US3606818A - Fluid-operated reciprocating motors - Google Patents

Fluid-operated reciprocating motors Download PDF

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Publication number
US3606818A
US3606818A US837126A US3606818DA US3606818A US 3606818 A US3606818 A US 3606818A US 837126 A US837126 A US 837126A US 3606818D A US3606818D A US 3606818DA US 3606818 A US3606818 A US 3606818A
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US
United States
Prior art keywords
valve
pistons
wall
plate
fluid
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 - Lifetime
Application number
US837126A
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English (en)
Inventor
Helmut Hirn
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.)
RILCO MASCHF
Rilco Maschinenfabrik & Co Kg GmbH
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RILCO MASCHF
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.)
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Publication date
Application filed by RILCO MASCHF filed Critical RILCO MASCHF
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Publication of US3606818A publication Critical patent/US3606818A/en
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Expired - Lifetime legal-status Critical Current

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    • 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/03—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with movement in two directions being obtained by two single-acting piston liquid engines, each acting in one direction
    • F03C1/035—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with movement in two directions being obtained by two single-acting piston liquid engines, each acting in one direction one single-acting piston being always under the influence of the liquid under pressure
    • 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
    • F03C1/003—Reciprocating-piston liquid engines controlling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • a reciprocating fluid operated motor including two interconnected spaced co-axial pistons of different diameters lying in two corresponding spaced cylinders separated by an intermediate wall, means for introducing pressure fluid on one side of the wall and for exhausting fluid from the other side of the wall and automatic valve means controlling the flow of fluid through passages in the wall including two valve plates interconnected by spacers of greater effective length than the thickness of the wall.
  • One valve plate is arranged to close the through passages and the other plate has aligned openings but is arranged to close the outlet duct.
  • the motor may also include automatic valve mechanism to hold the reciprocating pistons stationary at one end of their travel.
  • the invention relates to a pressure fluid-operated device for generating a reciprocating movement and comprising a piston-cylinder unit with a fluid inlet and outlet.
  • a pressure fluid-operated device for generating a reciprocating movement and comprising a piston-cylinder unit with a fluid inlet and outlet.
  • Such devices are suitable for many types of machine, in which a tool or machine part has to perform a reciprocating movement, e.g. stamping and pressing machines, rams, saws, riddling machines, conveyor apparatus and the like.
  • the invention consists in a pressure fluid-operated device for producing a reciprocating movement, comprising a housing having two coaxial cylinder spaces of different diameters and an intermediate wall, a pair of pistons movable in the spaces and connected to each other by a piston rod passing through the intermediate wall, the wall also having a through passage opening into opposite faces of the wall, and including two plate valves positioned on opposite sides of the intermediate wall to control the openings of the through passage, the plate valves being held apart at a fixed distance from each other in excess of the thickness of the intermediate wall by means of a spacer passing through the wall, and arranged to be operated by relative movement between the pistons and the housing, a discharge duct emerging into the face of the intermediate wall adjacent the larger cylinder space, to be controlled by the respective valve plate, and an inlet duct communicating with the smaller cylinder space.
  • the supply and discharge of pressure fluid to and from the two cylinder spaces is thus controlled by the reversing valve formed by the plate valves disposed within the housing between the two cylinder spaces, and the pistons and piston rod may therefore be dimensioned without regard to the accommodation or actuation of the valves.
  • the valves do not require any special expensive seals, since they are totally enclosed.
  • the .actuation of the plate valves results from the relative movement between the connected pistons and the housing, the housing normally being stationary while the pistons perform the reciprocating movement so as to reverse the plate valves when they reach their respective extreme positions. -It is also possible for the pistons to remain stationary while the cylinder performs the reciprocating movement, in which case the tool or machine part to be moved is connected to the cylinder.
  • the outer ends of the cylinder spaces may be open, so that the provision of cylinder covers is unnecessary.
  • the inner ends of the cylinder spaces adjacent the intermediate Wall may each have a relatively large diameter recess to accommodate the respective plate valve.
  • the plate valves are conveniently operated by the associated pistons through spring means, in order to cause an abrupt reversal and to prevent the pressure medium from escaping directly into the discharge duct from the supply duct during the reversal process.
