EP1614905B1 - Vane-type motor - Google Patents

Vane-type motor Download PDF

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Publication number
EP1614905B1
EP1614905B1 EP05013073A EP05013073A EP1614905B1 EP 1614905 B1 EP1614905 B1 EP 1614905B1 EP 05013073 A EP05013073 A EP 05013073A EP 05013073 A EP05013073 A EP 05013073A EP 1614905 B1 EP1614905 B1 EP 1614905B1
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EP
European Patent Office
Prior art keywords
vane
pressure
cylinder
motor shaft
type motor
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.)
Not-in-force
Application number
EP05013073A
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German (de)
French (fr)
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EP1614905A3 (en
EP1614905A2 (en
Inventor
Matthias Reuss
Stefan Schiffler
Andreas Schlüter
Katrin Zietsch-Prior
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ZF Friedrichshafen AG
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ZF Friedrichshafen AG
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Publication of EP1614905A2 publication Critical patent/EP1614905A2/en
Publication of EP1614905A3 publication Critical patent/EP1614905A3/en
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Publication of EP1614905B1 publication Critical patent/EP1614905B1/en
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Classifications

    • 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 generic DE 102 43 696 B3 describes a swivel motor comprising a cylinder filled with a pressure medium with at least one rib on its inner wall, wherein within the cylinder a motor shaft is pivotally mounted with at least one wing, wherein within at least two annular spaces between the cylinder and the motor shaft is present a pressure-biasing seal assembly, which, together with disc seals within the wings and the ribs, seals a working chamber formed by the cylinder with the rib and the motor shaft and the wing together with end caps of the cylinder, the annular spaces being interconnected via a pressure equalizing channel.
  • the purpose of the pressure compensation channel is that can accumulate in the annular spaces for the seal assemblies no pressure medium with different pressure levels, which generate a longitudinal force between the cylinder and the motor shaft.
  • Object of the present invention is to realize a further structural design for at least one pressure equalization channel within a swing motor
  • the transverse openings are intended to discharge the pressure in the annular spaces via the pressure equalization channel into a working space.
  • the Sall Anlagene take over the function of a check valve by preventing a direct flow connection between work spaces different instantaneous pressure depending on the direction of flow.
  • the disk seal is made of an annular sealing body in conjunction with a core piece, wherein the sealing body at least a connection opening between its outer and its inner wall and a gap between the disc seal and a 39°lluber is connected to the connection opening, so that the gap forms together with the connection opening the pressure equalization channel.
  • the advantage of this embodiment is that only a very short pressure equalization channel must be formed in the sealing body. The largest part of the pressure equalization channel results from the said gap.
  • the disc seal consists of a sprayable PTFE material. So far, a sealing frame of the disc seal were peeled from a PTFE block and then provided by punching and / or mechanical machining with the desired contour. The size and the lack of inherent stability of the sealing frame complicate the achievable accuracy of the sealing frame. Furthermore, the punching waste is very large in a PTFE disc seal. With the sprayed variant, a variety of contours can be produced.
  • the Fig. 1 shows an assembly in the form of a swing motor 1 in a longitudinal sectional view with a cylinder 3, in which a motor shaft 5 is rotatably mounted. With the cylinder 3 end lid 7 and 9 are welded. On the inner wall 11 of the cylinder 3 are two ribs 13 (FIG. Fig. 2 ) arranged with wings 15 of the motor shaft 5, the cylinder 3 and the covers 7; 9 four working chambers 17; Form 19, wherein working chambers with the same reference numeral via a pressure medium distribution system starting from hydraulic ports 21; 23 and transverse channels 25; 27 are interconnected within the motor shaft. The number of working chambers depends on the torque to be applied and on the required swivel angle of the slewing motor.
  • seals 31; 33 inserted in the design of disc seals, each of which separate adjacent working chambers.
  • Both covers 7; 9 form together with the motor shaft 5 annular spaces 37; 39, the seal assemblies 41; 43 for sealing the working chambers 17; 19 record.
  • pressurizing a common group of working chambers, e.g. B. 17 and a relatively smaller pressure in the working chambers 19 is a very low flow of oil into the annular spaces 37; Pressed 39, as set by the different pressure from the working chambers in the circumferential direction a slight deformation of the seal assembly and thus pressure medium from the working chambers 17 at a high pressure in the annular spaces 37, 39 penetrates.
  • the pressure medium volume occurring in particular at low working chamber pressures after high pressure phases are comparatively very small, but it could happen that z. B.
  • annular space 37 a larger momentary pressure of the pressure medium prevails as in the annular space 39. So that no axially effective displacement forces between the cylinder 3 with the covers 7, 9 and the motor shaft 5 occur, both annular spaces 37; 39 via a pressure equalization channel 45, s. Fig. 3 , connected with each other.
  • the pressure equalization channel is at least part of the length of the disk seals 31; 33 formed, which are arranged in a groove of the wing and / or the rib.
  • the pressure compensation channel is formed by a groove extending in the longitudinal direction of the window seal.
  • the Fig. 4 shows a non-inventive swing motor 1 in the basic design according to Fig. 1 , Deviating, the annular spaces 37; 39 via radial duct 51 connected to the pressure equalization channel 45, as in the Fig. 5 is shown enlarged.
  • the radial channels are z. B. formed by a coinage. This allows the pressure equalization channel 45 are dimensioned in the seal with a comparatively large cross-section, as a desired throttling function is generated within the pressure equalization channel of the embossing.
  • the Fig. 6 shows a detailed view of a window seal 31; 33 inside a groove.
  • the disk seal 31 comprises a sealing frame 53 in conjunction with a plurality of juxtaposed axially and radially elastic Rud Gires 55. Both sides arranged Sus 57; 59 complete the window seals.
  • the swivel motor according to Fig. 7 corresponds to the design of the pressure compensation channel 45 of the design Fig. 4 , Deviating is, as from the Fig. 8 it can be seen, the pressure-equalizing channel 45 is executed only on a lower and an upper side of the disk seal 31.
  • the window seal is, as from the synopsis of Figures 7; 9; 10 and 11 can be seen, at least one transverse opening 65 executed according to the invention.
  • the transverse opening 65 may extend over the entire width of the window seal and is defined by the side fills 57; 59 closed depending on the direction of flow.
  • the sealing frame 53 is possibly pressed together with the filling pieces 55 onto the side filling piece 59, which is supported on the right-hand groove side wall.
  • Within the pressure equalization channel 45 is about the same pressure as in the working chamber 17.
  • the filler 59 floats between the right groove side wall and the sealing frame with the filling pieces.
  • At a working pressure reduction in the annular spaces 37; 39 degraded pressure in the working chamber 19 before the sealing frame moves with the filler pieces also in the direction of the left groove side wall.
  • the filling pieces 57; 59 prevent a direct cross-connection between the working chambers 17; 19th
  • FIG. 12 to 15 another embodiment of the invention will be presented, in which the disk seal from an annular sealing body, for. B. in the embodiment of a sealing frame 53 according to the Fig. 6 , in connection with a core piece or filler 55 is performed, wherein the sealing body 53 has at least one connecting opening 69 between its outer and its inner wall, via the radial passage 47 with the annular spaces 37; 39 is connected.
  • the width of the groove within the vane or rib for the disc seal is greater than that formed by the side vents and the sealing frame together with the patches Stratification.
  • the connection opening extends only in a very short way and can be carried out with comparatively little effort in the sealing body. If the gap 71 forms between the groove side wall and a 39glall Cluster, then the pressure equalization channel can also be connected to the respective working chamber.
  • the Fig. 16 to 19 describe a disk seal 31; 33, which is used inter alia in a swivel motor according to the aforementioned figures.
  • the window seal 31; 33 has a double-T cross-sectional profile, which consists entirely of a, in particular sprayable PTFE material.
  • sprayable PTFE material is exemplified in the DE 41 12 248 A1 or DE 196 19 232 A1 , directed.
  • the transverse webs and the vertical web can assume such a width that for a reasonable groove width in the ribs and wings no 18.
  • Biasing means are arranged laterally from the vertical web between the transverse webs of the double-T cross-sectional profile of the disk seal, for example radially and / or axially elastic spring disks. Also, the end surfaces 61; 63 of the disc seal extending over the width of the transverse webs, so that on both sides of the vertical web pockets are present in which the spring washers 55 are clamped and during assembly can not fall out.
  • the transverse webs are provided in the direction of Nutenseitedon with a profile 77.
  • the profile consists of a number of recesses which have no connection to the axially extending pressure equalization channel 45.
  • the recesses serve to allow pressure fluid to flow into the grooves for the disc seal within the ribs and wings, so that the pressure medium pressure-dependent supports the bias on the disc seal.

