EP1178505B1 - Actuating mechanism with tow chain for electrical high voltage switches - Google Patents

Description

TECHNICAL FIELD OF THE INVENTION

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

STATE OF THE ART

In FR-A-1 588 485 is described a mechanism of this type, in which the transmission shaft is connected to an energy storage spring via a cable passing in a return pulley. angle. The shaft is driven about half a turn in a first direction when an accumulator spring is released, and is driven in the opposite direction by a motor to reset the spring. The rotation of the shaft is limited by two end stops which cooperate with an eccentric lug secured to the shaft. An attachment member holds the drive shaft in the armed position when the spring is bandaged. The fastening 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 that does not need a very fast operation. It is, on the other hand, totally unsuited to the operation of fast equipment using large closing or opening energies. Indeed, the mechanism produces significant shocks at the end of opening and closing stroke, when the transmission shaft and the elements which are related to it, whose moment of inertia is important, are stopped by the end stop race. These shocks are acceptable when the operating speed is close to that of a manual operation. They would be intolerable if the kinetic energy of the tree and moving masses became more important. On the one hand, shocks are likely to cause premature fatigue of moving parts and end stops.

On the other hand, the attachment members and stress reduction are mechanical parts very sensitive to parasitic mechanical vibrations, so that a device generating shock would be exposed to the risk of inadvertent tripping. In addition, such a device does not allow quick reset of the spring of the accumulator at the end of the opening stroke.

The EP 238 847 explicitly relates to a mechanism for actuating a very high voltage circuit breaker, so a fast motion mechanism and high kinetic energy. In order to reduce the forces exerted on a coupling member of the transmission shaft 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 in such a way that when the two springs are loaded, the chains are located on either side of the axis of rotation of the transmission shaft. Thus, the torque 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 preponderant, the second spring exceeds its neutral position, so that the two springs become engines. No special provision is made to limit the vibrations generated by the discharge of the storage springs.

SUMMARY OF THE INVENTION

The invention aims to provide a mechanism of the above type, which allows a very fast actuation of electrical switchgear high voltage having a high electrical power, so a large moving mass. More specifically, the invention aims to reduce the vibrations generated by the mechanism when closing the contacts of the equipment. It also aims to facilitate the quick reset of the energy accumulator when it reaches its unloaded 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 transmission shaft rotatable about a geometric axis of rotation fixed relative to the frame, the transmission shaft being provided with at least one crank;
• at least one elastic potential energy accumulator, comprising a first end member movable between a loaded position and an unloaded position, the accumulator delivering a kinetic driving energy when the first end member moves from its loaded position to its discharged position, and accumulating elastic potential energy when the first end member moves from its discharged 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 integral with the first end member of the energy accumulator and a second end mounted on the crankshaft of the transmission shaft, the transmission 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 exerts on the transmission shaft has no torque with respect to the geometrical axis of rotation of the transmission shaft, the low dead point 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 overtravel beyond its discharged position, to an end position;
• the chassis is provided with a deformable auxiliary energy accumulation means, this energy accumulation 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 fit:
  • deforming by absorbing at least a portion of the kinetic energy of the first end member of the energy accumulator when the first end member covers the overtravel toward the end position; and
  • recovering its initial shape by restoring to the first end member in the form of kinetic energy a portion of the kinetic energy that it has absorbed, when the first end member covers the overtravel beyond the discharged position by closer to the unloaded position.

The auxiliary energy storage means has a dual function. On the one hand, it dampens the shock transmitted by the battery to the chassis when passing through the bottom dead center. On the other hand, the restored energy accelerates the resetting of the energy accumulator.

According to one embodiment, the mechanism further comprises a freewheel coupling connecting the transmission shaft to the frame, allowing rotation of the transmission shaft in a direction of work and prohibiting the rotation of the transmission shaft in an opposite sense. A closing latch is adapted to lock the transmission shaft in an armed position, corresponding to the position charged with the energy accumulator. A switching shaft is adapted to be kinematically connected to at least one movable contact member of the switchgear. A coupling means integral with the transmission shaft is adapted to couple the transmission shaft to the switching shaft when the transmission shaft reaches a coupling position and to uncouple the transmission shaft from the switching shaft when the transmission shaft reaches a disengagement position, the coupling position being situated between the armed position and the low dead position position, in the working direction, the uncoupling position being situated between the coupling position and the bottom dead center position, in the working direction. The transmission shaft has a moment of inertia such that when the locking latch releases the transmission shaft, the first end member of the energy accumulator passes from its loaded position to its discharged position and causes the transmission shaft from its armed position to its bottom dead center position, then the transmission shaft continues to rotate from its bottom dead position toward its arming position in the working direction, causing the first end member from its unloaded position to its loaded position. The transmission shaft is then a flywheel which has a driving role after passing through the bottom dead center. The rearming of the device is then much faster. This This arrangement is particularly interesting for equipment of large dimensions. Indeed, the mass and the moment of inertia of the transmission shaft are sized according to the maximum torque to be transmitted to the contact members of the switchgear. The moment of inertia of the drive shaft increases with the dimensions of the contact members. The mechanism makes it possible to recover a portion of the kinetic energy of the shaft in order to partially rearm the springs. The engines that complete the rearmament then have less energy to supply, and can be dimensioned differently.