  • the spring means are preferably braced on the housing when in the inoperative state, and preferably the spring means associated with the two plate valves have different degrees of initial stress, so that when the device is put into operation, one plate valve will be resting on its valve seat, and the device can start up in any position of the pistons.
  • the facing surfaces of the plate valves which cooperate with the mouths of the through passage in the intermediate wall may be locally raised so that partial balancing of the pressure on both sides of the plate valves occurs.
  • the supply duct may be positioned in an outwardly extending piston rod or directly in the housing.
  • the smaller diameter cylinder space may be provided with a pressure relief valve.
  • the desired inoperative position will be achieved by the force of gravity, or for example by a spring.
  • Another possible method of providing an inoperative position in one extreme position of the pistons consists in disposing a shut-off valve in the discharge duct or in the discharge pipe. If the shut-off valve is closed, while pressure medium is being supplied to the larger diameter cylinder space, then the pistons, after the extreme position has been reached, cannot travel back in the opposite direction since the closed shut-off valve prevents the pressure medium escaping out of the larger-diameter cylinder space.
  • the shutoff valve may be operated automatically by the pressure in the larger-diameter cylinder space.
  • FIG. 1 is a longitudinal section through a first embodiment of the invention.
  • FIG. 2 is a longitudinal section through a second embodiment, similar parts being indicated by the same reference numerals.
  • FIG. 1 shows a housing 1 having two coaxial cylinder spaces 2 and 3 of different diameter, the spaces being positioned on opposite sides of an intermediate wall 4. Movably enclosed in the cylinder spaces 2 and 3 are pistons 5 and 6 respectively.
  • the pistons 5 and 6 each have a diameter corresponding to the diameter of their cylinder spaces 2 and 3 respectively, and are connected rigidly to each other by a piston rod 7 which extends through the intermediate wall 4.
  • the pistons 5 and 6 and the piston rod 7 are guided in the housing by packings 8 which also act as fluid seals.
  • a tool Secured to an extension 9 at one end of the piston rod 7 is a tool, not shown, for example the stamping plate of a soil consolidating device.
  • the annular wall faces 10 and 11 of the intermediate wall 4 have valve seats for plate valves 12 and 13 which are held by spacers 15 at a fixed distance from each other, in excess of the thickness of the intermediate wall 4, so that only one or other plate valve 12, 13 can rest on the corresponding wall face 10 or 11 respectively.
  • the intermediate wall 4 is also formed with through passages or ducts 16, having openings on both sides of the wall.
  • the openings in the wall face 11 are capable of being closed by the plate valve 13, but the plate valve 12 has apertures 17 in line with the openings into the face 10.
  • the smaller diameter cylinder space 3 communicates with a pressure medium supply duct 19 formed in the housing 1.
  • the cylinder spaces 2 and 3 have recesses 20, 21 of larger diameter to accommodate the plate valves 12, 13, so that the diameters of the pistons 5, 6 can be kept small.
  • the plate valves 12, 13 are engaged by springs 22, 23 in the form of pairs of radially corrugated annular plates which are located in and abut against the housing 1 through spring plates 24, 25.
  • the spring plates 24, 25 are guided on the piston rod 7 but allow fluid to flow into and out of the spaces 2, 3, and act in the manner described below in conjunction with the pistons 5, 6 in order to operate the plate valves 12, 13.
  • the device shown in FIG. 1 functions in the following manner In the illustrated position of the plate valves 12, 13, the pistons 5, -6 will move downwardly under the action of the pressure medium supplied through the duct 19, since the ducts 16 are covered by the plate valve 13 and the discharge duct 18 is open. The pressure therefore acts above the piston 6, while the fluid medium in the cylinder space 2 can escape through the duct 18. Upon further movement of the pistons 5, 6 downwardly, the piston 5 engages the spring plate 24, thus compressing the spring 22.
  • the plate springs 22, 23 are provided with differing initial com- 4 pressions. This ensures that the device starts to operate with the supply of pressure medium, since the plate valves 12, 13 cannot be located in an intermediate position in which the pressure medium could flow through the ducts 16 directly into the discharge duct 18.
  • shut-off valve 27 is disposed in the discharge pipe 26.
  • the shut-off valve 27 is closed, while the pistons 5, 6 are moving upwardly in the drawing, in other words while the plate valve 12 has closed the discharge duct 18, the pistons cannot any longer move downwardly after reaching the upper extreme position, since the pressure medium cannot escape from the cylinder space 2.
  • FIG. 2 differs initially from that shown in FIG. 1, in that the supply duct 19' is disposed in the extension 9 of the piston rod and discharges into the cylinder space 3 immediately above the smaller diameter piston 6.
  • Another difference is the construction of the plate valves 12' and 13', which have facing surfaces 28 and 29 to co-operate with the mouths of the ducts 16 and 18, the surfaces being raised locally in order to achieve partial balancing of the pressures on both sides of the plate valves 12 and 13, in order to reduce the resultant hydraulic of pneumatic pressure holding these plate valves against the wall faces 10, 11.
