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WO1982002423A1 - Dispositif d'actionnement de vanne - Google Patents

Dispositif d'actionnement de vanne Download PDF

Info

Publication number
WO1982002423A1
WO1982002423A1 PCT/GB1982/000004 GB8200004W WO8202423A1 WO 1982002423 A1 WO1982002423 A1 WO 1982002423A1 GB 8200004 W GB8200004 W GB 8200004W WO 8202423 A1 WO8202423 A1 WO 8202423A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
cylinder
actuator
valve
pressure
Prior art date
Application number
PCT/GB1982/000004
Other languages
English (en)
Inventor
Ltd Camtorc
Original Assignee
Mccormack Wallace
Bowditch David
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 Mccormack Wallace, Bowditch David filed Critical Mccormack Wallace
Publication of WO1982002423A1 publication Critical patent/WO1982002423A1/fr

Links

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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • 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
    • 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
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • 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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7716—Control of direction of movement of the output member with automatic return

Definitions

  • This invention relates to a valve actuator of the kind comprising a pressurised fluid-operated piston and cylinder assembly in which the piston is arranged to actu- ate the valve member of a valve.
  • the actuator in accordance with the invention may be employed to actuate linearly actuable valves, for example gate valves.
  • a pressure fluid-operated actuator of the kind comprising a housing with a cylindrical bore, a piston assembly comprising a pair of spaced-apart pistons coupled together for simultaneous sliding movement within said cylindrical bore, a cam situated between the two pistons and secured to a valve actuating shaft rotatable about an axis fixed relative to the housing and disposed substan- tially at right angles to the longitudinal axis of said cylindrical bore with the peripheral surface of the cam engaging the confronting surfaces of the two pistons of said piston assembly, and means for supplying pressurised fluid to a space in said cylindrical bore for moving said piston assembly within the cylindrical bore.
  • the actuator may be of the single-acting type, in which rotation of the valve actuating shaft in only one direction, for example in the opening direction of the valve, can be effected by supplying pressurised fluid to said space, spring means then being provided for effecting rotation of the valve actuating shaft in the opposite direction.
  • the actuator may be of the double-acting type, so ' that rotation of the valve actuating shaft in either direction can be effected by supplying pressurised fluid to different spaces in said cylindrical bore.
  • spring means may be provided to assist rotation of the shaft in the closing direction of the valve, so that the valve can be closed in the event of failure of the pressurised fluid supply.
  • actuator in the form of a single- or double-acting piston and cylinder assembly, in which the linear movement of the piston rod of the actuator actuates the linearly movable valve member of the valve.
  • This type of actuator may also comprise spring means for effecting or assisting movement of the piston, usually in the valve closing direction.
  • rotary and linear valve actuators are usually operated by a pressurised fluid supply (generally compress- ed air) at a pressure of up to about 10 kg/cm (gauge).
  • a pressurised fluid supply generally compress- ed air
  • pressure up to about 10 kg/cm (gauge)
  • torques of up to 1000 Nm or thrusts of up to 500 kg the actuator does not have an unacceptably large size.
  • the present invention aims to provide a valve actuator of the kind referred to which does not have the disadvan ⁇ tage just referred to.
  • a valve actuator compris- ing an actuator cylinder, an actuator piston movable in the cylinder, a valve actuating member actuable by said piston, and means for supplying pressurised fluid to said cylinder for moving said piston in said cylinder, is characterised in that said pressurised fluid-supplying means comprises a pressure intensifier driven by a pressur ⁇ ised medium at a first pressure and arranged to deliver said pressurised fluid to said actuator cylinder at a pressure higher than that of said pressurised medium.
  • Said pressure intensifier may comprise first and second piston and cylinder assemblies having their cylin ⁇ ders axially aligned with one another* and their pistons mechanically connected, ' the piston of said first piston and cylinder assembly having a larger area than the piston of said second piston and cylinder assembly, and means for supplying said pressurised medium at said first pres ⁇ sure to said first piston and cylinder assembly, said second piston and cylinder assembly constituting the means for supplying pressurised fluid at said higher pressure to said actuator cylinder.
