EP0917168B1 - 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
EP0917168B1
EP0917168B1 EP98402807A EP98402807A EP0917168B1 EP 0917168 B1 EP0917168 B1 EP 0917168B1 EP 98402807 A EP98402807 A EP 98402807A EP 98402807 A EP98402807 A EP 98402807A EP 0917168 B1 EP0917168 B1 EP 0917168B1
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EP
European Patent Office
Prior art keywords
wheel
tooth
retractable
gap
teeth
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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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EP98402807A
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German (de)
French (fr)
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EP0917168A1 (en
Inventor
Rolf Niklaus
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General Electric Switzerland GmbH
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GEC Alsthom AG
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Publication of EP0917168A1 publication Critical patent/EP0917168A1/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
    • H01H3/3005—Charging means
    • 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

Definitions

  • a shape of the teeth of said toothed pinion whose flanks join, radially outward, on a common edge and have, on the leading flank, an involute shape and, on the opposite flank, a flank 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.
  • 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 the 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 beyond 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 carry out, little expensive and which can also be adapted by a transformation appropriate, to mechanisms of this type that are already in use.
  • This goal is achieved by the mechanism as defined in the preamble and characterized in that said first clearance provided at the periphery of said large the toothed wheel is followed, in said predetermined direction of rotation, by a first radially retractable tooth against the constraint of a spring of compression, in that said first retractable tooth is followed, in said predetermined direction of rotation, from a second clearance provided at the periphery of this large gear wheel, generated by a discontinuity complementary to the teeth, this second clearance extending over at minus two gear steps, and in that the tooth that immediately follows said second clearance is a second radially retractable tooth against the stress of a compression spring.
  • said second clearance extends over a length slightly less than an integer number of gear steps and said second retractable tooth has flanks which join radially towards the exterior, on a common edge, and which have an inclined plane in its upper zone adjacent to the edge.
  • said second clearance extends over a length approximately 116 less than a gear step to an integer gear pitch and preferably over an approximate length equal to 2 (5/6) of gear pitch.
  • said second tooth retractable is followed, in said predetermined direction of rotation, by a third clearance which extends over at least two gear pitches.
  • said third clearance is followed by a tooth whose the flanks join radially outward, on a common edge, and which has an inclined plane in its upper zone adjacent to the edge.
  • said first clearance is followed, in the predetermined direction of rotation, of n teeth retractable axially against the spring stress, each of these retractable teeth being followed, in said predetermined direction of rotation, by a clearance extending over at least two gear steps.
  • said retractable teeth and the first non-retractable tooth following the last retractable tooth, in the predetermined direction of rotation have flanks which join radially towards the exterior, on a common edge, and which have an inclined plane in their upper zone adjacent to the edge.
  • Said retractable teeth are advantageously separated from the two teeth neighboring retractable by a clearance extending over a length slightly less than a whole number of gear steps.
  • 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 a drive pinion 21 integral 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 standby position slightly downstream from neutral 16a (in the predetermined direction of rotation A of the large toothed wheel), at 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 of rotation A. This movement is continues until the point where the interlocking spring is attached again slightly exceeds the neutral point 16a and where this spring is armed.
