EP0074419B1 - High-power electric circuit breaker with a hydraulically operated actuating device - Google Patents

High-power electric circuit breaker with a hydraulically operated actuating device 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
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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
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German (de)
French (fr)
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EP0074419A1 (en
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
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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/en
Priority to DE8181107195T priority patent/DE3173448D1/en
Priority to AT81107195T priority patent/ATE17413T1/en
Publication of EP0074419A1 publication Critical patent/EP0074419A1/en
Application granted granted Critical
Publication of EP0074419B1 publication Critical patent/EP0074419B1/en
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)

Abstract

1. A high power switch (2) including a hydraulic differential piston actuator (3) adapted to be continually biased in the opening direction of the switch by a high pressure source (38, 39) and to be selectively biased in the closing direction through a 2/3 way poppet valve (1a) comprising a valve body (46) disposed in a housing bore of said poppet valve for reciprocating movement between a first closure position (I) in which said differential piston actuator (3) is biased in the closing direction, and a second closure position (II) in which said differential piston actuator (3) is biased in the opening direction, and having two spaced sealing surfaces (44, 45) alternately engageable with one of two valve seats (42, 43) of equal diameter disposed between a passage (A) connected to the differential piston actuator (3), a return passage (R), and a pressure inlet (P), the two ends of said valve body (46) being provided with first and second piston-shaped extensions (50, 51) projecting into respective control chambers (52, 53), further including two alternately operable auxiliary control valves (8, 9) for displacing said valve body (46) between the two closure positions (I + II), and at least one guiding and sealing section (47) formed on said valve body (46) and extending between said first extension (50) and the sealing surface (44) cooperating with said valve seat (42) located between said return passage (R) and said passage (A) whilst being sealingly guided in said housing bore, characterized in that the control chamber (53) receiving said second extension (51) is in continual and direct communication with said high pressure source (38, 39), in that both auxiliary control valves (8, 9) are associated with the other control chamber (52), in that said valve body (46) has a further guiding and sealing section (48) adjacent its end associates with said pressure inlet (P), the diameter (D) of said section being equal to the diameter (D) of said valve seats (42, 43), and in that the pressure-receiving surface area of said second extension (51) is smaller that the pressure-receiving surface area of said first extension (50).

Description

Die Erfindung betrifft einen elektrischen Hochleistungsschalter der im Oberbegriff des Patentanspruchs 1 oder des unabhängigen Patentanspruchs 2 angegebenen Art.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.

An solche Hochleistungsschalter werden beim Öffnen ausserordentliche Anforderungen gestellt. Der Öffnungsvorgang muss in wenigen msek. vollständig abgeschlossen sein, da bei einer langsamen Öffnungsbewegung die anliegende elektrische Leistung zu einem Zerstören des Schalters oder zu einer Explosion führen könnte. Ein weiteres, wichtiges Kriterium bei der Konzeption solcher Schalter und ihrer hydraulischen Betätigungsvorrichtung ist die Forderung, dass der Schalter bei Ausfall der hydraulischen Versorgung oder bei einer neuerlichen Inbetriebnahme der hydraulischen Druckversorgung nach einem Ausfall in der Stellung zu verharren hat, in der er zuvor war.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.

