EP0081703A1 - Electro-hydraulic actuator - Google Patents

Electro-hydraulic actuator Download PDF

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Publication number
EP0081703A1
EP0081703A1 EP82110794A EP82110794A EP0081703A1 EP 0081703 A1 EP0081703 A1 EP 0081703A1 EP 82110794 A EP82110794 A EP 82110794A EP 82110794 A EP82110794 A EP 82110794A EP 0081703 A1 EP0081703 A1 EP 0081703A1
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EP
European Patent Office
Prior art keywords
drive according
throttle
pressure
pump
adjusting member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP82110794A
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German (de)
French (fr)
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EP0081703B1 (en
Inventor
Egon Dipl.-Ing. Lechner
Siegfried Mayer
Dieter Dipl.-Ing. Weigle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0081703A1 publication Critical patent/EP0081703A1/en
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Publication of EP0081703B1 publication Critical patent/EP0081703B1/en
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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to an actuator according to the preamble of the main claim.
  • the pump consists of a delivery thread, which is arranged with little radial play in a surrounding housing. Due to the rotation of the conveying thread, pressure medium is conveyed from one side to the other and the housing having axial mobility with respect to the conveying thread is displaced in the axial direction and performs the function of an adjusting member.
  • the disadvantage is that the pump is extremely dependent on viscosity, so that the actuator no longer works at high pressure medium temperatures (when using oil).
  • the drive according to the invention with the characterizing features of the main claim has the advantage that it is not only very simple, but also works reliably under all operating conditions. Advantageous further developments and improvements of the features specified in the main claim are possible through the measures listed in the subclaims. It is particularly advantageous to have the pump work in a closed circuit since there are practically no pressure medium losses.
  • FIG. 1 shows an electrohydraulic actuator in a schematic representation
  • FIG. 8 shows a detail.
  • 10 denotes a direct current electric motor which drives a reversible hydrostatic pump 11, in particular a gear pump.
  • Two delivery lines 12 and 13 are connected to these and lead to two pressure chambers 14, 15 of an actuating cylinder 16.
  • a double-acting piston 17 is arranged in a tightly sliding manner, which is loaded on both sides by springs 18, 19 arranged in the pressure chambers 14, 15. These hold the piston 17 in the middle position when the pump 11 is out of operation.
  • the device to be actuated is connected to the two piston rods 20, 21 protruding from the actuating cylinder - or of course only to one - e.g. a directional valve.
  • the two delivery lines 12, 13 are connected between the pump 11 and the actuating cylinder 16 by a line 22, in which a throttle 23, or even better an orifice, is arranged.
  • a diaphragm is particularly suitable because it is much less sensitive to viscosity than a choke.
  • the pump 11 operates in an open circuit.
  • Suction lines 26, 27 lead from the pressure lines 12, 13 to a container 28.
  • a check valve 29 or 30 is arranged in each suction line and can open in the direction from the container to the suction line.
  • the actuating cylinder is replaced by a directional control valve 32, ie this is now adjusted directly by the differential pressure in the pressure lines 12, 13 against the force of the springs 18, 19. Since they are basically the same parts, they also have the same reference numbers.
  • the throttle in the connecting line 22 is now adjustable and designated 33.
  • the mode of operation is not extensive res from the previously described, ie instead of a control piston, the slide of the directional valve is now adjusted directly.
  • the throttle 33 can be designed as a laminar throttle.
  • a linear characteristic requires a temperature-compensated laminar choke or an electronically controlled voltage on the direct current motor (compensation of choke and motor characteristic). 'The temperature compensation is possible via an expansion working element or a bimetal lines 58, 59 with throttles 60, 61 can be connected for the purpose of targeted leakage; however, this is not absolutely necessary.
  • the embodiment of Figure 4 differs from the previous ones essentially in that there is no longer a connecting line between the pressure lines 12, 13.
  • the pressure difference is now generated by throttles or orifices 35, 36, each of which is arranged in a line 37, 38 which leads from the delivery line 12 or 13 and leads to the container.
  • the chokes can be adjustable. None changes in the basic functionality. If the pump 10 delivers into the delivery line 12, a pressure corresponding to the setting of the throttle 25 builds up in this, and the valve is actuated.
  • the throttles can be adjustable as a function of pressure and temperature in order to adapt to the engine characteristic.
  • the throttles are arranged in lines 40, 41, which start from the pressure spaces 42, 43 of the directional control valve 32.
  • the chokes are designated 44, 45 and coupled to one another via a linkage 46 in such a way that they open in opposite directions NEN or close.
  • the function is again the same as in the exemplary embodiment according to FIG. 4 or the previous ones.
  • the check valves 29, 30 which act as suction valves are also provided. It is also possible to equip the last described embodiment without the check valves; the throttles 44, 45 can be used for suction from the container 28 (FIG. 6).
  • the embodiment according to FIG. 7 - which partially corresponds to the two previous ones with the throttle 44, 45 at the two pressure chambers of the valve, but not coupled this time - again has the connecting line 22 between the two pressure lines 12, 13, in which the throttle 23 is arranged is. Suction valves 29, 30 are also provided. With such a device, a partial exchange of the circulating pressure medium is achieved via the throttles 44, 45 in the control valve. These can of course also be coupled again or set individually.
  • FIG. 9 shows the simplest embodiment of an actuator according to the invention, which, however, is only effective on one side here.
  • the pump is now not reversible but delivers via a pressure line 50 into the pressure chamber 51 of the actuating cylinder 52 acting on one side.
  • Line 54 with throttle 53 is connected in parallel to the pressure line. The mode of operation is readily apparent from what has been described above.
  • the exemplary embodiment according to FIG. 8 shows a practical embodiment of the control valve 32, for example according to FIG. 5.
  • the control slide 60 has two external collars 61, 62 which control widening outlets and inlets 63, 64 on the housing. These parts form the chokes.