  • a ratchet mechanism 24 which comprises a ratchet 25 actuated by an electromagnet 26 and a stop 27 mounted on one of the faces of the large wheel tooth 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 carrier 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 angular 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 41 a and 41 b which correspond respectively to the positions l and O of the actuating lever 31.
  • the pawl 36 ensures the locking lever 35 is locked in a position which corresponds to position l 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 50 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 form 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 corresponding tooth.
  • the large toothed wheel 13 comprises, in the predetermined direction of rotation A, a discontinuity in the toothing 51, this discontinuity generating a first clearance 52a which constitutes an area without teeth.
  • a first tooth retractable 53a is arranged in this clearance. It is integral with a partially hollowed socket 54a which is housed in a recess 55a substantially cylindrical, formed in the thickness of the large gear.
  • a compression spring 56a is mounted in the closed space delimited between the cavity of the hollowed-out sleeve 54a and the recess 55a of the wheel, this spring having tendency to push tooth 53a radially to the outside of the wheel.
  • a stop plate 57a is fixed to the bottom of the first clearance 52a so partially closing the recess 55a.
  • This stop plate is fixed to the by means of at least one and preferably two locking screws 58a. Thanks to this assembly, the tooth 53a can partially retract inside of recess 55a, contrary to the constraint exerted by the spring of compression 56a.
  • the large wheel 13 has a second clearance 52b which is generated by a discontinuity complementary to the toothing 51 of this wheel.
  • This second release extends over at least two gear pitches. According to one embodiment preferred, this clearance extends over a length slightly less than one whole number of gear steps and advantageously on a whole number, for example three gear steps reduced by 1/6 gear step.
  • the tooth 53b of the toothing of the large toothed wheel, which follows said second clearance 52b, is also retractable under the constraint of a spring compression 56b.
  • the tooth 60 which follows the second retractable tooth 53b, after a third clearance 52c which extends over a length equal to a number whole gear pitch, includes, as well as each of the teeth retractable, sides which join radially outwards on a common edge.
  • the flank opposite the leading flank has an inclined plane in its upper part adjacent to the edge of the tooth.
  • the two retractable teeth 53a and 53b can be prominent compared to the other teeth 51 of the teeth of the large gear wheel, this which has the advantage of reducing the probability that the tip of said others teeth comes into contact with the tip of a pinion tooth 19.
  • Figures 3A to 3H illustrate what happens in the absence of a collision between the teeth 50 of the pinion 19 and the teeth of the large gear wheel 13.
  • the instant initial is represented by figures 3A and 3B, this last figure representing the coming into contact of a tooth of the pinion 19 and the first retractable tooth 53a of the large gear wheel 13.
  • Figures 3C and 3D show the relative position of the sprocket teeth relative to the teeth 51 missing, shown in broken lines, of the large gear wheel 13.
  • FIG. 3E illustrates in broken lines the primitive shape of a tooth 61 pinion 19 not cut appropriately. We see in this figure that if this shape were maintained, it would automatically cause a collision with the second retractable tooth 53b of the large toothed wheel.
  • the following figures 3F, 3G and 3H illustrate the relative positions of the teeth 50 of the pinion 19 and 53a, 53b and 60 of the large gear 13.
  • Figures 4A to 4H illustrate what happens when the tip of a tooth 50 pinion 19 meets the tip of the retractable tooth 53a of the ferris wheel toothed 13.
  • the initial instant of this contact between the two teeth 50 and 53a is shown in Figure 4B.
  • Point-to-point contact causes tooth retraction 53a.
  • Figures 4C and 4D illustrate the teeth of the pinion and those of the big gear have relative positions which are illustrated by Figures 4C and 4D.
  • Figure 4E illustrates the contact between a teeth 50 of the pinion 19 with the second retractable tooth 53b.
  • the number of retractable teeth is not limited to two and may extend to three or n axially retractable teeth against the constraint of a thrust spring, each of these teeth being followed by a clearance as defined above.

