ( 3 ) in opposite directions by way of hydraulic springs and a control device for alternating pressurization in opposite directions of the piston unit ( 4 ). In order to provide advantageous constructional conditions it is proposed that the cylinder unit ( 3 ) comprises an end section ( 10 ) of smaller cross section than the remaining cylinder space ( 9 ) and receives in a sealing manner the respective face side ( 12 ) of the piston unit ( 4 ) in the associated end position, that the end sections ( 10 ) connected via a throttle ( 13 ) to a return line ( 14 ) for the hydraulic medium are delimited by a control edge ( 11 ) each relative to the remaining cylinder space ( 9 ), and that the control device consists of an actuating drive ( 28 ) for an axial relative movement of the control edge ( 11 ) relative to the face side ( 12 ) of the piston. (FIG. 1 )

Description

Die Erfindung bezieht sich auf einen Hydraulischer Antrieb zum Verlagern eines Stellgliedes zwischen zwei vorgegebenen Endlagen mit einer zwei voneinander getrennte Zylinderräume bildenden Zylindereinheit, mit einer über die Zylinderräume gegensinnig durch hydraulische Federn beaufschlagbaren Kolbeneinheit und mit einer Steuereinrichtung zum abwechselnden gegensinnigen Beaufschlagen der Kolbeneinheit.The invention relates to a hydraulic drive for displacing an actuator between two predetermined end positions with a two separate cylinder chambers forming cylinder unit, with an over the cylinder spaces in the opposite direction acted upon by hydraulic springs piston unit and with a control device for alternately counteracting the piston unit.

Um die über einen hydraulischen Antrieb zum Öffnen eines Ventils einer Brennkraftmaschine eingesetzte Energie weitgehend auch zum Schließen des Ventils verwenden zu können, ist es bekannt ( EP 1 215 369 A2 ), die Kompressibilität des Hydraulikmittels zur Ausbildung zweier hydraulischer Federn für eine gegensinnige Beaufschlagung eines Kolbens zu nützen, so daß die über die eine hydraulische Feder auf den Kolben aufgebrachte Energie bis auf Reibungs- und Leckverluste in der anderen hydraulischen Feder gespeichert wird, um zur gegensinnigen Kolbenbeaufschlagung zur Verfügung zu stehen. Der Kolben mit dem anzutreibenden Ventilkörper bildet somit zusammen mit den beiden hydraulischen Federn einen freien Schwinger, der über eine Steuereinrichtung in den beiden Umkehrlagen festgehalten und freigegeben wird. Zu diesem Zweck wird ein Steuerventil in einer den Zylinder mit einem Druckspeicher der einen hydraulischen Feder verbindenden Beaufschlagungsleitung eingesetzt. In den beiden Endlagen des Kolbens wird das Steuerventil geschlossen, um beim Öffnen den Kolben über die jeweils gespannte hydraulische Feder unter einer Spannung der anderen hydraulischen Feder in die gegenüberliegende Endstellung zu bewegen, in der das Steuerventil zum Festhalten des Kolbens wieder geschlossen wird. Obwohl mit Hilfe dieses bekannten hydraulischen Antriebes Stellglieder mit einem vergleichsweise geringen Energieeinsatz zwischen zwei Endlagen mit hoher Geschwindigkeit verlagert werden können - es sind ja lediglich die Reibungs- und Leckverluste auszugleichen -, hängt die Bewegung des Stellgliedes auch von der Schaltgeschwindigkeit des Steuerventils ab. Außerdem ist für das Festhalten des Kolbens in den beiden Umkehrlagen ein gesonderter Steuereingriff notwendig.In order to be able to largely use the energy which is used via a hydraulic drive for opening a valve of an internal combustion engine to close the valve, it is known (US Pat. EP 1 215 369 A2 ), the compressibility of the hydraulic fluid to form two hydraulic springs for opposing loading of a piston to use, so that the energy applied to the piston via the one hydraulic spring is stored up to frictional and leakage losses in the other hydraulic spring to the opposing Kolbenbeaufschlagung available to be available. The piston with the valve body to be driven thus forms together with the two hydraulic springs a free oscillator, which is held and released via a control device in the two reversal positions. For this purpose, a control valve is used in an admission line connecting the cylinder to a pressure accumulator of a hydraulic spring. In the two end positions of the piston, the control valve is closed to move when opening the piston via the respectively tensioned hydraulic spring under tension of the other hydraulic spring in the opposite end position in which the control valve is closed to hold the piston again. Although with the help of this known hydraulic actuator actuators with a relatively low energy consumption between two limit positions can be shifted at high speed - it is only the friction and leakage losses compensate -, the movement of the actuator also depends on the switching speed of the control valve. In addition, a separate control intervention is necessary for the detention of the piston in the two reversing positions.

Darüber hinaus ist ein Arbeitszylinder bekannt ( DE 196 02 390 A1 ), bei dem der mit radialem Abstand in einem Zylinderraum geführte Arbeitskolben in einer Endlage mit einem Schaltring zusammenwirkt, der den Arbeitskolben gegenüber dem übrigen Zylinderraum abdichtet, so daß der Arbeitskolben beim Zusammenwirken mit dem Schaltring durch den Druck des Hydraulikmittels im Zylinderraum beaufschlagt wird, bei der Freigabe vom Schaltring aber trotz eines hohen Hydraulikmitteldrucks im Zylinderraum frei verschiebbar ist. Es ist daher nur eine einseitige Druckbeaufschlagung des Arbeitskolbens während der Anlage des Arbeitskolbens am Schaltring möglich, wobei der im Zylinderraum wirksame Hydraulikmitteldruck zur Beaufschlagung des Arbeitskolbens dient Bei einer Freigabe des Arbeitskolbens über Bohrungen des Schaltringes kann der Arbeitskolben nicht schlagartig freigegeben werden.In addition, a working cylinder is known ( DE 196 02 390 A1 ), in which the radial distance in a cylinder chamber guided working piston in an end position cooperates with a switching ring which seals the working piston relative to the rest of the cylinder chamber, so that the working piston is acted upon interaction with the switching ring by the pressure of the hydraulic fluid in the cylinder chamber at the release of the switching ring but despite a high hydraulic fluid pressure in the cylinder chamber is freely displaced. It is therefore only a one-sided pressurization of the working piston during the system of the working piston on the switching ring possible, wherein the cylinder space effective hydraulic medium pressure for acting on the working piston is used in a release of the working piston through holes of the switching ring, the working piston can not be released abruptly.