Abstract

1. Electrohydraulic positioning drive having a reversible pump (11) which is driven by an electric motor (10) and delivers pressure medium, in each case via one of two pressure lines (12, 13), to a double-acting adjusting member (16), an adjustable throttle means (22, 25) being connected onto the pressure lines, by means of which throttle means (22, 25) a connection can be made to a chamber of low pressure, characterised in that the adjusting member is a directional control valve (16), the slide valve (17) of which is acted upon on both sides by centering springs (18, 19), in that a throttle valve (22, 25) is connected on each directional control valve chamber (14, 15) acted upon by the pump, which throttle valve (22, 25) is connected to a chamber (21) of lower pressure, and in that the throttle valves are coupled and are adjustable in opposite directions.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Stellantrieb nach der Gattung des Hauptanspruchs. Bei einem derartigen bekannten Antrieb besteht die Pumpe aus einem Fördergewinde, das mit geringem radialem Spiel in einem.dieses umgebenden Gehäuse angeordnet ist. Durch die Rotation des Fördergewindes wird Druckmittel von der einen Seite zur anderen gefördert und das axiale Beweglichkeit gegenüber dem Fördergewinde aufweisende Gehäuse wird in axialer Richtung verschoben und übt die Funktion eines Verstellorgans aus. Nachteilig ist, daß die Pumpe außerordentlich stark viskositätsabhängig ist, so daß der Stellantrieb bei hohen Druckmitteltemperaturen (bei Verwendung von Öl) überhaupt nicht mehr funktioniert.The invention relates to an actuator according to the preamble of the main claim. In such a known drive, the pump consists of a delivery thread, which is arranged with little radial play in a surrounding housing. Due to the rotation of the conveying thread, pressure medium is conveyed from one side to the other and the housing having axial mobility with respect to the conveying thread is displaced in the axial direction and performs the function of an adjusting member. The disadvantage is that the pump is extremely dependent on viscosity, so that the actuator no longer works at high pressure medium temperatures (when using oil).

