EP1178505A1 - Actuating mechanism with tow chain for electrical high voltage switches - Google Patents

Abstract

The circuit breaker movement mechanism has a chassis (18) with a transmission shaft (16) and a handle (70). The braking mechanism has a locking mechanism (196) in the armed position charging the energy accumulator (10). There is a communications shaft (14) connected cinematically to a moving contact. The transmission shaft couples to the communication shaft. The decoupling position switches between the armed position and a dead point.

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a mechanism for operating a high cut-off device voltage, in particular of a circuit breaker, of the type comprising an energy accumulator potential elastic, a drive shaft intended to drive at least one contact mobile circuit breaker via kinematic transmission, and a flexible link traction, of the traction chain or cable type, having two ends, one connected to the energy accumulator, and the other to the transmission shaft, the flexible link passing through a intermediate return pulley.

STATE OF THE ART

In document FR-A-1 588 485 is described a mechanism of this type, in which the shaft transmission is connected to an energy storage spring via a cable passing through an angular pulley. The tree is driven on a U-turn about in a first direction when the spring is released, and is driven in reverse by a motor to reset the spring. The shaft rotation is limited by two end of travel stops which cooperate with an eccentric lug secured to the tree. A latching member keeps the drive shaft in the armed position when the spring is tight. The attachment member is controlled by an electromagnet to which it is connected via a gear reduction stage. The mechanism is explicitly intended for the operation of electrical equipment which does not require a very fast operation. On the other hand, it is totally unsuitable for the maneuver rapid switchgear using closing or opening energies important. Indeed, the mechanism produces significant shocks at the end of the stroke opening and closing, when the drive shaft and the elements linked to it, whose moment of inertia is important, are stopped by the limit stop. These shocks are acceptable when the maneuvering speed is close to that of a maneuver manual. They would be intolerable if the kinetic energy of the tree and the masses in movement became more important. On the one hand, shocks are likely to cause premature fatigue of moving parts and limit stops.

On the other hand, the attachment and gear reduction members are parts very sensitive to unwanted mechanical vibrations, so that a device generating shocks would be exposed to risks of inadvertent tripping. In addition, a such a device does not allow rapid resetting of the accumulator spring at the end of opening race.

Document EP 238 847 relates explicitly to an actuation mechanism a very high voltage circuit breaker, therefore a fast-moving and energy-saving mechanism high kinetics. In order to reduce the forces exerted on a tree attachment member transmission in the armed position, it has been proposed to combine a first spring connected to the transmission shaft via a first chain, and a second spring connected to the transmission shaft via a second chain. The chains are arranged so that when the two springs are loaded, the chains are located on either side of the axis of rotation of the drive shaft. So the couple exerted by the first spring is partially compensated by the torque exerted by the second spring. The armed position is therefore a position close to an unstable equilibrium. As soon as the shaft begins to rotate under the action of the spring whose torque is predominant, the second spring exceeds its neutral position, so that the two springs become motors. No special provision is made for limit the vibrations generated by the discharge of the storage springs.

STATEMENT OF THE INVENTION

The invention aims to provide a mechanism of the above type, which allows a very fast actuation of high voltage electrical switchgear having a high electrical power, therefore a significant mobile mass. More precisely, the invention aims to reduce the vibrations generated by the mechanism during closing switchgear contacts. It also aims to facilitate the rapid rearmament of the energy accumulator when it reaches its discharged position.

• un châssis ;
• un arbre de transmission mobile en rotation autour d'un axe géométrique de rotation fixe par rapport au châssis, l'arbre de transmission étant muni d'au moins une manivelle ;
• au moins un accumulateur d'énergie potentielle élastique, comportant un premier organe d'extrémité mobile entre une position chargée et une position déchargée, l'accumulateur délivrant une énergie cinétique motrice lorsque le premier organe d'extrémité se déplace de sa position chargée à sa position déchargée, et accumulant une énergie potentielle élastique lorsque le premier organe d'extrémité se déplace de sa position déchargée à sa position chargée ;
• au moins un lien souple de traction tendu entre l'accumulateur d'énergie et la manivelle, le lien souple de traction ayant une première extrémité solidaire de du premier organe d'extrémité de l'accumulateur d'énergie et une deuxième extrémité montée sur la manivelle de l'arbre de transmission, l'arbre de transmission étant mobile en rotation entre une position de point mort haut et une position de point mort bas, les deux positions de point mort étant des positions dans lesquelles le lien souple n'exerce sur l'arbre de transmission aucun couple par rapport à l'axe géométrique de rotation de l'arbre de transmission , la position de point mort bas étant atteinte lorsque le premier organe d'extrémité de l'accumulateur est dans sa position déchargée ;

caractérisé en ce que :

• le premier organe d'extrémité est apte à effectuer une surcourse au delà de sa position déchargée, jusqu'à une position de fin de course ;
• le châssis est muni d'un moyen d'accumulation d'énergie auxiliaire déformable, ce moyen d'accumulation d'énergie coopérant avec le premier organe d'extrémité lorsque le premier organe d'extrémité est situé entre la position déchargée et la position de fin de course et étant apte :
  • à se déformer en absorbant une partie au moins de l'énergie cinétique du premier organe d'extrémité de l'accumulateur d'énergie lorsque le premier organe d'extrémité couvre la surcourse en direction de la position de fin de course ; et
  • à retrouver sa forme initiale en restituant au premier organe d'extrémité sous forme d'énergie cinétique une partie de l'énergie cinétique qu'il a absorbée, lorsque le premier organe d'extrémité couvre la surcourse au delà de la position déchargée en se rapprochant de la position déchargée.