Der Erfindung liegt somit die Aufgabe zugrunde, einen hydraulischen Antrieb der eingangs geschilderten Art mit einfachen konstruktiven Mitteln so zu verbessern, daß eine von der Stellgeschwindigkeit der Steuereinrichtung unabhängige Bewegung des Stellgliedes sichergestellt werden kann und daß zum Festhalten der Kolbeneinheit in den Umkehrlagen kein gesonderter Steuereingriff erforderlich wird.The invention is therefore based on the object with simple structural means to improve a hydraulic drive of the type described so that an independent of the actuating speed of the control device movement of the actuator can be ensured and that for holding the piston unit in the reversal positions no separate control intervention required becomes.

Die Erfindung löst die gestellte Aufgabe dadurch, daß die Zylinderräume der Zylindereinheit einen die jeweilige Stirnseite der Kolbeneinheit in der zugehörigen Endlage dichtend aufnehmenden Endabschnitt kleineren Querschnitts als der übrige Zylinderraum aufweisen, daß die über eine Drossel an eine Rücklaufleitung für das Hydraulikmittel angeschlossenen Endabschnitte gegenüber dem übrigen Zylinderraum durch je eine Steuerkante begrenzt sind und daß die Steuereinrichtung aus einem Stelltrieb für eine axiale Relativbewegung der Steuerkante gegenüber der Kolbenstirnseite besteht.The invention solves the problem set by the fact that the cylinder chambers of the cylinder unit have a respective end face of the piston unit in the associated end position sealingly receiving end portion of smaller cross-section than the remaining cylinder space that connected via a throttle to a return line for the hydraulic fluid end portions opposite the rest Cylinder space are limited by one control edge and that the Control device consists of an actuator for an axial relative movement of the control edge relative to the piston end face.

Da zufolge dieser Maßnahmen die jeweilige Stirnseite der Kolbeneinheit in deren Endlage in den vom übrigen Zylinderraum abgesetzten Endabschnitt der Zylindereinheit eingreift, fällt in dieser Endlage der Beaufschlagungsdruck auf die in den Endabschnitt der Zylindereinheit eingreifende Kolbenstimseite weg, wenn der Druck in diesem Endabschnitt entsprechend abgebaut wird, was über eine Rücklaufleitung für das Hydraulikmittel sichergestellt wird. Dies bedeutet, daß die in der Endlage stirnseitig in den Endabschnitt des Zylinderraumes eingreifende Kolbeneinheit lediglich von der gegenüberliegenden Stirnseite her beaufschlagt ist und daher in dieser Endlage festgehalten wird, obwohl der Zylinderraum unter einem entsprechend hohen Druck steht. Zur gegensinnigen Ansteuerung der Kolbeneinheit ist der die Kolbenstirnseite aufnehmende Endabschnitt der Zylindereinheit mit dem übrigen Zylinderraum hydraulisch zu verbinden. Zu diesem Zweck bildet der abgesetzte Endabschnitt der Zylindereinheit eine Steuerkante, die relativ zur Kolbenstirnseite axial verlagert werden muß, um die Kolbenstirnseite mit dem Zylinderdruck zu beaufschlagen. Der sich bei einer solchen Relativverschiebung der Kolbenstirnseite gegenüber der Steuerkante im Bereich des Endabschnittes des Zylinderraumes schlagartig aufbauende Hydraulikmitteldruck beschleunigt die Kolbeneinheit gegen die gegenüberliegende Endlage hin, in der die Kolbeneinheit über die in den dortigen Endabschnitt der Zylindereinheit eingreifende Stirnseite gefangen wird. Da die an den Endabschnitt angeschlossene Rücklaufleitung für das Hydraulikmittel eine Drossel umfaßt, kann sich zwar der Druck im Endabschnitt des Zylinderraumes beim Einfahren der Kolbenstirnseite entsprechend abbauen, doch verhindert die Drossel beim schlagartigen Beaufschlagen der Stirnseite der Kolbeneinheit einen die Beschleunigung der Kolbeneinheit behindernden Druckabbau. Außerdem kann die an den Endabschnitt der Zylindereinheit angeschlossene Rücklaufleitung für das Hydraulikmittel zusätzlich über ein Schaltventil gesperrt werden.Since, according to these measures, the respective end face of the piston unit engages in its end position in the end portion of the cylinder unit remote from the remaining cylinder space, in this end position the loading pressure falls on the piston end face engaging in the end portion of the cylinder unit, if the pressure in this end portion is correspondingly reduced. what is ensured via a return line for the hydraulic fluid. This means that in the end position, the end face in the end portion of the cylinder chamber engaging piston unit only from the opposite end side is acted upon and is therefore held in this position, although the cylinder chamber is under a correspondingly high pressure. For the opposite control of the piston unit of the piston end side receiving end portion of the cylinder unit is to be connected hydraulically to the rest of the cylinder chamber. For this purpose, the offset end portion of the cylinder unit forms a control edge, which must be axially displaced relative to the piston end face in order to pressurize the piston end face with the cylinder pressure. The abruptly building up in such a relative displacement of the piston end face relative to the control edge in the region of the end portion of the cylinder chamber hydraulic medium pressure accelerates the piston unit against the opposite end position, in which the piston unit is caught on the engaging in the local end portion of the cylinder unit face. Since the connected to the end portion return line for the hydraulic fluid comprises a throttle, although the pressure in the end portion of the cylinder chamber when retracting the piston end accordingly reduce, but the throttle prevents the sudden acceleration of the piston unit obstructing the pressure of the piston unit obstructing the end of the piston unit. In addition, the connected to the end portion of the cylinder unit return line for the hydraulic fluid can be additionally blocked via a switching valve.

