FR2462015A1 - BISTABLE HYDROLIC VALVE ASSOCIATED WITH ELECTRODYNAMIC PROPELLER FOR CONTROLLING A HIGH VOLTAGE FAST CIRCUIT BREAKER - Google Patents

Abstract

THE INVENTION RELATES TO A BISTABLE HYDRAULIC VALVE WITH AN ELECTRODYNAMIC ACTUATOR FOR THE CONTROL OF A CYLINDER. THE VALVE 10 INCLUDES A SHUTTER 28 MOUNTED WITH BIDIRECTIONAL SLIDING IN A BODY 12 BETWEEN A FIRST AND A SECOND SEATS 40, 48 FIXED DURING THE EXCITATION OF AN ACTUATOR 14 WITH THOMSON EFFECT FOR THE SELECTIVE COMMUNICATION OF ' A CYLINDER EITHER A PRESSURIZED OIL ACCUMULATOR 56 OR A BLEEDING TANK 72. A DRAWER 100 IS ORGANIZED IN THE BODY 12 BETWEEN THE SEAT 48 AND THE INTAKE PORT 54 TO COOPERATE WITH THE FLANGE 44 AT THE TRIP LIMIT SWITCH SO AS TO INCREASE THE EFFECT OF HYDRODYNAMIC FORCES ON THE ORGAN 28. APPLICATION : HIGH VOLTAGE QUICK BREAKER CIRCUIT BREAKER.

Description

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  The invention relates to a hydraulic control device of a jack associated with the actuating mechanism of a high-voltage circuit breaker for closing and opening contacts, comprising: an oleopneumatic accumulator filled with pressurized oil - a lower pressure tarpaulin for the discharge of the oil of the cylinder during the trip,

  a hydraulic valve for selectively communicating the

  rin is either accumulator accumulator for engagement and maintenance

  contacts in the closed position, ie to the tarpaulin for the middle

  to purge when triggering,

  - supply and discharge ducts for the connection

  the valve respectively to the accumulator and the tarpaulin,

  and an electrodynamic thruster associated with said check valve

  rer said tripping of the circuit breaker.

  In a known device of the kind mentioned, said thruster cooperates with the valve in the direction of tripping to ensure the rapid purge of the cylinder, but is not suitable for reclosing the circuit breaker. The latter then requires

  an auxiliary control switch valve which acts on a key

  pet relay of an intermediate stage which introduces obligatorily

  long response times that are detrimental to the proper functioning of the dis-

junction when switching on.

  According to other known devices, said valve is not

  not stable in one of the trigger or engagement positions

  This makes the hydraulic control device more complicated by the addition of additional members between the flapper.

and the cylinder.

  The object of the invention is to avoid the disadvantages

  mentioned above and to produce a hydraulic control device

  ble and simple using a quick response bistable valve

  triggering and tripping.

  The hydraulic control device according to the invention

  is characterized by the fact that said thruster causes the

  transition from the trigger position to the switch-on position

  and vice versa of said hydraulic valve comprising: - a fixed body provided with a first seat disposed in the vicinity of an exhaust port communicating with said cover, and a

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  second seat located in the vicinity of an intake port in connection

  sound with said accumulator and offset from the first seat by a

  predetermined time, and a shutter member bi-directionally slidably mounted in said gap during the selective excitation of the thruster, so as to generate hydrodynamic forces in the vicinity of the decreasing section of passage of the oil in the orifices.

  exhaust or intake respectively at the end of the

  latching and triggering, subsequently causing the stable support of said closure member is against the first seat with closure of the exhaust port and opening of the inlet port in the engaged position, or against the second seat with closing of the inlet opening and opening of

  the exhaust port in the release position.

  According to a characteristic of the invention, said shutter member comprises two opposite active ends cooperating at the end of the engagement and tripping stroke with said first and second seats to delimit said sections of FIG.

  passage varying in opposite directions from one another for a sense

  completed the displacement race of said organ presenting in

  an intermediate position, a bridging of which the French

  is ensured by the electrodynamic forces of the said

  pre-emptive action of hydrodynamic forces

  generated in the corresponding passage section at the end

  engaging or tripping stroke.

