EP0061786B1 - Commande hydraulique ou pneumatique - Google Patents

Commande hydraulique ou pneumatique Download PDF

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Publication number
EP0061786B1
EP0061786B1 EP19820200143 EP82200143A EP0061786B1 EP 0061786 B1 EP0061786 B1 EP 0061786B1 EP 19820200143 EP19820200143 EP 19820200143 EP 82200143 A EP82200143 A EP 82200143A EP 0061786 B1 EP0061786 B1 EP 0061786B1
Authority
EP
European Patent Office
Prior art keywords
valve
space
piston
control member
drive system
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
EP19820200143
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German (de)
English (en)
Other versions
EP0061786B2 (fr
EP0061786A1 (fr
Inventor
Walter Bischofberger
Gerhard Mauthe
Gerhard Körner
Joachim Nasterlack
Horst Plettner
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.)
BBC Brown Boveri AG Switzerland
Original Assignee
BBC Brown Boveri AG Switzerland
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
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Application filed by BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Publication of EP0061786A1 publication Critical patent/EP0061786A1/fr
Application granted granted Critical
Publication of EP0061786B1 publication Critical patent/EP0061786B1/fr
Publication of EP0061786B2 publication Critical patent/EP0061786B2/fr
Expired legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators

Definitions

  • the invention relates to a hydraulic or pneumatic drive according to the preamble of claim 1.
  • Such a drive is known from CH-A-539 784.
  • this drive is preferably suitable for actuating the contact arrangement of a high-voltage circuit breaker, the switch being held in the switched-on position by pressurizing the space located above the larger piston surface of the differential piston with fluid under pressure via a piston rod connected to the differential piston.
  • the changeover valve is reversed so that the space above the larger piston area of the differential piston comes into contact with the low-pressure container.
  • the pressure in the space above the larger piston area is suddenly reduced, so the constant pressure of the fluid in the space above the smaller piston area brings the piston together with the piston rod and the movable part of the contact arrangement of the switch into the switch-off position.
  • the drive according to the invention can be produced in an extremely cost-effective manner, since instead of an expensive changeover valve with a large valve cross section, it only requires two inexpensive controllable valves with a comparatively small cross section. Furthermore, the booster valve stages required to control a valve with a large valve cross section can be saved, as a result of which not only the manufacturing costs of the drive but also its response times between the issuing of the control command and the start of the drive piston are reduced. Since the further controllable valve acts like a bypass, the fluid can flow very quickly into the low-pressure container when the pressure is released from the space above the larger piston surface, so that the drive movement and thus a switching operation can take place correspondingly quickly.
  • a particularly inexpensive embodiment of the drive according to the invention is achieved in that the further controllable valve is designed as a check valve which can be controlled together with the changeover valve, since a solid check valve is of simple construction and the control of both valves can be effected with simple means.
  • the switch-on or switch-off valves which initiate the start of the drive can be dimensioned particularly small if the switch-over valve can be activated before the further controllable valve.
  • a high-voltage circuit breaker designated 10 in FIG. 1 is actuated via a piston rod 12 of a piston-cylinder arrangement 14. Inside the piston-cylinder arrangement 14 there is a piston 16 which divides the cylinder space 18 into two spaces 20 and 22. The space 20 is penetrated by the piston rod 12 and is located above the smaller area of the piston 16, whereas the space 22 covers the dimension of the entire area of the piston. As a result, the piston 16 acts as a differential piston.
  • the space 20 above the smaller piston surface is connected to a hydraulic high-pressure accumulator 24 via a line 26 to which a further line 28 is connected, which on the one hand is connected to an input 30 of a three-way valve 32.
  • the outlet 34 of the valve 32 is connected via a line 36 to the space 22 above the larger piston area.
  • the second outlet 38 of the valve 32 is connected to a low-pressure container 46 via a line 40, 42 and 44.
  • the line 28 continues via a line 48 to a pump 50 which is driven by a motor 52.
  • the input of the pump is connected to the low-pressure container 46 via a filter 54.
  • the inlet 58 of a controllable check valve 56 is connected to the line 36; the outlet 60 of this check valve is connected to the low pressure line 40 and thus via the lines 42 and 44 to the low pressure container.
  • the check valve 56 is activated simultaneously with the changeover valve 32.
  • valve 32 As a result, a kind of bypass to the valve 32 is formed via the check valve 56, so that the outflow cross sections in the valve 32 can be significantly reduced compared to a solution without the controlled check valve 56. The fluid then no longer flows through the valve 32 to the low-pressure container alone, but rather via the valve 32 and the check valve 56.
  • FIGS. 2-4 show embodiments of the drive according to the invention in which the further controllable valve is activated with a delay compared to the changeover valve.