Die Steuereinrichtung für den hydraulischen Antrieb muß eine axiale Relativverschiebung zwischen der Kolbenstirnseite und der den Endabschnitt der Zylindereinheit begrenzenden Steuerkante bewirken. Zu diesem Zweck kann die Steuerkante der Endabschnitte der Zylindereinheit an einer axialverschiebbar gelagerten, mit dem Stelltrieb der Steuereinrichtung verbundenen Hülse ausgebildet sein, die über den Stelltrieb der Steuereinrichtung verlagert wird. Sobald die durch die Hülse gebildete Steuerkante an der Kolbenstirnseite vorbeibewegt wird, erfolgt die Druckbeaufschlagung der Kolbeneinheit. Die Verstellgeschwindigkeit der Hülse hat dabei keinen praktischen Einfluß auf die Beschleunigung der Kolbeneinheit, weil die Druckbeaufschlagung der Kolbeneinheit schlagartig mit der Freigabe der Kolbenstirnseite erfolgt.The control device for the hydraulic drive must bring about an axial relative displacement between the piston end side and the control edge delimiting the end portion of the cylinder unit. For this purpose, the control edge of the end portions of the cylinder unit may be formed on an axially displaceably mounted, connected to the adjusting drive of the control device sleeve which is displaced over the adjusting drive of the control device. As soon as the control edge formed by the sleeve is moved past the piston end face, the pressure is applied to the piston unit. The adjustment speed of the sleeve has no practical influence on the acceleration of the piston unit, because the pressurization of the piston unit occurs abruptly with the release of the piston end face.

Eine weitere Möglichkeit, die Kolbenstirnseite gegenüber der Steuerkante des Endabschnittes der Zylindereinheit zu verlagern, besteht darin, die Kolbeneinheit anzustoßen, so daß die Kolbenstirnseite über die zylinderfeste Steuerkante bewegt wird. Zu diesem Zweck kann der Stelltrieb der Steuereinrichtung die jeweils in den Endabschnitt der Zylindereinheit eingreifende Kolbenstirnseite beaufschlagen, was hydraulisch, mechanisch oder elektromagnetisch durchgeführt werden kann.Another possibility to displace the piston end face with respect to the control edge of the end portion of the cylinder unit, is to abut the piston unit, so that the piston end face is moved over the cylinder-fixed control edge. For this purpose, the adjusting drive of the control device act on the piston end face engaging in the end section of the cylinder unit, which can be carried out hydraulically, mechanically or electromagnetically.

Ist zumindest eine Stirnseite der Kolbeneinheit mit einem gegenüber der übrigen Kolbeneinheit unterschiedlich großen Querschnitt versehen, so kann der Druck im Zylinderraum zum Halten in der Endlage oder zum Lösen aus der Endlage genützt werden, weil ja über das Hydraulikmittel die dann abgestufte Kolbeneinheit auch nach dem Eingreifen der Stirnseite in den Endabschnitt des Zylinderraumes axial beaufschlagt bleibt, und zwar unabhängig von der Beaufschlagung der gegenüberliegenden Kolbenstirnseite.If at least one end face of the piston unit is provided with a cross section of differing size from the rest of the piston unit, then the pressure in the cylinder space can be used for holding in the end position or for releasing from the end position, because the piston unit then stepped on via the hydraulic means, even after intervention the end face remains axially loaded in the end portion of the cylinder chamber, regardless of the application of the opposite piston end face.

Bilden die mit hydraulischem Druckmittel beaufschlagten Zylinderräume auf beiden Seiten der Kolbeneinheit die hydraulischen Federn, ohne auf äußere Druckspeicher zurückzugreifen, so sind diese Druckräume mit steuerbaren Beaufschlagungsleitungen zu verbinden, um die Reibungs- und Leckverluste nach jedem Antriebshub ausgleichen zu können. Da diese Steuerung der Beaufschlagungsleitungen von der jeweiligen Lage der Kolbeneinheit abhängt, können die Beaufschlagungsleitungen durch Steuerkanten der Kolbeneinheit in Abhängigkeit von der axialen Kolbenlage geöffnet und geschlossen werden, so daß sich hierfür gesonderte Schaltventile mit der zugehörigen Ansteuerung erübrigen. In ähnlicher Weise kann auch die Rücklaufleitung für das Hydraulikmittel in den Endabschnitten der Zylindereinheit mit Hilfe einer entsprechenden Steuerkante der Kolbeneinheit gesteuert werden.Form the acted upon by hydraulic pressure fluid cylinder chambers on both sides of the piston unit, the hydraulic springs, without resorting to external pressure accumulator, these pressure chambers are connected to controllable admission lines to compensate for the friction and leakage losses after each drive stroke can. Since this control of the Beaufschlagungsleitungen depends on the respective position of the piston unit, the Beaufschlagungsleitungen can be opened and closed by control edges of the piston unit in response to the axial piston position, so that this unnecessary separate switching valves with the associated control. Similarly, the return line for the hydraulic fluid in the end portions of the cylinder unit can be controlled by means of a corresponding control edge of the piston unit.