  According to another characteristic of the invention, the supply ducts of the accumulator and discharge of the tank are respectively equipped with an intake nozzle and an exhaust nozzle determining the engagement speed and

circuit breaker tripping.

  According to a development of the invention, a drawer

  ge in said body of the valve is associated with the first and second seats to cooperate with the corresponding end of the shutter member respectively at the end of engagement stroke and

  triggering, so as to increase the effect of hydrodynamic forces

  support during the closing of the drawer, and the stability

  shutter member in interlocking and disengaging

  Tripping. Other advantages and features will emerge more clearly from the following description of four embodiments of the invention given by way of nonlimiting example and represented in the accompanying drawings, in which: FIG. schematic view in axial section

  a hydraulic control device equipped with a bistatic valve

  ble 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 intermediate positions and triggers

  is lying; Figures 4 and 5 are half-views in axial section of an alternative embodiment of the valve shown respectively in the engaged position and tripping; Figures 6 and 7 show sectional demivals

  of another embodiment of the valve in the position of

clipping and triggering;

  Figure 8 shows the diagrams of the hydro-electric forces

  dynamic forces exerted on the valve according to its axial position between the engagement and trigger positions, for different dimensions of decreasing values of the intake nozzle according to the device of Figures 1 to 3; Figure 9 is a partial sectional view of another

variant embodiment.

  With reference to FIGS. 1 to 3, the hydraulic valve designated by the general reference numeral 10 comprises a stationary body 12 arranged between an electrodynamic actuator 14 and a control cylinder 15 for triggering and engaging the mechanism of a circuit breaker.

  high tension. The actuator 14 comprises a bi-directional thruster

  dual axial air gap and electrodynamic repulsion of the

  type Thomson with a mobile disk 16 inserted between two booster

  The disc 16 made of conductive material is integral with an actuating rod 22 mounted alternately sliding in a bore 24 of the body 12 with the interposition of an annular seal 26. The valve comprises a shutter member 28 mechanically coupled to the actuating rod 22, and capable of occupying two positions

  longitudinally stable end-of-travel interlocking and

  latching respectively when the disc 16 is pressed against

  the coil 20 and the coil 18 of the actuator 14. The closure member

  28 comprises a coaxial hollow cylinder 30 of larger diameter

  than that of the rod 22, and sliding inside an

  32 central 32 of the body 12 having an annular groove 34 of housing

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  seal 36. One 38 of the ends of the cylinder

  30 of shutter is bevelled and cooperates in position

  latch (Fig. 1), after repulsion of the disc 16

  of the coil 20, with a first circular seat 40 arranged coaxially in the body 12, and having a diameter between the outer and inner diameters of the cylinder 30. The opposite end 42 of the cylinder 30 is provided with a rim 44 which the frustoconical shaped active face 46 comes into engagement in the triggering position with a second circular seat 48 of the body 12 during the excitation of the coil 20 and the repulsion of the disk 16 towards the adjacent coil 18. The two seats 40, 48 of the body 12 are separated longitudinally from one another by a

  predetermined axial distance d1, and the bi-directional sliding stroke

  directional of the shutter member 28 between the two seats 40,

  48 corresponds exactly to that of disc 16 between the two

  20, 18 of the actuator 14. The flange 44 is provided opposite the face 46 of an auxiliary face shaped shoulder 50 of

  greater than the central bore 32, and coming into abutment

  be the central section of the body 12, when the valve 10 is located

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 an opening

  Fig. 44 is a radial pressure jet for pressurized oil, connected to an oleopneumatic accumulator 56 or other high-pressure oil reservoir via a supply conduit 58.

  cylinder 30 comprises a plurality of holes 60 distributed circumferentially

  substantially in a ring diameter smaller than that of the seat 48, and communicating the admission port 54 with

  the inner conduit 62 of the hollow cylinder 30 in the engaged position

  valve 10 for feeding the cylinder 15, the

  pleating ensures the displacement of the movable piston 64 in the direction of the arrow F and the quick closing of the contacts of the circuit breaker. The end face 66, opposite that 52 of the body 12, bore 32, forms with the seat 40 juxtaposed an exhaust port 68 connected by a discharge pipe 70 with a tarpaulin 72 low

  pressure for the purge of the cylinder 15 in the position of de-

Closing (Fig. 3) of the valve 10.

