EP0283380B1 - Druckmittelbetriebener Schwenkflügelmotor ohne innere Dichtungen - Google Patents

Druckmittelbetriebener Schwenkflügelmotor ohne innere Dichtungen Download PDF

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Publication number
EP0283380B1
EP0283380B1 EP19880400535 EP88400535A EP0283380B1 EP 0283380 B1 EP0283380 B1 EP 0283380B1 EP 19880400535 EP19880400535 EP 19880400535 EP 88400535 A EP88400535 A EP 88400535A EP 0283380 B1 EP0283380 B1 EP 0283380B1
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EP
European Patent Office
Prior art keywords
shaft
casing
annular
vane
partition
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.)
Expired - Lifetime
Application number
EP19880400535
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English (en)
French (fr)
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EP0283380A3 (en
EP0283380A2 (de
Inventor
Patrick Garceau
Serge Legrand
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Societe Europeenne de Propulsion SEP SA
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Societe Europeenne de Propulsion SEP SA
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Application filed by Societe Europeenne de Propulsion SEP SA filed Critical Societe Europeenne de Propulsion SEP SA
Priority to AT88400535T priority Critical patent/ATE68567T1/de
Publication of EP0283380A2 publication Critical patent/EP0283380A2/de
Publication of EP0283380A3 publication Critical patent/EP0283380A3/fr
Application granted granted Critical
Publication of EP0283380B1 publication Critical patent/EP0283380B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 present invention relates to a fluidic device with a rotary vane, intended to be used either as a motor (rotary actuator) or as a receiver (reciprocating pump), comprising a fixed casing traversed by a rotating shaft around its axis and carrying said pallet, while the interior space to the casing, forming an annular volume of revolution around the shaft, the section of which by a radial plane is rectangular and which is limited by two flat annular base surfaces and two coaxial cylindrical surfaces, respectively interior and exterior, is divided into two chambers of complementarily variable volume by a radial partition, fixed relative to the casing, and by said pallet, movable in rotation with the shaft.
  • the latter is machined so as to have a thickness - along the direction of the axis of the shaft - equal, with very little play, to the distance separating the two flat annular surfaces limiting the annular space in this same direction , as well as a length and a cylindrical conformation of its end such that, after mounting the pallet on the shaft, the surface of its end is located on a cylinder of revolution coaxial with the shaft and of radius equal to one very small clearance, except that of the cylindrical surface externally limiting the annular space; the partition is machined so as to have a thickness - along the direction of the axis - equal, with very little play, to the distance separating the two annular surfaces mentioned above, as well as a cylindrical conformation of its edges radially contiguous to the shaft and the casing such that, after assembly of the constituent elements of the device, the surfaces of these edges are located on cylinders of revolution coaxial with the shaft.
  • Devices of this type are known, which can be used in particular as rotary actuators, in which the aforementioned pallet and partition are provided with a respective seal in order to avoid any leakage of fluid (hydraulic fluid or gas) between the rooms.
  • EP-A-0065588 also discloses a rotary hydraulic motor devoid of seals, corresponding to the state of the art defined in the preamble of claim 1.
  • This hydraulic motor of complex structure, therefore expensive to manufacture, does not allow leakage rates to be controlled because of its configuration which is incompatible with sufficiently precise machining and the use, between chambers, of partitions imperfectly maintained in a fixed position, resulting in short vanishing lines and unstable. In fact, it is thanks to the viscosity of the oil used to operate it, which reduces or even eliminates leaks, that this engine is free of seals.
  • the present invention aims to improve a fluidic device of the type considered so as to allow, despite the omission of any internal seal, to maintain the leakage rate between chambers at a very low and well defined level, with a pressurized fluid both liquid and gaseous, in particular thanks to the achievement of precise clearances between the various elements of the device and to the creation of creepage paths as long as possible.
  • the device according to the invention is characterized in that its constituent parts are made of a single material, that the casing is composed of a one-piece bell-shaped body and a flange attached to the body, that the fixed partition is formed in one piece with the flange, the surfaces of the cylindrical edges of said partition offering radii respectively equal, with very little play, to those of the cylindrical surfaces limiting externally and internally the annular space, that the shaft has, at least in its part extending inside the casing and in the bores offered by the latter for its passage, a cylindrical lateral surface everywhere of the same diameter, and that the pallet is constituted by the end of a bar of substantially parallelepiped shape attached to the shaft, and mounted in a housing radially hollowed therein, the lateral surface of the shaft being machined cylindrical ement before mounting the pallet, so that, in the assembled device, the pallet and the partition ensure, without seals, low, predetermined and stable fluid leaks from one room to another in the space annular, which the flange comprises, coaxially
  • the pallet and the partition ensure, without seals, negligible leakage of fluid from one chamber to another of the annular space.