Kurze Beschreibung der ZeichnungShort description of the drawing

In der Zeichnung ist der Erfindungsgegenstand beispielsweise dargestellt. Es zeigen:

Fig. 1
einen erfindungsgemäßen hydraulischen Antrieb zum Verlagern eines Stellgliedes in einem vereinfachten Blockschaltbild,
Fig. 2
den einer Seite der Kolbeneinheit zugehörigen Zylinderraum in einem schematischen Axialschnitt und
Fig. 3
eine der Fig. 1 entsprechende Darstellung einer Konstruktionsvariante eines erfindungsgemäßen hydraulischen Antriebes.
In the drawing, the subject invention is shown, for example. Show it:
Fig. 1
a hydraulic drive according to the invention for displacing an actuator in a simplified block diagram,
Fig. 2
the cylinder space associated with one side of the piston unit in a schematic axial section and
Fig. 3
1 corresponding representation of a design variant of a hydraulic drive according to the invention.

Weg zur Ausführung der ErfindungWay to carry out the invention

Gemäß dem Blockschaltbild der Fig. 1 weist der dargestellte hydraulische Antrieb eine in zwei Zylinderblöcke 1 und 2 unterteilte Zylindereinheit 3 auf, deren Kolbeneinheit 4 zwei mit den Zylinderblöcken 1 und 2 zusammenwirkende Kolbenkörper 5 und 6 umfaßt, die über ein zwischen zwei Endlagen zu verstellendes Stellglied 7 verbunden sind. Die Zylinderblöcke 1 und 2 bilden im Bereich ihrer voneinander abgekehrten Stirnwände 8 vom übrigen Zylinderraum 9 abgesetzte Endabschnitte 10 mit einem kleineren Querschnitt als der übrige Zylinderraum 9. Diese Endabschnitte 10 sind gegenüber dem übrigen Zylinderraum 9 durch eine Steuerkante 11 begrenzt und nehmen in der jeweiligen Endlage der Kolbeneinheit 4 die Stirnseite 12 des jeweiligen Kolbenkörpers 5 bzw. 6 auf. Die Endabschnitte 10 der Zylinderblöcke 1 und 2 sind über Drosseln 13 an je eine Rücklaufleitung 14 für das Hydraulikmittel angeschlossen. Die Druckräume 9 der Zylinderblöcke 1, 2 bilden gegebenenfalls mit äußeren Zusatzspeichern einen als Block dargestellten Hydraulikspeicher 15. Diese Hydraulikspeicher 15 stellen aufgrund der Kompressibilität des Hydraulikmittels hydraulische Federn dar, über die die Kolbenkörper 5 und 6 gegensinnig beaufschlagt werden können. Die Hydraulikspeicher 15 sind über Schaltventile 16 an eine Druckleitung 17 angeschlossen. Zusätzlich sind die Hydraulikspeicher 15 über Rückschlagventile 18 mit einer Druckleitung 19 verbunden, die einen vorgegebenen Mindestdruck für die Hydraulikspeicher 15 sicherstellt.According to the block diagram of Fig. 1, the hydraulic drive shown in a divided into two cylinder blocks 1 and 2 cylinder unit 3, the piston unit 4 comprises two cooperating with the cylinder blocks 1 and 2 piston body 5 and 6, which is to be adjusted between two end positions actuator 7 are connected. The cylinder blocks 1 and 2 form in the region of their mutually averted end walls 8 remote from the rest of the cylinder chamber 9 end portions 10 with a smaller cross-section than the remaining cylinder chamber 9. These end portions 10 are compared to the rest of the cylinder chamber 9 limited by a control edge 11 and take in the respective end position the piston unit 4, the end face 12 of the respective piston body 5 and 6 respectively. The end portions 10 of the cylinder blocks 1 and 2 are connected via throttles 13 to a respective return line 14 for the hydraulic medium. The pressure chambers 9 of the cylinder blocks 1, 2 optionally form a hydraulic accumulator 15 shown as a block with external auxiliary accumulators. These hydraulic accumulators 15 constitute hydraulic springs due to the compressibility of the hydraulic medium, by means of which the piston bodies 5 and 6 can be charged in opposite directions. The hydraulic accumulators 15 are connected via switching valves 16 to a pressure line 17. In addition, the hydraulic accumulator 15 are connected via check valves 18 to a pressure line 19, which ensures a predetermined minimum pressure for the hydraulic accumulator 15.

