EP0164334B1 - Cylindre hydraulique à multiplication d'effort - Google Patents

Cylindre hydraulique à multiplication d'effort Download PDF

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Publication number
EP0164334B1
EP0164334B1 EP85890103A EP85890103A EP0164334B1 EP 0164334 B1 EP0164334 B1 EP 0164334B1 EP 85890103 A EP85890103 A EP 85890103A EP 85890103 A EP85890103 A EP 85890103A EP 0164334 B1 EP0164334 B1 EP 0164334B1
Authority
EP
European Patent Office
Prior art keywords
piston
force
transmitter
shut
pressure medium
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
EP85890103A
Other languages
German (de)
English (en)
Other versions
EP0164334A1 (fr
Inventor
Dionizy Simson
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.)
Cessione hoerbiger Ventilwerke AG
Original Assignee
ENFO Grundlagen Forschungs AG
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 ENFO Grundlagen Forschungs AG filed Critical ENFO Grundlagen Forschungs AG
Priority to AT85890103T priority Critical patent/ATE36038T1/de
Publication of EP0164334A1 publication Critical patent/EP0164334A1/fr
Application granted granted Critical
Publication of EP0164334B1 publication Critical patent/EP0164334B1/fr
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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention relates to a hydraulic cylinder with force multiplication, with a cylinder housing in which a working piston with a piston rod on one side and a two-stage force booster piston having two regions of different diameters are sealed and arranged to be axially movable, the cylinder housing being a stepped bore with a shoulder between two regions of different diameter and the power booster piston with its areas of different diameters is guided in one of the areas of different diameters of the stepped bore to form an intermediate annular chamber, the pressure medium supply line being parallel to the drive side of the working piston and the drive side of the larger stage of the power transmission piston and in the supply line to the larger stage the power booster piston is arranged a shut-off device, which when the supply pressure increases as soon as the working piston to a Hind ernis meets opens, and the pressure chamber of the smaller stage of the power booster piston is connected to the drive side of the working piston.
  • Hydraulic cylinders are required in many places, where a fast stroke with little force and then a short, slow stroke with great force are important. Hydraulic cylinders with hydraulic ratios are used in fixture construction, manufacturing machines and presses, in civil engineering for piling and pulling devices. Such cylinders are more compact and lighter than single-stage hydraulic cylinders with the same effective force.
  • It hydraulic cylinder of the type mentioned is known for example from DE-A-1 903 852.
  • a two-stage working piston penetrates at least partially a partially sleeve-like power transmission piston, the smaller overdrive stage of the working piston being acted upon directly by the pressure medium supplied, whereas the larger working stage of the working piston is acted upon by pressure medium of higher pressure.
  • the increase in the supply pressure is used as soon as the working piston encounters an obstacle to act on the larger step of the power transmission piston, which then generates the higher pressure with its smaller step to act on the working step of the working piston. Due to the design of the working piston and the arrangement of both pistons acting in the same direction, this known hydraulic cylinder is also relatively large and can therefore only be used instead of the customary single-stage cylinder while accepting disadvantages in this regard.
  • the object of the present invention is to avoid the disadvantages of the known arrangements and to improve a hydraulic cylinder of the type mentioned at the outset in such a way that the simplest possible way without appreciable increase in size and weight compared to conventional single-stage cylinders.
  • the working piston is formed in a single stage and with a piston rod penetrating the force intensifying piston centrally sealed and is guided in the region of the stepped bore with a smaller diameter, the piston rod penetrating the region of the stepped bore with a larger diameter, and in that the annular chamber between the two areas of different diameters on the force intensifier piston and on the cylinder housing directly forms the pressure chamber of the smaller step of the force intensifier piston.