Preferably, the flexible link has a longitudinal elasticity such that it undergoes an elastic elongation when the first end member of the energy accumulator carries out its overtravel. According to one embodiment, the flexible link is a traction chain. 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:

• translation guiding means of the first movable end member relative to the frame along a geometric axis of translation fixed relative to the frame;
• a return pulley supported by the frame and in which the flexible link passes, such that a first portion of the flexible link is tensioned between the pulley and the first movable end member of the energy accumulator and is parallel to the translation axis, and 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 from the shaft on the one hand and the accumulator on the other hand, part of the forces transmitted by the flexible link being taken up by the support axis of the pulley. In addition, the pulley allows a return angle which limits the overall size of the mechanism. Since the transmission of the movement of the energy accumulator to the shaft is done by means of a flexible link, the relative positioning of the first end of the energy accumulator and the return pulley. does not have to 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 integral with one of the first and second end members, and a slider secured to the other of the first and second end members, the slider being movable in translation relative to the guide. The frame comprises at least one bearing abutment, the spring tending to bias the second end member against the abutment abutment. The telescopic link comprises an end stop disposed between the guide and the slider such that when the first end member moves from its loaded position to its unloaded position, the limit stop is interposed between the guide and the slider before the first end member reaches its unloaded position, and when the first end member continues its stroke past its unloaded position, the first movable member drives the second movable member. With such a device, there is no direct mechanical connection between the second end member of the energy accumulator and the frame of the mechanism at the time of arrival in the discharged position, which eliminates a source of energy. transmission of vibrations to the chassis. Advantageously, the limit stop is a damping stop capable of absorbing kinetic energy when the first end member passes from the intermediate position or the limit stop is interposed between the guide and the slide. in the unloaded position. The vibrations induced by the spring of the energy accumulator are absorbed by the damping stop while the first end member is overtravel, that is to say at a time when neither the first nor the second end member of the energy accumulator are not in contact with the frame.

Preferably, the transmission shaft is connected to the frame via a first freewheel. The mechanism further comprises: at least one electric motor connected to the transmission shaft via a second freewheel; a control device adapted to detect the passage of the transmission shaft by a predetermined position and to drive the electric motor, so that when the shaft of transmission exceeds its low dead center position, the electric motor starts to drive the driveshaft before the speed of the driveshaft vanishes. By thus controlling the electric motor, it is possible to take advantage of the kinetic energy acquired by the tree. In addition, if the damping and / or energy storage means are able to restore a portion of the energy they store during the overtravel of the first end member, it is also possible to take advantage of this energy, so that the rearming mechanism is very fast.

According to one embodiment, the auxiliary energy storage means comprises at least one stud comprising an elastomer material. The functions of energy accumulation and damping of the desired vibrations are thus accumulated very simply.

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 features will emerge more clearly from the description which follows, of a particular embodiment of the invention, given by way of non-limiting example, and represented in the accompanying drawings, in which:

• Figure 1 shows a perspective view of the mechanism of the invention in a position of bottom dead center, some parts have been omitted for better viewing;
• Figure 2 shows a view of the mechanism from another perspective, some parts having been omitted for better viewing;
• Figure 3 shows a sectional view of the apparatus, showing a subset of energy accumulation;
• Figure 4 shows a sectional view of the apparatus showing a start-up subassembly;
• Figure 5 shows a sectional view of the apparatus, showing a subset of arming;
• Fig. 6 is a sectional view of the apparatus showing a portion of a closing and opening control subassembly in a closed armed state;
• Figure 7 is a perspective view of a portion of the closing and opening control subassembly with a handle in a neutral position;
• Figure 8 shows a sectional view of the apparatus, showing a control subassembly of a resetting electrical circuit.

DETAILED DESCRIPTION OF AN EMBODIMENT

With reference to FIGS. 1 and 2, a mechanism for operating a high-voltage electrical switchgear is composed mainly of a closing energy accumulator 10, an armature subassembly 12 and a shaft switching members 14, interconnected by means of a transmission shaft 16 and supported by a frame 18. The switching shaft 14 is intended to be kinematically connected to one or more movable contact members of the switchgear. cut, so as to cause them reversibly from an open position to a closed position.

The chassis 18 comprises two parallel main plates 20, 22, fixed to one another by spacers 24. Some elements of the mechanism are located between the plates 20, 22 so that to visualize them, it was necessary to represent dotted the plate 20 in the view of Figure 1 and similarly dotted the plate 22 in Figure 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) attached to the plates 20, 22 of the frame 18, so that their axes of rotation are parallel to each other and perpendicular to the plane of the plates 20, 22 and 23.