Landscapes

  • Transmission Devices (AREA)
  • Gears, Cams (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Gear Transmission (AREA)
  • Lock And Its Accessories (AREA)
  • Push-Button Switches (AREA)
  • Mechanisms For Operating Contacts (AREA)

Abstract

The gearing release area has a protruding stop section and two spaced gear teeth which can retract into the gear body if misengagement occurs.

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 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 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 premier dégagement ménagé à la périphérie de ladite grande roue dentée et générée par une discontinuité dans la denture de cette grande roue dentée, ce premier 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, et
  • 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:
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 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 switching on 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 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 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 switching on said switching device,
  • a first clearance formed at the periphery of said large toothed wheel and generated by a discontinuity in the teeth of this large toothed wheel, this first relief being provided in an area of the teeth which is located near said toothed pinion when the shaft engagement is in abutment against the ratchet mechanism, and
  • 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:

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 de flanc 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.a shape of the teeth of said toothed pinion whose flanks join, radially outward, on a common edge and have, on the leading flank, an involute shape and, on the opposite flank, a flank 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 publiée sous le 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.The European patent application published under No. 0 651 409 A1 describes a mechanism of this type. In this realization all the teeth of the pinion toothed as well as the first tooth which follows, in the predetermined direction, the clearance caused by the discontinuity of the teeth of the ferris wheel toothed, are configured so that their sides converge towards a single and same edge. The purpose of this measure is to prevent a blockage of cogwheels. However, it turned out that the friction of an edge of the pinion toothed on the leading flank of the first tooth following the release of the large gear wheel, more or less power losses important due to friction. These losses, which depend on the position of the toothed pinion, result in variations in the time required for switch on the switchgear as well as significant wear of the first tooth following the release of the large gear. If the mechanism is used to control a switch intended to be engaged to reduce network overvoltages, synchronously with the voltage of this network, such variations appearing randomly 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 the 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 beyond 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, 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 carry out, 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 premier dégagement ménagé à la périphérie de ladite grande roue dentée est suivi, dans ledit sens prédéterminé de rotation, d'une première dent rétractable radialement contre la contrainte d'un ressort de compression, en ce que ladite première dent rétractable est suivie, dans ledit sens prédéterminé de rotation, d'un deuxième dégagement ménagé à la périphérie de cette grande roue dentée, généré par une discontinuité complémentaire de la denture, ce deuxième dégagement s'étendant sur au moins deux pas d'engrenage, et en ce que la dent qui suit immédiatement ledit deuxième dégagement est une deuxième dent rétractable radialement contre la contrainte d'un ressort de compression.This goal is achieved by the mechanism as defined in the preamble and characterized in that said first clearance provided at the periphery of said large the toothed wheel is followed, in said predetermined direction of rotation, by a first radially retractable tooth against the constraint of a spring of compression, in that said first retractable tooth is followed, in said predetermined direction of rotation, from a second clearance provided at the periphery of this large gear wheel, generated by a discontinuity complementary to the teeth, this second clearance extending over at minus two gear steps, and in that the tooth that immediately follows said second clearance is a second radially retractable tooth against the stress of a compression spring.

Selon un mode de réalisation préféré, ledit deuxième dégagement s'étend sur une longueur légèrement inférieure à un nombre entier de pas d'engrenage et ladite deuxième dent rétractable a des flancs qui se joignent radialement vers l'extérieur, sur une arête commune, et qui comportent un plan incliné dans sa zone supérieure adjacente à l'arête.According to a preferred embodiment, said second clearance extends over a length slightly less than an integer number of gear steps and said second retractable tooth has flanks which join radially towards the exterior, on a common edge, and which have an inclined plane in its upper zone adjacent to the edge.

De façon avantageuse, ledit deuxième dégagement s'étend sur une longueur inférieure d'approximativement 116 d'un pas d'engrenage à un nombre entier de pas d'engrenage et de préférence sur une longueur approximativement égale à 2 (5/6) de pas d'engrenage. Advantageously, said second clearance extends over a length approximately 116 less than a gear step to an integer gear pitch and preferably over an approximate length equal to 2 (5/6) of gear pitch.

D'une manière particulièrement avantageuse, ladite deuxième dent rétractable est suivie, dans ledit sens prédéterminé de rotation, d'un troisième dégagement qui s'étend sur au moins deux pas d'engrenage.In a particularly advantageous manner, said second tooth retractable is followed, in said predetermined direction of rotation, by a third clearance which extends over at least two gear pitches.

De façon préférentielle, ledit troisième dégagement est suivi d'une dent 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.Preferably, said third clearance is followed by a tooth whose the flanks join radially outward, on a common edge, and which has an inclined plane in its upper zone adjacent to the edge.

D'une manière plus générale, ledit premier dégagement est suivi, dans le sens prédéterminé de rotation, de n dents rétractables axialement contre la contrainte d'un ressort, chacune de ces dents rétractables étant suivie, dans ledit sens prédéterminé de rotation, d'un dégagement s'étendant sur au moins deux pas d'engrenage.More generally, said first clearance is followed, in the predetermined direction of rotation, of n teeth retractable axially against the spring stress, each of these retractable teeth being followed, in said predetermined direction of rotation, by a clearance extending over at least two gear steps.

Dans toutes les formes de réalisation, lesdites dents rétractables et la première dent non rétractable suivant la dernière dent rétractable, dans le sens prédéterminé de rotation, ont des flancs qui se joignent radialement vers l'extérieur, sur une arête commune, et qui comportent un plan incliné dans leur zone supérieure adjacente à l'arête.In all embodiments, said retractable teeth and the first non-retractable tooth following the last retractable tooth, in the predetermined direction of rotation, have flanks which join radially towards the exterior, on a common edge, and which have an inclined plane in their upper zone adjacent to the edge.

Lesdites dents rétractables sont avantageusement séparées des deux dents rétractables voisines par un dégagement s'étendant sur une longueur légèrement inférieure à un nombre entier de pas d'engrenage.Said retractable teeth are advantageously separated from the two teeth neighboring retractable by a clearance extending over a length slightly less than a whole number of gear steps.