In der in der Fig. 1 dargestellten Endlage der Kolbeneinheit 4 greift der Kolbenkörper 5 in den Endabschnitt 10 des Zylinderblockes 1 mit seiner Stirnseite 12 dichtend ein, so daß der im Druckraum 9 des Zylinderblockes 1 herrschende Hydraulikmitteldruck keine axialen Druckkräfte auf die Kolbeneinheit 4 ausüben kann, die somit durch den Beaufschlagungsdruck im Bereich des Zylinderblokkes 2 in dieser Endstellung gehalten wird. Um den Kolbenkörper 5 mit dem Hydraulikmitteldruck im Zylinderraum 9 zu beaufschlagen, muß der Endabschnitt 10 mit dem übrigen Zylinderraum 9 hydraulisch verbunden werden. Zu diesem Zweck wird der Endabschnitt 10 von einer Hülse 20 umschlossen, die die Steuerkante 11 bildet. Diese Hülse 20 ist axial verschiebbar gelagert und kann über einen Stelltrieb einer Steuereinrichtung gegenüber der Stirnseite 12 des Kolbenkörpers 5 axial verlagert werden, um die Stirnseite 12 freizugeben, die beim Vorbeibewegen der Steuerkante 11 schlagartig mit dem Druck des Hydraulikmittels im Zylinderraum 9 beaufschlagt wird und die Kolbeneinheit 4 mit dem Stellglied 7 gegen den Druck im Zylinderraum 9 des Zylinderblockes 2 beschleunigt. Die Drossel 13 in der Rücklaufleitung 14 unterbindet dabei einen entsprechenden Druckabfall im Endabschnitt 10. Mit der Entspannung des Hydraulikspeichers 15 des Zylinderblocks 1 wird der Hydraulikspeicher 15 des Zylinderblocks 2 über den in den Zylinderraum 9 einfahrenden Kolbenkörper 6 gespannt, wobei im Bereich der die Endlage der Kolbeneinheit 4 bildenden Bewegungsumkehr des freien Schwingers die Stirnseite 12 des Kolbenkörpers 6 in den Endabschnitt 10 des Zylinderblocks 2 dichtend eingreift. Die Kolbeneinheit wird daher in dieser Stellung durch den verbleibenden Druck des zum Teil entspannten Hydraulikspeichers 15 in der neuen Endlage gehalten. Die Verbindung der Hydraulikspeicher 15 mit der Druckleitung 19 über die Rückschlagventile 18 sichert einen Mindesthaltedruck für die Kolbeneinheit 4. Durch ein Öffnen des zugehörigen Schaltventils 16 kann der Hydraulikspeicher 15 für den die Kolbeneinheit 4 in der Endlage aufnehmenden Zylinderblock 2 zum Ausgleich von Reibungs- und Leckverlusten über die Druckleitung 17 auf einen vorgegebenen Systemdruck aufgeladen werden, um bei einer Ansteuerung des Zylinderblockes 2 über die Hülse 20 den vollen Systemdruck zur Beaufschlagung des Kolbenkörpers 6 entgegen dem Druck des dem Zylinderblock 1 zugehörigen, teilweise entspannten Hydraulikspeichers 15 zur Verfügung zu haben. Der mit dem Zylinderblock 1 zusammenwirkende Kolbenkörper 5 wird, wie dies bereits im Zusammenhang mit dem gegenüberliegenden Kolbenkörper 6 beschrieben wurde, beim Erreichen der Endstellung über die in den Endabschnitt 10 des Zylinderblockes 1 eingreifende und dadurch dem Beaufschlagungsdruck entzogene Kolbenstirnseite 12 gegenüber einer freien Schwingbewegung festgehalten, bis er durch ein neuerliches Verlagern der Hülse 20 wieder freigegeben wird. In der Zwischenzeit kann der dem Zylinderblock 1 zugehörige, durch das Rückstellen der Kolbeneinheit 4 wieder gespannte Hydraulikspeicher 15 zur Abdeckung der Reibungs- und Leckverluste über das Steuerventil 16 an die Druckleitung 17 angeschlossen werden, das vor der Ansteuerung der Hülse 20 über die hiefür vorgesehene Steuereinrichtung wieder zu schließen ist.In the end position of the piston unit 4 shown in FIG. 1, the piston body 5 engages in the end portion 10 of the cylinder block 1 with its end face 12 sealing, so that the pressure prevailing in the pressure chamber 9 of the cylinder block 1 hydraulic fluid pressure can exert no axial compressive forces on the piston unit 4, which is thus held by the biasing pressure in the range of Zylinderblokkes 2 in this end position. In order to pressurize the piston body 5 with the hydraulic fluid pressure in the cylinder chamber 9, the end portion 10 must be hydraulically connected to the rest of the cylinder chamber 9. For this purpose, the end portion 10 is enclosed by a sleeve 20 which forms the control edge 11. This sleeve 20 is mounted axially displaceable and can be axially displaced over an adjusting drive of a control device relative to the end face 12 of the piston body 5 to release the end face 12 which is abruptly acted on the passing of the control edge 11 with the pressure of the hydraulic fluid in the cylinder chamber 9 and the Piston unit 4 accelerates with the actuator 7 against the pressure in the cylinder chamber 9 of the cylinder block 2. The throttle 13 in the return line 14 prevents a corresponding pressure drop in the end portion 10. With the relaxation of the hydraulic accumulator 15 of the cylinder block 1, the hydraulic accumulator 15 of the cylinder block 2 is stretched over the retracting into the cylinder chamber 9 piston body 6, wherein in the region of the end position of the Piston unit 4 forming movement reversal of the free oscillator, the end face 12 of the piston body 6 in the end portion 10 of the cylinder block 2 sealingly engages. The piston unit is therefore held in this position by the remaining pressure of the partially relaxed hydraulic accumulator 15 in the new end position. The connection of the hydraulic accumulator 15 with the pressure line 19 via the check valves 18 ensures a minimum holding pressure for the piston unit 4. By opening the associated switching valve 16, the hydraulic accumulator 15 for the cylinder block 2 receiving the piston unit 4 in the end position to compensate for friction and leakage losses be charged via the pressure line 17 to a predetermined system pressure to have the full system pressure for actuation of the piston body 6 against the pressure of the cylinder block 1 associated, partially relaxed hydraulic accumulator 15 at a control of the cylinder block 2 via the sleeve 20. The cooperating with the cylinder block 1 piston body 5, as already in connection with the opposite piston body 6 was described, when reaching the end position on the engaging in the end portion 10 of the cylinder block 1 and thereby withdrawn the application pressure piston end face 12 against a free swinging motion until it is released by a renewed displacement of the sleeve 20 again. In the meantime, the cylinder block 1 associated, re-tensioned by the return of the piston unit 4 hydraulic accumulator 15 to cover the friction and leakage losses via the control valve 16 to the pressure line 17 are connected, before the control of the sleeve 20 via the provided therefor control device is close again.

