EP0074419A1 - Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique - Google Patents

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

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Publication number
EP0074419A1
EP0074419A1 EP81107195A EP81107195A EP0074419A1 EP 0074419 A1 EP0074419 A1 EP 0074419A1 EP 81107195 A EP81107195 A EP 81107195A EP 81107195 A EP81107195 A EP 81107195A EP 0074419 A1 EP0074419 A1 EP 0074419A1
Authority
EP
European Patent Office
Prior art keywords
valve body
valve
performance
cross
section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81107195A
Other languages
German (de)
English (en)
Other versions
EP0074419B1 (fr
Inventor
Rudolf Brunner
Siegfried Zenker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority to EP81107195A priority Critical patent/EP0074419B1/fr
Priority to DE8181107195T priority patent/DE3173448D1/de
Priority to AT81107195T priority patent/ATE17413T1/de
Publication of EP0074419A1 publication Critical patent/EP0074419A1/fr
Application granted granted Critical
Publication of EP0074419B1 publication Critical patent/EP0074419B1/fr
Expired legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H2033/308—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator comprising control and pilot valves

Definitions

  • the invention relates to an electrical high-performance disconnector with a hydraulic actuating device of the type specified in the preamble of the main claim.
  • 2/3-way seat valves are known for electrical high-performance disconnectors and their hydraulic actuation device (Heilmeier & Weinlein, Kunststoff, type designation: LSV 18), in which a section of the housing bore, the diameter of which corresponds to the diameter of the guide and sealing section of the valve body forming the control chamber into which the end part of the valve body protrudes.
  • the valve body has two spaced sealing surfaces that cooperate with the two valve seats on a sleeve insert in the housing bore to either establish a flow connection between the high pressure source and the side of the differential piston drive, which when loaded for closing or keeping the closed Disconnector is responsible, or to establish a second flow connection, with which this side of the differential piston drive is relieved to the return.
  • the control chamber is connected to the high-pressure source, either via a throttle bore in the valve body or via an external auxiliary control valve.
  • the control chamber can use a second auxiliary control valve in the first blocking position of the valve body with the return get connected.
  • the control chamber is in any case connected to the return via a throttle channel in the valve body and is depressurized.
  • High-performance electrical isolating switches are subject to extraordinary requirements when it comes to switching the isolating switch on or off.
  • the opening process must be completely completed in a few milliseconds, since if the isolating switch were to open slowly, the electrical power present would destroy the isolating switch or lead to an explosion with unforeseeable consequences.
  • the high-performance disconnector must function so reliably that only hydraulic devices which are characterized by particular reliability are used for its actuation.
  • Another important criterion in the design of a high-performance electrical isolating switch with its hydraulic actuating device is the requirement that the high-performance electrical isolating switch must remain in the position in which it is in the event of a failure of the hydraulic supply or when the hydraulic pressure supply is started up again has been before.
  • the invention has for its object to provide an electrical high-performance circuit breaker with a hydraulic actuator, in which an opening switching time for the high-performance circuit breaker can be achieved, which is shorter than the previously achievable.
  • DE-OS 2 213 244 discloses a high-performance isolating switch with a hydraulic actuating device, in which the 2/3 way poppet valve contains a valve body, the end parts of which are shaped into lugs, the diameter of which is approximately equal to the diameter of the valve seats , but is slightly smaller than the diameter of the guide and sealing sections.
  • the approach projecting into the control chamber serves as a mechanical stop for a spring-loaded and hydraulically piloted locking pin, with which the valve body is to be held in the first locking position as soon as an undesired pressure drop occurs.
  • the valve body In the area of the second approach, the valve body is provided with a through-hole, which creates a flow connection between the high-pressure source and the separated space of the housing bore into which this approach projects.-This means that to move the valve body into the first blocking position, the full cross-sectional area of the Guide and sealing section must be applied out of the control chamber or that inadvertently large hydraulic volume must be pressed out of the control chamber to open the disconnector. This large hydraulic volume means that the duration of the public voltage limit for the disconnector in the same way negatively limited, as was the case with the aforementioned prior art.