The energy accumulator 10, shown in section in FIG. 3, comprises two pairs of coil storage springs 26, held by a stiffening structure 28. This structure is composed of a first end plate 30 and a second end plate 32, connected to each other via a telescopic guide link. The telescopic link is formed by two parallel guides, each having a rod 34 integral with the first end plate 30, and sliding in a tube 36 integral with the second end 32. Each tube is provided with a bottom 38 pierced with an axial guide hole allowing free translation of the corresponding rod 34. A stop 42 consisting of a washer of elastomeric material surmounted by a metal washer, rests on this bottom 38. The free end of each rod 34 is inserted into the corresponding tube 36 and provided with a nut 44 forming a shoulder capable of coming into contact with the corresponding stop 42. The telescopic link obtained allows a translation movement of the first end plate 30 with respect to the second end plate 28, along a geometric axis of translation parallel to the rods 34. This movement is limited in the sense of distance. by encountering the shoulder formed by the nut 44, with the elastomeric limit stop 42.

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

Two identical windows 50 of generally rectangular shape, visible more particularly in Figures 4 and 7, are formed in the frame plates 20, 22 and arranged opposite one another. Each rectangular window 50 defines two long lateral sides 52 and two small horizontal sides 54, 56, one lower (54), the other upper (56). Two spans 58 are arranged side by side along the small 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 frame.

The end plates 30, 32 of the energy accumulator are provided with positioning ribs 60, cooperating with the rims of the windows, so as to guide the two end plates 30, 32, allowing their translation to follow. a geometric axis perpendicular to the geometric bearing plane defined by the bearing surfaces 58. In other words, the rods 34 remain substantially perpendicular to the geometric bearing plane, regardless of the movement of the energy accumulator 10 in the windows 50. The guidance is provided with a game of a few millimeters. The long sides 52 of the two windows 50 are provided with two grooves 62 for mounting, allowing lateral insertion of the subassembly formed by the energy accumulator 10 during assembly of the mechanism.

The movement of the first end plate 30 is limited by four pads 64 of elastomeric material, which together define a geometrical contact plane with the plate 30. These pads 64 form end stops for the first end plate 30. The studs 64 are screwed into nuts 66 welded to the rim of the shorter lower sides 54 of the windows 50, and stopped by locknuts 68. During assembly of the apparatus, the accumulator 10 is assembled as a sub-assembly. The distance between the upper and lower grooves 62 of the windows corresponds to the distance between the two end plates 30, 32 of the stiffening structure 28 of the accumulator 10. in its unloaded state. In order to insert this subassembly into the chassis, the studs 64 are screwed down, which has the effect of lowering the above-mentioned contact plane, below the level of the groove 62 below. It is then possible to insert the accumulator 10 laterally through the windows 50. Once the accumulator 10 has been inserted, the studs 64 are partially unscrewed, so as to progressively raise the accumulator until the upper plate 32 or in contact with the bearing surfaces 58 and that the lower plate 30 is in contact with the pads 64, the battery 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 bearing plane defined by the bearing surfaces 58 on the one hand, and the geometric contact plane 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 battery 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 frame 18. The two projecting parts of the plate 30 are each provided with a pair oblong holes.

The transmission shaft 16 is provided with two parallel cranks 70, 72 identical, visible in FIGS. 1 and 2. The cranks 70, 72 are situated on either side of the space portion 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 axis 76, a middle portion is located in the groove.

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

Each pull chain 80 is stretched between one of the cranks 70 and the projecting portion of the first plate 30 located on the same side of the plates 20, 22 of the frame. One end of the chain 80 is provided with an eyelet 82 forming a sleeve which pivots on the eccentric axis 76 of the crank. In FIG. 2, the eyelet is shown in dashed lines so as to make it possible to visualize the axis 76. The other end of the chain 80 is provided with a double eyelet 84, which is inserted into the pair of open oblong holes. and stopped by a pin 86. The chain 80 passes into an intermediate pulley 90, mounted idle on an axis 92 supported by the frame 18. A portion 94 of the chain, stretched between the pulley and the first end plate, is parallel to the axis of translation of the first plate 30, thus parallel to both the geometric axis defined by the telescopic guide connection of the stiffening structure 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 axis 76.

Each chain 80 works in a plane parallel to the plates 20, 22 of the chassis. There are two positions of the mechanism in which the geometric plane containing the geometric axis of rotation of the transmission shaft 16 and the pivot axis 76 of the bushing 82 becomes tangent to the periphery of the pulley 90 and to the part 96 chain. In one of these positions, visible in FIGS. 1 and 2, the bushing 82 is located between the shaft 16 and the pulley 90, which corresponds to a bottom dead center of the transmission shaft 16; to a position of stable equilibrium. In the other position, the drive shaft 16 is located between the bushing 82 and the pulley 90, which corresponds to a top dead center of the shaft 16, that is to say to an unstable equilibrium position. The length of the two chains 80 is such that when the transmission shaft 16 is placed in its low dead position - and stopped in this position - and the accumulator 10 is in its discharged state, the first plate of end 30 resting on the pads 64, the two chains 80 are subjected to a very low voltage, in fact the voltage just necessary for their maintenance in the pulleys 90.