In der Fig. 2 ist einer der beiden Zylinderblöcke 1, 2 der Zylindereinheit 3 näher dargestellt, wobei der Druckraum 9 den für die hydraulische Feder wesentlichen Hydraulikspeicher bildet. Die Stirnwand 8 weist einen koaxialen Ansatz 21 auf, auf dem die zur Steuerung des Kolbenkörpers 5, 6 erforderliche Hülse 20 axial verschiebbar gelagert ist. Dieser Ansatz ist außerdem mit einer Aufnahmebohrung 22 für einen über die Stirnseite 12 des Kolbenkörpers 5, 6 vorstehenden Führungsfortsatz 23 versehen, der eine Steuerkante 24 für eine ringförmige Anschlußnut 25 der Rücklaufleitung 14 besitzt. Die sich in der gezeichneten Endlage des Kolbenkörpers 5, 6 zwischen der Steuerkante 24 des Führungsfortsatzes 23 und der Anschlußnut 25 ergebende Drosselstelle dient als Drossel 13, wie sie im Blockschaltbild nach der Fig. 1 angedeutet ist. Durch diese Maßnahme wird die Rücklaufleitung 14 nur für das Eingreifen der Stirnseite 12 der Kolbenkörper 5, 6 in den Endabschnitt 10 der Zylinderblöcke 1, 2 geöffnet, wodurch größere Leckverluste vermieden werden.In Fig. 2, one of the two cylinder blocks 1, 2 of the cylinder unit 3 is shown in more detail, wherein the pressure chamber 9 forms the essential for the hydraulic spring hydraulic accumulator. The end wall 8 has a coaxial projection 21, on which the required for controlling the piston body 5, 6 sleeve 20 is mounted axially displaceable. This approach is also provided with a receiving bore 22 for a over the end face 12 of the piston body 5, 6 projecting guide extension 23 which has a control edge 24 for an annular connecting groove 25 of the return line 14. The resulting in the drawn end position of the piston body 5, 6 between the control edge 24 of the guide extension 23 and the connecting groove 25 throttle position serves as a throttle 13, as indicated in the block diagram of FIG. 1. By this measure, the return line 14 is opened only for the engagement of the end face 12 of the piston body 5, 6 in the end portion 10 of the cylinder blocks 1, 2, whereby larger leakage losses are avoided.

In ähnlicher Weise können Beaufschlagungsleitungen 26 für die Druckräume 9 der Zylinderblöcke 1, 2 durch Steuerkanten 27 der Kolbenkörper 5, 6 in Abhängigkeit von der Kolbenlage geöffnet und geschlossen werden. Im Falle eines auf den Druckraum 9 beschränkten Hydraulikspeichers dienen diese Beaufschlagungsleitungen 26 zum Anschluß des Druckraumes 9 an die Druckleitung 17, wobei die Steuerkante 27 die Aufgabe des Schaltventils 16 übernimmt. Die Verbindung des Druckraumes 9 mit der nur mit einem Teildruck beaufschlagten, ein Rückschlagventil 18 aufweisenden Druckleitung 19 bedarf keiner Steuerung.In a similar manner, admission lines 26 for the pressure chambers 9 of the cylinder blocks 1, 2 can be opened and closed by control edges 27 of the piston bodies 5, 6 as a function of the piston position. In the case of a limited to the pressure chamber 9 hydraulic accumulator these Beaufschlagungsleitungen 26 serve to connect the pressure chamber 9 to the pressure line 17, wherein the control edge 27 takes over the task of the switching valve 16. The connection of the pressure chamber 9 with the acted upon only with a partial pressure, a check valve 18 having pressure line 19 requires no control.

Die Hülse 20 wird durch einen Stelltrieb 28 beaufschlagt, der die Hülse 20 hydraulisch, mechanisch oder elektromagnetisch auf dem koaxialen Ansatz 21 des Zylinderblockes 1 bzw. 2 axial verstellt. Dieser Stelltrieb 28 braucht aber nicht außerhalb der Zylindereinheit 3 vorgesehen zu werden. Solche Stelltriebe können auch in die Zylindereinheit 3 eingebaut werden.The sleeve 20 is acted upon by an actuator 28, which adjusts the sleeve 20 hydraulically, mechanically or electromagnetically on the coaxial projection 21 of the cylinder block 1 and 2 axially. However, this actuator 28 does not need to be provided outside of the cylinder unit 3. Such actuators can also be installed in the cylinder unit 3.

