EP0136492A1 - Moteur à piston oscillant - Google Patents

Moteur à piston oscillant Download PDF

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Publication number
EP0136492A1
EP0136492A1 EP84109583A EP84109583A EP0136492A1 EP 0136492 A1 EP0136492 A1 EP 0136492A1 EP 84109583 A EP84109583 A EP 84109583A EP 84109583 A EP84109583 A EP 84109583A EP 0136492 A1 EP0136492 A1 EP 0136492A1
Authority
EP
European Patent Office
Prior art keywords
shaft
piston
shell
housing
engine according
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
EP84109583A
Other languages
German (de)
English (en)
Other versions
EP0136492B1 (fr
Inventor
Kurt Dipl.-Ing. Stoll
Georg Heid
Gerhard Schrag
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.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
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
Priority claimed from DE19833337422 external-priority patent/DE3337422C2/de
Application filed by Festo SE and Co KG filed Critical Festo SE and Co KG
Priority to AT84109583T priority Critical patent/ATE25750T1/de
Publication of EP0136492A1 publication Critical patent/EP0136492A1/fr
Application granted granted Critical
Publication of EP0136492B1 publication Critical patent/EP0136492B1/fr
Expired 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 invention relates to a hydraulic or pneumatic rotary drive in the form of a swinging piston engine according to claim 1.
  • a wide variety of designs of a hydraulic or pneumatic rotary drive are known from the prior art, in which the linear movement of a piston-cylinder device is converted into a rotary movement by means of a movement forming gear.
  • Such rotary drives have the disadvantage that a relatively complex gear is required. As a result, they are complicated in construction, space-consuming and can only be produced and assembled at comparatively high costs.
  • the object of the invention is to provide a hydraulic or pneumatic rotary drive which is extremely simple in construction, which is simple and inexpensive to produce. In particular, a design with few individual parts is sought, and extensive reworking of the individual parts during production should be avoided as far as possible. Another goal is to create a rotary actuator that is as possible is universally applicable and in particular enables a large number of different switching rotation angles to be set.
  • a rotary drive in the form of a hydraulic or pneumatic swing piston motor, the angle of rotation of which is adjustable by means of a fixed stop.
  • Fig. 1 shows the basic structure of the swing piston engine according to the invention.
  • This has a housing 1 and a shaft 2 rotatably mounted in the housing 1.
  • the shaft 2 is driven by means of a hydraulic or pneumatic pressure medium and into a back and forth movement offset, the switching angle of the shaft 2 can be specified within certain limits.
  • the drive takes place via a swivel piston 3, which is connected in a rotationally fixed manner to the shaft 2.
  • the pivoting piston 3 divides two working spaces 4, 5 in the housing 1.
  • a connection 6 for the pressure medium opens into each of the working spaces 4, 5. If the working space 4 is pressurized on one side of the pivoting piston 3 and the other working space 5 is relieved of pressure by means of a control circuit (not shown), the pivoting piston 3, which drives the shaft 2, rotates.
  • the pressure medium supply is reversed, so that the pressure medium loading and pressure relief of the working spaces 4, 5 is reversed.
  • the shaft 2 rotates in the opposite direction.
  • the shaft 2 is led out of the housing 1, and it allows coupling any load, which is thus rotated by a motor.
  • the angle of rotation of the pivoting piston 3 or the shaft 2 is structurally limited. In the illustrated embodiment, the maximum angle of rotation is 180 °, which has proven to be excellent for many practical applications.
  • the rotation angle is limited by end stops 7, which are molded onto the housing 1 or are firmly connected to the housing 1 and lie in the path of movement of the pivoting piston 3.
  • the pivoting piston 3 runs onto the end stops 7 and thereby reaches 180 offset end positions in the housing 1, one of which is shown on the right in FIG. 1. Apart from these end stops 7, according to the invention there is at least one fixed stop, not shown in FIG. 1, which allows a smaller angle of rotation than 180 ° to be set as desired.