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'exemples 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 les dents rétractables de la grande roue dentée,
  • Les figures 3A, 3B, 3C, 3D, 3E, 3F, 3G et 3H illustrent la cinématique de la grande roue dentée et du pignon denté dans la zone où les dents rétractables engrènent les dents du pignon, dans le cas où les dents du pignon et celles de la grande roue dentée n'entrent pas en collision, et
  • Les figures 4A, 4B, 4C, 4D, 4E, 4F, 4G et 4H illustrent la cinématique de la grande roue dentée et du pignon denté dans la zone où les dents rétractables engrènent les dents du pignon, dans le cas où les dents du pignon et celles de la grande roue dentée entrent en collision.
    • 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 examples, 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 teeth of the large gear wheel,
  • Figures 3A, 3B, 3C, 3D, 3E, 3F, 3G and 3H illustrate the kinematics of the large gear wheel and the toothed pinion in the area where the retractable teeth mesh the teeth of the pinion, in the case where the teeth of the pinion and those of the big gear do not collide, and
  • FIGS. 4A, 4B, 4C, 4D, 4E, 4F, 4G and 4H illustrate the kinematics of the large toothed wheel and of the toothed pinion in the area where the retractable teeth mesh the teeth of the pinion, in the case where the teeth of the pinion and those of the big cog collide.

    • 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 a drive pinion 21 integral 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 publiée sous le No 0 652 409 citée en préambule, est destiné, pour ce qui est du ressort d'enclenchement 15, à 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, à 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 du point mort 16a (dans le sens prédéterminé de rotation A de la grande roue dentée), 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 de rotation 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 électro-aimant 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 published under No. 0 652 409 cited in preamble, is intended, as regards the interlocking spring 15, to drive the engagement shaft 11 in a predetermined direction of rotation A (see arrow A in Figure 1) in order to ensure that the the switching device (not shown) and, with regard to the motor 23, to put under stress the engagement spring 15 so that he is armed and ready to release his accumulated energy to ensure everything switch on 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 standby position slightly downstream from neutral 16a (in the predetermined direction of rotation A of the large toothed wheel), at 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 of rotation A. This movement is continues until the point where the interlocking spring is attached again slightly exceeds the neutral point 16a and where this spring is armed. The stop of the large gear wheel in this position is obtained by a ratchet mechanism 24 which comprises a ratchet 25 actuated by an electromagnet 26 and a stop 27 mounted on one of the faces of the large wheel tooth 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 électro-aimant 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 41 a et 41 b qui correspondent respectivement aux positions l 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 l 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 carrier 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 angular 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 41 a and 41 b which correspond respectively to the positions l and O of the actuating lever 31. The pawl 36 ensures the locking lever 35 is locked in a position which corresponds to position l of the actuating lever 31.

    La figure 2 représente, à une échelle agrandie, une partie de la grande roue dentée 13 et le pignon denté 19. On notera que les dents 50 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 50 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 form 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 corresponding tooth.

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

    A la suite de cette première dent rétractable 53a, la grande roue 13 présente un deuxième dégagement 52b qui est engendré par une discontinuité complémentaire de la denture 51 de cette roue. Ce deuxième dégagement s'étend sur au moins deux pas d'engrenage. Selon une forme de réalisation préférée, ce dégagement s'étend sur une longueur légèrement inférieure à un nombre entier de pas d'engrenage et avantageusement sur un nombre entier, par exemple trois pas d'engrenage diminués de 1/6 de pas d'engrenage.Following this first retractable tooth 53a, the large wheel 13 has a second clearance 52b which is generated by a discontinuity complementary to the toothing 51 of this wheel. This second release extends over at least two gear pitches. According to one embodiment preferred, this clearance extends over a length slightly less than one whole number of gear steps and advantageously on a whole number, for example three gear steps reduced by 1/6 gear step.

