US3835501A - Actuators - Google Patents

Actuators Download PDF

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Publication number
US3835501A
US3835501A US00267176A US26717672A US3835501A US 3835501 A US3835501 A US 3835501A US 00267176 A US00267176 A US 00267176A US 26717672 A US26717672 A US 26717672A US 3835501 A US3835501 A US 3835501A
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Prior art keywords
fluid
space
chamber
actuator
spring
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Expired - Lifetime
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US00267176A
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English (en)
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A Nash
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Individual
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Individual
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    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position
    • 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

  • a pressure-fluid operated actuator used e.g. as a door opening and closing mechanism has restriction means limiting the flow of pressure fluid and so slowing down the rate of movement towards the end of a closing movement.
  • the restriction means do not affect the initial part of the movement and allow free entry of fluid into the actuator for the reverse movement.
  • the arrangement can include means which limit the degree of restriction offered.
  • This invention relates to pressure-fluid operated actuators or motors (hereinafter referred to simply as actuators) which are arranged for reciprocating movement, whether linear or angular.
  • a pressure-fluid operated actuator comprising an internal piston member dividing a chamber of the actuator into two mutually sealed spaces each provided with fluid porting, the piston member being movable between opposite end positions by the admission of pressure fluid through the porting in one space and the exhausting of fluid in the other space through the porting thereof, means arranged to be operative at said porting in at least one direction of travel of the piston member to restrict the outflow of fluid from the space and so to retard the movement of the piston member.
  • Such restriction of the outflowing fluid may be achieved by the provision of blocking means at said porting that can be displaced by the pressure of incoming fluid to allow that fluid to enter freely but that are operative in restricting the outflow of fluid already in the actuator chamber.
  • means are preferably provided to increase the restriction of the outflow from the contracting space after a predetermined part of the movement of the piston member.
  • additional means may comprise a valve member held on a resilient mounting to be normally spaced from the associated porting and displaceable towards said porting by the piston member as it approaches its end position. If the valve member closes the porting, it can be arranged that there is additionally a bleed port, possibly with adjustable restriction means for the further outflow of fluid so that fluid still in the contracting space can yet escape therefrom.
  • the valve member may, for example, be held on a cantilever spring and a resilient element attached to said spring can be arranged to be contacted by the piston member at a stage of its movement towards the valve member so as to deflect the cantilever spring and close said I porting.
  • FIG. 5 is a plan section of an alternative rotary actuator according to the invention, which can also be employed in the mechanism of FIG. 4.
  • the construction of the actuator is similar in many respects to that described in the Complete Specification of British Pat. No. 1,023,232 to which reference can be made for details of the construction of piston 2 that is pivotable on shaft 4 in a casing 6, the interior of which is divided by the piston into two mutually sealed spaces 8a, 8b.
  • the arrangement of the casing is symmetrical as seen in FIG. 1 about a line through the piston pivot axis and opposite side walls 10 have similar porting for the flow of working fluid, such as air, to and from the spaces 8a, 8b.
  • this porting comprises an external conduit connection 12 to a cross-bore 14 which is able to communicate with the chamber interior both through a main port 16 and an auxiliary port 18.
  • a throttling plate 20 Overlying the main port 16 there is a throttling plate 20 and a closure valve 22.
  • the throttling plate is formed by a berylliumcopper spring strip in which a small aperture 24 is provided within the area of the end opening of the port 16.
  • the plate is secured to the chamber side wall in cantilever manner by screws 26 at some distance from the port 16.
  • the pressure holds the plate against the chamber side wall and the aperture 24 determines the effective cross-sectional area for the flow.
  • the plate 22 is sufficiently resilient to be flexed by the pressure away from the chamber side wall so that a considerably larger cross-sectional area is available for the flow.
  • the valve 22 comprises a valve body 28 loosely held on one leg 30a of a hairpin spring 30 that is riveted to a further leaf spring 32 that is in its turn mounted to the casing by the screws 26.
  • the other leg 30b of the spring 30 projects away from the adjacent side wall of the casing and can be contacted by the piston 2 considerably before the end of the piston stroke.
  • the piston then displaces the spring 20 to swing the valve body against the aperture 24 to prevent further outflow therethrough. Because of the relatively loose mounting of the valve body 28 to the spring 30, the body will automatically align itself against the face of the plate 20 to seal the aperture 24.
  • a needle valve 34 has a screwed engagement with the casing to be located over the auxiliary port 18 and can be secured in a desired position of adjustment by a locknut 36 to determine the effective flow area of the port 18.
  • the presence of the auxiliary port allows a limited outflow from a diminishing volume chamber space after the main port has been closed by the valve body 28.
  • the motion of the piston may stop but the force exerted against the obstruction will then increase as outflow continues through the auxiliary port 18 and/or the main port 16 so that there is no increased risk of jamming the actuator in a partly displaced position despite the reduction of the operating force under normal conditions.
  • the needle valve may be modified in the manner indicated in FIG. 3, where screw adjustment member 42 is so connected to valve body 44 by a compression spring 46 that the valve opens at' a given pressure differential.
  • This has the effect also of reducing the possibility of piston bounce at the end of its movement.
