EP0074419B1 - Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique - Google Patents

Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique Download PDF

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Publication number
EP0074419B1
EP0074419B1 EP81107195A EP81107195A EP0074419B1 EP 0074419 B1 EP0074419 B1 EP 0074419B1 EP 81107195 A EP81107195 A EP 81107195A EP 81107195 A EP81107195 A EP 81107195A EP 0074419 B1 EP0074419 B1 EP 0074419B1
Authority
EP
European Patent Office
Prior art keywords
valve body
valve
pressure
extension
biased
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
EP81107195A
Other languages
German (de)
English (en)
Other versions
EP0074419A1 (fr
Inventor
Rudolf Brunner
Siegfried Zenker
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority to EP81107195A priority Critical patent/EP0074419B1/fr
Priority to DE8181107195T priority patent/DE3173448D1/de
Priority to AT81107195T priority patent/ATE17413T1/de
Publication of EP0074419A1 publication Critical patent/EP0074419A1/fr
Application granted granted Critical
Publication of EP0074419B1 publication Critical patent/EP0074419B1/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
    • 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
    • H01H2033/308—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator comprising control and pilot valves

Definitions

  • the invention relates to an electrical high-performance switch of the type specified in the preamble of patent claim 1 or independent patent claim 2.
  • Such high-performance switches are subject to extraordinary requirements when they are opened.
  • the opening process must take a few msec. be completely closed, since if the opening movement is slow, the applied electrical power could destroy the switch or cause an explosion.
  • Another important criterion in the design of such switches and their hydraulic actuating device is the requirement that the switch must remain in the position in which it was previously if the hydraulic supply fails or if the hydraulic pressure supply is started up again after a failure.
  • the piston-like lugs are formed in the seat valve at both ends of the valve body with different diameters and differently sized contact surfaces.
  • the area of application of the approach projecting into one control chamber is smaller than the area of application of the other approach projecting into the other control chamber.
  • the latter control chamber is then connected to the high-pressure source via a pressure-pilot-operated auxiliary valve when the valve body is to be moved into its second blocking position. So that the pressure at the first attachment can overcome the back pressure from the second attachment in order to move the valve body into the first blocking position, the control chamber into which the second attachment protrudes must be connected via the auxiliary valve.
  • the hydraulic control of the seat valve is extremely complex in terms of construction, since a large number of different auxiliary valves, which are dependent on the movement of the differential piston drive on the one hand or by switching magnets on the other hand can be controlled, is required.
  • the complex structure of the control device is not only expensive, but also entails the risk that the correct opening and closing of the switch can be called into question even in the event of a minor error due to the many movable elements and sealing points.
  • the differential piston drive is complex due to its pilot control task for the poppet valve. Delays in the signal transmission path cannot be avoided, especially when the switch is opened, so that the opening time that can actually be achieved is not sufficiently short.
  • the valve body and the bore in the housing of the seat valve are difficult to manufacture.
  • the invention has for its object to provide a high-performance switch of the type mentioned, which is as simple as possible in its construction and which opens practically without delay when the corresponding signal occurs.
  • the further sealing and guiding section of the valve body has a pressure compensation effect for the valve body, so that the valve body is axially relieved in each blocking position.
  • the actuating forces for moving the valve body between the two locking positions are generated exclusively by the application of the two approaches. Since the one control chamber into which the approach with the smaller contact surface projects is constantly connected to the high-pressure source, only the other control chamber needs to be monitored by the control valves, although two auxiliary control valves are sufficient, which are then actuated alternately.
  • the solution according to claim 2 is also structurally very simple, because the displacement movement of the valve body is in turn only controlled by the application of the two approaches, which have the same diameter.
  • the further guiding and sealing section of the valve body not only separates the working part of the housing bore from the control chamber responsible for opening the switch, but also forms the difference area which is necessary to push the valve body back into the position in which the high-performance switch is closed .
  • the valve body can be designed completely symmetrically in a simple manner and the housing bore also has a shape that is simple in terms of production technology.
  • a further expedient embodiment finally specifies claim 9.
  • the mechanical locking device has the task of avoiding an automatic movement of the valve body under the influence of impacts against the valve housing or vibrations in the event of a pressure failure.
  • the latching device is only designed to be so strong that its force is overcome immediately, even if the valve body or the lugs are subjected to weak hydraulic loads.
  • FIG. 1 shows a hydraulic actuating device for an electrical high-performance switch 2 (indicated by dashed lines).
  • the high-performance switch 2 is actuated by a hydraulic differential piston drive 3, which has a cylinder chamber 4 with a large loading cross section and a cylinder chamber 5 with a smaller loading cross section.
  • a piston rod 6 leads from the cylinder chamber 5 to the high-performance switch 2.
  • the cylinder chamber 5 is connected via a line 7a to a hydraulic main pressure supply line 7, which is fed from a high pressure pump 38.
  • a pressure accumulator 39 is also connected to the high-pressure supply line 7.
  • a line 7b branches off to a 2 / 3 -way seat valve 1 a, the housing of which is designated 40 and has three connections P, A, R.
  • Line 7b leads to port P (pressure port).
  • a further line 7c branches off from line 7, in which a first auxiliary control valve 8 and a second auxiliary control valve 9 are arranged.