  • Said first piston and cylinder assembly may be double-acting, so that the piston of said first piston and cylinder assembly may be reciprocated in its cylinder by said pressurised medium.
  • said pressure intensifier comprises a first double-acting piston and cylinder assembly having a piston of a first diameter D which is mechanically conn ⁇ ected to the piston of a second double-acting piston and cylinder assembly having a piston of a second diameter d which is smaller than D, the cylinders of the two assem ⁇ blies having their axes aligned with one another.
  • the piston of the first assembly is reciprocated in its cylin ⁇ der by supplying a pressurised fluid medium, for example compressed air, to its cylinder at a pressure p_, which is the aforesaid first pressure.
  • the pressure £ may, for example, be in the range of from 4 to 10 kg/cm (gauge).
  • This reciprocation of the piston of the first assembly results in reciprocation of the piston of the second assem- bly and the creation of a pressure P in the fluid in the aforesaid pressurised fluid-supplying means, the pressure P, which is the aforesaid second pressure, being higher than the pressure £ in accordance with the equation:
  • the pressure P created in said pressurised fluid-supplying means will be 25£. Therefore, for example, if the first piston and cylinder assembly is actuated with compressed air at a
  • the pressurised fluid at the pressure P is contained in a closed, or sub- stantially closed, circuit which includes the second piston and cylinder assembly of the pressure intensifier and the actuator cylinder of the valve actuator.
  • the pressurised fluid at the pressure P may be a fluid of the same or a different nature from the pressur- ised -medium at the pressure £.
  • the second piston and cylinder assembly is single-acting instead of double-acting, it is possible to use one and the same pressurised fluid in both of the piston and cylinder assem ⁇ blies of the pressure intensifier.
  • a single pressure intensifier may be common to a plurality of valve actuators, the actuator cylinders of the various actuators then being connected in parallel with the pressure intensifier.
  • Figure 1 is a schematic sectional view of a first embodiment of a valve actuator in accordance with the ⁇ invention, 'and
  • FIGS 2 and 3 are schematic sectional views of parts of two modified forms of the embodiment of Figure 1.
  • the valve actuator shown in Figure 1 comprises a housing 1 having a circular cylindrical bore 2 therein and end closure members 3 and 4. Slidable within the bore 2 is a piston assembly, generally designated by the reference numeral 5, which comprises two pistons 6, 7 held together in spaced-apart relationship by rods 8.
  • a valve actuating shaft 9 is rotatably mounted in the wall of the housing 1, the axis of the shaft being disposed at right angles to the longitudinal axis of the bore 2.
  • the shaft 9 is part of, or may be connected to, the valve member of a rotary fluid-control valve (not shown).
  • a disc cam 10 is secured to the shaft 9 and has its peripheral surface bearing against the confronting surfaces of the pistons 6, 7.
  • the space 11 in the bore 2 between the end closure member 3 and the piston 6 and the space 12 between the end closure member 4 and the piston 7 form part of a press ⁇ urised fluid-supplying means for moving the piston assembly 5 in the bore 2.
  • the pressurised fluid-supplying means comprises a pressure intensifier, generally designated by the numeral 13, conn ⁇ ected to the spaces 11, 12 by piping described hereinafter in greater detail.
  • the pressure intensifier 13 comprises axially aligned cylinders 14 and 15 having bores of diameters d and D, respectively, d being smaller than D.
  • Non-return valves 31 and 32 are provided in the pipes 27 and 28, respectively, these valves allowing the flow of fluid into the cylinder 14 in the direction from the valve 23, but not in the opposite direction.
  • the valve 23 is a change-over valve which can be adjusted into either one of first and second limit posi ⁇ tions. In its first limit position, shown in Figure 1, the valve 23 connects the pipe 22 to the pipe 24 and conn- ects the pipe 29 to the pipe 30. In its second limit position, the valve 23 connects the pipe 22 to the pipe 30 and connects the pipe 29 to the pipe 24.
  • the cylinder 14, the cylinder spaces 11 and 12 and the pipes 20-22, 24 and 27-30 are all filled with hydraulic fluid.
  • the space 31 between the pistons 6 and 7 serves as a reservoir of hydraulic fluid and is connected by a pipe 32 to the pipe 29.
  • the space 31 is vented to atmos ⁇ phere at 33.
  • the cylinder 15 has its opposite ends connected to pipes 34 and 35, respectively, which are connected, via a changeover valve 36, similar to the valve 23, to a reser ⁇ voir 37 of compressed air and to exhaust 38.
