[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP3390840B1 - Double stage valve assembly for hydraulic control of a piston cylinder for a high or middle voltage switch - Google Patents

Double stage valve assembly for hydraulic control of a piston cylinder for a high or middle voltage switch Download PDF

Info

Publication number
EP3390840B1
EP3390840B1 EP16802110.3A EP16802110A EP3390840B1 EP 3390840 B1 EP3390840 B1 EP 3390840B1 EP 16802110 A EP16802110 A EP 16802110A EP 3390840 B1 EP3390840 B1 EP 3390840B1
Authority
EP
European Patent Office
Prior art keywords
main valve
valve
control
stage
control face
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.)
Active
Application number
EP16802110.3A
Other languages
German (de)
French (fr)
Other versions
EP3390840A1 (en
Inventor
Thomas Brenneis
Matthias E. Schmidt
Thomas Klose
Niko ROBENS
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.)
ABB Schweiz AG
Original Assignee
ABB Schweiz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ABB Schweiz AG filed Critical ABB Schweiz AG
Publication of EP3390840A1 publication Critical patent/EP3390840A1/en
Application granted granted Critical
Publication of EP3390840B1 publication Critical patent/EP3390840B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0431—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the electrical control resulting in an on-off function
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members

Definitions

  • the invention relates to the field of hydraulic control of a piston-cylinder arrangement by means of a valve arrangement, the valve arrangement being part of a drive for actuating a high or medium voltage circuit breaker. Due to the interaction of hydraulics and mechanics, the drive is also referred to as a hybrid mechanical drive. High voltage is understood to mean the voltage range above 50 kV, while the medium voltage is considered to be the range between 1 and 50 kV.
  • valve stages include a pilot stage and a main stage.
  • the valve arrangement of the EP 2 234 135 B1 consists of a 3/2-way valve as pilot valve and two 2/2-way valves as main valves, while in the valve arrangement the DE 10 2009 053 901 B3 there are also two 2/2-way valves as main valves, but the function of the 3/2-way pilot valve is performed by two 2/2-way valves as pilot valves.
  • FIG. 1 is the valve arrangement of the EP 2 234 135 B1 shown together with the piston-cylinder arrangement controlled by the valve arrangement and the high-voltage circuit breaker 7 to be actuated.
  • Valve arrangement and piston-cylinder arrangement together belong to a hydraulic drive for actuating the high-voltage circuit breaker.
  • a first position of the pilot valve 11 the path is cleared from a high-pressure accumulator 9 via a first main valve 1 to a space 10 located inside the cylinder 12 and above the piston 6, ie the high-pressure fluid is supplied to the space 10 above the piston 6 , so that the high-voltage circuit breaker 7 is closed.
  • the fluid is usually formed by a hydraulic oil.
  • the space 10 is connected to a low-pressure tank 8 via a second main valve 2, ie the space 10 above the piston 6 is relieved of pressure, as a result of which the piston 6 moves back and the high-voltage circuit breaker 7 opens.
  • the first and second pilot valves, 3 and 4, the Fig. 2 are designed as electrically operated and spring-reset NC valves.
  • the technical spring return always results in the situation after a shift that in the pilot control area, i.e. in the hydraulic area of the pilot control stage, there is an enclosed oil volume, which is necessary for the correct positioning of the first main valve 1 and the second main valve 2 of the main stage for the duration is responsible until the next switching operation.
  • the 2/2-way valves 3 and 4 of the pilot stage are never completely leak-free. Depending on the switch position, the internal leakage at the pilot valves 3 and 4 can lead to an undesirable pressure build-up or reduction, which could jeopardize the correct positioning of the main valves 1 and 2.
  • a small orifice or throttle 5 is installed between the pilot control area, that is to say the hydraulic area in which the oil is enclosed, and the main control area, that is to say the area that drives the main piston 6.
  • the throttle 5 is located between the output side X of the pilot valves 3, 4 connected to the control inputs of the main valves 1, 2 and the output side Z of the main valves 1, 2 connected to the space 10 of the piston-cylinder arrangement (6, 12).
  • F1 has an opening effect for the first main valve 1
  • F2 and F3 have a closing effect. If the first main valve 1 is opened, the high-voltage circuit breaker 7 is closed, ie switched on.
  • all three control surfaces F1, F2, F3 of the first main valve 1 have the same pressure, namely high pressure. Because the size of the first control surface F1 is equal to the sum of the sizes of the second control surface F2 and the third control surface F3, the forces in the direction of opening or closing of the first main valve 1 are then in equilibrium.
  • the first main valve 1 is kept open in this state, that is to say the stationary switch-on state of the high-voltage circuit breaker 7, only by the spring catch 13, which is relatively weak in comparison with the pressure forces acting.
  • the second control surface F2 is subject to a pressure which is to a significant extent dependent on the flow of the hydraulic oil.
  • the object of the invention is to provide a valve arrangement for the hydraulic control of a piston-cylinder arrangement of a high or medium voltage circuit breaker, with which the problems described above of an unwanted or slow opening or a slow switching on of the high voltage circuit breaker can be remedied.
  • the first main valve has a total of four control surfaces, that is, in addition to the first control surface of the main valve, three further control surfaces, of which a second and a third control surface of the first main valve have a closing effect and a fourth control surface of the first main valve has an opening effect.
  • the second control surface of the first main valve is connected to the high pressure line; the third control surface of the first main valve is connected to the low pressure line; and the fourth control surface of the first main valve is connected to the outlet-side valve connection of the first main valve.
  • the size ratio of the opening to the closing control surfaces of the first main valve behaves in such a way that an opening force resulting in the opening state of the first main valve remains.
  • the latter is in contrast to the known design Fig. 2 , in which, after reaching the open state of the first main valve 1, there is a balance of forces between opening and closing forces on the first main valve, so that pressure fluctuations can lead to undesired closing.
  • the first main valve of the present invention now includes four instead of the known three control or active surfaces. Of the four control surfaces, two are closing and two are opening. In addition, one of the closing control surfaces is permanently connected to the low pressure line and above it to the low pressure tank. The sizes of the opening control surfaces are selected in relation to the sizes of the closing control surfaces so that the first main valve remains securely in the open state even in the event of pressure fluctuations.
  • the sum of the size of the first and the size of the fourth control surface of the first main valve is larger than the size of the second control surface of the first main valve, in a particularly preferred configuration the sum of the size of the first and the size of the fourth control surface of the first main valve is the same as the sum of the size of the second and the size of the third control surface of the first main valve. Since the third control surface is permanently connected to the low-pressure line, only the first, second and fourth control surfaces are at high pressure when the first main valve is open.
  • the second control surface of the first main valve is at least as large as the fourth control surface of the first main valve. This ensures that the closing effect of the second control surface is sufficient to overcome the opening effect of the fourth control surface and to initiate the closing of the first main valve immediately after the low pressure is applied to the first control surface.
  • the second main valve is provided with a spring force-based detent which engages when the second main valve is open. This ensures that the second main valve remains in the open state even after the high-voltage circuit breaker has been switched off, when the second main valve is completely depressurized. This desired behavior is also referred to as switch position memory. If there is no detent, the second main valve would otherwise be closed automatically by the return spring in the valve.
  • the first and / or the second main valve are provided with a manual reset option, that is to say a manually operable reset option.
  • a manual reset option that is to say a manually operable reset option.
  • the two-stage valve arrangement and thus the drive could no longer be put into operation since no pressure can be built up.
  • a pump would take the fluid, which is usually a hydraulic oil, only pump in a circuit, since the main valves would allow a direct flow from the high pressure line to the low pressure line, ie from the actual high pressure area into the low pressure tank.
  • the main valve affected by vibration-related adjustment can now be returned to its starting position, so that commissioning can take place without hindrance.
  • FIG 3 shows a possible embodiment of a two-stage valve arrangement according to the invention.
  • the two-stage valve arrangement is used for the hydraulic control of a piston 6 in a cylinder 12 of a high or medium voltage circuit breaker 7.
  • the two-stage valve arrangement comprises a main stage with two 2/2-way valves, which are referred to as the first main valve 31 and the second main valve 32, and a pilot stage with two 2/2-way valves, which are referred to as the first pilot valve 3 and as the second pilot valve 4.
  • the same reference numerals are used for those with the Figures 1 and 2 matching elements used.
  • a high-pressure line P which carries a fluid under high pressure, is connected directly to an inlet-side valve connection 33 of the first main valve 31 and is fed from a high-pressure accumulator 9.
  • the fluid is preferably a hydraulic oil, but can also be compressed air, for example.
  • a low pressure line T is connected directly to an inlet-side valve connection 34 of the second main valve 32, the low-pressure line T carrying the fluid under low pressure and being connected to a low-pressure tank 8.
  • the pilot stage has two connections on the input side, one of the connections, namely the input side connection 37 of the first pilot control valve 3, being connected to the high-pressure line P, and the other of the connections, namely the input side connection 38 of the second pilot control valve 4, being connected to the Low pressure line T is connected.
  • An outlet-side valve connection 35 of the first main valve 31 and an outlet-side valve connection 36 of the second main valve 32 are connected to one another at a hydraulic connection node Z, and above that to a space 10 located on one side of the piston 6, i.e. the outlet-side valve connections 35, 36 of the main valves 31, 32 feed directly into the space 10.
  • the pilot control stage has a hydraulic pilot control output X, which is connected to the output-side connection of the first and second pilot control valves 3, 4.
  • the pilot control output X is in turn connected to an opening first control surface F4 of the first main valve 31 and to a closing first control surface F8 of the second main valve 32.
  • the pilot stage establishes a connection between the high pressure line P and the hydraulic pilot control output X.
  • the first pilot valve 3 is open and the second pilot valve 4 is closed.
  • the high pressure then acting on the first control surfaces F4, F8 of the main valves 31, 32 causes the first main valve 31 to open and the second main valve 32 to close, so that the fluid under high pressure is supplied to the space 10 on one side of the piston 6 , whereby the high or medium voltage circuit breaker 7 is turned on, that is closed.
  • the pilot stage establishes a connection between the low-pressure line T and the hydraulic pilot control output X.
  • the first pilot valve 3 is closed and the second pilot valve 4 is open.
  • the low pressure then acting on the first control surfaces F4, F8 of the main valves 31, 32 causes the first main valve 31 to close and the second main valve 32 to open, so that fluid is discharged from the space 10 on one side of the piston 6 in the direction of the low pressure line T. becomes, which leads to switching off, ie opening, of the high or medium voltage circuit breaker 7.
  • the first main valve 31 has three further control surfaces, as does the one Figure 4 It can be seen which shows a possible embodiment of the first main valve 31.
  • first control surface F4 of the first main valve which has an opening effect
  • second and a third control surface, F5 and F6, of the first main valve both of which have a closing effect.
  • a fourth control surface F7 of the first main valve in turn has an opening effect.
  • the second control surface F5 of the first main valve is connected to the high-pressure line P within the two-stage valve arrangement; the third control surface F6 of the first main valve is connected to the low-pressure line T, and the fourth control surface F7 of the first main valve is connected to the outlet-side valve connection 35 of the first main valve 31.
  • the ratio of the size of the opening control surfaces, F4 and F7, to the closing control surfaces, F5 and F6, of the first main valve is such that when the first main valve is open, an opening force remains, so that the first Main valve 31 remains securely in the open state, even if pressure fluctuations occur in the high-pressure line P.
  • the area size of the first control surface F4 of the first main valve is to be designated AF4, and analogously the area sizes of the other control areas F5, F6, F7 of the first main valve are designated AF5, AF6 and AF7.
  • the second control surface of the first main valve is at least as large as the fourth control surface of the first main valve, that is AF5 ⁇ AF7. Due to the former size ratio, the design is based on Fig. 4 ensures that in the open state of the first main valve 31, when high pressure is applied to the first (F4), second (F5) and fourth (F7) control surface, an unexpected increase in the pressure at the second control surface F5 does not lead to an undesired closing of the first main valve leads.
  • the latter size ratio ensures that at the start of a desired closing operation of the first main valve 31, when changing from high pressure to low pressure on the first control surface F4, the high pressure on the second control surface F5 is sufficient to initiate the closing operation.
  • the first main valve 31 also has a spring force-based detent 40, which ensures that the first main valve 31 remains as safe as possible in the open state until a sufficiently large closing force acts against it.
  • the first main valve 31 is provided with a manual reset option 42, by means of which the first main valve can be brought back into the closed state after being adjusted for transport.
  • FIG. 5 A possible embodiment of the second main valve 32 is shown. This has a total of three control surfaces, that is, in addition to the first control surface F8, a second control surface F9 of the second main valve and a third control surface F10 of the second main valve.
  • the second control surface F9 of the second main valve is connected to the low-pressure line T
  • the third control surface F10 of the second main valve is connected to the outlet-side valve connection 36 of the second main valve 32.
  • the second main valve 32 is also provided with a spring force-based detent 39, which engages when the second main valve is open.
  • This spring force-based detent 39 counteracts in particular the force influence of the return spring 41, so that a switch position memory can be realized in this way, i.e. the second main valve is kept in the open state even after the high or medium voltage circuit breaker 7 has been switched off, when the second main valve is completely depressurized.
  • the return spring 41 is in the second main valve 32 Fig. 5 supplemented by a manual reset option 42, so that the second main valve can also be brought back into the closed state after a transport-related adjustment and undesired engagement of the detent 39.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)

