EP0022729B1 - Bistable hydraulic valve for operating a piston of a fast high tension circuit breaker - Google Patents

Bistable hydraulic valve for operating a piston of a fast high tension circuit breaker Download PDF

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Publication number
EP0022729B1
EP0022729B1 EP19800401062 EP80401062A EP0022729B1 EP 0022729 B1 EP0022729 B1 EP 0022729B1 EP 19800401062 EP19800401062 EP 19800401062 EP 80401062 A EP80401062 A EP 80401062A EP 0022729 B1 EP0022729 B1 EP 0022729B1
Authority
EP
European Patent Office
Prior art keywords
jack
tripping
hydraulically
seat
operating system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19800401062
Other languages
German (de)
French (fr)
Other versions
EP0022729A1 (en
Inventor
Jean-Paul Robert
Claude Pinet
Robert Jean
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.)
Merlin Gerin SA
Original Assignee
Merlin Gerin SA
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Filing date
Publication date
Application filed by Merlin Gerin SA filed Critical Merlin Gerin SA
Publication of EP0022729A1 publication Critical patent/EP0022729A1/en
Application granted granted Critical
Publication of EP0022729B1 publication Critical patent/EP0022729B1/en
Expired legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/285—Power arrangements internal to the switch for operating the driving mechanism using electro-dynamic repulsion
    • 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 propellant of a four-way hydraulic valve comprises a solenoid whose excitation causes the unidirectional movement of a movable closure element. This results in the actuation of a piston whose operating rod cooperates with a link mechanism to ensure the closing of the circuit breaker.
  • the opening of the circuit breaker occurs by means of tripping means separate from the interlocking valve, said means being formed by a tripping coil causing, in the event of excitation, unlocking of the link mechanism.
  • This device is complicated because it requires a double hydraulic and mechanical control to close and open the circuit breaker.
  • the movable element of the hydraulic valve is unstable in the open position, and a return spring ensures the return of said element to the closed position.
  • the thruster acts only in the direction of opening of the valve.
  • the object of the invention is to avoid the aforementioned drawbacks and to produce a reliable and enduring hydraulic control device, using a quick-response bistable hydraulic valve when the circuit breaker is engaged and tripped.
  • the supply duct of the accumulator is equipped in the vicinity of the second seat with an inlet nozzle of predetermined size for adjusting the engagement speed.
  • the discharge conduit for venting the cylinder contains an exhaust nozzle determining the tripping speed.
  • a drawer formed in said body of the valve is associated with the first and second seats in order to cooperate with the corresponding bearing faces of the shutter member respectively at the end of the engagement race and trigger, so as to increase the effect of the hydrodynamic support forces when closing said drawer, and the stability of the shutter member in the engaged and triggered position.
  • an anti-water hammer device in particular an oleopneumatic damper or a unidirectional nozzle, cooperates with the hydraulic circuit in the vicinity of said intake orifice to avoid internal overpressure of the valve oil during its displacement towards the engagement position.
  • said propellant element comprises an electrodynamic repulsion actuator with a movable conductive disc inserted in an axial air gap formed outside the valve body between two fixed engagement and release coils, the selective excitation by capacitor discharge causes the electrodynamic repulsion of the disc in a determined direction to ensure the crossing of the cylinder dead center towards the engaged or released position.
  • the propellant element of the obturator member comprises a hydraulic differential piston provided with two active faces sensitive to the pressure variation of the control oil contained in two elementary chambers, each equipped with an auxiliary valve. , such that the rapid opening of one of them causes the corresponding chamber to be placed under vacuum or in compression, followed by displacement of the differential piston in a determined direction.
  • the hydraulic valve designated by the general reference 10, comprises a fixed body 12 arranged between an electrodynamic actuator 14 and a jack 15 for controlling the tripping and engagement of the mechanism of a high voltage circuit breaker .
  • the actuator 14 comprises a bidirectional thruster with double axial air gap and electrodynamic repulsion of the Thomson type provided with a movable disc 16 interposed between two fixed engagement 18 and trigger 20 coils.
  • the disc 16 of conductive material is integral with an actuating rod 22 mounted with alternating sliding in a bore 24 of the body 12 with the interposition of an annular seal 26.
  • the valve 10 comprises a shutter member 28 mechanically coupled to the actuating rod 22, and capable of occupying two stable longitudinal positions at the end of the engagement and tripping travel respectively when the disc 16 is coupled against the coil 20 and the actuator coil 18 14.
  • the shutter member 28 comprises a cylinder 14.
  • the shutter member 28 comprises a coaxial hollow cylinder 30, of diameter greater than that of the rod 22, and sliding inside a central bore 32 of the body 12 provided with a annular groove 34 for housing a seal 36.
  • One 38 of the ends of the shutter cylinder 30 is cut in a bevel and cooperates in the locked position (fig.
  • the two seats 40, 48 of the body 12 are separated longitudinally from one another by a predetermined axial distance d 1 , and the bidirectional sliding stroke of the shutter member 28 between the two seats 40, 48 corresponds exactly to that of the disc 16 between the two coils 20, 18 of the actuator 14.
  • the flange 44 is provided, opposite the face 46, with an auxiliary face shaped as sparging 50 with a diameter greater than the central bore 32, and coming into abutment against the central section of the body 12 when the valve 10 is in the engaged position.
  • One 52 of the front faces of the body 12 pierced by the central bore 32 determines with the seat 48 adjacent a radial orifice 54 for admission of pressurized oil, in connection with an oleopneumatic accumulator 56 or another high-pressure oil reservoir via a supply conduit 58.
  • the flange 44 of the cylinder 30 comprises a plurality of holes 60 distributed circumferentially according to a crown of diameter smaller than that of the seat 48, and making the inlet orifice 54 communicate with the internal conduit 62 of the hollow cylinder 30 in the engagement position of the valve 10 for supplying the cylinder 15, the filling of which moves the movable piston 64 in the direction of arrow F and the rapid closing of the contacts of the circuit breaker.
  • the front face 66 opposite that 52 of the body 12, with a bore 32, forms with the seat 40 juxtaposed an exhaust orifice 68 in connection with a discharge duct 70 with a tank 72 at low pressure for venting of the jack 15 in the release position (fig. 3) of the valve 10.
  • the supply duct 58 is equipped with an inlet nozzle 74 of predetermined size for adjusting the speed of closing of the contacts, and the discharge duct 70 similarly includes an exhaust nozzle 76 which determines the opening speed of the contacts when the jack is vented 15.
  • the valve 10 is bistable and rests on one of the seats 40, 48, so as to selectively connect the actuator 15 either to the oleopneumatic accumulator 56 for switching on the circuit breaker and keeping the contacts in the closed position, or to the cover 72 for venting the jack 15 when the circuit breaker trips.
  • the latching position (fig. 1)
  • the shutter member 28 of the valve 10 comes into leaktight abutment on the seat 40 to close the exhaust port 68 towards the tank 72 and simultaneously open the intake port 54 oil under high pressure.
  • the release position (fig.3), the shutter member 28 engages with the seat 48 to close the intake port 54 and simultaneously open the exhaust port 68 for rapid emptying of the jack 15.
  • Each of the two engagement and tripping positions of the valve 10 is stable, and the passage from one to the other is caused by the displacement in translation of the disc 16 of the electrodynamic actuator 14.
  • the inlet 54 and exhaust 68 orifices are partially open and make the oleopneumatic accumulator 56 communicate with the tank 72.
  • the flow of oil expelled from the accumulator 56 towards the tank 72 is limited by the pressure drops in the supply duct 58, the inlet nozzle 74, the passage section SA of the oil in the orifice inlet 54, variable according to the position of the flange 44, the holes 60 and l e internal duct 62 of the shutter member 28.
  • the passage section SE of the oil in the exhaust orifice 68 varying in opposite direction from the intake section SA, the exhaust nozzle 76 and the duct repression 70.
  • FIG. 8 shows the variation of the resulting hydrodynamic forces F as a function of the position x for different decreasing values of the inlet nozzle 74 (curves l, II, III), and it can be seen that in the middle position of the valve (position 0) the forces F are practically zero.
  • This median position constitutes in a way a dead center passage, the crossing of which depends on the displacement force of the actuating rod 22 during the excitation of the electrodynamic actuator 14.
  • the main role of the latter is to ensure the sudden passage from neutral, and the hydrodynamic forces F then take over or add to the electrodynamic forces of repulsion of the disc 16 to apply the valve 10 to one of the seats 40, 48, and maintain it stably in this position. It has been found that the hydrodynamic forces F exerted on the valve 10 are generated when one of the sections SA and SE for the passage of the oil in the valve was close to the smallest of the sections for the passage of the hydraulic circuit between the accumulator 56 and tank 72, for example when the intake section SA corresponds to the section of the nozzle 74.
  • the curve is an optimum curve corresponding to a predetermined value of the intake nozzle 74 greater than that of the nozzle of the curve III in which the memory effect is likely to be zero in the event of rebound of the valve 10 when it comes to the corresponding seat 40, 48.
  • the tripping of the circuit breaker is controlled by the excitation of the tripping coil 20 of the actuator 14, in particular by means of a discharge of a capacitor causing the electrodynamic repulsion of the conductive disc 16 in the direction of the coil 18 and the displacement fast from the shutter member 28 to the opposite seat 48.
  • the shutter member 28 After passing neutral from the electrodynamic forces of the actuator 14 (fig. 2), the shutter member 28 is sucked in by the hydrodynamic forces engen drées in the decreasing section of admission SA of the hydraulic circuit at the level of the orifice 54 and comes to bear on the seat 48. This position 54 and comes to bear on the seat 48.
  • This position is stable when the diameter of the seat 48 is greater than that of the bore 32, and the inlet 54 and exhaust 68 ports are respectively closed and open for venting the jack 15 to the cover 72 causing the rapid opening of the contacts.
  • the resetting is carried out during the excitation of the engagement coil 18 which causes the electrodynamic repulsion of the disc 16 in the direction of the coil 20.
  • the translational travel of the disc 16 is identical to that of the shutter member 28, which after crossing the neutral position in the middle position (fig. 2) is urged into stable support on the seat 40 by the hydrodynamic forces generated in the decreasing exhaust section SE in the vicinity of the orifice 68.
  • the valve 10 is then found in the latching position shown in fig. 1.
  • An intermediate amplifier stage (not shown) can be arranged downstream of the jack to be controlled by the valve 10.
  • the shutter member 28 engages against the corresponding seat 48 or 40 at reduced speed thanks to two dampers 80, 82 (fig. 6 and 7) hydraulics active in the vicinity of the two triggering and latching positions, and integrated inside the body 12 of the valve 10.
  • the damper 80 comprises a shoulder 84 formed at the junction of the actuating rod 22 with the rim 44 of the cylinder 30, and playing the role of piston capable of sliding at the end of the triggering stroke in an annular groove 86 of the body 12, of diameter greater than that of the bore 24. The compression of the oil in the groove 86 brakes the moving element formed by the rod 22 and the shutter member 28 ensuring a slow arrival of the latter on the seat 48.
  • the damper 82 similarly includes a step 88 on the shoulder 50 of flange 44, and an annular groove 90 in al central bore 32 of the body 12.
  • the step 88 plays the role of oil compression piston in the groove 90 at the end of the engagement stroke and causes a rebound engagement of the member 28 on the seat 40.
  • valve 10 is equipped with a cylindrical drawer 100 associated with the seat 48 of the body 12, so as to cooperate with the flange 44 of the shutter member 28 at the end of the triggering stroke (FIG. 5) to increase the effect of hydrodynamic forces when closing the drawer 100. This results in better stability of the shutter member 28 in the release position, regardless of the size of the inlet nozzle 74.
  • the seat 48 on which is supported by the member 28 is located between the bore 24 and the slide 100.
  • the shoulder 50 of the flange 44 compresses the oil contained in the cavity 102 located between the drawer 100 and the inlet nozzle 74.
  • the latter is placed in communication with an oleopneumatic damper 104 with membrane 106, or other anti-water hammer accumulator whose small volume is overpressure relative to the pressure of the oil in the accumulator 56.
  • the rest of the operation is identical to that described with reference to FIGS. 1 and 3.
  • the oleopneumatic damper 104 is replaced by a unidirectional nozzle 110 inserted in the hydraulic circuit between the supply duct 58 of the accumulator 56 and the inlet orifice 54 of the cavity 102.
  • a spring 112 urges the nozzle 110 resting on a flange 114 of the drawer 100; in the event of overpressure of the oil in the cavity 102 occurring during the engagement, the radial displacement of the nozzle 110 against the spring 112 allows an expansion of the oil in a recess 116 and in the accumulator 56.
  • the two variants of figs. 4 to 7 can be fitted on the low pressure side with a cylindrical slide 120 formed in the body 12 between the exhaust orifice 68 and the seat 40 (fig. 9).
  • the end 38 of the closure member 28 cooperates with the slide 120 at the end of the interlocking stroke to increase the effect of the hydrodynamic forces and the stability of the valve 10 in the interlocking position.
  • the electrodynamic actuator 14 of the Thomson effect type with double coils 18, 20, for switching on and off control is replaced by a hydraulic device 200 with differential piston 202 for actuating the shutter member 28.
  • the same reference numerals designate parts which are identical or similar to those shown in FIGS. 1 to 9.
  • the hollow cylinder 30 of the shutter member 28 slidably mounted inside a bore 32 between two stable longitudinal positions at the end of the engagement and tripping travel.
  • One 38 of the ends of the cylindrical shutter member 28 is cut in a bevel and comes into engagement in the latching position (fig. 10) with the circular seat 40 to close the exhaust orifice 68 of the discharge duct 70 in conjunction with a low pressure tank (not shown).
  • the opposite end 42 of the cylinder 30 has a flange 44 with an active frustoconical face 46 cooperating in the release position (FIG.
  • the flange 44 comprises a plurality of holes 60 communicating the inlet port 54 with the internal conduit 62 of the hollow cylinder 30 in the engagement position of the valve 10 for supplying the actuator (not shown) for closing the contacts of the circuit breaker.
  • the end 42 of the cylinder 30 is connected by the actuating rod 22 to the differential control piston 202 capable of sliding in a fixed cylinder 204 of the body 12.
  • the piston 202 has two active faces 206, 208 cooperating with the opposite bottoms of the cylinder 204 to delimit two elementary chambers 210, 212 in communication with the high pressure accumulator by two supply conduits 214, 216.
  • the volume of chambers 210, 212 varies in opposite directions from one another according to the direction of movement of the differential piston 202 controlled by the depression of one of the chambers.
  • the shutter member 28 In the engagement position (fig. 10), the shutter member 28 is in stable abutment on the seat 40 after the chamber 210 of the hydraulic device 200 has been placed under vacuum. Triggering is controlled by placing the vacuum under pressure. another chamber 212 causing the differential piston 202 to translate to the right and the stop member 28 coming into abutment against the seat 48 (fig. 11), so as to close the intake orifice 54 and simultaneously open l 'exhaust port 68 for venting the cylinder.
  • FIGS. 12 to 16 represent four alternative embodiments using the principle of the differential piston 202 of the hydraulic control device 200, illustrated in FIGS. 11 and 12.
  • each elementary chamber 210, 212 is associated with an auxiliary rapid purge valve 220, 222 actuated by an electrodynamic propellant 224, 226 with Thomson effect.
  • Each thruster 224, 226 comprises a control coil 228, 230 disposed opposite a movable disc 232, 234 of conductive material, associated with a striker 236, 238 cooperating with the corresponding purge valve 220, 222.
  • each chamber 210, 212 is biased in the closed position by means of an elastic member, in particular a return spring 240, 242, which maintains the corresponding purge valve in sealed contact against a seat 243 , 245 as long as the propellant 224, 226 remains in the inactive de-excitation position of the coil 228, 230.
  • the supply line 214, 216 for high pressure oil from each chamber 210, 212 is provided with an intake nozzle 244 , 246, arranged opposite the purge valve 220, 222 with respect to the axial direction of the cylinder 204.
  • Each seat 243, 245 has a section greater than that of the corresponding nozzle 244, 246 and is connected by a discharge conduit to a low pressure compartment 250 in connection with the cover.
  • the operation of the hydraulic control device 200 according to FIG. 12 is as follows:
  • the circuit breaker is engaged after excitation of the control coil 228 of the thruster 224 with electrodynamic repulsion, the striker 236 of which opens the purge valve 220 for a predetermined time, for example of the order of a millisecond. This results in the decompression of the chamber 210 and the discharge of the oil contained in the chamber 210 to the compartment 250 at low pressure.
  • the differential piston 202 is then biased in axial translation in the direction of the arrow F i , and applies the shutter member 28 to the seat 40, so as to open the intake port 54 and simultaneously close the exhaust port 68.
  • the triggering is carried out by excitation of the coil 230 of the propellant 226 causing the opening of the purge valve 222 and the decompression of the chamber 212 whose oil is discharged towards the compartment 250 at low pressure.
  • the differential piston 202 is actuated in axial translation along the arrow F 2 until the closure member 28 engages against the seat 48 causing the admission orifice 54 to close and the simultaneous opening of the exhaust port 68.
  • the differential piston 202 is provided with a communication conduit of the two chambers 210, 212 allowing the elimination of one of the supply conduits 214, 216.
  • the structure of the rapid purge valves 220, 222 can be of any type, in particular with frustoconical or spherical bearing cooperating with the circular seats 243, 245.
  • the switching on and off commands result from the decompression of one of the chambers 210, 212, following an impulse shock from one of the strikers 236, 238 on the corresponding purge valve 220, 222 which remains open for a time very short.
  • the control energy of the thrusters 224, 226 is much lower than that necessary for the displacement of the shutter member 28 of the valve 10 according to FIGS. 1 to 9.
  • the supply lines 214, 216 of high pressure oil open into the opposite bottoms 252, 254 of the cylinder 204, in the vicinity of the purge valves 220, 222
  • Each of these valves has a drawer end, which closes the corresponding conduit 214, 216 when one of the coils 228, 230 of the thrusters 224, 226 is energized. Closure of the conduits 214, 216 from the start opening the purge valves 220, 2222 allows a saving of control oil contained in the oleopneumatic accumulator or other high pressure oil tank, and accelerates the decompression of the chambers 210, 212.
  • the seats 243, 245 of the purge valves 220, 222 are formed in the opposite bottoms 252, 254 of the cylinder 204.
  • the strikers 236, 238 of the electrodynamic thrusters 224, 226 move in opposite direction l '' from one another in a direction parallel to that of axial translation of the piston differential 202.
  • each purge valve 220, 222 comprises a first frustoconical portion 260 cooperating in the closed position with the corresponding seat 243, 245, a second intermediate lateral portion 262 of cylindrical shape capable of closing the supply duct 214, 216 of high pressure oil at the start of the valve opening stroke and a third cylindrical portion 264 in the shape of a piston with a diameter less than that of the intermediate portion 262.
  • Each bleed valve 220, 222 is provided with 'A plurality of holes 266 communicating the supply lines 214, 216 of high pressure oil with the chambers 210, 212 in the inactive position of the thrusters 224, 226 corresponding to the closing of the purge valves.
  • the piston of the third portion 264 moves into a central housing 268 of the low pressure compartment 250 connected to the tank.
  • a fixed O-ring 270 surrounds the piston 264 of each valve 220, 222, compensated and provides sealing between the housing 268 at low pressure and the chambers 210, 212 of the hydraulic device 200.
  • FIG. 14 The operation of the device of FIG. 14 is similar to that of FIG. 13, the only difference being the use of purge valves 220, 222 compensated, each having an end shaped as a piston 264 displaceable in the housing 268 at low pressure.
  • the differential piston 202 for controlling the bistable valve 10 forms an integral part of the closure member 28.
  • One 206 of the active faces of the differential piston is formed by a shoulder located in the central zone of the cylinder 30.
  • the other 208 active face of the differential piston is constituted by a solid cylindrical end piece 272 arranged opposite the end 38 of the cylinder 30, so as to slide in a bore 274 of the body 12.
  • the face 206 delimits the elementary chamber 210 formed in the body 12 between the discharge conduit 70 and the conduit 58, and in communication with the high pressure accumulator by the supply conduit 214 provided with the intake nozzle 244.
  • Decompression of the chamber 210 by the opening of the rapid purge ball valve 224 causes the shutter member 28 to be actuated towards the latching position (fig. 15).
  • the other face 208 delimits the second elementary chamber 212 arranged opposite the circuit breaker control cylinder, and in communication with the high pressure accumulator by the supply duct 216 with a nozzle 246.
  • a ball valve 226 for purging rapid is associated with chamber 212, the decompression of which when the purge valve 226 opens causes the shutter member 28 to engage with the seat 48, followed by tripping of the circuit breaker (fig. 16).