  • the fact of dissociating the shaft and the pallet into two separate parts makes it possible to easily give the tree a cylindrical surface of extremely precise revolution, which is not possible when the shaft and the pallet are constituted by a unique piece.
  • this same characteristic leads to a geometrically perfect conformation of the edge of the re-entrant angles which appear between the surface of the shaft and the two sides of the pallet perpendicular to the axis thereof, while a re-entrant angle cannot be machined on a single piece in a perfect manner.
  • the lateral surface of the shaft as well as the surfaces of the pallet located opposite, with very little clearance, the base surfaces and the external cylindrical surface of the annular space, comprise a thin layer d '' a non-stick coating.
  • the shaft must be guided in the device housing by a pair of bearings capable of ensuring perfect positioning of a rotating part, such as plain bearings, bearings without radial play, hydrostatic bearings or passive or active magnetic bearings, the latter type of bearings being capable of providing both radial and axial shaft guidance.
  • a pair of bearings capable of ensuring perfect positioning of a rotating part, such as plain bearings, bearings without radial play, hydrostatic bearings or passive or active magnetic bearings, the latter type of bearings being capable of providing both radial and axial shaft guidance.
  • the device comprises, according to a known advantageous arrangement due to its symmetry, a second pallet and a second partition identical to the aforementioned pallet and partition and arranged in diametrically opposite position, each chamber thus being divided into two diametrically opposite compartments , between which is provided a respective communication channel passing through the shaft
  • the two pallets are, according to the invention, constituted by the ends of the aforementioned bar, which crosses the shaft right through, while the second partition is shaped and arranged in the same way as the first partition.
  • This bar can be either secured to the shaft by means of a centering member, or left sliding through the shaft.
  • the pallet or each of the two pallets that the device comprises can be made of composite material.
  • the realization of the component parts of the device in a single material allows it to operate in a wide temperature range.
  • the device according to the invention can be devoid of any internal seal, the leaks between chambers being nevertheless extremely low. This results in frictionless and wear-free operation of the component parts of the device, which offers excellent linearity and remarkable precision, and benefits from a very long service life with performances of exceptional stability. This is why it is particularly well suited for use as a drive unit in high-quality position controls.
  • FIG. 1 shows a fluidic device with a rotary paddle of the type considered. It comprises a shaft 1 which can rotate about its axis 2 inside a coaxial cylindrical casing 3.
  • an internal space 4 in the form of a circular ring with rectangular section, delimited by the lateral surface 1a of the shaft 1, by the surface of the internal bore 3a of the casing 3 and by two flat annular surfaces, centered on axis 2 and belonging to a pair of circular flanges not visible in the drawing.
  • the annular space 4 is divided into two chambers 4a, 4b by a fixed partition 5 and by a movable pallet 6, the latter rotating with the shaft 1.
  • the chambers 4a, 4b are connected to an external circuit of pressurized fluid (hydraulic or pneumatic) via orifices 7a, 7b drilled in the side wall of the casing 3. It is clear that when the fluid under pressure is applied to the chamber 4a via the orifice 7a, the orifice 7b of the chamber 4b being connected to the cover of the external circuit, the shaft 1 is rotated in the direction indicated by the arrow, the angle of rotation being limited to approximately 280 °.
  • the device thus constitutes a rotary actuator.
  • the tree 1 comprises a second pallet 6 ′, the two pallets 6, 6 ′ projecting from the shaft at the ends of the same diameter.
  • a second partition 5 ′ is provided, diametrically opposite the partition 5.
  • each chamber 4a, 4b is broken down into two compartments, respectively 4a1, 4a2 and 4b1, 4b2, diametrically opposite, the two compartments of each chamber being connected by a respective channel 8, 9 drilled through the shaft 1. Thanks to this symmetrical arrangement, the action of the pressurized fluid on the shaft is balanced, at the cost of reducing the maximum angle of rotation by this one at around 100 °.
  • FIG. 3 shows a double-acting pumping circuit using the device of FIG. 2, provided in addition with two complementary orifices 7′a, 7′b opening into the compartments 4a2, 4b1 of the chambers.
  • Each of the orifices 7a, 7b, 7′a, 7′b is associated with a non-return valve 10, mounted in the fluid circuit shown with a direction such that, by imparting an alternating rotational movement to the shaft 1, obtains continuous suction effects at point A and discharge at point B of the circuit fluid.
  • the device according to the invention which will be described with reference to Figures 4 and following, has the configuration illustrated in Figure 2, as immediately apparent from a comparison of this figure with Figure 4. It is composed of a stator comprising a casing 3 and two partitions 5, 5 ′ and a rotor comprising a shaft 1 of axis 2 and a double pallet 6, 6 ′, which defines, with the two fixed partitions 5, 5 ′, two divided chambers each in two compartments communicating through the shaft by channels 8, 9.
  • the double pallet 6, 6 ′ is formed by a bar 13, of rectangular section and of length equal to the diameter of the bore 3a, its ends being rounded to the radius of curvature of said bore.
  • This bar is mounted in a housing 14 produced through the shaft 1, in a diametrical direction ( Figure 6), with dimensions such that it receives exactly the bar 13 ( Figure 7).
  • the housing is made in two parts, which, after assembly, admit the axis 2 of the shaft 1 as axis of symmetry: a body 15 in the shape of a bell and a flange 16 which closes the space inside the body 15.