  • FIG. 2 is provided with a pressure relief valve 30 through which the cylinder space 3 can communicate with the atmosphere or, in the case of hydraulic operation, with a return pipe.
  • a pressure relief valve 30 through which the cylinder space 3 can communicate with the atmosphere or, in the case of hydraulic operation, with a return pipe.
  • the valve 30 When the valve 30 is opened, the pressure medium supplied through the duct 19' is exhausted immediately without performing any work and the pistons 5, 6, move under gravity into an extreme position when the device is substantially vertical in operation.
  • the piston rod extension 9' is braced on the ground, as is the case with soil stamping devices, the housing 1 falls under its own weight until the spring plate 25 rests on the piston 6. If the device is arranged on an essentially horizontal longitudinal axis, than the extreme position can be achieved upon opening of the valve 30 by an appropriate spring loading of the pistons 5, 6.
  • the device may be held stationary in one extreme position of the pistons 5, 6, by means of a shut-off valve 27' which in operation corresponds to the shut-off valve 27 shown in FIG. 1, but in this case is operated by the pressure in the cylinder space 2.
  • the shut-off valve 27' has a piston 31 which is normally held by a spring 32 in the open position in which the discharge duct 18 communicates with the discharge pipe 26.
  • the device then operates as a reciprocating pressure medium motor, so long as pressure medium is being fed through the duct 19.
  • a manually operated rotary valve 33 is included in the connection between the piston 31 and the cylinder space 20.
  • the valve 33 has an exhaust port 34, and in the position shown in FIG. 2 the valve is open and the port 34 is closed.
  • the piston 31 If the piston 31 is depressed by the pressure obtaining in the cylinder space 2, with the rotary valve 33 in the open position as illustrated, it will move against the resistance of the spring 32 and shut off the discharge duct 18.
  • the pressure medium supplied via duct 19' can now move the pistons 5, 6 upwardly to the extreme position.
  • the plate valves 12, 13' are reversed in the manner described above in relation to FIG. 1, i.e. the plate valve 13' comes to rest on the wall face 11 and closes off the ducts 16, while the plate valve 12' is lifted and exposes the discharge duct 18, which however remains closed by the piston 31.
  • the pistons 5, 6 remain in this extreme position.
  • the rotary valve 33 is pivoted leftwards through 90 so that the pressure side of the piston 31 is exhausted to atmosphere via the control aperture 34,
  • the pressure side of the piston is connected with the discharge pipe 26 or directly with a reservoir, and in either case the spring 32 can displace the piston 31 into the open position.
  • the device is operated with a non-compressible working medium, e.g. oil
  • a non-compressible working medium e.g. oil
  • a pressure fluid-operated device for producing a reciprocating movement comprising a housing having two coaxial cylinder spaces of difierent diameters and an intermediate wall, a pair of pistons movable in the spaces and connected to each other by a piston rod passing through the intermediate wall, the wall also having a through passage opening into opposite faces of the wall, and including two plate valves positioned on opposite sides of the intermediate wall, the plate valve in the smaller cylinder space controlling the opening of the through passage into the said smaller cylinder space the plate valves being held apart at a fixed distance from each other in excess of the thickness of the intermediate wall by means of a spacer passing through the wall, and arranged to be operated by relative movement between the pistons and the housing, a discharge duct emerging into the face of the intermediate wall adjacent the larger cylinder space, to be controlled by the plate valve in said larger cylinder space, and an inlet duct communicating with the smaller cylinder space.
  • a device in which the inner ends of the cylinder spaces adjacent the intermediate wall each have a recess of larger diameter to accommodate the respective plate valve.
  • a device in which the plate valves are arranged to be operated by the associated pistons through spring means.
  • a device in which the facing surfaces of the plate valves which co-operate with the openings at the ends of the through passage have locally raised formations to provide partial pressure balancing of each plate valve.
  • a device in which the inlet duct is formed in a wall of the housing.
  • a device in which the smaller cylinder space is provided with a pressure relief valve.
  • a device in which a shutoff valve is provided in the discharge duct.
  • shutoff valve is adapted to be operated automatically by the pressure in the larger diameter cylinder space.
  • a device including a threeway on-otf relief valve, a non-return valve, and pressure accumulator means, disposed in the line between the respective cylinder space and the shut-01f valve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Motors (AREA)
  • Chairs Characterized By Structure (AREA)
  • Fluid-Damping Devices (AREA)
US837126A 1968-07-03 1969-06-27 Fluid-operated reciprocating motors Expired - Lifetime US3606818A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1703726A DE1703726C3 (de) 1968-07-03 1968-07-03 Druckflüssigkeitsbetriebene Vorrichtung zur Erzeugung einer hin- und hergehenden Bewegung