    La dent 53b de la denture de la grande roue dentée, qui suit ledit deuxième dégagement 52b, est également rétractable sous la contrainte d'un ressort de compression 56b. La dent 60 qui suit la deuxième dent rétractable 53b, après un troisième dégagement 52c qui s'étend sur une longueur égale à un nombre entier de pas d'engrenage, comporte, ainsi que chacune des dents rétractables, des flancs qui 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. D'une manière générale, les deux dents rétractables 53a et 53b peuvent être proéminentes par rapport aux autres dents 51 de la denture de la grande roue dentée, ce qui a pour avantage de réduire la probabilité que la pointe desdites autres dents entre en contact avec la pointe d'une dent du pignon 19.The tooth 53b of the toothing of the large toothed wheel, which follows said second clearance 52b, is also retractable under the constraint of a spring compression 56b. The tooth 60 which follows the second retractable tooth 53b, after a third clearance 52c which extends over a length equal to a number whole gear pitch, includes, as well as each of the teeth retractable, sides which join radially outwards on a common edge. The flank opposite the leading flank has an inclined plane in its upper part adjacent to the edge of the tooth. In a way general, the two retractable teeth 53a and 53b can be prominent compared to the other teeth 51 of the teeth of the large gear wheel, this which has the advantage of reducing the probability that the tip of said others teeth comes into contact with the tip of a pinion tooth 19.

    Les figures 3A à 3H illustrent ce qui se passe en l'absence de collision entre les dents 50 du pignon 19 et les dents de la grande roue dentée 13. L'instant initial est représenté par les figures 3A et 3B, cette dernière figure représentant l'entrée en contact d'une dent du pignon 19 et de la première dent rétractable 53a de la grande roue dentée 13. Les figures 3C et 3D montrent la position relative des dents du pignon par rapport aux dents 51 manquantes, représentées en traits interrompus, de la grande roue dentée 13. La figure 3E illustre en traits interrompus la forme primitive d'une dent 61 du pignon 19 non taillée de façon appropriée. On constate sur cette figure que si cette forme était maintenue, elle entraínerait automatiquement une collision avec la deuxième dent escamotable 53b de la grande roue dentée. Les figures suivantes 3F, 3G et 3H illustrent les positions relatives des dents 50 du pignon 19 et 53a, 53b et 60 de la grande roue dentée 13.Figures 3A to 3H illustrate what happens in the absence of a collision between the teeth 50 of the pinion 19 and the teeth of the large gear wheel 13. The instant initial is represented by figures 3A and 3B, this last figure representing the coming into contact of a tooth of the pinion 19 and the first retractable tooth 53a of the large gear wheel 13. Figures 3C and 3D show the relative position of the sprocket teeth relative to the teeth 51 missing, shown in broken lines, of the large gear wheel 13. FIG. 3E illustrates in broken lines the primitive shape of a tooth 61 pinion 19 not cut appropriately. We see in this figure that if this shape were maintained, it would automatically cause a collision with the second retractable tooth 53b of the large toothed wheel. The following figures 3F, 3G and 3H illustrate the relative positions of the teeth 50 of the pinion 19 and 53a, 53b and 60 of the large gear 13.

    Les figures 4A à 4H illustrent ce qui se passe lorsque la pointe d'une dent 50 du pignon 19 rencontre la pointe de la dent rétractable 53a de la grande roue dentée 13. L'instant initial de ce contact entre les deux dents 50 et 53a est représenté par la figure 4B. Le contact pointe sur pointe provoque la rétraction de la dent 53a. Au cours de la suite du mouvement, les dents du pignon et celles de la grande roue dentée ont des positions relatives qui sont illustrées par les figures 4C et 4D. La figure 4E illustre le contact entre une des dents 50 du pignon 19 avec la deuxième dent rétractable 53b. Cette dent se rétracte comme le montre la figure 4F, puis l'engrenage des deux roues dentées se fait normalement comme le montrent les figures 4G et 4H grâce aux dégagements 52a, 52b et 52c prévus entre les dents rétractables 53a, 53b et à la suite de la deuxième de ces dents.Figures 4A to 4H illustrate what happens when the tip of a tooth 50 pinion 19 meets the tip of the retractable tooth 53a of the ferris wheel toothed 13. The initial instant of this contact between the two teeth 50 and 53a is shown in Figure 4B. Point-to-point contact causes tooth retraction 53a. During the rest of the movement, the teeth of the pinion and those of the big gear have relative positions which are illustrated by Figures 4C and 4D. Figure 4E illustrates the contact between a teeth 50 of the pinion 19 with the second retractable tooth 53b. This tooth retracts as shown in Figure 4F, then the gear of the two wheels toothed is normally done as shown in Figures 4G and 4H thanks the clearances 52a, 52b and 52c provided between the retractable teeth 53a, 53b and following the second of these teeth.

