EP0586733B1 - Dispositif à action brusque pour interrupteurs électriques - Google Patents

Dispositif à action brusque pour interrupteurs électriques Download PDF

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Publication number
EP0586733B1
EP0586733B1 EP92115463A EP92115463A EP0586733B1 EP 0586733 B1 EP0586733 B1 EP 0586733B1 EP 92115463 A EP92115463 A EP 92115463A EP 92115463 A EP92115463 A EP 92115463A EP 0586733 B1 EP0586733 B1 EP 0586733B1
Authority
EP
European Patent Office
Prior art keywords
lever
spring
drive
output shaft
input shaft
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
Application number
EP92115463A
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German (de)
English (en)
Other versions
EP0586733A1 (fr
Inventor
Ernst Zürcher
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Switzerland GmbH
Original Assignee
GEC Alsthom T&D AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by GEC Alsthom T&D AG filed Critical GEC Alsthom T&D AG
Priority to AT92115463T priority Critical patent/ATE141712T1/de
Priority to DE59206960T priority patent/DE59206960D1/de
Priority to ES92115463T priority patent/ES2090439T3/es
Priority to EP92115463A priority patent/EP0586733B1/fr
Priority to JP25020393A priority patent/JP3401621B2/ja
Priority to US08/118,840 priority patent/US5444202A/en
Publication of EP0586733A1 publication Critical patent/EP0586733A1/fr
Application granted granted Critical
Publication of EP0586733B1 publication Critical patent/EP0586733B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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