  • the valve actuator shown in Figure 1 employs different pressurised media in the cylinders 14 and 15. If the wall 19 between the cylinders 14 and 15 is omitted, it is possible + * o use the same pressurised medium in both the cylinders 14 and 15. In this case, however, pressur ⁇ ised fluid at the pressure P will only be delivered to the cylinder space 11 (or 12) during upward movements (as viewed in Figure 1) of the piston 16 in the cylinder 14. During downward movements of the piston 16 only the pressure £ will arise in the cylinder space 42. This means, that it would take twice as long to turn the valve actuating shaft 9 through a given angle, compared with the embodiment shown in Figure 1.
  • Figures 2 and 3 show modified embodiments of the actuator of Figure 1 which employ the same pressure intensifier as the actuator of Figure 1.
  • the pressure intensifiers have been omitted from Figures 2 and 3, but it can be assumed that the parts shown in Figure 1 below the chain line A - A are also present in each of the embodiments of Figures 2 and 3 below the chain lines A - A in each of those Figures.
  • the valve actuator shown in Figure 2 again comprises a housing 1 with a cylindrical bore 2 and end closure members 3 and 4, a piston assembly 5 with spaced-apart pistons 6, 7 connected together by rods 8, a valve actuat ⁇ ing shaft 9 and a disc cam 10, all as described with refer ⁇ ence to Figure 1.
  • the numeral 50 designates a hollow cylindrical casing secured to the end closure member 4, the longitudinal axis of the casing 50 being aligned with the longitudinal axis of the bore 2.
  • a piston 51 is slidable in the casing 50 and a helical spring 52 is housed in the casing 50 between the end 53 of the casing and the piston 51.
  • a rod 54 which is slidable in fluid-tight manner in the end closure member 4, has one end connected to _the piston 51 and its other end abutting the piston 7.
  • the space 57 in the casing 50, between the piston 51 and the end 53 of the casing, is vented to atmosphere via a hole 58 in the end 53.
  • the change-over valve 23 again has two limit posi ⁇ tions. In the first limit position, shown in Figure 2, the valve connects the pipe 22 to the pipe 24. In its second limit position, the valve 23 connects the pipe 29 to the pipe 24.
  • hydraulic fluid at pressure P from the pressure intensifier 13 (see Figure 1) is delivered via pipes 22 and 24 to the spaee 11 in the bore 2 and to the space 55 in the casing 50.
  • the pressure intensifier 13 draws hydraulic fluid from the space 31 in the bore 2 via pipe 32.
  • the action of the pressure intensifier 13 results in movement of the piston assembly 5 to the right, as viewed in Figure 2, and clockwise rotation of the valve actuating shaft 9.
  • the hydraulic fluid supplied to the space 55 in the casing 50 moves the piston 51 to the right, as viewed in Figure 2, compressing the spring 52 and relieving the piston assembly 5 from the action of the spring 52.
  • FIG. 1 and 2 are rotary actuators.
  • Figure 3 shows a linear actuator comprising a housing 1, with a cylindrical bore 2 and end closure , members 3 and 4, in which a piston 60 is slidable.
  • the piston 60 has a piston rod 61 which passes through the end closure member 3 and forms part of, or is connected to, the linearly movable valve member of a fluid control valve (not shown), for example a gate valve.
  • a helical spring 62 is located in the housing 1 between the piston 60 and the end closure member 4.
  • the space 11 in the bore 2 is connected to the valve 23 by the pipe 24 and the space 63 in the bore 2, between the piston 60 and the end closure member 4, is connected to the pipe 32.
  • the change-over valve 23 is constructed in the same way as the change-over valve 23 of Figure 2.
  • hydraulic fluid at pressure P from the pressure intensifier 13 (see Figure 1) is delivered via pipes 22 and 24 to the space 11 in the bore 2.
  • the pressure intensifier 13 draws hydraulic fluid from the space 63 in the bore 2 via pipe 32.
  • the action of the pressure intensifier 13 results in movement of the piston 60 to the right, as viewed in Figure 3, and consequent mover.ent to the right of the valve actuating rod 61.
  • the spring 62 is compressed. If the change-over valve 23 is now moved to its previously mentioned second limit position, the pipe 24 is connected to the pipe 29, so that the space 11 becomes connected to the space 63 in the bore 2 via the pipes 24, 29 and 32.
  • the spring 62 then re-asserts itself and moves the piston 60 to the left (as viewed in Figure 3). This results in movement to the left of the valve actuating rod 61.
  • the invention is not, of course, limited to the par- ticular construction of the pressure intensifier 13 shown in Figure 1.
  • reciprocation of the piston for example, reciprocation of the piston