As shown in FIG. 4, the central portion of one of the shafts 76 furthermore constitutes a roller 98 which cooperates with a cam 100 of a starting lever 102. The starting lever 102 is supported by a pivot 104 mounted on the chassis 18 and is biased by a starting spring 106, banded between a free end of the lever 102 and a cleat mounted on the frame. This subset constitutes a starting device. When the transmission shaft 16 moves from the low dead center position to the top dead position, it passes fugitively through an intermediate position of winding, in which the roller 98 encounters the cam 100. When the shaft continues its rotation, the roller 98 arms the starting lever 102. The cam 100 has a vertex point 108. Shortly before arriving in the top dead center position, for example at 1 degree from this position, in a so-called start position in load, the roller 98 passes the top 108 of the cam 100, so that the start lever 102, biased by the starting spring 106, becomes motor relative to the roller 98. The starting lever 102 remains motor up the roller 98 loses contact with the cam 100, about 5 degrees after the top dead center position, in a position called end of support.

The subset of armament 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 integral with the frame 18, and a pawl 116 mounted on a motorized pumping lever 122. Each pawl is biased towards a coupling position with the ratchet wheel, by a torsion spring. The manual pumping lever 118 and the motorized pumping lever 122 are both pivotally mounted on the transmission shaft 116. The pawls 112, 113, 114, 115, 116 and ratchet perform freewheel couplings between the transmission shaft 16 and the manual pumping lever 118, between the transmission shaft 16 and the motorized pumping lever 122 and between the transmission shaft 16 and the frame 18.

A free end of the manual pumping lever 118 is connected to an input shaft 124 via a reduction lever 126 pivoting relative to the frame about a pivot 128, and two connecting 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 manual pumping lever 118. The end of the input shaft 124 includes a key 134 allowing the insertion of a detachable crank 136 visible in FIG. 1. When an operator turns the crank 136 by one revolution, the reduction lever 126 effects an oscillation which is transmitted with a gear ratio to the manual pumping lever 118, so that the manual pumping lever 118 makes an angular oscillation - back and forth - of an amplitude corresponding to about one and a half teeth of the ratchet wheel 110. However, the manual pumping lever 118 is designed as a backup accessory . In normal use, it is in a rest position, bearing against a limit stop 138 of the support 120.

A free end of the motorized pumping lever 122 is provided with a roller 140 cooperating with a cam 142 keyed on an output shaft 144 of a geared motor unit 146, visible in FIG. 1. The geared motor unit 146 comprises two electric motors 148. , 150 engaging a gear train 152 connected to the output shaft 144. A return spring 154 tends to bias the motorized pump lever 116 counterclockwise in FIG. output shaft 144 rotates one revolution, the motorized pumping lever 116 makes a round-trip oscillation of an angular amplitude corresponding to about 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 between them an angle corresponding to 4.5 teeth of the ratchet wheel 110. In normal use, when the manual pumping lever 118 abuts the abutment 138, the pawl 114 of the stopping support forms with the adjacent pawl 113 of the manual pumping lever 118 an angle corresponding to 5.25 teeth of the ratchet wheel. Thus, when the ratchet wheel 110 initiates a rotation in the opposite direction to that allowed by the ratchets, it can not cover an angle greater than that corresponding to 0.25 teeth without being supported and stopped by one of the ratchets .