  The supply duct 58 is equipped with an inlet nozzle 74 of predetermined size for adjusting the closing speed of the contacts, and the delivery duct 70

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  similarly comprises an exhaust nozzle 76 which de-

  finishes the opening speed of the contacts when setting the

purge cylinder 15.

  The valve 10 is bistable and rests on one of the seats 40, 48, so as to selectively connect the control cylinder 15 to the oleo-pneumatic accumulator 56 for the engagement of the circuit breaker and the maintenance in the closed position of the contacts. , is

  to the cover 72 for the purge of the cylinder 15 during the triggering

  circuit breaker. In the engaged position (Fig. 1), the

  shutter 28 of the valve 10 comes into sealing engagement on the seat 40 to close the exhaust port 68 to the tank 72 and simultaneously open the intake port 54 of oil under high pressure. In the release position (FIG 3), the shutter member 28 comes into engagement with the seat 48 to close

  intake port 54 and simultaneously open the escape port

  68 for rapid emptying of the cylinder 15. Each of the two

  the engagement and tripping of the valve 10 is sta-

  ble, and the transition from one to the other is caused by the displacement

  in translation of the disc 16 of the electrodynamic actuator 14. During the stroke of the shutter member 28 in a predetermined direction, and in particular in an intermediate position (FIG. 2), the intake orifices 54 and 68 are partially open and communicate the oleopneumatic accumulator 56 with the tarpaulin 72. The oil flow driven from the accumulator 56 to the

  covering 72 is limited by the pressure losses in the feed duct.

  58, the intake nozzle 74, the passage section SA

  oil in the inlet orifice 54, variable according to the posi-

  flange 44, the holes 60 and the internal conduit 62 of the or-

  shutter 28, the passage section SE of the oil in the ori-

  exhaust 68 varying in the opposite direction of the section ad-

  mission SA, the exhaust nozzle 76 and the discharge pipe

70.

  Hydrodynamic forces generated by the passage

  oil in the sections SA and SE provoke the support of the

  shutter 28 on one of the seats 40, 48. These hydraulic forces

  dynamic support on the valve 10 are variable depending on

  the position of the member 28 between the two extreme positions

  interlocking and tripping Figure 8 shows the variation of the resulting hydrodynamic forces F as a function of the position x for different decreasing values of the nozzle

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  74 (curves I, II, II), and it can be seen that in the

  median position of the valve (position 0) the forces F are practically

  absolutely nil. This median position constitutes a sort of neutral 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 abrupt passage of the neutral point, and the hydrodynamic forces F then take over or add to the electrodynamic repulsion forces of the disc 16 to apply

  the flap 10 on one of the seats 40, 48, and maintain it

  stable in this position. It has been found that

  drodynamics F exerted on the valve 10 are generated during

  that one of the sections SA and SE of passage of the oil in the

  pet was close to the smallest passage sections of the hydrulic circuit between the accumulator 56 and the tank 72, for example when the intake section SA corresponds to the section of the nozzle 74, the curve I is an optimum cgyrb corresnondant to a predetermined value of the gcl eur a but ion m4 greater than that of the nozzle of the curve III in which the memory effect may be zero in case of rebound of the valve 10 during its

  came to the seat 40, 48 corresponding.

  The operation of the bistable hydraulic valve according to FIGS. 1 to 3 is as follows: In the stable position of engagement (FIG 1), the disk 16 of the electrodynamic actuator 14 is pressed against the

  coil 20, and the hydrostatic forces apply the shutter member

  28 on the seat 40. The exhaust port 68 is closed and the opening of the inlet 54 ensures the passage of the oil

  high pressure stored in the accumulator 56 to the compression cylinder

  Mande 15, which holds the contacts in closed position. Note that the section of the ring determined by the outside diameter of the cylinder 30 and the diameter of the seat 40 must be smaller than the section of the actuating rod 22 so that the valve be stable

in the engaged position.