  • the switch-on position is shown on the left side of each figure, the switch-off position of the drive is shown on the right side.
  • control member of the changeover valve 32 is designated.
  • 37 is a branching point in a connecting line 39 and 63 between the control member 33 and inputs 65, 67 of switch-off valves 66 and 68 which can be actuated by the electromagnet 56.
  • a switch-on valve is designated by 64.
  • This drive now acts as follows: When switching off, at least one of the switch-off valves 66, 68 is first actuated. As a result, the high fluid pressure in the line 63, 39 in the switch-on position (cf. the left half of FIG. 2) and thus also in a pressure relief chamber of the control member 33 is reduced.
  • the changeover valve 32 is switched due to a differential effect of the control member 33, which is not explained in detail, and the fluid in the space 22, which is under high pressure, begins to flow out via the line 36, the valve 32 and the lines 40, 42 and 44 into the low-pressure container 46.
  • the space 22 is now relieved of pressure and the differential piston 16 is accelerated out of the idle state together with the piston rod 12 and the part of the contact arrangement of the switch attached to it.
  • the piston 16 displaces increasing liquid volumes from the space 22 with increasing speed per unit of time.
  • fluid is also removed from the space 22 via the further controllable valve 56.
  • the control element 57 which acts as a differential piston, switches the valve 56, and the fluid in the space 22 can now - in the manner mentioned above - also flow out into the low-pressure container 48 via the valve 56 and the lines 42 and 44.
  • the time delay when the further controllable valve is actuated is brought about by the fact that the control member 57 of this valve is connected to the space 22. If the shut-off valves 66 and 68 are actuated, the control member 33 of the changeover valve 32 is first reversed via the lines 63 and 39 and the space 22 is relieved of pressure after the valve 32 has been switched over via the line 36, the valve 32 and the lines 42 and 44. Now the pressure relief chamber of the control member 57 of the valve 56 is relieved and the valve 56 is reversed.
  • a particular advantage of this arrangement is that the fluid of the pressure relief chamber of the control member 57 does not flow out via the shut-off valves 66, 68 but via the line 36, the reversing valve 32 and the lines 42, 44, and that through the connection of the space 22 and Pressure relief chamber of the control member 57, the delay between the switch-off command and the response of the further controllable valve is practically so dimensioned that this valve responds precisely when the piston begins to move.
  • the embodiment according to FIG. 4 effects the delayed activation of the further controllable valve 56 via a device 70 which generates a signal indicating the position of the differential piston 16.
  • This signal is preferably given by an electrical or mechanical means to a control element 57 which responds to this signal.
  • This embodiment has the advantage that the further controllable valve is particularly inexpensive because of the mechanically or electrically actuable control member.

Landscapes

  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)

Claims (6)

1. Mécanisme d'entraînement hydraulique ou pneumatique, en particulier pour des appareils de commutation électriques, comportant un piston différentiel (16) guidé dans un cylindre (18) et une valve inverseuse (32) par l'intermédiaire de laquelle du fluide sous pression est introduit dans l'espace (22) situé au-dessus de la grande face du piston et par l'intermédiaire de laquelle le fluide contenu dans cet espace (22) peut être relâché vers un récipient à basse pression (46), caractérisé en ce qu'au moins une autre valve (56) pouvant être commandée est prévue, est raccordée par son entrée (58) à l'espace (22) situé au-dessus de la grande face du piston et par sa sortie (60) au récipient à basse pression (46) et peut être commandée d'une manière telle qu'elle libère pour le fluide le trajet allant de l'espace (22) situé au-dessus de la grande face du piston au récipient à basse pression (46) en même temps que la valve inverseuse (32) ou avec un certain retard par rapport à celle-ci.
2. Mécanisme d'entraînement suivant la revendication 1, caractérisé en ce qu'à titre d'autre valve (56) pouvant être commandée est prévue au moins une valve de retenue pouvant être commandée en même temps que la valve inverseuse (32).
3. Mécanisme d'entraînement suivant la revendication 1, caractérisé en ce que l'autre valve (56) pouvant être commandée est actionnée avec un certain retard par rapport à la valve inverseuse (32).
4. Mécanisme d'entraînement suivant la revendication 3, caractérisé en ce qu'un étrangleur (62) est prévu entre un organe de commande (57) de l'autre valve (56) pouvant être commandée et un point de dérivation dans une conduite de liaison (39, 63) entre un organe de commande (33) de la valve inverseuse (32) et une entrée (65, 67) d'au moins une valve de déclenchement (66, 68).
5. Mécanisme d'entraînement suivant la revendication 4, caractérisé en ce qu'un organe de commande (57) de l'autre valve (56) pouvant être commandée est en communication avec l'espace (22) prévu au-dessus de la grande face du piston.
6. Mécanisme d'entraînement suivant la revendication 5, caractérisé en ce que l'autre valve (56) pouvant être commandée présente un organe de commande (57) qui peut être actionné par un signal indiquant la position du piston différentiel (16).
EP19820200143 1981-03-26 1982-02-08 Commande hydraulique ou pneumatique Expired EP0061786B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH204781 1981-03-26
CH2047/81 1981-03-26