Bei einem aus der DE-B2-8 31 808 bekannten Hochleistungsschalter sind im Sitzventil an beiden Enden des Ventilkörpers die kolbenartigen Ansätze mit unterschiedlichen Durchmessern und verschieden grossen Beaufschlagungsflächen ausgebildet. Die Beaufschlagungsfläche des in die eine Steuerkammer ragenden Ansatzes ist kleiner als die Beaufschlagungsfläche des anderen in die andere Steuerkammer ragenden Ansatzes. Die letztgenannte Steuerkammer ist über ein druckvorgesteuertes Hilfsventil dann mit der Hochdruckquelle in Verbindung, wenn der Ventilkörper in seine zweite Sperrstellung verschoben werden soll. Damit zu einer Bewegung des Ventilkörpers in die erste Sperrstellung der Druck am ersten Ansatz den Gegendruck vom zweiten Ansatz überwinden kann, muss über das Hilfsventil die Steuerkammer mit dem Rücklauf verbunden werden, in die der zweite Ansatz ragt. Für die Bewegung des Ventilkörpers reichen zwar kleine Hydraulikvolumina aus, so dass verhältnismässig kurze Schaltzeiten möglich sind, jedoch ist die hydraulische Steuerung des Sitzventiles baulich ausserordentlich aufwendig, da eine Vielzahl verschiedenartiger Hilfsventile, die in Abhängigkeit von der Bewegung des Differentialkolbenantriebs einerseits bzw. durch Schaltmagneten andererseits angesteuert werden, erforderlich ist. Der komplexe Aufbau der Steuervorrichtung ist nicht nur teuer, sondern birgt auch die Gefahr in sich, dass bereits bei einem geringfügigen Fehler infolge der vielen beweglichen Elemente und Dichtstellen das ordnungsgemässe Öffnen und Schliessen des Schalters in Frage gestellt wird. Der Differentialkolbenantrieb ist infolge seiner Vorsteueraufgabe für das Sitzventil aufwendig aufgebaut. Verzögerungen im Signalübertragungsweg lassen sich insbesondere beim Öffnen des Schalters nicht vermeiden, so dass die tatsächlich realisierbare Öffnungszeit nicht ausreichend kurz ist. Dazu kommt, dass infolge der insgesamt fünf verschieden gross dimensionierten Beaufschlagungsflächen des Ventilkörpers dieser wie auch die Gehäusebohrung des Sitzventiles kompliziert herstellbar sind.In a high-performance switch known from DE-B2-8 31 808, 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. Although small hydraulic volumes are sufficient for the movement of the valve body, so that relatively short switching times are possible, 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. In addition, as a result of the five different sized actuation surfaces of the valve body, the valve body and the bore in the housing of the seat valve are difficult to manufacture.

Der Erfindung liegt die Aufgabe zugrunde, einen Hochleistungsschalter der eingangs genannten Art zu schaffen, der in seinem konstruktiven Aufbau möglichst einfach ist und der bei Auftreten des entsprechenden Signals praktisch unverzögert geöffnet wird.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.

Die gestellte Aufgabe wird erfindungsgemäss entweder durch die im kennzeichnenden Teil des Patentanspruchs 1 oder durch die im kennzeichnenden Teil des unabhängigen Patentanspruches 2 angegebenen Merkmale gelöst.The object is achieved according to the invention either by the features specified in the characterizing part of patent claim 1 or by the features specified in the characterizing part of independent patent claim 2.

Bei der Lösung gemäss Patentanspruch 1 hat der weitere Dichtungs- und Führungsabschnitt des Ventilkörpers eine Druckausgleichswirkung für den Ventilkörper, so dass dieser in jeder Sperrstellung axial entlastet ist. Die Stellkräfte zum Verschieben des Ventilkörpers zwischen den beiden Sperrstellungen werden ausschliesslich durch die Beaufschlagung der beiden Ansätze erzeugt. Da die eine Steuerkammer in die der Ansatz mit der kleineren Beaufschlagungsfläche ragt, ständig an die Hochdruckquelle angeschlossen ist, braucht nur die andere Steuerkammer durch die Steuerventile überwacht zu werden, wobei allerdings zwei Hilfssteuerventile ausreichen, die dann wechselseitig betätigt werden. Insbesondere beim Öffnen des Schalters entlastet ein Hilfssteuerventil die Steuerkammer schlagartig, so dass der ständig am anderen Ansatz wirkende Druck der Hochdruckquelle den Ventilkörper schlagartig verschiebt, worauf der Differentialkolbenantrieb mit einer schlagartigen Öffnungsbewegung reagiert. Das Sitzventil ist baulich einfach, da es für den Ventilkörper nur eine mit gleichem Durchmesser durchlaufende Gehäusebohrung benötigt. Auch der Ventilkörper lässt sich einfach herstellen und kann im wesentlichen symmetrisch aufgebaut sein.In the solution according to claim 1, 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. In particular when the switch is opened, an auxiliary control valve suddenly relieves the pressure on the control chamber, so that the pressure of the high-pressure source, which is constantly acting on the other approach, suddenly shifts the valve body, whereupon the differential piston drive reacts with an abrupt opening movement. The poppet valve is structurally simple since it only requires a housing bore with the same diameter for the valve body. The valve body is also easy to manufacture and can be constructed essentially symmetrically.

