EP1614905A2 - Moteur rotatif à palettes - Google Patents

Moteur rotatif à palettes Download PDF

Info

Publication number
EP1614905A2
EP1614905A2 EP05013073A EP05013073A EP1614905A2 EP 1614905 A2 EP1614905 A2 EP 1614905A2 EP 05013073 A EP05013073 A EP 05013073A EP 05013073 A EP05013073 A EP 05013073A EP 1614905 A2 EP1614905 A2 EP 1614905A2
Authority
EP
European Patent Office
Prior art keywords
seal
channel
motor according
pressure
annular spaces
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
EP05013073A
Other languages
German (de)
English (en)
Other versions
EP1614905B1 (fr
EP1614905A3 (fr
Inventor
Matthias Reuss
Stefan Schiffler
Andreas Schlüter
Katrin Zietsch-Prior
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP1614905A2 publication Critical patent/EP1614905A2/fr
Publication of EP1614905A3 publication Critical patent/EP1614905A3/fr
Application granted granted Critical
Publication of EP1614905B1 publication Critical patent/EP1614905B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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 swing 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 has a pressure-biasing seal assembly which, together with disc seals within the vanes and ribs, seals a working chamber formed by the cylinder with the rib and the motor shaft and the vane together with end lids of the cylinder, the annular spaces communicating with each other via a pressure equalizing channel are connected.
  • 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 object is achieved in that the pressure equalization channel is formed at least over a partial length of one of the window seals, which is arranged in a groove of the wing and / or the rib.
  • the great advantage of the invention is that for the production of the pressure equalization channel a significantly lower production cost must be operated on the motor shaft, as it is known from the prior art.
  • the pressure compensation channel is formed by a groove running in the longitudinal direction of the window seal. It is possible to let the pressure equalization channel over the entire length of the disk seal, so that there is a direct connection of the disk seal to the said annular spaces for the annular seal assemblies.
  • the radial channel z. B. formed by a coinage.
  • An embossed radial channel can be produced very easily and with great precision.
  • the possibility of pressure reduction from the pressure equalization channel is promoted by the pressure equalization channel is formed by a circumferential groove of the disc seal between the annular spaces.
  • the pressurized medium from the annular spaces can flow off in the direction of the dynamic sealing surface via the pressure compensation channel which is also present in the end faces of the window seal and can continue to escape into a working space.
  • the disc seal is made of an annular sealing body in conjunction with a core piece, wherein the sealing body has at least one connecting opening between its outer and its inner wall and a gap between the disc seal and a 39° Stirll Faculty is connected to the connection opening, so that the gap forms the pressure equalization channel together with the connection opening.
  • 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 side of a vertical web between transverse webs of the double-T cross-sectional profile of the disk seal biasing means are arranged.
  • the vertical web and the two transverse webs form pockets in which the biasing means, for. B. spring washers, can be easily held without the spring washers fall out again during assembly.
  • the transverse webs are provided in the direction of Nutendose except with a profile.
  • the pressure medium may flow through the profile into the grooves within the vanes and ribs for the disc seal and bias the disc seal pressure-dependently in all directions.
  • 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 disk seal made of PTFE. With the sprayed variant, a variety of contours can be produced.
  • seals 31; 33 inserted in the design of disc seals, each of which separate adjacent working chambers.
  • 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 equalization channel is formed by a groove running in the longitudinal direction of the disk seal.
  • 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.
  • FIG. 4 shows a swivel motor 1 in the basic design according to FIG. 1.
  • Deviating from the annular spaces 37; 39 connected via Radialkanäie 51 with the pressure equalization channel 45, as shown in FIG. 5 is 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.
  • 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 Gireus 55. Both sides arranged Sus 56; 59 complete the window seals.
  • the connection opening extends only in a very short way and can be performed with relatively 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 transverse webs are provided with a profile 77 in the direction of the groove side walls.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Actuator (AREA)
  • Motor Or Generator Frames (AREA)
EP05013073A 2004-07-07 2005-06-17 Moteur rotatif à palettes Not-in-force EP1614905B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004032747A DE102004032747A1 (de) 2004-07-07 2004-07-07 Schwenkmotor

Publications (3)

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

Family

ID=34980027

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05013073A Not-in-force EP1614905B1 (fr) 2004-07-07 2005-06-17 Moteur rotatif à palettes

Country Status (3)

Country Link
EP (1) EP1614905B1 (fr)
AT (1) ATE520883T1 (fr)
DE (1) DE102004032747A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2093465A1 (fr) * 2008-02-23 2009-08-26 Zf Friedrichshafen Ag Lame d'étanchéité

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008016751B3 (de) * 2008-03-31 2009-12-31 Zf Friedrichshafen Ag Scheibendichtung, insbesondere für einen Schwenkmotor
DE102008016749A1 (de) 2008-03-31 2009-10-08 Zf Friedrichshafen Ag Scheibendichtung, insbesondere für einen Schwenkmotor
DE102008016750A1 (de) 2008-03-31 2009-10-01 Zf Friedrichshafen Ag Schwenkmotor
DE102008026599B4 (de) * 2008-06-03 2016-09-01 Rausch & Pausch Gmbh Schwenkmotor mit Radialwellendichtungssystem

Citations (4)

* 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
DE10062477C1 (de) * 2000-12-14 2002-07-25 Zf Sachs Ag Schwenkmotor
WO2003024787A1 (fr) * 2001-09-11 2003-03-27 Japan Hamworthy & Co., Ltd. Structure d'etancheite pour appareil a gouverner de type rotatif a palettes
DE10243696B3 (de) * 2002-09-20 2004-03-11 Zf Sachs Ag Schwenkmotor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4339527C1 (de) * 1993-11-19 1995-02-16 Freudenberg Carl Fa Dichtungsanordnung
DE19935234C1 (de) * 1999-07-28 2000-11-09 Mannesmann Sachs Ag Dichtungsleiste
DE10021138A1 (de) * 2000-04-29 2001-10-31 Bayerische Motoren Werke Ag Dichtungselement für einen Schwenkmotor

Patent Citations (4)

* 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
DE10062477C1 (de) * 2000-12-14 2002-07-25 Zf Sachs Ag Schwenkmotor
WO2003024787A1 (fr) * 2001-09-11 2003-03-27 Japan Hamworthy & Co., Ltd. Structure d'etancheite pour appareil a gouverner de type rotatif a palettes
DE10243696B3 (de) * 2002-09-20 2004-03-11 Zf Sachs Ag Schwenkmotor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2093465A1 (fr) * 2008-02-23 2009-08-26 Zf Friedrichshafen Ag Lame d'étanchéité

Also Published As

Publication number Publication date
EP1614905B1 (fr) 2011-08-17
ATE520883T1 (de) 2011-09-15
EP1614905A3 (fr) 2008-01-09
DE102004032747A1 (de) 2006-01-26

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