Definitions

  • the present invention relates to a jump drive for quickly switching electrical switches on and off according to the preamble of claim 1.
  • a jump drive of this type is known from US-A-4,253,487.
  • This has an input shaft that can be rotated by hand between two end positions over a crank with a double-arm tensioning lever.
  • An output shaft with a double-armed drive lever which can be rotated back and forth between an off and an on position, runs parallel to the input shaft.
  • a compression spring of a spring-loaded arrangement is arranged, the compression springs canceling each other's prestress when the input and output shafts are parallel to one another.
  • the output shaft is held in the switch-off and switch-on position by a switch-on or switch-off pawl acting on the drive lever against the force of the compression spring that can be tensioned when the input shaft is rotated.
  • the clamping lever Shortly before the input shaft reaches the corresponding end position, the clamping lever runs onto the relevant pawl to release the drive lever and thus the output shaft. After the switching operation has ended, the drive lever again runs parallel to the tensioning lever. To perform an opposite switching operation, the input shaft is rotated in the opposite direction, whereby the other compression spring is now tensioned to actuate the output shaft.
  • a disadvantage of this spring drive is that it requires its own compression spring for switching on and switching off. Furthermore, the switch-off and switch-on positions of the output shaft cannot be reliably achieved by the force of the pressure springs, since the effect of the two pressure springs is canceled out in these positions.
  • a jump drive in which the input shaft and the output shaft are arranged coaxially to one another, is known from DE-AS 1 236 632.
  • the spring-loaded arrangement has two coaxial bends Coil springs, with only one spring acting in the switch-off direction, but both in the switch-on direction, so that different drive energies are available depending on the switch direction. If the output shaft does not move under the action of the spring-loaded arrangement after the locking position of the input shaft has been exceeded, a forced coupling is produced between these shafts. Another forced clutch ensures when switching on that the output shaft is brought fully into the on position.
  • This spring drive has a considerable depth in the direction of the waves.
  • the coil spring interacts with each of its spring ends via driver elements with the tensioning lever and the drive lever.
  • the helical spring is thus clamped both between the driver elements interacting with the tensioning lever and between the driver elements interacting with the drive lever. Since the coil spring is pretensioned according to the invention, the input and output shaft are coupled to one another at least under a force which corresponds to the pretension of the coil spring, regardless of their mutual position. So long the movement of the output shaft counteracts a force that is less than the biasing force of the coil spring, the two shafts are firmly coupled.
  • the output shaft is in any case pushed into the switch-on or switch-off position at least with the biasing force of the coil spring.
  • the coil spring can be subjected to pressure or tension. However, it acts when switched on and when switched off in the same direction, namely always as a compression spring or always as a tension spring under pre-tension.
  • the snap drive shown in the figures is provided for the rapid switching on and off of electrical switches 10 schematically indicated in FIG. 1, in particular load switches, disconnectors and earth switches for medium and high voltage. It has an input shaft 12 and an output shaft 14 spaced parallel to it. On the input shaft 12, a tension lever 16 sits in a rotationally fixed manner, which, from a first end position 18 indicated by solid lines in FIG. 1 and dash-dotted in FIG. 4, runs counterclockwise (by approximately an angle of 80 °) into a position shown in FIG. 1 dash-dotted and in Fig. 4 indicated by solid lines second end position 18 'and can be rotated back again.
  • the input shaft 12 is rotated by means of rotary means 20, which is indicated schematically in FIG. 1, for example by hand by means of a crank which can be plugged onto the input shaft 12 or electrically by means of a geared motor.
  • a drive lever 22 On the output shaft 14 connected to the switch 10, a drive lever 22 is seated in a rotationally fixed manner. It moves from a switch-off position 24 indicated by solid lines in FIG. 1 and in dash-dotted lines in FIG. 4 in a counterclockwise direction (also approximately at an angle of 80 °) into one 1 in dash-dot lines and in FIG. 4 switch-on position 24 'shown in solid lines and again is rotatable back.
  • a spring-loaded arrangement 26 interacts with the tensioning lever 16 and drive lever 22 and thus with the input shaft 12 and the output shaft 14, the coil spring 28 acting as a compression spring thereof being connected to the tensioning lever 16 and drive lever 22 via a link arrangement 30.
  • the tab arrangement 30 has a double tab 32 with two identical tabs 32 'and a single tab 34 arranged between the latter and displaceable relative thereto in the direction of the longitudinal extent.
  • the helical spring 28 encompasses the tab arrangement 30 and, with its spring end 36 facing the tensioning lever 16, is supported on the double tab 32 via a perforated disk 38 and a pin 40.
  • the pin 40 penetrates through the seat plate at right angles to the spring axis 28 'and thus at right angles to the longitudinal extension of the tab arrangement 30 and an elongated hole-like recess 42 of the individual tab 34 which extends in the longitudinal direction of the tab arrangement 30.
  • the spring end facing the drive lever 22 is supported in an analogous manner 36 'also via a perforated disk 38' and a pin 40 'on the individual tab 34.
  • the pin 40 ' passes through the tabs 32' of the double tab 32 through a slot-like recess 44, which extends in the longitudinal direction of the tab arrangement 30, and fits tightly over the single tab 34.
  • the tabs 32 ' have an elongated hole-like further recess 46 on their tension lever-side end region, this further recess 46 and the recess 42 of the individual plate 34 overlapping and in the region of the Overlap are penetrated by a driving pin 48 arranged on the tensioning mist 16.