  • the body 15 and the flange 16 each have a central bore, respectively 17 and 18, allowing the passage of the shaft 1.
  • the body 15 has another bore, of larger diameter, which n is other than the bore 3a externally limiting the annular space inside the casing which extends around the shaft 1.
  • n is other than the bore 3a externally limiting the annular space inside the casing which extends around the shaft 1.
  • Between these two bores 3a, 17 appears a plane annular shoulder 11 which forms one of the base surfaces limiting said space in the axial direction, the other annular base surface 12 appearing on the flange 16, around the bore 18.
  • This annular surface 12 is surrounded by another planar annular surface 19, forming an assembly flange, on which applies the casing 15 by a surface an planar ring 20 which the latter comprises.
  • the flange 19 is pierced with holes 21 arranged in a ring around the axis 2 and oriented parallel to it, these holes being intended to receive bolts 22 which are screwed into tapped holes 23 conjugated drilled in the annular surface 20 of the body 15, these bolts thus making it possible to assemble the latter and the flange 16 to form the casing 3.
  • a pin 24 for angular positioning is provided projecting from the surface 20 of the body 25; it is housed in a corresponding hole 25 drilled in the surface 19 of the flange 16.
  • the partitions 5, 5 ′ are integral with the flange 16, being formed by protuberances which rise in direction parallel to the axis 2, from the annular surface 12, their radially inner surface 27 directly extending the surface of the bore 18 of the flange.
  • the surface 12 is raised relative to the surface 19, so that the cylindrical skirt of the body 15 surrounding the bore 3a fits around said surface 12 in relief, its bore 3a fitting closely on a circular cylindrical shoulder 26 which appears between the surfaces 12 and 19 due to their offset in the axial direction.
  • the radially outer surface 28 of the partitions 5, 5 ′ extends in direct extension of the cylindrical surface of the shoulder 26.
  • a bar 13 is machined in order to give it the rectangular section a ⁇ b desired for the double pallet 6, 6 ′ (a being the width, and b the thickness in the direction of the axis 2 which will be the axis of the double pallet after assembly).
  • a blind hole 29 is drilled in the center of one of the faces of width a and the length of the bar is adjusted to a value slightly greater than the desired value, by machining its end faces along a cylindrical surface of the same axis 2 as the hole 29.
  • a light milling 30 is carried out at the ends of the faces of width b so that, in the completed device, the compartments 4a1, 2, 4b1, 2 of the chambers offer a non-zero minimum volume when the double pallet 6, 6 ′ is in limit switch (figure 4).
  • the shaft 1 is produced in the form of a cylinder of revolution and there is hollowed out, by electro-erosion, the housing 14 at dimensions a ⁇ b of the bar 13 constituting the double pallet 6, 6 ′.
  • the bar 13 is put into place in the housing 14 of the shaft 1, the bar being centered by a screw 31 engaged in a threaded hole 32 drilled axially at one of the ends of the shaft 1, this hole opening into the housing 14 so that the non-threaded end 31a of the screw, of diameter conjugate with that of the hole 29 of the bar 13, penetrates therein (FIG. 5).
  • the flange 16 is then produced from a thick disc in which the central bore 18 is machined with a diameter very slightly greater than the diameter of the shaft 1, then the annular surface 19, and the central ring appears. remaining, by milling, then radial grinding using a grinding wheel of thickness equal to the width a of the bar 13, the two partitions 5, 5 ′, leaving to this crown a residual height c (figure 6) corresponding to the projecting offset that the annular surface 12 must have, from which the partitions 5, 5 ′ rise, over a height h1 very slightly greater than the thickness b of the bar 13.
  • the machining of the body 15 includes the production, coaxially around the same axis which will be the axis 2 of the completed device, of the bore 17, identical to the bore 18 of the flange 16, these two bores serving as bearings to the cylindrical shaft 1, and the bore 3a, of diameter very slightly greater than the outside diameter of the crown of the flange which gave rise to the partitions 5, 5 ′ and to the raised annular surface 12, so that this bore can fit exactly around the shoulder 29 which externally limits the surface 12 and whose diameter is very slightly greater than the diameter of the cylindrical ends of the bar 13.
  • the two bores 17, 3a are connected by the annular shoulder 11 whose width radial is equal to that of the annular surface 12 of the flange.
  • the height h2 of the bore 3a, between the planes of the annular surfaces 12 and 20, is very slightly greater than the thickness b of the pallet increased by the nesting depth c of said bore ( Figure 5).
  • the surfaces of the component parts of the device which define the internal chambers are machined with very high precision so as to present dimensions with very low tolerance and an excellent surface condition.
  • the clearances between the various parts can be extremely reduced, namely by about 5 ⁇ m.
  • the clearances between the pallet faces 6, 6 ′ perpendicular to the axis 2 and the annular surfaces 11, 12 are slightly larger, of the order of 10 ⁇ m, in order to avoid any contact between the pallet and the casing. even if the shaft 1 takes a very slight obliquity with respect to the axis 2 due to the minimal clearances which exist between said shaft and its bearings constituted by the bores 17 and 18.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Actuator (AREA)
  • Toys (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Rotary Pumps (AREA)
  • Centrifugal Separators (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Drying Of Solid Materials (AREA)