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Antrieb mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß er nicht nur sehr einfach ausgebildet ist, sondern auch unter allen Betriebsbedingungen zuverlässig arbeitet. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Merkmale möglich. Besonders vorteilhaft ist es, die Pumpe im geschlossenen Kreis arbeiten zu lassen, da hier praktisch keine Druckmittelverluste auftreten.The drive according to the invention with the characterizing features of the main claim has the advantage that it is not only very simple, but also works reliably under all operating conditions. Advantageous further developments and improvements of the features specified in the main claim are possible through the measures listed in the subclaims. It is particularly advantageous to have the pump work in a closed circuit since there are practically no pressure medium losses.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen elektrohydraulischen Stellantrieb in schematischer Darstellung, Figuren 2 bis 7 Abwandlungen dieses Ausführungsbeispiels, Figur 8 eine Einzelheit.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows an electrohydraulic actuator in a schematic representation, FIGS. 2 to 7 modifications of this exemplary embodiment, FIG. 8 shows a detail.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist mit 10 ein Gleichstrom-Elektromotor bezeichnet, der eine reversierbare hydrostatische Pumpe 11, insbesondere eine Zahnradpumpe, antreibt. An diese sind zwei Förderleitungen 12 bzw. 13 angeschlossen, die zu zwei Druckräumen 14, 15 eines Stellzylinders 16 führen. In diesem ist ein doppeltwirkender Kolben 17 dicht gleitend angeordnet, der beidseitig von in den Druckräumen 14, 15 angeordneten Federn 18, 19 belastet ist. Diese halten den Kolben 17 in Mittelstellung, wenn die Pumpe 11 außer Betrieb ist. An die beiden aus dem Stellzylinder ragenden Kolbenstangen 20, 21 - oder natürlich auch nur an eine - ist das zu betätigende Gerät angeschlossen, z.B. ein Wegeventil.In FIG. 1, 10 denotes a direct current electric motor which drives a reversible hydrostatic pump 11, in particular a gear pump. Two delivery lines 12 and 13 are connected to these and lead to two pressure chambers 14, 15 of an actuating cylinder 16. In this, a double-acting piston 17 is arranged in a tightly sliding manner, which is loaded on both sides by springs 18, 19 arranged in the pressure chambers 14, 15. These hold the piston 17 in the middle position when the pump 11 is out of operation. The device to be actuated is connected to the two piston rods 20, 21 protruding from the actuating cylinder - or of course only to one - e.g. a directional valve.

Die beiden Förderleitungen 12, 13 sind zwischen Pumpe 11 und Stellzylinder 16 durch eine Leitung 22 miteinander verbunden, in der eine Drossel 23, oder noch besser eine Blende, angeordnet ist. Eine Blende eignet sich deshalb besonders gut, da sie wesentlich unempfindlicher gegen Viskosität ist als eine Drossel.The two delivery lines 12, 13 are connected between the pump 11 and the actuating cylinder 16 by a line 22, in which a throttle 23, or even better an orifice, is arranged. A diaphragm is particularly suitable because it is much less sensitive to viscosity than a choke.

Es sei angenommen, daß die Pumpe 11 nach Anlaufen des Elektromotors 10 in die Druckleitung 12 fördere. In dieser sowie in der Leitung 22 und im Druckraum 14 baut sich ein Druck auf, der abhängig ist vom Durchflußwiderstand der Drossel 23, vom Widerstand der Feder 19 sowie der an den Kolbenstangen angreifenden Kraft. Der Kolben 17 legt nun einen bestimmten Stellweg zurück, d.h. er bewegt sich so lange, bis Druck- und Federrückstellkräfte im Gleichgewicht sind bzw. das Hubende erreicht ist. Bei Motorstillstand läuft der Kolben in die Ausgangsstellung zurück. Die Sollwertspannung am Motor bestimmt die Drehzahl der Pumpe und diese den Förderstrom. Hinter der Drossel 23 fällt der Druck auf den Ansaugdruck ab, und das aus dem Druckraum 15 verdrängte Druckmittel sowie das über die Drossel 23 fließende gelangen zur Saugseite der Pumpe 11. Daraus ist zu erkennen, daß diese im geschlossenen Kreis arbeitet. Wird die Drehrichtung des Elektromotors 10 umgekehrt und damit die Pumpe 11 reversiert, so wird die Leitung 13 Druckleitung, und der Kolben 17 bewegt sich nach der entgegengesetzten Seite. Die Drehzahldrückung des Motors ist proportional zu der an der Drossel 23 erzeugten Druckdifferenz und diese wieder proportional der Drehzahl. Dies ergibt eine lineare Kennlinie für die Zuordnung des Stellwegs zur Sollwertspannung U am Elektromotor.It is assumed that the pump 11 pumps into the pressure line 12 after the electric motor 10 has started. In this and in the line 22 and in the pressure chamber 14, a pressure builds up, which is dependent on the flow resistance of the throttle 23, the resistance of the spring 19 and the force acting on the piston rods. The piston 17 now covers a certain travel, i.e. it moves until the pressure and spring restoring forces are balanced or the stroke end is reached. When the engine is stopped, the piston returns to the starting position. The setpoint voltage on the motor determines the speed of the pump and this determines the flow rate. Downstream of the throttle 23, the pressure drops to the suction pressure, and the pressure medium displaced from the pressure chamber 15 and the fluid flowing via the throttle 23 reach the suction side of the pump 11. From this it can be seen that this works in a closed circuit. If the direction of rotation of the electric motor 10 is reversed and thus the pump 11 is reversed, the line 13 becomes a pressure line and the piston 17 moves to the opposite side. The speed reduction of the motor is proportional to the pressure difference generated at the throttle 23 and this again proportional to the speed. This results in a linear characteristic curve for the assignment of the adjustment path to the setpoint voltage U on the electric motor.