Description

Die Erfindung betrifft den Bereich der hydraulischen Ansteuerung einer Kolben-Zylinderanordnung mittels einer Ventilanordnung, wobei die Ventilanordnung zu einem Antrieb zur Betätigung eines Hoch- oder Mittelspannungsleistungsschalters gehört. Aufgrund des Zusammenwirkens von Hydraulik und Mechanik wird der Antrieb auch als hybrid-mechanischer Antrieb bezeichnet. Unter Hochspannung wird hierbei der Spannungsbereich oberhalb von 50 kV verstanden, während als Mittelspannung der Bereich zwischen 1 und 50 kV angesehen wird.The invention relates to the field of hydraulic control of a piston-cylinder arrangement by means of a valve arrangement, the valve arrangement being part of a drive for actuating a high or medium voltage circuit breaker. Due to the interaction of hydraulics and mechanics, the drive is also referred to as a hybrid mechanical drive. High voltage is understood to mean the voltage range above 50 kV, while the medium voltage is considered to be the range between 1 and 50 kV.

Aus der EP 2 234 135 B1 sowie der DE 10 2009 053 901 B3 sind jeweils zweistufige Ventilanordnungen zur Betätigung eines Kolbens eines hydraulischen Antriebs bekannt, wobei der hydraulische Antrieb zur Betätigung eines Hochspannungsleistungsschalters vorgesehen ist. Die Ventilstufen umfassen eine Vorsteuerstufe und eine Hauptstufe.From the EP 2 234 135 B1 as well as the DE 10 2009 053 901 B3 Two-stage valve arrangements for actuating a piston of a hydraulic drive are known, the hydraulic drive being provided for actuating a high-voltage circuit breaker. The valve stages include a pilot stage and a main stage.

Die Ventilanordnung der EP 2 234 135 B1 besteht aus einem 3/2-Wegeventil als Vorsteuerventil sowie zwei 2/2-Wegeventilen als Hauptventile, während in der Ventilanordnung der DE 10 2009 053 901 B3 ebenfalls zwei 2/2-Wegeventile als Hauptventile vorhanden sind, jedoch die Funktion des 3/2-Wege-Vorsteuerventils durch zwei 2/2-Wegeventile als Vorsteuerventile ausgeübt wird.The valve arrangement of the EP 2 234 135 B1 consists of a 3/2-way valve as pilot valve and two 2/2-way valves as main valves, while in the valve arrangement the DE 10 2009 053 901 B3 there are also two 2/2-way valves as main valves, but the function of the 3/2-way pilot valve is performed by two 2/2-way valves as pilot valves.

In Figur 1 ist die Ventilanordnung der EP 2 234 135 B1 gemeinsam mit der durch die Ventilanordnung angesteuerten Kolben-Zylinderanordnung sowie dem zu betätigenden Hochspannungsleistungsschalter 7 dargestellt. Ventilanordnung und Kolben-Zylinderanordnung gehören gemeinsam zu einem hydraulischen Antrieb zur Betätigung des Hochspannungsleistungsschalters.In Figure 1 is the valve arrangement of the EP 2 234 135 B1 shown together with the piston-cylinder arrangement controlled by the valve arrangement and the high-voltage circuit breaker 7 to be actuated. Valve arrangement and piston-cylinder arrangement together belong to a hydraulic drive for actuating the high-voltage circuit breaker.

In einer ersten Stellung des Vorsteuerventils 11 wird der Weg von einem Hochdruckspeicher 9 über ein erstes Hauptventil 1 zu einem innerhalb des Zylinders 12 und oberhalb des Kolbens 6 befindlichen Raum 10 freigemacht, d.h. das unter Hochdruck stehende Fluid wird dem Raum 10 oberhalb des Kolbens 6 zugeführt, so dass der Hochspannungsleistungsschalter 7 geschlossen wird. Das Fluid wird üblicherweise durch ein Hydrauliköl gebildet. In einer zweiten Stellung des Vorsteuerventils 11 wird der Raum 10 über ein zweites Hauptventil 2 mit einem Niederdrucktank 8 verbunden, d.h. der Raum 10 oberhalb des Kolbens 6 wird druckentlastet, wodurch sich der Kolben 6 zurückbewegt und den Hochspannungsleistungsschalter 7 öffnet.In a first position of the pilot valve 11, the path is cleared from a high-pressure accumulator 9 via a first main valve 1 to a space 10 located inside the cylinder 12 and above the piston 6, ie the high-pressure fluid is supplied to the space 10 above the piston 6 , so that the high-voltage circuit breaker 7 is closed. The fluid is usually formed by a hydraulic oil. In a second position of the pilot valve 11, the space 10 is connected to a low-pressure tank 8 via a second main valve 2, ie the space 10 above the piston 6 is relieved of pressure, as a result of which the piston 6 moves back and the high-voltage circuit breaker 7 opens.