Claims (9)

1. Fluidvorrichtung mit Drehschaufel zur Verwendung entweder als Motor (Drehzylinder) oder als Empfänger (Pumpe mit Wechselbetätigung), umfassend ein ortsfestes Gehäuse (3), durch das eine um ihre Achse drehbare und die Schaufel (6) tragende Welle (1) führt, wobei der innerhalb des Gehäuses befindliche Raum unter Bildung eines um die Welle umlaufenden Ringraumes, dessen Querschnitt in einer radialen Ebene rechteckig ist und der von zwei planen Basisringflächen (11, 12) und zwei koaxialen Zylinderflächen (1a, 3a), d.h. einer inneren bzw. einer äußeren, begrenzt ist, in zwei Kammern (4a, 4b) von komplementär veränderlichem Volumen geteilt ist, u.zw. durch eine gegenüber dem Gehäuse feststehende radiale Wand (5) und durch die mit der Welle (1) drehbewegliche Schaufel (6), in welcher Vorrichtung die Schaufel (6) derart bearbeitet ist, daß sie eine Dicke (b) ― in Richtung der Achse der Welleaufweist, die mit einem sehr geringen knappen Spiel gleich dem Abstand (h₂ - c) ist, welcher die beiden den Ringraum in derselben Richtung begrenzenden planen Ringflächen (11, 12) trennt, sowie eine Länge und zylindrische Ausgestaltung ihres Endes aufweist, sodaß sich die Oberfläche ihres Endes nach Befestigung der Schaufel an der Welle auf einem zur Welle koaxialen Drehzylinder mit einem Radius befindet, welcher mit einem sehr geringen knappen Spiel gleich jenem der den Ringraum außen begrenzenden Zylinderfläche (3a) ist, und die Trennwand (5) derart bearbeitet ist, daß sie eine Dicke (h₁) ― in Richtung der Achse (2) ― aufweist, die mit einem sehr geringen knappen Spiel gleich dem die beiden Ringflächen (11, 12) trennenden Abstand (h₂ - c) ist, sowie eine zylindrische Ausgestaltung ihrer radial an die Welle (1) und an das Gehäuse (3) stoßenden Rändern (27, 28) aufweist, sodaß sich die Oberflächen dieser Ränder nach Zusammensetzen der die Vorrichtung bildenden Elemente auf zur Welle (1) koaxialen Rotationszylindern befinden, dadurch gekennzeichnet, daß ihre Bauteile aus einem einzigen Material hergestellt sind, daß das Gehäuse (3) aus einem einstückigen glockenähnlichen Körper (15) und einem am Körper angesetzten Flansch (16) zusammengesetzt ist, daß die feststehende Trennwand (5) einstückig mit dem Flansch (16) ausgebildet ist, wobei die Oberflächen der zylindrischen Ränder (27, 28) der Trennwand Radien aufweisen, die mit einem sehr geringen knappen Spiel jeweils gleich jenen der den Ringraum außen und innen begrenzenden Zylinderflächen (3a, 1a) sind, daß die Welle (1) zumindest in ihrem sich innerhalb des Gehäuses (3) und in den für ihren Durchtritt in diesem vorgesehenen Bohrungen (17, 18) erstreckenden Teil eine zylindrische Seitenfläche (1a) von überall gleichem Durchmesser aufweist, und daß die Schaufel (6) durch das Ende eines Stabes (13) von im wesentlichen parallelepipedischer Form gebildet ist, welcher auf der Welle (1) aufgesetzt und in einer radial in derselben gebohrten Aufnahme (14) gelagert ist, wobei die Seitenfläche (1a) der Welle (1) vor dem Einbau der Schaufel zylinderförmig bearbeitet wird, sodaß die Schaufel (6) und die Trennwand (5) bei zusammengebauter Vorrichtung ohne Dichtungsfugen schwache, vorbestimmte und unveränderliche Fluidleckagen von einer Kammer