Der hydraulische Antrieb gemäß der Fig. 3 unterscheidet sich von dem nach der Fig. 1 lediglich durch die Ansteuerung der Kolbenkörper 5, 6. Der Endabschnitt 10 der Zylinderblöcke 1, 2 mit der Steuerkante 11 wird nicht durch eine bewegliche Hülse, sondern durch eine Ausnehmung in der Stirnwand 8 gebildet, so daß zur axialen Relativbewegung der Steuerkante 11 gegenüber der Stirnseite 12 des Kolbenkörpers 5, 6 dieser verlagert werden muß. Zu diesem Zweck ist ein Stelltrieb 28 vorgesehen, mit dessen Hilfe die in den Endabschnitt 10 eingreifende Stirnseite 12 des Kolbenkörpers beaufschlagt werden kann, um den Kolbenkörper anzustoßen und die Stirnseite 12 über die Steuerkante 11 hinwegzubewegen, damit der Hydraulikdruck im Zylinderraum 9 zur Beaufschlagung des jeweiligen Kolbenkörpers 5, 6 genützt werden kann. Obwohl diese Kolbenbeaufschlagung im Ausführungsbeispiel nach der Fig. 3 hydraulisch erfolgt, kann der Stelltrieb den jeweiligen Kolbenkörper 5, 6 auch mechanisch oder elektromagnetisch anstoßen. Im übrigen arbeitet der hydraulische Antrieb gleich wie der in der Fig. 1 dargestellte. Durch das Spannen und Entspannen der Hydraulikspeicher 15 beim Hin- und Herbewegen der Kolbeneinheit 4 wird ein Großteil der zum Verstellen des Stellgliedes 7 in eine Richtung aufgewendete Energie gespeichert, um für die rückläufige Bewegung der Kolbeneinheit 4 zur Verfügung zu stehen, so daß lediglich die auftretenden Reibungs- und Leckverluste auszugleichen sind.The hydraulic drive of FIG. 3 differs from that of FIG. 1 only by the control of the piston body 5, 6. The end portion 10 of the cylinder blocks 1, 2 with the control edge 11 is not by a movable sleeve, but by a recess formed in the end wall 8 so that the axial relative movement of the control edge 11 relative to the end face 12 of the piston body 5, 6 of these must be displaced. For this purpose, an actuating drive 28 is provided, by means of which the end portion 10 engaging end face 12 of the piston body can be acted upon to abut the piston body and the end face 12 over the control edge 11 away, so that the hydraulic pressure in the cylinder chamber 9 for acting on the respective Piston body 5, 6 can be used. Although this Kolbenbeaufschlagung in the embodiment of FIG. 3 is hydraulically, the actuator can also abut the respective piston body 5, 6 mechanically or electromagnetically. Moreover, the hydraulic drive works the same as that shown in FIG. By tensioning and relaxing the hydraulic accumulator 15 when reciprocating the piston unit 4, a large part of the energy used to move the actuator 7 in one direction is stored to be available for the retrograde movement of the piston unit 4, so that only those occurring To compensate for friction and leakage losses.

Durch die beschriebenen Maßnahmen gelingt es, den Energieverbrauch insbesondere bei hohen Kolbenbeschleunigungen erheblich zu verringern, und zwar bei sehr kurzen Stellzeiten, weil ja die Kolbenkörper 5, 6 nur entsprechend angesteuert werden müssen und sich selbständig in der jeweiligen Endlage verriegeln. Erfindungsgemäße hydraulische Antriebe eignen sich folglich für Stellglieder mit kurzen Schaltzeiten, wie sie beispielsweise für Schalt- und Sicherheitsventile gefordert werden.By the measures described it is possible to reduce the energy consumption, especially at high piston accelerations considerably, and indeed at very short operating times, because yes, the piston body 5, 6 only in accordance must be controlled and lock themselves in the respective end position. Hydraulic drives according to the invention are therefore suitable for actuators with short switching times, as required, for example, for switching and safety valves.

Es braucht wohl nicht besonders hervorgehoben zu werden, daß sich die Erfindung nicht auf die dargestellten Ausführungsbeispiele beschränkt. So könnten zum Beispiel die Zylinderblöcke 1, 2 zu einem gemeinsamen Zylinder zusammengefaßt werden, in dem ein einziger Kolben als Kolbeneinheit gelagert ist. In diesem Fall ist zwischen dem Stellglied und der Kolbeneinheit eine Antriebsverbindung in Form einer Kolbenstange herzustellen. Um die Elastizität der hydraulischen Federn zu beeinflussen, können in das Hydraulikmittel Gasblasen eingeschlossen oder die hydraulischen Speicher zusätzlich durch Federn beaufschlagt werden.It need not be emphasized that the invention is not limited to the illustrated embodiments. Thus, for example, the cylinder blocks 1, 2 could be combined to form a common cylinder, in which a single piston is mounted as a piston unit. In this case, a drive connection in the form of a piston rod is to be established between the actuator and the piston unit. In order to influence the elasticity of the hydraulic springs, gas bubbles can be enclosed in the hydraulic medium or the hydraulic accumulators can additionally be acted upon by springs.

Claims (5)

  1. Hydraulic drive for displacing an actuator (7) between two predefined end positions with a cylindrical unit (3) forming two cylindrical chambers (9) separated from each other, with a piston unit (4) which can be impacted by hydraulic springs in opposite directions via the cylindrical chambers (9) and with a control device for alternating impacting in opposite directions of the piston unit (4), characterised in that the cylindrical chambers (9) of the cylindrical unit (3) comprise an end section (10) receiving the respective end face (12) of the piston unit (4) in the associated end position in a sealing way, said end section (10) having a smaller cross-section than the rest of the cylindrical chamber (9), in that the end sections (10) connected by means of a throttle element (13) to a return line (14) for the hydraulic medium are delimited in relation to the rest of the cylindrical chamber (9) by a respective control edge (11) and in that the control device consists of an actuating drive (28) for a relative axial movement of the control edge (11) relative to the piston end face (12).
  2. Hydraulic drive according to claim 1, characterised in that the control edge (11) of the end sections (10) of the cylindrical unit (3) is formed on a sleeve (20) mounted so as to be axially displaceable and connected to the actuating drive of the control device.
  3. Hydraulic drive according to claim 1, characterised in that the actuating drive (28) of the control device impacts the respective piston end face (12) engaging in the end section (10) of the cylindrical unit (3).
  4. Hydraulic drive according to one of the claims 1 to 3, characterised in that at least one end face (12) of the piston unit (4) has a cross section differing in size from that of the rest of the piston unit (4).
  5. Hydraulic drive according to one of the claims 1 to 4, characterised in that the return lines (14) for the hydraulic medium connected to the end sections (10) of the cylindrical unit (3) and / or impacting lines (26) connected to the cylindrical unit (3) on each piston side can be opened and closed by control edges (24, 27) of the piston unit (4) in dependence upon the axial piston position.
EP04736733A 2003-06-12 2004-06-14 Hydraulic drive for displacing an actuator Expired - Lifetime EP1631746B1 (en)