  • the second approach has no other function than to guide a spring pushing the valve body into the first blocking position and to effect a stop limitation.
  • control chamber is particularly well sealed from the housing bore and there is no mutual interference between the two spaces, an embodiment of the invention is expedient.
  • a further advantageous embodiment of the invention is set out in claim 3.
  • the second and projecting into the pressure chamber constantly generates a force on the valve body, which tries to move it into the second locking position. If the pressure is now reduced in the control chamber and the relatively small hydraulic quantity is rapidly discharged, the pressure prevailing at the other approach causes the valve body to be quickly shifted into the second blocking position and thus opens the disconnector.
  • only small hydraulic volumes need to be moved in the control chamber and in the pressure chamber, which reduces the technical effort for the poppet valve and also leads to a rapid changeover movement of the valve body.
  • the force exerted by the second approach is namely greater than the holding force for the valve body caused by the difference surface between the guide and sealing section and the valve seat. Again, only a small hydraulic volume has to be transported out of the control chamber to open the electrical high-performance disconnector, so that the switching time is desirably short.
  • valve seats and the guide sealing sections have the same diameter or cross section.
  • the housing bore can be formed continuously. Since the valve body is essentially pressure-balanced in this embodiment, the approaches have to provide the forces necessary for moving the valve body, which they do as a result of their different cross-sectional areas. If both paragraphs are pressurized are struck, the valve body is moved into the first blocking position. If, on the other hand, the control chamber is then relieved of pressure, only the force of the pressurization acts on the second attachment, which suddenly moves the valve body into the second blocking position.
  • a cross-sectional area ratio of 2: 1 is expediently selected in accordance with claim 7, which on the one hand ensures a correct switching of the valve body and on the other hand can still achieve small hydraulic volumes which are advantageous for the rapid opening of the disconnector.
  • the peg-like extensions dip into the valve seats and prevent the loss of hydraulic pressure medium, since they only allow the pressure medium to flow unhindered through a valve seat when the other valve seat is already largely closed by the other extension.
  • the peg-like extensions define precisely dimensioned gaps, each of which throttles the pressure medium flow in the manner mentioned above.
  • a further, expedient exemplary embodiment finally specifies claim 11.
  • the main purpose of the mechanical locking device is to prevent the valve body from moving automatically under the influence of impact against the valve housing or vibrations in the event of a pressure failure.
  • the locking device is only designed so strong that it is overcome immediately with any hydraulic loading of the valve body or the approaches.
  • a hydraulic actuating device 1 for an electrical high-performance disconnector 2 can be seen, which is indicated schematically in dashed lines.
  • the disconnector 2 is actuated by a hydraulic differential piston drive 3, the double can be acted upon and has a cylinder chamber 4 with a large loading cross section and a cylinder chamber 5 with a smaller loading cross section.
  • a piston rod 6 is led out of the cylinder space 5, with which the isolating switch is actuated.
  • the cylinder chamber 5 is connected via a line 7a to a hydraulic main pressure supply line 7 which is fed by a high pressure pump 38.
  • a pressure accumulator 39 is also connected to line 7.
  • a line 7b branches off to a 2/3-way seat valve, the housing of which is designated by 12.
  • Three main connections P, A, R are provided in the housing 12.
  • Line 7b leads to connection P.
  • a further line 7c branches off from line 7, in which a first auxiliary control valve 8 and a second auxiliary control valve 9 are arranged.
  • the line 7c leads behind the auxiliary control valves 8, 9 to the return R.
  • the auxiliary control valves 8 and 9 are magnetically actuated two-position two-way valves which are in their blocking position when the magnets are not energized.
  • a line leads from the cylinder space 4 to the main connection A, while the connection R is connected to the return line R via a line 11.
  • a longitudinally continuous housing bore 13 is provided, which is divided into a section 13a with a diameter D and a second section 13b with a somewhat smaller diameter D1.