Abstract

The pivot motor incorporates a channel which is formed at least partly by grooves of the sealing elements (31, 33) located respectively in a shaft wing (15) and in a cylinder rib (13), and serves for pressure equalization between two annular spaces in the motor housing.

Description

Die gattungsbildende DE 102 43 696 B3 beschreibt einen Schwenkmotor, umfassend einen mit einem Druckmittel gefüllten Zylinder mit mindestens einer Rippe an seiner Innenwandung, wobei innerhalb des Zylinders eine Motorwelle mit mindestens einem Flügel schwenkbar gelagert ist, wobei innerhalb von mindestens zwei Ringräumen zwischen dem Zylinder und der Motorwelle eine druckvorspannbare Dichtungsanordnung vorliegt, die zusammen mit Scheibendichtungen innerhalb der flügel und der Rippen eine Arbeitskammer abdichtet, welche von dem Zylinder mit der Rippe und der Motorwelle und dem Flügel zusammen mit endseitigen Deckeln des Zylinders gebildet wird, wobei die Ringräume über einen Druckausgleichskanal miteinander verbunden sind. Der Sinn des Druckausgleichskanals besteht darin, dass sich in den Ringräumen für die Dichtungsanordnungen keine Druckmittel mit unterschiedlichen Druckniveaus sammeln können, die eine Längskraft zwischen dem Zylinder und der Motorwelle erzeugen.The generic DE 102 43 696 B3 describes a swivel motor comprising a cylinder filled with a pressure medium with at least one rib on its inner wall, wherein within the cylinder a motor shaft is pivotally mounted with at least one wing, wherein within at least two annular spaces between the cylinder and the motor shaft is present a pressure-biasing seal assembly, which, together with disc seals within the wings and the ribs, seals a working chamber formed by the cylinder with the rib and the motor shaft and the wing together with end caps of the cylinder, the annular spaces being interconnected via a pressure equalizing channel. The purpose of the pressure compensation channel is that can accumulate in the annular spaces for the seal assemblies no pressure medium with different pressure levels, which generate a longitudinal force between the cylinder and the motor shaft.

