EP0881652B1 - Spring motor driving mechanism for a switching device, in particular for a circuit breaker - Google Patents

Spring motor driving mechanism for a switching device, in particular for a circuit breaker Download PDF

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Publication number
EP0881652B1
EP0881652B1 EP98401186A EP98401186A EP0881652B1 EP 0881652 B1 EP0881652 B1 EP 0881652B1 EP 98401186 A EP98401186 A EP 98401186A EP 98401186 A EP98401186 A EP 98401186A EP 0881652 B1 EP0881652 B1 EP 0881652B1
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EP
European Patent Office
Prior art keywords
toothed wheel
tooth
teeth
large toothed
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP98401186A
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German (de)
French (fr)
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EP0881652A1 (en
Inventor
Rolf Niklaus
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General Electric Switzerland GmbH
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GEC Alsthom T&D AG
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Publication of EP0881652A1 publication Critical patent/EP0881652A1/en
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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/22—Power arrangements internal to the switch for operating the driving mechanism
    • H01H3/30—Power arrangements internal to the switch for operating the driving mechanism using spring motor
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/22—Power arrangements internal to the switch for operating the driving mechanism
    • H01H3/30—Power arrangements internal to the switch for operating the driving mechanism using spring motor
    • H01H2003/3063—Decoupling charging handle or motor at end of charging cycle or during charged condition
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts
    • H01H3/36—Driving mechanisms, i.e. for transmitting driving force to the contacts using belt, chain, or cord

Definitions

  • European patent application No. 0 651 409 A1 describes a mechanism of this type.
  • all the teeth of the toothed pinion as well as the first tooth following, in the predetermined direction, the clearance generated by the discontinuity of the toothing of the large toothed wheel are configured so that their sides converge on a single edge.
  • the purpose of this measure is to prevent the gear wheels from blocking.
  • the friction of an edge of the toothed pinion on the side of attack of the first tooth following the release of the ferris wheel toothed generates more or less significant power losses due friction.
  • European patent No. 0 294 561 A2 describes a drive mechanism of a similar type, coupled to a disconnector and the first tooth of the large gear wheel, which is located immediately after the release is radially retractable against the stress of a compression spring. Yes this tooth abuts against the top of a tooth of the toothed pinion, at the beginning of latching process, it retracts radially by compressing the spring associated with it. As a result, this tooth can slide, without generating blocking on the edge of the corresponding tooth of the toothed pinion. When she has passed this edge, it engages in the hollow which follows the tooth of the pinion toothed.
  • the present invention proposes to remedy all of these disadvantages and remove the risk of malfunctions of these known mechanisms offering an effective solution, simple to perform and little expensive and which can also be adapted by a transformation appropriate, to mechanisms of this type that are already in use.
  • the tooth of the toothing of said large gear wheel that follows the additional clearance has a shape similar to that of the retractable tooth.
  • said additional clearance extends over three gear pitches.
  • said retractable tooth is prominent, in the non-retracted state, compared to the other teeth of the teeth of the big gear.
  • At least one additional tooth, beyond said first tooth which follows the complementary clearance of said large gear wheel has a shape similar to that of the retractable tooth.
  • An engagement spring 15, consisting by a tension spring, is coupled to the large toothed wheel 13 at a point attachment 16, via a chain 17 or any other means suitable, which passes over an angular pulley 18 in the example represented.
  • the large toothed wheel 13 meshes with a toothed pinion 19 which is coupled via a gear train 20 to an integral drive pinion 21 an output shaft 22 of a drive motor 23.
  • the engagement spring 15 exerts a traction on the chain 17 and causes the rotation of the large gear 13, in the predetermined direction indicated by arrow A, the attachment point 16 passing from a waiting position located slightly downstream (in the direction predetermined A of rotation of the large gear wheel) from neutral 16a, to a final position corresponding to a relaxation point 16b which is diametrically opposite to neutral 16a.