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  • Magnetically Actuated Valves (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

L'invention est relative à un dispositif de commande hydraulique d'un vérin associé au mécanisme de manceuvre d'un disjoncteur à haute tension pour la fermeture et l'ouverture des contacts, ledit dispositif comportant :

  • - un accumulateur rempli d'huile sous pression,
  • - une bâche à pression plus faible pour l'échappement de l'huile du vérin lors du déclenchement,
  • - un clapet hydraulique de mise en communication sélective du vérin, soit à l'accumulateur pour l'enclenchement et le maintien des contacts en position de fermeture, soit à la bâche pour la mise à la purge lors du déclenchement,
  • - des conduits d'alimentation et de refoulement pour le raccordement du clapet respectivement à l'accumulateur et à la bâche,
  • - un corps fixe pourvu d'un premier siège disposé au voisinage d'un orifice d'échappement du conduit de refoulement, et un deuxième siège situé au voisinage d'un orifice d'admission du conduit d'alimentation, les deux sièges étant décalés l'un de l'autre par un intervalle axial prédéterminé,
  • - et un élément propulseur susceptible de déplacer le clapet entre les deux sièges dudit intervalle pour assurer l'enclenchement ou le déclenchement du disjoncteur, ledit clapet comportant un organe d'obturation susceptible de coulisser dans un alésage du corps.
The invention relates to a hydraulic control device for a jack associated with the operating mechanism of a high-voltage circuit breaker for closing and opening of the contacts, said device comprising:
  • - an accumulator filled with pressurized oil,
  • - a lower pressure tank for escaping the oil from the actuator when triggered,
  • - a hydraulic valve for selective actuation of the jack, either at the accumulator for switching on and maintaining the contacts in the closed position, or at the cover for venting when tripping,
  • - supply and discharge conduits for connecting the valve respectively to the accumulator and to the tank,
  • - A fixed body provided with a first seat arranged in the vicinity of an outlet orifice of the delivery duct, and a second seat situated in the vicinity of an inlet orifice of the supply duct, the two seats being offset from each other by a predetermined axial interval,
  • - And a propellant capable of moving the valve between the two seats of said interval to ensure the engagement or tripping of the circuit breaker, said valve comprising a shutter member capable of sliding in a bore of the body.

