EP1953393A2 - Oscillating vane actuator - Google Patents

Oscillating vane actuator Download PDF

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Publication number
EP1953393A2
EP1953393A2 EP08001157A EP08001157A EP1953393A2 EP 1953393 A2 EP1953393 A2 EP 1953393A2 EP 08001157 A EP08001157 A EP 08001157A EP 08001157 A EP08001157 A EP 08001157A EP 1953393 A2 EP1953393 A2 EP 1953393A2
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EP
European Patent Office
Prior art keywords
aggregate according
working chambers
pressure
chamber
separating element
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Granted
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EP08001157A
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German (de)
French (fr)
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EP1953393A3 (en
EP1953393B1 (en
Inventor
Christian Böttger
Rainer Beilner
Matthias Reuss
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ZF Friedrichshafen AG
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ZF Friedrichshafen AG
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Publication of EP1953393A3 publication Critical patent/EP1953393A3/en
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Publication of EP1953393B1 publication Critical patent/EP1953393B1/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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type

Definitions

  • the invention relates to a unit actuated by pressure medium according to the preamble of claim 1.
  • Pressure-actuated units are usually used to support a component in an operating movement.
  • the component can be exposed to external stress.
  • a stabilizer assembly can perform a pivotal movement, but is additionally exposed to a compression movement of the wheels of an axle of a load that is significantly higher frequency than the rolling motion of a vehicle body and thus the pressure changes in the pressure medium supply.
  • a swivel motor comprising a cylinder with axially inwardly extending ribs, the ends of two lids is closed, a motor shaft with vanes, which have the same axial extent as the ribs of the cylinder, the wings of the motor shaft and the ribs of the cylinder together forming with the cylinder, the covers and the motor shaft individual working chambers, a first and a second pressure medium connection for each two separated by a rib working chambers, a composite system between the working chambers, which connects at least pairwise working chambers, wherein the arrangement of the connected working chambers is designed such in that the working chambers, which are connected to the first pressure medium connection, alternate with those which are connected to the second pressure medium connection, wherein at least one working chamber is connected to a pressure compensating element.
  • the pressure compensation element is formed by a pressure limiting valve which opens in the direction of the working chamber with the lower working pressure, so that pressure medium can flow from at least one working chamber of
  • the pressure relief valve opens depending on the differential pressure between two working chambers different assignment. Due to a suspension movement of the wheel, a first working chamber relieved and the adjacent chamber to be compressed. If a differential pressure is exceeded, then opens the pressure relief valve, although the working pressure in the compressed working chamber has not yet reached a critical value. In the pressure relief valve opening behavior can not be distinguished between allowable peak pressure in the compressed working chamber and a momentary differential pressure between two adjacent working chambers.
  • Another proposed solution according to the DE 101 40 460 C1 consists in that the unit operated with pressure medium is connected to an external air cushion, which is intended to prevent cavitation in a working chamber.
  • Object of the present invention is to provide a solution for the negative effect of the pressure pulsation in a pressure medium actuated unit.
  • the object is achieved in that the pressure compensation element is formed by a compensation chamber which is divided by a movable separating element, wherein in each case a partial compensation chamber is connected to at least one working chamber of a pressure medium connection.
  • the great advantage of the invention is that both working chamber groups are separated from each other, but a lack of volume or volume surplus can be compensated within the unit without additional pressure medium must be moved from outside.
  • the compensation chamber is advantageously connected to the composite systems of both working chamber groups.
  • a Dämpfmediumband in a working chamber group can be compensated by a Nachêt in the other working chamber groups, for which only a common pressure compensation means is needed.
  • the separating element is formed by a rigid disk.
  • the separating element is held by oppositely acting springs in an initial position.
  • the composite system is formed by channels which terminate in a lateral surface of the compensation chamber and form a slide valve with the movable separating element.
  • the slide valve provides for a throttling of the pressure medium displaced by the separating element from the partial compensating chamber, so that no abrupt volume changes can occur in the partial compensating chambers and therefore also in the working chambers.
  • the separating element has a sleeve portion sliding on the lateral surface, which communicates with the end opening of the channels interacts.
  • the length of the sleeve section can be used to determine the size of the compensatable volume.
  • the separating element can overrun the end opening of the connecting channel at least almost completely and thus close it.
  • a return movement of the separating element is facilitated in the starting position, at least one Nachströmö réelle is executed in the sleeve portion, which is at least at the maximum closed position of the end opening with the end opening in coverage.
  • At least one non-return valve opening in the direction of the partial compensation chamber is arranged between at least one composite system and the partial compensation chamber connected thereto.
  • the check valve is designed in the separating element and is formed by the Nachströmö réelle, so there is only a small construction cost.
  • the Nachströmö réelle is directionally closed by a biased on the inside of the sleeve section sealing ring, which completes the check valve.
  • the Fig. 1 shows in conjunction with the Figures 2 and 3 a swivel motor 1 in longitudinal section whose basic structure is also assumed in the following figures.
  • the swivel motor 1 comprises a cylinder 3, on whose inner diameter axially extending ribs 5 are executed. Inside the cylinder 3, a motor shaft 7 is rotatably mounted. On the motor shaft wings 9 are arranged, which extend parallel to the ribs 5. End is the cylinder 3 of lids 11; 13 closed.
  • the motor shaft with its wings and the cylinder with its ribs together with the covers working chambers 15; 17, which are separated by disc seals 19 in the wings and ribs.
  • 19 For receiving the pressure jumps occurring in the working chambers 17 at a higher-frequency external loads; 19 is a pressure compensation element 37, which is formed by a compensation chamber 39, of a movable separating element 41 in two partial compensation spaces 39a; 39b is divided.
  • the partial compensation chamber 39a is connected to a working chamber group 15 of a pressure medium connection 33 and the partial compensation chamber 39b to the working chamber group 17 of the pressure medium connection 35.
  • the separating element 41 is formed by a slide with a disk-shaped base body and is provided by oppositely acting springs 43; 45 held in a starting position.
  • the compensation chamber 39 is connected to the composite system, channels 29; 31, both working chamber groups 15; 17 disposed within the motor shaft 7.
  • An end-side, sealed cover 47 closes the blind hole forming the compensation chamber 39 in the motor shaft 7.
  • the spring 43 is supported on the cover 47 and the spring 45 on the blind hole bottom.
  • the channels 29; 31 end in a lateral surface of the compensation chamber and form with their end openings together with the movable separating element in each case a slide valve 49; 51, which perform an opposing opening and closing movement.
  • a slide valve 49; 51 which perform an opposing opening and closing movement.
  • circumferential grooves 53; 55 incorporated, which allows a connection of the working chambers of a working chamber group 15 or 17 even when the slide valve is closed.
  • the separating element 41 has on the lateral surface of the compensation chamber 39 sliding sleeve sections 57; 59 on, with the end openings of the channels 29; 31 cooperate.
  • At an axial distance from the end face of the sleeve portions 57; 59 is at least one Nachströmö réelle 61; 63 Fig. 2 ; executed at the maximum closed position of the separating element with the end opening of the respective channel 29; 31 is in overlap.
  • channels 29; 31 and the partial compensation spaces 39a connected thereto; 39 b at least one non-return valve opening in the direction of the respective partial compensating chamber is arranged, which is separated from the at least one inflow opening 61; 63 in the sleeve sections 57; 59 of the separating element 41 is formed.
  • the Nachströmö réelle 61; 63 inside the sleeve portion 57; 59 of a preloaded sealing ring 65, Fig. 4 locked.
  • FIGS. 1 and 2 show the separating element 41 in a middle position when the pressure medium inflow into the one working chamber group is effective despite the pressure medium outflow with a corresponding back pressure in the other working chamber group.
  • the separating element 41 leads against the force z. B. the spring 45 from an axial displacement movement in the direction of the blind hole bottom.
  • pressure medium volume is displaced according to the cross section of the inner diameter of the compensation chamber 39b multiplied by the displacement of the separating element through the annular groove 55 into the channel 31 and thus into the working chambers 17, so that no negative pressure can occur.
  • a minor volume in one Working chamber group is compensated by the movement of the separating element in conjunction with an increase in volume of the other working chamber group in the region of the partial compensation chamber.
  • the sleeve portion 59 can overrun the annular groove 55 and reduce the cross over passage between the compensation chamber 39 b and the annular groove 55. In the end position, the sleeve portion 59 abuts with its end face 67 on a shoulder 69 of the compensation chamber 39b. If available, the Nachströmö réelle 63 is then in overlap with the annular groove 55. One can do without a Nachströmö réelle when z. B. a sufficiently large gap between the sleeve sections and the lateral surface of the expansion chamber provides.
  • the separator 41 can be moved back to the starting position due to the then still prevailing different spring forces of the two springs until the spring forces are in equilibrium.
  • the constant pressure supply of all working chambers and the throttled movement of the separating element ensure a silent pressure medium flow within the aggregate.

