EP0111617A1 - Dispositif opérateur actionné par fluide sous pression avec organe de verrouillage - Google Patents

Dispositif opérateur actionné par fluide sous pression avec organe de verrouillage Download PDF

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Publication number
EP0111617A1
EP0111617A1 EP83100503A EP83100503A EP0111617A1 EP 0111617 A1 EP0111617 A1 EP 0111617A1 EP 83100503 A EP83100503 A EP 83100503A EP 83100503 A EP83100503 A EP 83100503A EP 0111617 A1 EP0111617 A1 EP 0111617A1
Authority
EP
European Patent Office
Prior art keywords
pressure
locking member
movable system
chamber
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.)
Granted
Application number
EP83100503A
Other languages
German (de)
English (en)
Other versions
EP0111617B1 (fr
Inventor
Steffen Paulo Russak
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.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer 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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0111617A1 publication Critical patent/EP0111617A1/fr
Application granted granted Critical
Publication of EP0111617B1 publication Critical patent/EP0111617B1/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
    • F15B15/26—Locking mechanisms
    • F15B15/261—Locking mechanisms using positive interengagement, e.g. balls and grooves, for locking in the end positions
    • 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
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads

Definitions

  • the invention relates to a pressure medium-actuated servomotor arrangement according to the preamble of claim 1.
  • Such an actuator arrangement is known in connection with a valve, which is held in a working position by the locking member.
  • the locking member is constantly loaded by a compression spring. This makes it possible to hold the valve in the working position without maintaining a pressure difference on the piston of the servomotor, so that a continuous medium outflow along the piston sliding surface is avoided.
  • This arrangement has the disadvantage that in order to release the movable system - for example when changing from the working position to a safety position - an axial load on the movable system is necessary, for example by applying a pressure difference to the piston of the servomotor. As soon as Such higher working requirements are no longer permitted, since the servomotor arrangement must be able to move into the safety position even when there is no pressure medium to drive the servomotor or the pressure medium is depressurized.
  • the invention has for its object to improve a servomotor arrangement of the type mentioned in such a way that a transition from a working position to a safety position of the servomotor is ensured without external energy supply, the design and the circuitry complexity should remain as small as possible.
  • the locking member is no longer in the way of a transition of the movable system from a working position into a safety position. Because in the case in which the pressure chamber is connected to the pressure medium source so that the locking member holds the movable system, the pressure on the end face is reduced, be it by connecting the pressure chamber to the pressure medium sink or if pressure medium is lost or even destroyed of the pressure medium system. In the case in which the pressure chamber is connected to the pressure medium sink so that the locking member holds the movable system, the pressure in the pressure chamber is increased, namely by connecting the pressure chamber to the pressure medium source in order to remove the locking member from the To fix hold.
  • the control of the locking member by means of the closing element is very simple.
  • the locking member can be designed inexpensively and less prone to malfunction, the simultaneous use of several locking members is possible, which in turn increases the safety of the servomotor.
  • the controllability of the locking member allows it to be relieved during the transition from one position of the movable system to another position, which reduces both the energy requirement and the wear compared to the known arrangement of the locking member.
  • the invention can be implemented in a large number of embodiments, which allows an expedient adaptation to the respective needs of the servomotor arrangement.
  • the design and dimensioning of the locking member according to claim 2 prevents a necessary shifting of the movable system into a safety position by the locking member.
  • a particularly simple embodiment of the locking member is contained in claim 3, by which it is avoided that the locking member slides on a surface.
  • the design of the locking member according to claim 4 allows the movable system to be held by only a small axial load on the locking member, since the holding force is largely absorbed by the guide of the little cup.