  • the end boundary walls of the housing bore 13 are penetrated by bores 14 and 15, the inner diameter of which is d.
  • a valve body 16 In the housing bore 13, a valve body 16 is guided to move back and forth in the longitudinal direction between two locking positions I and II.
  • the valve body 16 has a guide and sealing portion 17 near its left end, the outer diameter of which is D.
  • a conical sealing surface 18 is provided on the end face of section 17 facing bore section 13b.
  • a shaft 19 connects section 17 to a further sealing surface 20 which is provided on a shoulder and is at a distance from the sealing surface 18.
  • the transition from the bore section 13a to the bore section 13b forms a first valve seat 21, the inner width of which is D1.
  • a further valve seat 22, also with the width D1, is assigned to the sealing surface 20.
  • the axial distance between the sealing surfaces 18 and 20 is larger than the axial distance between the valve seats 21 and 22 by the working stroke of the valve body 16.
  • connections P, A, R are each assigned recesses 23, 24, 25, which ensure that the pressure medium can flow around the valve body on all sides.
  • the end parts of the valve body 16 are formed into piston-like projections 26, 27 which extend through the bores 14, 15 and have a diameter d.
  • Seals 28 are arranged in the region of the section 17 and in the bore wall of the bore 15.
  • a connecting line 29 continuously connects the annular space 24 to a control chamber 31, which is delimited by the left end of the bore section 13a, the bore end wall, the outer circumference of the extension 27 and the differential area denoted by D - d between the section 17 and the extension 27.
  • a flow restrictor 30 is provided in line 29, and its throttling effect can expediently be set.
  • a connecting line 32 leads from the control chamber 31 to the section of the line 7c between the auxiliary control valves 8 and 9.
  • the isolating switch 2 In the position shown, the isolating switch 2 is in the closed position, for which both cylinder frames 4, 5 of the hydraulic differential piston arrangement 3 are under the pressure provided by the high pressure source 8.
  • the cylinder chamber 5 is acted upon directly from the line 7, while the cylinder chamber 4 is supplied with the same pressure via the line 7b, the connection P, the free passage through the valve seat 22, the connection A and the line 10. Since the exposed area in the cylinder space 4 is larger than in the cylinder space 5, the isolating switch 2 remains closed. It also remains in this position if the pressure in the hydraulic supply should be reduced.
  • the auxiliary control valve 9 is actuated, so that the control chamber 31 is suddenly vented into the return line R via the line 32.
  • the hydraulic volume to be displaced is proportional moderately small and is determined by the working stroke of the valve body 16 and the difference surface D - d.
  • the sealing surface 20 comes to rest on the valve seat 22 and separates the connection A from the connection P down.
  • the sealing surface 18 is lifted off the valve seat 21 and the connection A is connected to the connection R.
  • the cylinder chamber 4 is suddenly relieved via the line 10, so that the pressure in the cylinder chamber 5 shifts the piston rod 6 to the left and opens the disconnector 2.
  • the valve body remains in this position.
  • the pressure from the branch line 7b acts on the differential surface D1-d and keeps the sealing surface 20 pressed against the valve body seat 22.
  • the control chamber 31 is also relieved to the port R via the line 29, so that no force can build up which could move the valve body 16 to the right again into its blocking position I.
  • the auxiliary control valves 8 and 9 are generally only operated for a short time.
  • auxiliary control valve 8 is briefly switched to its open position when auxiliary control valve 9 is closed, so that control chamber 31 acts on line 32 with the pressure from line 7 becomes.
  • the force then building up on the difference surface D - d pushes the valve body 16 to the right until again the position shown in Fig. 1 is reached.
  • port P is in turn connected to port A, while port A is separated from port R.
  • the cylinder chamber 4 is acted upon again and the disconnector 2 is thus brought into its closed position.
  • FIG. 2 shows a similar hydraulic actuating device for a high-performance disconnector, not shown, in which the same parts are identified by the reference numerals selected previously.
  • a 2/3-way seat valve is used, the housing 40 of which has a housing bore 41 which is formed with the same diameter D throughout.
  • two valve seats 42 and 43 of the same size are formed, which face the sealing surfaces 44 and 45 on the valve body 46.
  • the sealing surfaces 44 and 45 are arranged on guide and sealing sections 47, 48 which have the same diameter D as the valve seats 42 and 43.