According to the invention, this problem is solved by means of a mechanism for operating a high voltage electrical switchgear comprising

• a chassis ;
• a drive shaft movable in rotation about a geometric axis of rotation fixed relative to the chassis, the drive shaft being provided with at least one crank;
• at least one accumulator of elastic potential energy, comprising a first end member movable between a charged position and a discharged position, the accumulator delivering motive kinetic energy when the first end member moves from its charged position to its unloaded position, and accumulating elastic potential energy when the first end member moves from its unloaded position to its loaded position;
• at least one flexible traction link stretched between the energy accumulator and the crank, the flexible traction link having a first end secured to the first end member of the energy accumulator and a second end mounted on the crankshaft of the propeller shaft, the propeller shaft being rotatable between a top dead center position and a bottom dead center position, the two neutral positions being positions in which the flexible link does not exert on the transmission shaft no torque with respect to the geometric axis of rotation of the transmission shaft, the bottom dead center position being reached when the first end member of the accumulator is in its discharged position;

characterized in that:

• the first end member is capable of overtraveling beyond its unloaded position, to an end of travel position;
• the chassis is provided with a deformable auxiliary energy storage means, this energy storage means cooperating with the first end member when the first end member is located between the unloaded position and the position of end of race and being able:
  • deforming by absorbing at least part of the kinetic energy of the first end member of the energy accumulator when the first end member covers the overtravel towards the end position; and
  • to return to its initial shape by restoring to the first end member in the form of kinetic energy a part of the kinetic energy which it has absorbed, when the first end member covers the overtravel beyond the unloaded position while approaching the unloaded position.

The auxiliary energy storage means has a dual function. On the one hand, it amortizes the shock transmitted by the accumulator to the chassis when passing through the bottom dead center. On the other hand, the energy returned makes it possible to speed up the rearming of the accumulator. energy.

According to one embodiment, the mechanism further comprises a wheel coupling free connecting the drive shaft to the chassis, allowing the rotation of the shaft transmission in a working direction and preventing rotation of the transmission shaft in an opposite direction. A closing lock is capable of locking the drive shaft in an armed position, corresponding to the charged position of the energy accumulator. A switching shaft is able to be kinematically connected to at least one control member movable contact of the electrical switchgear. A means of coupling integral with the drive shaft is suitable for coupling the drive shaft with the shaft when the drive shaft reaches a coupling position and at disconnect the drive shaft from the switching shaft when the drive shaft transmission reaches a decoupling position, the coupling position being located between the armed position and the bottom dead center position, in the working direction, the uncoupling position being located between the coupling position and the position of bottom dead center, in the direction of work. The transmission shaft has such a moment of inertia that when the closing latch releases the drive shaft, the first member end of the energy accumulator changes from its charged position to its position discharged and drives the drive shaft from its armed position to its position bottom dead center, then the drive shaft continues to rotate from its neutral position dead down in the direction of its arming position in the working direction by driving the first end member from its discharged position to its charged position. The tree of transmission then constitutes a flywheel which has a driving role after passing through the bottom dead center. Resetting the device is then much faster. This arrangement is particularly advantageous for apparatus of dimensions important. Indeed, the mass and the moment of inertia of the drive shaft are dimensioned according to the maximum torque to be transmitted to the contact members of switchgear. The moment of inertia of the drive shaft increases with the dimensions of the contact members. The mechanism makes it possible to recover part of kinetic energy of the shaft to partially rearm the springs. The engines that complete the rearmament then have less energy to supply, and can be sized differently.

Preferably, the flexible link has a longitudinal elasticity such that it undergoes a elastic elongation when the first end member of the energy accumulator overtravel. According to one embodiment, the flexible link is a chain of traction. It can also be a cable or a rope.

• des moyens de guidage en translation du premier organe d'extrémité mobile par rapport au châssis suivant un axe géométrique de translation fixe par rapport au châssis ;
• une poulie de renvoi supportée par le châssis et dans laquelle passe le lien souple, de telle manière qu'une première partie du lien souple soit tendue entre la poulie et le premier organe d'extrémité mobile de l'accumulateur d'énergie et soit parallèle à l'axe de translation, et qu'une deuxième partie du lien souple soit tendue entre la poulie et la manivelle.

Advantageously, the mechanism further comprises:

• means for guiding in translation of the first end member movable relative to the chassis along a geometrical axis of translation fixed relative to the chassis;
• a return pulley supported by the chassis and through which the flexible link passes, such that a first part of the flexible link is stretched between the pulley and the first movable end member of the energy accumulator and is parallel to the translation axis, and that a second part of the flexible link is stretched between the pulley and the crank.

The pulley makes it possible to partially decouple the vibratory modes of the shaft on the one hand and on the other hand, part of the forces transmitted by the flexible link being taken up by the pulley support shaft. In addition, the pulley allows a bevel gear which limits the overall size of the mechanism. Since the transmission of movement of the energy accumulator to the tree is done via a link flexible, the relative positioning of the first end of the energy accumulator and the idler pulley need not be very precise. According to one embodiment, the second part of the flexible link makes an angle of about 135 ° with the first part of the flexible link.

According to a preferred embodiment, the energy accumulator comprises: a second end member, at least one spring banded between the first end member and the second end member, a telescopic connecting member comprising a guide secured to one of the first and second end members, and a slide secured to the other of the first and second end members, the slide being movable in translation relative to the guide. The chassis has at least one support stop, the spring tending to urge the second end member to bear against the support stop. The telescopic connection comprises an end of travel stop disposed between the guide and the slider in such a way that when the first end member passes from its position loaded in its unloaded position, the end stop comes between the guide and the slider before the first end member reaches its unloaded position, and that when the first end member continues its travel beyond its unloaded position, the first movable member drives the second movable member. With such a device, there has no direct mechanical connection between the second end member of the accumulator of energy and the chassis of the mechanism upon arrival in the unloaded position, which eliminates a source of vibration transmission to the chassis. Advantageously of the stop limit switch is a damping stop capable of absorbing kinetic energy when the first end member passes from the intermediate position or the end stop between the guide and the slide in the unloaded position. Vibrations induced by the spring of the energy accumulator are absorbed by the stop damping while the first end member overtraveling, that is to say at a time when neither the first nor the second end member of the accumulator of energy are only in contact with the chassis.

Preferably, the drive shaft is linked to the chassis via a first freewheel. The mechanism further comprises: at least one electric motor connected to the drive shaft via a second freewheel; a device for control able to detect the passage of the drive shaft through a position predetermined and to drive the electric motor, so that when the shaft of transmission exceeds its low neutral position, the electric motor starts to drive the drive shaft before the speed of the drive shaft cancels. By controlling the electric motor in this way, it is possible to take advantage of the energy kinetics acquired by the tree. In addition, if the means of amortization and / or accumulation of energy are capable of restoring part of the energy which they store during the overtravel of the first end member, it is also possible to take advantage of this energy, so the resetting of the mechanism is very fast.