Aufgabe der vorliegenden Erfindung ist es, eine weitere konstruktive Ausgestaltung für mindestens einen Druckausgleichskanal innerhalb eines Schwenkmotors zu realisieren,Object of the present invention is to realize a further structural design for at least one pressure equalization channel within a swing motor,

Erfindungsgemäß wird die Aufgabe bei einer ersten Variante durch die Merkmale des Patentanspruchs 1 gelöst.According to the invention, the object is achieved in a first variant by the features of patent claim 1.

Die Queröffnungen sollen den Druck in den Ringräumen über den Druckausgleichskanal in einen Arbeitsraum abführen. Die Seitenfüllstücke übernehmen dabei die Funktion eines Rückschlagventils, indem sie in Abhängigkeit der Anströmrichtung eine direkte Strömungsverbindung zwischen Arbeitsräumen unterschiedlichen Momentandrucks verhindern.The transverse openings are intended to discharge the pressure in the annular spaces via the pressure equalization channel into a working space. The Seitenfüllstücke take over the function of a check valve by preventing a direct flow connection between work spaces different instantaneous pressure depending on the direction of flow.

Prinzipiell ist es nicht einfach, eine Nut mit einer über die gesamte Breite vollständig ebene Nutgrundfläche zu fertigen. Übergangsradien zu den Nutseitenwänden sind notwendig, um Kerbspannungen zu vermeiden. Folglich können sich Lageungenauigkeiten der Seitenfüllstücke bezogen auf die Queröffnungen einstellen. Diese Probleme lassen sich dadurch umgehen, indem die Queröffnung im Bereich der dynamischen Dichtfläche der Scheibendichtung ausgeführt ist. Die dynamische Dichtfläche steht per Definition stets in Reibkontakt mit dem zur Scheibendichtung sich relativ beweglichen Bauteil.In principle, it is not easy to produce a groove with a groove surface which is completely flat over the entire width. Transition radii to the groove side walls are necessary to avoid notch stresses. As a result, positional inaccuracies of the side pockets may be adjusted with respect to the transverse openings. These problems can be circumvented by the transverse opening in the region of the dynamic sealing surface of the window seal is executed. The dynamic sealing surface is by definition always in frictional contact with the relative to the disk seal relatively movable component.

Bei einer Alternatiwariante ist die Scheibendichtung aus einem ringförmigen Dichtkörper in Verbindung mit einem Kernstück ausgeführt, wobei der Dichtkörper mindestens eine Verbindungsöffnung zwischen seiner Außen- und seinem Innenwandung aufweist und ein Spalt zwischen der Scheibendichtung und einem Seitenfüllstück an die Verbindungsöffnung angeschlossen ist, so dass der Spalt zusammen mit der Verbindungsöffnung den Druckausgleichskanal bildet.In an alternative variant, the disk seal is made of an annular sealing body in conjunction with a core piece, wherein the sealing body at least a connection opening between its outer and its inner wall and a gap between the disc seal and a Seitenfüllstück is connected to the connection opening, so that the gap forms together with the connection opening the pressure equalization channel.

Der Vorteil dieser Ausführungsform besteht darin, dass nur ein sehr kurzer Druckausgleichskanal in den Dichtkörper eingeformt werden muss. Der größte Teil des Druckausgleichskanals ergibt sich durch den besagten Spalt.The advantage of this embodiment is that only a very short pressure equalization channel must be formed in the sealing body. The largest part of the pressure equalization channel results from the said gap.

Ein wesentlicher Fertigungs- und Kostenvorteil ergibt sich dadurch, dass die Scheibendichtung aus einem spritzfähigen PTFE-Werkstoff besteht. Bislang wurden ein Dichtungsrahmen der Scheibendichtung aus einem PTFE-Block geschält und anschließend durch Stanzen und/oder mechanische Bearbeitung mit der gewünschten Kontur versehen. Die Baugröße und die mangelnde Eigenstabilität des Dichtungsrahmens erschweren die erreichbare Genauigkeit des Dichtungsrahmens. Des Weiteren ist der Stanzabfall bei einer Scheibendichtung aus PTFE sehr groß. Mit der gespritzten Variante lassen sich vielfältige Konturen herstellen.A significant manufacturing and cost advantage results from the fact that the disc seal consists of a sprayable PTFE material. So far, a sealing frame of the disc seal were peeled from a PTFE block and then provided by punching and / or mechanical machining with the desired contour. The size and the lack of inherent stability of the sealing frame complicate the achievable accuracy of the sealing frame. Furthermore, the punching waste is very large in a PTFE disc seal. With the sprayed variant, a variety of contours can be produced.