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

Referring to Figure 6, the transmission shaft 16 further supports and conventionally a drive cam 160 cooperating with a roller 162 mounted on a crank 164 fixed to the switching shaft 14. The cam has a portion non-motorized circular and a motor 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 moving contacts, each corresponding to a pole of the apparatus. A conventional configuration comprises 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. By moving from its open position to its closed position, the shaft 14 loads a spring of an elastic spring energy accumulator opening 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 reduction lever 178 which forms an intermediate lock. The reduction lever 178 pivots about an axis 180 and further comprises a second roller 182 cooperating with a rotary opening latch 184. The opening latch 184 is biased in the locking position by a spring (not shown), and controlled to an unlocking position by an opening control lock 186. This structure with three locks in cascade allows a reduction of the forces required for unlocking. The axes geometrical rotation of the three latches are parallel to each other and parallel to the geometric axes of 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 recall it in counterclockwise in Figure 6, to a locking position. The opening control latch 186, whose structure 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 shaft 210 is mounted in a bearing supported by the intermediate plate 23 of the frame, while a second bearing 222 is mounted on the plate 20. The control crank 216 is actuated by an electromechanical control relay 190 solenoid opening, provided with a plunger 192 with axial movement. The control crank 214 is actuated by a pin 224 supported by a rotary control lever 226. The lever 226 comprises a flywheel 228 projecting in front of the plate 20, so as to be accessible by an operator, this wheel being secured to the operator. 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 locking latch 196. The closing latches 196 and closure control 200 are pivotally mounted perpendicular to the plate 20, therefore parallel to the axes of rotation of the transmission shaft 16 and switching 14. They are recalled both by spring reminders which tend to recall them in the opposite direction of the clockwise in Figure 6, to their lock position. This structure with two cascaded locks allows a reduction of the forces required for unlocking. The closure control latch 200 has a structure close to that of the opening control latch 186, as shown in FIG. 7. It has a rotating hardware axis 240 having a half-moon cutout 242 cooperating with the closing latch 196, and two control cranks 244, 246. An end 248 of the shaft 240 is mounted in a bearing supported by the intermediate plate 23, while a second bearing 250 is mounted on the plate 20. The three hardware axes 210 , 230, 240 are parallel, so that the pivoting geometric axes of the closing control latch 200, the opening control latch 186 and the lever 226 are also parallel. The control crank 246 is actuated by a relay solenoid closing control electromechanical actuator 202, provided with a plunger 204 with axial movement. The control crank 244 is actuated by a pin 254 supported by the rotary control lever 226.

The steering wheel 228 of the handle 226 has a front face shown in Figure 8, facing the operator. It is capable of taking three positions: a neutral position shown in FIG. 8, a manual opening position, corresponding to a 90 ° rotation clockwise in FIG. 8, and a position manual control closing, corresponding to a rotation of 90 ° in the counterclockwise direction from the neutral position of Figure 8. The handle 226 is returned to its neutral center position by a spring wire 260 working in flexion. The ends of the spring wire 260 rest on two support pins 262, 264, and its median portion supports two bearing surfaces 266, 268 of the flywheel, the bearing 268 being coaxial with the pin 254. When the lever 226 moves from its neutral position to its position With the manual closing control, the stud 254 contacts the crank 244 of the closing control lock 196 and rotates the axle 240 and the half-moon 242, releasing the locking latch 196. The bearing 266 supports on the spring wire 260, which flexes and tends to return the handle to its neutral position, so that the joystick returns to position as soon as the operator drops it. Likewise, when the handle 226 moves from its neutral position to its manual opening position, the pin 224 rotates the crank 214 of the opening control latch 186, the axis 210 and the half-moon 212. releasing the opening latch 184. Simultaneously, the bearing 268 presses the spring 260 which flexes and tends to return the handle 226 to its neutral position.

When the roller 194 is locked by the lock 196, the transmission shaft 16 is about 1 degree beyond the top dead center position. This position of the mechanism will be said in the following position armed, and corresponds to a compressed position of the spring accumulator 10, which will be said charged position of the accumulator 10. It should be noted that the accumulator 10 is made to be compressed very slightly beyond its loaded position, when the mechanism passes through the top dead center.

The transmission shaft 16 further comprises a resetting control cam 204 visible in Figure 7, on which the crank 70 was deliberately omitted. The resetting control cam 204 cooperates with a rocker lever 206 which causes an electrical contact 208. The electrical contact 208 opens and closes a supply circuit of the two electric motors 148, 150 of the geared motor.

The operation of the mechanism is now described, assuming that initially the drive shaft 16 is in the armed position and the switching shaft 14 in the open position.

In the armed position, the transmission shaft 16 is retained in the immediate vicinity and slightly beyond the top dead center, by the hooking achieved by the closing lock 196. The springs 26 of the accumulator 10 are bandaged and exert on the two end plates 30, 32 a large thrust tending to move the plates 30, 32 away from each other. The second end plate 32 bears 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 the chains 80 to the cranks 70, 72 have a moment very low or zero relative to the axis of rotation of the shaft 16, due to the position of the cranks 70, 72 and the friction of the mechanism. The starting lever 102 is in a driving position with respect 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 rocking lever 206, so that the electrical contact 208 is open and that the motors 148, 150 are stopped.

Starting from the armed position, a manual closing order on the handle 226, or electrical on the closing control relay 202, rotates the closing control lock 200 to release the lock lock 196. then the latch 196 in the clockwise direction, which releases the drive shaft 16. The start lever 102 then plays its driving role. It drives the roller 98 and with it the transmission shaft 16, with a calibrated moment, a few degrees to the end position of support, located at 5 ° from the top dead center position. Even before reaching this end of support position, the transmission shaft 16 leaves the angular sector of friction which corresponds to an angle of +/- 3 ° around the top dead center position, so that the chains 80 begin to transmit a driving torque to the cranks 70, 72. In this very first phase of the closure, the The switching shaft 14 remains stationary because the roller 162 is still rolling 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 to be provided by spring. starting 106.

