EP0169511B1 - Stellglied für Drehbewegungen - Google Patents

Stellglied für Drehbewegungen Download PDF

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Publication number
EP0169511B1
EP0169511B1 EP85109061A EP85109061A EP0169511B1 EP 0169511 B1 EP0169511 B1 EP 0169511B1 EP 85109061 A EP85109061 A EP 85109061A EP 85109061 A EP85109061 A EP 85109061A EP 0169511 B1 EP0169511 B1 EP 0169511B1
Authority
EP
European Patent Office
Prior art keywords
shaft
actuator
central portion
chamber
seal means
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
Application number
EP85109061A
Other languages
English (en)
French (fr)
Other versions
EP0169511A1 (de
Inventor
Walter G. Lieberman
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.)
Tol O Matic Inc
Original Assignee
Tol O Matic Inc
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 Tol O Matic Inc filed Critical Tol O Matic Inc
Priority to AT85109061T priority Critical patent/ATE37429T1/de
Publication of EP0169511A1 publication Critical patent/EP0169511A1/de
Application granted granted Critical
Publication of EP0169511B1 publication Critical patent/EP0169511B1/de
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 present invention relates to a rotary actuator of the type set forth in the first part of claim 1.
  • a rotary actuator is known from IBM Technical Disclosure Bulletin, Vol. 25, No. 9, February 1983, pages 4665-4666.
  • a rotary actuator causes the rotation of an output drive shaft through a fixed arc at relatively high, instantaneous torque and relatively low speed.
  • the prior-art vane type rotary actuator includes a housing defining an inner chamber, a drive shaft extending through the inner chamber and at least one stationary (stator) vane and one rotating (rotor) vane defining a plurality of actuation chambers.
  • a single vane rotary actuator comprises a single stator vane connected with the interior of the cylinder wall and a single rotor vane connected with the rotating output shaft.
  • One objective in the design and manufacture of all vane type rotary actuators is to provide an effective seal for the actuation chambers so that air or other pneumatic fluid leakage between such chambers can be minimized.
  • One area which has caused particular problems in the manufacture of vane type rotary actuators is the area between the junction of the output shaft, the rotor and stator vane seals and the end cap. In presently existing rotary actuators, this seal is accomplished by an annular end cap seal member which is positioned in an annular groove in the end cap to seal against a portion of the output shaft as well as portions of the stator and rotor vane seals.
  • a shoulder portion of the output shaft to be sealed directly against an inner surface of the end wall.
  • the end cap is designed with an inner surface which extends inwardly past a portion of the output shaft so that a shoulder portion of such shaft will bear directly using it in sealing relationship.
  • the inward- most edge of this inner surface is cantilevered to give it limited flexibility. This permits the inner surface to make contact with the shoulder portion of the output shaft in a sealing relationship.
  • Figure 1 is a pictorial view of a rotary actuator in accordance with the present invention.
  • the actuator includes a housing comprising a cylinder portion 10, a pair of end caps 11 and 12 and an end portion 16 of the output shaft 14.
  • Figure 2 is a pictorial view of the rotary actuator of the present invention which has been broken apart to show the various internal components.
  • the cylinder portion 10 is sandwiched between the end caps 11 and 12 and includes a generally cylindrically shaped opening 24 extending therethrough in its longitudinal direction.
  • a pair of stator vanes comprising a pair of stator seal assemblies 25 and 26. These seal assemblies 25 and 26 engage the inner cylindrical surface of the opening 24 and extend radially inwardly from diametrically opposed positions toward the output shaft 14.
  • Each of the end caps 11 and 12 includes an annular recessed groove 36 disposed near the outer edge of its inner face.
  • the groove 36 is adapted to receive a conventional "o" ring 22 or other seal member to provide a sealing relationship between the inner surface 38 of each of the end caps 11 and 12 and a respective end face of the cylinder portion 10.
  • Each of the end caps 11 and 12 is provided with a plurality of openings 29 to accept corresponding threaded screws 30 or other connection members to retain the end caps 11 and 12 in sealing relationship against the end faces of the cylinder 10.
  • the cylinder portion 10 is provided with a groove 28 of generally circular cross sectional configuration along each of its corner edges.
  • Each of the grooves 28 is aligned with one of the openings 29 in the end caps 11 and 12 to threadedly receive the screws 30.
  • the grooves 28 can be provided with internal threads or they can be designed to receive self tapping screws 30 of the type contemplated by the preferred embodiment.