Auch die Lösung gemäss Patentanspruch 2 ist baulich sehr einfach, weil die Verschiebebewegung des Ventilkörpers wiederum nur durch die Beaufschlagung der beiden Ansätze gesteuert wird, die gleiche Durchmesser aufweisen. Der weitere Führungs- und Dichtabschnitt des Ventilkörpers trennt nicht nur den Arbeitsteil der Gehäusebohrung von der für das Öffnen des Schalters verantwortlichen Steuerkammer, sondern bildet auch die Differenzfläche, die notwendig ist, um den Ventilkörper wieder in die Stellung zurückzuschieben, in der der Hochleistungsschalter geschlossen wird. Der Ventilkörper lässt sich auf einfache Weise vollständig symmetrisch ausbilden und auch die Gehäusebohrung hat eine produktionstechnisch einfache Form.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.

Herstellungstechnische Vorteile ergeben sich bei einer Ausführungsform gemäss Anspruch 3, da die Ansätze in Form getrennter Hilfskolben vom eigentlichen Ventilkörper getrennt hergestellt und eingesetzt werden können. Dadurch ergibt sich auch eine Vereinfachung der Bauform des Ventilkörpers.Manufacturing advantages result in an embodiment according to claim 3, since the approaches in the form of separate auxiliary pistons can be manufactured and used separately from the actual valve body. This also simplifies the design of the valve body.

Eine weitere zweckmässige Ausführungsform geht aus Anspruch 4 hervor. Lecköl entweder aus dem Arbeitsteil der Gehäusebohrung oder aus den Steuerkammern wird sofort nach aussen abgeführt, so dass sich keine gegenseitige Beeinflussung im Arbeitsbereich und im Steuerbereich im Sitzventil ergeben. Durch diese Druckentlastung der Enden des Ventilkörpers wird auch eine lokale Trennung zwischen den Steuerkammern und dem Arbeitsteil der Gehäusebohrung erreicht, so dass fertigungsbedingte Undichtigkeiten zu keinen Störungen führen.Another expedient embodiment is set out in claim 4. Leakage oil from either The working part of the housing bore or from the control chambers is immediately discharged to the outside, so that there is no mutual interference in the working area and in the control area in the poppet valve. This pressure relief of the ends of the valve body also achieves a local separation between the control chambers and the working part of the housing bore, so that leaks caused by production do not lead to any faults.

In der Praxis hat es sich gemäss Anspruch 5 und 6 als besonders zweckmässig erwiesen, ein Flächenverhältnis von etwa 2:1 zu wählen, da dann einerseits ein korrektes Bewegen des Ventilkörpers sichergestellt wird, obwohl die zu bewegenden Hydraulikvolumina klein sind.In practice, it has proven to be particularly expedient according to claims 5 and 6 to choose an area ratio of about 2: 1, since on the one hand correct movement of the valve body is ensured, although the hydraulic volumes to be moved are small.

Eine weitere, wichtige Ausführungsform geht aus Anspruch 7 hervor. Mit der positiven Überdeckung wird sichergestellt, dass beim Verschieben des Ventilkörpers zwischen seinen beiden Sperrstellungen und insbesondere bei der Bewegung von der ersten Sperrstellung in die zweite Sperrstellung aus dem Arbeitsteil der Gehäusebohrung nur eine vertretbar geringe Hydraulikmenge als Verlust in den Rücklauf abströmt.Another important embodiment is set out in claim 7. The positive overlap ensures that when the valve body is moved between its two locking positions and in particular during the movement from the first locking position into the second locking position, only a reasonably small amount of hydraulic fluid flows out as a loss into the return line from the working part of the housing bore.

In der Praxis hat sich weiterhin eine Ausführung bewährt, wie sie aus Anspruch 8 hervorgeht. Die zapfenartigen Fortsätze tauchen in die Ventilsitze ein und verhindern einen übergrossen Verlust hydraulischen Druckmittels, da sie das Druckmittel erst dann ungehindert durch den Ventilsitz lassen, wenn der andere Ventilsitz bereits durch den anderen Fortsatz weitgehend verschlossen ist. Die zapfenartigen Fortsätze definieren genau bemessene Spalte, die den Druckmittelstrom jeweils in der zuvor erwähnten Weise drosseln.In practice, an embodiment has also proven itself, as can be seen from claim 8. The peg-like extensions dip into the valve seats and prevent an excessive loss of hydraulic pressure medium, since they only let the pressure medium freely through the valve seat when the other valve seat is already largely closed by the other extension. The peg-like extensions define precisely dimensioned gaps, each of which throttles the pressure medium flow in the manner mentioned above.