  • the engine 23 takes over to drive the drive shaft 11 rotating in the predetermined direction A. This movement continues until the point of attachment of the interlocking spring exceeds again slightly neutral 16a and where this spring is armed.
  • a mechanism with pawl 24 which comprises a pawl 25 actuated by an electromagnet 26 and a stop 27 mounted on one of the faces of the large toothed wheel 13, which cooperates with the pawl 25 to stop this wheel in the desired waiting position.
  • the mechanism 10 comprises a main shaft 30 which in particular carries an actuating lever 31 of a lever (not shown) of the switching device, a coupling lever 32 of this shaft to a trigger spring 33, a roller-carrying lever 34 which carries a cam follower roller 34a which cooperates with the cam 14, a locking lever 35 which cooperates with a pawl 36 actuated by an electromagnet 37 and a braking lever which is coupled to a brake 38 constituted for example by an oil jack or the like.
  • the trigger spring 33 is preferably identical or similar to the engagement spring 15 and is connected by means of a chain 39 guided by an angle deflection pulley 40 to the coupling lever 32.
  • the cam follower roller 34a is resting against the cam 14 mounted on the engagement shaft 11.
  • This cam controls the movement of the lever 34 between two positions 41a and 41b which correspond respectively to the positions I and O of the actuating lever 31.
  • the pawl 36 ensures the locking of the locking lever 35 in a position which corresponds to position I of the actuating lever 31.
  • Figure 2 shows, on an enlarged scale, part of the Ferris wheel toothed 13 and the toothed pinion 19.
  • the teeth of the pinion 19 have a particular geometry which corresponds to a point size.
  • the flanks of these teeth join radially outward on an edge common and present, on the flank of attack, a developing and on the opposite flank, a plane starting from the edge and which is inclined with respect to a radial straight line passing through the middle of the corresponding tooth.
  • the large toothed wheel 13 comprises, in the predetermined direction A of rotation a discontinuity in the toothing 51, this discontinuity generating a clearance 52 which constitutes an area without teeth.
  • a retractable tooth 53 is arranged in this clearance. It is attached to a socket 54 partially recessed which is housed in a recess 55 substantially cylindrical, arranged in the thickness of the large gear wheel.
  • a spring of compression 56 is mounted in the closed space delimited between the cavity of the recessed bush 54 and recess 55 of the wheel, this spring tending to push the tooth 53 radially outward from the wheel.
  • a plate stop 57 is fixed to the bottom of the clearance 52 so as to close off partially the recess 55. This stop plate is fixed by means of minus one and preferably two locking screws 58. Thanks to this assembly, the tooth 53 can partially retract inside the recess 55, at against the stress exerted by the compression spring 56.
  • the large wheel 13 has a additional clearance 60 which is generated by a discontinuity complementary to the toothing 51 of this wheel.
  • This clearance extends over at least two gear steps. According to a preferred embodiment, this clearance extends over three gear steps.
  • the tooth 61 of the toothing of the large gear wheel, which follows said clearance complementary 60 has a shape similar to that of the retractable tooth 53.
  • the flanks join radially towards outside on a common ridge.
  • the opposite flank to the attack flank has an inclined plane in its upper part adjacent to the edge of the tooth.
  • the retractable tooth 53 is prominent over the others teeth 51 of the teeth of the large gear wheel, which has the advantage of reduce the likelihood that its tip will come into contact with the tip of a pinion tooth 19.
  • Figures 3A to 3D illustrate what happens when the tip of a tooth 50 pinion 19 meets tip of retractable tooth 53 of ferris wheel toothed 13. The initial instant of this contact between the two teeth 50 and 53 is shown in Figure 3A.
  • the retractable tooth 53 retracts as shown in FIG. 38.
  • Two teeth 53a and 53b are shown in dotted lines. In fact they have been deleted and replaced by said additional clearance 60. It can be seen that if these two teeth had been retained, the risk that the next tooth 50a of the pinion 19 comes into contact and blocks tooth 53a would be very high. It's here reason why additional clearance was planned and that at least two teeth 53a and 53b have been removed. This release complementary completely eliminates the risk of blocking the big wheel toothed.
  • Figure 3C shows how the teeth of two wheels behave toothed.
  • the teeth 50a and 50b which follow the tooth 50 of the pinion 19 are located in the area of the additional clearance 60 during the entire movement joint of teeth 50 and 53.
  • Figure 3D shows the position of tooth 50c which comes into contact with the tooth 61 which is the first tooth following complementary clearance 60 of the large toothed wheel 13. It can be seen that the two teeth 50c, 61 do not cannot block each other due to their specific shape.