  • a feature that is similarly able to improve the characteristic of the actuator in this respect is the provision of filler pieces 48 for the purpose of reducing the dead air volume in the smaller space at the end of a stroke and thus reduce the possibility of bounce due to compressibility of the fluid remaining in that space.
  • the actuator described above can be employed in a variety of applications and can be of particular value in operating devices that have a relatively high inertia.
  • it can be used to operate the access doors of a passenger transport vehicle, as is diagrammatically illustrated in FIG. 4.
  • two double-leaf folding doors are movable from opposite sides of the door opening by respective actuators 50 of the form already described, each actuator having its piston shaft connected to the outer leaf 52 of the associated door.
  • the inner leaves 54 of the doors have rollers running in a guide track 56 across the width of the doorway.
  • the two actuators are operated simultaneously by a single remote air valve (not shown) of conventional form which supplies air, e.g. at 100 p.s.i.g. to one or other side of the actuator pistons.
  • the restriction arrangement will normally keep the pressure in the exhausting space to perhaps some 70-80 p.s.i.g. and is able to prevent the doors shutting too sharply, and may also be arranged to cause a momentary arrest of the motion at some predetermined angle, e.g. some 10 to 25 from an approaching end position.
  • some predetermined angle e.g. some 10 to 25 from an approaching end position.
  • the further example of actuator shown in FIG. is also a symmetrical arrangement and at each of the opposite side walls a, similarly to the first example, there is an external conduit connection 12 able to communicate with the chamber interior through a main port 16a and an auxiliary port 18a. Overlying the main port (but offset from the auxiliary port) there is a throttling plate 20a with aperture 24.
  • the plate is entirely analogous to the plate 20 of the first example and is of cranked form to reduce the possibility of foreign matter being trapped under it.
  • an externally adjustable needle valve 34 is associated with the auxiliary port 18a.
  • a closure valve overlying the main port 16a comprises a spring plate 60 of rather different form from the equivalent plate 30 of the first example, but having a similar valve body 28 loosely mounted on it.
  • the plate 60 is secured directly by the screws 26 holding the throttling plate 20a and extends in cantilever manner over the main port opening. It is made of a length of strip but is effectively of bifurcated form: that is to say it has the central part of its main portion 62 bent out to form a cantilevered secondary limb 64 to the free end of which is riveted the valve body 28.
  • the free end 66 of the plate 60 has a curved profile to allow it to ride smoothly over the profiled face of an adjacent filler piece 68 secured to the piston 2 to extend over substantially the full axial length of the piston.
  • the profile of the filler piece includes a first portion 70 that is at an increasing radial distance from the pivot axis of the piston as it approaches a second portion 72 which is at a constant radius to the piston pivot axis.
  • first portion 70 that is at an increasing radial distance from the pivot axis of the piston as it approaches a second portion 72 which is at a constant radius to the piston pivot axis.
  • the piston swings to an end position, it approaches the associated spring plate 60 and the free end 66 of the plate contacts the first portion 70 of the tiller piece profile.
  • This acts as a continuously rising cam while the piston continues its motion and the spring plate is thus flexed to bring the valve body 28 against the throttling plate aperture.
  • the valve body is maintained against the aperture during any residual movement of the piston after the spring plate runs off the cam portion 70, the second portion 72 of the profile then bearing on the spring plate.
  • the deflection of the spring plate is not increased further by the second portion 72 so that the stress in the plate is not increased at this stage
  • this actuator is the same as that of the first-described example.
  • connections 12 and needle valves 34 are shown difierently arrange, it will be appreciated that the two different forms of actuator can be arranged to have corresponding external configurations.
  • a rotary actuator for use with a source of compressible fluid under pressure comprising, in combination, a casing, a chamber within said casing, a pivotally mounted piston member within said chamber dividing the chamber of the actuator in two mutually sealed spaces, respective porting means provided leading from the exterior of the actuator to each space for the inflow of pressure fluid from said source and for the outflow of fluid from said spaces, the piston member being pivotable between opposite end positions in the chamber by the admission of pressure fluid through the porting means of one space and the exhausting of fluid from the other space through the porting means thereof, restriction means within the chamber arranged in conjunction with at least one said porting means to be operative in at least one direction of travel of the piston member by the displacement of the piston member to restrict the outflow of fluid from the contracting space in order to retard the movement of the piston member after a predetermined part of the contraction of said space, said restriction means comprising a valve member, a spring member supporting said valve member so that it is normally spaced from the associated porting
  • restriction means further comprises a blocking device at said porting means that is displaceable by the pressure of incoming fluid to allow that fluid to enter the associated chamber space freely but that is operative in restricting the outflow of fluid from said space.
  • An actuator according to claim 1 comprising a hairpin spring one arm of which forms said resilient element on the other arm of which has the valve member mounted upon it, a cantilever spring supporting said hairpin spring and being attached to said hairpin spring at a point spaced from the valve member.
  • said restriction means comprises a blocking device at said porting means that is displaceable by the pressure of incoming fluid to allow that fluid to enter the associated chamber space freely but that is operative in restricting the outflow of fluid from said space and wherein the blocking device and the spring member are secured to a wall of the actuator casing by common attaching means.
  • An actuator according to claim 6 comprising at least one member on which said surfaces are formed, said member acting as a filler to reduce the free fluid volume in the contracted space of the chamber said member extending substantially the full axial length of the piston member in its region.
  • An actuator according to claim 1 comprising a bleed port associated with said porting means of the chamber spaces and arranged to provide an alternative path for the outflow of fluid.