Beim Ausführungsbeispiel nach der Figur 2 arbeitet die Pumpe 11 im offenen Kreis. Von den Druckleitungen 12, 13 führen Saugleitungen 26, 27 zu einem Behälter 28. In jeder Saugleitung ist ein Rücks chlagventil 29 bzw. 30 angeordnet, die sich in Richtung vom Behälter zur Saugleitung hin zu öffnen vermögen.In the exemplary embodiment according to FIG. 2, the pump 11 operates in an open circuit. Suction lines 26, 27 lead from the pressure lines 12, 13 to a container 28. A check valve 29 or 30 is arranged in each suction line and can open in the direction from the container to the suction line.

Wenn die Pumpe durch Einschalten des Elektromotors in Betrieb gesetzt wird, wird nunmehr ein Teil des Druckmittels aus dem Behälter über eines der Rückschlagventile in die Saugleitung angesaugt und in die entsprechende Druckleitung verdrängt. Das andere Rückschlagventil ist dann durch den Betriebsdruck geschlossen. Man erreicht mit dieser Anordnung ein Nachsaugen von Druckmittel, das durch Leckage verloren geht.When the pump is started by switching on the electric motor, part of the pressure medium is now sucked out of the container via one of the check valves into the suction line and displaced into the corresponding pressure line. The other check valve is then closed by the operating pressure. With this arrangement, pressure medium is sucked in, which is lost due to leakage.

Für beide,-sowie auch die weiteren Ausführungsbeispiele gilt, daß sie eine Sicherheit insofern gewährleisten, als bei Ausfall des Elektromotors der Stellzylinder durch die Federn in Mittelstellung zurückgeführt wird.For both, as well as the other exemplary embodiments, it applies that they ensure safety insofar as the actuating cylinder is returned to the central position by the springs in the event of a failure of the electric motor.

Selbstverständlich ist es auch möglich, einen einfach wirkenden Stellzylinder vorzusehen, wobei die Pumpe dann nicht reversierbar ist; siehe hierzu Figur 9.Of course, it is also possible to provide a single-acting actuating cylinder, the pump then not being reversible; see Figure 9.

Beim Ausführungsbeispiel nach Figur 3 ist der Stellzylinder ersetzt durch ein Wegeventil 32, d.h.- dieses wird nun unmittelbar vom Differenzdruck in den Druckleitungen 12, 13 entgegen der Kraft der Federn 18, 19 verstellt. Da es sich im Prinzip um dieselben Teile handelt, tragen sie auch dieselben Bezugsziffern. Im Unterschied zum Ausführungsbeispiel nach Figur 2 bzw. Figur 1 ist die Drossel in der Verbindungsleitung 22 nunmehr verstellbar und mit 33 beichnet. Die Funktionsweise ergibt sich ohne weiteres aus dem zuvor Beschriebenen, d.h. es wird nunmehr anstatt eines Stellkolbens der Schieber des Wegeventils unmittelbar verstellt. Die Drossel 33 kann als Laminardrossel ausgebildet sein. Eine lineare Kennlinie erfordert eine temperaturkompensierte Laminardrossel oder eine elektronisch gesteuerte Spannung am Gleichstrommotor (Kompensation von Drossel- und Motorkennlinie).'Die Temperaturkompensation.ist über ein Dehnstoff-Arbeitselement oder ein Bimetall möglich.An die die Feder 18, 19 aufnehmenden Druckräume 56, 57 können zwecks gezielter Leckage Leitungen 58, 59 mit Drosseln 60, 61 angeschlossen sein; dies ist aber nicht unbedingt erforderlich.In the exemplary embodiment according to FIG. 3, the actuating cylinder is replaced by a directional control valve 32, ie this is now adjusted directly by the differential pressure in the pressure lines 12, 13 against the force of the springs 18, 19. Since they are basically the same parts, they also have the same reference numbers. In contrast to the exemplary embodiment according to FIG. 2 or FIG. 1, the throttle in the connecting line 22 is now adjustable and designated 33. The mode of operation is not extensive res from the previously described, ie instead of a control piston, the slide of the directional valve is now adjusted directly. The throttle 33 can be designed as a laminar throttle. A linear characteristic requires a temperature-compensated laminar choke or an electronically controlled voltage on the direct current motor (compensation of choke and motor characteristic). 'The temperature compensation is possible via an expansion working element or a bimetal lines 58, 59 with throttles 60, 61 can be connected for the purpose of targeted leakage; however, this is not absolutely necessary.