Die alternative Ventilanordnung der DE 10 2009 053 901 B3 ist in Figur 2 zu sehen, wieder zusammen mit der Kolben-Zylinderanordnung (6, 12) des hydraulischen Antriebs und dem zu betätigenden Schalter 7. Gleiche Elemente zu Fig. 1 tragen dieselben Bezugszeichen, und die grundsätzliche Arbeitsweise der Ventilanordnung ist dieselbe wie oben für Fig. 1 beschrieben.The alternative valve arrangement of the DE 10 2009 053 901 B3 is in Figure 2 to see, again together with the piston-cylinder arrangement (6, 12) of the hydraulic drive and the switch 7 to be actuated. Same elements Fig. 1 bear the same reference numerals, and the basic operation of the valve assembly is the same as above for Fig. 1 described.

Die ersten und zweiten Vorsteuerventile, 3 und 4, der Fig. 2 sind als elektrisch betätigte und federrückgestellte NC-Ventile ausgeführt. Durch die technisch bedingte Federrückstellung kommt es nach einer Schaltung stets zu der Situation, dass im Vorsteuerbereich, also im hydraulischen Bereich der Vorsteuerstufe, ein eingeschlossenes Ölvolumen entsteht, welches für die korrekte Positionierung des ersten Hauptventils 1 und des zweiten Hauptventils 2 der Hauptstufe für die Zeitdauer bis zum nächsten Schaltvorgang verantwortlich ist.The first and second pilot valves, 3 and 4, the Fig. 2 are designed as electrically operated and spring-reset NC valves. The technical spring return always results in the situation after a shift that in the pilot control area, i.e. in the hydraulic area of the pilot control stage, there is an enclosed oil volume, which is necessary for the correct positioning of the first main valve 1 and the second main valve 2 of the main stage for the duration is responsible until the next switching operation.

Die 2/2-Wegeventile 3 und 4 der Vorsteuerstufe sind jedoch niemals vollkommen leckagefrei. Je nach Schaltstellung kann nun die interne Leckage an den Vorsteuerventilen 3 und 4 zu einem unerwünschten Druckaufbau oder -abbau führen, was die korrekte Positionierung der Hauptventile 1 und 2 gefährden könnte. In der DE 10 2009 053 901 B3 wird das Problem dadurch gelöst, dass zwischen dem Vorsteuerbereich, also dem hydraulischen Bereich, in dem das Öl eingeschlossen ist, und dem Hauptsteuerbereich, also dem Bereich, der den Hauptkolben 6 antreibt, eine kleine Blende oder Drossel 5 eingebaut wird. Konkret befindet sich die Drossel 5 zwischen der mit den Steuereingängen der Hauptventile 1, 2 verbundenen Ausgangsseite X der Vorsteuerventile 3, 4 und der mit dem Raum 10 der Kolben-Zylinder-Anordnung (6, 12) verbundenen Ausgangsseite Z der Hauptventile 1, 2.However, the 2/2-way valves 3 and 4 of the pilot stage are never completely leak-free. Depending on the switch position, the internal leakage at the pilot valves 3 and 4 can lead to an undesirable pressure build-up or reduction, which could jeopardize the correct positioning of the main valves 1 and 2. In the DE 10 2009 053 901 B3 The problem is solved in that a small orifice or throttle 5 is installed between the pilot control area, that is to say the hydraulic area in which the oil is enclosed, and the main control area, that is to say the area that drives the main piston 6. Specifically, the throttle 5 is located between the output side X of the pilot valves 3, 4 connected to the control inputs of the main valves 1, 2 and the output side Z of the main valves 1, 2 connected to the space 10 of the piston-cylinder arrangement (6, 12).

In der EP 2933816 A1 wird vorgeschlagen, anstelle der Drossel ein Wechselventil einzusetzen, und zwar in der Art, dass das Wechselventil bis zu einem vordefinierten Volumenstrom bzw. bis zu einer vordefinierten Druckdifferenz einen Durchgang ermöglicht und oberhalb dieses vordefinierten Volumenstroms bzw. dieser vordefinierten Druckdifferenz die beiden an das Ventil angeschlossenen Druckleitungen voneinander trennt. Dabei ist das Hydraulikventil in beiden Volumenstromrichtungen gleichartig wirksam.In the EP 2933816 A1 It is proposed to use a shuttle valve instead of the throttle, in such a way that the shuttle valve up to a predefined Volume flow or up to a predefined pressure difference allows a passage and above this predefined volume flow or this predefined pressure difference separates the two pressure lines connected to the valve. The hydraulic valve is equally effective in both flow directions.

Hinsichtlich der aus der DE 10 2009 053 B3 bekannten Ventilanordnung (Fig. 2) wurden nun folgende Nachteile festgestellt: Das erste Hauptventil 1 besitzt drei Steuerflächen F1, F2, F3, mit dem Flächenverhältnis F1=F2+F3. Hierbei wirkt F1 für das erste Hauptventil 1 öffnend, und F2 und F3 wirken schließend. Wird das erste Hauptventil 1 geöffnet, wird der Hochspannungsleistungsschalter 7 geschlossen, d.h. eingeschaltet.Regarding from the DE 10 2009 053 B3 known valve arrangement ( Fig. 2 ) the following disadvantages have now been found: the first main valve 1 has three control surfaces F1, F2, F3, with the area ratio F1 = F2 + F3. F1 has an opening effect for the first main valve 1, and F2 and F3 have a closing effect. If the first main valve 1 is opened, the high-voltage circuit breaker 7 is closed, ie switched on.

Nach Beendigung dieses Einschaltvorganges wirkt auf alle drei Steuerflächen F1, F2, F3 des ersten Hauptventils 1 der gleiche Druck, und zwar Hochdruck. Aufgrund der Gleichheit der Größe der ersten Steuerfläche F1 mit der Summe aus den Größen der zweiten Steuerfläche F2 und der dritten Steuerfläche F3 befinden sich dann die Kräfte in Richtung Öffnen bzw. Schließen des erstens Hauptventils 1 im Gleichgewicht. Das erste Hauptventil 1 wird in diesem Zustand, also dem stationären Einschaltzustand des Hochspannungsleistungsschalters 7, lediglich durch die, im Vergleich zu den wirkenden Druckkräften, verhältnismäßig schwache Federrastierung 13 geöffnet gehalten. Hierbei unterliegt die zweite Steuerfläche F2 einem Druck, der zu einem nennenswerten Anteil von der Strömung des Hydrauliköls abhängig ist.After this switch-on process has ended, all three control surfaces F1, F2, F3 of the first main valve 1 have the same pressure, namely high pressure. Because the size of the first control surface F1 is equal to the sum of the sizes of the second control surface F2 and the third control surface F3, the forces in the direction of opening or closing of the first main valve 1 are then in equilibrium. The first main valve 1 is kept open in this state, that is to say the stationary switch-on state of the high-voltage circuit breaker 7, only by the spring catch 13, which is relatively weak in comparison with the pressure forces acting. In this case, the second control surface F2 is subject to a pressure which is to a significant extent dependent on the flow of the hydraulic oil.

Da der tatsächlich wirkende Druck abhängig von der real vorhandenen Durchströmung des ersten Hauptventils 1 ist, kommt es vor, dass das Kräfteverhältnis zwischen den Kräften der Steuerflächen F1, F2 und F3 nicht mehr ausgeglichen ist, sondern sich zeitweise so verändert, dass die durch die zweite Steuerfläche F2 erzeugte Kraft steigt. Dadurch wird die von der ersten Steuerfläche F1 erzeugte Öffnungskraft kleiner als die Summe der Schließkräfte der zweiten und dritten Steuerflächen, F2 und F3, und das erste Hauptventil 1 schließt. Die sich dadurch ändernde Strömung verringert damit zwar wieder die durch die zweite Steuerfläche F2 wirkende Schließkraft, so dass sich das erste Hauptventil 1 wieder im Gleichgewicht befindet. Das Kräftegleichgewicht bewirkt jedoch keine erneute Öffnung des ersten Hauptventils 1, sondern es verharrt im aktuellen geschlossenen Zustand. Ein derartiges Verweilen des ersten Hauptventils 1 in der Geschlossen-Stellung bei gleichzeitigem Einschaltzustand des Hochspannungsleistungsschalters 7 ist unerwünscht, da es den Leckage-Ausgleich im Steuerbereich zwischen den Hauptventilen 1 und 2 aufgrund des Abtrennens der Steuerleitungen vom Hochdruckspeicher 9 verhindert. Dies kann zur Folge haben, dass entweder ein unerwünschtes Öffnen und damit Ausschalten des Hochspannungsleistungsschalters 7 aufgrund einer Leckage im X-Bereich erfolgt, oder sogar ein unerwünschtes langsam stattfindendes Ausschalten aufgrund einer Leckage im Z-Bereich. Beides stellt eine maßgebliche Fehlfunktion des hybrid-mechanischen Antriebs dar.Since the actually acting pressure is dependent on the actual flow through the first main valve 1, it happens that the force ratio between the forces of the control surfaces F1, F2 and F3 is no longer balanced, but changes temporarily so that the second Control surface F2 generated force increases. As a result, the opening force generated by the first control surface F1 becomes smaller than the sum of the closing forces of the second and third control surfaces, F2 and F3, and the first main valve 1 closes. The flow thereby changing admittedly reduces the closing force acting through the second control surface F2, so that the first main valve 1 is again in equilibrium. However, the balance of forces does not cause the first main valve 1 to open again, but instead remains in the current closed state. Such a stay of the first main valve 1 in the closed position while the high-voltage circuit breaker 7 is switched on is undesirable since it prevents leakage compensation in the control area between the main valves 1 and 2 due to the control lines being disconnected from the high-pressure accumulator 9. This can have the consequence that either an undesired opening and thus switching off of the high-voltage circuit breaker 7 takes place due to a leak in the X range, or even an undesired slow switching off due to a leak in the Z range. Both represent a significant malfunction of the hybrid mechanical drive.