  • the housing bore 41 is provided at both ends with elongated blind bores 41a and 41b, of which the bore 41a has a diameter d2 and the bore 41b has a diameter d1.
  • the cross-sectional areas of the valve seats 42 and 43 are approximately in a ratio of 1: 4: 10 to the cross-sectional areas of the bores 41a and 4lb.
  • the parts of the housing bore 41 remaining behind the two sections 47 and 48 are through relief lines 49 with a return line, not shown -Connection point connected so that no pressure can be built up behind the sections 47 and 48.
  • An auxiliary piston 50 is guided in a displaceably sealed manner in the bore 41a, while an in the bore 41b Auxiliary piston 51 is arranged in the same way.
  • a control chamber 52 is formed between the auxiliary piston 50 and the bore 41a, while a pressure chamber 53 is formed between the auxiliary piston 51 and the bore 41b, which is continuously connected to the line 7 via a line 54 and is under pressure from the pressure source 8 .
  • the control chamber 52 is connected via a line 55 to the line section between the auxiliary control valves 8 and 9 and is simultaneously acted upon via line 29 and the throttle 30 with the pressure prevailing in the housing bore 41.
  • this seat valve is directly comparable to the function of the embodiment of FIG. 1, although here the pressure in the pressure chamber 53 on the auxiliary piston 51 is used to move the valve body into the second blocking position II after the control chamber 52 has been relieved.
  • the control chamber 52 is acted upon either by the line 29 or the line 55 with the pressure from the pressure source 8, so that the auxiliary piston of larger cross section overcomes the force which is constantly acting on the smaller auxiliary piston 41 and brings the valve body into the position shown in Fig. 2.
  • this seat valve also remains in the position in which it was previously. In the blocking position I it is then held by the force of the larger auxiliary piston 50, while in the blocking position II it is held solely by the force of the smaller auxiliary piston 51, so that the control chamber is then relieved to return.
  • a housing bore 61 is provided in the housing 60 and is composed of a central section 61b with the diameter D1 and two end sections 61a with the respective diameter D2.
  • the diameter of the left housing bore section 61a has no influence on the function of the valve and could also be selected differently.
  • a valve body 62 has two axially spaced guide and sealing sections 63 and 64 which cooperate with sealing surfaces 67 and 68 with valve seats 66 and 65 which are formed between the housing bore sections.
  • a peg-like extension 69 is arranged on each sealing surface 67 and 68, the outside diameter of which corresponds approximately to the passage width D1 of the valve seats 65, 66 and the axial length of which corresponds approximately to half the possible working stroke of the valve body 62.
  • the blind bores 61c which extend the housing bore 61 and each have the same diameter d, extend into the housing 60 and form a control chamber 71 and a pressure chamber 72 there, in which auxiliary pistons 70 with the same diameter d are displaceably guided in a sealed manner.
  • the pressure chamber 72 is in turn connected directly to the pressure source via the line 54, so that it is constantly under pressure.
  • a locking member 73 which is under the force of a spring 75.
  • the locking member locks the valve body 62 in its two locking positions I and II, provided that no hydraulic pressure is applied.
  • This locking device is primarily intended to mechanically Prevent seat valve 1b from accidentally shifting valve body 62.
  • valve body 62 cooperates here with the valve seats 65, 66 with a positive overlap, i.e.
  • the extensions 69 each ensure that the connection P is only connected to the connection A when the connection R is largely separated from the connection A by the immersion of the extension 69. This measure prevents an excessive amount of hydraulic fluid from getting into the return when switching over.
  • the control chamber 71 is relieved, so that the holding force of the auxiliary piston 70 is eliminated and the second auxiliary piston 70 in the pressure chamber 72 moves the valve body 62 to the left with its force until the sealing surface 68 abuts the valve seat 65.
  • the cross section of the auxiliary piston 70 is larger than the differential area between D1 and D2 on which the pressure in the port P rests. So that the valve body can then be pushed back into its blocking position I, the control chamber 71 must be pressurized again so that the forces of the two auxiliary pistons 70 cancel each other out.
  • auxiliary control valves can of course be connected in parallel to the control chamber, so that the high-performance isolating switch can be opened with another in the event of failure of one auxiliary control valve.