  • Another driving pin 50 is arranged on the drive lever 22; the latter extends through the recess 44 of the double strap 32 outside the end 34 ′ of the single strap 34 on this side.
  • the tabs 32 'of the double tab 32 interact with the driving pin 48 via a first driving stop 52 and with the further driving pin 50 via a second driving stop 54.
  • the first driving stop 52 is formed by the end of the further recess 46 facing the spring end 36 and the second driving stop 54 is formed by the end of the recess 44 facing away from this.
  • the individual tab 34 cooperates with its end of the recess 42 facing away from the spring end 36 'with the driving pin 48 as the first driving stop 56 and with the end 34' with the further driving pin 50 as the second driving stop 58.
  • the tabs 32 'of the double tab 32 have at their end of the recess 44 facing the tensioning lever 16 a stop 60 and which cooperate with the pin 40' the individual tab 34 at its end of the recess 42 facing the drive lever 22 has a stop 62 which interacts with the driving pin 48.
  • the end of the further recess 46 of the double bracket 32 remote from the drive lever 22 interacts as a stop 64 with the driving pin 48 of the tensioning lever 16 in order to forcibly take the output shaft 14 with it when it is switched off.
  • a locking device 66 controlled by the input shaft 12 interacts with the output shaft 14 and is described in more detail below in connection with FIGS. 9 and 10.
  • This locking device 66 holds the output shaft 14 in its switch-off position 24 when it is switched on, until the input shaft 12 reaches a switch-in / unlocking position 68 when rotating from the first end position 18 in the direction toward the second end position 18 ', as in FIG Position driving pin 48 is indicated.
  • the stroke which the driving pin 48 travels from the first end position 18 to the switch-on-unlatching position 68 is indicated by the double arrow E in FIG. 3.
  • FIGS. 7 and 8 show the spring-loaded arrangement 26, with another possible embodiment of the plate arrangement 30.
  • the difference from the plate arrangement 30 shown in FIGS. 1 to 6 is that the single plate 34 now as a tube 70 and the double plate 32 as that Single tab 72 extending through tube 70 are formed.
  • the recess 42 cooperating with the pins 40, 40 ', the driving pin 48 and further driving pin 50 on the tube 70 and the recess 44 and further recess 46 on the tab 72.
  • the end of the tube 70 on the output shaft side and the axial ends of the recesses 42, 44, 46 on the tube 70 and on the tab 72 act in the same manner as in the embodiment according to FIGS. 1 to 6 as driving stops 52, 54, 56, 58 and stops 60,62,64. In this regard, reference is made to the description above.
  • the locking device 66 shown in FIGS. 9 and 10 has a control slide 74 which can be moved back and forth in the direction of the double arrow S and which cooperates with its two control cams 76, 76 'with two mutually opposite control lugs 78, 78' of a cross-shaped release lever 80 .
  • the trigger lever 80 is articulated on one end to a holding lever 82 which is non-rotatably seated on the output shaft 14 and is articulated at the other end with the free end of a rocker 84 mounted in a fixed position.
  • the rocker 84 is pressed against a stop pin 88 by a compression spring 86, so that the rocker 84 abutting the stop pin 88 and the trigger lever 80 are in an over-center position when the output shaft 14 is in the switch-off position 24 and switch-on position 24 '.
  • the control slide 74 which is displaceably guided via an elongated hole guide pin guide 90 parallel to the spring axis 28 ′ and the longitudinal extent of the link arrangement 30, is articulated via a connecting link 92 to a control lever 94 which is non-rotatably seated on the input shaft 12.
  • the control slide 74 is shown in its position corresponding to the first end position 18 of the input shaft 12, in which the output shaft 14 is in the switch-off position 24. Compared to this position, the control slide 74 is displaced when the input shaft 12 is brought into the second end position 18 'into a corresponding position shown in FIG. 10.
  • 10 shows the mutual dead center position of the release lever 80 and the rocker 84 in the switched-on position 24 '.
  • the first control lug 78 projects into the path of movement of the first control cam 76 (FIG. 9), and in the switch-on position 24 'the second control lug 78' engages in the path of movement of the second control cam 76 '(FIG. 10).
  • the locking device 66 functions as follows: If the input shaft 12 is turned from its first end position 18 (FIG. 9) counterclockwise towards the second end position 18 'in order to switch on the switch 10, the first control cam 76 runs onto the first control lug 78 and takes this with it, which entails rotating the release lever 80 around its connecting pin with the holding lever 82 in the counterclockwise direction. The rocker 84 is raised against the force of the compression spring 86 from the stop pin 88. As soon as the input shaft 12 reaches the switch-on unlatching position 68 (cf. FIG. 3), the axis of the connecting pin mentioned crosses the straight line between the bearing axis of the rocker 84 and its connection to the release lever 80, which is equivalent to the dead center position being exceeded.
  • the output shaft 14 is released so that it moves into the switch-on position 24 'under the force of the spring-loaded arrangement 26. pivots.
  • the trigger lever 80 also rotates about the linkage to the rocker 84 by a little more than 180 ° into the other over-dead center position shown in FIG. 10, where the output shaft 14 is prevented from rotating in the direction toward the switch-off position 24.
  • the input shaft 12 is pivoted clockwise from its second end position 18 'towards the first end position 18.
  • the second control cam 76 ' runs onto the second control lug 78' and takes it with it, which now results in the rotation of the trigger lever 80 clockwise around the linkage to the holding lever 82.
  • the rocker 84 is in turn lifted off the stop pin 88.
  • the axis of the connection mentioned crosses the extension of the straight line between the bearing axis of the rocker 84 and its articulation to the release lever 80, so that the mutual dead center position is now eliminated .