According to one embodiment, the auxiliary energy storage means comprises at at least one stud comprising an elastomeric material. We thus very simply cumulate the energy accumulation and vibration damping functions sought.

BRIEF DESCRIPTION OF THE FIGURES

• la figure 1 représente une vue en perspective du mécanisme de l'invention dans une position de point mort bas, certaines pièces ayant été omises pour une meilleure visualisation ;
• la figure 2 représente une vue du mécanisme suivant une autre perspective, certaines pièces ayant été omises pour une meilleure visualisation ;
• la figure 3 représente une vue en coupe de l'appareillage, montrant un sous-ensemble d'accumulation d'énergie ;
• la figure 4 représente une vue en coupe de l'appareillage, montrant un sous-ensemble de démarrage ;
• la figure 5 représente une vue en coupe de l'appareillage, montrant un sous-ensemble d'armement ;
• la figure 6 représente une vue en coupe de l'appareillage, montrant une partie d'un sous-ensemble de commande de fermeture et d'ouverture, dans un état armé, fermé ;
• la figure 7 représente une vue en perspective d'une partie du sous-ensemble de commande de fermeture et d'ouverture, avec une manette en position neutre ;
• la figure 8 représente une vue en coupe de l'appareillage, montrant un sous-ensemble de commande d'un circuit électrique de réarmement.

Other advantages and characteristics will emerge more clearly from the description which follows, of a particular embodiment of the invention, given by way of nonlimiting example, and represented in the appended drawings in which:

• FIG. 1 represents a perspective view of the mechanism of the invention in a bottom dead center position, certain parts having been omitted for better viewing;
• FIG. 2 represents a view of the mechanism from another perspective, certain parts having been omitted for better viewing;
• FIG. 3 represents a sectional view of the apparatus, showing a subset of energy accumulation;
• Figure 4 shows a sectional view of the apparatus, showing a starting sub-assembly;
• Figure 5 shows a sectional view of the apparatus, showing an arming sub-assembly;
• Figure 6 shows a sectional view of the apparatus, showing part of a closing and opening control sub-assembly, in an armed, closed state;
• FIG. 7 represents a perspective view of part of the closing and opening control sub-assembly, with a lever in the neutral position;
• Figure 8 shows a sectional view of the apparatus, showing a control sub-assembly of an electrical reset circuit.

DETAILED DESCRIPTION OF AN EMBODIMENT

Referring to Figures 1 and 2, a mechanism for operating an electrical apparatus high voltage shutdown is mainly composed of an energy accumulator closure 10, an arming subset 12 and a switching shaft 14, connected between them by means of a transmission shaft 16 and supported by a chassis 18. The switching shaft 14 is intended to be kinematically connected to one or more movable contact members of the switchgear, so as to drive them reversibly from an open position to a closed position.

The chassis 18 comprises two parallel main plates 20, 22, fixed to each other by spacers 24. Some elements of the mechanism are located between the plates 20, 22 of so that to visualize them, it was necessary to represent the dashed plate 20 on the view in FIG. 1 and to show the dashed plate 22 in the same way in FIG. 2. An intermediate plate 23 is held by spacers between the plates 20 and 22. The transmission shaft 16 and the switching shaft 14 are pivotally mounted on guide bearings (not shown) fixed to the plates 20, 22 of the chassis 18, so that their axes of rotation are parallel to each other and perpendicular to the planes of plates 20, 22 and 23.

The energy accumulator 10, shown in section in FIG. 3, comprises two pairs of accumulation springs 26 with flanges, retained by a stiffening structure 28. This structure is composed of a first end plate 30 and a second plate end 32, connected to each other by means of a guide link telescopic. The telescopic link is formed by two parallel guides, comprising each a rod 34 integral with the first end plate 30, and sliding in a tube 36 secured to the second end 32. Each tube is provided with a bottom 38 pierced an axial guide hole allowing the free translation of the corresponding rod 34. A stop 42 consisting of a washer of elastomer material surmounted by a washer metal, rests on this bottom 38. The free end of each rod 34 is inserted into the tube 36 corresponding and provided with a nut 44 forming a shoulder capable of coming in contact with the corresponding stop 42. The telescopic connection obtained allows translational movement of the first end plate 30 relative to the second end plate 28, along a geometric axis of translation parallel to the rods 34. This movement is limited in the direction of the distance by the meeting of the shoulder constituted by the nut 44, with the elastomer end stop 42.

The coil springs 26 are supported by their ends on the end plates 30, 32 and are mounted coaxially outside of each of the two parallel guides. The springs 26 are compression springs, that is to say springs which increase their potential energy when compressed and which provide work during their extension. In this case, the energy accumulator 10 is dimensioned in such a way that when the nuts 44 are in contact with the end stops 42, the springs 26 are completely relaxed and just in contact with the two end plates 30, 32. This state of the energy accumulator 10 will be said hereinafter discharged state.

Two identical windows 50 of generally rectangular shape, more particularly visible in FIGS. 4 and 7, are formed in the plates of the chassis 20, 22 and arranged opposite one from the other. Each rectangular window 50 defines two large lateral sides 52 and two small horizontal sides 54, 56, one lower (54), the other upper (56). Of them staves 58 are arranged side by side along the short upper side of each window. The four spans 58 together define a geometric support plane for the second end plate 32 of the energy accumulator 10, this plane being perpendicular to the plates 20, 22 of the chassis.

The end plates 30, 32 of the energy accumulator are provided with ribs of positioning 60, cooperating with the windowsills, so as to produce a guiding the two end plates 30, 32, allowing their translation along an axis geometric perpendicular to the geometric support plane defined by the spans 58. In in other words, the rods 34 remain substantially perpendicular to the geometric plane support, whatever the movement of the energy accumulator 10 in the windows 50. Guidance is ensured with a play of a few millimeters. The long sides 52 of the two windows 50 are provided with two mounting grooves 62, allowing lateral insertion of the sub-assembly formed by the energy accumulator 10 during assembly of the mechanism.