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. 1-3
Schnittdarstellungen eines Schwenkmotors
Fig. 4 - 6
Scheibendichtung mit umlaufendem Druckausgleichskanal
Fig. 7-11
Erfindungsgemäße Scheibendichtung mit zusätzlichen Queröffnungen
Fig. 12 - 15
Erfindungsgemäße Scheibendichtung mit Verbindungsöffnung innerhalb der Stirnflächen
Fig. 16 - 19
Scheibendichtung mit Doppel-T-Querschnittsprofil
It shows:
Fig. 1-3
Sectional views of a slewing motor
Fig. 4-6
Window seal with circulating pressure equalization channel
Fig. 7-11
Inventive disc seal with additional transverse openings
FIGS. 12-15
Inventive disc seal with connection opening within the end faces
Fig. 16 - 19
Window seal with double-T cross section profile

Die Fig. 1 zeigt ein Aggregat in der Bauform eines Schwenkmotors 1 in einer Längsschnittdarstellung mit einem Zylinder 3, in dem eine Motorwelle 5 drehbar gelagert ist. Mit dem Zylinder 3 sind endseitig Deckel 7 und 9 verschweißt. An der Innenwandung 11 des Zylinders 3 sind zwei Rippen 13 (Fig. 2) angeordnet, die mit Flügeln 15 der Motorwelle 5, dem Zylinder 3 und den Deckeln 7; 9 vier Arbeitskammern 17; 19 bilden, wobei Arbeitskammern mit gleicher Bezugsziffer über ein Druckmittelverteilungssystem ausgehend von Hydraulikanschlüssen 21; 23 und Querkanälen 25; 27 innerhalb der Motorwelle miteinander verbunden sind. Die Zahl der Arbeitskammern ist abhängig vom aufzubringenden Drehmoment und vom notwendigen Schwenkwinkel des Schwenkmotors.The Fig. 1 shows an assembly in the form of a swing motor 1 in a longitudinal sectional view with a cylinder 3, in which a motor shaft 5 is rotatably mounted. With the cylinder 3 end lid 7 and 9 are welded. On the inner wall 11 of the cylinder 3 are two ribs 13 (FIG. Fig. 2 ) arranged with wings 15 of the motor shaft 5, the cylinder 3 and the covers 7; 9 four working chambers 17; Form 19, wherein working chambers with the same reference numeral via a pressure medium distribution system starting from hydraulic ports 21; 23 and transverse channels 25; 27 are interconnected within the motor shaft. The number of working chambers depends on the torque to be applied and on the required swivel angle of the slewing motor.

Innerhalb der Flügel und Rippen sind Dichtungen 31; 33 in der Bauform von Scheibendichtungen eingelegt, die jeweils benachbarte Arbeitskammern voneinander trennen.Within the wings and ribs are seals 31; 33 inserted in the design of disc seals, each of which separate adjacent working chambers.

Beide Deckel 7; 9 bilden zusammen mit der Motorwelle 5 Ringräume 37; 39, die Dichtungsanordnungen 41; 43 zur Abdichtung der Arbeitskammern 17; 19 aufnehmen. Während der Druckbeaufschlagung einer gemeinsamen Gruppe von Arbeitskammern, z. B. 17 und einem vergleichsweise kleineren Druck in den Arbeitskammern 19 wird ein sehr geringer Ölstrom in die Ringräume 37; 39 gedrückt, da sich durch die unterschiedliche Druckbeaufschlagung aus den Arbeitskammern in Umfangsrichtung eine geringfügige Deformation der Dichtungsanordnung einstellt und damit Druckmittel aus den Arbeitskammern 17 mit einem hohen Druck in die Ringräume 37, 39 eindringt. Die insbesondere bei niedrigen Arbeitskammerdrücken nach Hochdruckphasen auftretenden Druckmittelvolumen sind vergleichsweise sehr klein, doch könnte der Fall eintreten, dass z. B. in dem Ringraum 37 ein größerer Momentandruck des Druckmittels vorherrscht als im Ringraum 39. Damit keinesfalls axial wirksame Verschiebekräfte zwischen dem Zylinder 3 mit den Deckeln 7, 9 und der Motorwelle 5 auftreten, sind beide Ringräume 37; 39 über einen Druckausgleichskanal 45, s. Fig. 3, miteinander verbunden.Both covers 7; 9 form together with the motor shaft 5 annular spaces 37; 39, the seal assemblies 41; 43 for sealing the working chambers 17; 19 record. While pressurizing a common group of working chambers, e.g. B. 17 and a relatively smaller pressure in the working chambers 19 is a very low flow of oil into the annular spaces 37; Pressed 39, as set by the different pressure from the working chambers in the circumferential direction a slight deformation of the seal assembly and thus pressure medium from the working chambers 17 at a high pressure in the annular spaces 37, 39 penetrates. The pressure medium volume occurring in particular at low working chamber pressures after high pressure phases are comparatively very small, but it could happen that z. B. in the annular space 37, a larger momentary pressure of the pressure medium prevails as in the annular space 39. So that no axially effective displacement forces between the cylinder 3 with the covers 7, 9 and the motor shaft 5 occur, both annular spaces 37; 39 via a pressure equalization channel 45, s. Fig. 3 , connected with each other.