  • the wing 8 and the shoulder 9 each run sealingly on circular cylindrical lateral surfaces of the housing 1.
  • the outer surfaces 11, 12 are arranged coaxially with respect to the axis of rotation 10 of the shaft 2, and the outer surface 11 assigned to the wing 8 has a substantially larger diameter than the outer surface 12 sealing the attachment 9.
  • the outer surfaces 11, 12 are curved in the opposite direction, and they are diametrically opposed to each other with their opening.
  • the angular extent of the lateral surfaces 11, 12 essentially corresponds to the maximum angle of rotation of the pivoting piston 3, ie 180 ° in the exemplary embodiment shown. Smaller deviations result from the thickness of the pivoting piston 3 and the design of its seals.
  • a sealing body 13 can be seen, which covers both side walls 14 and the end face 15 of the wing 8.
  • This sealing body 13 runs with two laterally projecting lips 16 on the lateral surface 11, which extends over a little more than 180 ° in order to enable the sealing body 13 to make a sealing contact even in the end positions of the pivoting piston 3.
  • the lateral surface 12 assigned to the extension 9 extends over an angle of somewhat less than 180 ° . It is provided in the area between the end stops 7, and the extension 9 is covered with a sealing body 17 which projects between the stops 7 in the end positions of the pivoting piston 3.
  • the sealing body 17 has a bell shape widening away from the shaft 2, and it carries three symmetrically arranged sealing lips on its radial outside.
  • the outer contour of the housing 1 essentially follows the course of the lateral surfaces 11, 12 on which the pivoting piston 3 runs in a sealed manner.
  • the outer jacket 19 of the housing 1 also has a semicircular plan.
  • a triangular outline was chosen for the outside of the housing 1, the legs of the triangle enclosing an obtuse angle and receiving the circular-cylindrical lateral surface 12 assigned to the projection 9 between them.
  • the housing 1 is cylindrical with respect to the base area thus defined, the generatrix of the cylinder being perpendicular to the plane of the drawing in FIG. 1.
  • the height of the housing can be varied according to the desired piston area; in the interest of a high drive torque, however, a flat housing design is preferred, in which the height of the housing 1 'is smaller than the radial extension of the pivoting piston 3.
  • the described pivoting piston motor is obviously extremely compact, and, based on the housing size, a remarkably high size is obtained Drive torque.
  • Particular advantages in terms of production result if the housing 1 is divided into a semi-cylindrical shell 21 and a cover 22 in a separation plane indicated at 20. The division is selected so that the shell 21 contains the lateral surface 11 assigned to the wing 8 and the cover 22 contains the lateral surface 12 sealing the attachment 9.
  • FIGS. 2 to 5 a further exemplary embodiment of the oscillating piston engine according to the invention is shown in more detailed technical details.
  • Fig. 2 shows a somewhat modified form of the housing 1. This in turn consists of a shell 21 and a cover 22 closing this shell 21.
  • the shell 21 has a semicircular cylindrical portion 23, the cylinder axis of which coincides with the axis of rotation of the shaft 2.
  • the shaft 2 is received in bearing bushes 24 which are molded onto the shell 21. It protrudes from the shell 21 at both ends, a free end 25 serving to couple a load, not shown.
  • a stop device 26 is provided which allows the angle of rotation of the pivoting piston 3 or the shaft 2 to be set.
  • an extension 27 of the shell 21 adjoins the cover 22. This is in one piece and molded onto the shell 21 with a smooth transition. Overall, it gives it a floor plan in the form of a cut oval, with respect to which the shell 21 is essentially cylindrical.
  • the shell 28 of the shell is closed in the region of the semicircular cylindrical part 23 and laterally on the extension 27.
  • the flat rear side of the shell facing away from the semicircular cylindrical portion 23 21 open so that the pivoting piston 3 can be installed from this side. After assembly of the pivoting piston 3, the opening is closed by means of the cover 22.