  • the output shaft 14 is now pivoted back into the switch-off position 24, which entails turning the trigger lever 80 into the position shown in FIG. 9.
  • 11 and 12 show, in the same representation as FIGS. 1 and 4, a spring drive, the spring-loaded arrangement 26 of which has two coil springs 28, 28 ''.
  • the tensioning lever 16 seated on the input shaft 12 and the drive lever 22 arranged on the output shaft 14 are double-armed and each helical spring 28, 28 '' acting as a compression spring acts via the corresponding tab arrangement 30, 30 'with the corresponding arms of the tensioning lever 16 and the drive lever 22 together.
  • 11 and 12 associated with the lower coil spring 28 Tab arrangement 30 is identical to the tab arrangement shown in FIGS. 1 to 6.
  • the structure of the tab arrangement 30 'shown above also essentially corresponds to that of the lower tab arrangement 30, whereby it is arranged in reverse, so that the area facing the tensioning lever 16 in the lower spring storage arrangement 26 and lower tab arrangement 30 now faces the drive lever 22 and vice versa .
  • the lower spring-loaded arrangement 26 and tab arrangement 30 thus have the same effect as the arrangement shown in FIGS. 1 to 6 when switched on, whereas the spring-loaded arrangement 26 and tab arrangement 30 shown in FIGS. 11 and 12 above have the same effect when switched on as the arrangement of FIGS. 1 to 6 when switching off.
  • the further recess 46 of the individual link 34 is not designed like an elongated hole but as an open recess at the end of the individual link 34 on this side.
  • the take-out shaft is forcibly carried along when switching off through the further recess 46 in the double link 32 of the lower link arrangement 30.
  • the embodiment of the locking device 66 shown in FIGS. 13 and 14 has a double-armed control lever 74 'which is freely rotatably mounted on the output shaft 14 and which, with its two control cams 76, 76' arranged on one lever arm, with the two control lugs 78, 78 located opposite one another 'of the cross-shaped trigger lever 80 cooperates.
  • the holding lever 82 which is non-rotatably seated on the output shaft 14, is pivotably connected to one end of the release lever 80, which in turn is connected is hinged at its other end to the stationary rocker 84.
  • FIGS. 13 and 14 has a double-armed control lever 74 'which is freely rotatably mounted on the output shaft 14 and which, with its two control cams 76, 76' arranged on one lever arm, with the two control lugs 78, 78 located opposite one another 'of the cross-shaped trigger lever 80 cooperates.
  • the holding lever 82 which is non-rotatably seated on the output shaft 14, is pivotably
  • the rocker 84 is urged by the compression spring 86 in the upward direction against the stop pin 88, so that the rocker 84 abutting the stop pin 88 and the release lever 80 are in their off position 24 (FIG. 13) and switch-on position 24 '(FIG. 14) of the output shaft 14 located in an over-center position.
  • the connecting link 92 connects the input shaft 12 to the control lever 74 ', in that the former is articulated on one end to the control lever 94 which is non-rotatably seated on the input shaft 12 and on the other to the lever arm of the control lever 74' remote from the control cams 76, 76 '.
  • the basic mode of operation of this embodiment of the locking device 66 is the same as that shown in FIGS. 9 and 10. 13, the control lever 74 'is in its position corresponding to the first end position 18 of the input shaft 12 and the output shaft 14 is in the switched-off position 24.
  • the control lever 74 ' is also pivoted counterclockwise.
  • the trailing control cam 76 runs onto the corresponding control lug 78 and takes it with the trigger lever 80 being rotated in the counterclockwise direction in order to link it to the holding lever 82.
  • the input shaft 12 is rotated clockwise from its second end position 18 ', with the result that the control cam 76' now runs onto the control lug 78 'and takes it with it until the trigger lever exceeds its dead center position with the rocker 84. As a result, the output shaft 14 is released for switching off.
  • the operation of the spring drive according to the invention is as follows: if the input shaft 12 is in its first end position 18 and the output shaft 14 is in the switched-off position 24, as shown in FIGS. 1 and 2 and 11, the spring end 36 of the prestressed coil spring 28 is supported the first driving stop 52 of the double strap 32 on the driving pin 48 of the tensioning lever 16. Furthermore, the double strap 32 with the second driving stops 54 bears on the other driving pin 50 on the one hand and the single tongue 34 with its second driving stop 58 on the other pin 50 on the other hand. As a result, the switch-off position 24 of the output shaft 14 is given.
  • the switch-on unlatching position 68 is not far from the second end position 18 ′ of the input shaft 12.
  • the stops 60 run onto the pin 40 'and the pin 40 onto the stop 62, which leads to a forced take-along further driving pin 50 and thus the output shaft 14 through the second driving stop 58 of the individual plate 34 until the input shaft 12 has reached the second end position 18 '.
  • the locking device 66 releases the output shaft 14, after which it moves under the force of the helical spring 28, 28''from the on position 24' in a clockwise direction towards the off position 24.
  • the double tab 32 with its first driving stops 52 again comes into contact with the driving pin 48 and the further driving pin 50 runs onto the second driving stop 58 of the single tab 34.
  • the energy not required for switching off is taken up again by the helical spring 28.
  • a switch-off brake can therefore be dispensed with.
  • the stops 60 and 62 or the stop 64 must be omitted, this can be done by correspondingly extending the recesses 42, 44 and the further recess 46 done. If necessary, this further recess 46 can be made open, as shown in FIGS. 11 and 12 above.
  • clamping lever 16 can also be used as a control lever for the pawl device 66.
  • the connecting strap 92 is articulated directly to the tensioning lever 16.
  • the drive lever 22 can also serve as a holding lever.
  • the trigger lever 80 is articulated to the drive lever 22.

