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US3691907A - Reciprocating fluid operated actuator - Google Patents

Reciprocating fluid operated actuator Download PDF

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Publication number
US3691907A
US3691907A US25842A US3691907DA US3691907A US 3691907 A US3691907 A US 3691907A US 25842 A US25842 A US 25842A US 3691907D A US3691907D A US 3691907DA US 3691907 A US3691907 A US 3691907A
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United States
Prior art keywords
piston
reversing valve
end wall
cylinder
spring
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Expired - Lifetime
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US25842A
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English (en)
Inventor
Hanns-Dieter Paschke
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L23/00—Valves controlled by impact by piston, e.g. in free-piston machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure

Definitions

  • a reciprocating fluid operated actuator comprising a cylinder containing a differential piston and means for admitting fluid under pressure to the opposite ends of the cylinder and a reversing valve in the closed end wall of the cylinder for selectively opening and closing an inlet and outlet port at that end.
  • the reversing valve is arranged to be actuated automatically by the piston through a spring and a lost motion mechanism at the opposite ends of the piston stroke.
  • a further pressure chamber On the remote side of this end wall is a further pressure chamber, to which pressure fluid is admitted, and the reversing valve includes a valve element in this chamber controlling the flow through an inlet passage from the chamber into the adjacent end of the main cylinder, and a second valve element within the main cylinder controlling the outlet.
  • the pressure inlets and outlets are all connected to the main cylinder.
  • the piston diameter must exceed a certain minimum size as otherwise the reversing valvecannot be accommodated, but in many applications, where only a limited output force is required a piston diameter of a few centimeters or less is sufficient, although this does not allow a reversing valve to be located in the piston.
  • a further disadvantage lies in the fact that the piston rod must always be extended out of the cylinder, since the piston rod itself contains the return flow line. Often however it is not necessary for the piston rod to project externally, for example when the device is used as an oscillation generator for riddling devices, in which, by virtue of the reciprocating mass of the piston, the cylinder is itself caused to oscillate, these oscillations being transferred to the riddling plates, screens or the like.
  • Another disadvantage is than if the supply and/or return lines are connected to the oscillating piston rod it is necessary to provide flexible connections.
  • the invention consists broadly in a reciprocating fluid pressure operated actuator, comprising a cylinder containing a displaceable differential piston having opposing faces of different effective areas the said piston and cylinder defining a first volume associated with the smaller area side of said piston, and a second volume associated with the larger area side of said piston, a fluid pressure inlet communicating with said first volume, a second fluid pressure inlet and a fluid outlet communicating with said second volume, and a reversing valve mounted in or on a wall of said cylinder and arranged selectively to open and close said second fluid pressure inlet and said fluid outlet, in opposition, said reversing valve being controlled, through springs means, by said piston at or adjacent the extreme operative positions of said piston, and so arranged that said valve is held in one or other operative position by the pressure of the operating fluid until so reversed.
  • the end wall of the second cylinder volume bounds on the opposite side a chamber in to which a fluid pressure supply line leads, there being provided in the endwall a first passage which'connects together the two end faces and a second passageconnecting the end face which lies towards or within the cylinder space to a return flow line, the reversing valve having one valve element on each side of the end wall, these valve elements alternately covering or exposing the end of the first passage on one side of the end'wall and exposing or covering the end ofthe second passage on the other side of the end wall.
  • this second cylinder space is linked with the return flow line, so that the pressure fluid acting on the smaller piston face, "pushesthe piston towards the aforesaid end wall.
  • the reversing valve is rapidly switched over and the connection of this second cylinder space with the return flow line is closed and a connection'made between this cylinder space and the supply line, so that the pressure acting on the larger piston face displaces the piston in the other direction.
  • the reversing valve should always be moved abruptly from one position into the other, in order to avoid a midway position in which both passages in the end wall are temporarily open, since this would allow the pressure fluid to escape directly into the return flow line.
  • This abrupt change-over is achieved by means of toggle-action springs which are stressed by the movement of the piston into its extreme positions, and then abruptly shift the reversing valve to the other position.
  • the reversing valve is operated by the piston through a combined tension and compression spring, the spring being compressionstressedupon reversal into one position and tensionstressed upon reversal into the other position.
  • reversing valve can also be operated by the'piston through two tension or compression springs acting in opposite directions, or by a single compression spring.
  • the combined tension and compression spring can be arranged to bear directly at one end against the piston and at the other on the reversing valve.