    L'invention ne se limite pas aux formes de réalisation représentées qui ne constituent que des exemples de construction. En particulier le nombre de dents rétractables n'est pas limité à deux et peut s'étendre à trois ou n dents rétractables axialement à l'encontre de la contrainte d'un ressort de poussée, chacune de ces dents étant suivie d'un dégagement tel que défini précédemment.The invention is not limited to the embodiments shown which are only examples of construction. In particular, the number of retractable teeth is not limited to two and may extend to three or n axially retractable teeth against the constraint of a thrust spring, each of these teeth being followed by a clearance as defined above.

    Claims (9)

    1. A spring drive mechanism (10) for power switchgear, in particular a power switch for medium or high voltage and in particular a circuit breaker, the 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 entrain firstly the engagement shaft in a predetermined direction of rotation (A) to put the switchgear into circuit, and secondly a large toothed-wheel (13) mounted on the engagement shaft (11) and a small toothed-wheel (19) which meshes with said large toothed-wheel and which is coupled to a drive member (23) for driving, by means of said small toothed-wheel, said large toothed-wheel and said engagement shaft in said predetermined direction to stress the engagement spring for the purpose of putting the switchgear into circuit, said engagement shaft being organized to pass from a position (16b) in which the engagement spring is relaxed, at least in part, 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 the predetermined direction of rotation (A) and to release said engagement shaft (11) to put said switchgear into circuit;
      a first gap (52a) 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 the engagement shaft is bearing against the pawl mechanism; and
      means for preventing the large toothed-wheel (13) and the small toothed-wheel (19) from mutually jamming each other 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 (19) in which the flanks of a tooth meet radially outwards at a common edge and present, on the leading flank, an involute shape, and on the opposite flank, a flank plane extending from the edge and inclined relative to a radial straight line passing through the middle of the tooth; and
      a shape for the tooth of the large toothed-wheel (13) that follows the gap in said predetermined direction, in which its flanks meet radially outwards at a common edge, and which include an inclined plane in the top zone adjacent to the edge;
      the mechanism being characterized in that said first gap (52a) formed in the periphery of said large toothed-wheel (13) is followed in said predetermined direction of rotation (A) by a first retractable tooth (53a) that is radially retractable against bias from a compression spring (56a), in that said first retractable tooth is followed in said predetermined direction of rotation (A) by a second gap (52b) formed in the periphery of said large toothed-wheel (13), generated by an additional discontinuity in its teeth, said second gap extending over at least two gear pitch steps, and in that the tooth immediately following said second gap (52b) is a second retractable tooth (53b) that is radially retractable against the bias of a compression spring (56b).
    2. A mechanism according to claim 1, characterized in that said second gap (52b) extends over a length that is slightly less than an integer number of gear pitch steps, and in that said second retractable tooth (53b) has flanks which meet radially outwards at a common edge and which include an inclined plane in its top zone adjacent to the edge.
    3. A mechanism according to claim 2, characterized in that said second gap extends over a length that is approximately one-sixth of a gear pitch step shorter than an integer number of gear pitch steps.
    4. A mechanism according to claim 3, characterized in that said second gap extends over a length that is approximately equal to 2 5 / 6 of a gear pitch step.
    5. A mechanism according to claim 3, characterized in that said second retractable tooth (53b) is followed in said predetermined direction of rotation (A) by a third gap (52c) which extends over at least two gear pitch steps.
    6. A mechanism according to claim 5, characterized in that said third gap (52c) is followed by a tooth (60) whose flanks meet radially outwards at a common edge, and which includes an inclined plane in its top zone adjacent to the edge.
    7. A mechanism according to claim 1, characterized in that said first gap (52a) is followed in the predetermined direction of rotation (A) by a plurality of retractable teeth that are retractable along the axis of the tooth against spring bias, each of the retractable teeth being followed in said predetermined direction of rotation (A) by a gap extending over at least two gear pitch steps.
    8. A mechanism according to claim 7, characterized in that each of said retractable teeth and the first non-retractable tooth following the last retractable tooth in the predetermined direction of rotation (A) has flanks which meet radially outwards at a common edge, and includes an inclined plane in its top zone adjacent to the edge.
    9. A mechanism according to claim 8, characterized in that each of said retractable teeth is spaced apart from each adjacent retractable tooth by a gap extending over a length that is slightly less than an integer number of gear pitch steps.
    EP98402807A 1997-11-13 1998-11-13 Spring motor driving mechanism for a switching device, in particular for a circuit breaker Expired - Lifetime EP0917168B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    FR9714223 1997-11-13
    FR9714223A FR2770929B1 (en) 1997-11-13 1997-11-13 SPRING DRIVE MECHANISM FOR A SWITCHING APPARATUS, IN PARTICULAR A CIRCUIT BREAKER