  The tripping of the circuit-breaker is controlled by the ex-

  citation of the trigger coil 20 of the actuator 14, particularly

  by means of a discharge of a capacitor causing the repulsion

  electrodynamic coupling of the conductive disk 16 towards the coil 18 and the rapid movement of the shutter member 28 towards

  the opposite seat 48. After a breakeven due to the electric forces

  trodynamics of the actuator 14 (FIG 2), the shutter member 28

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  is sucked by the hydrodynamic forces generated in the

  decreasing admission SA of the hydraulic circuit at the orifice 54 and abuts 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 orifices of intake 54 and exhaust 68 are respectively closed and open for the purge of the

  cylinder 15 to the tarpaulin 72 causing the rapid opening of the contacts.

  The reclosing is done during the excitation of

  the switching coil 18 which causes the electrodynamic repulsion

  of the disk 16 towards the coil 20. The race in

  translation of the disc 16 is identical to that of the obturator

  28, which after crossing the neutral position in the middle position

  diane (Fig. 2) is biased in stable support on the seat 40 by the hydrodynamic forces generated in the decreasing section

  exhaust pipe SE in the vicinity of the orifice 68. The valve 10 is

  is then in the engaged position shown in the

Fig. 1.

  An intermediate amplifier stage (not shown)

  can be arranged downstream of the jack to be controlled by the key

pet 10.

  To avoid the matting of the valve 10 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 by means of two dampers 80, 82 (FIG. and 7)

  active hydraulics in the vicinity of the two trigger positions.

  and engagement, and integrated within the body 12 of the valve 10. The damper 80 has 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 trigger stroke in an annular groove 86 of

  body 12, with a diameter greater than that of the bore 24. The

  oil pressure in the throat 86 slows down the mobile

  m by the rod 22 and the closure member 28 ensuring an

  slow rivet of the latter on the seat 48. The shock absorber 82 com-

  similarly takes a step 88 on the shoulder 50 of the flange 44, and an annular groove 90 in the central bore 32 of the body 12. The step 88 acts as a compression piston of

  the oil in the groove 90 at the end of the engagement stroke and pro-

  voque a commitment without rebound of the organ 28 on the seat 40.

  According to the variant embodiment illustrated in FIGS.

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  4 and 5, the same reference numerals designate identical or similar

  to those of fig. 1 to 3. The valve 10 is equipped with a drawer

  cylindrical associated with the seat 48 of the body 12, so as to co-

  operate with the rim 44 of the closure member 28 at the end of the trigger stroke (FIG 5) to increase the effect of the hydrodynamic forces during the closure of the slide 100. This results in a better stability of the organ shutter 28 in the position of

  trigger, regardless of the size of the inlet nozzle.

  74. The seat 48 on which the member 28 is supported is located

be the bore 24 and the drawer 100.

  When the valve 10 is moved towards the engagement position (FIG 4), the shoulder 50 of the flange 44 compresses the oil contained in the cavity 102 situated between the slide 100 and the intake nozzle 74. pressure in the cavity 102, the latter is put in communication with a

  Oleopneumatic damper 104 with membrane 106, or other accumula-

  anti-water hammer whose low volume is overpressurized with respect to the pressure of the oil in the accumulator 56. The rest of the operation is identical to that described with reference

in figs. 1 and 3 ..

  According to another variant shown in FIGS. 6 and 7, the oleopneumatic damper 104 is replaced by a jet 110

  unidirectional inserted in the hydraulic circuit between the con-

  supply 58 of the accumulator 56 and the admission port

  54 of the cavity 102. A spring 112 urges the nozzle 110 bearing on a flange 114 of the drawer 100; in the event of overpressure of the oil in the cavity 102 occurring during 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.

  Both variants of fig. 4 to 7 can be equi-

  low pressure side of a 120 cylindrical drawer arranged in

  the body 12 between the exhaust port 68 and the seat 40 (rig.9).

  The end 38 of the closure member 28 cooperates with the slide 120 at the end of the engagement stroke to increase the effect of the hydrodynamic forces and the stability of the valve 10 in the engagement position. The invention is of course in no way limited to

  modes of implementation more particularly described and

  In the accompanying drawings, however, it extends to any variant remaining within the framework of mechanical and hydraulic equivalences.