  • a longitudinally displaceable rod which is connnected to the piston against withdrawal, and which cooperates with the reversing valve and is in turn connected to the piston in one of the two directions of displacement through a spring which is not biassed until the rod actuates the reversing valve.
  • the piston itself can through a spring, switch the reversing valve into one position while only reversal into the other position is performed by the rod, and in fact likewise through the same spring. 7
  • the moment of switchover of the reversing valve depends on the one hand on the spring tension and on the other on the pressure of the fluid supplied.
  • the reversing valve In order to be able to keep the piston stroke constant regardless of the pressure level, it is advantageous for the reversing valve to be connected to the piston through a stop which admits of a clearance between the reversing valve and the piston in keeping with thepiston stroke desired.
  • This stop can for example be constituted by the spring disposed between the piston and the reversing valve or between the piston and the aforesaid rod, when this spring is fully compressed, in other words, when its spiral turns abut against each other.
  • the reversing valve In order to ensure that the device will start up when the pressure fluid is supplied, the reversing valve should be spring-loaded, or subject to gravity or other force such that, in its inoperative state, it blocks one or other passage in theend wall, to avoid the reversing valve being in an intermediate position when the device is started, in which case the pressure fluid could flow through-the passages in the end wall directly into the return flow line.
  • This spring may be constituted by a spring which at the same time forms the spring abutment for the reversing valve.
  • FIG. 1 is a longitudinal section through a reciprocating fluid-operated actuator according to the invention, including a reversing valve operated directly by the piston through 'a combined tension and compression spring,
  • FIG. 2 is a longitudinal section through a second example which includes a reversing valve switched over in onedirection directly by the piston through a compression spring and in the other direction by a rod guided in the piston,
  • FIG. 3 is a longitudinal section through the third example, in which the reversing valve is switched over in both directions by a rod guided in the piston, and
  • FIG. 4 illustrates a modified form of the embodiment of FIG. 2.
  • the device consists of a cylinder 1 whose ends are closed by covers 2 and 3, and which contains a movable differential piston 4. Extending from the piston 4 is a piston rod 5 which passesthrough the end cover 3 and has on its free end a threaded portion 6 for attachment to amachine part which is to be moved. As a result of the piston'rod 5, the end face 7 of the piston is smaller in area than the end face 8 of the piston.
  • the piston 4 is sealed with respecttoithe interior cylinder wall by an .O-ring 9, and thus separates from each other two cylinder spaces 10 and 11.
  • Another fluid pressure supply connection 15 leads into a chamber 14 lying on the opposite side of a wall 13 which forms the end wall of the other cylinder space 10.
  • a first passage 16 which connects the two end faces 17 and 18 of the end wall 13, and a second passage 19 which connects the end face 17 which is within the cylinder space 10 to a return or exhaust flow connection 20.
  • a reversing valve Longitudinally displaceable in the end wall 13 is a reversing valve generally designated 21, which has valve elements 22 and 23 mounted one on each side of the end wall 13.
  • valve elements are in the form of valve plates or discs which are connected to each other by a pin 24 and separated by a fixed distance which is greater than the thickness of the end wall 13 in this region.
  • the valve plate 22 is so constructed that it can selectively mask or expose, the end of the passage 19, and the valve plate 23 can likewise mask or expose the end of the passage 16 which leads into the chamber 14.
  • the reversing valve is switched over at or adjacent the extreme positions of the piston 4 by means of a combined tension and compression spring 25, which is attached at one end to the reversing valve 21 and at the other end to a spring plate 26 which is displaceable in the piston 4.
  • the spring plate 26 can move between stops 28 and.29in a recess 27 in. the piston 4 or in the piston rod 5, and thus acts as a lost motion rnechanism.
  • a spring 30 which urges the reversing valve2l into the position shown in FIG. 1 when the device is not operating. This prevents both passages 16 and 19 being open when the device is started by the supply of pressure fluid to the connections 12 and 15, and so prevents fluid flowing fromthe passage 16 through the cylinder space 10 and directly into the return flow line 20'.
  • Thisdevice operates in the following manner:
  • the supply of pressure fluid through the connection 12 applies pressure to the smaller piston face 7, while in the position of the reversing valve 21 as illustrated the return flow line 19 is open.
  • the piston 4 therefore moves to the left (in the drawing).
  • the spring plate 26 engages the stop 29, and upon further leftwards displacement of the piston 4, the spring 25 is compressed.
  • the force of the spring 25 can overcome the combined force of the spring 30 and the pressure acting on the valve plate 23, so'that the reversing valve is abruptly shifted into its other operative position, in which it seals off the return flow passage 19 and opens the passage 16.
  • the end wall 13 of the cylinder space 10' is formed by a component inserted into the cylinder 1', and which again has a passage 16 providing communication between the two end faces 17' and 18', and a passage 19 which connects the end face 17' which lies within the cylinder space 10' to a return or exhaust connection 20'.
  • the passages 16' and 19 are controlled by a reversing valve 21 which has two valve plates 22' and 23', one on each side of the end wall 13, which are held apart at a fixed distance from each other by one or more spacer pins 24', the distance being greater than the thickness of the end wall 13'.