Abstract

The assembly i.e. oscillating motor (1) has a cylinder with axially running ribs that are closed at one side by two covers (11). Vanes of a motor shaft and the ribs form individual working chambers (17) in cooperation with the cylinder, the covers and the shaft. A connection system pair-wisely connects the working chambers, which are connected with a fluid medium supply. A pressure compensation element (37) is formed by a compensation chamber, which is subdivided by a movable separating element (41). Sections (39a, 39b) of the compensation chamber are connected with the working chambers.

Description

Die Erfindung betrifft ein mit Druckmittel betätigtes Aggregat gemäß dem Oberbegriff von Patentanspruch 1.The invention relates to a unit actuated by pressure medium according to the preamble of claim 1.

Druckmittel betätigte Aggregate werden in der Regel eingesetzt, um ein Bauteil in einer Betriebsbewegung zu unterstützen. Das Bauteil kann dabei einer äußeren Belastung ausgesetzt sein. Bei einem Aggregat in der Bauform eines Schwenkmotors z. B. in einem Fahrzeugfahrwerk kann eine Stabilisatoranordnung eine Schwenkbewegung ausführen, ist aber zusätzlich bei einer Einfederungsbewegung der Räder einer Achse einer Belastung ausgesetzt, die deutlich hochfrequenter ist, als die Wankbewegung eines Fahrzeugaufbaus und damit den Druckänderungen in der Druckmittelversorgung.Pressure-actuated units are usually used to support a component in an operating movement. The component can be exposed to external stress. In an aggregate in the design of a slewing motor z. As in a vehicle chassis, a stabilizer assembly can perform a pivotal movement, but is additionally exposed to a compression movement of the wheels of an axle of a load that is significantly higher frequency than the rolling motion of a vehicle body and thus the pressure changes in the pressure medium supply.