Eine weitere zweckmässige Ausführungsform gibt schliesslich Anspruch 9 an. Die mechanische Rastvorrichtung hat die Aufgabe bei einem Druckausfall eine selbsttätige Bewegung des Ventilkörpers unter dem Einfluss von Schlägen gegen das Ventilgehäuse oder Vibrationen zu vermeiden. Die Rastvorrichtung ist aber nur so stark ausgelegt, dass ihre Kraft bei auch nur schwacher hydraulischer Beaufschlagung des Ventilkörpers oder der Ansätze sofort überwunden wird.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. However, 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.

Ausführungsformen der Erfindung werden nachstehend anhand der Zeichnungen erläutert. Es zeigt

  • Fig. 1 einen elektrischen Hochleistungsschalter mit seiner hydraulischen Betätigungsvorrichtung, und zwar mit einer ersten Ausführungsform eines 2/3-Wege-Sitzventils, und
  • Fig. 2 eine hydraulische Betätigungsvorrichtung für den elektrischen Hochleistungsschalter mit einer zweiten Ausführungsform eines 2/3-Wege-Sitzventils.
Embodiments of the invention are explained below with reference to the drawings. It shows
  • Fig. 1 is a high power electrical switch with its hydraulic actuator, with a first embodiment of a 2/3 -way valve seat, and
  • Fig. 2 shows a hydraulic actuating device for the electric high-power switch with a second embodiment of a 2/3 -way valve seat.

Aus Fig. 1 ist eine hydraulische Betätigungsvorrichtung für einen elektrischen Hochleistungsschalter 2 erkennbar (strichliniert angedeutet). Der Hochleistungsschalter 2 wird durch einen hydraulischen Differentialkolbenantrieb 3 betätigt, der einen Zylinderraum 4 mit grossem Beaufschlagungsquerschnitt sowie einen Zylinderraum 5 mit kleinerem Beaufschlagungsquerschnitt besitzt. Aus dem Zylinderraum 5 führt eine Kolbenstange 6 zum Hochleistungsschalter 2.1 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.

Der Zylinderraum 5 steht über eine Leitung 7a mit einer hydraulischen Hauptdruck-Versorgungsleitung 7 in Verbindung, die aus einer Hochdruckpumpe 38 gespeist wird. An die Hochdruck-Versorgungsleitung 7 ist ferner ein Druckspeicher 39 angeschlossen. Von der Hochdruck-Versorgungsleitung 7 zweigt eine Leitung 7b zu einem 2/3-Wege-Sitzventii 1 a ab, dessen Gehäuse mit 40 bezeichnet ist und drei Anschlüsse P, A, R aufweist. Die Leitung 7b führt zum Anschluss P (Druckanschluss). Von der Leitung 7 zweigt eine weitere Leitung 7c ab, in der ein erstes Hilfssteuerventil 8 und ein zweites Hilfssteuerventil 9 angeordnet sind. Die Leitung 7c führt hinter den Hilfssteuerventilen 8, 9 zum Anschluss R (Rücklauf). Die Hilfssteuerventile 8 und 9 sind bei diesem Ausführungsbeispiel magnetisch betätigte Zweistellungs-Ventile, die bei nicht erregten Magneten in ihrer Sperrstellung stehen.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. From 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.

Vom Zylinderraum 4 führt eine Leitung 10 zum Anschluss A, während der Anschluss R über eine Leitung 11 an den Rücklauf (Anschluss R) angeschlossen ist.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).

Im Gehäuse 40 des Sitzventils ist eine längsdurchgehende Gehäusebohrung 41 mit gleichbleibendem Durchmesser D vorgesehen, in der ein Ventilkörper 46 zwischen zwei Sperrstellungen 1 und II hin- und herbewegbar ist.In the housing 40 of the seat valve, 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.

In der Gehäusebohrung 41 sind zwei gleichgrosse Ventilsitze 42 und 43 ausgebildet, denen Dichtflächen 44 und 45 am Ventilkörper 46 gegenüberstehen. Die Dichtflächen 44 und 45 sind an Führungs- und Dichtabschnitten 47, 48 angeordnet, die den gleichen Durchmesser D besitzen, wie die Ventilsitze 42 und 43.In the housing bore 41, two 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.