  • the end wall 13' also separates off a chamber 14' into which leads apressure fluid supply connection 15'.
  • FIG. 1 two counteracting compression springs 31 and 32 are arranged to act on the reversing valve 21' in opposite directions, the spring 31 being stronger than the spring 32, so as to hold the reversing valve 21' normally in an inoperative position.
  • the spring 31 therefore simultaneously performs the function of spring 30 in FIG. 1.
  • the spring 32 abuts at one end on the valve plate 22' and at the other end on a displaceable spring abutment plate 33, the movement of which in one direction is restricted by a snap ring 34.
  • a flange 35 on the end of a rod 36 which is movable relative to the piston 4 comes in contact with a stop 37 attached to the piston 4' and at the same time a stop 38 on the other end of the rod 36 engages the valve plate 22' so that the reversing valve 21 assisted by the force of the spring 31, snaps into the other extreme position in which the passage 16 is blocked and the passage 19 is opened.
  • the pressure fluid fed through the connection 12' can now displace the piston4' leftwardly again.
  • the piston 4' engages the spring plate 33 and upon further movement of the piston 4' to the left, the spring 32 is compressed until the spring force is sufficient to overcome the force of the spring 31 and the pressure acting on the spring plate 23'.
  • the reversing valve 21' then snaps back into the position illustrated.
  • the parts are again indicated by the same reference numerals, each with an added double suffix.
  • This example differs from that shown in FIG. 1 essentially in that the reversing valve 21" is switched over in both directions by means of a rod 40 which is longitudinally displaceable in the piston 4", or in the piston rod 5", between two compression springs 41 and 42.
  • the reversing valve 21 comprises a valve plate 43 connected rigidly to the rod 40, and a ball valve 44, which are held apart from each other by a pin 45, the distance being greater than the thickness of the end wall 13".
  • the reversing valve 21" When the spring compression is sufficient to overcome force of the spring 46 and the fluid pressure acting on the ball valve 44, the reversing valve 21" is abruptly switched over, the valve plate 43 then abutting against the end face 17" and blocking the passage 19", simultaneously the pin 45 lifts the ball valve 44 from its seating, so that the pressure fluid can flow from the connection through the passage 16" into the cylinder space 10".
  • the spring 46 serves also like the spring 30 in FIG. 1, to keep the reversing valve 21" in a defined inoperative position when no pressure fluid is admitted.
  • FIG. 4 identical or identically-acting parts are designated by the same reference numerals as in FIG. 2, butwith the index a.
  • the reversing valve 21a is operated in both directions by the samecompression spring 50.
  • the spring 50 is disposed with a slight pre-tension between two spring abutments 51 and 52, of which the spring abutment 51 cooperates with the valve plate 23a while the spring abutment 52 cooperates with the valve plate 220.
  • the spring abutment 51 is connected rigidly to the rod 36a and the spring abutment 52 has a tubular extension 53 which extends loosely through the valve plate 22a.
  • the spring 50 with its spring abutments 51 and 52 is housed in a bore 54 in the end wall 13a, so that the length of the cylinder space 10a may be kept to a minimum for any selected piston stroke.
  • the pressure fluid fed through the connection 15a flows through the passage 16a into the cylinder space 10a and acts on the larger piston face 8a so that the piston 4a moves downwardly.
  • a stop 37a attached to the piston engages a flange 35a on the lower end of the rod 360 so that the spring 50 is compressed by the spring abutment 51 and, through the spring abutment 52, shifts the valve plate 220 downwards off its seat 17a.
  • the spacer 24a which is rigidly fixed to the two valve plates 22a and 23a pulls the valve plate 23a down onto its seat 180.
  • the inoperative position of the reversing valve 214 which is achieved by spring force in the other examples, can be achieved by force of gravity in the vertical arrangement illustrated.
  • a reciprocating fluid pressure operated .actuator comprising a cylinder having an end wall and containing a displaceable differential piston having opposing faces of different effective areas, the said piston and cylinder defining a first cylinder space associated with the smaller area side of said piston, and a second cylinder space associated with the larger area side of said piston, a fluid pressure supply connection communicating with said first cylinder space, said end wall having a fluid pressure supply passage and a fluid return passage adapted to communicate with said second cylinder space, a reversing valve mounted on said end wall of said cylinder and arranged selectively to open and close said fluid pressure passage and said fluid return passage, spring means coupled with said reversing valve and said piston, said reversing valve being controlled through said spring means by said piston adjacent the exn-eme operative positions of said piston, the valve being held in each of its operative positions by the fluid pressure and by the force of the spring means, such spring force being independent of the position of the piston during its travel between the extreme positions, said end wall having a side defining the end of
  • An actuator according to claim 4 including a longitudinally movable element connected to said piston and operatively connected to said valve, and means for preventing withdrawal of said movable element from said piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Actuator (AREA)
  • Hydraulic Motors (AREA)
US25842A 1969-04-08 1970-04-06 Reciprocating fluid operated actuator Expired - Lifetime US3691907A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691917792 DE1917792A1 (de) 1969-04-08 1969-04-08 Druckmittelbetriebene Vorrichtung zur Erzeugung einer hin- und hergehenden Bewegung