En cas d'utilisation d'un propulseur unidirectionnel actif dans un seul sens, par exemple dans le sens du déclenchement du clapet pour assurer la purge rapide du vérin, il est nécessaire pour assurer le réenclenchement du disjoncteur de prévoir une valve d'enclenchement auxiliaire de commande qui agirait sur un clapet relais d'un étage intermédiaire. Un tel dispositif est compliqué et introduit obligatoirement des temps de réponse longs néfastes au bon fonctionnement du disjoncteur lors de l'enclenchement.When using a unidirectional thruster active in one direction, for example in the direction of tripping of the valve to ensure rapid bleeding of the jack, it is necessary to ensure the reclosing of the circuit breaker to provide an auxiliary engagement valve control which would act on a relay valve of an intermediate stage. Such a device is complicated and necessarily introduces long response times detrimental to the proper functioning of the circuit breaker during switching on.

Selon le brevet britannique GB 752.947, le propulseur d'une valve hydraulique à quatre voies comporte un solénoide dont l'excitation provoque le déplacement unidirectionnel d'un élément d'obturation mobile. Il en résulte l'actionnement d'un piston dont la tige de manoeuvre coopère avec un mécanisme à biellettes pour assurer la fermeture du disjoncteur. L'ouverture du disjoncteur intervient par l'intermédiaire de moyens de déclenchement distincts de la valve d'enclenchement, lesdits moyens étant formés par une bobine de déclenchement provoquant en cas d'excitation le déverrouillage du mécanisme à biellettes. Ce dispositif est compliqué car il nécessite une double commande hydraulique et mécanique pour la fermeture et l'ouverture du disjoncteur.According to British patent GB 752,947, the propellant of a four-way hydraulic valve comprises a solenoid whose excitation causes the unidirectional movement of a movable closure element. This results in the actuation of a piston whose operating rod cooperates with a link mechanism to ensure the closing of the circuit breaker. The opening of the circuit breaker occurs by means of tripping means separate from the interlocking valve, said means being formed by a tripping coil causing, in the event of excitation, unlocking of the link mechanism. This device is complicated because it requires a double hydraulic and mechanical control to close and open the circuit breaker.

Selon le brevet USA 4.118.613, l'élément mobile du clapet hydraulique est instable dans la position d'ouverture, et un ressort de rappel assure le retour dudit élément vers la position de fermeture. Le propulseur agit uniquement dans le sens d'ouverture du clapet.According to USA patent 4,118,613, the movable element of the hydraulic valve is unstable in the open position, and a return spring ensures the return of said element to the closed position. The thruster acts only in the direction of opening of the valve.

Selon le brevet français N° 2.026.241, il est classique d'utiliser un propulseur électrodynamique à effet Thomson pour actionner une soupape d'admission de gaz comprimé associée à un disjoncteur pneumatique. Le propulseur électrodynamique est néanmoins agencé à l'intérieur du corps de la soupape. Un ressort de rappel coopère d'autre part avec l'organe mobile obturateur de la soupape dans l'une de ses deux directions.According to French Patent No. 2,026,241, it is conventional to use an electrodynamic thruster with Thomson effect to actuate a compressed gas intake valve associated with a pneumatic circuit breaker. The electrodynamic propellant is nevertheless arranged inside the body of the valve. A return spring cooperates on the other hand with the movable valve member in one of its two directions.

Le but de l'invention est d'éviter les inconvénients précités et de réaliser un dispositif de commande hydraulique fiable et endurant, utilisant un clapet hydraulique bistable à réponse rapide lors de l'enclenchement et du déclenchement du disjoncteur.The object of the invention is to avoid the aforementioned drawbacks and to produce a reliable and enduring hydraulic control device, using a quick-response bistable hydraulic valve when the circuit breaker is engaged and tripped.

Le dispositif de commande hydraulique selon l'invention est caractérisé par le fait que l'organe d'obturation du clapet est caractérisé par le fait que l'organe d'obturation du clapet est stable dans les deux positions extrêmes de fin de course d'enclenchement et de déclenchement et est formé par un cylindre creux comprenant :

  • - une première face d'appui à l'une des extrémités du cylindre venant en engagement stable en fin de course d'enclenchement contre le premier siège agencé entre le conduit de refoulement et le conduit du vérin,
  • - une deuxième face d'appui à l'extrémité opposée du cylindre coopérant en position stable de fin de course de déclenchement avec le deuxième siège, situé entre le conduit d'alimentation et l'élément propulseur, ce dernier étant accouplé mécaniquement au cylindre du côté de ladite deuxième face d'appui,
  • - et un conduit interne débouchant aux deux extrémités du cylindre par des ouvertures opposées, présentant chacune une dimension inférieure à celle du siège correspondant.
The hydraulic control device according to the invention is characterized in that the shutter member of the valve is characterized in that the shutter member of the valve is stable in the two extreme end positions of travel engagement and trigger and is formed by a hollow cylinder comprising:
  • a first bearing face at one of the ends of the cylinder coming into stable engagement at the end of the interlocking race against the first seat arranged between the delivery pipe and the jack pipe,
  • - a second bearing face at the opposite end of the cylinder cooperating in a stable end-of-trip position with the second seat, located between the supply duct and the propellant element, the latter being mechanically coupled to the cylinder of the side of said second bearing face,
  • - And an internal conduit opening at both ends of the cylinder through opposite openings, each having a dimension smaller than that of the corresponding seat.

Selon un mode particulier de réalisation, le conduit d'alimentation de l'accumulateur est équipé au voisinage du deuxième siège d'un gicleur d'admission de dimension prédéterminée pour le réglage de la vitesse d'enclenchement. Le conduit de refoulement pour la mise à la purge du vérin renferme un gicleur d'échappement déterminant la vitesse de déclenchement.According to a particular embodiment, the supply duct of the accumulator is equipped in the vicinity of the second seat with an inlet nozzle of predetermined size for adjusting the engagement speed. The discharge conduit for venting the cylinder contains an exhaust nozzle determining the tripping speed.

Selon une autre caractéristique particulière de l'invention, un tiroir ménagé dans ledit corps du clapet est associé aux premier et deuxième sièges pour coopérer avec les faces d'appui correspondantes de l'organe d'obturation respectivement en fin de course d'enclenchement et de déclenchement, de manière à augmenter l'effet des forces hydrodynamiques d'appui lors de la fermeture dudit tiroir, et la stabilité de l'organe d'obturation en position d'enclenchement et de déclenchement.According to another particular characteristic of the invention, a drawer formed in said body of the valve is associated with the first and second seats in order to cooperate with the corresponding bearing faces of the shutter member respectively at the end of the engagement race and trigger, so as to increase the effect of the hydrodynamic support forces when closing said drawer, and the stability of the shutter member in the engaged and triggered position.

Selon une autre caractéristique particulière de l'invention, un dispositif anti-coup de bélier, notamment un amortisseur oléopneumatique ou un gicleur unidirectionnel, coopère avec le circuit hydraulique au voisinage dudit orifice d'admission pour éviter une surpression interne de l'huile du clapet lors de son déplacement vers la position d'enclenchement.According to another particular characteristic of the invention, an anti-water hammer device, in particular an oleopneumatic damper or a unidirectional nozzle, cooperates with the hydraulic circuit in the vicinity of said intake orifice to avoid internal overpressure of the valve oil during its displacement towards the engagement position.

Selon une autre caractéristique particulière de l'invention, ledit élément propulseur comprend un actionneur à répulsion électrodynamique à disque mobile conducteur inséré dans un entrefer axial ménagé à l'extérieur du corps du clapet entre deux bobines fixes d'enclenchement et de déclenchement dont l'excitation sélective par décharge de condensateur provoque la répulsion électrodynamique du disque dans un sens déterminé pour assurer le franchissement du point mort du cylindre vers la position d'enclenchement ou de déclenchement.According to another particular characteristic of the invention, said propellant element comprises an electrodynamic repulsion actuator with a movable conductive disc inserted in an axial air gap formed outside the valve body between two fixed engagement and release coils, the selective excitation by capacitor discharge causes the electrodynamic repulsion of the disc in a determined direction to ensure the crossing of the cylinder dead center towards the engaged or released position.

Selon un développement de réalisation, l'élément propulseur de l'organe obturateur comporte un piston différentiel hydraulique doté de deux faces actives sensibles à la variation de pression de l'huile de commande contenue dans deux chambres élémentaires, équipée chacune d'un clapet auxiliaire, tel que l'ouverture rapide de l'un d'eux provoque la mise en dépression ou en compression de la chambre correspondante suivie du déplacement du piston différentiel dans un sens déterminé.According to an embodiment, the propellant element of the obturator member comprises a hydraulic differential piston provided with two active faces sensitive to the pressure variation of the control oil contained in two elementary chambers, each equipped with an auxiliary valve. , such that the rapid opening of one of them causes the corresponding chamber to be placed under vacuum or in compression, followed by displacement of the differential piston in a determined direction.