Landscapes

  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Mechanisms For Operating Contacts (AREA)
  • Push-Button Switches (AREA)
  • Rotary Switch, Piano Key Switch, And Lever Switch (AREA)

Claims (10)

  1. Commande à déclic pour la connexion et la déconnexion rapides d'interrupteurs électriques, en particulier d'interrupteurs de puissance, disjoncteurs et interrupteurs de mise à la terre pour moyenne et haute tension, avec un arbre d'entrée (12), présentant un levier de tension (16) et pouvant pivoter entre deux positions extrêmes (18, 18'), avec un arbre de sortie (14), parallèle à l'arbre précité, pouvant pivoter entre une position de déconnexion (24) et une position de connexion (24'), et présentant un levier d'entraînement (22), avec un montage de ressorts accumulateurs (26), comportant au moins un ressort hélicoidal (28, 28"), qui coopère par ses extrémités (36, 36'), mobiles l'une par rapport à l'autre dans la direction de l'axe du ressort (28'), avec le levier de tension (16) et avec le levier d'entraînement (22), et un dispositif déconnectable (66) pour l'appui de l'arbre de sortie (14) dans la position de déconnexion (24) et dans la position de connexion (24'), à l'encontre de la force du montage de ressorts accumulateurs (26) qui peut être mis sous tension lors de la rotation de l'arbre d'entrée (12) à partir de chaque position extrême (18, 18') dans la direction de l'autre position extrême, jusqu'à une position de décliquetage (68, 68') de l'arbre d'entrée (12), laquelle précède l'une de chaque autre position extrême (18, 18'), caractérisée en ce que le ressort hélicoïdal (28, 28") coopère par chacune de ses extrémités (36, 36') avec le levier de tension (16) et le levier d'entraînement (22) par l'intermédiaire d'éléments d'entraînement (52, 54, 56, 58), et est maintenu à l'état de précontrainte entre les éléments d'entraînement (52, 54, 56, 58).
  2. Commande à déclic suivant la revendication 1, caractérisée par des moyens, agissant par l'arbre d'entrée (12) après le dépassement de l'une au moins des positions de décliquetage (68, 68'), pour l'entraînement forcé de l'arbre de sortie (14) par l'arbre d'entrée (12).
  3. Commande à déclic suivant l'une des revendications 1 et 2, caractérisée en ce que les extrémités de ressort (36, 36') s'appuient respectivement sur une éclisse (32, 34), chaque éclisse (32, 34) présentant un élément d'entraînement (52, 54, 56, 58) pour le levier de tension (16) et pour le levier d'entraînement (22).
  4. Commande à déclic suivant les revendications 2 et 3, caractérisée en ce que les moyens prévus pour l'entraînement forcé de l'arbre de sortie (14) présentent une butée (60, 62, 64) disposée sur une éclisse (32, 34), cette butée (60, 62, 64) étant distante d'une contre-butée (40, 40', 48, 50), coopérant avec elle, d'au moins de la course (E, A) entre la position extrême correspondante (18, 18') et la position de décliquetage concernée (68, 68').
  5. Commande à déclic suivant la revendication 4, caractérisée en ce que les éclisses (32, 34), enveloppées de préférence par le ressort hélicoïdal (28, 28"), présentent des évidements (42, 44, 46) en forme de trous longitudinaux, ces évidements étant traversés par des organes d'entraînement (48, 50), disposés sur le levier de tension (16) et/ou sur le levier d'entraînement (22) et coopérant avec les éléments d'entraînement (52, 54, 56, 58), et en ce que les éléments d'entraînement (52, 54, 56, 58) et, éventuellement, la butée (60, 62, 64), sont réalisés sur les extrémités des évidements (42, 44, 46) prévus sur les éclisses (32, 34).
  6. Commande à déclic suivant l'une des revendications 3 à 5, caractérisée en ce que l'une des éclisses (34) est formée par un conduit (70) traversé par l'autre éclisse (32).
  7. Commande à déclic suivant l'une des revendications 1 à 6, caractérisée en ce que la course de tension (A) du ressort hélicoïdal (28) dans l'un des sens de commutation, dans le sens de déconnexion de préférence, jusqu'à la position de décliquetage correspondante (68'), est inférieure à la course de tension (E) dans l'autre sens de commutation, de sorte que le ressort hélicoïdal (28) absorbe l'énergie qui n'est pas nécessaire à l'interrupteur (10).
  8. Commande à déclic suivant l'une des revendications 1 à 7, caractérisée en ce que le montage de ressorts accumulateurs (26) présente deux ressorts hélicoïdaux (28, 28"), qui coopèrent respectivement avec un bras du levier de tension et du levier d'entraînement (16, 22) à deux bras, l'un des ressorts hélicoidaux (28, 28") coopérant éventuellement, par l'une de ses extrémités, avec le levier de tension ou avec le levier d'entraînement, par l'intermédiaire d'un seul entraîneur.
  9. Commande à déclic suivant l'une des revendications 1 à 8, caractérisée en ce que le dispositif d'appui (66) présente une bascule (84) et un levier de déclenchement (80), monté éventuellement à rotation sur cette dernière, assemblé avec l'arbre de sortie (14), et actionnable à partir de l'arbre d'entrée (12), la bascule (84) et le levier de déclenchement (80) étant dans une position de point mort mutuelle, dans leurs positions de verrouillage.
  10. Commande à déclic suivant la revendication 9, caractérisée en ce que le levier de déclenchement (80) présente des ergots de commande (78, 78'), qui coopèrent avec des cames de commande (76, 76') prévues sur un élément de commande (74, 74'), assemblé avec l'arbre d'entrée (12).
EP92115463A 1992-09-10 1992-09-10 Dispositif à action brusque pour interrupteurs électriques Expired - Lifetime EP0586733B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
AT92115463T ATE141712T1 (de) 1992-09-10 1992-09-10 Sprungantrieb für elektrische schalter
DE59206960T DE59206960D1 (de) 1992-09-10 1992-09-10 Sprungantrieb für elektrische Schalter
ES92115463T ES2090439T3 (es) 1992-09-10 1992-09-10 Accionamiento de salto para interruptores electricos.
EP92115463A EP0586733B1 (fr) 1992-09-10 1992-09-10 Dispositif à action brusque pour interrupteurs électriques
JP25020393A JP3401621B2 (ja) 1992-09-10 1993-09-10 高速電気開閉スイッチのばね駆動装置
US08/118,840 US5444202A (en) 1992-09-10 1993-09-10 Actuator for electrical switches

