EP1614905B1 - Moteur rotatif à palettes - Google Patents

Moteur rotatif à palettes 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
Authority
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
Other languages
German (de)
English (en)
Other versions
EP1614905A2 (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 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.

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)

Claims (4)

  1. Moteur rotatif (1) comprenant un arbre de moteur (5) et un cylindre (3) rempli de fluide sous pression avec au moins une ailette (13) sur sa paroi intérieure, l'arbre de moteur (5) étant monté à l'intérieur du cylindre (3) de manière pivotante avec au moins une palette (15), un agencement d'étanchéité (41 ; 43) pouvant être précontraint en pression, appartenant au moteur rotatif (1), étant disposé à l'intérieur d'au moins deux espaces annulaires (37 ; 39) entre le cylindre (3) et l'arbre de moteur (5), lequel agencement d'étanchéité, conjointement avec des joints d'étanchéité à disque (31 ; 33) appartenant au moteur rotatif (1), étanchéifie une chambre de travail (17 ; 19) à l'intérieur des palettes (15) et des ailettes (13), laquelle est formée par le cylindre (3) avec l'ailette (13) et l'arbre de moteur (5) et la palette (15) conjointement avec des couvercles (7 ; 9) du côté de l'extrémité du cylindre (3), les espaces annulaires (37 ; 39) étant connectés l'un à l'autre par le biais d'un canal d'équilibrage de la pression,
    le canal d'équilibrage de la pression (45) étant formé au moins sur une longueur partielle de l'un des joints d'étanchéité à disque (31 ; 33), qui est disposé dans une rainure de la palette (15) et/ou de l'ailette (13),
    caractérisé en ce que
    le joint d'étanchéité à disque (31, 33) présente au moins une ouverture transversale (65), qui peut être fermée par l'intermédiaire de pièces de remplissage latérales (57 ; 59) du côté de l'extrémité en fonction du sens d'afflux.
  2. Moteur rotatif selon la revendication 1,
    caractérisé en ce que
    l'ouverture transversale (65) est réalisée dans la région de la surface d'étanchéité dynamique (67) du joint d'étanchéité à disque (31 ; 33).
  3. Moteur rotatif (1) comprenant un arbre de moteur (5) et un cylindre (3) rempli de fluide sous pression avec au moins une ailette (13) sur sa paroi intérieure, l'arbre de moteur (5) étant monté à l'intérieur du cylindre (3) de manière pivotante avec au moins une palette (15), un agencement d'étanchéité (41 ; 43) pouvant être précontraint en pression, appartenant au moteur rotatif (1), étant disposé à l'intérieur d'au moins deux espaces annulaires (37 ; 39) entre le cylindre (3) et l'arbre de moteur (5), lequel agencement d'étanchéité, conjointement avec des joints d'étanchéité à disque (31 ; 33) appartenant au moteur rotatif (1), étanchéifie une chambre de travail (17 ; 19) à l'intérieur des palettes (15) et des ailettes (13), laquelle est formée par le cylindre (3) avec l'ailette (13) et l'arbre de moteur (5) et la palette (15) conjointement avec des couvercles (7 ; 9) du côté de l'extrémité du cylindre (3), les espaces annulaires (37 ; 39) étant connectés l'un à l'autre par le biais d'un canal d'équilibrage de la pression,
    le canal d'équilibrage de la pression (45) étant formé au moins sur une longueur partielle de l'un des joints d'étanchéité à disque (31 ; 33), qui est disposé dans une rainure de la palette (15) et/ou de l'ailette (13),
    caractérisé en ce que
    le joint d'étanchéité à disque (31, 33) est réalisé à partir d'un corps d'étanchéité annulaire (53) en conjonction avec au moins un élément formant noyau (55), le corps d'étanchéité (53) présentant au moins une ouverture de connexion (69) entre sa paroi extérieure et sa paroi intérieure, et une fente (71) étant raccordée entre les composants du joint d'étanchéité à disque (31, 33) et/ou une pièce de remplissage latérale (57 ; 59) et/ou une paroi latérale de rainure à l'ouverture de connexion, de sorte que la fente (71) forme, conjointement avec l'ouverture de connexion (69), le canal d'équilibrage de la pression.
  4. Moteur rotatif selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    le joint d'étanchéité à disque (31 ; 33) se compose d'un matériau en PTFE pulvérisable.
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 EP1614905A2 (fr) 2006-01-11
EP1614905A3 EP1614905A3 (fr) 2008-01-09
EP1614905B1 true 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)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008010899A1 (de) * 2008-02-23 2009-08-27 Zf Friedrichshafen Ag Scheibendichtung
DE102008016749A1 (de) 2008-03-31 2009-10-08 Zf Friedrichshafen Ag Scheibendichtung, insbesondere für einen Schwenkmotor
DE102008016751B3 (de) * 2008-03-31 2009-12-31 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

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 (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
DE10062477C1 (de) * 2000-12-14 2002-07-25 Zf Sachs Ag Schwenkmotor
JP3957577B2 (ja) * 2001-09-11 2007-08-15 ジャパン・ハムワージ株式会社 ロータリーベーン式舵取機のシール構造
DE10243696B3 (de) * 2002-09-20 2004-03-11 Zf Sachs Ag Schwenkmotor

Also Published As

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

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