EP0065588A1 - Hydraulischer Schwenkflügelantrieb - Google Patents

Hydraulischer Schwenkflügelantrieb Download PDF

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Publication number
EP0065588A1
EP0065588A1 EP81104040A EP81104040A EP0065588A1 EP 0065588 A1 EP0065588 A1 EP 0065588A1 EP 81104040 A EP81104040 A EP 81104040A EP 81104040 A EP81104040 A EP 81104040A EP 0065588 A1 EP0065588 A1 EP 0065588A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
diameter
flanges
vane
rotor
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
EP81104040A
Other languages
English (en)
French (fr)
Other versions
EP0065588B1 (de
Inventor
Shimoda Shinobu
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.)
Torquer Co Ltd
Original Assignee
Torquer Co Ltd
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 Torquer Co Ltd filed Critical Torquer Co Ltd
Priority to DE8181104040T priority Critical patent/DE3176067D1/de
Priority to EP81104040A priority patent/EP0065588B1/de
Publication of EP0065588A1 publication Critical patent/EP0065588A1/de
Application granted granted Critical
Publication of EP0065588B1 publication Critical patent/EP0065588B1/de
Expired legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08Characterised by the construction of the motor unit
    • F15B15/12Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type

Definitions

  • the present invention relates to a rotary actuator serving reciprocating rotation and a making method thereof.
  • the rotary actuator is employed for providing the reciprocating rotation (oscillation) within limited angle.
  • the conventional rotary actuator substantially comprises a casing securing a stopper to an inner wall thereof, a stator and vanes, and the reciprocating rotation (oscillation) has been accomplished by alternately supplying oil under pressure into an inlet and an outlet ports.
  • sealing material such as rubber, synthetic resin or the like is attached to the vanes.
  • the sealing material is extreme in abrasion, or creats friction in relation with an inner side of a cylinder, resulting in hindering efficiency of generating rotation torque. Being in these circumstances, requisions have arisen to appearence of such rotary actuator which prevents the oil leakage without using the sealing material.
  • Fig. 1 is a partial cross sectional front view of an embodiment according to the invention, in which vanes are two installed.
  • a cylinder 1 is mounted with a rotor thereon, and is closed at its both sides by securing end covers 2 and 3 with bolts 4, 5.
  • the cylinder 1 is defined with holes on an upper and a lower faces into which core metals will be inserted.
  • the core metal 7 is secured to the cylinder 1 by tightening bolts, and this metal serves to restrain action of stoppers 8, 9 as later mentioned.
  • the cylinder 1 is further formed with oil ports 10, 11 around the core metal 7 for charging and discharging the oil under pressure.
  • the rotor to be disposed within the cylinder 1 comprises a rotor shaft 12, flanges 13, 14 parallel thereto, small diameter portions 15, 16 as outer sides of the flanges 13, 14, and the vanes 17, 18 fixed between the flanges 13, 14.
  • the rotor shaft 12 is formed with a narrow path 21 communicating oil chambers 19 and 20 as seen in Fig. 2, and a narrow path 22 communicating oil chambers which will be gradually defined between the stopper 8 and the vane 17 and between the stopper 9 and the vane 18 by rotation of the rotor.
  • the paths 21, 22 may be omitted if the vane and the stopper make a one pair, and those may be also omitted if the cylinder 1 is formed on its lower face with oil ports as the oil ports 10, 11.
  • the rotor is made in a following manner. That is a circular material is ready for which is in diameter the same as or a bit larger than the flange, and it is machined on respective parts. At the outset, it is processed up to size of the diameter of the small diameter portions 15, 16, leaving parts which will be the flanges 13, 14 at left and right sides, subsequently the processing is continued up to size of the diameter of the rotor shaft 12, leaving parts which will be the small diameter portions 15, 16.
  • portions of the flanges 13, 14, the small diameter portions 15, 16 and the rotor shaft 12 are formed integrally and sequentially.
  • the viscosity of the oil is utilized for preventing the oil leakage without using the sealing material to the vanes 17, 18.
  • vanes 17, 18 such cylindrical body like a doughnut is ready for which has an inner diameter equal to the diameter of the rotor shaft 12 and has an outer diameter being equal to or a bit larger than the outer diameter of the flanges 13, 14, and it is cut out at one part into a sector of small width and is kept by a bolt between the flanges 13, 14.