Publications (1)

Publication Number Publication Date
US3606818A true US3606818A (en) 1971-09-21

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ID=5688531

Family Applications (1)

Application Number Title Priority Date Filing Date
US837126A Expired - Lifetime US3606818A (en) 1968-07-03 1969-06-27 Fluid-operated reciprocating motors

Country Status (7)

Country Link
US (1) US3606818A (enrdf_load_stackoverflow)
AT (1) AT298547B (enrdf_load_stackoverflow)
CH (1) CH503192A (enrdf_load_stackoverflow)
DE (1) DE1703726C3 (enrdf_load_stackoverflow)
FR (1) FR2019291A1 (enrdf_load_stackoverflow)
GB (1) GB1229144A (enrdf_load_stackoverflow)
SE (1) SE341168B (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3735708A (en) * 1970-04-17 1973-05-29 Plasser Bahnbaumasch Franz Drive for vibrating a track maintenance machine tool
WO1997024533A1 (en) * 1995-12-29 1997-07-10 Kvaerner Pulping Ab Hydraulic unit
US5676033A (en) * 1995-05-09 1997-10-14 Szabo; Zsolt Pneumatic drive device

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3735708A (en) * 1970-04-17 1973-05-29 Plasser Bahnbaumasch Franz Drive for vibrating a track maintenance machine tool
US5676033A (en) * 1995-05-09 1997-10-14 Szabo; Zsolt Pneumatic drive device
WO1997024533A1 (en) * 1995-12-29 1997-07-10 Kvaerner Pulping Ab Hydraulic unit
AU702086B2 (en) * 1995-12-29 1999-02-11 Kvaerner Pulping Ab Hydraulic unit
US6095028A (en) * 1995-12-29 2000-08-01 Kvaerner Pulping Ab Hydraulic unit

Also Published As

Publication number Publication date
DE1703726C3 (de) 1974-03-07
CH503192A (de) 1971-02-15
AT298547B (de) 1972-05-10
FR2019291A1 (enrdf_load_stackoverflow) 1970-07-03
SE341168B (enrdf_load_stackoverflow) 1971-12-13
GB1229144A (enrdf_load_stackoverflow) 1971-04-21
DE1703726B2 (de) 1973-08-09
DE1703726A1 (de) 1971-01-28

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