Das Ausführungsbeispiel nach Figur 4 unterscheidet sich durch die vorhergehenden im wesentlichen dadurch, daß nun zwischen den Druckleitungen 12, 13 keine Verbindungsleitung mehr vorhanden ist. Die Druckdifferenz wird nunmehr erzeugt durch Drosseln oder Blenden 35, 36, die jeweils in eine von der Förderleitung 12 bzw. 13 ausgehende Leitung 37, 38 angeordnet sind, welche zum Behälter führen. Die Drosseln können einstellbar sein. An der grundsätzlichen Funktionsweise ändert sich hierbei nichts. Fördert die Pumpe 10 in die Förderleitung 12, so baut sich in dieser ein der Einstellung der Drossel 25 entsprechender Druck auf, und das Ventil wird betätigt. Die Drosseln können in Abhängigkeit von Druck und Temperatur verstellbar sein, um eine Anpassung an die Motorkennlinie zu erreichen.The embodiment of Figure 4 differs from the previous ones essentially in that there is no longer a connecting line between the pressure lines 12, 13. The pressure difference is now generated by throttles or orifices 35, 36, each of which is arranged in a line 37, 38 which leads from the delivery line 12 or 13 and leads to the container. The chokes can be adjustable. Nothing changes in the basic functionality. If the pump 10 delivers into the delivery line 12, a pressure corresponding to the setting of the throttle 25 builds up in this, and the valve is actuated. The throttles can be adjustable as a function of pressure and temperature in order to adapt to the engine characteristic.

Beim Ausführungsbeispiel nach der Figur 5 sind die Drosseln in Leitungen 40, 41 angeordnet, welches von den Druckräumen 42, 43 des Wegeventils 32 ausgehen. Die Drosseln sind mit 44, 45 bezeichnet und über ein Gestänge 46 so miteinander gekoppelt, daß sie sich gegensinnig öffnen bzw. schließen. Die Funktion ist dabei wiederum dieselbe wie beim Ausführungsbeispiel nach Figur 4 bzw. den vorhergehenden. Außerdem sind noch wie beim Ausführungsbeispiel nach Figur 2 bzw. 3, die als Nachsaugventile wirkenden Rückschlagventile 29, 30 vorgesehen. Es ist auch möglich, das zuletzt beschriebene Ausführungsbeispiel ohne die Rückschlagventile auszustatten; dabei können die Drosseln 44, 45 zum Ansaugen aus Behälter 28 verwendet werden (Figur 6).In the exemplary embodiment according to FIG. 5, the throttles are arranged in lines 40, 41, which start from the pressure spaces 42, 43 of the directional control valve 32. The chokes are designated 44, 45 and coupled to one another via a linkage 46 in such a way that they open in opposite directions NEN or close. The function is again the same as in the exemplary embodiment according to FIG. 4 or the previous ones. In addition, as in the exemplary embodiment according to FIGS. 2 and 3, the check valves 29, 30 which act as suction valves are also provided. It is also possible to equip the last described embodiment without the check valves; the throttles 44, 45 can be used for suction from the container 28 (FIG. 6).

Das Ausführungsbeispiel nach Figur 7 - welches teilweise den beiden vorhergehenden mit den Drossel 44, 45 an den beiden Druckräumen des Ventils entspricht, diesmal jedoch nicht gekoppelt - weist wieder die Verbindungsleitung 22 zwischen den beiden Druckleitungen 12, 13 auf, in der die Drossel 23 angeordnet ist. Auch sind Nachsaugventile 29, 30 vorgesehen. Mit einer solchen Einrichtung erreicht man einen Teilaustausch des umlaufenden Druckmittels über die Drosseln 44, 45 im Steuerventil. Diese können selbstverstänlich auch wieder gekoppelt sein oder individuell eingestellt werden.The embodiment according to FIG. 7 - which partially corresponds to the two previous ones with the throttle 44, 45 at the two pressure chambers of the valve, but not coupled this time - again has the connecting line 22 between the two pressure lines 12, 13, in which the throttle 23 is arranged is. Suction valves 29, 30 are also provided. With such a device, a partial exchange of the circulating pressure medium is achieved via the throttles 44, 45 in the control valve. These can of course also be coupled again or set individually.