The movement of the first end plate 30 is limited by four studs 64 in elastomeric material, which together define a geometric plane of contact with the plate 30. These studs 64 form end-of-travel stops for the first plate end 30. The studs 64 are screwed into nuts 66 welded to the edge of the small lower sides 54 of windows 50, and stopped by locknuts 68. When mounting the apparatus, the accumulator 10 is assembled as a sub-assembly outside the chassis, under the shape shown in Figure 3. The distance between the upper grooves 62 and lower windows corresponds to the distance between the two end plates 30, 32 of the stiffening structure 28 of the accumulator 10 in its discharged state. With a view to inserting this sub-assembly into the chassis, the studs 64 are screwed in fully, which has the effect of lowering the contact plane previously mentioned, below the level of the lower groove 62. It is then possible to insert the accumulator 10 laterally at the through windows 50. Once the accumulator 10 is inserted, the pads 64 are partially unscrewed, so as to gradually raise the accumulator until the plate upper 32 is in contact with the surfaces 58 and the lower plate 30 is in contact studs 64, the accumulator 10 remaining in its discharged state. Finally, the locknuts 68 are positioned so as to block the studs 64 in position. Once the assembly is completed, the distance between the geometric support plane defined by the spans 58 on the one hand, and the plane geometric contact defined by the pads 64 on the other hand, is substantially equal to the distance between the first plate 30 and the second plate 32 when the accumulator is in its discharged state.

The first end plate 30 projects through the windows 50 on either side of the space delimited by the plates 20, 22 of the chassis 18. The two projecting parts of the plate 30 are each provided with a pair of oblong through holes.

The transmission shaft 16 is provided with two identical parallel cranks 70, 72, visible in Figures 1 and 2. The cranks 70, 72 are located on either side of the portion of space delimited by the plates 20, 22 of the chassis. Each crank is provided two flat cheeks perpendicular to the axis of rotation of the transmission shaft 16, forming between them a groove 74. The two flat cheeks support an eccentric pin 76, part of which is located in the throat.

A flexible kinematic connection between the energy accumulator 10 and the shaft of transmission 16 is established by means of two identical traction chains 80, which are located on either side of the space delimited by the two plates 20, 22 of the chassis. The chains 80 have been shown in a simplified manner in the figures, but they comprise preferably articulated links. The assembly of the two chains 80 is symmetrical relative to a median geometric plane parallel to the plates 20, 22 of the chassis 18.

Each traction chain 80 is stretched between one of the cranks 70 and the projecting part of the first plate 30 located on the same side of the plates 20, 22 of the chassis. One end of the chain 80 is provided with an eyelet 82 forming a socket which pivots on the eccentric axis 76 of the crank. In FIG. 2, the eyelet is shown in dotted lines, so as to allow view the axis 76. The other end of the chain 80 is provided with a double eyelet 84, which is inserted into the pair of through oblong holes and stopped by a pin 86. The chain 80 passes through an intermediate pulley 90, mounted idly on a supported axis 92 by the chassis 18. Part 94 of the chain, stretched between the pulley and the first plate end, is parallel to the axis of translation of the first plate 30, therefore parallel to the times to the geometric axis defined by the telescopic guide link of the structure stiffening 28 of the energy accumulator 10 and to the guide surfaces formed by the edges of the long sides 52 of the windows 50. Another part 96 of the chain is stretched between the pulley and the axle 76.

Each chain 80 works in a plane parallel to the plates 20, 22 of the chassis. It exists two positions of the mechanism in which the geometric plane containing the axis geometric rotation of the drive shaft 16 and the pivot axis 76 of the sleeve 82 becomes tangent to the periphery of the pulley 90 and to the part 96 of the chain. In one of these positions, visible in Figures 1 and 2, the socket 82 is located between the shaft 16 and the pulley 90, which corresponds to a bottom dead center of the transmission shaft 16, that is to say to a stable equilibrium position. In the other position, the transmission shaft 16 is between the bush 82 and the pulley 90, which corresponds to a top dead center of the shaft 16, that is to say at an unstable equilibrium position. The length of the two chains 80 is such as when the drive shaft 16 is placed in its bottom dead center position - and stopped in this position -, and that the accumulator 10 is in its discharged state, the first end plate 30 resting on the studs 64, the two chains 80 are only subject to very low tension, in fact the tension just necessary to keep them in the pulleys 90.

As shown in Figure 4, the central part of one of the axes 76 further constitutes a roller 98 which cooperates with a cam 100 of a starting lever 102. The lever start 102 is supported by a pivot 104 mounted on the chassis 18 and is recalled by a starting spring 106, bandaged between a free end of the lever 102 and a cleat mounted on the chassis. This sub-assembly constitutes a starting device. When the tree of transmission 16 changes from the bottom dead center position to the top dead center position, it fleetingly passes through an intermediate winding position, in which the roller 98 meets the cam 100. When the shaft continues to rotate, the roller 98 arms the lever start 102. The cam 100 has a top point 108. Shortly before arriving at top dead center position, for example 1 degree from this position, in a so-called position at the start of treatment, the roller 98 passes the top 108 of the cam 100, so that the starting lever 102, recalled by the starting spring 106, becomes engine by relative to the roller 98. The starting lever 102 remains engine until the roller 98 loses contact with the cam 100, approximately 5 degrees after the top dead center position, in a so-called end of care position.

The arming sub-assembly 12, a detail of which is shown in FIG. 5, comprises a ratchet wheel 110, integral with the transmission shaft 16, and which cooperates with five pawls, namely: two pawls 112, 113 mounted on a manual pumping lever 118, two pawls 114, 115 mounted on a stop support 120 secured to the chassis 18, and a pawl 116 mounted on a motorized pumping lever 122. Each pawl is returned to a position of coupling with the ratchet wheel, by a torsion spring. The lever manual pumping 118 and motorized pumping lever 122 are both fitted pivoting on the drive shaft 116. The pawls 112, 113, 114, 115, 116 and the wheel ratchet make freewheel couplings between the transmission shaft 16 and the lever manual pumping 118, between the transmission shaft 16 and the motorized pumping lever 122 and between the transmission shaft 16 and the chassis 18.