  • Claim 9 relates to a particularly advantageous application of the servomotor arrangement according to the invention, whereby the implementation of the strictest safety requirements is made possible.
  • a special pressure medium source can usually be dispensed with, the need for an external pressure medium supply line being eliminated, which moreover offers safety-related advantages.
  • a servomotor arrangement 1 has a movable system 2, which comprises a piston 4, which is axially displaceable in a cylinder 3.
  • a cylindrical extension 5 is provided on the piston 4 on its upper side in FIG. 1, which cooperates with a locking member 10 which is accommodated in a cover 35 of the cylinder 3.
  • the locking member 10 has an end face 11 which delimits a pressure chamber 12 which is connected via a bore 13 and a pressure medium line 14 to a steam generator 16 which acts as a first pressure medium source.
  • Arranged in the bore 13 are two check valves 15 connected in series, which have a strong throttling effect when the pressure medium flows towards the pressure chamber 12 and block a pressure medium flow towards the steam generator 16.
  • a bore 17 which contains two check valves 18 connected in series and into one as second pressure medium source acting piston chamber 6 of the actuator assembly.
  • the bore 17 is connected via a cranked bore 19, which branches between the check valves 15 and 18, with the atmosphere acting as a pressure medium sink.
  • the cover 35 is attached in a gas-tight manner to an upper end face 34 of the cylinder 3 by means of screws, not shown.
  • the bore 19 is drilled from the outside, forming a valve seat 19 ', and this bore is surrounded by a threaded blind hole.
  • a connection piece 21 of a solenoid valve 20 is screwed, which forms a closure member, which is here in the connection between the pressure chamber 12 and the pressure medium sink (atmosphere).
  • the solenoid valve 20 contains a DC coil 22 and an axially displaceable part 23 1 which consists of a spindle 24, a collar 25 and an armature 26.
  • a compression spring 28, which acts on the collar 25, is supported on the bottom of the threaded blind hole.
  • the DC coil 22 is connected to a control signal line 29.
  • the servomotor arrangement 1 comprises a valve 30 which is open in the normal position, the housing of which enclosing a valve chamber 33 forms a piece together with its inlet connection 31 and its outlet connection 32 and with the cylinder 3.
  • the piston 4 has on its lower side in FIG. 1 a piston rod 7 which extends through the piston chamber 6 and a wall 8 separating this chamber from the valve chamber 33.
  • the piston rod 7 carries a closure part 40 which has a peripheral sealing surface 42 which cooperates with a valve seat 44 in the valve chamber 33.
  • the piston 4 is on its side facing away from the piston rod 7 near the circumference with a rear seat seal 36 provided, which cooperates sealingly with a counter surface on the cover 35, so that in the uppermost position of the piston 4, which corresponds to the normal operating position, a piston chamber 9 is sealed off from the piston chamber 6.
  • the piston chamber 6 and the valve chamber 33 are connected via a U-shaped bore 37 to an adjustable throttle 38 in the form of a screw.
  • the sections of the bore 37 shown in FIG. 1 in the same plane of the drawing actually run spatially, so that the throttle 38 can be adjusted from the outside.
  • the piston chamber 9 is connected to the atmosphere via a bore 48 and an adjustable throttle 49 designed as a hollow screw.
  • the bore 37 is connected to a chamber 51 in the wall of the cylinder 3 via a U-shaped bore 50, which branches off between the valve chamber 33 and the throttle 38.
  • the bore 48 is also connected to this chamber 51 via a cranked bore 50 'and 50 ".
  • the chamber 51 contains a small piston 52 which carries a support piston 57 via a conical transition piece and a cylindrical neck.
  • the piston 52 is in one cylinder chamber 53 adjoining chamber 51, which is connected via a bore 54 to the section of bore 37 leading from throttle 38 to piston chamber 6, so that there is a permanent, unthrottled connection between cylinder chamber 53 and piston chamber 6.
  • Supporting piston 57 is guided in a section of the bore 50 ′′ which is elongated upward in FIG. 1 and has a considerably smaller diameter than the cylinder space 53 and is connected to the atmosphere via a bore 56.
  • the conical transition piece on the piston 52 acts as a closure body a seat formed on the edge between the bore 50 "and the chamber 51.
  • the closure part 40 of the valve 30 is in its normal position, i.e. the valve is open and a pressure medium flows through the inlet connection 31 and the valve chamber 33 into the outlet connection 32; the valve chamber 33 is therefore under pressure.