  • Shell 21 and cover 22 are clamped in a manner described in more detail by means of a band which is placed around the jacket 28 of the shell 21.
  • the band is fastened to the cover 22 by means of two tie rods; 2 mounting holes 29 in the cover 22 can be seen in FIG. 2.
  • the mounting holes 29 lie at the level of the casing 28 and they receive the tie rods from the rear of the cover 22.
  • Fig. 3 shows the swing piston engine in section, the free end 25 of the shaft 2 now protruding downward.
  • This end carries an axially extending, projecting driver 30, which gives the end 25 a non-circular shape.
  • driver 30 can, if necessary, via spacers, etc. a load can be coupled in a convenient manner.
  • the shaft 2 is suitably received in the bearing bushes 24, a guide sleeve 31 being provided in a bearing bush 24.
  • the depth of insertion of the shaft 2 into the housing 1 is limited by means of a collar 32, which comes to rest on the end face of one of the bearing bushes 24, and on the opposite side of the housing, the shaft 2 is captively supported against the housing 1 by the stop device 26.
  • the shaft of the shaft 2 is provided over part of its length with jacket teeth 34 running in the axial longitudinal direction, which can be seen in FIG. 3 in an uncut plan view.
  • a step toothing is selected, the tooth flanks of which run essentially radially.
  • the Mantelverstattun g / serves to twist-proof connection between the shaft 2 and the pivoting piston 3 and a disk 35 of the stop device 26.
  • the shaft 2 protrudes with a toothed section on the side facing away from its free end 25 from the bearing bush 24 of the housing 1.
  • the disc 35 has a matching counter-toothing on the circumference of a central bore, by means of which it can be positively attached to the shaft 2.
  • the disc 35 comes to rest on the end face of the bearing bush 24, and it is locked in this mounting position by means of a locking ring 36 on the shaft of the shaft 2.
  • the locking ring 36 engages in the manner of a snap ring in a circumferential groove on the casing of the shaft 2. Apart from the non-rotatable connection between the shaft 2 and the disk 35, a captive mounting of the shaft 2 in the housing 1 is achieved at the same time.
  • the disk 35 carries at least one stop body 37 (cf. FIG. 4), which can be adjusted in angle on the disk 35.
  • the stop body 37 can in particular have a pie-like shape, ie on its sides facing the shaft 2 or away from it by circular cylinders.
  • the stop body 37 runs on a counter stop 38 fixed to the housing (see FIG. 3).
  • the counter stop 38 is formed on the cover 22.
  • the counter stop 38 has the same pie slice shape
  • a single stop body 37 is sufficient to adjust the angle of rotation of the swivel piston motor according to the invention, but an arrangement with two stop bodies / which limit the angle of rotation at both ends is preferred, the latter on opposite sides of the counterstop 38 run.
  • the stop body 37 consist of two mutually adjustable jaws 40, which come to rest on both sides of the disc 35 in the mounted state.
  • the required clearance at the bottom 41, i. H. the side of the disk 35 facing the housing 1 is ensured by its arrangement on the protruding bearing bush 24.
  • the free space is restricted only in the area of the counter-stop 38, which projects right up to the underside 41 of the disk 35.
  • the jaw 40 of the stop body 37 resting against this underside 41 has a threaded bore which is aligned with the elongated hole 39 in the disk 35.
  • a screw 43 engages in this threaded bore, which has an abutment in the other jaw 40 and clamps the stop body 37 on the disk 35.
  • the stop body 37 can be continuously adjusted in the elongated hole 39, which results in a stepless adjustment for the angle of rotation of the oscillating piston engine.
  • a latching according to the tongue and groove principle can also be provided.
  • a tooth or the like, not shown, is preferably on the inner jacket of the hood 44. formed, which positively falls into a matching notch on the outer circumference of the disc 35.
  • the hood 44 is provided on its upper side with openings 47, which allow the penetration of a tool for adjusting the stop body 37.
  • the openings 47 can, for example, follow the course of the elongated holes 39 on the disk 35, i. H. lie in a circular arc around the center of rotation of the hood 44. However, other shapes for the openings 47 are also possible.