    Publications (2)

    Publication Number Publication Date
    EP0917168A1 EP0917168A1 (en) 1999-05-19
    EP0917168B1 true EP0917168B1 (en) 2004-10-06

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    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP98402807A Expired - Lifetime EP0917168B1 (en) 1997-11-13 1998-11-13 Spring motor driving mechanism for a switching device, in particular for a circuit breaker

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    US (1) US6066820A (en)
    EP (1) EP0917168B1 (en)
    JP (1) JP4143191B2 (en)
    CN (1) CN1096092C (en)
    AT (1) ATE279015T1 (en)
    CA (1) CA2251271A1 (en)
    DE (1) DE69826809T2 (en)
    FR (1) FR2770929B1 (en)
    RU (1) RU2156004C2 (en)

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    KR100325408B1 (en) * 1999-10-26 2002-03-04 이종수 Contact point closing/open apparatus for circuit breaker
    FR2819626B1 (en) * 2001-01-12 2003-02-21 Alstom HIGH-VOLTAGE DISCONNECTOR WITH AIR INSULATION
    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
    FR2846779B1 (en) * 2002-10-30 2005-01-28 Alstom CIRCUIT BREAKER COMPRISING A CONTROL ARRANGEMENT AND A CUTTING CHAMBER, ITS ASSEMBLY METHOD AND AUXILIARY ARM FOR THIS ASSEMBLY
    GB0502557D0 (en) * 2005-02-08 2005-03-16 Patel Hitesh D Gear means
    US7319203B1 (en) * 2007-01-10 2008-01-15 Eaton Corporation Circuit interrupter and operating mechanism therefor
    JP5951262B2 (en) * 2012-01-11 2016-07-13 株式会社東芝 Switchgear and switchgear operating mechanism
    CN102867663B (en) * 2012-09-24 2014-12-24 中国西电电气股份有限公司 Clutch device of gear transmission system of breaker spring operating mechanism
    CN102881474B (en) * 2012-10-15 2014-12-24 上海思源高压开关有限公司 Spring energy storage control module, operating mechanism and circuit breaker
    RU2676466C2 (en) * 2014-10-27 2018-12-29 Хамзат Исхакович Геграев Load break switch aggregate drive
    DE102016215888A1 (en) 2016-08-24 2018-03-01 Siemens Aktiengesellschaft Coupling device and method for coupling and decoupling a tensioning gear of a circuit breaker
    DE102017122008B4 (en) * 2017-09-22 2020-11-05 Lisa Dräxlmaier GmbH ELECTRIC SWITCH
    CN110459414A (en) * 2019-05-09 2019-11-15 厦门宏发汽车电子有限公司 A kind of the contact control mechanism and switch of active homing
    CN110486447A (en) * 2019-09-19 2019-11-22 广东电网有限责任公司 A kind of non-wholecircle driven gear

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    ATE80494T1 (en) * 1987-12-14 1992-09-15 Sprecher Energie Ag SPRING-LOAD MECHANISM FOR A HIGH-VOLTAGE SWITCH.
    DE59307350D1 (en) * 1993-11-03 1997-10-16 Gec Alsthom T & D Ag Spring drive for a switching device
    EP0658909B1 (en) * 1993-12-13 1996-10-23 GEC Alsthom T&D AG Drive mechanism for a power circuit breaker

    Also Published As

    Publication number Publication date
    CN1096092C (en) 2002-12-11
    ATE279015T1 (en) 2004-10-15
    US6066820A (en) 2000-05-23
    JPH11224573A (en) 1999-08-17
    FR2770929A1 (en) 1999-05-14
    CN1230758A (en) 1999-10-06
    RU2156004C2 (en) 2000-09-10
    EP0917168A1 (en) 1999-05-19
    DE69826809D1 (en) 2004-11-11
    FR2770929B1 (en) 2000-01-28
    DE69826809T2 (en) 2005-11-17
    JP4143191B2 (en) 2008-09-03
    CA2251271A1 (en) 1999-05-13

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