Abstract

The mechanism has a large cogged wheel (13) with a set of gear teeth (53), which are axially retractable by means of a spring (56). The wheel follows a direction (A) and as a fixed tooth portion (60) moves forward the retractable gear tooth disengages.

Description

La présente invention concerne un mécanisme d'entraínement à ressort pour un appareil de commutation de puissance, en particulier pour un commutateur de puissance pour moyenne et haute tension et notamment un disjoncteur, ce mécanisme comportant:

  • un ressort d'enclenchement, qui est couplé excentriquement à un arbre d'enclenchement librement rotatif autour de son axe, ledit ressort étant agencé pour entraíner d'une part l'arbre d'enclenchement dans un sens prédéterminé de rotation pour assurer la mise en circuit de l'appareil de commutation et d'autre part une grande roue dentée montée sur l'arbre d'enclenchement et un pignon denté qui engrène ladite grande roue dentée et qui est couplé à un organe d'entraínement pour entraíner ladite grande roue dentée par l'intermédiaire dudit pignon denté et ledit arbre d'enclenchement dans ledit sens prédéterminé pour mettre sous contrainte le ressort d'enclenchement en vue de la mise en circuit de l'appareil de commutation, ledit arbre d'enclenchement étant agencé pour passer d'une position initiale dans laquelle le ressort d'enclenchement est au moins partiellement détendu. au-delà d'une position de point mort dans laquelle le ressort d'enclenchement est sous contrainte,
  • un mécanisme à cliquet qui est agencé pour être en appui contre ladite grande roue dentée dans une position d'appui qui se situe au-delà de la position de point mort dans ledit sens prédéterminé et pour libérer ledit arbre d'enclenchement pour la mise en circuit dudit appareil de commutation,
  • un dégagement ménagé à la périphérie de ladite grande roue dentée et générée par une discontinuité dans la denture de cette grande roue dentée, ce dégagement étant ménagé dans une zone de la denture qui se situe près dudit pignon denté lorsque l'arbre d'enclenchement est en appui contre le mécanisme à cliquet,
  • des moyens pour empêcher le blocage mutuel de la grande roue dentée et du pignon denté après la libération de l'arbre d'enclenchement par le mécanisme à cliquet, ces moyens comprenant:
    • une forme des dents dudit pignon denté dont les flancs se joignent. radialement vers l'extérieur, sur une arête commune et présentent sur le flanc d'attaque, une forme en développante et sur le flanc opposé, un plan partant de l'arête et qui est incliné par rapport à une droite radiale passant par le milieu de la dent, et,
    • une forme de la dent de la grande roue dentée qui se présente après le dégagement, dans ledit sens prédéterminé, dont les flancs se joignent radialement vers l'extérieur sur une arête commune et qui comporte un plan incliné dans sa zone supérieure adjacente à l'arête.
The present invention relates to a spring drive mechanism for a power switching device, in particular for a power switch for medium and high voltage and in particular a circuit breaker, this mechanism comprising:
  • a latching spring, which is eccentrically coupled to a latching shaft freely rotatable about its axis, said spring being arranged to drive on the one hand the latching shaft in a predetermined direction of rotation to ensure the setting circuit of the switching device and on the other hand a large toothed wheel mounted on the interlocking shaft and a toothed pinion which meshes with said large toothed wheel and which is coupled to a drive member for driving said large toothed wheel by means of said toothed pinion and said engagement shaft in said predetermined direction for stressing the engagement spring with a view to switching on the switching apparatus, said engagement shaft being arranged to pass from an initial position in which the engagement spring is at least partially relaxed. beyond a neutral position in which the engagement spring is under stress,
  • a ratchet mechanism which is arranged to bear against said large toothed wheel in a support position which is located beyond the neutral position in said predetermined direction and to release said engagement shaft for setting circuit of said switching apparatus,
  • a clearance provided at the periphery of said large toothed wheel and generated by a discontinuity in the teeth of this large toothed wheel, this clearance being provided in an area of the teeth which is located near said toothed pinion when the interlocking shaft is resting against the ratchet mechanism,
  • means for preventing the mutual locking of the large toothed wheel and the toothed pinion after the release of the engagement shaft by the ratchet mechanism, these means comprising:
    • a shape of the teeth of said toothed pinion whose sides join. radially outwards, on a common edge and have on the leading flank, an involute shape and on the opposite flank, a plane starting from the edge and which is inclined relative to a radial straight line passing through the middle of the tooth, and,
    • a shape of the tooth of the large toothed wheel which occurs after the release, in said predetermined direction, the sides of which join radially outward on a common edge and which has an inclined plane in its upper zone adjacent to the fish bone.

La demande de brevet européen No 0 651 409 A1 décrit un mécanisme de ce type. Dans cette réalisation toutes les dents du pignon denté ainsi que la première dent qui suit, dans le sens prédéterminé, le dégagement engendré par la discontinuité de la denture de la grande roue dentée, sont configurées de telle sorte que leurs flancs convergent vers une seule et même arête. Cette mesure a pour but d'empêcher un blocage des roues dentées. Toutefois, il s'est avéré que la friction d'une arête du pignon denté sur le flanc d'attaque de la première dent qui suit le dégagement de la grande roue dentée, engendre des pertes de puissance plus ou moins importantes dues aux frottements. Ces pertes qui dépendent de la position du pignon denté, ont pour conséquence des variations du temps requis pour enclencher l'appareil de commutation ainsi qu'une usure non négligeable de la première dent qui suit le dégagement de la grande roue dentée. Si le mécanisme est utilisé pour la commande d'un commutateur destiné à être enclenché pour réduire les surtensions du réseau, de façon synchrone avec la tension de ce réseau, de telles variations apparaissant de façon aléatoire ne sont pas tolérables.European patent application No. 0 651 409 A1 describes a mechanism of this type. In this embodiment all the teeth of the toothed pinion as well as the first tooth following, in the predetermined direction, the clearance generated by the discontinuity of the toothing of the large toothed wheel, are configured so that their sides converge on a single edge. The purpose of this measure is to prevent the gear wheels from blocking. However, it turned out that the friction of an edge of the toothed pinion on the side of attack of the first tooth following the release of the ferris wheel toothed, generates more or less significant power losses due friction. These losses, which depend on the position of the toothed pinion, have as a result of variations in the time required to switch on the device switching and significant wear of the first tooth which follows the release of the large gear wheel. If the mechanism is used for controlling a switch intended to be engaged to reduce network overvoltages, synchronously with the voltage of this network, such randomly occurring variations are not tolerable.