  • the outer diameters of the vanes 17, 18 are prepared as slightly larger than a determined outer diameter of the flange, it is possible to accord to the outer diameter of the flanges 13, 14 by grinding the vanes 17, 18 on protruding parts thereof from the flanges 13, 14 after having fixed the vanes 17, 18 between the flanges 13, 14.
  • the vanes 17, 18 are secured to the flanges 13, 14 by the bolts. If the vanes 17, 18 are formed with cutouts 23, the oil smoothly penetrates between the contacting vane and stopper.
  • the rotor 6 is urged into the cylinder 1 under condition that the stoppers 8, 9 are kept between the flanges 13, 14 on the upper and lower parts thereof.
  • the stoppers 8, 9 are positioned within spaces defined between the rotor shaft 12, the flanges 13, 14 and the inner wall of the cylinder 1, but are not fixed to either of them. Thereby, thrust loading acting on the rotor shaft 12 may be absorbed and at the same time the sizing error or setting-up error at each of the parts may be corrected.
  • radial bearings 24, 25 are forcibly set at the both sides, outer wheel of which bearings 24, 25 are a bit larger in the diameter than the inner diameter of the cylinder.
  • the inner wheels of the radial bearings 24, 25 are mounted on the small diameter portions 15, 16 of the rotor.
  • the rotor is securely supported in that the radial bearings 24, 25 are used, the outer wheel of which has the diameter larger than the inner diameter of the cylinder, so that the clearance is maintained between the circumferential faces of the flanges 13, 14 and the inner wall of the cylinder.
  • the core metals 7 are inserted into the holes 6 and are fixed at end portions seated within bores 26, 27 of the stoppers 8, 9.
  • F igs.5 and 6 illustrate the other embodiment, in which cushion mechanism is disposed.
  • oil ports 28, 29 are prepared with a main path 30 and a subpath 31, and the main path 30 is directed to an oil chamber.
  • the subpath 31 is communicated with the oil chamber via a path 34 which is normally closed by a ball valve 33 acted by a spring 32, and a bypath 35.
  • the bypath 35 is controlled in its width by a control screw 36 in the cylinder 1.
  • the other mechanisms are the same as mentioned above.
  • the action of the inventive rotary actuator will be referred to. If the pressure oil is supplied from the oil port 10, the oil goes between the upper stopper 8 and the vane 17, i.e., into the cutout 23, the vane 17 contacting the stopper 8 slowly separates therefrom and rotates in the counterclockwise direction in Fig. 2 until it contacts the lower stopper 9. Then, part of the oil is led via the narrow path 21 into between the vane 18 and the stopper 9 and separates the both.
  • the oil charged in the oil chamber 19 passes through the narrow path 21 by the vane 17 into the oil chamber 20, and is discharged from the oil port 11 by the vane 18 together with the oil charged in the chamber 20, and the rotation of the rotor is stopped in that the vane 17 contacts the stopper 9 and the vane 18 contacts the stopper 8.
  • the same operation as mentioned is then performed to the reverse, that is, the vanes 17, 18 rotates in the opposite direction and returns to the state shown in Fig. 2.
  • the said normal and reverse rotations are repeated and the rotary shaft is effected with reciprocating rotation.
  • the rotor While the rotor serves the normal and reverse rotations, the rotor is always given the thrust load which is a component force other than the radial load. As far as the component force is light, it may be sufficiently received by only supporting the rotor on the radial bearing. However, if a large thrust load were acted on while the thrust load is acted on the rotary shaft from the outside, the inner wheels of the radial bearings 24, 25 would slightly biased toward the thrust in response to the extent of such thrust load and the rotor also moves accordingly, though the outer wheels of the radial bearings are so close to the inner face of the cylinder 1 and do not move.
  • the stoppers 8, 9 are not fixed to the cylinder 1 at its inner wall, whereby the stoppers 8, 9 may be moved while the rotor moves with fitting to neighbourhood to avoid occurrence of said disadvantages. Being supported under non-fixing condition, the stoppers 8, 9 move freely and fit to the adjacient members. Therefore, it is possible to adjust the sizing errors or the setting-up errors when the members are set up.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Rotary Pumps (AREA)
EP81104040A 1981-05-26 1981-05-26 Hydraulischer Schwenkflügelantrieb Expired EP0065588B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8181104040T DE3176067D1 (en) 1981-05-26 1981-05-26 Hydraulic actuator of the oscillating-vane type
EP81104040A EP0065588B1 (de) 1981-05-26 1981-05-26 Hydraulischer Schwenkflügelantrieb