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Abstract

Un dispositif d'actionnement de vanne rotatif ou lineaire comprend un cylindre (1), un piston (6, 7) mobile dans un cylindre (1), un organe d'actionnement de vanne (9) actionne par le piston (6, 7) et des moyens d'alimentation en fluide sous pression, par exemple un fluide hydraulique, du cylindre (1) pour deplacer le piston (6, 7) dans le cylindre. Les moyens d'alimentation en fluide sous pression comprennent un dispositif d'intensification de pression (13) entraine par un milieu sous pression, par exemple de l'air comprime a une premiere pression et concus pour envoyer ce fluide sous pression au cylindre (1) du dispositif d'actionnement a une pression superieure a celle du milieu sous pression. Le dispositif d'intensification de pression (13) comprend de maniere appropriee un premier assemblage a piston et cylindre a double effet ayant un premier piston (7) qui est connecte mecaniquement a un second piston (16) d'un second assemblage a piston cylindre a double effet, le second piston (16) ayant une section plus petite que la section du premier piston (17) et les cylindres (15, 14) des deux assemblages a piston et cylindre ont leurs axes alignes, et des moyens (34-38) pour l'alimentation en milieu sous pression a cette premiere pression du premier assemblage a piston et cylindre dans le but d'animer d'un mouvement alternatif le premier piston (17) dans son cylindre (15). Le second assemblage a piston et cylindre constitue alors les moyens d'alimentation en fluide sous pression a la pression plus elevee du cylindre d'actionnement (1).
PCT/GB1982/000004 1981-01-12 1982-01-11 Dispositif d'actionnement de vanne WO1982002423A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8100799 1981-01-12
GB8100799810112 1981-01-12

Publications (1)

Publication Number Publication Date
WO1982002423A1 true WO1982002423A1 (fr) 1982-07-22

Family

ID=10518926

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1982/000004 WO1982002423A1 (fr) 1981-01-12 1982-01-11 Dispositif d'actionnement de vanne

Country Status (3)

Country Link
EP (1) EP0069128A1 (fr)
AU (1) AU7939982A (fr)
WO (1) WO1982002423A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992008375A1 (fr) * 1990-11-19 1992-05-29 Real Foods Pty. Ltd. Appareil de cuisson
WO1995022026A1 (fr) * 1994-02-10 1995-08-17 Abb Research Ltd Arrangement relatif a un actuateur de soupape
WO2006066521A1 (fr) * 2004-12-20 2006-06-29 Bosch Rexroth Ag Entrainement lineaire a convertisseur de force
DE102010063487A1 (de) * 2010-12-20 2012-06-21 Zf Friedrichshafen Ag Vorrichtung zur Betätigung eines Arbeitszylinders
EP3470687A1 (fr) * 2017-10-12 2019-04-17 Nova Werke AG Actionneur de soupape pneumatique

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1269305A (fr) * 1960-06-25 1961-08-11 Frank & Pignard Dispositif de commande hydro-pneumatique à double effet, à rétablissement et compensation automatiques des volumes hydrauliques
GB939951A (en) * 1960-04-21 1963-10-16 Conrad Roy Bates Improvements relating to booster-assisted hydraulic systems
US3405522A (en) * 1964-11-25 1968-10-15 Toyoda Machine Works Ltd Hydraulic motor control circuit
FR2041511A5 (fr) * 1969-04-28 1971-01-29 Viaud Jean
US3570101A (en) * 1968-07-01 1971-03-16 Skyhi Ltd Hydraulic and pneumatic system for controlling tools
US4043533A (en) * 1975-08-14 1977-08-23 Atwood & Morrill Co. Auxiliary closing force for valves

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB939951A (en) * 1960-04-21 1963-10-16 Conrad Roy Bates Improvements relating to booster-assisted hydraulic systems
FR1269305A (fr) * 1960-06-25 1961-08-11 Frank & Pignard Dispositif de commande hydro-pneumatique à double effet, à rétablissement et compensation automatiques des volumes hydrauliques
US3405522A (en) * 1964-11-25 1968-10-15 Toyoda Machine Works Ltd Hydraulic motor control circuit
US3570101A (en) * 1968-07-01 1971-03-16 Skyhi Ltd Hydraulic and pneumatic system for controlling tools
FR2041511A5 (fr) * 1969-04-28 1971-01-29 Viaud Jean
US4043533A (en) * 1975-08-14 1977-08-23 Atwood & Morrill Co. Auxiliary closing force for valves

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992008375A1 (fr) * 1990-11-19 1992-05-29 Real Foods Pty. Ltd. Appareil de cuisson
WO1995022026A1 (fr) * 1994-02-10 1995-08-17 Abb Research Ltd Arrangement relatif a un actuateur de soupape
US5992819A (en) * 1994-02-10 1999-11-30 Abb Research Ltd. Arrangement in a valve actuator
WO2006066521A1 (fr) * 2004-12-20 2006-06-29 Bosch Rexroth Ag Entrainement lineaire a convertisseur de force
DE102010063487A1 (de) * 2010-12-20 2012-06-21 Zf Friedrichshafen Ag Vorrichtung zur Betätigung eines Arbeitszylinders
EP3470687A1 (fr) * 2017-10-12 2019-04-17 Nova Werke AG Actionneur de soupape pneumatique

Also Published As

Publication number Publication date
EP0069128A1 (fr) 1983-01-12
AU7939982A (en) 1982-08-02

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