  • Working piston and power booster piston are thus arranged directly in the same cylinder housing, the power booster piston moving in the opposite direction to the direction of movement of the working piston when pressure is applied, which enables a simple and compact construction.
  • the area of the stepped bore with a smaller diameter lying between the working piston and the pressure booster piston has an opening for pressure medium supply and discharge, which on the one hand allows the two pistons to be easily returned to their starting position after the working stroke has been carried out and on the other hand results in a very simple way a stroke limitation, since when this opening is shut off by the working piston no further stroke is possible.
  • an opening piston can be acted upon by pressure medium, which opens the shut-off element in the pressure medium supply line to the drive side of the force transmission piston.
  • pressure medium can flow off without pressure from the drive side of the power booster piston via the associated shut-off device.
  • a further shut-off element is connected in the pressure medium supply line to the drive side of the working piston, which opens at a lower pressure than that assigned to the power transmission piston and has an associated opening piston which is parallel to the Opening piston of the other shut-off element can be acted upon with pressure medium.
  • a single-stage working piston and a two-stage power booster piston 3 are arranged in the cylinder housing 1, a piston rod 4 connected to the working piston 2 passing through the power booster piston 3.
  • the working piston 2 has a circumferential groove 5 with a sealing ring 6 provided therein.
  • the force intensifier piston 3 comprises the regions 7 and 8 which form the two stages and which have a different diameter from one another.
  • a circumferential groove 9 and 10 with seals 11 and 12 are provided in the area 7 and in the area 8.
  • a circumferential groove 14 with a seal 15 provided therein is also provided in the bore 13 provided in the region 8 of the force booster piston 3 for the passage of the piston rod 4.
  • the cylinder housing 1 is closed on the side of the force booster piston 3 by a cylinder cover 16, through which the piston rod 4 is guided.
  • a circumferential groove 18 is provided in the bore 17 of the cylinder cover 16, a circumferential groove 18 is provided with a seal 19 attached therein.
  • a first shut-off element which is acted upon by a first, weak spring 21 and is designed as a shut-off piston 22, and a second shut-off element acted upon by a second, strong spring 23 and which is designed as a shut-off piston 24.
  • Both the first and the second shut-off piston are designed in two stages, a part 25 or 26 with a larger diameter and a part 27 or 28 with a smaller diameter being provided in each case.
  • a piston rod 29 or 30 is connected to each of the parts 27 and 28 with a smaller diameter, which each lead into a chamber 31 or 32 opposite the shut-off piston. Opening pistons 33 and 34 are provided in the chambers 31 and 32.
  • a supply line 35 for the pressure medium leads into the chamber 31 in the area between the piston rod 29 and the end face of the opening piston 33, the two chambers 31 and 32 being connected by a line 36.
  • the chamber 37 surrounding the front part 27 of the first shut-off piston 22 is connected via a line 38 to a first pressure chamber 39 on the drive side of the working piston between the latter and the cylinder wall.
  • a branch line 40 leads into an annular chamber 41 between the area 7 of the force booster piston 3 and the inner wall of the cylinder housing 1.
  • This annular chamber 41 is laterally by a shoulder 42 on the outer circumference of the force booster piston 3 and by a shoulder 43 on the inner wall of the Cylinder housing 1 limited.
  • the chamber surrounding the front part 28 of the second shut-off piston 24 is connected via a line 44 for the pressure medium to a second pressure chamber 45 on the drive side of the force booster piston 3 between the boundary surface 46 of the force booster piston opposite the cylinder cover 16 and the cylinder cover.
  • the chamber 47 between the working piston 2 and the power booster piston 3 is connected via a line 48 to the chambers on the right side of the opening piston 33 and 34 according to the figure.
  • the pressure medium is conveyed from the unpressurized chamber 47 via a line 48 into a container (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Servomotors (AREA)
  • Vehicle Body Suspensions (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (4)