In der DE 10 2004 051 444 A1 wird diese Problematik der Pulsation des Druckmediums erläutert und als Lösung ein Schaumkörper vorgeschlagen, der in mindestens einer Arbeitskammer des Aggregats angeordnet ist. Mit dem Schaumkörper ist zumindest der Nachteil verbunden, dass der Betriebsweg des Weiteren ist dafür Sorge zu tragen, dass über die Lebensdauer des Aggregats keine Zersetzungserscheinungen auftreten, die Partikel von dem Schaumkörper freisetzen und die zu Verstopfungen im Aggregat oder im Druckversorgungssystem führen.In the DE 10 2004 051 444 A1 this problem of pulsation of the pressure medium is explained and proposed as a solution, a foam body which is arranged in at least one working chamber of the unit. At least the disadvantage associated with the foam body is that the operating path of the Furthermore, it must be ensured that over the life of the unit no decomposition phenomena occur that release particles from the foam body and lead to blockages in the unit or in the pressure supply system.

Aus der gattungsbildenden DE 10 2004 039 767 A1 ist ein Schwenkmotor bekannt, umfassend einen Zylinder mit axial am Innendurchmesser verlaufenden Rippen, der endseitig von zwei Deckeln verschlossen ist, eine Motorwelle mit Flügeln, die dieselbe axiale Erstreckung besitzen wie die Rippen des Zylinders, wobei die Flügel der Motorwelle und die Rippen des Zylinders zusammen mit dem Zylinder, den Deckeln und der Motorwelle einzelne Arbeitskammern bilden, einen ersten und einen zweiten Druckmediumanschluss für zwei jeweils durch eine Rippe getrennte Arbeitskammern, ein Verbundsystem zwischen den Arbeitskammern, das mindestens paarweise Arbeitskammern verbindet, wobei die Anordnung der verbundenen Arbeitskammern derart ausgeführt ist, dass die Arbeitskammern, die mit dem ersten Druckmediumanschluss verbunden sind, sich mit denen abwechseln, die mit dem zweiten Druckmediumanschluss verbunden sind, wobei mindestens eine Arbeitskammer mit einem Druckkompensationselement verbunden ist. Das Druckkompensationselement wird von einem Druckbegrenzungsventil gebildet, das in Richtung der Arbeitskammer mit dem geringeren Arbeitsdruck öffnet, so dass Druckmedium von mindestens einer Arbeitskammer einer ersten Gruppe in eine Arbeitskammer der zweiten Gruppe überströmen kann.From the generic DE 10 2004 039 767 A1 a swivel motor is known, comprising a cylinder with axially inwardly extending ribs, the ends of two lids is closed, a motor shaft with vanes, which have the same axial extent as the ribs of the cylinder, the wings of the motor shaft and the ribs of the cylinder together forming with the cylinder, the covers and the motor shaft individual working chambers, a first and a second pressure medium connection for each two separated by a rib working chambers, a composite system between the working chambers, which connects at least pairwise working chambers, wherein the arrangement of the connected working chambers is designed such in that the working chambers, which are connected to the first pressure medium connection, alternate with those which are connected to the second pressure medium connection, wherein at least one working chamber is connected to a pressure compensating element. The pressure compensation element is formed by a pressure limiting valve which opens in the direction of the working chamber with the lower working pressure, so that pressure medium can flow from at least one working chamber of a first group into a working chamber of the second group.

Das Druckbegrenzungsventil öffnet in Abhängigkeit des Differenzdrucks zwischen zwei Arbeitskammern unterschiedlicher Zuordnung. Aufgrund einer Federungsbewegung des Rades kann eine erste Arbeitskammer entlastet und die benachbarte Kammer komprimiert werden. Wird ein Differenzdruck unterschritten, dann öffnet das Druckbegrenzungsventil, obwohl der Arbeitsdruck in der komprimierten Arbeitskammer noch keinen kritischen Wert erreicht hat. Bei dem Druckbegrenzungsventil kann das Öffnungsverhalten nicht zwischen zulässigem Spitzendruck in der komprimierten Arbeitkammer und einem momentanen Differenzdruck zwischen zwei benachbarten Arbeitskammern nicht unterschieden werden.The pressure relief valve opens depending on the differential pressure between two working chambers different assignment. Due to a suspension movement of the wheel, a first working chamber relieved and the adjacent chamber to be compressed. If a differential pressure is exceeded, then opens the pressure relief valve, although the working pressure in the compressed working chamber has not yet reached a critical value. In the pressure relief valve opening behavior can not be distinguished between allowable peak pressure in the compressed working chamber and a momentary differential pressure between two adjacent working chambers.

Eine weiterer Lösungsvorschlag gemäß der DE 101 40 460 C1 besteht darin, dass das mit Druckmittel betriebene Aggregat mit einem externen Luftpolster verbunden ist, das eine Kavitation in einer Arbeitskammer verhindern soll.Another proposed solution according to the DE 101 40 460 C1 consists in that the unit operated with pressure medium is connected to an external air cushion, which is intended to prevent cavitation in a working chamber.