Le brevet européen No 0 294 561 A2 décrit un mécanisme d'entraínement d'un type similaire, accouplé à un sectionneur et dont la première dent de la grande roue dentée, qui se situe immédiatement après le dégagement est rétractable radialement contre la sollicitation d'un ressort de compression. Si cette dent bute contre le sommet d'une dent du pignon denté, au début du processus d'enclenchement, elle se rétracte radialement en comprimant le ressort qui lui est associé. De ce fait, cette dent peut glisser, sans générer de blocage sur l'arête de la dent correspondante du pignon denté. Lorsqu'elle a dépassé cette arête, elle s'engage dans le creux qui suit la dent du pignon denté. Toutefois, il existe un risque important que la dent rétractable continue à entraíner la grande roue dentée par frottement, malgré son escamotage progressif à l'intérieur du logement qui contient le ressort. Dans ce cas, la deuxième dent qui suit le dégagement ménagé sur la grande roue dentée, et qui n'est pas rétractable, peut buter contre l'arête d'une dent du pignon denté et bloquer tout l'engrenage. Cette probabilité est élevée, car le pignon denté est découplé de son entraínement par un accouplement à roue libre et peut donc tourner très facilement.European patent No. 0 294 561 A2 describes a drive mechanism of a similar type, coupled to a disconnector and the first tooth of the large gear wheel, which is located immediately after the release is radially retractable against the stress of a compression spring. Yes this tooth abuts against the top of a tooth of the toothed pinion, at the beginning of latching process, it retracts radially by compressing the spring associated with it. As a result, this tooth can slide, without generating blocking on the edge of the corresponding tooth of the toothed pinion. When she has passed this edge, it engages in the hollow which follows the tooth of the pinion toothed. However, there is a significant risk that the retractable tooth will continue to drive the big toothed wheel by friction, despite its retraction progressive inside the housing which contains the spring. In this case second tooth following the clearance provided on the large gear wheel, and which is not retractable, can abut against the edge of a tooth of the toothed pinion and lock all the gear. This probability is high, because the toothed pinion is decoupled from its drive by a freewheel coupling and can so turn very easily.

La présente invention se propose de remédier à l'ensemble de ces inconvénients et de supprimer les risques de dysfonctionnements de ces mécanismes connus en offrant une solution efficace, simple à réaliser et peu coûteuse et qui peut en outre être adaptée par une transformation appropriée, aux mécanismes de ce type qui sont déjà en service.The present invention proposes to remedy all of these disadvantages and remove the risk of malfunctions of these known mechanisms offering an effective solution, simple to perform and little expensive and which can also be adapted by a transformation appropriate, to mechanisms of this type that are already in use.

Ce but est atteint par le mécanisme tel que défini en préambule et caractérisé en ce que ledit dégagement ménagé à la périphérie de ladite grande roue dentée est suivi, dans ledit sens prédéterminé, d'une dent rétractable radialement contre la contrainte d'un ressort de compression, et en ce que ladite dent rétractable est suivie, dans ledit sens prédéterminé, par un dégagement complémentaire ménagé à la périphérie de cette grande roue dentée, généré par une discontinuité complémentaire de la denture, ce dégagement complémentaire s'étendant sur au moins deux pas d'engrenage.This goal is achieved by the mechanism as defined in the preamble and characterized in that said clearance provided at the periphery of said large wheel toothed is followed, in said predetermined direction, by a retractable tooth radially against the stress of a compression spring, and in that said retractable tooth is followed, in said predetermined direction, by a additional clearance provided at the periphery of this large wheel toothed, generated by a complementary discontinuity of the teeth, this additional clearance extending over at least two gear pitches.

Selon un mode de réalisation préféré, la dent de la denture de ladite grande roue dentée qui suit le dégagement complémentaire a une forme similaire à celle de la dent rétractable.According to a preferred embodiment, the tooth of the toothing of said large gear wheel that follows the additional clearance has a shape similar to that of the retractable tooth.

Selon une forme de réalisation particulièrement avantageuse, ledit dégagement complémentaire s'étend sur trois pas d'engrenage.According to a particularly advantageous embodiment, said additional clearance extends over three gear pitches.

De préférence, ladite dent rétractable est proéminente, à l'état non rétracté, par rapport aux autres dents de la denture de la grande roue dentée.Preferably, said retractable tooth is prominent, in the non-retracted state, compared to the other teeth of the teeth of the big gear.

Enfin, selon une forme de réalisation avantageuse, qui offre une garantie supplémentaire contre les risques de blocage de la grande roue dentée et du pignon, au moins une dent supplémentaire, au-delà de ladite première dent qui suit le dégagement complémentaire de ladite grande roue dentée a une forme similaire à celle de la dent rétractable.Finally, according to an advantageous embodiment, which offers a guarantee additional against the risk of blocking the large gear wheel and the pinion, at least one additional tooth, beyond said first tooth which follows the complementary clearance of said large gear wheel has a shape similar to that of the retractable tooth.