in die andere Kammer des Ringraumes gewährleisten, daß der Flansch (16), die zentrale Bohrung (18) für den Durchtritt der Welle (1) koaxial umgebend, eine erste plane Ringfläche aufweist, die eine (12) der Basisflächen des Ringraumes bildet und von der die Trennwand (5) aufragt, radial begrenzt von den Flächen (27, 28) mit Radien, die jeweils gleich sind den Begrenzungsradien der ersten Ringfläche (12), wobei letztere von einer zweiten, planen Ringfläche (19) umgeben ist, auf welcher der Körper (15) nach dem Zusammenbau ruht, wobei der Körper und der Flansch in zusammengebautem Zustand dieselbe Achse, die mit der Achse (2) der Welle (1) zusammenfällt, aufweisen, und daß die erste Ringfläche (12) des Flansches (16) gegenüber seiner zweiten Ringfläche (19) erhaben ist, wobei die beiden Flächen über eine kreisförmig-zylindrische Schulter (26) aneinander anschließen, auf welcher der Körper (15) mit seiner Bohrung (3a), die die den Ringraum außen begrenzende Zylinderfläche festlegt, genau aufsteckbar ist.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß sie eine zweite Schaufel (6′) und eine zweite Trennwand (5′) umfaßt, die identisch zur Schaufel (6) bzw. zur Trennwand (5) und diametral entgegengesetzt angeordnet sind, wodurch jede Kammer (4a, 4b) in zwei diametral gegenüberliegende Abteile (4a1, 4a2, 4b1, 4b2) geteilt ist, zwischen denen jeweils ein durch die Welle gehender Verbindungskanal (8, 9) vorgesehen ist, wobei die beiden Schaufeln (6, 6′) durch die Enden des Stabes (13) gebildet sind, welcher die Welle (1) vollkommen durchragt, und die zweite Trennwand (5′) auf dieselbe Weise wie die erste Trennwand (5) ausgebildet und angebracht ist.
3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Stab (13) durch ein Zentrierorgan (31) mit der Welle verbunden ist.
4. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Stab (13) durch die Welle (1) gleiten gelassen wird.
5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Seitenfläche (1a) der Welle (1) sowie die Flächen der Schaufel (6), die sich mit sehr geringem Spiel gegenüber den Basisflächen (11, 12) und der zylindrischen Außenfläche (3a) des Ringraumes befinden, eine dünne Schicht einer Antihaftbeschichtung aufweisen.
6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Welle (1) durch ein Paar Gleitlager im Gehäuse (3) geführt ist.
7. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Welle (1) durch ein Paar Wälzlager ohne radiales Spiel im Gehäuse (3) geführt ist.
8. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Welle (1) durch ein Paar hydrostatische Lager im Gehäuse (3) geführt ist.
9. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Welle (1) durch ein Paar passive oder aktive Magnetlager im Gehäuse (3) geführt ist.
EP19880400535 1987-03-18 1988-03-08 Druckmittelbetriebener Schwenkflügelmotor ohne innere Dichtungen Expired - Lifetime EP0283380B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88400535T ATE68567T1 (de) 1987-03-18 1988-03-08 Druckmittelbetriebener schwenkfluegelmotor ohne innere dichtungen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8703745 1987-03-18
FR8703745A FR2612572B1 (fr) 1987-03-18 1987-03-18 Dispositif fluidique a palette rotative sans joint d'etancheite interne