D'autres avantages et caractéristiques ressortiront plus clairement de l'exposé qui va suivre de différents modes de mise en oeuvre de l'invention, donnés à titre d'exemples non limitatifs et représentés aux dessins annexés, dans lesquels :

  • la figure 1 est une vue schématique en coupe axiale d'un dispositif de commande hydraulique équipé d'un clapet bistable selon l'invention, représenté en position d'enclenchement ;
  • les figures 2 et 3 montrent des vues analogues à celles de la fig. 1 du clapet en positions intermédiaire et de déclenchement ;
  • les figures 4 et 5 sont des demi-vues en coupe axiale d'une variante de réalisation du clapet représenté respectivement en position d'enclenchement et de déclenchement ;
  • les figures 6 et 7 montrent des demi-vues en coupe d'une autre variante de réalisation du clapet en position d'enclenchement et de déclenchement ;
  • la figure 8 représente les diagrammes des forces hydrodynamiques s'exerçant sur le clapet en fonction de sa position axiale entre les positions d'enclenchement et de déclenchement, pour différentes dimensions de valeurs décroissantes du gicleur d'admission selon le dispositif des figures 1 à 3 ;
  • la figure 9 est une vue partielle en coupe d'une autre variante de réalisation ;
  • les figures 10 et 11 représentent une vue partielle schématique en coupe axiale d'un autre mode de réalisation du dispositif de commande hydraulique équipé d'un piston différentiel, respectivement en positions d'enclenchement et de déclenchement du disjoncteur;
  • les figures 12 et 13 montrent des vues analogues à celle de la fig. 10 de deux autres variantes de l'invention ;
  • la figure 14 est une vue analogue à celle de la figure 10 d'un développement de l'invention ;
  • les figures 15 et 16 représentent des vues analogues à celles des figures 10 et 11, d'une autre variante de réalisation, à clapet compensé bistable positionné respectivement en position d'enclenchement et de déclenchement du disjoncteur.
Other advantages and characteristics will emerge more clearly from the description which follows of different embodiments of the invention, given by way of nonlimiting examples and represented in the appended drawings, in which:
  • Figure 1 is a schematic view in axial section of a hydraulic control device equipped with a bistable valve according to the invention, shown in the engaged position;
  • Figures 2 and 3 show views similar to those of FIG. 1 of the valve in the intermediate and release positions;
  • Figures 4 and 5 are half-views in axial section of an alternative embodiment of the valve shown respectively in the engagement and release position;
  • Figures 6 and 7 show half-sectional views of another alternative embodiment of the valve in the engagement and release position;
  • FIG. 8 represents the diagrams of the hydrodynamic forces exerted on the valve as a function of its axial position between the engagement and trigger positions, for different dimensions of decreasing values of the intake nozzle according to the device of FIGS. 1 to 3 ;
  • Figure 9 is a partial sectional view of another alternative embodiment;
  • Figures 10 and 11 show a schematic partial view in axial section of another embodiment of the hydraulic control device equipped with a differential piston, respectively in the ON and OFF positions of the circuit breaker;
  • Figures 12 and 13 show views similar to that of FIG. 10 of two other variants of the invention;
  • Figure 14 is a view similar to that of Figure 10 of a development of the invention;
  • Figures 15 and 16 show views similar to those of Figures 10 and 11, of another alternative embodiment, with bistable compensated valve positioned respectively in the latching and tripping position of the circuit breaker.

En référence aux figures 1 à 3, le clapet hydraulique, désigné par le repère général 10, comporte un corps 12 fixe agencé entre un actionneur électrodynamique 14 et un vérin 15 de commande de déclenchement et d'enclenchement du mécanisme d'un disjoncteur haute tension. L'actionneur 14 comprend un propulseur bidirectionnel à double entrefer axial et à répulsion électrodynamique du type Thomson doté d'un disque 16 mobile intercalé entre deux bobines fixes d'enclenchement 18 et de déclenchement 20. Le disque 16 en matériau conducteur est solidaire d'une tige d'actionnement 22 montée à coulissement alterné dans un alésage 24 du corps 12 avec interposition d'un joint d'étanchéité 26 annulaire. Le clapet 10 comprend un organe obturateur 28 accouplé mécaniquement à la tige d'actionnement 22, et susceptible d'occuper deux positions longitudinales stables en fin de course d'enclenchement et de déclenchement respectivement lorsque le disque 16 est accolé contre la bobine 20 et la bobine 18 de l'actionneur14. L'organe obturateur28 comporte un cylindre 14. L'organe obturateur 28 comporte un cylindre creux 30 coaxial, de diamètre supérieur à celui de la tige 22, et coulissant à l'intérieur d'un alésage 32 central du corps 12 doté d'une gorge 34 annulaire de logement d'un joint d'étanchéité 36. L'une 38 des extrémités du cylindre 30 d'obturation est taillée en biseau et coopère en position d'enclenchement (fig. 1), après répulsion du disque 16 en direction de la bobine 20, avec un premier siège 40 circulaire ménagé coaxiale- ment dans le corps 12, et présentant un diamètre compris entre les diamètres externe et interne du cyiindre 30. L'extrémité opposée42 du cylindre 30 est munie d'un rebord 44 dont la face active 46 de forme tronconique vient en engagement en position de déclenchement avec un deuxième siège 48 circulaire du corps 12 lors de l'excitation de la bobine 20 et de la répulsion du disque 16 en direction de la bobine 18 adjacente. Les deux sièges 40, 48 du corps 12 sont séparés longitudinalement l'un de l'autre par une distance axiale prédéterminée d1, et la course de coulissement bidirectionnelle de l'organe obturateur 28 entre les deux sièges 40, 48 correspond exactement à celle du disque 16 entre les deux bobines 20, 18 de l'actionneur 14. Le rebord 44 est doté à l'opposé de la face 46 d'une face auxiliaire conformée en épauiement50 de diamètre supérieur à l'alésage central32, et venant en butée contre le tronçon central du corps 12 lorsque le clapet 10 se trouve en position d'enclenchement.With reference to FIGS. 1 to 3, the hydraulic valve, designated by the general reference 10, comprises a fixed body 12 arranged between an electrodynamic actuator 14 and a jack 15 for controlling the tripping and engagement of the mechanism of a high voltage circuit breaker . The actuator 14 comprises a bidirectional thruster with double axial air gap and electrodynamic repulsion of the Thomson type provided with a movable disc 16 interposed between two fixed engagement 18 and trigger 20 coils. The disc 16 of conductive material is integral with an actuating rod 22 mounted with alternating sliding in a bore 24 of the body 12 with the interposition of an annular seal 26. The valve 10 comprises a shutter member 28 mechanically coupled to the actuating rod 22, and capable of occupying two stable longitudinal positions at the end of the engagement and tripping travel respectively when the disc 16 is coupled against the coil 20 and the actuator coil 18 14. The shutter member 28 comprises a cylinder 14. The shutter member 28 comprises a coaxial hollow cylinder 30, of diameter greater than that of the rod 22, and sliding inside a central bore 32 of the body 12 provided with a annular groove 34 for housing a seal 36. One 38 of the ends of the shutter cylinder 30 is cut in a bevel and cooperates in the locked position (fig. 1), after repulsion of the disc 16 in the direction of the coil 20, with a first circular seat 40 formed coaxially in the body 12, and having a diameter between the external and internal diameters of the cylinder 30. The opposite end 42 of the cylinder 30 is provided with a flange 44 of which the active face 46 of frustoconical shape comes into engagement in the release position with a second circular seat 48 of the body 12 during the excitation of the coil 20 and the repulsion of the disc 16 in the direction of the adjacent coil 18. The two seats 40, 48 of the body 12 are separated longitudinally from one another by a predetermined axial distance d 1 , and the bidirectional sliding stroke of the shutter member 28 between the two seats 40, 48 corresponds exactly to that of the disc 16 between the two coils 20, 18 of the actuator 14. The flange 44 is provided, opposite the face 46, with an auxiliary face shaped as sparging 50 with a diameter greater than the central bore 32, and coming into abutment against the central section of the body 12 when the valve 10 is in the engaged position.

L'une 52 des faces frontales du corps 12 percé par l'alésage central 32 détermine avec le siège 48 adjacent un orifice 54 radial d'admission d'huile sous pression, en liaison avec un accumulateur oléopneumatique 56 ou un autre réservoir d'huile sous haute pression par un conduit d'alimentation 58. Le rebord 44 du cylindre 30 comprend une pluralité de trous 60 répartis cir- conférentiellement selon une couronne de diamètre inférieur à celui du siège 48, et faisant communiquer l'orifice d'admission 54 avec le conduit interne 62 du cylindre 30 creux en position d'enclenchement du clapet 10 pour l'alimentation du vérin 15 dont le remplissage assure le déplacement du piston 64 mobile dans le sens de la flèche F et la fermeture rapide des contacts du disjoncteur. La face frontale 66, opposée à celle 52 du corps 12, à alésage 32, forme avec le siège 40 juxtaposé un orifice d'échappement 68 en liaison par un conduit de refoulement 70 avec une bâche 72 à basse pression pour la mise à la purge du vérin 15 en position de déclenchement (fig.3) du clapet 10.One 52 of the front faces of the body 12 pierced by the central bore 32 determines with the seat 48 adjacent a radial orifice 54 for admission of pressurized oil, in connection with an oleopneumatic accumulator 56 or another high-pressure oil reservoir via a supply conduit 58. The flange 44 of the cylinder 30 comprises a plurality of holes 60 distributed circumferentially according to a crown of diameter smaller than that of the seat 48, and making the inlet orifice 54 communicate with the internal conduit 62 of the hollow cylinder 30 in the engagement position of the valve 10 for supplying the cylinder 15, the filling of which moves the movable piston 64 in the direction of arrow F and the rapid closing of the contacts of the circuit breaker. The front face 66, opposite that 52 of the body 12, with a bore 32, forms with the seat 40 juxtaposed an exhaust orifice 68 in connection with a discharge duct 70 with a tank 72 at low pressure for venting of the jack 15 in the release position (fig. 3) of the valve 10.

Le conduit d'alimentation 58 est équipé d'un gicleur d'admission 74 de dimension prédéterminée pour le réglage de la vitesse de fermeture des contacts, et le conduit de refoulement70 comporte d'une manière analogue un gicleur d'échappement 76 qui détermine la vitesse d'ouverture des contacts lors de la mise à la purge du vérin 15.The supply duct 58 is equipped with an inlet nozzle 74 of predetermined size for adjusting the speed of closing of the contacts, and the discharge duct 70 similarly includes an exhaust nozzle 76 which determines the opening speed of the contacts when the jack is vented 15.