La présente invention sera mieux comprise en référence à la description d'une forme de réalisation préférée et des dessins correspondants donnés à titre d'exemple non limitatifs, dans lesquels :

  • La figure 1 représente une vue d'ensemble schématique illustrant une forme de réalisation préférée du mécanisme selon l'invention,
  • La figure 2 représente une vue de détail montrant plus spécifiquement la dent rétractable de la grande roue dentée, et
  • Les figures 3A, 3B, 3C et 3D illustrent la cinématique de la grande roue dentée et du pignon denté dans la zone où la dent rétractable engrène les dents du pignon.
    • The present invention will be better understood with reference to the description of a preferred embodiment and the corresponding drawings given by way of nonlimiting example, in which:
  • FIG. 1 represents a schematic overview illustrating a preferred embodiment of the mechanism according to the invention,
  • FIG. 2 represents a detail view showing more specifically the retractable tooth of the large gear wheel, and
  • FIGS. 3A, 3B, 3C and 3D illustrate the kinematics of the large toothed wheel and the toothed pinion in the zone where the retractable tooth meshes with the teeth of the pinion.

    • En référence à la figure 1, le mécanisme 10 d'entraínement à ressort tel que représenté, destiné à être couplé à un appareil de commutation comporte un arbre d'enclenchement 11, librement rotatif autour de son axe 12 et portant d'une part une grande roue dentée 13 et d'autre part une came 14 dont la fonction sera expliquée par la suite. Un ressort d'enclenchement 15, constitué par un ressort de traction, est couplé à la grande roue dentée 13 en un point d'attache 16, par l'intermédiaire d'une chaíne 17 ou de tout autre moyen approprié, qui passe sur une poulie de renvoi d'angle 18 dans l'exemple représenté. La grande roue dentée 13 engrène un pignon denté 19 qui est couplé via un train d'engrenages 20 à un pignon d'entraínement 21 solidaire d'un arbre de sortie 22 d'un moteur d'entraínement 23.Referring to Figure 1, the spring drive mechanism 10 as shown, intended to be coupled to a switching device comprises a interlocking shaft 11, freely rotatable about its axis 12 and bearing on the one hand a large toothed wheel 13 and on the other hand a cam 14 whose function will be explained later. An engagement spring 15, consisting by a tension spring, is coupled to the large toothed wheel 13 at a point attachment 16, via a chain 17 or any other means suitable, which passes over an angular pulley 18 in the example represented. The large toothed wheel 13 meshes with a toothed pinion 19 which is coupled via a gear train 20 to an integral drive pinion 21 an output shaft 22 of a drive motor 23.

    Cet ensemble de composants du mécanisme connu en soi et décrit en détail dans la demande de brevet européen Nr. 0 652 409 cité en préambule, est destiné, pour ce qui est du ressort d'enclenchement 15, d'entraíner l'arbre d'enclenchement 11 dans un sens prédéterminé de rotation A (voir flèche A sur la figure 1) en vue d'assurer la mise en circuit de l'appareil de commutation (non représenté) et pour ce qui est du moteur d'entraínement 23, de mettre sous contrainte le ressort d'enclenchement 15 afin qu'il soit armé et prêt à libérer son énergie accumulée pour assurer à tout moment la mise en circuit de l'appareil de commutation. A cet effet, lors d'un enclenchement de l'appareil, le ressort d'enclenchement 15 exerce une traction sur la chaíne 17 et provoque la rotation de la grande roue dentée 13, dans le sens prédéterminé indiqué par la flèche A, le point d'attache 16 passant d'une position d'attente située légèrement en aval (dans le sens prédéterminé A de rotation de la grande roue dentée) du point mort 16a, à une position finale correspondant à un point de relaxation 16b qui est diamétralement opposé au point mort 16a. Par la suite, le moteur d'entraínement 23 prend le relais pour entraíner l'arbre d'enclenchement 11 en rotation dans le sens prédéterminé A. Ce déplacement se poursuit jusqu'au moment où le point d'attache du ressort d'enclenchement dépasse à nouveau légèrement le point mort 16a et où ce ressort est armé. L'arrêt de la grande roue dentée, dans cette position est obtenu par un mécanisme à cliquet 24 qui comporte un cliquet 25 actionné par un électroaimant 26 et une butée 27 montée sur une des faces de la grande roue dentée 13, qui coopère avec le cliquet 25 pour arrêter cette roue dans la position d'attente souhaitée.This set of components of the mechanism known per se and described in detail in the European patent application Nr. 0 652 409 cited in the preamble, is intended, as regards the engagement spring 15, to drive the shaft engagement 11 in a predetermined direction of rotation A (see arrow A in FIG. 1) in order to ensure the switching on of the apparatus of switching (not shown) and with regard to the drive motor 23, to stress the engagement spring 15 so that it is armed and ready to release its accumulated energy to ensure at all times the switching on of the switching device. To this end, during a engagement of the device, the engagement spring 15 exerts a traction on the chain 17 and causes the rotation of the large gear 13, in the predetermined direction indicated by arrow A, the attachment point 16 passing from a waiting position located slightly downstream (in the direction predetermined A of rotation of the large gear wheel) from neutral 16a, to a final position corresponding to a relaxation point 16b which is diametrically opposite to neutral 16a. Subsequently, the engine 23 takes over to drive the drive shaft 11 rotating in the predetermined direction A. This movement continues until the point of attachment of the interlocking spring exceeds again slightly neutral 16a and where this spring is armed. The judgment of the large gear wheel, in this position is obtained by a mechanism with pawl 24 which comprises a pawl 25 actuated by an electromagnet 26 and a stop 27 mounted on one of the faces of the large toothed wheel 13, which cooperates with the pawl 25 to stop this wheel in the desired waiting position.