Aufgabe der vorliegenden Erfindung ist es eine Lösung für die negative Wirkung der Druckpulsation in einem Druckmittel betätigten Aggregat bereitzustellen.Object of the present invention is to provide a solution for the negative effect of the pressure pulsation in a pressure medium actuated unit.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass das Druckkompensationselement von einem Ausgleichsraum gebildet wird, der von einem beweglichen Trennelement unterteilt wird, wobei jeweils ein Teilausgleichsraum mit mindestens einer Arbeitskammer eines Druckmediumanschlusses verbunden ist.According to the invention the object is achieved in that the pressure compensation element is formed by a compensation chamber which is divided by a movable separating element, wherein in each case a partial compensation chamber is connected to at least one working chamber of a pressure medium connection.

Der große Vorteil der Erfindung besteht darin, dass beide Arbeitskammergruppen voneinander getrennt sind, jedoch ein Volumenmangel oder Volumenüberschuss innerhalb des Aggregats ausgeglichen werden kann, ohne dass von Außen Druckmedium zusätzlich bewegt werden muss.The great advantage of the invention is that both working chamber groups are separated from each other, but a lack of volume or volume surplus can be compensated within the unit without additional pressure medium must be moved from outside.

Dabei ist der Ausgleichsraum vorteilhafterweise an die Verbundsysteme beider Arbeitskammergruppen angeschlossen. Ein Dämpfmediummangel in einer Arbeitskammergruppe kann durch eine Nachförderung in die anderen Arbeitskammergruppen kompensiert werden, wofür nur ein gemeinsames Druckkompensationsmittel benötigt wird.In this case, the compensation chamber is advantageously connected to the composite systems of both working chamber groups. A Dämpfmediummangel in a working chamber group can be compensated by a Nachförderung in the other working chamber groups, for which only a common pressure compensation means is needed.

Im Hinblick auf ein insgesamt kompakt bauendes Aggregat ist der Ausgleichsraum innerhalb der Motorwelle ausgeführt.With regard to an overall compactly built aggregate of the compensation chamber is carried out within the motor shaft.

Gemäß einem Unteranspruch wird das Trennelement von einer starren Scheibe gebildet.According to a subclaim, the separating element is formed by a rigid disk.

Für ein definiertes Druckverhalten in den Arbeitskammern wird das Trennelement von entgegengesetzt wirksamen Federn in einer Ausgangsstellung gehalten.For a defined pressure behavior in the working chambers, the separating element is held by oppositely acting springs in an initial position.

Das Verbundsystem wird von Kanälen gebildet, die in einer Mantelfläche des Ausgleichsraums enden und mit dem beweglichen Trennelement ein Schieberventil bilden. Das Schieberventil sorgt für eine Drosselung des von dem Trennelement aus dem Teilausgleichsraum verdrängten Druckmediums, so dass bei den Teilausgleichsräumen und damit auch bei den Arbeitskammern keine schlagartigen Volumenänderungen auftreten können.The composite system is formed by channels which terminate in a lateral surface of the compensation chamber and form a slide valve with the movable separating element. The slide valve provides for a throttling of the pressure medium displaced by the separating element from the partial compensating chamber, so that no abrupt volume changes can occur in the partial compensating chambers and therefore also in the working chambers.

In weiterer vorteilhafter Ausgestaltung weist das Trennelement einen auf der Mantelfläche gleitenden Hülsenabschnitt auf, der mit der Endöffnung der Kanäle zusammenwirkt. Durch die Länge des Hülsenabschnitts kann die Größe des kompensierbaren Volumens bestimmt werden.In a further advantageous embodiment, the separating element has a sleeve portion sliding on the lateral surface, which communicates with the end opening of the channels interacts. The length of the sleeve section can be used to determine the size of the compensatable volume.

Das Trennelement kann die Endöffnung des Verbindungskanals zumindest nahezu vollständig überfahren und damit verschließen. Damit eine Rückstellbewegung des Trennelements in die Ausgangsstellung erleichtert wird, ist in dem Hülsenabschnitt mindestens eine Nachströmöffnung ausgeführt, die zumindest bei maximaler Schließstellung der Endöffnung mit der Endöffnung in Überdeckung steht.The separating element can overrun the end opening of the connecting channel at least almost completely and thus close it. Thus, a return movement of the separating element is facilitated in the starting position, at least one Nachströmöffnung is executed in the sleeve portion, which is at least at the maximum closed position of the end opening with the end opening in coverage.

Eine einfache Nachströmöffnung wirkt sich auf die Drosselwirkung des Schieberventils aus. Um diesen Effekt zu minimieren ist zwischen mindestens einem Verbundsystem und dem daran angeschlossenen Teilausgleichsraum mindestens ein in Richtung des Teilausgleichsraums öffnendes Rückschlagventil angeordnet.A simple Nachströmöffnung affects the throttle effect of the slide valve. In order to minimize this effect, at least one non-return valve opening in the direction of the partial compensation chamber is arranged between at least one composite system and the partial compensation chamber connected thereto.