  • the same pressure prevails in the piston chamber 6 as in the valve chamber 33, since this communicates with the piston chamber 6 via the bore 37 and the throttle 38.
  • the pressure in the piston chamber 6 also acts in the cylinder chamber 53 and thus on the piston 52.
  • the same pressure is also effective via the bore 50 in the chamber 51 and loads part of the conical transition piece of the piston 52 Piston 52 on a fictitious circular area with the diameter of the bore 50 "on the one hand the medium pressure upwards and on the other hand the atmospheric pressure downwards.
  • the compression spring 28 pushes the displaceable part 23 in FIG. 1 to the left, so that the blocking of the bore 19 is released, and pressure medium flows out of the piston chamber 6 and out of the pressure chamber 12 into the atmosphere. Since not enough pressure medium can flow from the valve chamber 33 into the piston chamber 6 because of the throttle 38, the pressure drops in the piston chamber 6 and in the cylinder chamber 53. However, since the full pressure of the pressure medium flowing through the valve 30 is still present in the chamber 51, the piston 52 is shifted downward in FIG , the chamber 51 and the bores 50 ′′, 50 ′ and 48 flow into the piston chamber 9.
  • the path from the pressure chamber 12 to the atmosphere via the bores 13, 17 and 19 is designed such that it is shorter and has less throttle resistance than the path from the piston chamber 6 to the atmosphere via the bore 17, the check valves 18 and the bore 19 the volume of the pressure chamber 12 is much smaller than that of the piston chamber 6.
  • the check valves 15 have a strong throttling effect. This ensures that when the solenoid valve 20 is opened, the locking member 10 is relieved in front of the piston chamber 6 and releases the movable system 2, thereby ensuring not only the effectiveness of the entire arrangement consisting of the servomotor 1 and valve 30, but also wear of the locking surfaces is avoided.
  • the coil 22 is energized, whereby the solenoid valve 20 closes; the reverse process then takes place compared to that described above. It is important that the pressure increase in the piston chamber 6 takes place very slowly, because during the upward movement of the piston 4 the volume of the piston chamber 6 increases continuously, so that the pressure build-up in this chamber with the aid of the pressure medium supply from the valve chamber 33 via the bore 37 to Stop of the rear seat seal 36 on the counter surface, is slowed down. On the other hand, pressure medium must be expelled from the piston chamber 9 into the atmosphere via the throttle 49, so that the pressure in the chamber 9 decreases only slightly during the piston movement until it stops.
  • valve 30 has to be kept open at a very low pressure of the pressure medium, possibly less than 1 bar, which e.g. is common in the operation of steam turbines.
  • the pressure in the housing of the valve 30 drops.
  • the pressure in the piston chamber 6, in the cylinder chamber 53 and in the chamber 51 also drops.
  • the piston 52 moves as soon as the Pressure in the cylinder chamber 53 can no longer carry it, and connects the bore 50 with the bore 50 "and 50" and 48. This connection also causes the pressure in the piston chamber 9 to decrease.
  • the coil 22 is connected to voltage via the control signal line 29.
  • the solenoid valve 20 remains closed.
  • the check valves 18 prevent the pressure in the bores 17, 19 and 13 between the pressure chamber 12 and the solenoid valve 20 from dropping to the pressure level in the piston chamber 6, so that the pressure determined by the steam generator 16 prevails in the region mentioned.
  • the locking member 10 remains as desired in the locking position as long as the solenoid valve 20 is under tension. This prevents the valve 30 from closing.
  • the holding effect of the locking member 10 remains for a certain time even in the event of a failure of the steam generator 16 thanks to the action of the check valves 15 and 18.
  • the locking member 10 is arranged in the pressure area of the piston chamber 6, it is possible to dimension the locking member 10 in dependence on the existing pressures in such a way that the piston chamber 6 only engages at low pressure , which reduces wear.
  • two pressure medium sources are shown.
  • FIG. 2 the locking member 10 is shown in FIG. 1 in the form of a membrane on an enlarged scale.
  • the membrane 410 has on the right side in FIG End face 11, which is exposed to the pressure medium in the pressure chamber 12.
  • the other side of the membrane 410 runs parallel to a braking surface 101 on the extension 5 of the movable system 2, a narrow gap separating these two surfaces from one another when the membrane is not in the locking position.