  • the line 7c leads behind the auxiliary control valves 8, 9 to the connection R (return).
  • the auxiliary control valves 8 and 9 are magnetically actuated two-position valves in this embodiment, which are in their blocking position when the magnets are not energized.
  • a line 10 leads from the cylinder chamber 4 to the connection A, while the connection R is connected via a line 11 to the return line (connection R).
  • a longitudinally continuous housing bore 41 with a constant diameter D is provided, in which a valve body 46 can be moved back and forth between two blocking positions 1 and II.
  • valve seats 42 and 43 of the same size are formed, which face the sealing surfaces 44 and 45 on the valve body 46.
  • the sealing surfaces 44 and 45 are arranged on guide and sealing sections 47, 48 which have the same diameter D as the valve seats 42 and 43.
  • the housing bore 41 is provided at both ends with extending blind bores 41 a and 41 b, of which the blind bore 41 a has a diameter d2 and the blind bore 41 b has a diameter d1.
  • the cross-sectional areas of the valve seats 42 and 43 are approximately in a ratio of 1: 4: 10 to the cross-sectional areas of the blind bores 41 a and 41 b.
  • the parts of the housing bore 41 remaining behind the two guide and sealing sections 47 and 48 are relieved of pressure by relief lines 49.
  • An auxiliary piston 50 is displaceably immersed in the blind bore 41, while an auxiliary piston 51 is immersed in the blind bore 41b, so that control chambers 52, 53 are formed.
  • the control chamber 53 is continuously connected to the line 7.
  • the control chamber 52 is connected via a line 55 to the line section between the auxiliary control valves 8 and 9 and is simultaneously acted upon via line 29 and the throttle 30 with the pressure prevailing in the housing bore 41.
  • valve body 46 This pressure also prevails in the control chambers 52, 53.
  • the auxiliary piston 50 holds the valve body 46 in this position. Since the valve seat 42 is the same size as the guide and sealing section 48, the valve body 46 is axially pressure-balanced per se. The sealing surface 41 lies against the valve seat 42 and separates the connections A, P from the return connection (connection R). The pressure is held. The valve body 46 is in the blocking position I.
  • the auxiliary control valve 9 When the high-performance switch 2 is to be opened, the auxiliary control valve 9 is actuated, so that the control chamber 52 is suddenly relieved via the line 55 into the return R '.
  • the hydraulic volume to be displaced is relatively small.
  • the force of the auxiliary piston 51 predominates and pushes the valve body 46 to the left into its second blocking position 11.
  • the sealing surface 45 comes to rest on the valve seat 43 and separates the connection A from the connection P.
  • the sealing surface 44 is lifted off the valve seat 42 and the connection A is connected to the connection R.
  • the cylinder chamber 4 is suddenly relieved via the line 10, so that the pressure in the cylinder chamber 5 shifts the piston 3 to the left and opens the high-performance switch 2.
  • the control chamber 52 is pressurized via line 55 with the pressure from the pressure source 38, 39, so that the auxiliary piston 50, which is larger in cross section, acts on the smaller auxiliary piston 51 at all times Overcomes force and brings the valve body 46 into the position shown in FIG. 1.
  • the valve body 46 remains in the position in which it was previously. In the blocking position I it is held by the greater force of the auxiliary piston 50, while in the blocking position 11 it is held solely by the force of the smaller auxiliary piston 51.
  • Fig. 2 shows another embodiment of a hydraulic actuating device for a switch, not shown, in which the / 3 -way valve seat can be produced particularly easily 1b with its housing 60 and mounted 2.
  • a housing bore 61 is provided, which is composed of a central section 61 b with the diameter D1 and two end sections 61 a with the respective diameter D2.
  • the diameter of the left end section 61a has no influence on the function of the valve and could also be selected differently.
  • a valve body 62 has two axially spaced guide and sealing sections 63 and 64 which carry sealing surfaces 67 and 68 which cooperate with valve seats 66 and 65.
  • a peg-like extension 69 is arranged on each sealing surface 67 and 68, the outside diameter of which corresponds approximately to the diameter D1 of the valve seats 65, 66 and the axial length of which corresponds approximately to half the possible working stroke of the valve body.
  • the housing bore 61 extending blind holes 61 c each with the same diameter d extend in the housing 60 and form there control chambers 71 and 72, in which auxiliary pistons 70 with the same diameter d are guided displaceably and sealed.
  • the control chamber 72 is in turn directly connected to the pressure source via the line 54, so that it is constantly under pressure.
  • a locking member 73 which is under the force of a spring 75.
  • the locking member locks the valve body 62 in its two locking positions I and II, provided that no hydraulic pressure is applied.
  • This latching device is intended, above all, to prevent forces acting mechanically on the 2 / 3 -way seat valve 1 b from unintentionally displacing the valve body 62.
  • the valve body 62 here cooperates with the valve seats 65, 66 with a positive overlap, i.e.
  • the extensions 69 each ensure that the connection P is only connected to the connection A when the connection R is largely separated from the connection A by the extension 69 being immersed. This measure prevents an excessive amount of hydraulic fluid from getting into the return when switching over.
  • the auxiliary control valve 9 If, in the position shown in FIG. 2, the auxiliary control valve 9 is switched to its through position, the control chamber 71 is relieved, so that the holding force of the auxiliary piston 70 is eliminated and the second auxiliary piston 70 in the pressure chamber 72 moves the valve body 62 to the left with its force until the sealing surface 68 abuts the valve seat 65. To do this, however, it is necessary that the cross section of the auxiliary piston 70 is larger than the difference area between the diameters D1 and D2 on which the pressure in the port P rests. So that the valve body can then be pushed back into its blocking position I, the control chamber 71 must be pressurized again so that the forces of the two auxiliary pistons 70 cancel each other out.
  • auxiliary control valves could be connected in parallel to the one control chamber, so that the high-performance switch can be opened with another in the event of failure of one auxiliary control valve.