Landscapes

  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Multiple-Way Valves (AREA)
EP81107195A 1981-09-11 1981-09-11 Disjoncteur électrique à haut pouvoir de coupure ayant un dispositif de commande hydraulique Expired EP0074419B1 (fr)

Priority Applications (3)

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

Applications Claiming Priority (1)

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

Publications (2)

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

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ID=8187903

Family Applications (1)

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

Country Status (3)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2539465A1 (fr) * 1983-01-13 1984-07-20 Beringer Hydraulik Gmbh Valve de commutation a siege
EP0229918A1 (fr) * 1986-01-23 1987-07-29 Licentia Patent-Verwaltungs-GmbH Entraînement pour un disjoncteur de puissance à haute tension
EP1302958A1 (fr) * 2001-10-15 2003-04-16 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Soupape à siège pour vérin différentiel pour sectionneur
EP2282065A1 (fr) 2009-07-30 2011-02-09 HAWE Hydraulik SE Soupape à siège de commutation hydraulique et dispositif de section de puissance
CN104425175A (zh) * 2013-08-23 2015-03-18 株式会社日立制作所 遮断器的流体压力驱动装置
CN105003478A (zh) * 2015-06-30 2015-10-28 河南平高电气股份有限公司 控制阀及使用该控制阀的断路器液压操动机构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2213244A1 (de) * 1972-03-18 1973-09-27 Bbc Brown Boveri & Cie Hydraulisches umschalt-sitzventil bzw. gesteuertes rueckschlagventil
DE7240231U (de) * 1972-10-02 1974-07-18 Bbc Ag Hydraulisches Schaltventil
DE2831808B2 (de) * 1977-07-20 1980-10-16 Hitachi, Ltd., Tokio Hydraulische Antriebsvorrichtung für einen elektrischen Hochspannungs-Leistungsschalter
DE3004599A1 (de) * 1980-02-08 1981-08-13 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Hauptventil-ansteuerung fuer einen hochspannungs-leistungsschalter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2213244A1 (de) * 1972-03-18 1973-09-27 Bbc Brown Boveri & Cie Hydraulisches umschalt-sitzventil bzw. gesteuertes rueckschlagventil
DE7240231U (de) * 1972-10-02 1974-07-18 Bbc Ag Hydraulisches Schaltventil
DE2831808B2 (de) * 1977-07-20 1980-10-16 Hitachi, Ltd., Tokio Hydraulische Antriebsvorrichtung für einen elektrischen Hochspannungs-Leistungsschalter
DE3004599A1 (de) * 1980-02-08 1981-08-13 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Hauptventil-ansteuerung fuer einen hochspannungs-leistungsschalter

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2539465A1 (fr) * 1983-01-13 1984-07-20 Beringer Hydraulik Gmbh Valve de commutation a siege
EP0229918A1 (fr) * 1986-01-23 1987-07-29 Licentia Patent-Verwaltungs-GmbH Entraînement pour un disjoncteur de puissance à haute tension
EP1302958A1 (fr) * 2001-10-15 2003-04-16 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Soupape à siège pour vérin différentiel pour sectionneur
US6761186B2 (en) * 2001-10-15 2004-07-13 Heilmeier & Weinlein Fabrik F. Oel-Hydraulik Gmbh & Co. Kg Seated-type valve for a double-action cylinder of an electric disconnector
EP2282065A1 (fr) 2009-07-30 2011-02-09 HAWE Hydraulik SE Soupape à siège de commutation hydraulique et dispositif de section de puissance
CN104425175A (zh) * 2013-08-23 2015-03-18 株式会社日立制作所 遮断器的流体压力驱动装置
CN105003478A (zh) * 2015-06-30 2015-10-28 河南平高电气股份有限公司 控制阀及使用该控制阀的断路器液压操动机构

Also Published As

Publication number Publication date
DE3173448D1 (en) 1986-02-20
EP0074419B1 (fr) 1986-01-08
ATE17413T1 (de) 1986-01-15

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