Le clapet 10 est bistable et repose sur l'un des sièges 40, 48, de manière à raccorder sélectivement le vérin 15 de commande soit à l'accumulateur oléopneumatique 56 pour l'enclenchement du disjoncteur et le maintien en position fermée des contacts, soit à la bâche 72 pour la mise à la purge du vérin 15 lors du déclenchement du disjoncteur. En position d'enclenchement (fig. 1), l'organe obturateur 28 du clapet 10 vient en appui étanche sur le siège 40 pour fermer l'orifice d'échappement 68 vers la bâche 72 et ouvrir simultanément l'orifice d'admission 54 d'huile sous haute pression. En position de déclenchement (fig.3), l'organe obturateur 28 vient en engagement avec le siège 48 pour fermer l'orifice d'admission 54 et ouvrir simultanément l'orifice d'échappement 68 pour la vidange rapide du vérin 15. Chacune des deux positions d'enclenchement et de déclenchement du clapet 10 est stable, et le passage de l'une à l'autre est provoqué par le déplacement en translation du disque 16 de l'actionneur électrodynamique 14. Lors de la course de l'organe d'obturation 28 selon un sens prédéterminé, et notamment dans une position intermédiaire (fig. 2), les orifices d'admission 54 et d'échappement 68 sont partiellement ouverts et font communiquer l'accumulateur oléopneumatique 56 avec la bâche 72. Le débit d'huile chassé de l'accumulateur56 vers la bâche 72 est limité par les pertes de charge dans le conduit d'alimentation 58, le gicleur d'admission 74, la section de passage SA de l'huile dans l'orifice d'admission 54, variable selon la position du rebord 44, les trous 60 et le conduit interne 62 de l'organe obturateur 28. la section de passage SE de l'huile dans l'orifice d'échappement 68 variant en sens inverse de la section d'admission SA, le gicleur d'échappement 76 et le conduit de refoulement 70.The valve 10 is bistable and rests on one of the seats 40, 48, so as to selectively connect the actuator 15 either to the oleopneumatic accumulator 56 for switching on the circuit breaker and keeping the contacts in the closed position, or to the cover 72 for venting the jack 15 when the circuit breaker trips. In the latching position (fig. 1), the shutter member 28 of the valve 10 comes into leaktight abutment on the seat 40 to close the exhaust port 68 towards the tank 72 and simultaneously open the intake port 54 oil under high pressure. In the release position (fig.3), the shutter member 28 engages with the seat 48 to close the intake port 54 and simultaneously open the exhaust port 68 for rapid emptying of the jack 15. Each of the two engagement and tripping positions of the valve 10 is stable, and the passage from one to the other is caused by the displacement in translation of the disc 16 of the electrodynamic actuator 14. During the travel of the shutter member 28 in a predetermined direction, and in particular in an intermediate position (FIG. 2), the inlet 54 and exhaust 68 orifices are partially open and make the oleopneumatic accumulator 56 communicate with the tank 72. The flow of oil expelled from the accumulator 56 towards the tank 72 is limited by the pressure drops in the supply duct 58, the inlet nozzle 74, the passage section SA of the oil in the orifice inlet 54, variable according to the position of the flange 44, the holes 60 and l e internal duct 62 of the shutter member 28. the passage section SE of the oil in the exhaust orifice 68 varying in opposite direction from the intake section SA, the exhaust nozzle 76 and the duct repression 70.

Les forces hydrodynamiques engendrées par le passage de l'huile dans les sections SA et SE provoquent l'appui de l'organe obturateur 28 sur l'un des sièges 40, 48. Ces forces hydrodynamiques d'appui sur le clapet 10 sont variables en fonction de la position de l'organe 28 entre les deux positions extrêmes stables d'enclenchement et de déclenchement. La figure 8 montre la variation des forces F hydrodynamiques résultantes en fonction de la position x pour différentes valeurs décroissantes du gicleur d'admission 74 (courbes l, II, III), et on constate que dans la position médiane du clapet (position 0) les forces F sont pratiquement nulles. Cette position médiane constitue en quelque sorte un passage de point mort dont le franchissement dépend de la force de déplacement de la tige d'actionnement 22 lors de l'excitation de l'actionneur électrodynamique 14. Le rôle principal de ce dernier est d'assurer le passage brusque du point mort, et les forces F hydrodynamiques prennent ensuite le relais ou s'additionnent aux forces électrodynamiques de répulsion du disque 16 pour appliquer le clapet 10 sur l'un des sièges 40, 48, et le maintenir de manière stable dans cette position. On a constaté que les forces hydrodynamiques F s'exerçant sur le clapet 10 sont engendrées lorsque l'une des sections SA et SE de passage de l'huile dans le clapet était voisine de la plus petite des sections de passage du circuit hydraulique entre l'accumulateur 56 et la bâche 72, par exemple lorsque la section d'admission SA correspond à la section du gicleur 74. La courbe est une courbe optimum correspondant à une valeur prédéterminée du gicleur d'admission 74 supérieure à celle du gicleur de la courbe III dans laquelle l'effet mémoire risque d'être nul en cas de rebondissement du clapet 10 lors de sa venue sur le siège 40, 48 correspondant.The hydrodynamic forces generated by the passage of oil in the sections SA and SE cause the shutter member 28 to rest on one of the seats 40, 48. These hydrodynamic bearing forces on the valve 10 are variable in function of the position of the member 28 between the two stable end positions of engagement and tripping. FIG. 8 shows the variation of the resulting hydrodynamic forces F as a function of the position x for different decreasing values of the inlet nozzle 74 (curves l, II, III), and it can be seen that in the middle position of the valve (position 0) the forces F are practically zero. This median position constitutes in a way a dead center passage, the crossing of which depends on the displacement force of the actuating rod 22 during the excitation of the electrodynamic actuator 14. The main role of the latter is to ensure the sudden passage from neutral, and the hydrodynamic forces F then take over or add to the electrodynamic forces of repulsion of the disc 16 to apply the valve 10 to one of the seats 40, 48, and maintain it stably in this position. It has been found that the hydrodynamic forces F exerted on the valve 10 are generated when one of the sections SA and SE for the passage of the oil in the valve was close to the smallest of the sections for the passage of the hydraulic circuit between the accumulator 56 and tank 72, for example when the intake section SA corresponds to the section of the nozzle 74. The curve is an optimum curve corresponding to a predetermined value of the intake nozzle 74 greater than that of the nozzle of the curve III in which the memory effect is likely to be zero in the event of rebound of the valve 10 when it comes to the corresponding seat 40, 48.

Le fonctionnement du clapet hydraulique bistable selon les fig. à à 3 est le suivant :

  • Dans la position stable d'enclenchement (fig. 1), le disque 16 de l'actionneur électrodynamique 14 est accolé contre la bobine 20, et les forces hydrostatiques appliquent l'organe obturateur 28 sur le siège 40. L'orifice d'échappement 68 est fermé et l'ouverture de l'orifice d'admission 54 assure le passage de l'huile haute pression stockée dans l'accumulateur 56 vers le vérin de commande 15, qui maintient les contacts en position fermée.
The operation of the bistable hydraulic valve according to fig. to to 3 is as follows:
  • In the stable engagement position (fig. 1), the disc 16 of the electrodynamic actuator 14 is placed against the coil 20, and the hydrostatic forces apply the shutter member 28 to the seat 40. The exhaust port 68 is closed and the opening of the inlet port 54 ensures the passage of the high pressure oil stored in the accumulator 56 towards the control cylinder 15, which maintains the contacts in the closed position.

Le déclenchement du disjoncteur est commandé par l'excitation de la bobine de déclenchement 20 de l'actionneur 14, notamment au moyen d'une décharge d'un condensateur entraînant la répulsion électrodynamique du disque 16 conducteur en direction de la bobine 18 et le déplacement rapide de l'organe obturateur 28 vers le siège 48 opposé. Après passage du point mort dû aux forces électrodynamiques de l'actionneur 14 (fig. 2), l'organe obturateur 28 est aspiré par les forces hydrodynamiques engendrées dans la section décroissante d'admission SA du circuit hydraulique au niveau de l'orifice 54 et vient en appui sur le siège 48. Cette position 54 et vient en appui sur le siège 48. Cette position est stable lorsque le diamètre du siège 48 est supérieur à celui de l'alésage 32, et les orifices d'admission 54 et d'échappement 68 sont respectivement fermé et ouvert pour la mise à la purge du vérin 15 à la bâche 72 entraînant l'ouverture rapide des contacts.The tripping of the circuit breaker is controlled by the excitation of the tripping coil 20 of the actuator 14, in particular by means of a discharge of a capacitor causing the electrodynamic repulsion of the conductive disc 16 in the direction of the coil 18 and the displacement fast from the shutter member 28 to the opposite seat 48. After passing neutral from the electrodynamic forces of the actuator 14 (fig. 2), the shutter member 28 is sucked in by the hydrodynamic forces engen drées in the decreasing section of admission SA of the hydraulic circuit at the level of the orifice 54 and comes to bear on the seat 48. This position 54 and comes to bear on the seat 48. This position is stable when the diameter of the seat 48 is greater than that of the bore 32, and the inlet 54 and exhaust 68 ports are respectively closed and open for venting the jack 15 to the cover 72 causing the rapid opening of the contacts.

Le réenclenchement s'effectue lors de l'excitation de la bobine 18 d'enclenchement qui provoque la répulsion électrodynamique du disque 16 en direction de la bobine 20. La course en translation du disque 16 est identique à celle de l'organe obturateur 28, qui après franchissement du point mort en position médiane (fig. 2) est sollicité en appui stable sur le siège 40 par les forces hydrodynamiques engendrées dans la section décroissante d'échappement SE au voisinage de l'orifice 68. Le clapet 10 se retrouve ensuite dans la position d'enclenchement représentée à la fig. 1.The resetting is carried out during the excitation of the engagement coil 18 which causes the electrodynamic repulsion of the disc 16 in the direction of the coil 20. The translational travel of the disc 16 is identical to that of the shutter member 28, which after crossing the neutral position in the middle position (fig. 2) is urged into stable support on the seat 40 by the hydrodynamic forces generated in the decreasing exhaust section SE in the vicinity of the orifice 68. The valve 10 is then found in the latching position shown in fig. 1.

Un étage amplificateur intermédiaire (non représenté) peut être disposé en aval du vérin pour être commandé par le clapet 10.An intermediate amplifier stage (not shown) can be arranged downstream of the jack to be controlled by the valve 10.