Das Ausführungsbeispiel nach Figur 9 zeigt die einfachste Ausführungsform eines erfindungsgemäßen Stellantriebs, der hier allerdings nur einseitig wirksam ist. Die Pumpe ist nun nicht reversierbar sondern fördert über eine Druckleitung 50 in den Druckraum 51 des einseitig wirkenden Stellzylinders 52. Parallel an die Druckleitung ist die Leitung 54 mit Drossel 53 angeschlossen. Die Wirkungsweise ergibt sich ohne weiteres aus dem zuvor Beschriebenen.The exemplary embodiment according to FIG. 9 shows the simplest embodiment of an actuator according to the invention, which, however, is only effective on one side here. The pump is now not reversible but delivers via a pressure line 50 into the pressure chamber 51 of the actuating cylinder 52 acting on one side. Line 54 with throttle 53 is connected in parallel to the pressure line. The mode of operation is readily apparent from what has been described above.

Das Ausführungsbeispiel nach Figur 8 zeigt eine praktische Ausführung des Steuerventils 32 beispielsweise nach Figur 5. Der Steuerschieber 60 hat zwei außenliegende Bunde 61, 62, welche sich erweiternde Ab- bzw. Zuläufe 63, 64 am Gehäuse steuern. Diese Teile bilden die Drosseln.The exemplary embodiment according to FIG. 8 shows a practical embodiment of the control valve 32, for example according to FIG. 5. The control slide 60 has two external collars 61, 62 which control widening outlets and inlets 63, 64 on the housing. These parts form the chokes.

Claims (14)