A free end of the manual pump lever 118 is connected to an input shaft 124 by via a reduction lever 126 pivoting relative to the chassis around a pivot 128, and two transmission rods 130, 132 connecting the transmission lever 126 on the one hand to a crank 134 of the input shaft 124 and on the other hand to the pumping lever manual 118. The end of the input shaft 124 has a key 134 allowing inserting a removable crank 136 visible in FIG. 1. When an operator turns crank 136 by one turn, the reduction lever 126 performs an oscillation which is transmitted with a gear reduction to the manual pump lever 118, so that the manual pump lever 118 makes an angular oscillation - back and forth - of one amplitude corresponding to about a tooth and a half of the ratchet wheel 110. However, the manual pump lever 118 is designed as an emergency accessory. In use normal, it is in a rest position, pressing against a limit stop 138 of support 120.

A free end of the motorized pumping lever 122 is provided with a cooperating roller 140 with a cam 142 keyed onto an output shaft 144 of a geared motor group 146, visible in FIG. 1. The geared motor group 146 comprises two electric motors 148, 150 driving a gear train 152 connected to the output shaft 144. A spring of recall 154 tends to recall the motorized pumping lever 116 in the opposite direction of clockwise in Figure 5. When the output shaft 144 rotates of one turn, the motorized pumping lever 116 makes a back and forth oscillation of a angular amplitude corresponding to approximately 3.8 teeth of the ratchet wheel 110.

The two pawls 112, 113 supported by the manual pumping lever 118 form between them an angle corresponding to 4.5 teeth of the ratchet wheel 110. Similarly, the two pawls 114, 115 of the stop support 120 form an angle between them corresponding to 4.5 teeth of the ratchet wheel 110. In normal use, when the manual pump lever 118 is in abutment against the stop 138, the pawl 114 of the stop support forms with the adjacent pawl 113 of the manual pump lever 118 an angle corresponding to 5.25 teeth of the ratchet wheel. Thus, when the ratchet wheel 110 starts to rotate in the opposite direction to that permitted by the pawls, it cannot cover an angle greater than that corresponding to 0.25 teeth without being taken over and stopped by one of the pawls.

The ratchet wheel 110 is provided with a toothless sector 158, which is at the height of the pawl 116 supported by the motorized pump lever 122 when the drive shaft 16 is near the top dead center. When the toothless sector 158 is in opposite the motorized pumping lever 122, it can perform a full oscillation at empty.

Referring to Figure 6, the drive shaft 16 further supports and so classic a drive cam 160 cooperating with a roller 162 mounted on a crank 164 fixed to the switching shaft 14. The cam has a circular part non-driving and a driving part. The switching shaft 14 is kinematically connected to at least one movable contact member 166 of the switchgear, via a kinematic chain 168 that has been shown purely schematically. Naturally, the switching shaft can simultaneously drive several contacts mobile, each corresponding to a pole of the apparatus. A classic configuration has three poles, corresponding to the three phases of a three-phase electrical network. The shaft 14 oscillates between an open position and a closed position forming an angle of 55 ° with each other. Moving from its open position to its closed position, the shaft 14 charges a spring with an elastic opening potential energy accumulator 170. A trigger 172 is pivotally mounted on the crank 164 of the switching shaft 14. A spring 174 tends to drive the trigger 172 projecting from the crank 164. The trigger 172 forms a spout which cooperates with an intermediate roller 176 carried by a lever reduction gear 178 which forms an intermediate lock. The leverage 178 pivots about an axis 180 and further comprises a second roller 182 cooperating with a rotary opening lock 184. The opening lock 184 is returned to the position of locked by a spring (not shown), and driven to an unlocked position by an opening control lock 186. This structure with three cascaded locks allows a reduction in the efforts required for unlocking. The axes geometric rotation of the three locks are parallel to each other and parallel to the axes geometric rotation of the transmission shafts 16 and switching 14. Each of the three locks is provided with a return spring (not shown), which tends to return it in the anti-clockwise in Figure 6 to a locked position. The opening control lock 186, the structure of which is visible in FIG. 7, comprises a material axis 210 having a half-moon cutout 212 cooperating with the opening latch 184, and two control cranks 214, 216. One end 218 of the axis 210 is mounted in a bearing supported by the intermediate plate 23 of the chassis, while a second bearing 222 is mounted on the plate 20. The control crank 216 is actuated by an electromechanical relay 190 for opening control at electromagnet, provided with a plunger 192 with axial movement. The control crank 214 is actuated by a stud 224 supported by a rotary control lever 226. The lever 226 has a flywheel 228 projecting in front of the plate 20, so as to be accessible by an operator, this steering wheel being secured to a material axis of rotation 230 one end 232 of which is guided in rotation in the plate 20.

The drive cam 160 is also provided with an eccentric pin, carrying a roller 194 intended to cooperate with a rotary closing lock 196. The closing locks 196 and closing control 200 are pivotally mounted, perpendicular to the plate 20, therefore parallel to the axes of rotation of the transmission and switching shafts 16 14. They are both recalled by recall springs which tend to recall them in the counterclockwise in Figure 6, toward their locked position. This structure with two cascaded locks allows a reduction in efforts necessary for unlocking. The closing control lock 200 has a structure close to that of the opening control lock 186, as shown in Figure 7. It comprises a rotary material axis 240 having a half-moon cutout 242 cooperating with the closing latch 196, and two control cranks 244, 246. One end 248 of the axis 240 is mounted in a bearing supported by the intermediate plate 23, then a second bearing 250 is mounted on the plate 20. The three material axes 210, 230, 240 are parallel, so that the geometric axes of pivoting of the latch closing control 200, opening control lock 186 and lever 226 are also parallel. The control handle 246 is actuated by a relay electromechanical closing control 202 with electromagnet, provided with a plunger 204 with axial movement. The control crank 244 is actuated by a pin 254 supported by the rotary control handle 226.