Sofern die Strömungsänderung an der zweiten Steuerfläche F2 wiederum während des Einschaltvorgangs des Hochspannungsleistungsschalters 7 auftritt, wird dieser Einschaltvorgang stark verlangsamt. Eine derartige langsame Einschaltung wird ebenfalls als maßgeblicher Funktionsfehler des hybrid-mechanischen Antriebs eingestuft.If the flow change on the second control surface F2 again occurs during the switching-on process of the high-voltage circuit breaker 7, this switching-on process is greatly slowed down. Such slow activation is also classified as a significant malfunction of the hybrid mechanical drive.

Aufgabe der Erfindung ist es, eine Ventilanordnung zur hydraulischen Ansteuerung einer Kolben-Zylinderanordnung eines Hoch- oder Mittelspannungsleistungsschalters anzugeben, mit der die oben beschriebenen Probleme einer ungewollten bzw. langsamen Ausschaltung oder einer langsamen Einschaltung des Hochspannungsleistungsschalters behoben werden kann.The object of the invention is to provide a valve arrangement for the hydraulic control of a piston-cylinder arrangement of a high or medium voltage circuit breaker, with which the problems described above of an unwanted or slow opening or a slow switching on of the high voltage circuit breaker can be remedied.

Diese Aufgabe wird erfindungsgemäß gelöst durch die Merkmale des Anspruchs 1.According to the invention, this object is achieved by the features of claim 1.

Ausgegangen wird dabei von der bekannten zweistufigen Ventilanordnung nach Figur 1 bzw. 2 zur hydraulischen Ansteuerung eines Kolbens in einem Zylinder eines Hoch- oder Mittelspannungsleistungsschalters, umfassend

  • eine Hauptstufe mit einem als 2/2-Wegeventil ausgeführten ersten Hauptventil und einem als 2/2-Wegeventil ausgeführten zweiten Hauptventil, wobei eine, ein im Betriebszustand der Ventilanordnung unter Hochdruck stehendes Fluid führende, Hochdruckleitung (P) direkt mit einem eingangsseitigen Ventilanschluss des ersten Hauptventils verbunden ist, und wobei eine, ein unter Niederdruck stehendes Fluid führende, Niederdruckleitung direkt mit einem eingangsseitigen Ventilanschluss des zweiten Hauptventils verbunden ist, und
  • eine Vorsteuerstufe mit mindestens einem Vorsteuerventil, welche eingangsseitig zwei Anschlüsse aufweist, wobei einer der Anschlüsse mit der Hochdruckleitung und der andere der Anschlüsse mit der Niederdruckleitung verbunden ist, wobei
  • ein ausgangsseitiger Ventilanschluss des ersten Hauptventils und ein ausgangsseitiger Ventilanschluss des zweiten Hauptventils miteinander und mit einem auf einer Seite des Kolbens befindlichen Raum hydraulisch verbunden sind,
  • ein hydraulischer Vorsteuerausgang der Vorsteuerstufe sowohl mit einer öffnend wirkenden ersten Steuerfläche des ersten Hauptventils als auch mit einer schließend wirkenden ersten Steuerfläche des zweiten Hauptventils verbunden ist,
  • die Vorsteuerstufe in einer ersten Stellung des mindestens einen Vorsteuerventils eine Verbindung zwischen der Hochdruckleitung und dem hydraulischen Vorsteuerausgang herstellt, wodurch der auf die ersten Steuerflächen der Hauptventile wirkende Hochdruck ein Öffnen des ersten Hauptventils und ein Schließen des zweiten Hauptventils bewirkt, so dass dem auf einer Seite des Kolbens befindlichen Raum unter Hochdruck stehendes Fluid zugeführt wird, und
  • die Vorsteuerstufe in einer zweiten Stellung des mindestens einen Vorsteuerventils eine Verbindung zwischen der Niederdruckleitung und dem hydraulischen Vorsteuerausgang herstellt, wodurch der auf die ersten Steuerflächen der Hauptventile wirkende Niederdruck ein Schließen des ersten Hauptventils und ein Öffnen des zweiten Hauptventils bewirkt, so dass aus dem auf einer Seite des Kolbens befindlichen Raum Fluid in Richtung Niederdruckleitung abgeführt wird.
This is based on the known two-stage valve arrangement Figure 1 or 2 for the hydraulic control of a piston in a cylinder of a high or medium voltage circuit breaker, comprising
  • a main stage with a first main valve designed as a 2/2-way valve and a second main valve designed as a 2/2-way valve, a high-pressure line (P) carrying a fluid under high pressure in the operating state of the valve arrangement directly with an inlet-side valve connection of the first Main valve is connected, and wherein a, a low pressure fluid carrying low pressure line is directly connected to an inlet valve port of the second main valve, and
  • a pilot stage with at least one pilot valve, which has two connections on the input side, one of the connections being connected to the high pressure line and the other of the connections being connected to the low pressure line, wherein
  • an outlet-side valve connection of the first main valve and an outlet-side valve connection of the second main valve are hydraulically connected to one another and to a space on one side of the piston,
  • a hydraulic pilot control output of the pilot stage is connected both to an opening-acting first control surface of the first main valve and to a closing-acting first control surface of the second main valve,
  • the pilot stage in a first position of the at least one pilot valve establishes a connection between the high pressure line and the hydraulic pilot control output, whereby the high pressure acting on the first control surfaces of the main valves causes the first main valve to open and the second main valve to close, so that on one side fluid under high pressure is supplied to the piston, and
  • the pilot stage in a second position of the at least one pilot valve establishes a connection between the low-pressure line and the hydraulic pilot-control output, whereby the low pressure acting on the first control surfaces of the main valves causes the first main valve to close and the second main valve to open, so that on a Side of the piston located fluid is discharged towards the low pressure line.

Gemäß der Erfindung weist das erste Hauptventil insgesamt vier Steuerflächen auf, also zusätzlich zur ersten Steuerfläche des Hauptventils noch drei weitere Steuerflächen, von denen eine zweite und eine dritte Steuerfläche des ersten Hauptventils schließend wirken und eine vierte Steuerfläche des ersten Hauptventils öffnend wirkt. Dabei ist die zweite Steuerfläche des ersten Hauptventils an die Hochdruckleitung angeschlossen; die dritte Steuerfläche des ersten Hauptventils ist an die Niederdruckleitung angeschlossen; und die vierte Steuerfläche des ersten Hauptventils ist mit dem ausgangsseitigen Ventilanschluss des ersten Hauptventils verbunden.According to the invention, the first main valve has a total of four control surfaces, that is, in addition to the first control surface of the main valve, three further control surfaces, of which a second and a third control surface of the first main valve have a closing effect and a fourth control surface of the first main valve has an opening effect. The second control surface of the first main valve is connected to the high pressure line; the third control surface of the first main valve is connected to the low pressure line; and the fourth control surface of the first main valve is connected to the outlet-side valve connection of the first main valve.

Das Größenverhältnis der öffnend wirkenden zu den schließend wirkenden Steuerflächen des ersten Hauptventils verhält sich dabei so, dass im geöffneten Zustand des ersten Hauptventils eine öffnend wirkende resultierende Kraft bestehen bleibt. Letzteres steht im Gegensatz zur bekannten Ausgestaltung nach Fig. 2, bei der es nach Erreichen des geöffneten Zustands des ersten Hauptventils 1 zu einem Kräftegleichgewicht zwischen öffnend und schließend wirkenden Kräften am ersten Hauptventil kommt, so dass Druckschwankungen zu einem unerwünschten Schließen führen können.The size ratio of the opening to the closing control surfaces of the first main valve behaves in such a way that an opening force resulting in the opening state of the first main valve remains. The latter is in contrast to the known design Fig. 2 , in which, after reaching the open state of the first main valve 1, there is a balance of forces between opening and closing forces on the first main valve, so that pressure fluctuations can lead to undesired closing.