1. Vérin hydraulique à multiplication de l'effort, comprenant un corps de cylindre (1, 16) dans lequel sont montés à joint étanche et mobiles en translation axiale un piston travaillant (2) muni d'une tige de piston unilatérale (4) et un piston amplificateur d'effort (3), à deux étages, qui présente deux régions (7, 8) de différent diamètre, le corps (1, 16) du vérin présentant un alésage échelonné avec un épaulement (43) entre deux régions de différent diamètre, et le piston amplificateur d'effort (3) étant guidé respectivement par ses deux régions de différent diamètre dans les deux régions de différent diamètre de l'alésage échelonné, en formant une chambre annulaire (41) interposée entre ces régions, la conduite d'arrivée du fluide de pression (35) aboutissant en parallèle au côté moteur (39) du piston travaillant (2) et au côté moteur (45) du grand étage du piston amplificateur d'effort (3), et un organe d'arrêt (28) étant intercalé dans la conduite d'arrivée (44) aboutissant au grand étage (8) du piston amplificateur d'effort, cet organe s'ouvrant en réponse à une élévation de la pression de la conduite d'arrivée de pression dès que le piston travaillant (2) rencontre un obstacle, et la chambre de pression (41) du petit étage (7) du piston amplificateur d'effort (3) étant reliée au côté moteur (39) du piston travaillant, caractérisé en ce que le piston travaillant (2) est d'une configuration à un seul étage et comprend une tige de piston (4) qui traverse le piston amplificateur d'effort (3) sur son axe et à joint étanche, ce piston coulissant dans la région de petit diamètre de l'alésage échelonné et la tige de piston (4) traversant la région de grand diamètre de l'alésage échelonné, et en ce que la chambre annulaire comprise entre les deux régions (7, 8) de différent diamètre au droit du piston amplificateur d'effort (3) et au droit du corps (1, 16) du ' vérin forme directement la chambre de pression (41) du petit étage du piston amplificateur d'effort (3).
2. Vérin hydraulique selon la revendication 1, caractérisé en ce que la région de petit diamètre de l'alésage échelonné qui est comprise entre le piston travaillant (2) et le piston amplificateur d'effort présente un orifice donnant sur la conduite d'arrivée ou de départ de fluide travaillant (48).
3. Vérin selon la revendication 2, caractérisé en ce que, en parallèle avec l'orifice compris entre les deux pistons (2, 3), est prévu un piston d'ouverture (34) pouvant être chargé par le fluide de pression et qui ouvre l'organe d'arrêt (28) intercalé dans la conduite d'arrivée de fluide de pression qui aboutit au côté moteur (45) du piston amplificateur d'effort (3).
4. Vérin selon la revendication 3, caractérisé en ce qu'il est prévu, en parallèle avec l'organe d'arrêt (28) intercalé dans la conduite d'arrivée de fluide de pression qui aboutit au côté moteur (45) du piston amplificateur d'effort (3), un organe d'arrêt supplémentaire (27) intercalé dans la conduite d'arrivée de fluide de pression qui aboutit au côté moteur (39) du piston travaillant (2), organe qui s'ouvre à une plus faible pression que l'organe associé au piston amplificateur d'effort, et qui est muni d'un piston d'ouverture respectif (33) qui peut être chargé par le fluide de pression en parallèle avec le piston d'ouverture (34) de l'autre organe d'arrêt (28).
EP85890103A 1984-05-11 1985-05-03 Cylindre hydraulique à multiplication d'effort Expired EP0164334B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85890103T ATE36038T1 (de) 1984-05-11 1985-05-03 Hydraulischer zylinder mit kraftmultiplikation.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2357/84 1984-05-11
CH2357/84A CH665007A5 (de) 1984-05-11 1984-05-11 Hydraulischer zylinder mit kraftmultiplikation.