1. Elektro-hydraulischer Stellantrieb mit einer von einem Elektromotor angetrieben Pumpe, die Druckmittel über mindestens eine Druckleitung zu einem Verstellorgan fördert, auf das eine Gegenkraft einwirkt, dadurch gekennzeichnet, daß an die Druckleitung (12, 13) ein Drosselorgan (23; 33; 35, 36; 44, 45) angeschlossen ist, über das eine Verbindung zu einem Raum niedrigeren Druckes besteht.1. Electro-hydraulic actuator with a pump driven by an electric motor, which conveys pressure medium via at least one pressure line to an adjusting element, on which a counterforce acts, characterized in that a throttle element (23; 33; 35, 36; 44, 45) is connected, via which there is a connection to a room of lower pressure. 2. Antrieb nach Anspruch 1, dadurch gekennzeichnet, daß die Gegenkraft durch eine Feder (18, 19) erzeugt wird.2. Drive according to claim 1, characterized in that the counterforce is generated by a spring (18, 19). 3. Antrieb nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß das Drosselorgan eine viskositätsunabhängige Blende ist.3. Drive according to claim 1 and / or 2, characterized in that the throttle element is a viscosity-independent diaphragm. 4. Antrieb nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Drosselorgan parallel an die Druckleitung angeschlossen ist.4. Drive according to one of claims 1 to 3, characterized in that the throttle element is connected in parallel to the pressure line. 5. Antrieb nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Pumpe (11) reversierbar ist.5. Drive according to one of claims 1 to 4, characterized in that the pump (11) is reversible. 6. Antrieb nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Verstellorgan (16) doppeltwirkend ausgebildet ist.6. Drive according to one of claims 1 to 5, characterized in that the adjusting member (16) is double-acting. 7. Antrieb nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das Verstellorgan ein Wegeventil (32) ist, dessen Steuerschieber beidseits von Zentrierfedern belastet ist und daß an jeden von der Pumpe beaufschlagten Druckraum des Wegeventils eine Drossel (44, 45) angeschlossen ist, die zum Raum niedrigeren Druckes Verbindung hat.7. Drive according to one of claims 1 to 6, characterized in that the adjusting member is a directional valve (32), the control slide is loaded on both sides by centering springs and that a throttle (44, 45) is connected to each pressure chamber of the directional valve acted upon by the pump that is connected to the space of lower pressure. 8. Antrieb nach Anspruch 7, dadurch gekennzeichnet, daß die Drosseln gekoppelt und gegensinnig verstellbar sind.8. Drive according to claim 7, characterized in that the throttles are coupled and adjustable in opposite directions. -9. Antrieb nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß die Pumpe im geschlossenen Kreis arbeitet und daß die beiden an sie angeschlossenen Leitungen (12, 13) durch eine Leitung (22) miteinander verbunden sind, in der das Drosselorgan (23) angeordnet ist.-9. Drive according to one of claims 1 to 8, characterized in that the pump operates in a closed circuit and that the two lines (12, 13) connected to it are connected to one another by a line (22) in which the throttle element (23) is arranged is. 10. Antrieb nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß die Pumpe im offenen Kreis arbeitet und bei Reversierbarkeit Druckmittel über Rückschlagventile (29, 30) aus einem Behälter ansaugt.10. Drive according to one of claims 1 to 8, characterized in that the pump works in an open circuit and in reversible pressure medium sucks via check valves (29, 30) from a container. 11. Antrieb nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß das Verstellorgan (60, 61, 62) im Zusammenwirken mit einem Abfluß (63, 64) selbst das Drosselorgan bildet (Figur 8).11. Drive according to one of claims 1 to 10, characterized in that the adjusting member (60, 61, 62) in cooperation with a drain (63, 64) itself forms the throttle member (Figure 8). 12. Antrieb nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, daß der Elektromotor ein Gleichstrommotor ist.12. Drive according to one of claims 1 to 11, characterized in that the electric motor is a DC motor. 13. Antrieb nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß das Verstellorgan ein Arbeitszylinder ist.13. Drive according to one of claims 1 to 12, characterized in that the adjusting member is a working cylinder. 14. Antrieb nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß die Drossel eine temperaturkompensierte Laminardrossel ist und die Temperaturkompensation über ein Dehnstoff-Arbeitselement oder ein Bimetall erfolgt.14. Drive according to one of claims 1 to 13, characterized in that the throttle is a temperature-compensated laminar throttle and the temperature compensation takes place via an expansion working element or a bimetal.
EP82110794A 1981-12-05 1982-11-23 Electro-hydraulic actuator Expired EP0081703B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813148174 DE3148174A1 (en) 1981-12-05 1981-12-05 ELECTROHYDRAULIC ACTUATOR
DE3148174 1981-12-05

Publications (2)

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EP0081703A1 true EP0081703A1 (en) 1983-06-22
EP0081703B1 EP0081703B1 (en) 1986-02-26

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ID=6147968

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EP82110794A Expired EP0081703B1 (en) 1981-12-05 1982-11-23 Electro-hydraulic actuator

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EP (1) EP0081703B1 (en)
JP (1) JPS58102807A (en)
DE (2) DE3148174A1 (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2163875A (en) * 1984-08-28 1986-03-05 Commercial Shearing Positioning of hydraulic elements
US4872310A (en) * 1986-12-12 1989-10-10 British Aerospace, Plc Electro-hydraulic actuator assembly
EP0362592A2 (en) * 1988-10-04 1990-04-11 ITT Automotive Europe GmbH Hydraulic power steering for motor vehicles
EP0482329A1 (en) * 1990-09-22 1992-04-29 Steag Ag Hydraulic actuator for controlling and regulating valves
EP0665381A1 (en) * 1994-01-28 1995-08-02 PAUL PLEIGER Maschinenfabrik GmbH & Co. KG System for operating hydraulically actuated valves
GB2422862A (en) * 2005-02-03 2006-08-09 Schlumberger Holdings Apparatus for actuating downhole tools
WO2009071264A1 (en) * 2007-12-04 2009-06-11 Robert Bosch Gmbh Hydraulic system having adjustable rapid-lowering valve
US7610754B2 (en) 2005-02-03 2009-11-03 Daikin Industries, Ltd. Fluid pressure unit and fluid pressure unit control method