Der Druckausgleichskanal wird zumindest auf einer Teillänge von den Scheibendichtungen 31; 33 gebildet, die in einer Nut des Flügels und/oder der Rippe angeordnet sind. In diesem nicht erfindungsgemäßen Ausführungsbeispiel wird der Druckausgleichskanal von einer in Längsrichtung der Scheibendichtung verlaufenden Nut gebildet. Des weiteren sind die Ringräume 37; 39 über Stichkanäle 47; 49 in der Motorwelle mit dem Druckausgleichskanal 45 verbunden, wobei die Stichkanäle in einem Abstand zum äußeren Ende der Scheibendichtung 31 in den Druckausgleichskanal 45 münden.The pressure equalization channel is at least part of the length of the disk seals 31; 33 formed, which are arranged in a groove of the wing and / or the rib. In this embodiment not according to the invention, the pressure compensation channel is formed by a groove extending in the longitudinal direction of the window seal. Furthermore, the annular spaces 37; 39 via branch channels 47; 49 connected in the motor shaft with the pressure equalization channel 45, wherein the branch channels open at a distance from the outer end of the disk seal 31 in the pressure equalization channel 45.

Die Fig. 4 zeigt einen nicht erfindungsgemäßen Schwenkmotor 1 in der prinzipiellen Bauform gemäß Fig. 1. Abweichend werden die Ringräume 37; 39 über Radialkanäie 51 mit dem Druckausgleichskanal 45 verbunden, wie in der Fig. 5 vergrößert dargestellt ist. Die Radialkanäle werden z. B. von einer Prägung gebildet. Dadurch kann der Druckausgleichskanal 45 in der Dichtung mit einem vergleichsweise großen Querschnitt dimensioniert werden, da eine gewünschte Drosselfunktion innerhalb des Druckausgleichskanals von der Prägung erzeugt wird. Die Fig. 6 zeigt eine Detailansicht einer Scheibendichtung 31; 33 innerhalb einer Nut. Bei dieser Lösung umfasst die Scheibendichtung 31 einen Dichtungsrahmen 53 in Verbindung mit mehreren nebeneinander angeordneten axial und radial elastischen Füllstücken 55. Beidseitig angeordnete Seitenfüllstücke 57; 59 komplettieren die Scheibendichtungen.The Fig. 4 shows a non-inventive swing motor 1 in the basic design according to Fig. 1 , Deviating, the annular spaces 37; 39 via radial duct 51 connected to the pressure equalization channel 45, as in the Fig. 5 is shown enlarged. The radial channels are z. B. formed by a coinage. This allows the pressure equalization channel 45 are dimensioned in the seal with a comparatively large cross-section, as a desired throttling function is generated within the pressure equalization channel of the embossing. The Fig. 6 shows a detailed view of a window seal 31; 33 inside a groove. In this solution, the disk seal 31 comprises a sealing frame 53 in conjunction with a plurality of juxtaposed axially and radially elastic Füllstücken 55. Both sides arranged Seitenfüllstücke 57; 59 complete the window seals.

Ein weiterer Unterschied zur Ausführung nach den Figuren 1 und 3 besteht darin, dass der Druckausgleichskanal 45 von einer zwischen den Ringräumen 37; 39 umlaufenden Nut der Scheibendichtung 31, 33 gebildet wird. Auch in den endseitigen Stirnflächen 61, 63 der Scheibendichtung ist der Druckausgleichskanal 45 ausgeführt.Another difference to the execution after the FIGS. 1 and 3 is that the pressure equalization channel 45 of a between the annular spaces 37; 39 circumferential groove of the disc seal 31, 33 is formed. Also in the end-side end faces 61, 63 of the disk seal of the pressure compensation channel 45 is executed.