Landscapes

  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Multiple-Way Valves (AREA)

Claims (9)

1. Disjoncteur à haut pouvoir de coupure (2), doté d'un entraînement hydraulique par piston différentiel (3) sollicité en permanence, dans le sens d'ouverture du disjoncteur, par une source haute pression (38, 39), et alternativement dans le sens de fermeture par une soupape à siège 2/3 voies (1a), d'un corps de soupape (46) animé d'un mouvement de va-et-vient dans un alésage de la cage de soupape, entre une première position d'arrêt (I), pour laquelle l'entraînement par piston différentiel (3) est sollicité dans le sens de fermeture, et une seconde position d'arrêt (II), pour laquelle l'entraînement précité (3) est sollicité dans le sens d'ouverture, le corps (46) présentant deux faces de joint (44, 45) distantes l'une de l'autre et s'appliquant alternativement sur l'un des deux sièges de soupape (42, 43) de même diamètre, prévus entre un raccordement (A) relié à l'antraînement par piston différentiel (3), un retour (R) et un raccordement de pression (P), d'un premier et d'un second prolongements en forme de piston (50, 51), disposés aux deux extrémités du corps de soupape (46) et pénétrant respectivement dans deux compartiments pilotes (52, 53), de deux vannes-pilotes auxiliaires (8, 9), actionnées alternativement et assurant le déplacement du corps de soupape (46) entre ses deux positions d'arrêt (I, Il), ainsi que d'une section de giudage et d'étanchéité au moins (47) prévue sur le corps de soupape (46), la section précitée s'étendant entre la face de joint (44) d'une part, combinée au siège de soupape (42) compris entre le retour (R) et le raccordement (A), et le premier prolongement (50) d'autre part, la section (47) présentant par ailleurs un guidage étanche dans l'alésage de la cage, caractérisé en ce que le compartiment pilote (53), qui reçoit le second prolongement (51), est raccordé directement et en permanence à la source haute pression (38, 39), en ce que les deux vannes-pilotes auxiliaires (8, 9) sont affectées à l'autre compartiment (52), en ce que le corps de soupape (46) présente, sur son extrémité correspondant au raccordement de pression (P), une autre section de guidage et d'étanchéité (48), dont le diamètre (D) est égal à celui des sièges de soupape (42, 43), et en ce que la surface de sollicitation du deuxième prolongement (51) est inférieure à celle du premier (50).
2. Disjoncteur à haut pouvoir de coupure (2), doté d'un entraînement hydraulique par piston différentiel (3) sollicité en permanence, dans le sens d'ouverture du disjoncteur, par une source haute pression (38, 39), et alternativement dans le sens de fermeture par une soupape à siège 2/3 voies (1 b), d'un corps de soupape (62) animé d'un mouvement de va-et-vient dans un alésage de la cage de soupape, entre une premiène position d'arrêt (I), pour laquelle l'entraînement par piston différentiel (3) est sollicité dans le sens de fermeture, et une seconde position d'arrêt (11), pour laquelle l'entraînement précité (3) est sollicité dans le sens d'ouverture, le corps (62) présentant deux faces de joint (67, 68) distantes l'une de l'autre et s'appliquant alternativement sur l'un des deux sièges de soupape (66, 65) de même diamètre, prévus entre un raccordement (A) relié à l'entraînement par piston différentiel (3), un retour (R) et un raccordement de pression (P), d'un premier et d'un second prolongements en forme de piston (70), disposés aux deux extrémités du corps de soupape (62) et pénétrant respectivement dans deux compartiments pilotes (71, 72), de deux vannes-pilotes auxiliaires (8, 9), actionnées alternativement et assurant le déplacement du corps de