  • the openings 47 allow a screwdriver to reach the head of the screws 43, by means of which the stop bodies 37 are screwed onto the disk 35. The screws 43 can be loosened, the stop body 37 adjusted on the disk 35 and the screws 43 tightened again.
  • the pivoting piston 3 shows the two-part construction of the housing 1 from a shell 21 and a cover 22 that closes the shell 21.
  • the pivot piston 3 runs with the majority of the piston surface in the shell 21, and it is both against the shell 21 and also sealed against the cover 22.
  • the pivot piston 3 consists in particular of a non-rotatable bush 49 and a shaft 49 molded, radially projecting wing 50.
  • the bushing 49 carries on its inner jacket an axially extending counter-toothing that fits the toothing on the shaft 2.
  • the counter toothing is thus also contoured in a step-like manner in the exemplary embodiment shown, the tooth flanks running essentially radially.
  • the pivoting piston 3 can be plugged onto the shaft 2 with this toothed bush 49, and it is then non-rotatably connected to the shaft 2.
  • the pivoting piston is sealed against the shell 21 by means of a seal 51.
  • This seal 51 occupies the outer edge of the wing 50, and it is still placed in the area of the bushing 49 around the shaft 2.
  • the bushing 49 is provided on its two axial end faces with a circumferential ring step which receives the seal 51.
  • the sealing parts on the end faces of the bushing 49 are connected to one another via the sealing part on the outer edge of the wing 50.
  • the entire seal 51 is preferably manufactured in one piece and can be positively fixed on the surface of the pivoting piston 3.
  • the seal 51 can in particular be sprayed onto the pivoting piston 3 made of plastic.
  • the pivoting piston 3 is also sealed in its area near the shaft against the cover 22.
  • the bushing 49 with the part of its casing facing away from the wing 50 runs on a seal 52 which is attached to the cover 22.
  • the seal 52 between swivel body 3 and cover 22 is in the illustrated embodiment stretched between the shell 21 and the lid 22. It sits with a flange-like section 53 in a groove of the cover 22 and covers the bottom and the inner boundary wall of the groove.
  • an intermediate space remains between the outer boundary wall of the groove and the seal 52, into which the edge 54 of the shell 21 can be inserted.
  • the edge 54 of the shell 21 presses the seal 52 into the groove, the depth of engagement of the shell 21 into the groove being limited by a step 55 on the outer edge of its end face. By means of this stage 55, the shell 21 with the cover 22 comes into flush contact.
  • a sealing web 56 extends, on which the bush 49 of the pivoting piston 3 runs.
  • the construction according to the invention makes it possible to use one and the same seal 52 both for sealing the pivoting piston 3 and for the necessary seal between the shell 21 and the cover 22.
  • the seal 52 extends with its flange-like section 53 Uby 2 the entire edge of the shell 21, and the seal / receiving groove in the cover 22 is contoured in accordance with the outer shape of the shell 21 in the region of its edge 54.
  • the groove can have an oval shape.
  • a band 57 which is preferably made of steel, is used for tensioning.
  • the band 57 is received between two webs 58, which are formed parallel and at a distance from one another on the outer jacket of the shell 21.
  • the band 57 is held on both ends of the cover 22 by means of two tie rods 59 (see FIG. 5).
  • the tie rods 59 each contain a pin 60 which is fixed to the end of the band 57.
  • the pin 60 can be soldered to the band 57, for example, and in particular hard-soldered.
  • the end of the pin 60 facing away from the band 57 is received in a stepped housing bore 61 in the cover 22.
  • the pin 60 has an external thread, and on this external thread a nut 62 can be screwed, which is supported against a step 63 of the housing bore 61.
  • the nut 62 is countersunk in the housing bore 61 on the side of the cover 22 facing away from the disk 21. Rotating the nut 62 by means of a suitable actuating tool leads to an axial displacement of the pin 60, which in turn rests non-rotatably on the housing / via the band 57; this tensions the band 57. Due to the two-sided reception of the band 57 in tie rods 59, the tensile stress can be transmitted uniformly to the shell 21 and the cover 22, and tilting of these two parts during assembly is effectively avoided.