  • the cylinder portion 10 is preferably constructed of a light metal such as aluminum, although various other materials including certain plastics can also be used.
  • An output shaft 14 is centrally positioned within the cylindrical opening 24 and extends through the cylinder 10.
  • the output shaft includes a central portion 15 of an enlarged diameter and an end section 16 of lesser diameter extending outwardly along the longitudinal axis from each end of the central portion 15.
  • a pair of shoulder portions 18 join the central portion 15 with the end portions 16.
  • Each of the shoulders 18 includes an annular surface which, in the preferred embodiment, is disposed at generally right angles with respect to the longitudinal axis of the shaft 14.
  • a pair of rotor vanes comprising a pair of rotor seal assemblies 19 and 20 are mounted onto the central portion 15 of the output shaft 14 along its longitudinal axis and on diametrically opposite sides.
  • each of the rotor vane seal assemblies is comprised of a rigid mounting element 42 and an outer lip seal member 44.
  • the rigid mounting members 42 are secured to the central portion 15 of the output shaft in a longitudinal slot 41 by any appropriate means such as cementing or by press fitting the members 42 into their respective slots 41.
  • Figure 10 is a pictorial, split view of the lip seal member 44. As shown, the member 44 includes an inner, rectangularly shaped opening 50 which fits over and is secured to the mounting member 42.
  • each of the lip seal members 44 Disposed on the outer side surfaces of each of the lip seal members 44 is a raised portion or bumber 21 which is adapted for engagement with a side portion of the stator seal.
  • the bumber 21 functions to limit the rotational movement of the output shaft 14 and thus the entire rotor so as to preclude interference or undesirable contact between the lip portions of the rotor seals 19 and 20 and the stator seals 25 and 26.
  • the lip seal members 44 are connected to the mounting member 42 and also to the central portion 15 by appropriate adhesive or vulcanization means. When fully assembled, the lip portions of each of the seal members 44 form a sealing relationship with the inner surface of the cylindrical opening 24 and the inner surfaces of the end caps 11 and 12.
  • the lip seal member 44 can be constructed from a variety of different materials, the preferred embodiment contemplates the seal member 44 to be constructed of Buna N.
  • each of the stator vane seal assemblies 25 and 26 is comprised of an inner support member 45 integrally formed with the cylinder 10 and an outer lip seal member 46.
  • the support portions 45 are diametrically opposed to each other and extend in a longitudinal direction along an inner surface of the cylindrical opening 24.
  • the ends of the support member 45 do not extend all the way to the end face of the cylinder 10, but are spaced inwardly therefrom to accommodate the lip seal member 46.
  • the structure of the lip seal member 46 is shown best in Figures 4 and 11.
  • the lip seal member 46 includes a central groove 51 corresponding substantially in shape and size to the cross sectional configuration of the support member 45, thus permitting the member 46 to be placed over and retained by the support 45.
  • the seal 46 is retained in this position by the shaft 18. An appropriate adhesive or other means may also be used. When so positioned, the lip portions of the seal 46 form a sealing relationship with the inner surface of the opening 24, the central portion 15 of the shaft 14 and the inner end surfaces of the end caps 11 and 12.
  • each of the end caps 11 and 12 includes a plurality of openings 29 to facilitate connection of the end caps to the cylinder portion 10.
  • Each of the end caps 11 and 12 is also provided on a pair of openings or ports 39 and 40 on the inner surface 38 ( Figures 2 and 7) which are in communication with the interior of the pneumatic actuation chambers when the actuator is assembled.
  • each of these ports 39 and 40 is directly connected by passages 48 and 49, respectively, to a supply and exhaust port 34.
  • the inner surface 38 of each of the end caps 11 and 12 extends inwardly toward the shaft 14 to a centrally positioned circular opening 33.
  • This annular portion 32 extends radially inwardly from the main body portion of the end cap and is defined at its innermost edge by the opening 33.
  • the inner surface of this annular portion 32 forms a sealing surface for engagement by the shoulder 18 of the shaft 14.
  • Each of the end caps also includes a counterbore 31 into which a bearing member 35 is seated.
  • the counterbore 31 extends inwardly to the annular portion 32 and has a diameter of D 3 ( Figure 13).
  • the diameter D 3 is preferably greater than the diameter of the central portion 15 of the shaft to allow the portion 32 to flex slightly when engaged by the shoulder portion 18 of the shaft.