Der Schwenkmotor gemäß Fig. 7 entspricht bis auf die Ausgestaltung des Druckausgleichskanals 45 der Bauform nach Fig. 4. Abweichend ist, wie aus der Fig. 8 ersichtlich ist, der Druckausgleichskanal 45 lediglich an einer Unter und einer Oberseite der Scheibendichtung 31 ausgeführt. Innerhalb der Scheibendichtung ist, wie aus der Zusammenschau der Figuren 7; 9; 10 und 11 erkennbar ist, erfindungsgemäß mindestens eine Queröffnung 65 ausgeführt. Die Queröffnung 65 kann sich über die gesamte Breite der Scheibendichtung erstrecken und wird durch die Seitenfüllstücke 57; 59 in Abhängigkeit der Anströmungsrichtung verschlossen. Wenn beispielsweise in der Arbeitskammer 19 ein größerer Momentandruck herrscht als in der Arbeitskammer 17, dann wird der Dichtungsrahmen 53 ggf. zusammen mit den Füllstücken 55 auf das Seitenfüllstück 59 gedrückt, das sich an der rechten Nutseitenwand abstützt. Innerhalb des Druckausgleichskanals 45 liegt etwa derselbe Druck vor, wie in der Arbeitskammer 17. Das Füllstück 59 schwimmt zwischen der rechten Nutseitenwand und dem Dichtungsrahmen mit den Füllstücken. Bei einer Arbeitsdruckreduzierung kann sich der in den Ringräumen 37; 39 aufgebaute Druck in die Arbeitskammer 19 abbauen, bevor sich der Dichtungsrahmen mit den Füllstücken ebenfalls in Richtung der linken Nutseitenwand bewegt. Die Füllstücke 57; 59 verhindern eine direkte Querverbindung zwischen den Arbeitskammern 17; 19.The swivel motor according to Fig. 7 corresponds to the design of the pressure compensation channel 45 of the design Fig. 4 , Deviating is, as from the Fig. 8 it can be seen, the pressure-equalizing channel 45 is executed only on a lower and an upper side of the disk seal 31. Within the window seal is, as from the synopsis of Figures 7; 9; 10 and 11 can be seen, at least one transverse opening 65 executed according to the invention. The transverse opening 65 may extend over the entire width of the window seal and is defined by the side fills 57; 59 closed depending on the direction of flow. If, for example, a greater momentary pressure prevails in the working chamber 19 than in the working chamber 17, then the sealing frame 53 is possibly pressed together with the filling pieces 55 onto the side filling piece 59, which is supported on the right-hand groove side wall. Within the pressure equalization channel 45 is about the same pressure as in the working chamber 17. The filler 59 floats between the right groove side wall and the sealing frame with the filling pieces. At a working pressure reduction in the annular spaces 37; 39 degraded pressure in the working chamber 19 before the sealing frame moves with the filler pieces also in the direction of the left groove side wall. The filling pieces 57; 59 prevent a direct cross-connection between the working chambers 17; 19th

Die Varianten nach den Figuren 4 bis 11 lassen sich bezüglich der Queröffnungen 65 sehr vorteilhaft kombinieren. Dann ist es sinnvoll, die Queröffnung 65 im Bereich der dynamischen Dichtfläche 67, s. Fig. 7, auszuführen, um die Funktion der Füllstücke als Rückschlagventilelement zu verbessern. Im Bereich der dynamischen Dichtfläche 67 treten im Gegensatz zum Nutgrund keine Übergangsradien zwischen dem Nutgrund und den Nutseitenwänden auf, die ggf. die radiale Verschiebung der Füllstücke verursachen könnten.Variants after FIGS. 4 to 11 can be combined very advantageous with respect to the transverse openings 65. Then it makes sense, the transverse opening 65 in the region of the dynamic sealing surface 67, s. Fig. 7 to perform to improve the function of the filler as a check valve element. In the area of the dynamic sealing surface 67, in contrast to the groove base, there are no transition radii between the groove base and the groove side walls, which could possibly cause the radial displacement of the filler pieces.

Mit den Fig. 12 bis 15 soll eine weitere erfindungsgemäße Ausführungsform vorgestellt werden, bei der die Scheibendichtung aus einem ringförmigen Dichtkörper, z. B. in der Ausgestaltung eines Dichtrahmens 53 gemäß der Fig. 6, in Verbindung mit einem Kernstück oder auch Füllstück 55 ausgeführt ist, wobei der Dichtkörper 53 mindestens eine Verbindungsöffnung 69 zwischen seiner Außen- und seiner Innenwandung aufweist, die über den Radialkanal 47 mit den Ringräumen 37; 39 verbunden ist. Die Breite der Nut innerhalb des Flügels oder der Rippe für die Scheibendichtung ist größer als die aus den Seitenfüllstücken und dem Dichtungsrahmen zusammen mit den Füllstücken gebildete Schichtung. Deshalb stellt sich innerhalb der Nut ein geometrisch nicht exakt bestimmbarer Spalt 71 innerhalb der Scheibendichtung und/oder zwischen der Scheibendichtung und/oder den Seitenfüllstücken und/oder zu den Nutenseitenwänden ein, der wechselweise in Abhängigkeit der Druckverhältnisse in den Arbeitskammern 17; 19 vorliegt, und an die Verbindungsöffnung angeschlossen, so dass der sich über die gesamte Länge der Scheibendichtung erstreckende Spalt 71 zusammen mit den Verbindungsöffnungen den Druckausgleichskanal zwischen den Dichtungsanordnungen 37; 39 bildet. Die Verbindungsöffnung erstreckt sich nur auf einem sehr kurzen Weg und kann auch mit vergleichsweise geringem Aufwand in dem Dichtkörper ausgeführt werden. Wenn sich der Spalt 71 zwischen der Nutenseitenwand und einem Seitenfüllstück bildet, dann kann der Druckausgleichskanal auch an die jeweilige Arbeitskammer angeschlossen sein.With the Fig. 12 to 15 another embodiment of the invention will be presented, in which the disk seal from an annular sealing body, for. B. in the embodiment of a sealing frame 53 according to the Fig. 6 , in connection with a core piece or filler 55 is performed, wherein the sealing body 53 has at least one connecting opening 69 between its outer and its inner wall, via the radial passage 47 with the annular spaces 37; 39 is connected. The width of the groove within the vane or rib for the disc seal is greater than that formed by the side vents and the sealing frame together with the patches Stratification. Therefore, within the groove, a geometrically not exactly determinable gap 71 within the window seal and / or between the window seal and / or the Seitenfüllstücken and / or to the Nutenseitenwänden, which alternately depending on the pressure conditions in the working chambers 17; 19 is present, and connected to the connection opening, so that over the entire length of the disk seal extending gap 71 together with the connection openings the pressure equalization channel between the seal assemblies 37; 39 forms. The connection opening extends only in a very short way and can be carried out with comparatively little effort in the sealing body. If the gap 71 forms between the groove side wall and a Seitenfüllstück, then the pressure equalization channel can also be connected to the respective working chamber.