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Claims (10)

  1. Hydraulic control device of a jack   connected to the actuating mechanism of a high-voltage circuit-breaker for closing and opening contacts, comprising: - an oleopneumatic accumulator filled with oil under pressure, - a lower pressure tank for discharging the oil the cylinder during the trip,   a hydraulic valve for selectively communicating the vehicle   rin is either accumulator accumulator for engagement and maintenance   contacts in the closed position, ie to the tarpaulin for the middle   to purge when triggering,   - supply and discharge ducts for the connection   the valve respectively to the accumulator and the tarpaulin,   and an electrodynamic thruster associated with said check valve   surer said tripping circuit breaker, characterized in that said thruster causes the passage of the trigger position to the latching position and vice versa said hydraulic valve comprising: - a fixed body provided with a first seat disposed in the vicinity of an exhaust port communicating with said tarpaulin, and a   second seat located in the vicinity of an inlet port   with said accumulator and shifted from the first seat by a predetermined interval; and a shutter member bi-directionally slidably mounted in said gap during the selective excitation of the thruster, so as to generate hydrodynamic forces in the vicinity of the descending section. oil passing through the holes   exhaust or intake respectively at the end of the   latching and triggering, subsequently causing the stable support of said closure member is against the first seat with closure of the exhaust port and opening of the inlet port in the engaged position, or against the second seat with closing of the inlet opening and opening of   the exhaust port in the release position.   2. Hydraulic control device of a jack according to   claim 1, characterized by the fact that said organ of ob-   turation comprises two opposite active ends cooperating at the end of the engagement and tripping stroke with said first and second seats to delimit said sections of   passage varying in opposite directions from one another for a sense 2462015   completed the displacement race of said organ presenting in   an intermediate position, a bridging of which the French   is ensured by the electrodynamic forces of the said   pre-emptive action of hydrodynamic forces   generated in the corresponding passage section at the end   engaging or tripping stroke.   3. Hydraulic control device of a cylinder, se-   according to claim 2, characterized in that said organ   shutter, secured to said thruster by an actuating rod   has a hollow cylinder whose internal conduit ensures the communication of the accumulator with the tarpaulin during the   sliding stroke between the two extreme positions of de- clipping and engagement.   4. Hydraulic control device of a cylinder, se-   1, 2 or 3, characterized in that said supply duct of the accumulator is equipped in the vicinity   said second seat of an inlet nozzle of predetermined size   completed for setting the interlocking speed.   5. Hydraulic control device of a cylinder, se-   1, 2, 3 or 4, characterized by the fact that   said discharge pipe for the purge of the cylinder   closes an exhaust nozzle that determines the speed of is lying.   6. Hydraulic control device of a cylinder, se-   one of the claims 1 to 5, characterized by the fact that   hydraulic damper integrated in said valve body becomes active at the end of the engagement or tripping stroke for   ensure the abutment at reduced speed of the closure member   against said first or second seats.   7. Hydraulic control device of a cylinder, se-   one of the claims 2 to 6, characterized in that   drawer formed in said valve body is associated with the first and second seats to cooperate with the corresponding end   shutter member respectively at the end of   and triggering, so as to increase the effect of hydrodynamic bearing forces when closing said drawer-,   and the stability of the closure member in interlocking positions. and trigger.   8. Hydraulic control device of a cylinder, se-   good the claim 7, characterized in that said drawer there 2462015   is arranged on the one hand between the second seat and the inlet opening   in the vicinity of the trip position, and secondly between the first seat and the exhaust port in the vicinity of the engagement position.   9. Hydraulic control device of a cylinder, se-   one of the preceding claims, characterized in that   that an anti-hammer device, in particular a shock absorber   oleopneumatic or unidirectional nozzle, cooperates with the cir-   baked in the vicinity of said inlet for   an internal overpressure of the valve oil during its de-   placement to the engaged position.   10. Control device according to any one of   Claims 2 to 9, characterized in that said thruster   electrodynamic device comprises a conductive mobile disc inserted in an axial air gap formed between two fixed engagement and tripping coils whose selective excitation by capacitor discharge causes the electrodynamic repulsion of said disc   in a specific direction corresponding to the engagement or de-   latching and the passage of the dead point of said shutter member.