Die Gehäusebohrung 41 ist an beiden Enden mit verlängernden Sackbohrungen 41 a und 41 b versehen, von denen die Sackbohrung 41 a einen Durchmesser d2 und die Sackbohrung 41 b einen Durchmesser d1 aufweist. Die Querschnittsflächen der Ventilsitze 42 und 43 stehen zu den Querschnittsflächen der Sackbohrungen 41 a und 41 b in etwa in einem Verhältnis von 1:4:10. Die hinter den beiden Führungs- und Dichtabschnitten 47 und 48 verbleibenden Teile der Gehäusebohrung 41 sind durch Entlastungsleitungen 49 druckentlastet.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.

In die Sackbohrung 41 taucht verschieblich ein Hilfskolben 50 ein, während in die Sackbohrung 41 b ein Hilfskolben 51 eintaucht, so dass Steuerkammern 52, 53 gebildet werden. Die Steuerkammer 53 ist ständig an die Leitung 7 angeschlossen. Die Steuerkammer 52 steht über eine Leitung 55 mit dem Leitungsabschnitt zwischen den Hilfssteuerventilen 8 und 9 in Verbindung und wird gleichzeitig über die Leitung 29 und die Drossel 30 mit dem Druck beaufschlagt, der in der Gehäusebohrung 41 jeweils herrscht.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.

In der dargestellten Lage ist der Hochleistungsschalter 2 geschlossen. Beide Zylinderräume 4, 5 stehen unter dem von der Hochdruckquelle 38, 39 bereitgestellten Druck. Der Zylinderraum 5 wird unmittelbar aus der Leitung 7 beaufschlagt, während der Zylinderraum 4 über die Leitung 7b, den Anschluss P (Druckanschluss), den freien Durchgang durch den Ventilsitz 43, den Anschluss A und die Leitung 10 mit dem gleichen Druck versorgt wird.In the position shown, the high-performance switch 2 is closed. Both cylinder spaces 4, 5 are under the pressure provided by the high pressure source 38, 39. The cylinder space 5 is acted upon directly from line 7, while the cylinder space 4 is supplied with the same pressure via line 7b, connection P (pressure connection), free passage through valve seat 43, connection A and line 10.

Dieser Druck herrscht auch in den Steuerkammern 52, 53. Der Hilfskolben 50 hält den Ventilkörper 46 in dieser Stellung. Da der Ventilsitz 42 gleich gross ist wie der Führungs- und Dichtabschnitt 48 ist der Ventilkörper 46 an sich axial druckausgeglichen. Die Dichtfläche 41 liegt am Ventilsitz 42 an und trennt die Anschlüsse A, P vom Rücklaufanschluss (Anschluss R). Der Druck wird gehalten. Der Ventilkörper 46 steht in der Sperrstellung I.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.

Wenn der Hochleistungsschalter 2 geöffnet werden soll, wird das Hilfssteuerventil 9 betätigt, so dass die Steuerkammer 52 schlagartig über die Leitung 55 in den Rücklauf R' entlastet wird. Das dabei zu verdrängende Hydraulikvolumen ist verhältnismässig klein. Darauffolgend überwiegt die Kraft des Hilfskolbens 51 und schiebt den Ventilkörper 46 nach links in seine zweite Sperrstellung 11, Die Dichtfläche 45 kommt zur Anlage am Ventilsitz 43 und trennt den Anschluss A vom Anschluss P ab. Gleichzeitig wird die Dichtfläche 44 vom Ventilsitz 42 abgehoben und der Anschluss A mit dem Anschluss R verbunden. Die Zylinderkammer 4 wird über die Leitung 10 schlagartig entlastet, so dass der Druck in der Zylinderkammer 5 den Kolben 3 nach links verschiebt und den Hochleistungsschalter 2 öffnet.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. Subsequently, 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. At the same time, 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.