  • the membrane 410 consists of a flexible material, for example a spring steel sheet, and is tightly welded to a fixed part of the servomotor arrangement 1, but in such a way that its flexibility and the associated mobility are still sufficiently preserved.
  • the braking surface 101 is provided on an insert 102, which is fastened to the movable system 2 of the servomotor arrangement and, for example, consists of a silver-plated or nickel-plated austenitic steel sheet which has a high coefficient of friction compared to the membrane 410.
  • the pressure medium passes through the bore 13 into the pressure chamber 12.
  • the diaphragm 410 is acted upon by the pressure medium in the pressure chamber 12 and deforms in the process, so that it is pressed against the braking surface 101 and holds the movable system 2 by friction.
  • the connection to the pressure medium source interrupted and switched to a pressure medium sink, the pressure in the pressure chamber 12 drops and the membrane 410 is relaxed. Due to its own elasticity, it now resumes its original shape parallel to the braking surface 101, so that the movable system 2 is released.
  • Both a single membrane and a plurality of membranes 410 can be arranged around the extension 5. It is also possible to use a single cylindrical membrane enclosing the extension 5, which is shown in FIG the locking position the extension 5 evenly loaded on the entire circumference.
  • the example according to FIG. 3 differs from that according to FIG. 2 in that the membrane 410 has a curvature 103 which in the locking position engages in a corresponding recess 104 in the extension 5. Due to the abutment of the curvature 103 in the depression 104, forces arise which act in addition to the friction, so that a smaller pressure than in the example according to FIG. 2 is required in order to lock the movable system 2 with the same dimensions of the locking member.
  • the locking member is designed as a small cup 110.
  • the end face 11 of the cologne is tightly connected to a corrugated tube 111, so that it is slidably guided coaxially with the corrugated tube 111 in a bore in the fixed 67 part of the servomotor arrangement 1.
  • a bearing bush 112 facilitates sliding, and a plurality of ring grooves 113 in the small cup ensure peripheral pressure compensation.
  • a collar 114 of Cologne 110 limits the stroke of Cologne by striking an annular seat 115 on the fixed part.
  • the movable system 2 has a depression 104, which, with its upper section in FIG. 4, forms a shoulder 105, against which the little bolster 110 rests with a support surface 116 in its locking position.
  • a cover 117 is fastened to the fixed 67 part by screws 118, an O-ring 119 sealing this connection.
  • the corrugated tube 111 is tightly connected to the cover 117 and encloses the pressure space 12. This space is not connected to the bore 13 in the cover 117 and a three-way valve 61 forming the closing element pressure medium source (nozzle 60) and a pressure medium sink (nozzle 62), also not shown, connected.
  • Fig. 4 the Kölbchen 110 is shown in the holding position, the three-way valve 61 assumes the position shown, in which the pressure chamber 12 is connected to the pressure medium source.
  • the collar 114 is pressed onto the ring seat 115. If one rotates the three-way valve, the connection is interrupted with the pressure medium source and that via the connecting piece 62 fabricated 61 by 90 0 anticlockwise to the pressure medium sink.
  • the pressure in the pressure chamber 12 drops; and the force acting on the small basket 110 is reduced, which corresponds to the product of the pressure in the pressure chamber 12 times the size of the end face 11.
  • the force now prevails that the little boy 110 wants to push away from the recess 104, so that the little boy 110 slides in the direction of the pressure chamber 12 and thereby compresses the corrugated tube 111 and releases the movable system 2.
  • the force component which acts on the support surface 116 and which influences the displacement of the small basket 110 depends on the angle ⁇ between the direction of movement of the system 2 and the support surface 116.
  • two sealing surfaces 106 and 107 are provided on the collar 114, which interact with corresponding seats 46 and 46 ', respectively.
  • the sealing surface 106 is opened the seat 46 is pressed, which prevents pressure medium from flowing through the gap between the small piston 110 and the bearing bush 112, which could cause damage.
  • the basket 110 is in the position in which the movable system 2 is free and there is a pressure difference on the basket in the direction of the pressure chamber 12, the sealing surface 107 is pressed onto the seat 46 'and no foreign medium can enter penetrate the bore 13. Appropriate dimensioning of the effective areas on the small cap 110 depending on the pressures present is to be carried out.