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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-Driven Valves (AREA)
US00267176A 1971-07-02 1972-06-28 Actuators Expired - Lifetime US3835501A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB3118771A GB1392296A (en) 1971-07-02 1971-07-02 Rotary actuators

Publications (1)

Publication Number Publication Date
US3835501A true US3835501A (en) 1974-09-17

Family

ID=10319307

Family Applications (1)

Application Number Title Priority Date Filing Date
US00267176A Expired - Lifetime US3835501A (en) 1971-07-02 1972-06-28 Actuators

Country Status (5)

Country Link
US (1) US3835501A (enExample)
JP (1) JPS5644288B1 (enExample)
DE (1) DE2232110A1 (enExample)
FR (1) FR2144770B1 (enExample)
GB (1) GB1392296A (enExample)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3036592C2 (de) * 1980-09-27 1984-05-24 Südhydraulik Kork-Steinbach GmbH & Co KG, 2400 Lübeck Fluid-betriebener Drehkolbenantrieb, insbesondere hydraulischer Drehkolben
DE3804081A1 (de) * 1988-02-10 1989-08-24 Knorr Bremse Ag Druckmittelbetaetigter tuerantrieb
KR900700715A (ko) * 1988-03-11 1990-08-16 노엘 캐롤 문 작동기
WO1990005230A1 (en) * 1988-11-09 1990-05-17 Noel Carroll Actuator for gate

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1016514A (en) * 1912-02-06 Frederik Nielsen Shock-absorber.
US1690113A (en) * 1927-03-17 1928-11-06 Gordon B Hooton Spring snubber for automobiles
US1785814A (en) * 1929-02-05 1930-12-23 Enos H Kreider Vehicle shock absorber
US1812244A (en) * 1929-08-06 1931-06-30 Enos H Kreider Vehicle shock absorber
US1899909A (en) * 1932-07-22 1933-02-28 Bernard V Curnen Shock absorbing mechanism
US3010433A (en) * 1958-03-18 1961-11-28 Nat Pneumatic Co Inc Pneumatic motion-checking device and door operating system including same
US3064303A (en) * 1959-05-18 1962-11-20 Illinois Lock Co Valve for door closer

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2696805A (en) * 1949-06-21 1954-12-14 Productive Inventions Inc Fluid motor for wiper apparatus
US2778338A (en) * 1953-01-27 1957-01-22 Shafer Valve Co Internal fluid shut off for hydraulic motor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1016514A (en) * 1912-02-06 Frederik Nielsen Shock-absorber.
US1690113A (en) * 1927-03-17 1928-11-06 Gordon B Hooton Spring snubber for automobiles
US1785814A (en) * 1929-02-05 1930-12-23 Enos H Kreider Vehicle shock absorber
US1812244A (en) * 1929-08-06 1931-06-30 Enos H Kreider Vehicle shock absorber
US1899909A (en) * 1932-07-22 1933-02-28 Bernard V Curnen Shock absorbing mechanism
US3010433A (en) * 1958-03-18 1961-11-28 Nat Pneumatic Co Inc Pneumatic motion-checking device and door operating system including same
US3064303A (en) * 1959-05-18 1962-11-20 Illinois Lock Co Valve for door closer

Also Published As

Publication number Publication date
FR2144770A1 (enExample) 1973-02-16
FR2144770B1 (enExample) 1976-08-06
JPS5644288B1 (enExample) 1981-10-19
GB1392296A (en) 1975-04-30
DE2232110A1 (de) 1973-01-18

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