Die Fig. 16 bis 19 beschreiben eine Scheibendichtung 31; 33, die u. a. in einem Schwenkmotor gemäß den vorgenannten Figuren einsetzbar ist. Die Scheibendichtung 31; 33 weist ein Doppel-T-Querschnittsprofil auf, das vollständig aus einem, insbesondere spritzfähigen PTFE-Werkstoff besteht. Hinsichtlich der Herstellung eines spritzfähigen PTFE-Werkstoffs wird beispielhaft auf die DE 41 12 248 A1 oder DE 196 19 232 A1 . verwiesen. Es bestehen keinerlei Queröffnungen innerhalb des Vertikalstegs. Des weiteren können die Querstege und der Vertikalsteg eine derartige Breite einnehmen, dass für eine vernünftige Nutbreite in den Rippen und Flügeln keine Seitenfüllstücke verwendet werden müssen.The Fig. 16 to 19 describe a disk seal 31; 33, which is used inter alia in a swivel motor according to the aforementioned figures. The window seal 31; 33 has a double-T cross-sectional profile, which consists entirely of a, in particular sprayable PTFE material. With regard to the production of a sprayable PTFE material is exemplified in the DE 41 12 248 A1 or DE 196 19 232 A1 , directed. There are no transverse openings within the vertical web. Furthermore, the transverse webs and the vertical web can assume such a width that for a reasonable groove width in the ribs and wings no Seitenfüllstücke must be used.

Seitlich von dem Vertikalsteg zwischen den Querstegen des Doppel-T-Querschnittsprofils der Scheibendichtung sind Vorspannmittel angeordnet, beispielsweise radial und/oder axial elastische Federscheiben. Auch die Stirnflächen 61; 63 der Scheibendichtung erstrecken sich über die Breite der Querstege, so dass beiderseits des Vertikalstegs Taschen vorliegen, in denen die Federscheiben 55 eingeklemmt werden und während der Montage auch nicht herausfallen können.Biasing means are arranged laterally from the vertical web between the transverse webs of the double-T cross-sectional profile of the disk seal, for example radially and / or axially elastic spring disks. Also, the end surfaces 61; 63 of the disc seal extending over the width of the transverse webs, so that on both sides of the vertical web pockets are present in which the spring washers 55 are clamped and during assembly can not fall out.

Wie aus der Fig. 16 ersichtlich ist, sind die Querstege in Richtung der Nutenseitewände mit einem Profil 77 versehen. Das Profil besteht aus einer Anzahl von Aussparungen, die keine Verbindung zu dem axial verlaufenden Druckausgleichskanal 45 besitzen. Die Ausnehmungen dienen dazu, Druckmedium in die Nuten für die Scheibendichtung innerhalb der Rippen und Flügel einströmen zu lassen, damit das Druckmedium die Vorspannung auf die Scheibendichtung druckabhängig unterstützt.Like from the Fig. 16 can be seen, the transverse webs are provided in the direction of Nutenseitewände with a profile 77. The profile consists of a number of recesses which have no connection to the axially extending pressure equalization channel 45. The recesses serve to allow pressure fluid to flow into the grooves for the disc seal within the ribs and wings, so that the pressure medium pressure-dependent supports the bias on the disc seal.

Die Wahl des Dichtungsquerschnitts für die Scheibendichtung ist unabhängig von der Anwendung und der Ausgestaltung des Druckausgleichskanals.The choice of the sealing cross section for the disc seal is independent of the application and the design of the pressure compensation channel.