Publications (1)

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US3691907A true US3691907A (en) 1972-09-19

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Application Number Title Priority Date Filing Date
US25842A Expired - Lifetime US3691907A (en) 1969-04-08 1970-04-06 Reciprocating fluid operated actuator

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US (1) US3691907A (de)
CH (1) CH510198A (de)
DE (1) DE1917792A1 (de)
FR (1) FR2038313A1 (de)
GB (1) GB1299003A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4165788A (en) * 1976-11-08 1979-08-28 Roger Montabert Hydraulic percussion apparatus
US4240329A (en) * 1979-01-05 1980-12-23 Proteus Corporation Fluid pressure servo detent mechanism
US4265164A (en) * 1978-04-24 1981-05-05 Kabushiki Kaisha Asahi Enterprise Pressure detecting device
DE3048814A1 (de) * 1979-12-27 1981-09-24 Hitachi, Ltd., Tokyo Hydraulische betaetigungseinrichtung
US4401168A (en) * 1981-07-09 1983-08-30 Conzinc Riotinto Malaysia Sendirian Berhard Impact applying mechanism
US4870890A (en) * 1986-09-17 1989-10-03 Cowan Philip L Automatic reversing valve
US20140138887A1 (en) * 2011-07-08 2014-05-22 Rafael Knobloch Gas spring with dampening

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2728571C2 (de) * 1977-06-24 1982-02-25 J. Warne Burkburnett Tex. Carter jun. Dampfmaschine
DE3003755A1 (de) * 1979-02-02 1980-08-14 British Nuclear Fuels Ltd Verfahren und vorrichtung zum abscheiden von feststoffteilchen aus einer fluessigkeit
HU180810B (en) * 1979-04-05 1983-04-29 Cspel Autogyar Slack adjuster
EP0321573B1 (de) * 1987-05-28 1993-08-04 Yamada Yuki Seizo Co. Ltd. Hin- und herbewegende schaltungsstrukttur für pumpe
DE3938492A1 (de) * 1989-11-20 1991-05-23 Dengen Co Druckmittelbetriebener motor
DE19960630B4 (de) * 1998-12-18 2014-01-16 Entegris, Inc. Kunststoffventil

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH50741A (de) * 1910-03-30 1911-07-01 Haeny & Cie E Durch eine Druckflüssigkeit betriebener Kolbenmotor
US2804055A (en) * 1953-10-26 1957-08-27 Martha H Hill Fluid motor with piston actuated valve means
US3183788A (en) * 1962-11-09 1965-05-18 Olsson Bror Sigurd Devices for performing rotational movements
US3441592A (en) * 1965-04-14 1969-04-29 Bayer Ag Arylimino chlorocarbonyl cyanides and preparation thereof

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH50741A (de) * 1910-03-30 1911-07-01 Haeny & Cie E Durch eine Druckflüssigkeit betriebener Kolbenmotor
US2804055A (en) * 1953-10-26 1957-08-27 Martha H Hill Fluid motor with piston actuated valve means
US3183788A (en) * 1962-11-09 1965-05-18 Olsson Bror Sigurd Devices for performing rotational movements
US3441592A (en) * 1965-04-14 1969-04-29 Bayer Ag Arylimino chlorocarbonyl cyanides and preparation thereof

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4165788A (en) * 1976-11-08 1979-08-28 Roger Montabert Hydraulic percussion apparatus
US4265164A (en) * 1978-04-24 1981-05-05 Kabushiki Kaisha Asahi Enterprise Pressure detecting device
US4240329A (en) * 1979-01-05 1980-12-23 Proteus Corporation Fluid pressure servo detent mechanism
DE3048814A1 (de) * 1979-12-27 1981-09-24 Hitachi, Ltd., Tokyo Hydraulische betaetigungseinrichtung
US4401168A (en) * 1981-07-09 1983-08-30 Conzinc Riotinto Malaysia Sendirian Berhard Impact applying mechanism
US4870890A (en) * 1986-09-17 1989-10-03 Cowan Philip L Automatic reversing valve
US20140138887A1 (en) * 2011-07-08 2014-05-22 Rafael Knobloch Gas spring with dampening

Also Published As

Publication number Publication date
CH510198A (de) 1971-07-15
FR2038313A1 (de) 1971-01-08
DE1917792A1 (de) 1970-11-05
GB1299003A (en) 1972-12-06

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