Das Rückschlagventil ist in dem Trennelement ausgeführt und wird von der Nachströmöffnung gebildet, so nur ein geringer Bauaufwand besteht.The check valve is designed in the separating element and is formed by the Nachströmöffnung, so there is only a small construction cost.

Die Nachströmöffnung wird von einem innenseitig am Hülsenabschnitt vorgespannten Dichtring richtungsabhängig verschlossen, der das Rückschlagventil vervollständigt.The Nachströmöffnung is directionally closed by a biased on the inside of the sleeve section sealing ring, which completes the check valve.

Anhand der folgenden Figurenbeschreibung soll die Erfindung näher erläutert werden.The invention will be explained in more detail with reference to the following description of the figures.

Es zeigt:

Fig. 1
Längsschnitt durch das Aggregat im Bereich der Arbeitskammern
Fig. 2
Längsschnitt durch das Aggregat im Bereich der Dichtungen zwischen den Arbeitskammern
Fig. 3
Querschnitt durch das Aggregat im Bereich des Druckkompensationselements
Fig. 4
Teilausschnitt des Druckkompensationselements
It shows:
Fig. 1
Longitudinal section through the unit in the area of the working chambers
Fig. 2
Longitudinal section through the unit in the area of the seals between the working chambers
Fig. 3
Cross section through the unit in the area of the pressure compensation element
Fig. 4
Part of the pressure compensation element

Die Fig. 1 zeigt in Verbindung mit den Figuren 2 und 3 einen Schwenkmotor 1 im Längsschnitt dessen prinzipieller Aufbau auch bei den nachfolgenden Figuren vorausgesetzt wird. Der Schwenkmotor 1 umfasst einen Zylinder 3, an dessen Innendurchmesser axial verlaufende Rippen 5 ausgeführt sind. Innerhalb des Zylinders 3 ist eine Motorwelle 7 drehbeweglich gelagert. Auf der Motorwelle sind Flügel 9 angeordnet, die sich parallel zu den Rippen 5 erstrecken. Endseitige wird der Zylinder 3 von Deckeln 11; 13 verschlossen. Die Motorwelle mit ihren Flügeln und der Zylinder mit seinen Rippen bilden zusammen mit den Deckeln Arbeitskammern 15; 17, die durch Scheibendichtungen 19 in den Flügeln und Rippen voneinander getrennt sind. Des Weiteren sind in Ringräumen 21; 23 der Deckel 11; 13 Wellendichtungen 25; 27 gekammert, die einen Austritt von Druckmedium aus den Arbeitskammern 15; 17 verhindern. Jeweils zwischen den Arbeitskammern 15 und 17 besteht ein Verbundsystem aus Kanälen 29; 31 in der Motorwelle 7. Ein erster Druckmediumanschluss 33 versorgt über den Kanal 29 die Arbeitskammern 15 und ein zweiter Druckmediumanschluss 35 erfüllt diese Funktion über den Kanal 31 für die Arbeitskammern 17. In den jeweils miteinander verbundenen Arbeitskammern herrscht ein gleiches Druckniveau. Durch Zu- oder Abfluss von Druckmedium über die Druckmediumanschlüsse 33; 35 übt der Schwenkmotor ein Drehmoment aus, das z. B. zur Verstellung eines geteilten Stabilisators innerhalb eines Fahrwerks für ein Kraftfahrzeug genutzt wird.The Fig. 1 shows in conjunction with the Figures 2 and 3 a swivel motor 1 in longitudinal section whose basic structure is also assumed in the following figures. The swivel motor 1 comprises a cylinder 3, on whose inner diameter axially extending ribs 5 are executed. Inside the cylinder 3, a motor shaft 7 is rotatably mounted. On the motor shaft wings 9 are arranged, which extend parallel to the ribs 5. End is the cylinder 3 of lids 11; 13 closed. The motor shaft with its wings and the cylinder with its ribs together with the covers working chambers 15; 17, which are separated by disc seals 19 in the wings and ribs. Furthermore, in annular spaces 21; 23, the lid 11; 13 shaft seals 25; 27 chambered, the outlet of pressure medium from the working chambers 15; 17 prevent. Between each of the working chambers 15 and 17 there is a composite system of channels 29; 31 in the motor shaft 7. A first pressure medium connection 33 supplies via the channel 29, the working chambers 15 and a second pressure medium connection 35 fulfills this function via the channel 31 for the working chambers 17. In each interconnected working chambers there is a same pressure level. By inflow or outflow of pressure medium via the pressure medium connections 33; 35, the swivel motor exerts a torque that z. B. is used for adjusting a split stabilizer within a chassis for a motor vehicle.

Zur Aufnahme der bei einer höherfrequenten äußeren Belastungen auftretenden Drucksprüngen in den Arbeitskammern 17; 19 dient ein Druckkompensationselement 37, das von einem Ausgleichsraum 39 gebildet wird, der von einem beweglichen Trennelement 41 in zwei Teilausgleichsräume 39a; 39b unterteilt wird. Der Teilausgleichsraum 39a ist mit einer Arbeitskammergruppe 15 eines Druckmediumanschlusses 33 und der Teilausgleichsraum 39b mit der Arbeitskammergruppe 17 des Druckmediumanschlusses 35 verbunden.For receiving the pressure jumps occurring in the working chambers 17 at a higher-frequency external loads; 19 is a pressure compensation element 37, which is formed by a compensation chamber 39, of a movable separating element 41 in two partial compensation spaces 39a; 39b is divided. The partial compensation chamber 39a is connected to a working chamber group 15 of a pressure medium connection 33 and the partial compensation chamber 39b to the working chamber group 17 of the pressure medium connection 35.