Mit anderen Worten beinhaltet das erste Hauptventil der vorliegenden Erfindung nun vier anstelle der bekannten drei Steuer- oder Wirkflächen. Von den vier Steuerflächen wirken zwei schließend und zwei öffnend. Zusätzlich wird eine der schließend wirkenden Steuerflächen permanent mit der Niederdruckleitung und darüber mit dem Niederdrucktank verbunden. Die Größen der öffnend wirkenden Steuerflächen sind dabei im Verhältnis zu den Größen der schließend wirkenden Steuerflächen so gewählt, dass das erste Hauptventil auch bei Druckschwankungen sicher im geöffneten Zustand verbleibt.In other words, the first main valve of the present invention now includes four instead of the known three control or active surfaces. Of the four control surfaces, two are closing and two are opening. In addition, one of the closing control surfaces is permanently connected to the low pressure line and above it to the low pressure tank. The sizes of the opening control surfaces are selected in relation to the sizes of the closing control surfaces so that the first main valve remains securely in the open state even in the event of pressure fluctuations.

In einer Ausgestaltung ist die Summe aus der Größe der ersten und der Größe der vierten Steuerfläche des ersten Hauptventils größer als die Größe der zweiten Steuerfläche des ersten Hauptventils, wobei in einer besonders bevorzugten Ausgestaltung die Summe aus der Größe der ersten und der Größe der vierten Steuerfläche des ersten Hauptventils genauso groß ist wie die Summe aus der Größe der zweiten und der Größe der dritten Steuerfläche des ersten Hauptventils. Da die dritte Steuerfläche dauerhaft mit der Niederdruckleitung verbunden ist, befinden sich im geöffneten Zustand des ersten Hauptventils nur die erste, zweite und vierte Steuerfläche auf Hochdruck. Sollte es zu unerwünschten Druckerhöhungen an der direkt mit der Hochdruckleitung verbundenen zweiten Steuerfläche kommen, so genügt die öffnende Wirkung der zusammen größeren, und dabei insbesondere der um den Betrag der Größe der dritten Steuerfläche vergrößerten, ersten und vierten Steuerflächen aus, um ein unerwünschtes Schließen des ersten Hauptventils zu vermeiden.In one configuration, the sum of the size of the first and the size of the fourth control surface of the first main valve is larger than the size of the second control surface of the first main valve, in a particularly preferred configuration the sum of the size of the first and the size of the fourth control surface of the first main valve is the same as the sum of the size of the second and the size of the third control surface of the first main valve. Since the third control surface is permanently connected to the low-pressure line, only the first, second and fourth control surfaces are at high pressure when the first main valve is open. Should there be undesirable pressure increases on the second control surface connected directly to the high-pressure line, the opening effect of the larger together, and in particular the amount of the size of the, is sufficient third control surface enlarged, first and fourth control surfaces to avoid undesired closing of the first main valve.

In einer weiteren Ausgestaltung ist die zweite Steuerfläche des ersten Hauptventils mindestens so groß wie die vierte Steuerfläche des ersten Hauptventils. Auf diese Weise wird sichergestellt, dass die schließende Wirkung der zweiten Steuerfläche ausreicht, um direkt nach Anlegen des Niederdrucks an die erste Steuerfläche die öffnende Wirkung der vierten Steuerfläche zu überwinden und das Schließen des ersten Hauptventils einzuleiten.In a further embodiment, the second control surface of the first main valve is at least as large as the fourth control surface of the first main valve. This ensures that the closing effect of the second control surface is sufficient to overcome the opening effect of the fourth control surface and to initiate the closing of the first main valve immediately after the low pressure is applied to the first control surface.

In einer weiteren Ausführung ist das zweite Hauptventil mit einer federkraftbasierten Rastierung versehen, die im geöffneten Zustand des zweiten Hauptventils einrastet. Auf diese Weise wird sichergestellt, dass das zweite Hauptventil auch nach dem Ausschalten des Hochspannungsleistungsschalters, wenn das zweite Hauptventil komplett drucklos ist, in geöffnetem Zustand verbleibt. Dieses gewünschte Verhalten wird auch als Schaltstellungsgedächtnis bezeichnet. Bei nicht vorhandener Rastierung würde ansonsten das zweite Hauptventil durch die im Ventil vorhandene Rückstellfeder automatisch geschlossen werden.In a further embodiment, the second main valve is provided with a spring force-based detent which engages when the second main valve is open. This ensures that the second main valve remains in the open state even after the high-voltage circuit breaker has been switched off, when the second main valve is completely depressurized. This desired behavior is also referred to as switch position memory. If there is no detent, the second main valve would otherwise be closed automatically by the return spring in the valve.

In einer weiteren Ausführung sind das erste und/oder das zweite Hauptventil mit einer manuellen Rückstellmöglichkeit, das heißt einer manuell betätigbaren Rückstellmöglichkeit versehen. Auf diese Weise wird ein Nachteil der bekannten Ventilanordnungen nach Fig. 1 bzw. Fig. 2 beseitigt, welcher im Zusammenhang mit einem Transport, beispielsweise bei Auslieferung des Leistungsschalter-Antriebs, auftreten kann. Während des Transports befindet sich die gesamte zweistufige Ventilanordnung im drucklosen Zustand, weshalb die beiden Hauptventile lediglich durch ihre eigene Federrastierung bzw. Rückstellfeder in den jeweiligen Schaltstellungen gehalten werden. Sollte sich eines bzw. beide der Hauptventile in eine Zwischenstellung begeben, beispielsweise ausgelöst durch Vibration oder Schockbelastung, könnte die Situation auftreten, dass beide Hauptventile gleichzeitig durchlässig wären. In diesem Fall könnte die zweistufige Ventilanordnung und damit der Antrieb nicht mehr in Betrieb genommen werden, da kein Druck aufgebaut werden kann. Statt dessen würde eine Pumpe das Fluid, welches üblicherweise ein Hydrauliköl ist, lediglich im Kreis fördern, da die Hauptventile einen direkten Durchfluss von der Hochdruckleitung zur Niederdruckleitung, d.h. vom eigentlichen Hochdruckbereich in den Niederdrucktank, gestatten würden.In a further embodiment, the first and / or the second main valve are provided with a manual reset option, that is to say a manually operable reset option. In this way, a disadvantage of the known valve arrangements after Fig. 1 respectively. Fig. 2 eliminated, which can occur in connection with transport, for example when the circuit breaker drive is delivered. During transport, the entire two-stage valve arrangement is in the depressurized state, which is why the two main valves are held in the respective switching positions only by their own spring catch or return spring. Should one or both of the main valves move into an intermediate position, for example triggered by vibration or shock, the situation could arise that both main valves would be permeable at the same time. In this case, the two-stage valve arrangement and thus the drive could no longer be put into operation since no pressure can be built up. Instead, a pump would take the fluid, which is usually a hydraulic oil, only pump in a circuit, since the main valves would allow a direct flow from the high pressure line to the low pressure line, ie from the actual high pressure area into the low pressure tank.

Mittels der manuellen Rückstellmöglichkeit kann nun das von vibrationsbedingtem Verstellen betroffene Hauptventil wieder in seine Ausgangslage zurückverbracht werden, so dass die Inbetriebnahme ungehindert stattfinden kann.Using the manual reset option, the main valve affected by vibration-related adjustment can now be returned to its starting position, so that commissioning can take place without hindrance.

Anhand der in den weiteren Zeichnungen dargestellten Ausführungsbeispiele sollen die Erfindung und ihre mögliche Ausgestaltung näher beschrieben werden.The invention and its possible configuration are to be described in more detail with reference to the exemplary embodiments illustrated in the further drawings.

Es zeigen:

Fig. 1
eine erste bekannte zweistufige Ventilanordnung zur Betätigung eines Kolbens und damit eines Hochspannungsleistungsschalters;
Fig. 2
eine zweite bekannte zweistufige Ventilanordnung mit einer Blende zur Abführung eines Leckagestroms;
Fig. 3
eine dritte zweistufige Ventilanordnung gemäß der Erfindung;
Fig. 4
eine Ausführung des ersten Hauptventils aus Fig. 3;
Fig. 5
eine Ausführung des zweiten Hauptventils aus Fig. 3.
Show it:
Fig. 1
a first known two-stage valve arrangement for actuating a piston and thus a high-voltage circuit breaker;
Fig. 2
a second known two-stage valve arrangement with an orifice for discharging a leakage flow;
Fig. 3
a third two-stage valve arrangement according to the invention;
Fig. 4
execution of the first main valve Fig. 3 ;
Fig. 5
an execution of the second main valve Fig. 3 ,

Figur 3 zeigt eine mögliche Ausführung einer zweistufigen Ventilanordnung gemäß der Erfindung. Die zweistufige Ventilanordnung dient der hydraulischen Ansteuerung eines Kolbens 6 in einem Zylinder 12 eines Hoch- oder Mittelspannungsleistungsschalters 7. Die zweistufige Ventilanordnung umfasst dabei eine Hauptstufe mit zwei 2/2-Wegeventilen, welche als erstes Hauptventil 31 und als zweites Hauptventil 32 bezeichnet werden, sowie eine Vorsteuerstufe mit zwei 2/2-Wegeventilen, welche als erstes Vorsteuerventil 3 und als zweites Vorsteuerventil 4 bezeichnet werden. Gleiche Bezugszeichen werden dabei für die mit den Figuren 1 und 2 übereinstimmenden Elemente verwendet. Figure 3 shows a possible embodiment of a two-stage valve arrangement according to the invention. The two-stage valve arrangement is used for the hydraulic control of a piston 6 in a cylinder 12 of a high or medium voltage circuit breaker 7. The two-stage valve arrangement comprises a main stage with two 2/2-way valves, which are referred to as the first main valve 31 and the second main valve 32, and a pilot stage with two 2/2-way valves, which are referred to as the first pilot valve 3 and as the second pilot valve 4. The same reference numerals are used for those with the Figures 1 and 2 matching elements used.