  • the bearing 35 is press fit into the bore 31 and includes a central opening to rotatably support the end portion 16 of the output or drive shaft 14.
  • the dimension D 2 shown in Figure 13 defines the radial dimension of the annular portion 32, while the dimension D, defines the longitudinal dimension of the portion 32.
  • the innermost edge of the annular portion 32 (defined by the opening 33) has a diameter slightly larger than the diameter of the end portion 16 of the shaft 14, but a diameter less than the diameter of the central portion 15. This allows the end portions 16 to rotate freely within the openings 33 and the shoulder portion 18 of the output shaft to engage the inner surface of the portion 32 in a sealing relationship when the unit is assembled. This relationship is illustrated best in Figures 5 and 6.
  • the length of the central portion 15 of the shaft 14 is slightly longer than the length of the cylinder portion 10.
  • the inwardly extending annular portions 32 will be squeezed against the shoulder portion 18, thus forming a sealing relationship between the shoulder 18 and the portion 32.
  • the cylinder 10 is approximately 44.73 mm, whereas the central portion 15 is approximately 0.125 mm longer. Because of this difference in length, the annular portions 32 are slightly flexed as the end caps 11 and 12 are secured to the cylinder portion 30. Thus, the annular portions 32 must be capable of accommodating this flexing.
  • the annular portion 32 can have various dimensional configurations, the preferred embodiment contemplates a structure in which the longitudinal dimension D, of the portion 32 is less than the radial dimension D 2 .
  • the portion 32 should also be constructed of a material which permits the above flexing.
  • various metals and other materials will function satisfactorily, the preferred embodiment contemplates the end caps to be constructed of a hard plastic such as nylon.
  • the shaft 14 with its rotor seal assemblies 19 and 20 is inserted into the cylindrical opening 24 in the cylinder portion 10.
  • the "O" rings 22, 22 are then inserted in the corresponding grooves 36 on the inside surface of the end plates 11 and 12 and the end plates are secured to the end faces of the cylinder portion 10 by the screws 30.
  • the inner surface of the annular portion 32 ( Figures 9 and 13) is biased against the shoulder portions 18 of the shaft 14 in a sealing relationship.
  • the end portions 16 of the shaft are rotatably supported by the bearing members 35.
  • actuation chambers are formed within the cylinder portion 10 between the various stator and rotor vanes. These chambers 54, 55, 56 and 57 are illustrated best in Figure 4.
  • pressurized pneumatic fluid such as air is alternately supplied to and exhausted from these chambers through the ports 39 and 40 and corresponding supply and exhaust openings 34.
  • pressurized pneumatic fluid is introduced into the chambers 55 and 57 through the ports 39 and 40 and the opening 34 in the end cap 12, the shaft 14 will be caused to rotate in a counterclockwise direction as viewed in Figure 4.
  • both the side edges of the rotor and stator seal members, reference numerals 44 and 46, respectively, and the shoulder portion 18 of the shaft 14 are in sealing engagement with the inside surface 38 of the end caps 11 and 12.
  • the inner edge of the stator seal members 46 ( Figure 5) and the innermost portion of the side edges of the rotor seal members 44 are in sealing relationship with the central portion 15 of the shaft.
  • Figure 14 illustrates one such alternate embodiment.
  • the end cap assembly includes an end cap support member 60 and an adjacent end cap seal plate 61.
  • a groove is formed in the end surface of the cylinder 10 and an "0" ring 64 is positioned therein to seal against the inside surface of the plate 61.
  • the plate 61 extends inwardly past the center bore 31. This forms an inwardly extending annular portion 65 for sealing relationship with the central portion 15 of the output shaft.
  • the shaft is rotatably supported at each of its ends 16 by an appropriate bearing 35.
  • An alternate structure is also contemplated which has no separate end caps or cylinder portion, but which includes actuation chambers having a cross sectional configuration of a semicircle, a semi-elipse or some other configuration such as that illustrated in Figure 15.
  • an "o" ring 71 is disposed between a pair of housing sections 66 and 68.
  • the output shaft includes a central portion 15 and a pair of end portions 16.
  • a pair of rotor seals 69 and supports 70 are connected with the central portion of the shaft 15 and are configured to conform with the inner surface of the housing sections 66 and 68.
  • the inner surface defined by the sections 66 and 68 is symmetrical and includes an inner annular portion 32 for sealing engagement with the central portion 15 of the output shaft.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Damping Devices (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (10)