Das Trennelement 41 wird von einem Schieber mit einem scheibenförmigen Grundkörper gebildet und wird von entgegengesetzt wirksamen Federn 43; 45 in einer Ausgangsstellung gehalten. Der Ausgleichsraum 39 ist an das Verbundsystem, Kanäle 29; 31, beider Arbeitskammergruppen 15; 17 innerhalb der Motorwelle 7 angeordnet. Ein endseitiger, abgedichteter Deckel 47 verschließt die den Ausgleichsraum 39 bildenden Sacklochbohrung in der Motorwelle 7. Die Feder 43 stützt sich an dem Deckel 47 und die Feder 45 an dem Sacklochgrund ab.The separating element 41 is formed by a slide with a disk-shaped base body and is provided by oppositely acting springs 43; 45 held in a starting position. The compensation chamber 39 is connected to the composite system, channels 29; 31, both working chamber groups 15; 17 disposed within the motor shaft 7. An end-side, sealed cover 47 closes the blind hole forming the compensation chamber 39 in the motor shaft 7. The spring 43 is supported on the cover 47 and the spring 45 on the blind hole bottom.

Die Kanäle 29; 31 enden in einer Mantelfläche des Ausgleichsraums und bilden mit Ihren Endöffnungen zusammen mit dem beweglichen Trennelement jeweils ein Schieberventil 49; 51, die eine gegensinnige Öffnungs- und Schließbewegung ausführen. In der Mantelfläche sind umlaufende Nuten 53; 55 eingearbeitet, die auch bei geschlossenem Schieberventil eine Verbindung der Arbeitskammern einer Arbeitskammergruppe 15 oder 17 ermöglicht.The channels 29; 31 end in a lateral surface of the compensation chamber and form with their end openings together with the movable separating element in each case a slide valve 49; 51, which perform an opposing opening and closing movement. In the lateral surface are circumferential grooves 53; 55 incorporated, which allows a connection of the working chambers of a working chamber group 15 or 17 even when the slide valve is closed.

Das Trennelement 41 weist auf der Mantelfläche des Ausgleichsraums 39 gleitenden Hülsenabschnitte 57; 59 auf, die mit den Endöffnungen der Kanäle 29; 31 zusammenwirken. In einem axialen Abstand zur Stirnfläche der Hülsenabschnitte 57; 59 ist mindestens eine Nachströmöffnung 61; 63, Fig. 2; ausgeführt, die bei maximaler Schließstellung des Trennelements mit der Endöffnung des jeweiligen Kanals 29; 31 in Überdeckung steht.The separating element 41 has on the lateral surface of the compensation chamber 39 sliding sleeve sections 57; 59 on, with the end openings of the channels 29; 31 cooperate. At an axial distance from the end face of the sleeve portions 57; 59 is at least one Nachströmöffnung 61; 63 Fig. 2 ; executed at the maximum closed position of the separating element with the end opening of the respective channel 29; 31 is in overlap.

Zwischen dem Verbundsystem, Kanäle 29; 31 und den daran angeschlossenen Teilausgleichsräumen 39a; 39b ist mindestens ein in Richtung des jeweiligen Teilausgleichsraums öffnendes Rückschlagventil angeordnet, das von der mindestens einen Nachströmöffnung 61; 63 in den Hülsenabschnitten 57; 59 des Trennelements 41 gebildet wird. Dabei wird die Nachströmöffnung 61; 63 innenseitig am Hülsenabschnitt 57; 59 von einem vorgespannten Dichtring 65, Fig. 4, verschlossen.Between the composite system, channels 29; 31 and the partial compensation spaces 39a connected thereto; 39 b, at least one non-return valve opening in the direction of the respective partial compensating chamber is arranged, which is separated from the at least one inflow opening 61; 63 in the sleeve sections 57; 59 of the separating element 41 is formed. In this case, the Nachströmöffnung 61; 63 inside the sleeve portion 57; 59 of a preloaded sealing ring 65, Fig. 4 , locked.