    Par ailleurs, le mécanisme 10 comporte un arbre principal 30 qui porte notamment un levier d'actionnement 31 d'une manette (non représentée) de l'appareil de commutation, un levier de couplage 32 de cet arbre à un ressort de déclenchement 33, un levier porte-galet 34 qui porte un galet suiveur de came 34a qui coopère avec la came 14, un levier de blocage 35 qui coopère avec un cliquet 36 actionné par un électroaimant 37 et un levier de freinage qui est couplé à un frein 38 constitué par exemple par un vérin à huile ou similaire. Le ressort de déclenchement 33 est de préférence identique ou similaire au ressort d'enclenchement 15 et est relié au moyen d'une chaíne 39 guidée par une poulie de renvoi d'angle 40 au levier de couplage 32. Le galet suiveur de came 34a est en appui contre la came 14 montée sur l'arbre d'enclenchement 11. Cette came commande le mouvement du levier 34 entre deux positions 41a et 41b qui correspondent respectivement aux positions I et O du levier d'actionnement 31. Le cliquet 36 assure le verrouillage du levier de blocage 35 dans une position qui correspond à la position I du levier d'actionnement 31. Furthermore, the mechanism 10 comprises a main shaft 30 which in particular carries an actuating lever 31 of a lever (not shown) of the switching device, a coupling lever 32 of this shaft to a trigger spring 33, a roller-carrying lever 34 which carries a cam follower roller 34a which cooperates with the cam 14, a locking lever 35 which cooperates with a pawl 36 actuated by an electromagnet 37 and a braking lever which is coupled to a brake 38 constituted for example by an oil jack or the like. The trigger spring 33 is preferably identical or similar to the engagement spring 15 and is connected by means of a chain 39 guided by an angle deflection pulley 40 to the coupling lever 32. The cam follower roller 34a is resting against the cam 14 mounted on the engagement shaft 11. This cam controls the movement of the lever 34 between two positions 41a and 41b which correspond respectively to the positions I and O of the actuating lever 31. The pawl 36 ensures the locking of the locking lever 35 in a position which corresponds to position I of the actuating lever 31.

    La figure 2 représente, à échelle agrandie une partie de la grande roue dentée 13 et le pignon denté 19. On notera que les dents du pignon 19 présentent une géométrie particulière qui correspond à une taille en pointe. Les flancs de ces dents se joignent radialement vers l'extérieur sur une arête commune et présentent, sur le flanc d'attaque, une forme en développante et sur le flanc opposé, un plan partant de l'arête et qui est incliné par rapport à une droite radiale passant par le milieu de la dent correspondante.Figure 2 shows, on an enlarged scale, part of the Ferris wheel toothed 13 and the toothed pinion 19. It will be noted that the teeth of the pinion 19 have a particular geometry which corresponds to a point size. The flanks of these teeth join radially outward on an edge common and present, on the flank of attack, a developing and on the opposite flank, a plane starting from the edge and which is inclined with respect to a radial straight line passing through the middle of the corresponding tooth.

    La grande roue dentée 13 comporte, dans le sens prédéterminé A de rotation une discontinuité de la denture 51, cette discontinuité engendrant un dégagement 52 qui constitue une zone sans dents. Une dent rétractable 53 est disposée dans ce dégagement. Elle est solidaire d'une douille 54 partiellement évidée qui est logée dans un évidement 55 sensiblement cylindrique, ménagé dans l'épaisseur de la grande roue dentée. Un ressort de compression 56 est monté dans l'espace fermé délimité entre la cavité de la douille évidée 54 et l'évidement 55 de la roue, ce ressort ayant tendance à repousser la dent 53 radialement vers l'extérieur de la roue. Pour empêcher la sortie de cette dent et pour limiter sa course vers l'extérieur, une plaque d'arrêt 57 est fixée au fond du dégagement 52 de manière à obturer partiellement l'évidement 55. Cette plaque d'arrêt est fixée au moyen d'au moins une et de préférence deux vis de blocage 58. Grâce à cet assemblage, la dent 53 peut s'escamoter en partie à l'intérieur de l'évidement 55, à l'encontre de la contrainte qu'exerce le ressort de compression 56.The large toothed wheel 13 comprises, in the predetermined direction A of rotation a discontinuity in the toothing 51, this discontinuity generating a clearance 52 which constitutes an area without teeth. A retractable tooth 53 is arranged in this clearance. It is attached to a socket 54 partially recessed which is housed in a recess 55 substantially cylindrical, arranged in the thickness of the large gear wheel. A spring of compression 56 is mounted in the closed space delimited between the cavity of the recessed bush 54 and recess 55 of the wheel, this spring tending to push the tooth 53 radially outward from the wheel. To prevent the exit of this tooth and to limit its outward travel, a plate stop 57 is fixed to the bottom of the clearance 52 so as to close off partially the recess 55. This stop plate is fixed by means of minus one and preferably two locking screws 58. Thanks to this assembly, the tooth 53 can partially retract inside the recess 55, at against the stress exerted by the compression spring 56.