Eine Hochdruckleitung P, welche ein unter Hochdruck stehendes Fluid führt, ist direkt mit einem eingangsseitigen Ventilanschluss 33 des ersten Hauptventils 31 verbunden und wird aus einem Hochdruckspeicher 9 gespeist. Das Fluid ist bevorzugt ein Hydrauliköl, kann aber beispielsweise auch Druckluft sein. Eine Niederdruckleitung T ist direkt mit einem eingangsseitigen Ventilanschluss 34 des zweiten Hauptventils 32 verbunden, wobei die Niederdruckleitung T das unter Niederdruck stehende Fluid führt und mit einem Niederdrucktank 8 verbunden ist.A high-pressure line P, which carries a fluid under high pressure, is connected directly to an inlet-side valve connection 33 of the first main valve 31 and is fed from a high-pressure accumulator 9. The fluid is preferably a hydraulic oil, but can also be compressed air, for example. A low pressure line T is connected directly to an inlet-side valve connection 34 of the second main valve 32, the low-pressure line T carrying the fluid under low pressure and being connected to a low-pressure tank 8.

Die Vorsteuerstufe weist eingangsseitig zwei Anschlüsse auf, wobei einer der Anschlüsse, und zwar der eingangsseitige Anschluss 37 des ersten Vorsteuerventils 3, mit der Hochdruckleitung P verbunden ist, und wobei der andere der Anschlüsse, nämlich der eingangsseitige Anschluss 38 des zweiten Vorsteuerventils 4, mit der Niederdruckleitung T verbunden ist.The pilot stage has two connections on the input side, one of the connections, namely the input side connection 37 of the first pilot control valve 3, being connected to the high-pressure line P, and the other of the connections, namely the input side connection 38 of the second pilot control valve 4, being connected to the Low pressure line T is connected.

Ein ausgangsseitiger Ventilanschluss 35 des ersten Hauptventils 31 und ein ausgangsseitiger Ventilanschluss 36 des zweiten Hauptventils 32 sind miteinander an einem hydraulischen Verbindungsknoten Z verbunden, und darüber mit einem auf einer Seite des Kolbens 6 befindlichen Raum 10, d.h. die ausgangsseitigen Ventilanschlüsse 35, 36 der Hauptventile 31, 32 speisen direkt in den Raum 10 ein.An outlet-side valve connection 35 of the first main valve 31 and an outlet-side valve connection 36 of the second main valve 32 are connected to one another at a hydraulic connection node Z, and above that to a space 10 located on one side of the piston 6, i.e. the outlet-side valve connections 35, 36 of the main valves 31, 32 feed directly into the space 10.

Die Vorsteuerstufe besitzt einen hydraulischen Vorsteuerausgang X, welcher jeweils mit dem ausgangsseitigen Anschluss des ersten und zweiten Vorsteuerventils 3, 4 verbunden ist. Der Vorsteuerausgang X wiederum ist mit einer öffnend wirkenden ersten Steuerfläche F4 des ersten Hauptventils 31 und mit einer schließend wirkenden ersten Steuerfläche F8 des zweiten Hauptventils 32 verbunden.The pilot control stage has a hydraulic pilot control output X, which is connected to the output-side connection of the first and second pilot control valves 3, 4. The pilot control output X is in turn connected to an opening first control surface F4 of the first main valve 31 and to a closing first control surface F8 of the second main valve 32.

In einer ersten Stellung der Vorsteuerventile 3, 4 stellt die Vorsteuerstufe eine Verbindung zwischen der Hochdruckleitung P und dem hydraulischen Vorsteuerausgang X her. In dieser ersten Stellung ist das erste Vorsteuerventil 3 geöffnet und das zweite Vorsteuerventil 4 geschlossen. Der daraufhin auf die ersten Steuerflächen F4, F8 der Hauptventile 31, 32 wirkende Hochdruck bewirkt ein Öffnen des ersten Hauptventils 31 und ein Schließen des zweiten Hauptventils 32, so dass dem auf einer Seite des Kolbens 6 befindlichen Raum 10 das unter Hochdruck stehende Fluid zugeführt wird, wodurch der Hoch- oder Mittelspannungsleistungsschalter 7 eingeschaltet, also geschlossen, wird.In a first position of the pilot valves 3, 4, the pilot stage establishes a connection between the high pressure line P and the hydraulic pilot control output X. In this first position, the first pilot valve 3 is open and the second pilot valve 4 is closed. The high pressure then acting on the first control surfaces F4, F8 of the main valves 31, 32 causes the first main valve 31 to open and the second main valve 32 to close, so that the fluid under high pressure is supplied to the space 10 on one side of the piston 6 , whereby the high or medium voltage circuit breaker 7 is turned on, that is closed.

Die Vorsteuerstufe stellt in einer zweiten Stellung der Vorsteuerventile 3, 4 eine Verbindung zwischen der Niederdruckleitung T und dem hydraulischen Vorsteuerausgang X her. In dieser zweiten Stellung ist das erste Vorsteuerventil 3 geschlossen und das zweite Vorsteuerventil 4 geöffnet. Der daraufhin auf die ersten Steuerflächen F4, F8 der Hauptventile 31, 32 wirkende Niederdruck bewirkt ein Schließen des ersten Hauptventils 31 und ein Öffnen des zweiten Hauptventils 32, so dass aus dem auf einer Seite des Kolbens 6 befindlichen Raum 10 Fluid in Richtung Niederdruckleitung T abgeführt wird, was zum Ausschalten, also Öffnen, des Hoch- oder Mittelspannungsleistungsschalters 7 führt.In a second position of the pilot valves 3, 4, the pilot stage establishes a connection between the low-pressure line T and the hydraulic pilot control output X. In this second position, the first pilot valve 3 is closed and the second pilot valve 4 is open. The low pressure then acting on the first control surfaces F4, F8 of the main valves 31, 32 causes the first main valve 31 to close and the second main valve 32 to open, so that fluid is discharged from the space 10 on one side of the piston 6 in the direction of the low pressure line T. becomes, which leads to switching off, ie opening, of the high or medium voltage circuit breaker 7.

Erfindungsgemäß weist das erste Hauptventil 31 drei weitere Steuerflächen auf, wie auch der Figur 4 zu entnehmen ist, welche eine mögliche Ausführung des ersten Hauptventils 31 zeigt. Neben der ersten Steuerfläche F4 des ersten Hauptventils, welche öffnend wirkt, gibt es eine zweite und eine dritte Steuerfläche, F5 und F6, des ersten Hauptventils, welche beide schließend wirken. Eine vierte Steuerfläche F7 des ersten Hauptventils wirkt wiederum öffnend.According to the invention, the first main valve 31 has three further control surfaces, as does the one Figure 4 It can be seen which shows a possible embodiment of the first main valve 31. In addition to the first control surface F4 of the first main valve, which has an opening effect, there are a second and a third control surface, F5 and F6, of the first main valve, both of which have a closing effect. A fourth control surface F7 of the first main valve in turn has an opening effect.

Die zweite Steuerfläche F5 des ersten Hauptventils ist innerhalb der zweistufigen Ventilanordnung an die Hochdruckleitung P angeschlossen; die dritte Steuerfläche F6 des ersten Hauptventils ist an die Niederdruckleitung T angeschlossen, und die vierte Steuerfläche F7 des ersten Hauptventils ist mit dem ausgangsseitigen Ventilanschluss 35 des ersten Hauptventils 31 verbunden.The second control surface F5 of the first main valve is connected to the high-pressure line P within the two-stage valve arrangement; the third control surface F6 of the first main valve is connected to the low-pressure line T, and the fourth control surface F7 of the first main valve is connected to the outlet-side valve connection 35 of the first main valve 31.

Gemäß der Erfindung verhält sich das Größenverhältnis der öffnend wirkenden Steuerflächen, F4 und F7, zu den schließend wirkenden Steuerflächen, F5 und F6, des ersten Hauptventils so, dass im geöffneten Zustand des ersten Hauptventils eine öffnend wirkende resultierende Kraft bestehen bleibt, so dass das erste Hauptventil 31 sicher im geöffneten Zustand verbleibt, selbst wenn es in der Hochdruckleitung P zu Druckschwankungen kommen sollte.According to the invention, the ratio of the size of the opening control surfaces, F4 and F7, to the closing control surfaces, F5 and F6, of the first main valve is such that when the first main valve is open, an opening force remains, so that the first Main valve 31 remains securely in the open state, even if pressure fluctuations occur in the high-pressure line P.