The steering wheel 228 of the lever 226 has a front face shown in FIG. 8, facing the operator. It is able to take three positions: a neutral position represented on the Figure 8, a manual opening control position, corresponding to a rotation of 90 ° clockwise in Figure 8, and a control position manual closing, corresponding to a 90 ° rotation in the opposite direction clockwise from the neutral position in Figure 8. Handle 226 is returned to its neutral middle position by a spring wire 260 working in flexion. The ends of the spring wire 260 rest on two support axes 262, 264, and its middle part supports two ranges 266, 268 of the steering wheel, the range 268 being coaxial with the stud 254. When the lever 226 moves from its neutral position to its manual control position closing, the pin 254 comes into contact with the crank 244 of the control lock closing 196 and rotates the axis 240 and the halfpipe 242, releasing the lock closing 196. The bearing 266 presses on the spring wire 260, which flexes and tends to bring back the lever to its neutral position, so that the lever returns to the position as soon as the operator lets go. Similarly, when the lever 226 passes from its neutral position to its manual opening control position, the pin 224 rotates the crank 214 of the opening control lock 186, the axis 210 and the half-moon 212, releasing the opening lock 184. Simultaneously, the bearing 268 presses on the spring 260 which flexes and tends to return the lever 226 to its neutral position.

When the roller 194 is blocked by the latch 196, the drive shaft 16 is located about 1 degree beyond the top dead center position. This position of the mechanism will be said hereinafter armed position, and corresponds to a compressed position of the spring accumulator 10, which will be called the charged position of the accumulator 10. It is note that the accumulator 10 is caused to be compressed very slightly beyond its loaded position, when the mechanism passes through top dead center.

The transmission shaft 16 further comprises a reset control cam 204 visible in Figure 7, in which the crank 70 has been deliberately omitted. The cam reset command 204 cooperates with a toggle lever 206 which causes contact electric 208. The electric contact 208 makes it possible to open and close a circuit supply of the two electric motors 148, 150 of the gear motor.

We now describe the operation of the mechanism, assuming that initially, the transmission shaft 16 is in the armed position and the switching shaft 14 in open position.

In the armed position, the transmission shaft 16 is retained in the immediate vicinity and slightly beyond top dead center, by hooking made by the closing bolt 196. The springs 26 of the accumulator 10 are bandaged and exert on the two plates end 30, 32 a significant push tending to move away the plates 30, 32 one of the other. The second end plate 32 is supported on the bearing surfaces 58, and the first end plate 30 is held in position by the two chains 80. However, the forces transmitted by chains 80 to cranks 70, 72 have a very weak moment or no relative to the axis of rotation of the shaft 16, due to the position of the cranks 70, 72 and friction of the mechanism. The start lever 102 is in a driving position relative to the crank 72, and exerts on it a calibrated force corresponding to the calibration of the starting spring 106. The reset control cam 204 does not act on the lever lever 206, so that the electrical contact 208 is open and the motors 148, 150 are arrested.

Starting from the armed position, a manual closing order on lever 226, or electric on the closing control relay 202, rotates the control lock closing 200 so as to release the closing latch 196. The roller 194 drives then the latch 196 clockwise, which releases the drive shaft 16. The lever start 102 then plays its driving role. It drives the roller 98 and with it the shaft of transmission 16, with a calibrated moment, over a few degrees to the end position support, located 5 ° from the top dead center position. Before I even reach this end of support position, the drive shaft 16 leaves the angular sector of friction which corresponds to an angle of +/- 3 ° around the top dead center position, so and the chains 80 begin to transmit engine torque to the cranks 70, 72. In this very first phase of closure, the switching shaft 14 remains stationary because the roller 162 still rolls on a part of the drive cam 160 which is circular and centered on the axis of rotation of the control shaft 16. This limits the work required by starting spring 106.

As soon as the angular position is reached allowing the chains 80 to become motor, the springs 26 of accumulator 10 relax and drive the first end plate 30, the two chains 80 and the transmission shaft 16 in rotation. The second plate end 32 remains in abutment against the bearing surfaces 58. The drive cam 160 begins to drive the crank 164 when the roller 162 begins to roll on the non-circular driving part of the cam, which corresponds to a fleeting start position drive shaft, located at 8 ° from the top dead center position. Driven by the cam 160, the crank 164 of the switching shaft 14 pivots from the open position to closed position. The transmission shaft 16 therefore transmits in this phase the kinetic energy from the energy accumulator 10 to the switching shaft 14.

When the switching shaft 14 reaches the closed position, the nozzle of the trigger 172 disappears in contact with the intermediate latch 178, then comes out under the pressure of the spring trigger 174. The thrust of the spring of the opening energy accumulator 170 tends to rotate the cam 164 clockwise, so that the trigger 172 comes to bear against the intermediate lock 178, and biases the intermediate lock 178 in the direction schedule. The intermediate lock bears against the opening lock 184 and the requests clockwise. The opening latch 184 in turn bears against the opening control lock 186 where it is blocked by the half-moon 212 in locking position, thereby locking the switching shaft 14 in closed position. Before reaching the bottom dead center position, 165 ° from the top dead center, the cam 160 loses contact with the roller 162, which uncouples the shaft switch 14 of the drive shaft 16. In the subsequent rearming phase, the drive cam 160 is no longer in contact with the roller 162, and the movement of the shaft transmission 16 is independent of that of the switching shaft 14.

Shortly before the drive shaft 16 reaches its bottom dead center position, the cam reset command 160 starts to toggle lever 206 in a position actuating the electrical contact 208. The latter closes a supply circuit for the motors 148, 150, which start to drive the reduction trains 152. The lever motorized pumping 122 performs oscillations but the pawl 116 does not hook with the ratchet wheel 110 as long as the angular speed of wheel 110 is greater than the speed angle of the pump lever 122. Thus, the gearmotor can reach gradually its operating regime before starting to train the shaft of transmission 16 in a later phase described later.

When the drive shaft 16 reaches its bottom dead center position, the first plate end 30 reaches a transient position relative to the chassis 18, called position discharged, corresponding to the discharged state of the accumulator 10. The nuts 44 of the rods 34 of the accumulator 10 reach the end of travel stops 42. In this position transient, the second end plate 32 is still in contact with the surfaces 58 then that the first end plate 30 is just in contact with the studs 64, so that the limit switches 44 assume only the shock absorption.

When the springs 26 relax, the first plate 30 has acquired kinetic energy important. As soon as the nuts 44 come into contact with the limit stops 42, the second plate 32 forms with the first a rigid assembly, and this assembly tends to take off from its support on the spans 58 and to move en bloc on the momentum of the first plate 30. This energy is sufficient to cause an elongation of the 80 chains by elastic deformation. The first end plate 30 then sinks in the pads 64 which compress. Under the effect of these joint requests, the plate end 30 decelerates strongly until its speed is canceled.