Publications (2)

Publication Number Publication Date
EP0164334A1 EP0164334A1 (fr) 1985-12-11
EP0164334B1 true EP0164334B1 (fr) 1988-07-27

Family

ID=4231904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85890103A Expired EP0164334B1 (fr) 1984-05-11 1985-05-03 Cylindre hydraulique à multiplication d'effort

Country Status (7)

Country Link
US (1) US4620419A (fr)
EP (1) EP0164334B1 (fr)
JP (1) JPS6136505A (fr)
AT (1) ATE36038T1 (fr)
CH (1) CH665007A5 (fr)
DE (1) DE3564010D1 (fr)
ZA (1) ZA853539B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012007681A1 (de) * 2012-04-17 2013-10-17 Festo Ag & Co. Kg Fluidbetätigter Linearantrieb

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4841846A (en) * 1986-02-24 1989-06-27 Grambling William D Pneumatic actuators with liquid seals for oil and gas well swabs
DE3620876A1 (de) * 1986-06-21 1987-12-23 Hehl Karl Hydraulikelement und damit aufgebautes ziehwerkzeug
JPH02211965A (ja) * 1988-10-31 1990-08-23 Toshiba Mach Co Ltd 型締シリンダ装置
US5062268A (en) * 1990-02-02 1991-11-05 The University Of British Columbia Fluid actuator
US5188014A (en) * 1990-02-14 1993-02-23 Dionizy Simson Hydraulic cylinder with pressure transmission
DE59101302D1 (de) * 1990-02-14 1994-05-11 Dionizy Simson Hydraulikzylinder mit Druckübersetzung.
DE4128389A1 (de) * 1991-08-27 1993-03-04 Grau Gmbh Doppelt wirkender betaetigungszylinder
JP2623075B2 (ja) * 1995-02-03 1997-06-25 悦男 安藤 流体シリンダ
DE10306128A1 (de) * 2003-02-14 2004-08-26 Richard Voß Grubenausbau GmbH Verfahren und Vorrichtung zur Druckerhöhung in Zylindern, insbesondere hydraulischen Stempeln
JP5939950B2 (ja) * 2012-10-01 2016-06-22 株式会社コスメック 倍力機構付きシリンダ装置

Citations (4)

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Publication number Priority date Publication date Assignee Title
GB1420389A (en) * 1972-04-12 1976-01-07 Dexploitation Des Ressorts Aut Pressure converters
US4011724A (en) * 1971-09-16 1977-03-15 Lockheed Aircraft Corporation Dual force actuator
GB1600733A (en) * 1978-02-27 1981-10-21 Midgley A C Coining presses
DE3119307A1 (de) * 1980-05-22 1982-04-22 Gerard Gaston Frans Brampton Ontario Smeets "druckverstaerker"

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Publication number Priority date Publication date Assignee Title
US615912A (en) * 1898-12-13 Steam-engine
DE1176066B (de) * 1960-01-20 1964-08-13 Demag Ag Druckmittelbetaetigter Rammhammer
US3186173A (en) * 1960-09-15 1965-06-01 American Mach & Foundry Variable pressure hydraulic system
JPS4110721Y1 (fr) * 1965-06-14 1966-05-20
US3473328A (en) * 1967-11-01 1969-10-21 Jergens Tool Specialty Co Pressure multiplying booster
DE1964076C3 (de) * 1969-12-22 1978-04-27 G.L. Rexroth Gmbh, 8770 Lohr Arbeitszylinder mit Eilgang und Krafthub
JPS5144078U (fr) * 1974-09-30 1976-04-01
FR2394386A1 (fr) * 1977-01-27 1979-01-12 Somifra Procede et dispositif automatique d'alimentation en matiere telle qu'un elastomere pour machine a injecter
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
JPS55142101A (en) * 1979-04-23 1980-11-06 Masuo Shiaku Output booster for gas reciprocating expansion cylinder

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4011724A (en) * 1971-09-16 1977-03-15 Lockheed Aircraft Corporation Dual force actuator
GB1420389A (en) * 1972-04-12 1976-01-07 Dexploitation Des Ressorts Aut Pressure converters
GB1600733A (en) * 1978-02-27 1981-10-21 Midgley A C Coining presses
DE3119307A1 (de) * 1980-05-22 1982-04-22 Gerard Gaston Frans Brampton Ontario Smeets "druckverstaerker"

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012007681A1 (de) * 2012-04-17 2013-10-17 Festo Ag & Co. Kg Fluidbetätigter Linearantrieb
DE102012007681B4 (de) * 2012-04-17 2016-01-21 Festo Ag & Co. Kg Fluidbetätigter Linearantrieb

Also Published As

Publication number Publication date
US4620419A (en) 1986-11-04
JPS6136505A (ja) 1986-02-21
EP0164334A1 (fr) 1985-12-11
ZA853539B (en) 1986-01-29
DE3564010D1 (en) 1988-09-01
CH665007A5 (de) 1988-04-15
ATE36038T1 (de) 1988-08-15

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