  • the shoulder 105 in FIG. 5 is not part of a recess, but extends as an annular shoulder around the movable system, and the seal between the cover 117 and the fixed part consists of a captured seal 120.
  • the locking member 210 has a spherical shape, which partly delimits the pressure chamber 12 and partly - in the locking position - lies in the recess 104 of the movable system 2. This embodiment is particularly simple and inexpensive.
  • two spherical intermediate elements 70 are arranged between the small basket 310 and the movable system.
  • the claw 310 forming part of a locking member can be moved parallel to the direction of movement of the movable system 2 and has two sealing seats 72 and 73 as a stroke limitation, which cooperate with corresponding counter surfaces on the fixed part.
  • the sealing seat 72 is located to the Kölbchens 310 while the sealing seat 73 on the other end face of K is located at the end face 11 ölbchens.
  • Piston rings 74 which seal in a known manner, are accommodated in the cylindrical guide surface of the small piston 310.
  • a plurality of balls 70 are arranged as intermediate elements between the lower end face of the cilette 310 in FIG.
  • the support surface 68 which is opposite the small basket 310, has an inclination ⁇ with respect to the direction of displacement of the system-2. The magnitude of the inclination depends on the pressure of the pressure medium and on the position of the point of attack 75 with which the movable system 2 is supported on the balls 70 when fully engaged.
  • the support surface 68 has an edge 69 surrounding the movable system 2, which prevents the balls 7.0 from falling out when the system 2 is extended.
  • the embodiment according to FIG. 7 includes a closing element, a pressure medium source and a pressure medium sink, all of which are not shown in FIG. 7. This also includes a sealing element (not shown) between the cover 66 and the fixed part 67. The pressure medium passes through the bore 13 in the cover 66 into the pressure chamber 12.
  • the movable system 2 loads the balls 70 by means of the shoulder 105 in the annular groove 108, specifically in the direction from the pressure chamber 12 towards the balls 70.
  • the balls 70 absorb the load on the point of attack 75 and transfer a part thereof to the support surface 68.
  • This surface breaks down the force exerted on them into two comes Components: A force component perpendicular to the support surface 68, which acts as the cause of a frictional force, and a force component parallel to the support surface 68, which - contrary to the frictional force - tries to remove the balls 70 from the movable system 2.
  • the balls 70 are prevented from moving by the small piston 310, which is held in place by the pressure medium which acts on the end face 11 in the pressure chamber 12.
  • the cologne 310 lies sealingly on the associated one by means of the sealing seat 73. Counter surface, whereby escape of pressure medium is avoided.
  • the locking is released by connecting the pressure chamber 12 to the pressure medium sink by adjusting the closing element (not shown), as a result of which the pressure on the cologne is relieved and moved upwards by the balls 70. If the pressure in the vicinity of the balls 70 exceeds that in the pressure chamber 12, the sealing seat 72 and its counter surface prevent pressure medium from flowing out via the pressure chamber 12 into the bore 13.
  • balls 70 are shown as intermediate members. However, other shaped parts can be used that slide in a predictable direction by applying force at a particular location, such as e.g. is the case with locking mechanisms. The use of angle levers is also conceivable.
  • the contact between the cobs and the shoulder can be point-shaped, linear or flat, depending on the design of the contact surfaces. This allows the size of the surface pressure to be varied within wide limits at this point, depending on the existing pressures, materials and friction coefficients.
  • the restoring force which pushes the little boy back out of the engagement position is brought about by the movable system 2 itself, which acts on the oblique contact surface 116 or the supporting surface 68 via the shoulder 105.
  • at least one spring e.g. made of steel, move back.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Braking Systems And Boosters (AREA)
  • Control Of Fluid Pressure (AREA)
  • Fluid-Driven Valves (AREA)
  • Safety Valves (AREA)
EP83100503A 1982-12-15 1983-01-21 Dispositif opérateur actionné par fluide sous pression avec organe de verrouillage Expired EP0111617B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH7288/82A CH659111A5 (de) 1982-12-15 1982-12-15 Druckmittelbetaetigte stellmotoranordnung mit arretierglied.
CH7288/82 1982-12-15