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81104040A EP0065588B1 (de) 1981-05-26 1981-05-26 Hydraulischer Schwenkflügelantrieb

Publications (2)

Publication Number Publication Date
EP0065588A1 true EP0065588A1 (de) 1982-12-01
EP0065588B1 EP0065588B1 (de) 1987-04-01

Family

ID=8187738

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81104040A Expired EP0065588B1 (de) 1981-05-26 1981-05-26 Hydraulischer Schwenkflügelantrieb

Country Status (2)

Country Link
EP (1) EP0065588B1 (de)
DE (1) DE3176067D1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0283380A2 (de) * 1987-03-18 1988-09-21 Societe Europeenne De Propulsion Druckmittelbetriebener Schwenkflügelmotor ohne innere Dichtungen
CN109483589A (zh) * 2018-12-28 2019-03-19 武汉科技大学 一种易于加工的液压转角自伺服柔顺驱动器
CN114623122A (zh) * 2022-04-07 2022-06-14 北京理工大学 一种高压摆动液压缸

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2798462A (en) * 1956-02-15 1957-07-09 Ex Cell O Corp Hydraulic motor with wide vane and duplicate ports for cushioning vane and pressurized seals
GB885185A (en) * 1959-10-12 1961-12-20 Automotive Prod Co Ltd Improvements in or relating to rotary fluid pressure actuators
DE1750352A1 (de) * 1968-04-24 1971-01-21 Hermann Steinbach Ein- oder Mehrkammer-Drehkolbenzylinder
DE2161831A1 (de) * 1970-12-16 1972-06-22 Ferag Ag Stellantrieb
DE2321043A1 (de) * 1973-04-26 1974-11-14 Suedhydraulik Marktoberdorf Al Drehkolbenzylinder

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE516082A (de) * 1951-12-19

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2798462A (en) * 1956-02-15 1957-07-09 Ex Cell O Corp Hydraulic motor with wide vane and duplicate ports for cushioning vane and pressurized seals
GB885185A (en) * 1959-10-12 1961-12-20 Automotive Prod Co Ltd Improvements in or relating to rotary fluid pressure actuators
DE1750352A1 (de) * 1968-04-24 1971-01-21 Hermann Steinbach Ein- oder Mehrkammer-Drehkolbenzylinder
DE2161831A1 (de) * 1970-12-16 1972-06-22 Ferag Ag Stellantrieb
DE2321043A1 (de) * 1973-04-26 1974-11-14 Suedhydraulik Marktoberdorf Al Drehkolbenzylinder

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0283380A2 (de) * 1987-03-18 1988-09-21 Societe Europeenne De Propulsion Druckmittelbetriebener Schwenkflügelmotor ohne innere Dichtungen
FR2612572A1 (fr) * 1987-03-18 1988-09-23 Europ Propulsion Dispositif fluidique a palette rotative sans joint d'etancheite interne
EP0283380A3 (en) * 1987-03-18 1989-09-27 Societe Europeenne De Propulsion Fluid vane actuator without internal sealings
CN109483589A (zh) * 2018-12-28 2019-03-19 武汉科技大学 一种易于加工的液压转角自伺服柔顺驱动器
CN109483589B (zh) * 2018-12-28 2024-01-05 武汉科技大学 一种易于加工的液压转角自伺服柔顺驱动器
CN114623122A (zh) * 2022-04-07 2022-06-14 北京理工大学 一种高压摆动液压缸

Also Published As

Publication number Publication date
DE3176067D1 (en) 1987-05-07
EP0065588B1 (de) 1987-04-01

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