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* Cited by examiner, † Cited by third party
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DE19600650C2 (en) * 1996-01-10 2003-05-28 Trinova Gmbh Drive for a hydraulic double-acting actuator
DE19958257B4 (en) * 1999-12-03 2008-04-24 Bosch Rexroth Aktiengesellschaft Semi-open hydraulic circuit
JP2004263645A (en) * 2003-03-03 2004-09-24 Opton Co Ltd Hydraulic device
CN103429911B (en) * 2011-03-07 2017-02-08 莫戈公司 Subsea actuation system
DE102013005127B4 (en) 2013-03-26 2017-10-19 BUKO Solutions GmbH adjustment
DE202013002862U1 (en) 2013-03-26 2013-04-23 BUKO Solutions GmbH adjustment
DE102013008792B4 (en) * 2013-05-23 2016-12-22 Thomas Magnete Gmbh Method and device for adjusting a hydraulic variable displacement pump
CN105003481B (en) * 2015-07-01 2017-02-01 天津大学 Integrated variable-damping hydraulic support system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH201066A (en) * 1937-10-26 1938-11-15 Escher Wyss Maschf Ag Hydraulic servo motor for actuating rotating closing elements.
DE841094C (en) * 1950-09-05 1952-06-13 Elektro Mechanik G M B H Electro-hydraulic adjusting drive with slide control
US2916879A (en) * 1956-04-04 1959-12-15 John T Gondek Combination hydraulic power unit
FR1518913A (en) * 1967-02-15 1968-03-29 Puma Soc Control device for a double-acting cylinder or the like
FR2009929A1 (en) * 1968-05-21 1970-02-13 Bbc Brown Boveri & Cie HYDROELECTRIC CONTROL DEVICE

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4218884A (en) * 1978-11-08 1980-08-26 Harold Gold Hydraulic speed governor
DE2940403A1 (en) * 1979-10-05 1981-04-09 G.L. Rexroth Gmbh, 8770 Lohr DEVICE FOR REGULATING AN ACTUATOR, IN PARTICULAR REGULATING THE LIFTING DEVICE OF A TRACTOR, COMBINE HARNESS OR THE LIKE.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH201066A (en) * 1937-10-26 1938-11-15 Escher Wyss Maschf Ag Hydraulic servo motor for actuating rotating closing elements.
DE841094C (en) * 1950-09-05 1952-06-13 Elektro Mechanik G M B H Electro-hydraulic adjusting drive with slide control
US2916879A (en) * 1956-04-04 1959-12-15 John T Gondek Combination hydraulic power unit
FR1518913A (en) * 1967-02-15 1968-03-29 Puma Soc Control device for a double-acting cylinder or the like
FR2009929A1 (en) * 1968-05-21 1970-02-13 Bbc Brown Boveri & Cie HYDROELECTRIC CONTROL DEVICE

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2163875A (en) * 1984-08-28 1986-03-05 Commercial Shearing Positioning of hydraulic elements
FR2573169A1 (en) * 1984-08-28 1986-05-16 Commercial Shearing APPARATUS FOR REMOTELY POSITIONING A VALVE
US4872310A (en) * 1986-12-12 1989-10-10 British Aerospace, Plc Electro-hydraulic actuator assembly
EP0362592A2 (en) * 1988-10-04 1990-04-11 ITT Automotive Europe GmbH Hydraulic power steering for motor vehicles
WO1990003908A2 (en) * 1988-10-04 1990-04-19 Alfred Teves Gmbh Hydraulic servo-assisted steering system for motor vehicles
WO1990003908A3 (en) * 1988-10-04 1990-06-28 Teves Gmbh Alfred Hydraulic servo-assisted steering system for motor vehicles
EP0362592A3 (en) * 1988-10-04 1990-09-05 ITT Automotive Europe GmbH Hydraulic power steering for motor vehicles
EP0482329A1 (en) * 1990-09-22 1992-04-29 Steag Ag Hydraulic actuator for controlling and regulating valves
EP0665381A1 (en) * 1994-01-28 1995-08-02 PAUL PLEIGER Maschinenfabrik GmbH & Co. KG System for operating hydraulically actuated valves
GB2422862A (en) * 2005-02-03 2006-08-09 Schlumberger Holdings Apparatus for actuating downhole tools
US7610754B2 (en) 2005-02-03 2009-11-03 Daikin Industries, Ltd. Fluid pressure unit and fluid pressure unit control method
WO2009071264A1 (en) * 2007-12-04 2009-06-11 Robert Bosch Gmbh Hydraulic system having adjustable rapid-lowering valve

Also Published As

Publication number Publication date
DE3269488D1 (en) 1986-04-03
EP0081703B1 (en) 1986-02-26
DE3148174A1 (en) 1983-06-09
JPS58102807A (en) 1983-06-18

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