  • the band connection according to the invention of the housing parts is structurally simple, inexpensive and particularly secure. In particular with a metal, e.g. B. die-cast, manufactured housing but also other forms of connection come into consideration, for example by screwing.
  • the structure of the shell 21 can be seen again from an essentially semicircular cylindrical section 23 and an extension 27 formed thereon, which protrudes beyond a central cylinder plane containing the axis of rotation 10 of the pivoting piston 3 and guide sleeves 31, bearing eyes or the like.
  • Bearing means for receiving the shaft 2 carries.
  • the shell 21 is in one piece in the entire sealing and working area of the pivoting piston 3. In particular, no housing sealing points occur in the running area of the swivel piston wing 50.
  • the shell 21 can be made from plastic or cast metal without bumps and burrs, the demolding taking place from the opening which is closed with the cover 22.
  • This form of production is particularly cost-effective, and it has the advantage that the sealing area of the pivoting piston 3 does not require any post-processing.
  • the radial outside of the shell 21 is rounded off in the exemplary embodiment shown, only the jacket region between the webs 58 receiving the band offers a flat contact surface.
  • the wing 50 of the pivoting piston 3 is profiled in accordance with the contour of the shell 21.
  • the lid 22 is essentially flat. It carries two connections for the pressure medium, not shown in the figures, which each open into one of the working spaces 4, 5 divided by the pivoting piston 3.
  • the oscillating piston engine according to the invention is extremely compact in construction and it manages with a very small number of individual parts. Compared to conventional pinion designs, space savings of around 50% and cost savings of around 30% can be achieved.
  • the assembly of the swing piston engine is extremely simple.
  • the pivoting piston 3 is inserted into the shell 21, the shaft 2 is inserted through the toothed bushing 49, the stop device 26 is mounted and the shell 21 is closed with the cover 22.
  • a structure without a stop device 26 is also readily possible
  • the oscillating piston motor can be built in a simple and advantageous manner with integrated signal transmitters for pneumatic or electrical control.
  • the infinitely adjustable swivel range ensures universal application options as a hydraulic or pneumatic rotary drive.
  • An adjustable maximum rotation angle of 180 0, to which the individual components are preferably adapted more than 180 to a rotation angle of slightly is preferred to allow a compensation of manufacturing tolerances.
  • Application examples are the actuation of doors, windows, flaps such as silo flaps and fittings.
  • the motor according to the invention can perform a variety of actuating movements, e.g. B. Set the course in conveyor systems, open and close valves, clamp and release vices, etc.
  • Other options for the oscillating piston motor are robot arms, manipulators, transfer, turning and stamping stations; Furthermore, stirring and bending devices and lifting devices can be operated.
  • Rotary index limited rotary indexing tables can be operated with a single swing piston motor according to the invention; In a preferred use of a plurality of swiveling piston motors which operate intermittently and act on the same shaft via a one-way clutch, a slow-running circular drive can also be realized. There are other possible applications for harmonic linear drives, windshield wiper drives and use as a pneumatic torsion spring.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Compressor (AREA)
  • Hydraulic Motors (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
EP84109583A 1983-08-31 1984-08-11 Moteur à piston oscillant Expired EP0136492B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84109583T ATE25750T1 (de) 1983-08-31 1984-08-11 Schwenkkolbenmotor.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3331382 1983-08-31
DE3331382 1983-08-31
DE19833337422 DE3337422C2 (de) 1983-10-14 1983-10-14 Hydraulischer oder pneumatischer Schwenkkolbenmotor
DE3337422 1983-10-14