Pour éviter le matage du clapet 10 dû à la propulsion rapide de l'actionneur électrodynamique 14, l'organe d'obturation 28 vient en engagement contre le siège correspondant 48 ou 40 à vitesse réduite grâce à deux amortisseurs 80, 82 (fig. 6 et 7) hydrauliques actifs au voisinage des deux positions de déclenchement et d'enclenchement, et intégrés à l'intérieur du corps 12 du clapet 10. L'amortisseur 80 comporte un épaulement 84 ménagé à la jonction de la tige d'actionnement 22 avec le rebord 44 du cylindre 30, et jouant le rôle de piston susceptible de coulisser en fin de course de déclenchement dans une gorge 86 annulaire du corps 12, de diamètre supérieur à celui de l'alésage 24. La compression de l'huile dans la gorge 86 freine l'équipage mobile formé par la tige 22 et l'organe d'obturation 28 en assurant une arrivée lente de ce dernier sur le siège 48. L'amortisseur 82 comprend d'une manière similaire un gradin 88 sur l'épaulement 50 du rebord 44, et une gorge 90 annulaire dans l'alésage central 32 du corps 12. Le gradin 88 joue le rôle de piston de compression de l'huile dans la gorge 90 en fin de course d'enclenchement et provoque un engagement sans rebond de l'organe 28 sur le siège 40.To prevent the valve 10 from matting due to the rapid propulsion of the electrodynamic actuator 14, the shutter member 28 engages against the corresponding seat 48 or 40 at reduced speed thanks to two dampers 80, 82 (fig. 6 and 7) hydraulics active in the vicinity of the two triggering and latching positions, and integrated inside the body 12 of the valve 10. The damper 80 comprises a shoulder 84 formed at the junction of the actuating rod 22 with the rim 44 of the cylinder 30, and playing the role of piston capable of sliding at the end of the triggering stroke in an annular groove 86 of the body 12, of diameter greater than that of the bore 24. The compression of the oil in the groove 86 brakes the moving element formed by the rod 22 and the shutter member 28 ensuring a slow arrival of the latter on the seat 48. The damper 82 similarly includes a step 88 on the shoulder 50 of flange 44, and an annular groove 90 in al central bore 32 of the body 12. The step 88 plays the role of oil compression piston in the groove 90 at the end of the engagement stroke and causes a rebound engagement of the member 28 on the seat 40.

Selon la variante de réalisation illustrée aux fig. 4 et 5, les mêmes repères désignent des pièces identiques ou similaires à celles des figs. 1 à 3. Le clapet 10 est équipé d'un tiroir 100 cylindrique associé au siège 48 du corps 12, de manière à coopérer avec le rebord 44 de l'organe d'obturation 28 en fin de course de déclenchement (fig.5) pour augmenter l'effet des forces hydrodynamiques lors de la fermeture du tiroir 100. Il en résulte une meilleure stabilité de l'organe d'obturation 28 en position de déclenchement, indépendamment de la dimension du gicleur d'admission 74. Le siège 48 sur lequel s'appuie l'organe 28 est situé entre l'alésage 24 et le tiroir 100.According to the variant embodiment illustrated in FIGS. 4 and 5, the same references designate parts which are identical or similar to those of FIGS. 1 to 3. The valve 10 is equipped with a cylindrical drawer 100 associated with the seat 48 of the body 12, so as to cooperate with the flange 44 of the shutter member 28 at the end of the triggering stroke (FIG. 5) to increase the effect of hydrodynamic forces when closing the drawer 100. This results in better stability of the shutter member 28 in the release position, regardless of the size of the inlet nozzle 74. The seat 48 on which is supported by the member 28 is located between the bore 24 and the slide 100.

Lors du déplacement du clapet 10 vers la position d'enclenchement (fig.4), l'épaulement 50 du rebord 44 comprime l'huile contenue dans la cavité 102 située entre le tiroir 100 et le gicleur d'admission 74. Pour éviter une montée en pression dans la cavité 102, cette dernière est mise en communication avec un amortisseur oléopneumatique 104 à membrane 106, ou autre accumulateur anti-coup de bélier dont le faible volume est en surpression par rapport à la pression de l'huile dans l'accumulateur 56. Le reste du fonctionnement est identique à celui décrit en référence aux fig. 1 et 3.During the movement of the valve 10 towards the latching position (FIG. 4), the shoulder 50 of the flange 44 compresses the oil contained in the cavity 102 located between the drawer 100 and the inlet nozzle 74. To avoid a pressure build-up in the cavity 102, the latter is placed in communication with an oleopneumatic damper 104 with membrane 106, or other anti-water hammer accumulator whose small volume is overpressure relative to the pressure of the oil in the accumulator 56. The rest of the operation is identical to that described with reference to FIGS. 1 and 3.

Selon une autre variante représentée aux figs. 6 et 7, l'amortisseur oléopneumatique 104 est remplacé par un gicleur 110 unidirectionnel inséré dans le circuit hydraulique entre le conduit d'alimentation 58 de l'accumulateur 56 et l'orifice d'admission 54 de la cavité 102. Un ressort 112 sollicite le gicleur 110 en appui sur un rebord 114 du tiroir 100 ; en cas de surpression de l'huile dans la cavité 102 intervenant lors de l'enclenchement, le déplacement radial du gicleur 110 à l'encontre du ressort 112 permet une expansion de l'huile dans un évidement 116 et dans l'accumulateur 56.According to another variant shown in FIGS. 6 and 7, the oleopneumatic damper 104 is replaced by a unidirectional nozzle 110 inserted in the hydraulic circuit between the supply duct 58 of the accumulator 56 and the inlet orifice 54 of the cavity 102. A spring 112 urges the nozzle 110 resting on a flange 114 of the drawer 100; in the event of overpressure of the oil in the cavity 102 occurring during the engagement, the radial displacement of the nozzle 110 against the spring 112 allows an expansion of the oil in a recess 116 and in the accumulator 56.

Les deux variantes des figs. 4 à 7 peuvent être équipées côté basse pression d'un tiroir 120 cylindrique ménagé dans le corps 12 entre l'orifice d'échappement 68 et le siège 40 (fig. 9). L'extrémité 38 de l'organe d'obturation 28 coopère avec le tiroir 120 en fin de course d'enclenchement pour augmenter l'effet des forces hydrodynamiques et la stabilité du clapet 10 en position d'enclenchement.The two variants of figs. 4 to 7 can be fitted on the low pressure side with a cylindrical slide 120 formed in the body 12 between the exhaust orifice 68 and the seat 40 (fig. 9). The end 38 of the closure member 28 cooperates with the slide 120 at the end of the interlocking stroke to increase the effect of the hydrodynamic forces and the stability of the valve 10 in the interlocking position.

Selon les variantes des figures 10 à 16, l'actionneur électrodynamique 14 du type à effet Thomson à doubles bobines 18, 20, de commande d'enclenchement et de déclenchement est remplacé par un dispositif hydraulique 200 à piston différentiel 202 d'actionnement de l'organe obturateur 28. Les mêmes numéros de repère désignent des pièces identiques ou similaires à celles représentées aux figures 1 à 9.According to the variants of FIGS. 10 to 16, the electrodynamic actuator 14 of the Thomson effect type with double coils 18, 20, for switching on and off control is replaced by a hydraulic device 200 with differential piston 202 for actuating the shutter member 28. The same reference numerals designate parts which are identical or similar to those shown in FIGS. 1 to 9.

En référence aux figures 10 et 11, on reconnaît en particulier le cylindre 30 creux de l'organe obturateur 28 monté à coulissement à l'intérieur d'un alésage 32 entre deux positions longitudinales stables de fin de course d'enclenchement et de déclenchement. L'une 38 des extrémités de l'organe obturateur 28 cylindrique est taillée en biseau et vient en engagement en position d'enclenchement (fig. 10) avec le siège 40 circulaire pour obturer l'orifice d'échappement 68 du conduit de refoulement 70 en liaison avec une bâche (non représentée) à basse pression. L'extrémité opposée 42 du cylindre 30 comporte un rebord 44 à face active 46 tronconique coopérant en position de déclenchement (fig. 11) avec le deuxième siège 48 circulaire pour obturer l'orifice d'admission 54 d'huile sous pression, relié à un accumulateur (non représenté) à haute pression par un conduit d'alimentation 58. Le rebord 44 comprend une pluralité de trous 60 faisant communiquer l'orifice d'admission 54 avec le conduit interne 62 du cylindre 30 creux en position d'enclenchement du clapet 10 pour l'alimentation du vérin (non représenté) de commande de fermeture des contacts du disjoncteur. L'extrémité 42 du cylindre 30 est raccordée par la tige d'actionnement 22 au piston différentiel202 de commande susceptible de coulisser dans un cylindre 204 fixe du corps 12. Le piston 202 comporte deux faces actives 206, 208 coopérant avec les fonds opposés du cylindre 204 pour délimiter deux chambres 210, 212 élémentaires en communication avec l'accumulateur haute pression par deux conduits d'alimentation 214, 216. Le volume des chambres 210, 212 varie en sens inverse l'un de l'autre selon le sens de déplacement du piston 202 différentiel piloté par la mise en dépression de l'une des chambres.With reference to FIGS. 10 and 11, it is recognized in particular the hollow cylinder 30 of the shutter member 28 slidably mounted inside a bore 32 between two stable longitudinal positions at the end of the engagement and tripping travel. One 38 of the ends of the cylindrical shutter member 28 is cut in a bevel and comes into engagement in the latching position (fig. 10) with the circular seat 40 to close the exhaust orifice 68 of the discharge duct 70 in conjunction with a low pressure tank (not shown). The opposite end 42 of the cylinder 30 has a flange 44 with an active frustoconical face 46 cooperating in the release position (FIG. 11) with the second circular seat 48 for closing the inlet port 54 for pressurized oil, connected to a high pressure accumulator (not shown) by a supply line 58. The flange 44 comprises a plurality of holes 60 communicating the inlet port 54 with the internal conduit 62 of the hollow cylinder 30 in the engagement position of the valve 10 for supplying the actuator (not shown) for closing the contacts of the circuit breaker. The end 42 of the cylinder 30 is connected by the actuating rod 22 to the differential control piston 202 capable of sliding in a fixed cylinder 204 of the body 12. The piston 202 has two active faces 206, 208 cooperating with the opposite bottoms of the cylinder 204 to delimit two elementary chambers 210, 212 in communication with the high pressure accumulator by two supply conduits 214, 216. The volume of chambers 210, 212 varies in opposite directions from one another according to the direction of movement of the differential piston 202 controlled by the depression of one of the chambers.

En position d'enclenchement (fig. 10), l'organe obturateur 28 se trouve en appui stable sur le siège 40 après mise en dépression de la chambre 210 du dispositif hydraulique 200. Le déclenchement est commandé par la mise en dépression de l'autre chambre 212 entraînant la translation du piston différentiel 202 vers la droite et la venue en butée de l'organe obturateur 28 contre le siège 48 (fig. 11), de manière à fermer l'orifice d'admission 54 et à ouvrir simultanément l'orifice d'échappement 68 pour la mise à la purge du vérin.In the engagement position (fig. 10), the shutter member 28 is in stable abutment on the seat 40 after the chamber 210 of the hydraulic device 200 has been placed under vacuum. Triggering is controlled by placing the vacuum under pressure. another chamber 212 causing the differential piston 202 to translate to the right and the stop member 28 coming into abutment against the seat 48 (fig. 11), so as to close the intake orifice 54 and simultaneously open l 'exhaust port 68 for venting the cylinder.