Die Figuren 1 und 2 zeigen das Trennelement 41 in einer mittleren Stellung, wenn der Druckmediumzufluss in die eine Arbeitskammergruppe trotz des Druckmediumabflusses mit einem entsprechenden Gegendruck in der anderen Arbeitskammergruppe wirksam ist. Insbesondere bei einem plötzlichen Druckabfall in einer Arbeitskammergruppe führt das Trennelement 41 gegen die Kraft z. B. der Feder 45 eine axiale Verschiebebewegung in Richtung des Sacklochgrundes aus. Dabei wird Druckmediumvolumen entsprechend dem Querschnitt des Innendurchmessers des Ausgleichsraums 39b multipliziert mit dem Verschiebeweg des Trennelements durch die Ringnut 55 in den Kanal 31 und damit in die Arbeitskammern 17 verdrängt, so dass kein Unterdruckauftreten kann. Ein Mindervolumen in einer Arbeitskammergruppe wird durch die Bewegung des Trennelements in Verbindung mit einer Volumenvergrößerung der anderen Arbeitskammergruppe im Bereich des Teilausgleichsraums kompensiert.The FIGS. 1 and 2 show the separating element 41 in a middle position when the pressure medium inflow into the one working chamber group is effective despite the pressure medium outflow with a corresponding back pressure in the other working chamber group. In particular, in a sudden pressure drop in a working chamber group, the separating element 41 leads against the force z. B. the spring 45 from an axial displacement movement in the direction of the blind hole bottom. In this case, pressure medium volume is displaced according to the cross section of the inner diameter of the compensation chamber 39b multiplied by the displacement of the separating element through the annular groove 55 into the channel 31 and thus into the working chambers 17, so that no negative pressure can occur. A minor volume in one Working chamber group is compensated by the movement of the separating element in conjunction with an increase in volume of the other working chamber group in the region of the partial compensation chamber.

Der Hülsenabschnitt 59 kann die Ringnut 55 überfahren und den Übertrittquerschnitt zwischen dem Ausgleichsraum 39b und der Ringnut 55 reduzieren. In der Endposition steht der Hülsenabschnitt 59 mit seiner Stirnfläche 67 an einem Absatz 69 des Ausgleichsraums 39b an. Sofern vorhanden, steht die Nachströmöffnung 63 dann in Überdeckung mit der Ringnut 55. Man kann auf eine Nachströmöffnung verzichten, wenn man z. B. ein ausreichend großes Spaltmaß zwischen den Hülsenabschnitten und der Mantelfläche des Ausgleichsraums vorsieht.The sleeve portion 59 can overrun the annular groove 55 and reduce the cross over passage between the compensation chamber 39 b and the annular groove 55. In the end position, the sleeve portion 59 abuts with its end face 67 on a shoulder 69 of the compensation chamber 39b. If available, the Nachströmöffnung 63 is then in overlap with the annular groove 55. One can do without a Nachströmöffnung when z. B. a sufficiently large gap between the sleeve sections and the lateral surface of the expansion chamber provides.

Wenn der plötzliche Druckunterschied kompensiert ist, dann kann das Trennelement 41 aufgrund der dann noch vorherrschenden unterschiedlichen Federkräfte der beiden Federn in die Ausgangsposition zurückbewegt werden, bis auch die Federkräfte im Gleichgewicht stehen. Die ständige Druckversorgung aller Arbeitskammern und die gedrosselte Bewegung des Trennelements sorgen für einen geräuschlosen Druckmediumfluss innerhalb des Aggregats.If the sudden pressure difference is compensated, then the separator 41 can be moved back to the starting position due to the then still prevailing different spring forces of the two springs until the spring forces are in equilibrium. The constant pressure supply of all working chambers and the throttled movement of the separating element ensure a silent pressure medium flow within the aggregate.

Claims (12)