Zum Zurückbewegen des Ventilkörpers 46 in die erste Sperrstellung I (Schliessen des Hochleistungsschalters 2) wird die Steuerkammer 52 über die Leitung 55 mit dem Druck aus der Druckquelle 38, 39 beaufschlagt, so dass der im Querschnitt grössere Hilfskolben 50 die ständig am kleineren Hilfskolben 51 wirkende Kraft überwindet und den Ventilkörper 46 in die in Fig. 1 gezeigte Stellung bringt. Nach einem Druckabfall und erneutem Aufbau des hydraulischen Druckes bleibt der Ventilkörper 46 in der Stellung, in der er zuvor gewesen ist. In der Sperrstellung I wird er durch die grössere Kraft des Hilfskolbens 50 gehalten, während er in der Sperrstellung 11 allein durch die Kraft des kleineren Hilfskolbens 51 gehalten wird.To move the valve body 46 back into the first blocking position I (closing 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. After a drop in pressure and a renewed build-up of the hydraulic pressure, 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 zeigt eine weitere Ausführungsform einer hydraulischen Betätigungsvorrichtung für einen nicht dargestellten Schalter, bei dem das 2/3-Wege-Sitzventil 1b mit seinem Gehäuse 60 besonders einfach hergestellt und montiert werden kann. Im Gehäuse 60 ist eine Gehäusebohrung 61 vorgesehen, die sich aus einem mittleren Abschnitt 61 b mit dem Durchmesser D1 und zwei Endabschnitten 61 a mit dem jeweiligen Durchmesser D2 zusammensetzt. Der Durchmesser des linken Endabschnittes 61a ist ohne Einfluss auf die Funktion des Ventils und könnte auch anders gewählt werden. Ein Ventilkörper 62 besitzt zwei in einem axialen Abstand voneinander liegende Führungs- und Dichtabschnitte 63 und 64, die Dichtflächen 67 und 68 tragen, die mit Ventilsitzen 66 und 65 zusammenarbeiten. An jeder Dichtfläche 67 und 68 ist ein zapfenartiger Fortsatz 69 angeordnet, dessen Aussendurchmesser in etwa dem Durchmesser D1 der Ventilsitze 65, 66 entspricht und dessen axiale Länge annähernd der Hälfte des möglichen Arbeitshubes des Ventilkörpers entspricht.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. In the housing 60, 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.

Die Gehäusebohrung 61 verlängernde Sackbohrungen 61 c mit jeweils dem gleichen Durchmesser d erstrecken sich im Gehäuse 60 und bilden dort Steuerkammern 71 und 72, in welchen Hilfskolben 70 mit gleichen Durchmessern d abgedichtet verschieblich geführt sind. Die Steuerkammer 72 ist über die Leitung 54 wiederum unmittelbar mit der Druckquelle verbunden, so dass sie ständig unter Druck steht.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.

An einem der Führungs- und Dichtabschnitte 63 oder 64 greift in Rastvertiefungen 74 ein Rastglied 73 an, das unter der Kraft einer Feder 75 steht. Das Rastglied verriegelt den Ventilkörper 62 in seinen beiden Sperrstellungen I und II, sofern keine hydraulische Druckbeaufschlagung erfolgt. Diese Rastvorrichtung soll vor allem mechanisch auf das 2/3-Wege-Sitzventil 1 b einwirkende Kräfte daran hindern, den Ventilkörper 62 ungewollt zu verschieben.On one of the guide and sealing sections 63 or 64 engages in locking recesses 74, 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.

Der Ventilkörper 62 arbeitet hier mit den Ventilsitzen 65, 66 mit einer positiven Überdeckung zusammen, d.h. die Fortsätze 69 tragen jeweils dafür Sorge, dass der Anschluss P mit dem Anschluss A erst verbunden wird, wenn der Anschluss R mit dem Anschluss A durch das Eintauchen des Fortsatzes 69 weitgehend getrennt wird. Diese Massnahme verhindert, dass beim Umschalten eine zu grosse Hydraulikmenge in den Rücklauf gelangen kann.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.

Wenn in der in Fig. 2 dargestellten Lage das Hilfssteuerventil 9 in seine Durchgangsstellung geschaltet wird, wird die Steuerkammer 71 entlastet, so dass die Haltekraft des Hilfskolbens 70 wegfällt und der zweite Hilfskolben 70 in der Druckkammer 72 mit seiner Kraft den Ventilkörper 62 nach links verschiebt, bis die Dichtfläche 68 am Ventilsitz 65 anliegt. Dazu ist es allerdings erforderlich, dass der Querschnitt des Hilfskolbens 70 grösser ist, als die Differenzfläche zwischen den Durchmessern D1 und D2, auf der der Druck im Anschluss P lastet. Damit der Ventilkörper dann wieder in seine Sperrstellung I zurückgeschoben werden kann, muss die Steuerkammer 71 wieder mit Druck beaufschlagt werden, so dass sich die Kräfte der beiden Hilfskolben 70 aufheben. Dann wirkt der Druck im Anschluss P auf die Differenzfläche zwischen dem Ventilsitz 65 und dem Führungs- und Dichtabschnitt 64 (D2-D1) und drückt den Ventilkörper 62 wieder nach rechts bis in die in Fig. 2 gezeigte Stellung. Der sich allmählich öffnende Spalt zwischen der Dichtfläche und dem Ventilsitz 65, unterstützt durch die Wirkung des Fortsatzes 69, führt zu einem Drosseleffekt, durch welchen zwischen dem Anschluss P und dem Anschluss A stets ein Druckgefälle vorliegt, welches dafür sorgt, dass der Ventilkörper 62 soweit nach rechts geschoben wird, bis seine Dichtfläche 67 am Ventilsitz 66 anliegt. Dann herrschen wieder eindeutige Kraftverhältnisse, da der volle Druck auf der Differenzfläche D2-D1 lastet.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. Then the pressure in port P acts on the differential area between the valve seat 65 and the guide and sealing section 64 (D2-D1) and presses the valve body 62 to the right again into the position shown in FIG. 2. The gradually opening gap between the sealing surface and the valve seat 65, supported by the action of the extension 69, leads to a throttling effect, by means of which there is always a pressure drop between the port P and the port A, which ensures that the valve body 62 extends as far is pushed to the right until its sealing surface 67 on the valve seat 66 is present. Then there are clear force relationships again, since the full pressure is on the differential surface D2-D1.