As soon as the angular position is reached allowing the chains 80 to become driving, the springs 26 of the accumulator 10 relax and drive the first end plate 30, the two chains 80 and the transmission shaft 16 in rotation. The second end plate 32 remains in abutment against the bearings 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 position fugitive start of drive shaft drive, 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 the closed position. The transmission shaft 16 thus transmits in this phase the kinetic energy of the energy accumulator 10 to the switching shaft 14.

When the switching shaft 14 arrives in the closed position, the trigger tip 172 disappears in contact with the intermediate lock 178, and then spring under the thrust of the trigger spring 174. The spring force of the energy accumulator opening 170 tends to rotate the cam 164 clockwise, so that the trigger 172 abuts against the intermediate lock 178, and urges the intermediate lock 178 clockwise. The intermediate lock bears against the opening latch 184 and urges it clockwise. The opening latch 184 in turn bears against the opening control latch 186 where it is blocked by the half-moon 212 in the locked position, thereby locking the switching shaft 14 in position closed. Before reaching the bottom dead center position, at 165 ° from the top dead center position, the cam 160 loses contact with the roller 162, which disconnects the switching shaft 14 from the transmission 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 transmission shaft 16 is independent of that of the switching shaft 14.

Shortly before the transmission shaft 16 reaches its bottom dead center position, the reset control cam 160 starts driving the rocker lever 206 into an actuating position of the electrical contact 208. The latter closes a circuit of FIG. supply of the motors 148, 150, which begin to drive the gear trains 152. The motorized pumping lever 122 oscillates but the pawl 116 does not engage with the ratchet wheel 110 as long as the angular velocity of the wheel 110 is greater than the angular velocity of the pumping lever 122. Thus, the geared motor can gradually reach its operating speed before starting to drive the transmission shaft 16 in a subsequent phase described below.

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

Upon expansion of the springs 26, the first plate 30 has acquired significant kinetic energy. 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 detach from its support on the bearing surfaces 58 and to move en bloc in the launch of the first plate 30. This energy is sufficient to cause an elongation of the chains 80 by elastic deformation. The first end plate 30 then sinks into the pads 64 which compress. Under the effect of these joint stresses, the end plate 30 strongly decelerates until its speed vanishes.

Due to the relatively large kinetic moment of the transmission shaft 16 and the moving masses which are integral with it, the transmission shaft 16 tends to continue its travel beyond the low dead point and initiates a rearmament a little more chains 80. The pads 64 tend to want to regain their original shape and pushing the end plate 30, thereby restoring a portion of the energy they have stored. At the same time, the chains 80 tend to regain their original size. Its effects accumulate to immediately propel the end plate 30 in the direction of rearming. In practice, it is found that the contact between the plate 30 and the pads 64 only gives rise to a rebound. It must also be emphasized that this phase is very fast and that the deformations described are of very small amplitude. As an indication, the amplitude of the overtravel of the first end plate 30, which corresponds to the depression of the pads 64 and approximately to the detachment of the second plate 32, is of the order of ten millimeters.

Under the effect of the kinetic energy of the transmission shaft 16 and the moving masses which are integral with it, the transmission shaft 16 performs nearly a third of the rearming stroke by decelerating progressively until that the ratchet wheel 110 causes the coupling of the transmission shaft to the geared motor. In this phase, the transmission shaft 16 acts as a flywheel. The mechanism thus makes it possible to recover in this phase a large part of the energy available in the mechanism at the passage through the bottom dead point, thus saving considerable time in the subsequent phase of rearming the accumulator 10, which will to be described now.

Under the effect of the springs 26 of the accumulator 10, the rotation speed of the transmission shaft 16 is canceled, and the shaft 16 tends to start in the opposite direction. Immediately, one of the four stationary pawls 112, 113, 114, 115 hooks the ratchet wheel 110, unless it is directly supported by the pawl 116 of the motorized pumping lever 122, according to its own oscillation. The staggered arrangement of the four pawls 112, 113, 114, 115 allows in any case to ensure that the shaft 16 will be hooked before having traveled more than a quarter of the angular sector of a tooth of the ratchet wheel in the opposite direction of the direction of travel. This therefore makes it possible to limit the impact of the pawl supporting the ratchet wheel 110. The motorized pumping lever 122 then takes charge of the ratchet wheel 110 and makes it traverse an angular sector corresponding to 3.5 teeth to each of the ratchet wheels 110. his half-motor oscillations. During each non-driving half-oscillation, when the cam 142 releases the motorized pumping lever 122 and the spring 154 recalls the lever 122 towards its end-of-travel position in the opposite direction of the needles 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 transmits the accumulator 10 to the battery 10. mechanical energy produced by the motors 148, 150. The compression of the springs 26 of the accumulator 10 continues until the transmission shaft 16 reaches its top dead center.