soupape (62) entre ses deux positions d'arrêt (I, II), ainsi que d'une section de guidage et d'étanchéité au moins (63) prévue sur le corps de soupape (62), la section précitée s'étendant entre la face de joint (67) d'une part, combinée au siège de soupape (66) compris entre le retour (R) et le raccordement (A), et le premier prolongement (70) d'autre part, la section (63) présentant par ailleurs un guidage étanche dans l'alésage de la cage, caractérisé en ce que le compartiment pilote (72), qui reçoit le second prolongement (70), est raccordé directement et en permanence à la source haute pression (38, 39), en ce que les deux vannes-pilotes auxiliaires (8, 9) sont affectées à l'autre compartiment (71), en ce que le corps de soupape (62) présente, sur son extrémité correspondant au raccordement de pression (P), une autre section de guidage et d'étanchéité (64), dont le diamètre (D2) est supérieur au diamètre (D1 ) des sièges de soupape (65, 66), et en ce que les surfaces de sollicitation des deux prolongements (70) sont de dimension égale, mais sont respectivement supérieures à la différence de surface définie par les diamètres (D1, D2) des sièges de soupape (66, 65) et de l'autre section de guidage et d'étanchéité (64).
3. Disjoncteur à haut pouvoir de coupure selon une des revendications 1 et 2, caractérisé en ce que les prolongements (50, 51; 70) sont constitués par des pistons auxiliaires séparés du corps de soupape (46; 62), aux extrémités duquel ils peuvent être appliqués.
4. Disjoncteur à haut pouvoir de coupure selon une des revendications 1 et 2, caractérisé en ce que les extrémités des sections de guidage et d'é- tanchéite (63, 64; 47, 48), opposées aux faces de joint (67, 68; 44, 45), sont soumises à une décharge de pression hydraulique.
5. Disjoncteur à haut pouvoir de coupure selon la revendication 1, caractérisé en ce que le rapport entre les surfaces de sollicitation des prolongements (50,51 ) est de 2:1 environ.
6. Disjoncteur à haut pouvoir de coupure selon la revendication 2, caractérisé en ce que le rapport des surfaces de sollicitation respectives des prolongements (70) sur la surface différentielle, comprise entre les sections de guidage et d'étanchéité (63, 64) et les sièges de soupape (64, 66), est de 2:1 environ.
7. Disjoncteur à haut pouvoir de coupure selon la revendication 2, caractérisé en ce que le corps de soupape (62) fonctionne par chevauchement positif avec ses sièges (65, 66) lors de sa course entre les deux positions d'arrêt (I, II).
8. Disjoncteur à haut pouvoir de coupure selon la revendication 2, caractérisé en ce que la partie antérieure des faces de joints (67, 68) du corps de soupape (62) est munie de prolongements en forme de tampon (69), dont la section est au maximum égale à celle des sièges (66, 65).
9. Disjoncteur à haut pouvoir de coupure selon la revendication 2, caractérisé par un dispositif d'encliquetage mécanique (73, 74, 75), prévu pour le maintien du corps de soupape (62) dans ses deux positions d'arrêt (1, 11).
EP81107195A 1981-09-11 1981-09-11 Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique Expired EP0074419B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP81107195A EP0074419B1 (fr) 1981-09-11 1981-09-11 Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique
DE8181107195T DE3173448D1 (en) 1981-09-11 1981-09-11 High-power electric circuit breaker with a hydraulically operated actuating device
AT81107195T ATE17413T1 (de) 1981-09-11 1981-09-11 Elektrischer hochleistungsschalter mit hydraulischer betaetigungsvorrichtung.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81107195A EP0074419B1 (fr) 1981-09-11 1981-09-11 Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique

Publications (2)

Publication Number Publication Date
EP0074419A1 EP0074419A1 (fr) 1983-03-23
EP0074419B1 true EP0074419B1 (fr) 1986-01-08

Family

ID=8187903

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81107195A Expired EP0074419B1 (fr) 1981-09-11 1981-09-11 Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique

Country Status (3)

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EP (1) EP0074419B1 (fr)
AT (1) ATE17413T1 (fr)
DE (1) DE3173448D1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8300760U1 (de) * 1983-01-13 1984-11-08 Beringer-Hydraulik GmbH, Neuheim, Zug Umschaltsitzventil
DE3601877C1 (de) * 1986-01-23 1987-06-04 Licentia Gmbh Antrieb fuer Hochspannungs-Leistungsschalter
DE20116920U1 (de) * 2001-10-15 2002-01-03 Heilmeier & Weinlein Sitzventil für den Differentialzylinder eines elektrischen Trennschalters
EP2282065B1 (fr) 2009-07-30 2012-05-16 HAWE Hydraulik SE Soupape à siège de commutation hydraulique et dispositif de section de puissance
JP2015041555A (ja) * 2013-08-23 2015-03-02 株式会社日立製作所 遮断器の流体圧駆動装置
CN105003478A (zh) * 2015-06-30 2015-10-28 河南平高电气股份有限公司 控制阀及使用该控制阀的断路器液压操动机构

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2213244A1 (de) * 1972-03-18 1973-09-27 Bbc Brown Boveri & Cie Hydraulisches umschalt-sitzventil bzw. gesteuertes rueckschlagventil
DE7240231U (de) * 1972-10-02 1974-07-18 Bbc Ag Hydraulisches Schaltventil
JPS6028082B2 (ja) * 1977-07-20 1985-07-03 株式会社日立製作所 流体圧駆動装置
DE3004599A1 (de) * 1980-02-08 1981-08-13 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Hauptventil-ansteuerung fuer einen hochspannungs-leistungsschalter

Also Published As

Publication number Publication date
EP0074419A1 (fr) 1983-03-23
DE3173448D1 (en) 1986-02-20
ATE17413T1 (de) 1986-01-15

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