Bei beiden Ausführungsformen könnten an die eine Steuerkammer mehrere Hilfssteuerventile parallel angeschlossen werden, damit der Hochleistungsschalter bei Ausfall eines Hilfssteuerventiles mit einem anderen geöffnet werden kann.In both embodiments, several 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.

Claims (9)

1. A high power switch (2) including a hydraulic differential piston actuator (3) adapted to be continually biased in the opening direction of the switch by a high pressure source (38, 39) and to be selectively biased in the closing direction through a 2/3 way poppet valve (1 a) comprising a valve body (46) disposed in a housing bore of said poppet valve for reciprocating movement between a first closure position (I) in which said differential piston actuator (3) is biased in the closing direction, and a second closure position (II) in which said differential piston actuator (3) is biased in the opening direction, and having two spaced sealing surfaces (44, 45) alternately engageable with one of two valve seats (42, 43) of equal diameter disposed between a passage (A) connected to the differential piston actuator (3), a return passage (R), and a pressure inlet (P), the two ends of said valve body (46) being provided with first and second piston-shaped extensions (50, 51) projecting into respective control chambers (52, 53), further including two alternately operable auxiliary control valves (8, 9) for displacing said valve body (46) between the two closure positions (I + II), and at least one guiding and sealing section (47) formed on said valve body (46) and extending between said first extension (50) and the sealing surface (44) cooperating with said valve seat (42) located between said return passage (R) and said passage (A) whilst being sealingly guided in said housing bore, characterized in that the control chamber (53) receiving said second extension (51 ) is in continual and direct communication with said high pressure source (38, 39), in that both auxiliary control valves (8, 9) are associated with the other control chamber (52), in that said valve body (46) has a further guiding and sealing section (48) adjacent its end associates with said pressure inlet (P), the diameter (D) of said section being equal to the diameter (D) of said valve seats (42, 43), and in that the pressure-receiving surface area of said second extension (51) is smaller that the pressure-receiving surface area of said first extension (50).
2. A high power switch (2) including a hydraulic differential piston actuator (3) adapted to be continually biased in the opening direction of the switch from a high pressure source (38, 39), and to be selectively biased in the closing direction through a 2/3 way poppet valve (1 b) comprising a valve body (62) disposed in a housing bore of said poppet valve for reciprocating movement between a first closure position (I) in which said differential piston actuator (3) is biased in the closing direction, and a second closure position (II) in which said differential piston actuator (3) is biased in the opening direction, and having two spaced sealing surfaces (67, 68) alternately engageable with one of two valve seats (66, 65) having equal diameter and disposed between a passage (A) connected to the differential piston actuator (3), a return passage (R), and a pressure inlet (P), the two ends of said valve body (62) being provided with first and second piston-type extensions (70) projecting into respective control chambers (71, 72), further including two alternately operable auxiliary control valves (8, 9) for displacing said valve body (62) between the two closure positions (I, II) and at least one guiding and sealing section (63) formed on said valve body (62) extending between said first extension (70) and the sealing surface (67) cooperating with the valve seat (66) locates between said return passage (R) and said passage (A), and sealingly guided in said housing bore, characterized in that the control chamber (72) receiving said second extension (70) is in continual and direct communication with said high pressure source, in that both said auxiliary control valves (8, 9) are associated with the other control chamber (71), in that said valve body (62) has a further guiding and sealing section (64) adjacent its end associated with said pressure inlet (P), the diameter (D2) of said section being greater than the diameter (D1) if said valve seats (65, 66), and in that the pressure-receiving surface areas of the two extensions (70) are of equal size, the pressure-receiving surface area of each extension (70) by itself being greater than the difference of the pressure-receiving surface area determined by the diameters (D1, D2) of the valve seats (66, 65) and of said further guiding and sealing section (64).
3. A high power switch according to claims 1 or 2, characterized in that said extensions (50, 51; 70) are formed separate from said valve body (46, 62) as auxiliary pistons adapted to be abuttingly engaged with the ends of said valve body (46; 62).
4. A high power switch according to claims 1 or 2, characterized in that the ends of said guiding and sealing sections (63, 64; 47, 48) facing away from said sealing surfaces (67, 68; 44, 45) are hydraulically pressure-relieved.
5. A high power switch according to claim 1, characterized in that the ratio between the pressure-receiving surface areas of said extensions (50, 51) is about 2:1.
6. A high power switch according to claim 2, characterized in that the ratio between the respective pressure-receiving surface areas of each extension (70) and the differential surface area between the guiding and sealing sections (63, 64) and the valve seats (64, 66) is about 2:1.
7. A high power switch according to claim 2, characterized in that said valve body (62) cooperates with said valve seats (65, 66) in a positive covering relationship on being displaced between its two closure positions (I, II).
8. A high power switch according to claim 2, characterized in that said valve body (62) is formed with pinion-shaped projections (69) extending forwards of the sealing surfaces (67, 68), the cross-sectional area of said projections being not greater than the cross-sectional area of said valve seats (66, 65).
9. A high power switch according to claim 2, characterized by mechanical snap engagement means (73, 74, 75) for said valve body (62) by means of which it is selectively retained in its two closure positions (I, II).
EP81107195A 1981-09-11 1981-09-11 High-power electric circuit breaker with a hydraulically operated actuating device Expired EP0074419B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP81107195A EP0074419B1 (en) 1981-09-11 1981-09-11 High-power electric circuit breaker with a hydraulically operated actuating device
DE8181107195T DE3173448D1 (en) 1981-09-11 1981-09-11 High-power electric circuit breaker with a hydraulically operated actuating device
AT81107195T ATE17413T1 (en) 1981-09-11 1981-09-11 HIGH PERFORMANCE ELECTRIC BREAKER WITH HYDRAULIC ACTUATION DEVICE.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81107195A EP0074419B1 (en) 1981-09-11 1981-09-11 High-power electric circuit breaker with a hydraulically operated actuating device