When the transmission shaft 16 continues its travel towards the top dead center, the roller 98 of the crank 72 meets the starting lever 102 and drives it to a cocking position by pulling the starter spring 106. Shortly before that the transmission shaft 16 reaches its top dead center, the roller 98 passes the top 108 of the cam 100 of the starting lever 102, so that the start lever 102 becomes motor. At approximately the same time, the pawl 116 of the motorized pumping lever 122 is found opposite the toothless angular sector 158 of the ratchet wheel 110, whereas the resetting control cam 204 releases the contact 208 which opens the pawl circuit. supply of motors 148, 150. Even if the stopping of the electric motors is not instantaneous, the absence of teeth ensures the decoupling between the motorized pumping lever 122 and the transmission shaft 16. The transmission shaft 16 passes the top dead center under the bias of the starting lever 102, until the roller 194 of the drive cam 160 comes into contact with the locking latch 196. The latch is biased 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 stops in the armed position. The control subassembly is then in the closed, armed state shown in FIG.

As for the switching shaft 14, its subsequent movement from the closed position is dictated by the opening spring 170 and by the opening latch 184. The manual opening order given by rotation of the handle 226, or electromechanical relay 190, is transmitted to the opening control lock 186, the opening lock 184 and the intermediate lock formed by the reduction lever 178, the latter fading and releasing the trigger 172. The switching shaft 14 then moves 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 encountering the drive cam 160. Arrived in the open position, the switching shaft 14 is stopped by end stops (not shown), and the roller 162 comes into contact with the cam, if it has completed its rearming.

Naturally, various modifications are possible.

The electrical equipment concerned can be of any type, including a high-voltage circuit breaker or a high-voltage switch. The intended voltage range includes both medium voltage and very high voltage.

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

The mechanism may include only one pull chain. The chain or chains can be replaced by any type of flexible connection allowing tensile stress, for example a belt or a cable. Naturally, we will be interested in choosing a flexible link with a certain elasticity. In practice, the elasticity of conventional articulated traction chains is sufficient to allow the chain to lengthen when passing through the bottom dead center.

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

The springs of the energy accumulator may be traction springs rather than compression springs, if the overall bulk permits.

In the discharged state of the accumulator, the springs 26 can be further slightly compressed, which limits their movement when they are subjected to shocks from the passage through the bottom dead center. The discharged state is always the state in which the springs 26 can no longer supply energy to the plate 30, and corresponds to the position where the nuts 44 meet the stops 42.

The intermittent transmission members constituted by the pumping levers 118 and 122 may be replaced by continuous transmission means. The freewheel couplings may be made by means other than a ratchet mechanism 110 and pawls 112, 113, 114, 115, 116, for example with intermediate balls or coupling rollers between two cylindrical surfaces. .

The starter subassembly may be of any type that makes it possible to apply a force to the shaft on a part of the stroke thereof, close to the armed position. It may be for example a drawer device movable in translation. This subassembly does not necessarily act on the crank 72, as any element integral with the shaft may also be suitable. It is possible to provide that the winding of the starting spring is not carried out via the transmission shaft, but for example directly by the geared motor.

The number of intermediate locks between the locking latch and the corresponding relay on the one hand, and the opening latch and the corresponding relay on the other hand, is chosen according to the reduction of forces required.

Claims (12)

1. An actuating mechanism for electrical high voltage switches comprising:

   • a frame (18),

   • a transmission shaft (16) rotatably mounted around a geometric axis of rotation that is fixed in relation to the frame (18), the transmission shaft (16) being fitted with at least one crank (70, 72);

   • at least one resilient potential energy accumulator (10), comprising a first end device (30) that is movable between a loaded position and an unloaded position, the accumulator (10) supplying motive kinetic energy when the first end device (30) moves from its loaded position to its unloaded position, and accumulating resilient potential energy when the first end device (30) moves from its unloaded position to its loaded position;

   • at least one flexible tow link (80) stretched between the energy accumulator (10) and the crank (70, 72), the flexible tow link (80) having a first end (84) integrally formed with the first end device (30) of the energy accumulator (10) and a second end (82) mounted on the crank (70, 72) of the transmission shaft (16), the transmission shaft (16) being rotatably mounted between a top dead centre position and a bottom dead centre position, the two dead centre positions being positions in which the flexible link (80) does not exert on the transmission shaft (16) any torque in relation to the geometric axis of rotation of the transmission shaft (16), the bottom dead centre position being reached when the first end device (30) of the accumulator is in its unloaded position;

   characterized in that:

   • the first end device (30) is adapted to perform overtravel beyond its unloaded position, up to an end-of-travel position;

   • the frame (18) is fitted with a deformable auxiliary means of energy accumulation (64), this means of energy accumulation co-operating with the first end device (30) when the first end device (30) is located between the unloaded position and the end-of-travel position and being adapted:

   • to deform by absorbing at least a portion of the kinetic energy of the first end device (30) of the energy accumulator when the first end device covers the overtravel in the direction of the end-of-travel position; and