Publications (2)

Publication Number Publication Date
EP0111617A1 true EP0111617A1 (fr) 1984-06-27
EP0111617B1 EP0111617B1 (fr) 1987-12-09

Family

ID=4322786

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83100503A Expired EP0111617B1 (fr) 1982-12-15 1983-01-21 Dispositif opérateur actionné par fluide sous pression avec organe de verrouillage

Country Status (7)

Country Link
US (1) US4700925A (fr)
EP (1) EP0111617B1 (fr)
JP (1) JPS59131080A (fr)
CA (1) CA1221283A (fr)
CH (1) CH659111A5 (fr)
DE (1) DE3374891D1 (fr)
ES (1) ES527633A0 (fr)

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US5024335A (en) * 1988-11-30 1991-06-18 Lundell Vernon J Automatic sorter
KR910003292A (ko) * 1989-07-27 1991-02-27 박원희 공압실린더의 피스턴 시일장치
DE4116429A1 (de) * 1991-05-18 1992-11-19 Vse Vakuumtechn Gmbh Schnell oeffnendes oder schliessendes ventil
DE19841631C2 (de) * 1998-09-11 2002-02-28 Daimler Chrysler Ag Pneumatischer Linearantrieb für kryogene Steuerventile
US7669830B2 (en) * 2006-10-25 2010-03-02 Honeywell International Inc. Three position shutoff valve
WO2018130649A1 (fr) * 2017-01-12 2018-07-19 Minimax Gmbh & Co. Kg Soupape à pression constante, et station de soupape d'alarme et système de gicleur
CN112524323B (zh) * 2020-12-12 2023-06-09 广东三竺新能源有限公司 一种手工锁定的电磁燃气阀

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DE1808573A1 (de) * 1968-11-13 1970-06-04 Lothar Seer Selbsthemmende Zylindereinheit
US3523675A (en) * 1967-12-18 1970-08-11 M & J Valve Co Valve operating apparatus with locking means
DE2152809A1 (de) * 1970-10-27 1972-05-04 Hoerbiger Ventilwerke Ag, Wien Pneumatischer oder hydraulischer Stellzylinder mit einer Einrichtung zur mechanischen Verriegelung seines Stellkolbens
DE3105203A1 (de) * 1981-02-13 1982-09-09 Robert Bosch Gmbh, 7000 Stuttgart Wegeventil fuer hydraulische anlagen

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Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1520585A (fr) * 1967-02-27 1968-04-12 Financ Et Ind Des Ateliers Et Perfectionnements apportés à la commande, par servo-moteur, d'appareils tels que vannes et soupapes
US3523675A (en) * 1967-12-18 1970-08-11 M & J Valve Co Valve operating apparatus with locking means
DE1808573A1 (de) * 1968-11-13 1970-06-04 Lothar Seer Selbsthemmende Zylindereinheit
DE2152809A1 (de) * 1970-10-27 1972-05-04 Hoerbiger Ventilwerke Ag, Wien Pneumatischer oder hydraulischer Stellzylinder mit einer Einrichtung zur mechanischen Verriegelung seines Stellkolbens
DE3105203A1 (de) * 1981-02-13 1982-09-09 Robert Bosch Gmbh, 7000 Stuttgart Wegeventil fuer hydraulische anlagen

Also Published As

Publication number Publication date
ES8501071A1 (es) 1984-11-16
EP0111617B1 (fr) 1987-12-09
CH659111A5 (de) 1986-12-31
DE3374891D1 (en) 1988-01-21
CA1221283A (fr) 1987-05-05
JPS59131080A (ja) 1984-07-27
ES527633A0 (es) 1984-11-16
US4700925A (en) 1987-10-20

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