Im Folgenden soll die Flächengröße der ersten Steuerfläche F4 des ersten Hauptventils mit AF4 bezeichnet werden, und analog die Flächengrößen der übrigen Steuerflächen F5, F6, F7 des ersten Hauptventils mit AF5, AF6 und AF7. In der Ausführung nach Figur 4 sind die Flächengrößen AF4, AF5, AF6 und AF7 so gewählt, dass die Summe aus der Größe der ersten (AF4) und der Größe der vierten (AF7) Steuerfläche des ersten Hauptventils genauso groß ist wie die Summe aus der Größe der zweiten (AF5) und der Größe der dritten (AF6) Steuerfläche des ersten Hauptventils, also AF4 + AF7 = AF5 + AF6. Damit ist auch gleichzeitig die Bedingung erfüllt, dass die Summe aus der Größe der ersten (AF4) und der Größe der vierten (AF7) Steuerfläche des ersten Hauptventils größer ist als die Größe der zweiten Steuerfläche (AF5), also AF4 + AF7 > AF5. Außerdem ist die zweite Steuerfläche des ersten Hauptventils mindestens so groß ist wie die vierte Steuerfläche des ersten Hauptventils, also AF5 ≥ AF7. Durch ersteres Größenverhältnis wird in der Ausgestaltung nach Fig. 4 sichergestellt, dass im geöffneten Zustand des ersten Hauptventils 31, wenn an der ersten (F4), zweiten (F5) und vierten (F7) Steuerfläche Hochdruck anliegt, eine unerwartete Vergrößerung des Druckes an der zweiten Steuerfläche F5 nicht zu einem unerwünschten Schließen des ersten Hauptventils führt. Das letztere Größenverhältnis sorgt dafür, dass zu Beginn eines gewünschten Schließvorgangs des ersten Hauptventils 31, wenn an der ersten Steuerfläche F4 von Hochdruck auf Niederdruck gewechselt wird, der Hochdruck an der zweiten Steuerfläche F5 ausreicht, um den Schließvorgang einzuleiten.In the following, the area size of the first control surface F4 of the first main valve is to be designated AF4, and analogously the area sizes of the other control areas F5, F6, F7 of the first main valve are designated AF5, AF6 and AF7. In execution after Figure 4 the area sizes AF4, AF5, AF6 and AF7 are selected so that the sum of the size of the first (AF4) and the size of the fourth (AF7) control surface of the first main valve is as large as the sum of the size of the second (AF5) and the size of the third (AF6) control surface of the first main valve, that is AF4 + AF7 = AF5 + AF6. This also fulfills the condition that the sum of the size of the first (AF4) and the size of the fourth (AF7) control surface of the first main valve is larger than the size of the second control surface (AF5), i.e. AF4 + AF7> AF5. In addition, the second control surface of the first main valve is at least as large as the fourth control surface of the first main valve, that is AF5 ≥ AF7. Due to the former size ratio, the design is based on Fig. 4 ensures that in the open state of the first main valve 31, when high pressure is applied to the first (F4), second (F5) and fourth (F7) control surface, an unexpected increase in the pressure at the second control surface F5 does not lead to an undesired closing of the first main valve leads. The latter size ratio ensures that at the start of a desired closing operation of the first main valve 31, when changing from high pressure to low pressure on the first control surface F4, the high pressure on the second control surface F5 is sufficient to initiate the closing operation.

Wie in den Figuren 3 und 4 dargestellt, weist das erste Hauptventil 31 darüber hinaus eine federkraftbasierte Rastierung 40 auf, welche dafür sorgt, dass das erste Hauptventil 31 im geöffneten Zustand möglichst sicher verbleibt, bis eine ausreichend große Schließkraft dagegen wirkt.As in the Figures 3 and 4 shown, the first main valve 31 also has a spring force-based detent 40, which ensures that the first main valve 31 remains as safe as possible in the open state until a sufficiently large closing force acts against it.

Darüber hinaus ist das erste Hauptventil 31 mit einer manuellen Rückstellmöglichkeit 42 versehen, mit deren Hilfe das erste Hauptventil nach einem transportbedingten Verstellen wieder in den geschlossenen Zustand verbracht werden kann.In addition, the first main valve 31 is provided with a manual reset option 42, by means of which the first main valve can be brought back into the closed state after being adjusted for transport.

In Figur 5 ist eine mögliche Ausgestaltung des zweiten Hauptventils 32 dargestellt. Dieses weist insgesamt drei Steuerflächen auf, also neben der ersten Steuerfläche F8 eine zweite Steuerfläche F9 des zweiten Hauptventils, sowie eine dritte Steuerfläche F10 des zweiten Hauptventils. In der zweistufigen Ventilanordnung nach Fig. 3 ist die zweite Steuerfläche F9 des zweiten Hauptventils an die Niederdruckleitung T angeschlossen, und die dritte Steuerfläche F10 des zweiten Hauptventils ist mit dem ausgangsseitigen Ventilanschluss 36 des zweiten Hauptventils 32 verbunden.In Figure 5 A possible embodiment of the second main valve 32 is shown. This has a total of three control surfaces, that is, in addition to the first control surface F8, a second control surface F9 of the second main valve and a third control surface F10 of the second main valve. According to the two-stage valve arrangement Fig. 3 the second control surface F9 of the second main valve is connected to the low-pressure line T, and the third control surface F10 of the second main valve is connected to the outlet-side valve connection 36 of the second main valve 32.

Auch das zweite Hauptventil 32 ist mit einer federkraftbasierten Rastierung 39 versehen ist, die im geöffneten Zustand des zweiten Hauptventils einrastet. Diese federkraftbasierte Rastierung 39 wirkt dabei insbesondere dem Krafteinfluss der Rückstellfeder 41 entgegen, so dass auf diese Weise ein Schaltstellungsgedächtnis realisiert werden kann, d.h. das zweite Hauptventil wird auch nach dem Ausschalten des Hoch- oder Mittelspannungsleistungsschalters 7, wenn das zweite Hauptventil komplett drucklos ist, in geöffnetem Zustand gehalten.The second main valve 32 is also provided with a spring force-based detent 39, which engages when the second main valve is open. This spring force-based detent 39 counteracts in particular the force influence of the return spring 41, so that a switch position memory can be realized in this way, i.e. the second main valve is kept in the open state even after the high or medium voltage circuit breaker 7 has been switched off, when the second main valve is completely depressurized.

Die Rückstellfeder 41 ist beim zweiten Hauptventil 32 der Fig. 5 noch durch eine manuelle Rückstellmöglichkeit 42 ergänzt, so dass auch das zweite Hauptventil nach einem transportbedingten Verstellen und unerwünschten Einrasten der Rastierung 39 wieder in den geschlossenen Zustand verbracht werden kann.The return spring 41 is in the second main valve 32 Fig. 5 supplemented by a manual reset option 42, so that the second main valve can also be brought back into the closed state after a transport-related adjustment and undesired engagement of the detent 39.

Claims (8)