Due to the relatively large angular momentum of the drive shaft 16 and the moving masses which are integral with it, the transmission shaft 16 tends to continue its course beyond the bottom dead center and initiates a rearming movement by stretching a little more chains 80. The studs 64 tend to want to regain their original shape and to push back the end plate 30, thus restoring part of the energy they have stored. Simultaneously, the chains 80 tend to regain their original size. Its effects add up to immediately propel the end plate 30 into the direction of rearmament. In practice, it can be seen that the contact between the plate 30 and the studs 64 only gives rise to a rebound. It should also be noted that this phase is very rapid and that the deformations described are of very small amplitude. For information, the amplitude of the overtravel of the first end plate 30, which corresponds to the insertion of the studs 64 and approximately when the second plate comes off 32 is of the order of ten millimeters.

Under the effect of the kinetic energy of the transmission shaft 16 and the masses in movement which are integral with it, the transmission shaft 16 performs nearly a third of the reset stroke by decelerating gradually until the ratchet wheel 110 causes the transmission shaft to be coupled to the gearmotor. In this phase, the transmission shaft 16 plays the role of a flywheel. The mechanism therefore makes it possible to recover in this phase a significant part of the energy available in the mechanism when passing through bottom dead center, resulting in considerable time savings in the phase subsequent reset of the accumulator 10, which will now be described.

Under the effect of the springs 26 of the accumulator 10, the speed of rotation of the shaft transmission 16 is canceled, and the shaft 16 tends to start again in the opposite direction. One immediately of the four stationary pawls 112, 113, 114, 115 hang the ratchet wheel 110, unless that it is not directly supported by the pawl 116 of the motorized pumping lever 122, following its own oscillation. The layered arrangement of the four pawls 112, 113, 114, 115 in any case ensures that the shaft 16 will be hung before having traveled more than a quarter of the angular sector of a tooth of the ratchet wheel in the direction reverse direction of travel. This therefore makes it possible to limit the shock of the ratchet taking charge of the ratchet wheel 110. The motorized pumping lever 122 then takes loads the ratchet wheel 110 and makes it travel an angular sector corresponding to 3.5 teeth at each of its half-motor oscillations. During each half-oscillation no drive, when the cam 142 releases the motorized pumping lever 122 and the spring 154 recalls lever 122 to its end position counterclockwise of a watch in FIG. 5, the ratchet wheel 110 rests on one or the other of the four pawls 112, 113, 114, 115. The transmission shaft 16 ensures the transmission to the accumulator 10 of the mechanical energy produced by the motors 148, 150. The compression of the springs 26 of the accumulator 10 continues until the shaft of transmission 16 reaches its top dead center.

When the drive shaft 16 continues its race towards top dead center, the roller 98 of the crank 72 meets the starting lever 102 and drives the latter towards a position by tensioning the starting spring 106. Shortly before the drive shaft 16 reaches its top dead center, the roller 98 passes the top 108 of the cam 100 of the lever starting 102, so that the starting lever 102 becomes engine. Nearly simultaneously, the pawl 116 of the motorized pumping lever 122 is found opposite the angular sector without teeth 158 of the ratchet wheel 110, while the control cam reset 204 releases contact 208 which opens the motor supply circuit 148, 150. Even if the stopping of electric motors is not instantaneous, the absence of teeth ensures decoupling between the motorized pumping lever 122 and the drive shaft 16. The transmission shaft 16 passes the top dead center under the stress of the starting 102, until the roller 194 of the drive cam 160 comes into contact with closing latch 196. The latch is pressed clockwise, but blocked in the position of FIG. 6 by the half-moon 242 of the closing control lock 200.

The transmission shaft 16 then comes to a standstill in the armed position. The subset of control is then in the armed, closed state, represented in FIG. 6.

As for the switching shaft 14, its subsequent movement, from the position closed, is dictated by the opening spring 170 and by the opening latch 184. The order manual opening given by rotation of handle 226, or electric by relay electromechanical 190, is transmitted to the opening control lock 186, to the lock opening 184 and to the intermediate lock formed by the reduction lever 178, this last erasing and releasing the trigger 172. The switching shaft 14 then passes from the closed position to the open position under the action of the spring of the energy accumulator opening 170 which discharges, without the roller 162 meeting the drive cam 160. Arrived in the open position, the switching shaft 14 is stopped by stops of limit switch (not shown), and the roller 162 comes into contact with the cam, if the latter has completed its rearmament.

Naturally, various modifications are possible.

The electrical equipment concerned can be of any type, in particular a high circuit breaker voltage or a high voltage switch. The target area of tension includes as well medium voltage than very high voltage.

The gearmotor can only be driven by a single electric motor.

The mechanism may include only one traction chain. The chain (s) can be replaced by any type of flexible link allowing a tensile stress, by example a strap or cable. Naturally, it would be better to choose a flexible link having some elasticity. In practice, the elasticity of articulated traction chains conventional is sufficient to allow an extension of the chain when passing through the bottom dead center.

The armed position can be located slightly before or slightly after the position of top dead center, in the angular friction sector where the traction chains do not cannot have a driving action on the drive shaft.

The energy storage springs can be tension springs rather than compression springs, if the overall dimensions allow it.

In the discharged state of the accumulator, the springs 26 may still be slightly tablets, which limits their movement when subjected to impact from passing through the bottom dead center. The discharged state is always the state in which the springs 26 cannot no longer supply energy to plate 30, and corresponds to the position where the nuts 44 meet the stops 42.

The intermittent transmission members that constitute the pump levers 118 and 122 can be replaced by continuous transmission means. Couplings freewheeling can be achieved by other means than by a ratchet 110 and pawls 112, 113, 114, 115, 116, for example with balls or rollers coupling intermediaries between two cylindrical surfaces.

The starting sub-assembly can be of any type allowing a force to be applied to the tree on part of its stroke, close to the armed position. he can for example, a device with a mobile drawer in translation. This subset does not act not necessarily on crank 72, because any element integral with the shaft can also suit. It is possible to provide that the winding of the starting spring is not performed through the drive shaft, but for example directly through the gearmotor.