1. Stellglied für Drehbewegungen, umfassend
ein Gehäuse (10-12), in dem eine von einer Innenfläche definierte Kammer (24) ausgebildet ist,
ein Paar von Wellenöffnungen (33) an entgegengesetzten Stirnseiten (11, 12) der Kammer (24),
eine Welle (14) mit einem innerhalb der Kammer (24) angeordneten Mittelteil (15), einem Paar von Endabschnitten (16), die von dem Mittelteil (15) nach außen ragen und die Wellenöffnungen (33) durchsetzen, und einem jeden Endabschnitt (16) mit dem Mittelteil (15) verbindenden Schulterabschnitt (18), wobei mindestens die Enden des Mittelteils (15) einen größeren Durchmesser aufweisen als die Wellenöffnungen (33) und die Endabschnitte (16) und wobei jeder Schulterabschnitt (18) einer zwischen dem Mittelteil (15) und dem jeweiligen Endabschnitt (16) verlaufende generell ringförmige Fläche aufweist,
eine mit der Innenfläche verbundene erste Schaufel (25, 26) mit einer ersten Dichtungseinrichtung (46) zum dichtenden Eingriff mit dem Mittelteil (15) der Welle (14),
eine mit dem Mittelteil (15) der Welle (14) verbundene zweite Schaufel (19, 20) mit einer zweiten Dichtungseinrichtung (44) zum dichtenden Eingriff mit der Innenfläche, wobei die zweite Dichtungseinrichtung (44) über den Umfang der zweiten Schaufel (19, 20) verläuft und an der Außenkante der Ringfläche (18) endet,
mindestens ein Paar von zwischen der ersten und der zweiten Schaufel (25,26; 19, 20) definierten Betätigungskammern (54-57), und
eine Einrichtung (34, 39, 40, 48, 49) zum selektiven Ein- und Ausleiten von Druckfluid in die bzw. aus den Betätigungskammern (54-57), dadurch gekennzeichnet,
daß jede Ringfläche (18) an einem jeweiligen Stirnflächenteil (38) der Innenfläche nahe und radial außerhalb der betreffenden Wellenöffnung (33) dichtend anliegt, und
daß das Gehäuse (10-12) nahe und radial außerhalb einer der Wellenöffnungen (33) einen inneren Stirndichtungsabschnitt (32), der infolge des direkten dichtenden Eingriffs zwischen der Ringfläche (18) und dem betreffenden Stirnflächenabschnitt (38) begrenzt auslenkbar ist, sowie einen mit der Wellenöffnung (33) koaxialen Bohrungsabschnitt (31) aufweist, der an den inneren Stirndichtungsabschnitt (32) angrenzt und einen Durchmesser (D3) hat, der größer ist als der Durchmesser an der Stirnseite des Wellen-Mittelteils (15).
2. Stellglied nach Anspruch 1, wobei die Kammer (24) eine generell zylindrische Kammer ist, die an ihren Stirnseiten von einem Paar von generell parallelen, in Abstand voneinander befindlichen Stirnflächen (38) gebildet ist, wobei jede Stirnfläche auf jeweils eine der Wellenöffnungen (33) zu einwärts verläuft.
3. Stellglied nach Anspruch 2, wobei das Gehäuse (10-12) ein Paar von in Abstand voneinander befindlichen Stirnkappen (11, 12) umfaßt, die die Stirnflächen (38) und Wellenöffnungen (33) bilden.
4. Stellglied nach Anspruch 3, wobei jede der Stirnkappen (11, 12) eine zu ihrer Stirnfläche (38) generell parallele Außenfläche und eine von dieser in Richtung der Stirnfläche (38) nach innen verlaufende Gegenbohrung (31) aufweist und somit den Bohrungsabschnitt sowie den inneren Stirndichtungsabschnitt (32) bildet.
5. Stellglied nach Anspruch 3 oder 4, wobei das Gehäuse (10-12) einen zwischen den Stirnkappen (11, 12) angeordneten Rohrabschnitt (10) umfaßt, dessen Länge geringer ist als die Länge des Wellen-Mittelteils (15), so daß im zusammengebauten Zustand des Stellgliedes zwischen den Schulterabschnitten (18) und den Stirnflächen (38) eine Dichtungskraft erzeugt wird.
6. Stellglied nach einem der Ansprüche 3 bis 5, wobei die Stirnkappen (11, 12) und/oder der Rohrabschnitt (10) aus einem Kunststoff, vorzugsweise Nylon, bestehen.
7. Stellglied nach einem der Ansprüche 1 bis 6, wobei die Kammer (24) symmetrisch ist und eine Symmetrieachse aufweist, und wobei die Wellenöffnungen (33) zu der Symmetrieachse konzentrisch sind.
8. Stellglied nach einem der Ansprüche 4 bis 7, umfassend ein in der Gegenbohrung (31) jeder der Stirnkappen (11, 12) angeordnetes Lager (35) zur drehbaren Lagerung der Stirnabschnitte (16) der Welle (14).
9. Stellglied nach einem der Ansprüche 1 bis 8, wobei die erste und die zweite Dichtungseinrichtung (46,44) Lippendichtungs-Einrichtungen sind.
10. Stellglied nach Anspruch 9, wobei mindestens eine (44) der beiden Dichtungseinrichtungen (46, 44) einen erhabenen Abschnitt (21) aufweist, um zu verhindern, daß die Kanten der ersten und der zweiten Lippendichtungs-Einrichtungen einander stören.
EP85109061A 1984-07-20 1985-07-19 Stellglied für Drehbewegungen Expired EP0169511B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109061T ATE37429T1 (de) 1984-07-20 1985-07-19 Stellglied fuer drehbewegungen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US63271984A 1984-07-20 1984-07-20
US632719 1984-07-20