  1. Two-stage valve arrangement for the hydraulic actuation of a piston (6) in a cylinder (12) of a high voltage or medium voltage circuit breaker (7), comprising
    • a main stage with a first main valve (31) which is configured as a 2/2-way valve and a second main valve (32) which is configured as a 2/2-way valve, a high pressure line (P) which conducts a fluid under high pressure being connected directly to an inlet-side valve connector (33) of the first main valve (31), and a low pressure line (T) which conducts a fluid under low pressure being connected directly to an inlet-side valve connector (34) of the second main valve (32), and
    • a pilot control stage with at least one pilot control valve (3, 4), which pilot control stage has two connectors (37, 38) on the inlet side, one of the two connectors (37) being connected to the high pressure line (P), and the other one of the two connectors (38) being connected to the low pressure line (T),
    • an outlet-side valve connector (35) of the first main valve (31) and an outlet-side valve connector (36) of the second main valve (32) being connected hydraulically to one another (Z) and to a space (10) which is situated on one side of the piston (6),
    • a hydraulic pilot control outlet (X) of the pilot control stage being connected both to a first control face (F4) of the first main valve (31), which first control face (F4) acts in an opening manner, and to a first control face (F8) of the second main valve (32), which first control face (F8) acts in a closing manner,
    • the pilot control stage establishing, in a first position of the at least one pilot control valve (3, 4), a connection between the high pressure line (P) and the hydraulic pilot control outlet (X), as a result of which the high pressure which acts on the first control face (F4) of the first main valve (31) and on the first control face (F8) of the second main valve (32) brings about opening of the first main valve (31) and closing of the second main valve (32), with the result that fluid under high pressure is fed to the space (10) which is situated on one side of the piston (6), and
    • the pilot control stage establishing, in a second position of the at least one pilot control valve (3, 4), a connection between the low pressure line (T) and the hydraulic pilot control outlet (X), as a result of which the low pressure which acts on the first control face (F4) of the first main valve (31) and on the first control face (F8) of the second main valve (32) brings about closing of the first main valve (31) and opening of the second main valve (32), with the result that fluid is discharged from the space (10) which is situated on one side of the piston (6) in the direction of the low pressure line (T), characterized in that
    • the first main valve (31) has three further control faces (F5, F6, F7), of which a second control face (F5) of the first main valve (31) and a third control face (F6) of the first main valve (31) act in a closing manner, and a fourth control face (F7) of the first main valve (31) acts in an opening manner,
    • the second control face (F5) of the first main valve (31) being connected to the high pressure line (P),
    • the third control face (F6) of the first main valve (31) being connected to the low pressure line (T),
    • the fourth control face (F7) of the first main valve (31) being connected to the outlet-side valve connector (35) of the first main valve (31), and
    • the size ratio of the control faces (F4, F7) of the first main valve (31) which act in an opening manner to the control faces (F5, F6) of the first main valve (31) which act in a closing manner being such that a resulting force which acts in an opening manner remains in force in the open state of the first main valve (31).
  2. Two-stage valve arrangement according to Claim 1, characterized in that the sum of the area size of the first control face (AF4) of the first main valve (31) and the area size of the fourth control face (AF7) of the first main valve (31) is greater than the area size of the second control face (AF5) of the first main valve (31).
  3. Two-stage valve arrangement according to Claim 2, characterized in that the sum of the area size of the first control face (AF4) of the first main valve (31) and the area size of the fourth control face (AF7) of the first main valve (31) is as great as the sum of the area size of the second control face (AF5) of the first main valve (31) and the area size of the third control face (AF6) of the first main valve (31).
  4. Two-stage valve arrangement according to one of the preceding claims, characterized in that the second control face (AF5) of the first main valve (31) is at least as large as the fourth control face (AF7) of the first main valve (31).
  5. Two-stage valve arrangement according to one of the preceding claims, characterized in that the second main valve (32) is provided with a spring force-based latching means (39) which latches in the open state of the second main valve (32).
  6. Two-stage valve arrangement according to one of the preceding claims, characterized in that the first main valve (31) and/or the second main valve (32) are/is provided with a manual restoring option (42, 43).
  7. Two-stage valve arrangement according to one of the preceding claims, characterized in that the second main valve (32) has two further control faces (F9, F10), of which a second control face (F9) of the second main valve (32) is connected to the low pressure line (T), and a third control face (F10) of the second main valve (32) is connected to the outlet-side valve connector (36) of the second main valve (32).
  8. Two-stage valve arrangement according to one of the preceding claims, characterized in that the pilot control stage comprises two 2/2-way valves as pilot control valves (3, 4).
EP16802110.3A 2015-12-14 2016-11-30 Double stage valve assembly for hydraulic control of a piston cylinder for a high or middle voltage switch Active EP3390840B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015121719.8A DE102015121719A1 (en) 2015-12-14 2015-12-14 Valve arrangement for the hydraulic control of a piston-cylinder arrangement of a high or medium voltage circuit breaker
PCT/EP2016/079284 WO2017102331A1 (en) 2015-12-14 2016-11-30 Two-stage valve arrangement for hydraulic control of a piston-cylinder arrangement of a high- or medium-voltage power switch

Publications (2)

Publication Number Publication Date
EP3390840A1 EP3390840A1 (en) 2018-10-24
EP3390840B1 true EP3390840B1 (en) 2020-01-01

Family

ID=57421881

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16802110.3A Active EP3390840B1 (en) 2015-12-14 2016-11-30 Double stage valve assembly for hydraulic control of a piston cylinder for a high or middle voltage switch

Country Status (5)

Country Link
US (1) US10830256B2 (en)
EP (1) EP3390840B1 (en)
CN (1) CN108603520B (en)
DE (1) DE102015121719A1 (en)
WO (1) WO2017102331A1 (en)

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3038449A (en) * 1959-06-03 1962-06-12 Gen Dynamics Corp Hydraulic control system
GB2041170B (en) 1979-01-25 1983-02-16 Lucas Industries Ltd Flow control valve
JPS5917074A (en) 1982-07-16 1984-01-28 Hitachi Constr Mach Co Ltd Logic valve
JPS59158026A (en) * 1983-02-28 1984-09-07 住友精密工業株式会社 Hydraulically operating circuit for breaker
AU603907B2 (en) * 1987-06-30 1990-11-29 Hitachi Construction Machinery Co. Ltd. Hydraulic drive system
US5816132A (en) * 1996-07-12 1998-10-06 Ross Operating Valve Company Load-sensing pneumatic control system
JP4178736B2 (en) * 2000-08-30 2008-11-12 株式会社デンソー Table feeding system
US6662705B2 (en) * 2001-12-10 2003-12-16 Caterpillar Inc Electro-hydraulic valve control system and method
US7021191B2 (en) * 2003-01-24 2006-04-04 Viking Technologies, L.C. Accurate fluid operated cylinder positioning system
US20080295681A1 (en) * 2007-05-31 2008-12-04 Caterpillar Inc. Hydraulic system having an external pressure compensator
DE102009014421A1 (en) 2009-03-26 2010-09-30 Abb Technology Ag valve assembly
DE102009017879A1 (en) * 2009-04-17 2010-10-21 Festo Ag & Co. Kg Fluidic system
DE102009053901B3 (en) 2009-11-20 2011-04-28 Abb Technology Ag valve assembly
US9250632B2 (en) * 2011-12-30 2016-02-02 Sti Srl Valve positioning system with bleed prevention
EP2933816B1 (en) 2014-04-16 2018-06-13 ABB Schweiz AG Hydraulic valve for preventing of leakages in a drive for actuating a high voltage or medium voltage circuit breaker

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN108603520A (en) 2018-09-28
WO2017102331A1 (en) 2017-06-22
EP3390840A1 (en) 2018-10-24
DE102015121719A1 (en) 2017-06-14
US10830256B2 (en) 2020-11-10
US20190017521A1 (en) 2019-01-17
CN108603520B (en) 2020-03-13

Similar Documents

Publication Publication Date Title
EP2234135B1 (en) Valve assembly
WO2011061041A1 (en) Valve arrangement
WO2015185607A1 (en) Hydraulic control device for a quick-acting valve of a steam turbine and steam turbine assembly
CH708877B1 (en) Hydraulic valve arrangement with control / regulation function and associated return valve.
EP3012463B1 (en) Hydraulic assembly
EP2672124A2 (en) Hydraulic system and pressure limiting valve
EP2642132B1 (en) Hydraulic valve assembly with hydraulic pilot valve assembly
DE102009035278A1 (en) Pressure booster and associated control valve
EP3390840B1 (en) Double stage valve assembly for hydraulic control of a piston cylinder for a high or middle voltage switch
EP3679254B1 (en) Valve
DE112008003999T5 (en) Fluid powered actuation system
EP0430089A1 (en) Actuator
EP3436705B1 (en) Control device
DE102008061238A1 (en) Hydraulic drive device for electrical switchgear, has servo controller with valve providing hydraulic control of hydraulic delay element, where drive device and another drive device are in fluid connection with one another
EP2933816A1 (en) Hydraulic valve for preventing of leakages in a drive for actuating a high voltage or medium voltage circuit breaker
DE4244304A1 (en) Actuating device for a hydraulic actuator with pressure-proportional control signal
DE102016212306A1 (en) Intermediate block and compact axle with an intermediate block
DE102015218576B4 (en) CONTROL UNIT
DE102014216034A1 (en) Valve arrangement with adjustable load feedback
DE102021005824B4 (en) safety valve device
DE102022201755A1 (en) Control slide with a defined broken ring edge
CH642770A5 (en) HYDRAULIC ACTUATOR FOR A HIGH VOLTAGE CIRCUIT BREAKER.
DE3000983C2 (en)
DE102021207837A1 (en) Method for operating a hydraulic machine with compensation of a flow force on the control slide
WO2005111430A1 (en) Hydraulic valve arrangement, in particular water hydraulic valve arrangement

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20180614

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
RIN1 Information on inventor provided before grant (corrected)

Inventor name: KLOSE, THOMAS

Inventor name: SCHMIDT, MATTHIAS E.

Inventor name: BRENNEIS, THOMAS

Inventor name: ROBENS, NIKO

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20190918

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KLOSE, THOMAS

Inventor name: BRENNEIS, THOMAS

Inventor name: ROBENS, NIKO

Inventor name: SCHMIDT, MATTHIAS E.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1220109

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200115

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502016008289

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200101

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200527

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200501

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200402

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502016008289

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Representative=s name: DENNEMEYER & ASSOCIATES S.A., DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502016008289

Country of ref document: DE

26N No opposition filed

Effective date: 20201002

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502016008289

Country of ref document: DE

Owner name: HITACHI ENERGY SWITZERLAND AG, CH

Free format text: FORMER OWNER: ABB SCHWEIZ AG, BADEN, CH

Ref country code: DE

Ref legal event code: R082

Ref document number: 502016008289

Country of ref document: DE

Representative=s name: DENNEMEYER & ASSOCIATES S.A., DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 502016008289

Country of ref document: DE

Owner name: ABB POWER GRIDS SWITZERLAND AG, CH

Free format text: FORMER OWNER: ABB SCHWEIZ AG, BADEN, CH

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20201130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20201130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502016008289

Country of ref document: DE

Owner name: HITACHI ENERGY SWITZERLAND AG, CH

Free format text: FORMER OWNER: ABB POWER GRIDS SWITZERLAND AG, BADEN, CH

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1220109

Country of ref document: AT

Kind code of ref document: T

Effective date: 20211130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211130

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230527

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20231121

Year of fee payment: 8