Claims (4)

  1. Vane-type motor (1), comprising a motor shaft (5) and a cylinder (3) which is filled with a pressure medium and has at least one fin (13) on its inner wall, wherein the motor shaft (5) is pivotably mounted with at least one vane (15) within the cylinder (3), wherein a pressure-prestressable sealing arrangement (41; 43) which is associated with the vane-type motor (1) is present inside at least two annular spaces (37; 39) between the cylinder (3) and the motor shaft (5), which sealing arrangement (41; 43), together with plate gaskets (31; 33) which are associated with the vane-type motor (1) inside the vanes (15) and the fins (13), seals off a working chamber (17; 19) which is formed by the cylinder (3) with the fin (13) and the motor shaft (5) and the vane (15) together with end-side covers (7; 9) of the cylinder (3), wherein the annular spaces (37; 39) are connected to one another via a pressure-equalizing duct, wherein the pressure-equalizing duct (45) is formed, at least over part of its length, by one of the plate gaskets (31; 33) which is arranged in a groove in the vane (15) and/or the fin (13),
    characterized
    in that the plate gasket (31, 33) has at least one lateral opening (65) which can be closed off at the ends by lateral filling elements (57; 59) as a function of the direction of flow against it.
  2. Vane-type motor according to Claim 1,
    characterized
    in that the lateral opening (65) is embodied in the region of the dynamic sealing face (67) of the plate gasket (31; 33).
  3. Vane-type motor (1), comprising a motor shaft (5) and a cylinder (3) which is filled with a pressure medium and has at least one fin (13) on its inner wall, wherein the motor shaft (5) is pivotably mounted with at least one vane (15) within the cylinder (3), wherein a pressure-prestressable sealing arrangement (41; 43) which is associated with the vane-type motor (1) is present inside at least two annular spaces (37; 39) between the cylinder (3) and the motor shaft (5), which sealing arrangement (41; 43), together with plate gaskets (31; 33) which are associated with the vane-type motor (1) inside the vanes (15) and the fins (13), seals off a working chamber (17; 19) which is formed by the cylinder (3) with the fin (13) and the motor shaft (5) and the vane (15) together with end-side covers (7; 9) of the cylinder (3), wherein the annular spaces (37; 39) are connected to one another via a pressure-equalizing duct, wherein the pressure-equalizing duct (45) is formed, at least over part of its length, by one of the plate gaskets (31; 33) which is arranged in a groove in the vane (15) and/or the fin (13),
    characterized
    in that the plate gasket (31; 33) is embodied from an annular sealing body (53) in conjunction with at least one core element (55), wherein the sealing body (53) has at least one connecting opening (69) between its outer wall and its inner wall, and a gap (71) between the components of the plate gasket (31, 33) and/or a lateral filling element (57; 59) and/or a groove side wall is connected to the connecting opening, with the result that the gap (71), together with the connecting opening (69), forms the pressure-equalizing duct.
  4. Vane-type motor according to one of Claims 1 to 3,
    characterized
    in that the plate gasket (31; 33) is composed of an injectable PTFE material.
EP05013073A 2004-07-07 2005-06-17 Vane-type motor Not-in-force EP1614905B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004032747A DE102004032747A1 (en) 2004-07-07 2004-07-07 swing motor

Publications (3)

Publication Number Publication Date
EP1614905A2 EP1614905A2 (en) 2006-01-11
EP1614905A3 EP1614905A3 (en) 2008-01-09
EP1614905B1 true EP1614905B1 (en) 2011-08-17

Family

ID=34980027

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05013073A Not-in-force EP1614905B1 (en) 2004-07-07 2005-06-17 Vane-type motor

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EP (1) EP1614905B1 (en)
AT (1) ATE520883T1 (en)
DE (1) DE102004032747A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008010899A1 (en) * 2008-02-23 2009-08-27 Zf Friedrichshafen Ag Window seal
DE102008016750A1 (en) 2008-03-31 2009-10-01 Zf Friedrichshafen Ag swing motor
DE102008016749A1 (en) 2008-03-31 2009-10-08 Zf Friedrichshafen Ag Window seal, in particular for a swivel motor
DE102008016751B3 (en) * 2008-03-31 2009-12-31 Zf Friedrichshafen Ag Window seal, in particular for a swivel motor
DE102008026599B4 (en) * 2008-06-03 2016-09-01 Rausch & Pausch Gmbh Swivel motor with radial shaft seal system

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3053236A (en) * 1960-09-08 1962-09-11 Thompson Ramo Woeldridge Inc Oscillatory actuator seal system
DE4339527C1 (en) * 1993-11-19 1995-02-16 Freudenberg Carl Fa Sealing arrangement
DE19935234C1 (en) * 1999-07-28 2000-11-09 Mannesmann Sachs Ag Sealing rail for rotary piston engine has packing piece provided with sealing body divided into 2 parallel halves acted on by spring element with separation element between them
DE10021138A1 (en) * 2000-04-29 2001-10-31 Bayerische Motoren Werke Ag Sealing element for a swivel motor
DE10062477C1 (en) * 2000-12-14 2002-07-25 Zf Sachs Ag Swiveling motor with casing and motor shaft forming chamber has channel system with throttle point to prevent leakage between cavities at different pressures
JP3957577B2 (en) * 2001-09-11 2007-08-15 ジャパン・ハムワージ株式会社 Rotary vane type steering machine seal structure
DE10243696B3 (en) * 2002-09-20 2004-03-11 Zf Sachs Ag Pivot motor has pressure equalization between working chambers provided via pressure equalization channel formed by groove between motor shaft and concentric sleeve

Also Published As

Publication number Publication date
EP1614905A3 (en) 2008-01-09
EP1614905A2 (en) 2006-01-11
ATE520883T1 (en) 2011-09-15
DE102004032747A1 (en) 2006-01-26

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