Druckmittel betätigtes Aggregat, insbesondere Schwenkmotor, umfassend einen Zylinder mit axial am Innendurchmesser verlaufenden Rippen, der endseitig von zwei Deckeln verschlossen ist, eine Motorwelle mit Flügeln, die dieselbe axiale Erstreckung besitzen wie die Rippen des Zylinders, wobei die Flügel der Motorwelle und die Rippen des Zylinders zusammen mit dem Zylinder, den Deckeln und der Motorwelle einzelne Arbeitskammern bilden, einen ersten und einen zweiten Druckmediumanschluss für zwei jeweils durch eine Rippe getrennte Arbeitskammern, ein Verbundsystem zwischen den Arbeitskammern, das mindestens paarweise Arbeitskammern verbindet, wobei die Anordnung der verbundenen Arbeitskammern derart ausgeführt ist, dass die Arbeitskammern, die mit dem ersten Druckmediumanschluss verbunden sind, sich mit denen abwechseln, die mit dem zweiten Druckmediumanschluss verbunden sind, wobei mindestens zwei Arbeitskammer unterschiedlicher Zuordnung der Druckmediumanschlüsse mit einem Druckkompensationselement verbunden sind,
dadurch gekennzeichnet,
dass das Druckkompensationselement (37) von einem Ausgleichsraum (39) gebildet wird, der von einem beweglichen Trennelement (41) unterteilt wird, wobei jeweils ein Teilausgleichsraum (39a; 39b) mit mindestens einer Arbeitskammer (15; 17) eines Druckmediumanschlusses (33; 35) verbunden ist.Pressure-actuated unit, in particular a swing motor, comprising a cylinder with axially inwardly extending ribs, the end of two lids is closed, a motor shaft with vanes, which have the same axial extent as the ribs of the cylinder, the wings of the motor shaft and the ribs of the Cylinder together with the cylinder, the covers and the motor shaft forming individual working chambers, a first and a second pressure medium connection for two each separated by a rib working chambers, a composite system between the working chambers, which connects at least pairwise working chambers, wherein the arrangement of the connected working chambers carried out in such a way in that the working chambers, which are connected to the first pressure medium connection, alternate with those which are connected to the second pressure medium connection, wherein at least two working chamber different assignment of the Pressure medium connections are connected to a pressure compensation element,
characterized,
in that the pressure compensation element (37) is formed by a compensation chamber (39) which is subdivided by a movable separating element (41), one partial compensation chamber (39a, 39b) being provided with at least one working chamber (15; 17) of a pressure medium connection (33; ) connected is. Aggregat nach Anspruch 1,
dadurch gekennzeichnet,
dass der Ausgleichsraum (39) an die Verbundsysteme beider Arbeitskammergruppen (15; 17) angeschlossen ist.Aggregate according to Claim 1,
characterized,
that the compensation chamber (39) is connected to the composite systems of both working chamber groups (15; 17). Aggregat nach Anspruch 1,
dadurch gekennzeichnet,
dass der Ausgleichsraum (39) innerhalb der Motorwelle (7) ausgeführt ist.Aggregate according to Claim 1,
characterized,
in that the compensation space (39) is embodied inside the motor shaft (7). Aggregat nach Anspruch 1,
dadurch gekennzeichnet,
dass das Trennelement (41) von einer starren Scheibe gebildet wird.Aggregate according to Claim 1,
characterized,
in that the separating element (41) is formed by a rigid disk. Aggregat nach Anspruch 2,
dadurch gekennzeichnet,
dass das Verbundsystem von Kanälen (29; 31) gebildet wird, die in einer Mantelfläche des Ausgleichsraums (39) enden und mit dem beweglichen Trennelement (41) ein Schieberventil (49; 51) bilden.Aggregate according to claim 2,
characterized,
in that the composite system is formed by channels (29; 31) which terminate in a lateral surface of the compensation chamber (39) and form a slide valve (49; 51) with the movable separating element (41). Aggregat nach Anspruch 1,
dadurch gekennzeichnet,
dass das Trennelement (41) von entgegengesetzt wirksamen Federn (43; 45) in einer Ausgangsstellung gehalten wird.Aggregate according to Claim 1,
characterized,
in that the separating element (41) is held in a starting position by oppositely acting springs (43; 45). Aggregat nach Anspruch 5,
dadurch gekennzeichnet,
dass das Trennelement (41) einen auf der Mantelfläche gleitenden Hülsenabschnitt (57; 59) aufweist, der mit der Endöffnung der Kanäle (29; 31) zusammenwirkt.Aggregate according to Claim 5,
characterized,
in that the separating element (41) has a sleeve section (57, 59) which slides on the lateral surface and which cooperates with the end opening of the channels (29, 31). Aggregat nach Anspruch 7,
dadurch gekennzeichnet,
dass in dem Hülsenabschnitt (57; 59) mindestens eine Nachströmöffnung (61; 63) ausgeführt ist, die zumindest bei maximaler Schließstellung der Endöffnung mit der Endöffnung in Überdeckung steht.Aggregate according to claim 7,
characterized,
in that the sleeve section (57; 59) at least one flow opening (61; 63) is constructed that is at least at the maximum closing position of the end opening with the end opening into register. Aggregat nach Anspruch 2,
dadurch gekennzeichnet,
dass zwischen mindestens einem Verbundsystem (29; 31) und dem daran angeschlossenen Teilausgleichsraum (39a; 39b) mindestens ein in Richtung des Teilausgleichsraums (39a; 39b) öffnendes Rückschlagventil angeordnet ist.Aggregate according to claim 2,
characterized,
in that at least one non-return valve opening in the direction of the partial compensation chamber (39a, 39b) is arranged between at least one composite system (29, 31) and the partial compensation chamber (39a, 39b) connected thereto. Aggregat nach Anspruch 9,
dadurch gekennzeichnet,
dass das Rückschlagventil in dem Trennelement (41) ausgeführt ist.Aggregate according to claim 9,
characterized,
that the check valve is embodied in the partition member (41). Aggregat nach Anspruch 10,
dadurch gekennzeichnet,
dass das Rückschlagventil von der Nachströmöffnung (61; 63) gebildet wird.Aggregate according to claim 10,
characterized,
that the check valve of the flow opening (61; 63) is formed. Aggregat nach Anspruch 10,
dadurch gekennzeichnet,
dass die Nachströmöffnung (61; 63) von einem innenseitig am Hülsenabschnitt (57; 59) vorgespannten Dichtring (63) richtungsabhängig verschlossen wird.Aggregate according to claim 10,
characterized,
in that the inflow opening (61, 63) is closed in a direction-dependent manner by a sealing ring (63) pretensioned on the inside of the sleeve section (57; 59).
EP08001157A 2007-02-01 2008-01-23 Oscillating vane actuator Not-in-force EP1953393B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007005839A DE102007005839A1 (en) 2007-02-01 2007-02-01 Pressure medium actuated unit

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EP1953393A2 true EP1953393A2 (en) 2008-08-06
EP1953393A3 EP1953393A3 (en) 2011-04-20
EP1953393B1 EP1953393B1 (en) 2012-08-08

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Also Published As

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DE102007005839A1 (en) 2008-08-07
US7866253B2 (en) 2011-01-11
US20080185796A1 (en) 2008-08-07
EP1953393A3 (en) 2011-04-20
EP1953393B1 (en) 2012-08-08

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