Publications (2)

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

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ID=8187903

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81107195A Expired EP0074419B1 (en) 1981-09-11 1981-09-11 High-power electric circuit breaker with a hydraulically operated actuating device

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8300760U1 (en) * 1983-01-13 1984-11-08 Beringer-Hydraulik GmbH, Neuheim, Zug Reversing seat valve
DE3601877C1 (en) * 1986-01-23 1987-06-04 Licentia Gmbh Drive for high-voltage circuit breakers
DE20116920U1 (en) * 2001-10-15 2002-01-03 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Seat valve for the differential cylinder of an electrical disconnector
EP2282065B1 (en) 2009-07-30 2012-05-16 HAWE Hydraulik SE Hydraulic switching valve and circuit breaker device
JP2015041555A (en) * 2013-08-23 2015-03-02 株式会社日立製作所 Fluid pressure driving device for circuit breaker
CN105003478A (en) * 2015-06-30 2015-10-28 河南平高电气股份有限公司 Control valve and circuit breaker hydraulic operating mechanism using control valve

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2213244A1 (en) * 1972-03-18 1973-09-27 Bbc Brown Boveri & Cie HYDRAULIC SWITCH-OVER SEAT VALVE OR CONTROLLED NON-RETURN VALVE
DE7240231U (en) * 1972-10-02 1974-07-18 Bbc Ag Hydraulic switching valve
JPS6028082B2 (en) * 1977-07-20 1985-07-03 株式会社日立製作所 Fluid pressure drive device
DE3004599A1 (en) * 1980-02-08 1981-08-13 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt MAIN VALVE CONTROL FOR A HIGH VOLTAGE CIRCUIT BREAKER

Also Published As

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

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