   • to recover its initial shape by restoring to the first end device in the form of kinetic energy a portion of the kinetic energy that it absorbed , when the first end device (30) covers the overtravel beyond the unloaded position whilst approaching the unloaded position.
2. An actuating mechanism according to claim 1, characterised in that the mechanism further comprises:

   • a free wheel coupling (110, 114, 115) connecting the transmission shaft (16) to the frame (18), enabling the rotation of the transmission shaft (16) in a working direction and preventing the rotation of the transmission shaft (16) in an opposite direction.
3. An actuating mechanism according to claim 2, characterised in that the mechanism further comprises:

   • a closing lock (196) adapted to lock the transmission shaft (16) in a set position, corresponding to the loaded position of the energy accumulator (10);

   • a switching shaft (14) adapted to be kinematically connected to at least one movable contact device (166) of the electrical switches;

   • a coupling means (160) integrally formed with the transmission shaft (16) and adapted to couple the transmission shaft (16) with the switching shaft (14) when the transmission shaft (16) reaches a coupling position and to uncouple the transmission shaft (16) from the switching shaft (14) when the transmission shaft (16) reaches an uncoupling position, the coupling position being located between the set position and the bottom dead centre position, in the working direction, the uncoupling position being located between the coupling position and the bottom dead centre position, in the working direction.
4. An actuating mechanism according to claim 3, characterised in that the transmission shaft (16) has a moment of inertia such as when the closing lock (196) releases the transmission shaft (16), the first end device (30) of the energy accumulator (10) moves from its loaded position to its unloaded position and drives the transmission shaft (16) from its set position towards its bottom dead centre position, then the transmission shaft (16) pursues its rotation from its bottom dead centre position in the direction of its setting position in the working direction whilst driving the first end device (30) from its unloaded position to its loaded position.
5. An actuating mechanism according to any one of the preceding claims, characterised in that the flexible link (80) features longitudinal resilience such that it undergoes resilient elongation when the first end device (30) of the energy accumulator (10) performs its overtravel.
6. An actuating mechanism according to any one of the preceding claims, characterized in that the flexible link (80) is a tow chain.
7. An actuating mechanism according to any one of the preceding claims, characterised in that it further comprises:

   • translation guiding means (52, 60) of the first end device that is movable in relation to the frame (18), following a geometric axis of translation that is fixed in relation to the frame (18);

   • a guide pulley (90) supported by the frame (18) and through which the flexible link (80) passes, such that a first portion (94) of the flexible link is stretched between the pulley (90) and the first movable end device (30) of the energy accumulator (10) and is parallel to the axis of translation, and that a second portion (96) of the flexible link is stretched between the pulley (90) and the crank (70, 72).
8. An actuating mechanism according to claim 7, characterised in that the second portion (96) of the flexible link forms an angle in the order of 135° with the first portion (94) of the flexible link.
9. An actuating mechanism according to any one of the preceding claims, characterised in that

   • the energy accumulator (10) comprises:

   • a second end device (32),

   • at least one spring (26) stretched between the first end device (30) and the second end device (32),

   • a telescopic link device comprising a guide (36) integrally formed with one of the first and second end devices, and a slider (34) integrally formed with the other of the first and second end devices, the slider (34) being translationally movable in relation to the guide (36),

   • the frame (18) comprises at least one support stop (58), the spring (26) tending to bring the second end device (32) against the support stop (58),

   • the telescopic link comprises an end-of-travel stop (42) disposed between the guide (36) and the slider (34) such that when the first end device (30) moves from its loaded position to its unloaded position, the end-of-travel stop (42) fits between the guide (36) and the slider (34) before the first end device (30) reaches its unloaded position, and when the first end device (30) continues its travel beyond its unloaded position, the first movable device (30) drives the second movable device (32).
10. An actuating mechanism according to claim 9, characterised in that the end-of-travel stop (42) is a damping stop adapted to absorb kinetic energy when the first end device moves from the intermediate position in which the end-of-travel stop (42) fits between the guide (36) and the slider (34) to its unloaded position.
11. An actuating mechanism according to any one of the preceding claims, characterised in that

    • the transmission shaft (16) is connected to the frame (18) by means of a first free wheel (110, 114, 115);

    • the mechanism further comprises:

    • at least one electric motor (148, 150) connected to the transmission shaft (16) by means of a second free wheel (110, 116),

    • a control device (204, 206, 208) adapted to detect the passage of the transmission shaft (16) through a predetermined position, and to drive the electric motor (148, 150), such that when the transmission shaft (16) exceeds its bottom dead centre position, the electric motor (148, 150) begins to drive the transmission shaft (16) before the speed of the transmission shaft (16) cancels out.
12. An actuating mechanism according to any one of the preceding claims, characterised in that the auxiliary means of energy accumulation (64) comprises at least one pad comprising an elastomeric material.

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