    A la suite de cette dent rétractable 53, la grande roue 13 présente un dégagement complémentaire 60 qui est engendré par une discontinuité complémentaire de la denture 51 de cette roue. Ce dégagement s'étend sur au moins deux pas d'engrenage. Selon une forme de réalisation préférée, ce dégagement s'étend sur trois pas d'engrenage.Following this retractable tooth 53, the large wheel 13 has a additional clearance 60 which is generated by a discontinuity complementary to the toothing 51 of this wheel. This clearance extends over at least two gear steps. According to a preferred embodiment, this clearance extends over three gear steps.

    La dent 61 de la denture de la grande roue dentée, qui suit ledit dégagement complémentaire 60 présente une forme similaire à celle de la dent rétractable 53. Pour ces deux dents, au moins, les flancs se joignent radialement vers l'extérieur sur une arête commune. Le flanc opposé au flanc d'attaque présente un plan incliné dans sa partie supérieure adjacente à l'arête de la dent. En outre, la dent rétractable 53 est proéminente par rapport aux autres dents 51 de la denture de la grande roue dentée, ce qui a pour avantage de réduire la probabilité que sa pointe rentre en contact avec la pointe d'une dent du pignon 19.The tooth 61 of the toothing of the large gear wheel, which follows said clearance complementary 60 has a shape similar to that of the retractable tooth 53. For these two teeth, at least, the flanks join radially towards outside on a common ridge. The opposite flank to the attack flank has an inclined plane in its upper part adjacent to the edge of the tooth. In addition, the retractable tooth 53 is prominent over the others teeth 51 of the teeth of the large gear wheel, which has the advantage of reduce the likelihood that its tip will come into contact with the tip of a pinion tooth 19.

    Les figures 3A à 3D illustrent ce qui se passe lorsque la pointe d'une dent 50 du pignon 19 rencontre la pointe de la dent rétractable 53 de la grande roue dentée 13. L'instant initial de ce contact entre les deux dents 50 et 53 est représenté par la figure 3A.Figures 3A to 3D illustrate what happens when the tip of a tooth 50 pinion 19 meets tip of retractable tooth 53 of ferris wheel toothed 13. The initial instant of this contact between the two teeth 50 and 53 is shown in Figure 3A.

    La dent rétractable 53 s'escamote comme le montre la figure 38. Deux dents 53a et 53 b sont représentées en pointillés. En fait elles ont été supprimées et remplacées par ledit dégagement complémentaire 60. On constate que si ces deux dents avaient été maintenues, le risque que la dent suivante 50a du pignon 19 vienne en contact et bloque la dent 53a serait très élevé. C'est la raison pour laquelle le dégagement complémentaire a été prévu et qu'au moins deux dents 53a et 53b ont été supprimées. Ce dégagement complémentaire supprime totalement le risque de blocage de la grande roue dentée.The retractable tooth 53 retracts as shown in FIG. 38. Two teeth 53a and 53b are shown in dotted lines. In fact they have been deleted and replaced by said additional clearance 60. It can be seen that if these two teeth had been retained, the risk that the next tooth 50a of the pinion 19 comes into contact and blocks tooth 53a would be very high. It's here reason why additional clearance was planned and that at least two teeth 53a and 53b have been removed. This release complementary completely eliminates the risk of blocking the big wheel toothed.

    La figure 3C montre comment se comportent les dents des deux roues dentées. Les dents 50a et 50b qui suivent la dent 50 du pignon 19 se situent dans la zone du dégagement complémentaire 60 pendant tout le déplacement conjoint des dents 50 et 53.Figure 3C shows how the teeth of two wheels behave toothed. The teeth 50a and 50b which follow the tooth 50 of the pinion 19 are located in the area of the additional clearance 60 during the entire movement joint of teeth 50 and 53.

    La figure 3D montre la position de la dent 50c qui entre en contact avec la dent 61 qui est la première dent qui suit le dégagement complémentaire 60 de la grande roue dentée 13. On constate que les deux dents 50c, 61 ne peuvent pas se bloquer mutuellement en raison de leur forme spécifique.Figure 3D shows the position of tooth 50c which comes into contact with the tooth 61 which is the first tooth following complementary clearance 60 of the large toothed wheel 13. It can be seen that the two teeth 50c, 61 do not cannot block each other due to their specific shape.