Publications (3)

Publication Number Publication Date
EP0283380A2 EP0283380A2 (de) 1988-09-21
EP0283380A3 EP0283380A3 (en) 1989-09-27
EP0283380B1 true EP0283380B1 (de) 1991-10-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880400535 Expired - Lifetime EP0283380B1 (de) 1987-03-18 1988-03-08 Druckmittelbetriebener Schwenkflügelmotor ohne innere Dichtungen

Country Status (9)

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EP (1) EP0283380B1 (de)
AT (1) ATE68567T1 (de)
DE (1) DE3865470D1 (de)
DK (1) DK165706C (de)
ES (1) ES2026665T3 (de)
FR (1) FR2612572B1 (de)
IE (1) IE60733B1 (de)
NO (1) NO171872C (de)
PT (1) PT86953B (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5394766A (en) * 1992-07-21 1995-03-07 The Walt Disney Company Robotic human torso
FR2754021B1 (fr) * 1996-09-30 1998-10-30 Bernard Amalric Verin telescopique rotatif a palettes
DE19821435C2 (de) * 1998-05-13 2000-05-04 Bar Pneumatische Steuerungssys Schwenkantrieb zur Betätigung einer Armatur
IT1398128B1 (it) * 2009-03-27 2013-02-14 Rovel S R L Attuatore azionato da un fluido in pressione
CN104564512B (zh) * 2014-12-19 2016-08-24 合肥创源车辆控制技术有限公司 一种液力马达
JP2020002966A (ja) * 2018-06-26 2020-01-09 川崎重工業株式会社 ロータリアクチュエータおよびロボット鉗子

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1171749B (de) * 1960-02-06 1964-06-04 F E Weatherill Ltd Hydraulischer Drehstellmotor
GB1468167A (en) * 1973-06-13 1977-03-23 Simms Group Res Dev Ltd Rotary fluid pressure actuators
DE3176067D1 (en) * 1981-05-26 1987-05-07 Torquer Co Hydraulic actuator of the oscillating-vane type

Also Published As

Publication number Publication date
FR2612572A1 (fr) 1988-09-23
PT86953A (pt) 1989-03-30
FR2612572B1 (fr) 1991-04-12
ES2026665T3 (es) 1992-05-01
NO171872C (no) 1993-05-12
DK150188D0 (da) 1988-03-18
IE60733B1 (en) 1994-08-10
EP0283380A3 (en) 1989-09-27
PT86953B (pt) 1995-03-01
DE3865470D1 (de) 1991-11-21
NO881181D0 (no) 1988-03-17
NO171872B (no) 1993-02-01
NO881181L (no) 1988-09-19
IE880639L (en) 1988-09-18
ATE68567T1 (de) 1991-11-15
DK150188A (da) 1988-09-19
EP0283380A2 (de) 1988-09-21
DK165706B (da) 1993-01-04
DK165706C (da) 1993-05-24

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