Les figures 12 à 16 représentent quatre variantes de réalisation utilisant le principe du piston différentiel 202 du dispositif de commande hydraulique200, illustré aux figures 11 et 12.FIGS. 12 to 16 represent four alternative embodiments using the principle of the differential piston 202 of the hydraulic control device 200, illustrated in FIGS. 11 and 12.

En référence à la figure 12, à chaque chambre élémentaire 210, 212 est associé un clapet auxiliaire de purge rapide 220, 222 actionné par un propulseur électrodynamique 224, 226 à effet Thomson. Chaque propulseur 224, 226 comporte une bobine 228, 230 de commande disposée en regard d'un disque 232, 234 mobile en matériau conducteur, associé à un percuteur 236, 238 coopérant avec le clapet de purge 220, 222 correspondant. Ce dernier est agencé dans chaque chambre 210, 212 et est sollicité en position de fermeture par l'intermédiaire d'un organe élastique, notamment un ressort de rappel 240, 242, qui maintient le clapet de purge correspondant en appui étanche contre un siège 243, 245 tant que le propulseur 224, 226 reste en position inactive de désexcitation de la bobine 228, 230. Le conduit d'alimentation 214, 216 en huile haute pression de chaque chambre 210, 212 est doté d'un gicleur d'admission 244, 246, disposé à l'opposé du clapet de purge 220, 222 par rapport à la direction axiale du cylindre 204. Chaque siège 243, 245 présente une section supérieure à celle du gicleur 244, 246 correspondant et est relié par un conduit de refoulement à un compartiment 250 basse pression en liaison avec la bâche.With reference to FIG. 12, each elementary chamber 210, 212 is associated with an auxiliary rapid purge valve 220, 222 actuated by an electrodynamic propellant 224, 226 with Thomson effect. Each thruster 224, 226 comprises a control coil 228, 230 disposed opposite a movable disc 232, 234 of conductive material, associated with a striker 236, 238 cooperating with the corresponding purge valve 220, 222. The latter is arranged in each chamber 210, 212 and is biased in the closed position by means of an elastic member, in particular a return spring 240, 242, which maintains the corresponding purge valve in sealed contact against a seat 243 , 245 as long as the propellant 224, 226 remains in the inactive de-excitation position of the coil 228, 230. The supply line 214, 216 for high pressure oil from each chamber 210, 212 is provided with an intake nozzle 244 , 246, arranged opposite the purge valve 220, 222 with respect to the axial direction of the cylinder 204. Each seat 243, 245 has a section greater than that of the corresponding nozzle 244, 246 and is connected by a discharge conduit to a low pressure compartment 250 in connection with the cover.

Le fonctionnement du dispositif de commande hydraulique 200 selon la figure 12 est le suivant :The operation of the hydraulic control device 200 according to FIG. 12 is as follows:

L'enclenchement du disjoncteur intervient après excitation de la bobine de commande 228 du propulseur 224 à répulsion électrodynamique dont le percuteur 236 provoque l'ouverture du clapet de purge 220 pendant un temps prédéterminé, par exemple de l'ordre de la milliseconde. Il en résulte la décompression de la chambre 210 et le refoulement de l'huile contenue dans la chambre 210 vers le compartiment 250 à basse pression. Le piston différentiel 202 est alors sollicité en translation axiale dans le sens de la flèche Fi, et applique l'organe d'obturation 28 sur le siège 40, de manière à ouvrir l'orifice d'admission 54 et à fermer simultanément l'orifice d'échappement 68.The circuit breaker is engaged after excitation of the control coil 228 of the thruster 224 with electrodynamic repulsion, the striker 236 of which opens the purge valve 220 for a predetermined time, for example of the order of a millisecond. This results in the decompression of the chamber 210 and the discharge of the oil contained in the chamber 210 to the compartment 250 at low pressure. The differential piston 202 is then biased in axial translation in the direction of the arrow F i , and applies the shutter member 28 to the seat 40, so as to open the intake port 54 and simultaneously close the exhaust port 68.

Le déclenchement s'effectue par excitation de la bobine 230 du propulseur 226 entraînant l'ouverture du clapet de purge 222 et la décompression de la chambre 212 dont l'huile est refoulée vers le compartiment 250 à basse pression. Le piston différentiel 202 est actionné en translation axiale suivant la flèche F2 jusqu'à la venue en engagement de l'organe d'obturation 28 contre le siège 48 provoquant la fermeture de l'orifice d'admission 54 et l'ouverture simultanée de l'orifice d'échappement 68.The triggering is carried out by excitation of the coil 230 of the propellant 226 causing the opening of the purge valve 222 and the decompression of the chamber 212 whose oil is discharged towards the compartment 250 at low pressure. The differential piston 202 is actuated in axial translation along the arrow F 2 until the closure member 28 engages against the seat 48 causing the admission orifice 54 to close and the simultaneous opening of the exhaust port 68.

Selon une variante de réalisation (non représentée) de la figure 12, le piston différentiel 202 est pourvu d'un conduit de communication des deux chambres 210, 212 permettant la suppression de l'un des conduits d'alimentation 214, 216.According to an alternative embodiment (not shown) of FIG. 12, the differential piston 202 is provided with a communication conduit of the two chambers 210, 212 allowing the elimination of one of the supply conduits 214, 216.

La structure des clapets de purge rapide 220, 222 peut être d'un type quelconque, notamment à portée tronconique ou sphérique coopérant avec les sièges 243, 245 circulaires. Les commandes d'enclenchement et de déclenchement résultent de la décompression de l'une des chambres 210, 212, suite à un choc impulsionnel de l'un des percuteurs 236, 238 sur le clapet de purge 220, 222 correspondant qui reste ouvert un temps très court. L'énergie de commande des propulseurs 224, 226 est nettement inférieure à celle nécessaire au déplacement de l'organe d'obturation 28 du clapet 10 suivant les figures 1 à 9.The structure of the rapid purge valves 220, 222 can be of any type, in particular with frustoconical or spherical bearing cooperating with the circular seats 243, 245. The switching on and off commands result from the decompression of one of the chambers 210, 212, following an impulse shock from one of the strikers 236, 238 on the corresponding purge valve 220, 222 which remains open for a time very short. The control energy of the thrusters 224, 226 is much lower than that necessary for the displacement of the shutter member 28 of the valve 10 according to FIGS. 1 to 9.

En référence à la figure 13, représentant une variante de la figure 12, les conduits d'alimentation 214, 216 d'huile à haute pression débouchent dans les fonds 252, 254 opposés du cylindre 204, au voisinage des clapets de purge 220, 222. Chacun de ces clapets présente une extrémité en tiroir, qui obture le conduit 214, 216 correspondant lors de l'excitation de l'une des bobines 228, 230 des propulseurs 224, 226. L'obturation des conduits 214, 216 dès le début d'ouverture des clapets de purge 220, 2222 permet une économie d'huile de commande contenue dans l'accumulateur oléopneumatique ou autre réservoir d'huile sous haute pression, et accélère la décompression des chambres 210, 212.With reference to FIG. 13, representing a variant of FIG. 12, the supply lines 214, 216 of high pressure oil open into the opposite bottoms 252, 254 of the cylinder 204, in the vicinity of the purge valves 220, 222 Each of these valves has a drawer end, which closes the corresponding conduit 214, 216 when one of the coils 228, 230 of the thrusters 224, 226 is energized. Closure of the conduits 214, 216 from the start opening the purge valves 220, 2222 allows a saving of control oil contained in the oleopneumatic accumulator or other high pressure oil tank, and accelerates the decompression of the chambers 210, 212.

Selon le dispositif de la figure 14, les sièges 243, 245 des clapets de purge 220, 222 sont ménagés dans les fonds opposés 252, 254 du cylindre 204. Les percuteurs 236, 238 des propulseurs 224, 226 électrodynamiques se déplacent en sens inverse l'un de l'autre selon une direction parallèle à celle de translation axiale du piston différentiel 202. Le corps de chaque clapet de purge 220, 222 comporte une première portion 260 tronconique coopérant en position de fermeture avec le siège correspondant 243, 245, une deuxième portion latérale 262 intermédiaire de forme cylindrique susceptible d'obturer le conduit d'alimentation 214, 216 d'huile à haute pression au début de la course d'ouverture du clapet et une troisième portion 264 cylindrique en forme de piston de diamètre inférieur à celui de la portion intermédiaire 262. Chaque clapet de purge 220, 222 est pourvu d'une pluralité de trous 266 faisant communiquer les conduits d'alimentation 214, 216 d'huile à haute pression avec les chambres 210, 212 en position inactive des propulseurs 224, 226 correspondant à la fermeture des clapets de purge. Lors de l'ouverture de l'un des clapets de purge le piston de la troisième portion 264 se déplace dans un logement 268 central du compartiment 250 à basse pression relié à la bâche. Un joint 270 torique fixe entoure le piston 264 de chaque clapet 220, 222, compensé et assure l'étanchéité entre le logement 268 à basse pression et les chambres 210, 212 du dispositif hydraulique 200.According to the device of FIG. 14, the seats 243, 245 of the purge valves 220, 222 are formed in the opposite bottoms 252, 254 of the cylinder 204. The strikers 236, 238 of the electrodynamic thrusters 224, 226 move in opposite direction l '' from one another in a direction parallel to that of axial translation of the piston differential 202. The body of each purge valve 220, 222 comprises a first frustoconical portion 260 cooperating in the closed position with the corresponding seat 243, 245, a second intermediate lateral portion 262 of cylindrical shape capable of closing the supply duct 214, 216 of high pressure oil at the start of the valve opening stroke and a third cylindrical portion 264 in the shape of a piston with a diameter less than that of the intermediate portion 262. Each bleed valve 220, 222 is provided with 'A plurality of holes 266 communicating the supply lines 214, 216 of high pressure oil with the chambers 210, 212 in the inactive position of the thrusters 224, 226 corresponding to the closing of the purge valves. When one of the purge valves opens, the piston of the third portion 264 moves into a central housing 268 of the low pressure compartment 250 connected to the tank. A fixed O-ring 270 surrounds the piston 264 of each valve 220, 222, compensated and provides sealing between the housing 268 at low pressure and the chambers 210, 212 of the hydraulic device 200.

Le fonctionnement du dispositif de la figure 14 est similaire à celui de la figure 13, la seule différence étant l'utilisation de clapets de purge 220, 222 compensés, ayant chacun une extrémité conformée en piston 264 déplaçable dans le logement 268 à basse pression.The operation of the device of FIG. 14 is similar to that of FIG. 13, the only difference being the use of purge valves 220, 222 compensated, each having an end shaped as a piston 264 displaceable in the housing 268 at low pressure.