Publications (3)

Publication Number Publication Date
EP0061786A1 EP0061786A1 (fr) 1982-10-06
EP0061786B1 true EP0061786B1 (fr) 1985-05-15
EP0061786B2 EP0061786B2 (fr) 1989-09-06

Family

ID=4224692

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820200143 Expired EP0061786B2 (fr) 1981-03-26 1982-02-08 Commande hydraulique ou pneumatique

Country Status (2)

Country Link
EP (1) EP0061786B2 (fr)
DE (1) DE3263469D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3612827A1 (de) * 1986-04-16 1987-10-22 Bbc Brown Boveri & Cie Hydraulischer antrieb fuer ein elektrisches schaltgeraet

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3915107A1 (de) * 1989-05-09 1990-11-22 Asea Brown Boveri Hydraulischer antrieb
DE4227562A1 (de) * 1992-08-20 1994-02-24 Abb Patent Gmbh Verfahren zum Steuern eines Hydraulikantriebes
DE4340533C2 (de) * 1993-11-29 1998-02-19 Abb Patent Gmbh Hydraulikeinrichtung zur Betätigung eines Antriebskolbens für ein bewegliches Bauteil
RU2147385C1 (ru) * 1998-02-13 2000-04-10 Акционерное общество открытого типа "Научно-исследовательский, проектно-конструкторский институт высоковольтного аппаратостроения" Гидромеханический привод элегазового выключателя
RU2141146C1 (ru) * 1998-04-23 1999-11-10 Российский Федеральный Ядерный Центр - Всероссийский Научно-Исследовательский Институт Экспериментальной Физики Способ контроля и управления гидроприводом
DE10345788A1 (de) * 2003-10-02 2005-04-21 Bayer Materialscience Ag Wässrige Beschichtungsmittel für Can Coating
DE102011106584A1 (de) * 2011-06-16 2012-12-20 Voith Patent Gmbh Vorrichtung zur hydraulischen Betätigung eines Absperrorgans
EP2933816B1 (fr) 2014-04-16 2018-06-13 ABB Schweiz AG Soupape hydraulique destinée à éviter les fuites dans un mécanisme de commande d'un commutateur de puissance à moyenne ou haute tension

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2861144A (en) * 1957-07-08 1958-11-18 Gen Electric Stored energy type closing device for an electric circuit breaker
FR1181089A (fr) * 1957-08-12 1959-06-11 Perfectionnements aux circuits hydrauliques de commande
DE1690130C3 (de) * 1968-01-12 1979-02-15 Siemens Ag, 1000 Berlin U. 8000 Muenchen Hydraulischer Antrieb für elektrische Leistungsschalter
FR2308815A1 (fr) * 1975-04-23 1976-11-19 Alsthom Cgee Commande oleopneumatique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3612827A1 (de) * 1986-04-16 1987-10-22 Bbc Brown Boveri & Cie Hydraulischer antrieb fuer ein elektrisches schaltgeraet

Also Published As

Publication number Publication date
EP0061786B2 (fr) 1989-09-06
DE3263469D1 (en) 1985-06-20
EP0061786A1 (fr) 1982-10-06

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