Publications (2)

Publication Number Publication Date
EP0136492A1 true EP0136492A1 (fr) 1985-04-10
EP0136492B1 EP0136492B1 (fr) 1987-03-04

Family

ID=25813609

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84109583A Expired EP0136492B1 (fr) 1983-08-31 1984-08-11 Moteur à piston oscillant

Country Status (4)

Country Link
US (1) US4611530A (fr)
EP (1) EP0136492B1 (fr)
KR (1) KR880000983B1 (fr)
AT (1) ATE25750T1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2165589A (en) * 1984-10-13 1986-04-16 Festo Kg Hydraulic or pneumatic oscillating-piston motor
EP0632204A1 (fr) * 1993-05-29 1995-01-04 Festo KG Ailette pour un actionneur rotatif
EP1520996A2 (fr) * 2003-10-04 2005-04-06 Festo AG & Co Vérin rotatif actionné par fluide
CN106481362A (zh) * 2015-08-28 2017-03-08 郑恒 一种新型摆动式气动马达

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9203536U1 (de) * 1992-03-17 1992-05-07 Naumann, Willi, 7560 Gaggenau Vorrichtung zum Ausführen von Winkelschrittbewegungen mit einem pneumatisch gesteuerten Rundschaltteller
JPH10110706A (ja) * 1996-10-08 1998-04-28 Mitsubishi Electric Corp 回転式油圧アクチュエータ
USD419183S (en) * 1998-03-16 2000-01-18 Stouffer Industries, Inc. Locking hub
US9957831B2 (en) * 2014-07-31 2018-05-01 The Boeing Company Systems, methods, and apparatus for rotary vane actuators

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB688917A (en) * 1950-04-03 1953-03-18 William Edward O Shei Improvements in or relating to differential fluid pressure motors of the oscillatingpaddle type
BE652317A (fr) * 1963-08-26 1964-12-16
US3688645A (en) * 1970-06-29 1972-09-05 Matryx Corp Vane-type actuator
DE2808375A1 (de) * 1978-02-27 1979-08-30 Suedhydraulik Marktoberdorf Ko Drehkolbenzylinder mit justierbarer schwenkwinkelbegrenzung und endlagendaempfung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR652317A (fr) * 1927-09-10 1929-03-07 Spiegel May Perfectionnements aux mécanismes sélecteurs plus particulièrement employés dans les machines à imprimer les adresses
US2209921A (en) * 1937-06-12 1940-07-30 Trico Products Corp Windshield cleaner motor
US2741702A (en) * 1952-02-09 1956-04-10 Keen Harry Automatic tuning system for transmitters and receivers
US2786455A (en) * 1954-01-04 1957-03-26 Gen Motors Corp Fluid motor
GB1210941A (en) * 1968-02-22 1970-11-04 Serck Industries Ltd Improvements in or relating to pressure fluid operating actuators
GB1443516A (en) * 1972-07-21 1976-07-21 Nash A R B Actuators
US4263840A (en) * 1979-10-29 1981-04-28 Stratobrake Corporation Safety brake mechanism
DE3337422C2 (de) * 1983-10-14 1985-10-10 Festo KG, 7300 Esslingen Hydraulischer oder pneumatischer Schwenkkolbenmotor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB688917A (en) * 1950-04-03 1953-03-18 William Edward O Shei Improvements in or relating to differential fluid pressure motors of the oscillatingpaddle type
BE652317A (fr) * 1963-08-26 1964-12-16
US3688645A (en) * 1970-06-29 1972-09-05 Matryx Corp Vane-type actuator
DE2808375A1 (de) * 1978-02-27 1979-08-30 Suedhydraulik Marktoberdorf Ko Drehkolbenzylinder mit justierbarer schwenkwinkelbegrenzung und endlagendaempfung

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2165589A (en) * 1984-10-13 1986-04-16 Festo Kg Hydraulic or pneumatic oscillating-piston motor
FR2571785A1 (fr) * 1984-10-13 1986-04-18 Festo Kg Moteur a piston oscillant
US4784047A (en) * 1984-10-13 1988-11-15 Kurt Stoll Oscillating piston motor
EP0632204A1 (fr) * 1993-05-29 1995-01-04 Festo KG Ailette pour un actionneur rotatif
EP1520996A2 (fr) * 2003-10-04 2005-04-06 Festo AG & Co Vérin rotatif actionné par fluide
EP1520996A3 (fr) * 2003-10-04 2005-07-27 Festo AG & Co Vérin rotatif actionné par fluide
CN106481362A (zh) * 2015-08-28 2017-03-08 郑恒 一种新型摆动式气动马达
CN106481362B (zh) * 2015-08-28 2019-02-19 郑恒 一种摆动式气动马达

Also Published As

Publication number Publication date
KR880000983B1 (ko) 1988-06-10
EP0136492B1 (fr) 1987-03-04
ATE25750T1 (de) 1987-03-15
KR850001974A (ko) 1985-04-10
US4611530A (en) 1986-09-16

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