Selon une autre variante illustrée aux figures 15 et 16, le piston différentiel 202 de commande du clapet 10 bistable fait partie intégrante de l'organe d'obturation 28. L'une 206 des faces actives du piston différentiel est formée par un épaulement situé dans la zone médiane du cylindre 30. L'autre 208 face active du piston différentiel est constituée par un embout 272 cylindrique massif agencé à l'opposé de l'extrémité 38 du cylindre 30, de manière à coulisser dans un alésage 274 du corps 12. La face 206 délimite la chambre élémentaire 210 ménagée dans le corps 12 entre le conduit de refoulement 70 et le conduit 58, et en communication avec l'accumulateur haute pression par le conduit d'alimentation 214 doté du gicleur d'admission 244. La décompression de la chambre 210 par l'ouverture du clapet à bille de purge rapide 224 entraîne l'actionnement de l'organe obturateur 28 vers la position d'enclenchement (fig. 15). L'autre face 208 délimite la deuxième chambre élémentaire 212 agencée à l'opposé du vérin de commande du disjoncteur, et en communication avec l'accumulateur haute pression par le conduit d'alimentation 216 à gicleur 246. Un clapet à bille 226 de purge rapide est associé à la chambre 212 dont la décompression lors de l'ouverture du clapet de purge 226 provoque la venue en engagement de l'organe obturateur 28 contre le siège 48, suivi du déclenchement du disjoncteur (fig. 16).According to another variant illustrated in FIGS. 15 and 16, the differential piston 202 for controlling the bistable valve 10 forms an integral part of the closure member 28. One 206 of the active faces of the differential piston is formed by a shoulder located in the central zone of the cylinder 30. The other 208 active face of the differential piston is constituted by a solid cylindrical end piece 272 arranged opposite the end 38 of the cylinder 30, so as to slide in a bore 274 of the body 12. The face 206 delimits the elementary chamber 210 formed in the body 12 between the discharge conduit 70 and the conduit 58, and in communication with the high pressure accumulator by the supply conduit 214 provided with the intake nozzle 244. Decompression of the chamber 210 by the opening of the rapid purge ball valve 224 causes the shutter member 28 to be actuated towards the latching position (fig. 15). The other face 208 delimits the second elementary chamber 212 arranged opposite the circuit breaker control cylinder, and in communication with the high pressure accumulator by the supply duct 216 with a nozzle 246. A ball valve 226 for purging rapid is associated with chamber 212, the decompression of which when the purge valve 226 opens causes the shutter member 28 to engage with the seat 48, followed by tripping of the circuit breaker (fig. 16).

L'invention n'est bien entendu nullement limitée aux modes de mise en oeuvre plus particulièrement décrits et représentés aux dessins annexés, mais elle s'étend bien au contraire à toute variante restant dans le cadre des équivalences mécaniques et hydrauliques.The invention is of course in no way limited to the modes of implementation more particularly described and shown in the accompanying drawings, but it extends quite the contrary to any variant remaining within the framework of mechanical and hydraulic equivalences.

Claims (12)

1. Hydraulically-actuated operating system of a jack associated with a switching operation mechanism of a high tension circuit breaker for closing and opening of the contacts, said device including :
- an accumulator (56) filled with oil under pressure,
- a lower pressure sump (72) for the leakage of the jack (15) oil when the tripping occurs,
- an hydraulic poppet valve (10) to selectively connect the jack (15), either to the accumulator (56) for closure and hold of the contacts in switch-off position, or to the sump (72) for venting when the tripping occurs,
- supply (58) and back-flow (70) ducts for the connection of the poppet valve to the accumulator (56) and to the sump (72) respectively,
- a fixed body (12) equipped with a first seat (40) located in close proximity to a leakage port (68) of a back-flow duct (70), and with a second seat (48) located in close proximity to an inlet port (54) of the supply duct (58), the two seats (40, 48) being shifted from each other by a predetermined axial gap,
- and a propelling unit (14, 200), capable of moving the poppet valve between the two seats (40, 48) of said gap to ensure closure or tripping of the circuit breaker, said poppet valve (10) comprising a closing member (28) capable of sliding in a reaming (32) of the body (12), characterized in that the closing member (28) of the poppet valve (10) is stable in the two farthest positions of limit closure and tripping, and is formed by an hollow cylinder (30) comprising :
- a first supporting face (38) at one of the cylinder (30) ends being brought into stable engagement in limit closure against the first seat (40) disposed between the back-flow duct (70) and the jack, (15) duct (62a),
- a second supporting face (42) at the opposite end of the cylinder (30) cooperating in stable position of limit tripping with the second seat .(48) located between the supply duct (58) and the propelling unit (14, 200), the last one being mechanically coupled to the cylinder (30) on the side of said second supporting face (42),
- and an inner duct (62b) opening at the two ends of the cylinder (30) by opposite apertures, each showing a size lower than the corresponding seat (40, 48) one.
2. Hydraulically-actuated operating system of a jack, according to claim 1, characterized in that the opposite supporting face (38, 42) of the cylinder (30) define with said first and second seats (40, 48) sections of oil passage in the leakage (68) or inlet (54) ports, said sections varying in the opposite direction from each other for a determined direction of the cylinder (30) travel showing in an intermediate position a dead point passage, the clearing of which is ensured by the driving forces of the propelling unit (14, 200) being previously exerted before the action of the hydrodynamic forces generated in the corresponding passage section in limit closure or tripping.
3. Hydraulically-actuated operating system of a jack, according to claim 1 or 2, characterized in that said supply duct (58) of the accumulator (56) is equipped with an inlet nozzle (74) of predetermined size in close proximity to said second seat (48) for the closure speed regulation.
4. Hydraulically-actuated operating system of a jack, according to claim 1, 2 or 3, characterized in that said back-flow duct (70) for the jack (15) venting encloses a leakage nozzle (76) settling the tripping speed.
5. Hydraulically-actuated operating system of a jack, according to one of the claims 2 to 4, characterized in that a slide valve (120, 100) accommodated in said body (12) of the poppet valve (10) is associated with first (40) and second (48) seats to cooperate with the corresponding supporting faces (38, 42) of the closing member in limit closure and tripping respectively, so as to increase the effect of the supporting hydrodynamic forces when said slide valve closes, and the closing member stability in closure and tripping positions.
6. Hydraulically-actuated operating system of a jack, according to claim 5, characterized in that each slide valve (100, 120) is disposed between the second seat (48) and the inlet port (54) in close proximity to the tripping position, and between the first seat (40) and the leakage port (68) in close proximity to the closure position respectively.
7. Hydraulically-actuated operating system of a jack, according to one of the former claims, characterized in that a shock suppression device, in particular an oleopneumatic damper (104) or an unidirectional nozzle (110), cooperates with the hydraulic circuit in close proximity to said inlet port (54) to avoid an inner over-pressure of the poppet valve oil when it travels toward the closure position.
8. Hydraulically-actuated operating system of a jack, according to any of the claims 2 to 7, characterized in that said propelling unit comprises an actuator with electrodynamic repulsion (14), with conducting movable disk (16) inserted in an axial air-gap accomodated outside the body (12) of the poppet valve between two closure and tripping stationary coils (18, 20) of which the selective excitation by capacitor discharge induces the electrodynamic repulsion of the disk (16) in a determined direction to ensure the clearing of the cylinder (30) dead point toward closure or tripping position.
9. Hydraulically-actuated operating system of a jack, according to any of the claims 1 to 7, characterized in that the propelling unit (200) of the closing member (28) comprises an hydraulic differential piston (202) having two active faces (206, 208) sensitive to the pressure variation of the control oil contained in two elementary chambers (210, 212), each equipped with an auxiliary poppet valve (220, 222), so that the fast opening of one of them induces the depressing or compressing of the corresponding chamber (210, 212) followed by the displacement of the differential piston (202) in a determined direction.
10. Hydraulically-actuated operating system of a jack, according to claim 9, characterized in that each elementary chamber (210, 212) communicates with the accumulator (56) by a supply duct (214, 216) and that each auxiliary poppet valve (220, 222) cooperates with an electrodynamic release (224, 226) with striker (236, 238) to induce in active position the depressing of one of the chambers (210, 212) by opening the corresponding poppet valve and the oil leakage toward a compartment (250) in connection with the sump (72).
11. Hydraulically-actuated operating system of a jack, according to claim 10, characterized in that each auxiliary poppet valve (220, 222) for rapid venting is disposed to close the supply duct (214, 216) of the corresponding chamber (210, 212) at the beginning of its opening travel.
12. Hydraulically-actuated operating system of a jack, according to claim 9, 10 or 11, characterized in that said differential piston (202) to control the bistable poppet valve (10) is part and parcel of the closing member (28), one of the active faces of the piston being formed by a shoulder (206) located in the median zone of the cylinder (30), and the other face being constituted by a solid cylindrical tip (272) opposite the first supporting face (38).
EP19800401062 1979-07-16 1980-07-15 Bistable hydraulic valve for operating a piston of a fast high tension circuit breaker Expired EP0022729B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7918757A FR2462015A1 (en) 1979-07-16 1979-07-16 BISTABLE HYDROLIC VALVE ASSOCIATED WITH ELECTRODYNAMIC PROPELLER FOR CONTROLLING A HIGH VOLTAGE FAST CIRCUIT BREAKER
FR7918757 1979-07-16

Publications (2)

Publication Number Publication Date
EP0022729A1 EP0022729A1 (en) 1981-01-21
EP0022729B1 true EP0022729B1 (en) 1983-02-16

Family

ID=9228089

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800401062 Expired EP0022729B1 (en) 1979-07-16 1980-07-15 Bistable hydraulic valve for operating a piston of a fast high tension circuit breaker

Country Status (4)

Country Link
EP (1) EP0022729B1 (en)
JP (1) JPS5615516A (en)
DE (1) DE3062026D1 (en)
FR (1) FR2462015A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0750799Y2 (en) * 1987-10-14 1995-11-15 カシオ計算機株式会社 Tone phase synchronizer
CN112503044B (en) * 2020-03-20 2022-12-16 国网上海市电力公司 Hydraulic control valve and hydraulic operating mechanism

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2765378A (en) * 1953-05-26 1956-10-02 Allis Chalmers Mfg Co Circuit breaker with hydraulic motor controlled by a hydraulically biased valve
SE321020B (en) * 1968-07-16 1970-02-23 Asea Ab
US3764944A (en) * 1972-07-06 1973-10-09 C Erven Spiral motor coil
US4118613A (en) * 1977-06-27 1978-10-03 General Electric Company Hydraulically-actuated operating system for an electric circuit breaker

Also Published As

Publication number Publication date
DE3062026D1 (en) 1983-03-24
FR2462015B1 (en) 1982-01-22
EP0022729A1 (en) 1981-01-21
JPS5615516A (en) 1981-02-14
FR2462015A1 (en) 1981-02-06

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