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AT0091303A AT500672B8 (en) 2003-06-12 2003-06-12 HYDRAULIC DRIVE FOR DISPLACING A MEMBER
PCT/AT2004/000202 WO2004111468A1 (en) 2003-06-12 2004-06-14 Hydraulic drive for displacing an actuator

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EP1631746A1 EP1631746A1 (en) 2006-03-08
EP1631746B1 true EP1631746B1 (en) 2007-08-15

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EP (1) EP1631746B1 (en)
KR (1) KR101056532B1 (en)
CN (1) CN100398845C (en)
AT (2) AT500672B8 (en)
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Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8454321B2 (en) 2009-05-22 2013-06-04 General Compression, Inc. Methods and devices for optimizing heat transfer within a compression and/or expansion device
JP5723871B2 (en) 2009-05-22 2015-05-27 ジェネラル コンプレッション インコーポレイテッド Compression and / or expansion device
CA2785472A1 (en) 2009-12-24 2011-06-30 General Compression Inc. Methods and devices for optimizing heat transfer within a compression and/or expansion device
US8915073B1 (en) 2010-09-13 2014-12-23 Daniel Theobald Fluid power device, method and system
WO2012078606A1 (en) 2010-12-07 2012-06-14 General Compression, Inc. Compressor and/or expander device with rolling piston seal
US8997475B2 (en) 2011-01-10 2015-04-07 General Compression, Inc. Compressor and expander device with pressure vessel divider baffle and piston
US8572959B2 (en) 2011-01-13 2013-11-05 General Compression, Inc. Systems, methods and devices for the management of heat removal within a compression and/or expansion device or system
CA2824798A1 (en) 2011-01-14 2012-07-19 General Compression, Inc. Compressed gas storage and recovery system and method of operation
US8272212B2 (en) 2011-11-11 2012-09-25 General Compression, Inc. Systems and methods for optimizing thermal efficiencey of a compressed air energy storage system
US8522538B2 (en) 2011-11-11 2013-09-03 General Compression, Inc. Systems and methods for compressing and/or expanding a gas utilizing a bi-directional piston and hydraulic actuator
CN102767546B (en) * 2012-08-13 2015-03-18 合肥熔安动力机械有限公司 Five-station hydraulic cylinder
AT516507B1 (en) * 2014-12-02 2016-06-15 Gfm-Gmbh forging machine
CN109391578B (en) * 2017-08-11 2022-07-22 华为技术有限公司 Signal sending method, signal receiving method, terminal equipment and network equipment

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1343760A (en) * 1962-10-13 1963-11-22 Cie Parisienne Outil Air Compr Damping cylinders
BE793149A (en) * 1971-12-27 1973-06-21 Westinghouse Bremsen Apparate LIMIT SWITCH CUSHIONING DEVICE
US5058857A (en) * 1990-02-22 1991-10-22 Mark Hudson Solenoid operated valve assembly
FR2665925B1 (en) * 1990-08-17 1993-10-29 Renault Regie Nale Usines ELECTROHYDRAULIC CONTROL DEVICE FOR A VALVE OF AN INTERNAL COMBUSTION ENGINE.
CN2075165U (en) * 1990-10-16 1991-04-17 李云章 Elastic coupling vehicle for connecting railway rolling stock
US5221072A (en) * 1992-01-14 1993-06-22 North American Philips Corporation Resilient hydraulic actuator
JP2869265B2 (en) * 1992-05-29 1999-03-10 三菱電機株式会社 Breaker
DE4233115C2 (en) * 1992-10-02 1995-04-13 Ulrich Keller Hydraulically operated locking and coupling device
DE4242601A1 (en) * 1992-12-17 1994-06-30 Eisenbach B Rotox Gmbh Fluid power cylinder with adjustable stroke
JPH0734857A (en) * 1993-07-26 1995-02-03 Nissan Motor Co Ltd Exhaust gas purifying device for diesel engine
DE19602390A1 (en) * 1995-01-28 1996-08-01 Ulrich Keller Work cylinder with piston and cylinder
CN1067341C (en) * 1998-03-25 2001-06-20 吴荣毅 Automotive braking collision-proof device
DE19824579C1 (en) * 1998-06-02 1999-06-17 Tuenkers Maschinenbau Gmbh Bell-crank lever clamping device or piston and cylinder unit
AT411090B (en) 2000-12-12 2003-09-25 Jenbacher Ag FULLY VARIABLE HYDRAULIC VALVE ACTUATOR

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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KR101056532B1 (en) 2011-08-12
ATE370337T1 (en) 2007-09-15
AT500672B1 (en) 2006-08-15
AT500672A1 (en) 2006-02-15
WO2004111468A1 (en) 2004-12-23
US7395748B2 (en) 2008-07-08
AT500672B8 (en) 2007-02-15
CN1802513A (en) 2006-07-12
DE502004004658D1 (en) 2007-09-27
US20060137336A1 (en) 2006-06-29
KR20060026043A (en) 2006-03-22
EP1631746A1 (en) 2006-03-08
CN100398845C (en) 2008-07-02

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