    Claims (5)

    1. A spring drive mechanism (10) for power switchgear, in particular a power switch for medium and high voltage, in particular a circuit breaker, said mechanism comprising:
      an engagement spring (15) eccentrically coupled to an engagement shaft (11) that is free to rotate about its axis, said spring being organized to put the switchgear into circuit by driving, in a predetermined direction of rotation (A), both the engagement shaft and a large toothed wheel (13) mounted on the engagement shaft (11) together with a small toothed wheel (19) which meshes with said large toothed wheel and which is coupled to a drive member (23) for putting the engagement spring under stress so that it can put the switchgear into circuit, said drive member operating by driving said engagement shaft and said large toothed wheel via said small toothed wheel in said predetermined direction, said engagement shaft being organized to pass from a position (16b) in which the engagement spring is at least partially relaxed to beyond a dead-center position (16a) in which the engagement spring is under stress;
      a pawl mechanism (24) organized to bear against the large toothed wheel (13) in a bearing position situated beyond the dead-center position in said predetermined direction (A) and to release said engagement shaft (11) to put the switchgear into circuit;
      a gap (52) formed in the periphery of said large toothed wheel and generated by a discontinuity in the teeth (51) of said large toothed wheel, said gap being provided in a zone of the teeth which is situated close to said small toothed wheel (19) when said engagement shaft is bearing against the pawl mechanism; and
      means for preventing mutual jamming between the large toothed wheel (13) and the small toothed wheel (19) after the engagement shaft has been released by the pawl mechanism, said means comprising:
      a shape for the teeth (50) of said small toothed wheel having flanks that meet radially outwards on a common edge and presenting, on the leading flank, an involute shape and on the opposite flank, a flank plane extending from the edge and sloping relative to a radial straight line passing through the middle of the tooth; and
      a shape for the tooth (53) of the large toothed wheel (13) that follows the gap in said predetermined direction, its flanks meeting radially outwards at a common edge and including a sloping plane in its top zone adjacent to the edge;
         the mechanism being characterized in that said gap (52) formed in the periphery of said large toothed wheel (13) is followed, in said predetermined direction, by a tooth (53) that is radially retractable against the stress of a compression spring (56), and in that said retractable tooth is followed in said predetermined direction (A) by an additional gap (60) formed at the periphery of said large toothed wheel (13), and generated by an additional discontinuity in its teeth, said additional gap extending over at least two meshing steps.
    2. A mechanism according to claim 1, characterized in that the first tooth (61) of the teeth of said large toothed wheel (13) following the additional gap (60) has a shape similar to the shape of the retractable tooth (53).
    3. A mechanism according to claim 1, characterized in that said additional gap (60) extends over three meshing steps.
    4. A mechanism according to claim 1, characterized in that said retractable tooth (53), when in the non-retracted state, stands proud relative to the other teeth (51) of the large toothed wheel (13).
    5. A mechanism according to claim 2, characterized in that at least one additional tooth beyond said first tooth (61) following the additional gap (60) of said large toothed wheel (13) is of a shape similar to that of the retractable tooth (53).
    EP98401186A 1997-05-26 1998-05-18 Spring motor driving mechanism for a switching device, in particular for a circuit breaker Expired - Lifetime EP0881652B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    FR9706371A FR2763740B1 (en) 1997-05-26 1997-05-26 SPRING DRIVE MECHANISM FOR A SWITCHING APPARATUS, IN PARTICULAR A CIRCUIT BREAKER
    FR9706371 1997-05-26

    Publications (2)

    Publication Number Publication Date
    EP0881652A1 EP0881652A1 (en) 1998-12-02
    EP0881652B1 true EP0881652B1 (en) 2001-11-28

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    EP98401186A Expired - Lifetime EP0881652B1 (en) 1997-05-26 1998-05-18 Spring motor driving mechanism for a switching device, in particular for a circuit breaker

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    US (1) US5981889A (en)
    EP (1) EP0881652B1 (en)
    CN (1) CN1159740C (en)
    AT (1) ATE209824T1 (en)
    CA (1) CA2238965C (en)
    DE (1) DE69802617T2 (en)
    FR (1) FR2763740B1 (en)

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    FR2821696B1 (en) * 2001-03-01 2003-04-25 Alstom HIGH VOLTAGE CIRCUIT BREAKER HAVING A SPRING DRIVE WITH AN ADDITIONAL ENERGY RECOVERY SPRING
    FR2840726B1 (en) * 2002-06-06 2004-11-12 Alstom MECHANICAL SPRING CONTROL FOR HIGH OR MEDIUM VOLTAGE CIRCUIT BREAKER, INCLUDING A GEAR COOPERATING WITH A PINION
    JP3861832B2 (en) * 2003-03-11 2006-12-27 株式会社日立製作所 Switch
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    CA2238965C (en) 2004-07-20
    CN1159740C (en) 2004-07-28
    DE69802617D1 (en) 2002-01-10
    CN1200550A (en) 1998-12-02
    EP0881652A1 (en) 1998-12-02
    FR2763740A1 (en) 1998-11-27
    ATE209824T1 (en) 2001-12-15
    CA2238965A1 (en) 1998-11-26
    DE69802617T2 (en) 2002-08-01
    FR2763740B1 (en) 1999-07-16
    US5981889A (en) 1999-11-09

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