Publications (2)

Publication Number Publication Date
EP0169511A1 EP0169511A1 (de) 1986-01-29
EP0169511B1 true EP0169511B1 (de) 1988-09-21

Family

ID=24536650

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109061A Expired EP0169511B1 (de) 1984-07-20 1985-07-19 Stellglied für Drehbewegungen

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EP (1) EP0169511B1 (de)
JP (1) JPS61105303A (de)
AT (1) ATE37429T1 (de)
CA (1) CA1259536A (de)
DE (1) DE3565157D1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107246423A (zh) * 2017-06-23 2017-10-13 武汉科技大学 一种具有全封闭笼式密封系统的叶片式摆动液压油缸

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2637803B1 (fr) * 1988-10-19 1993-07-09 Ire Celltarg Sa Ligands specifiques de recepteurs d'hormones steroides estrogenes et progestagenes, application et produits intermediaires de synthese
JPH0561563U (ja) * 1991-08-15 1993-08-13 株式会社コガネイ シリンダチューブおよびそれを用いたシリンダ装置
FR2727477A1 (fr) * 1994-11-28 1996-05-31 Aerospatiale Verin rotatif conique et son application a la commande d'une gouverne d'aeronef
JP2008151214A (ja) * 2006-12-15 2008-07-03 Honda Motor Co Ltd ベーン式油圧機器、電動機および内燃機関のバルブタイミング制御装置
CN100458250C (zh) * 2007-06-21 2009-02-04 济南高仕机械制造有限公司 扇型气动执行器
KR100956849B1 (ko) 2008-04-23 2010-05-12 (주)케이엔알시스템 로터리 액추에이터 및 로터리 액추에이터형 관절구조
ITBS20100050A1 (it) * 2010-03-12 2011-09-13 Gimatic Spa Attuatore oscillante a palette multiple
CN108561366A (zh) * 2018-07-11 2018-09-21 无锡气动技术研究所有限公司 微型回转气缸

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB893361A (en) * 1958-06-12 1962-04-11 Fairey Co Ltd Improvements relating to hydraulic or pneumatic jacks
FR2528920B1 (fr) * 1982-06-18 1988-06-17 Japanlicensor Kk Actionneur rotatif du type a ailette
DE3222982C2 (de) * 1982-06-19 1986-04-30 Südhydraulik Kork-Steinbach GmbH & Co KG, 2400 Lübeck Drehkolbenzylinder

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107246423A (zh) * 2017-06-23 2017-10-13 武汉科技大学 一种具有全封闭笼式密封系统的叶片式摆动液压油缸
CN107246423B (zh) * 2017-06-23 2019-06-07 武汉科技大学 一种具有全封闭笼式密封系统的叶片式摆动液压油缸

Also Published As

Publication number Publication date
DE3565157D1 (en) 1988-10-27
ATE37429T1 (de) 1988-10-15
EP0169511A1 (de) 1986-01-29
CA1259536A (en) 1989-09-19
JPS61105303A (ja) 1986-05-23

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