The number of intermediate locks between the closing lock and the corresponding relay on the one hand, and the opening lock and the corresponding relay on the other hand, is selected by function of the reduction in effort required.

Claims (12)

Operating mechanism for a high voltage electrical switchgear comprising a frame (18); a transmission shaft (16) movable in rotation about a geometric axis of rotation fixed relative to the chassis (18), the transmission shaft (16) being provided with at least one crank (70, 72); at least one elastic potential energy accumulator (10), comprising a first end member (30) movable between a charged position and a discharged position, the accumulator (10) delivering kinetic motive energy when the first member end (30) moves from its loaded position to its discharged position, and accumulating elastic elastic energy when the first end member (30) moves from its discharged position to its charged position; at least one flexible traction link (80) stretched between the energy accumulator (10) and the crank (70, 72), the flexible traction link (80) having a first end (84) integral with the first member end (30) of the energy accumulator (10) and a second end (82) mounted on the crank (70, 72) of the drive shaft (16), the drive shaft (16) being movable in rotation between a top dead center position and a bottom dead center position, the two neutral positions being positions in which the flexible link (80) exerts no torque on the drive shaft (16) relative to the geometric axis of rotation of the drive shaft (16), the bottom dead center position being reached when the first end member (30) of the accumulator is in its discharged position; characterized in that : the first end member (30) is capable of overtraveling beyond its unloaded position, to an end of travel position; the chassis (18) is provided with a deformable auxiliary energy storage means (64), this energy storage means cooperating with the first end member (30) when the first end member ( 30) is located between the unloaded position and the end position and being suitable: deforming by absorbing at least part of the kinetic energy of the first end member (30) of the energy accumulator when the first end member covers the overtravel towards the end position; and to recover its initial shape by restoring to the first end member in the form of kinetic energy a part of the kinetic energy which it has absorbed, when the first end member (30) covers the overtravel beyond the position discharged when approaching the discharged position. Operating mechanism according to claim 1, characterized in that the mechanism further comprises: a freewheel coupling (110, 114, 115) connecting the transmission shaft (16) to the chassis (18), allowing the rotation of the transmission shaft (16) in a working direction and preventing rotation of the 'drive shaft (16) in an opposite direction. Operating mechanism according to claim 2, characterized in that the mechanism further comprises: a closing lock (196) capable of locking the drive shaft (16) in an armed position, corresponding to the charged position of the energy accumulator (10); a switching shaft (14) capable of being kinematically connected to at least one movable contact member (166) of the electrical switchgear; coupling means (160) integral with the drive shaft (16) and adapted to couple the drive shaft (16) with the switching shaft (14) when the drive shaft (16) reaches a coupling position and uncoupling the drive shaft (16) from the switching shaft (14) when the drive shaft (16) reaches a decoupling position, the coupling position being located between the armed position and the bottom dead center position in the working direction, the uncoupling position being located between the coupling position and the bottom neutral position in the working direction. Operating mechanism according to claim 3, characterized in that the drive shaft (16) has a moment of inertia such that when the closing latch (196) releases the drive shaft (16), the first member 'end (30) of the energy accumulator (10) passes from its charged position to its discharged position and drives the drive shaft (16) from its armed position to its bottom dead center position, then the transmission shaft (16) continues to rotate from its bottom dead center position towards its arming position in the working direction by driving the first end member (30) from its unloaded position to its loaded position. Operating mechanism according to any one of the preceding claims, characterized in that the flexible link (80) has a longitudinal elasticity such that it undergoes elastic elongation when the first end member (30) of the accumulator energy (10) overtakes. Operating mechanism according to any one of the preceding claims, characterized in that the flexible link (80) is a traction chain. Operating mechanism according to any one of the preceding claims, characterized in that it further comprises: means for guiding in translation (52, 60) the first end member movable relative to the frame (18), along a geometric axis of translation fixed relative to the frame (18); a return pulley (90) supported by the chassis (18) and through which the flexible link (80) passes, so that a first part (94) of the flexible link is stretched between the pulley (90) and the first movable end member (30) of the energy accumulator (10) and is parallel to the axis of translation, and a second part (96) of the flexible link is stretched between the pulley (90) and the crank (70, 72). Operating mechanism according to claim 7, characterized in that the second part (96) of the flexible link makes an angle of the order of 135 ° with the first part (94) of the flexible link. Operating mechanism according to any one of the preceding claims, characterized in that the energy accumulator (10) comprises a second end member (32), at least one spring (26) banded between the first end member (30) and the second end member (32), a telescopic connecting member comprising a guide (36) secured to one of the first and second end members, and a slide (34) secured to the other of the first and second end members, the slide (34) being movable in translation relative to the guide (36), the chassis (18) comprises at least one support stop (58), the spring (26) tending to urge the second end member (32) to bear against the support stop (58), the telescopic link comprises an end of travel stop (42) disposed between the guide (36) and the slide (34) so that when the first end member (30) passes from its loaded position to its unloaded position, the end stop (42) is interposed between the guide (36) and the slide (34) before the first end member (30) reaches its unloaded position, and that when the first end member ( 30) continues its race beyond its unloaded position, the first movable member (30) drives the second movable member (32). Maneuvering mechanism according to claim 9, characterized in that the end of travel stop (42) is a damping stop capable of absorbing kinetic energy when the first end member passes from the intermediate position or the stop limit switch (42) is interposed between the guide (36) and the slide (34) in the unloaded position. Operating mechanism according to any one of the preceding claims, characterized in that the transmission shaft (16) is linked to the chassis (18) via a first free wheel (110, 114, 115); the mechanism also includes: at least one electric motor (148, 150) connected to the transmission shaft (16) via a second freewheel (110, 116), a control device (204, 206, 208) adapted to detect the passage of the drive shaft (16) through a predetermined position, and to drive the electric motor (148, 150), so that when the shaft transmission (16) exceeds its bottom dead center position, the electric motor (148, 150) begins to drive the drive shaft (16) before the speed of the drive shaft (16) is canceled. Operating mechanism according to any one of the preceding claims, characterized in that the auxiliary energy storage means (64) comprises at least one stud comprising an elastomeric material.

Images