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP92115463A EP0586733B1 (fr) 1992-09-10 1992-09-10 Dispositif à action brusque pour interrupteurs électriques

Publications (2)

Publication Number Publication Date
EP0586733A1 EP0586733A1 (fr) 1994-03-16
EP0586733B1 true EP0586733B1 (fr) 1996-08-21

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP92115463A Expired - Lifetime EP0586733B1 (fr) 1992-09-10 1992-09-10 Dispositif à action brusque pour interrupteurs électriques

Country Status (6)

Country Link
US (1) US5444202A (fr)
EP (1) EP0586733B1 (fr)
JP (1) JP3401621B2 (fr)
AT (1) ATE141712T1 (fr)
DE (1) DE59206960D1 (fr)
ES (1) ES2090439T3 (fr)

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US6448522B1 (en) * 2001-01-30 2002-09-10 General Electric Company Compact high speed motor operator for a circuit breaker
TW481344U (en) * 2001-04-27 2002-03-21 Delta Electronics Inc Switching mechanism of fuse-less switch
FR3045930B1 (fr) * 2015-12-18 2017-12-22 Schneider Electric Ind Sa Dispositif de guidage d'un ressort dans un mecanisme de commande et appareil de protection electrique le comportant.
CN108346526A (zh) * 2018-03-21 2018-07-31 广东电网有限责任公司清远供电局 一种可调式低压空气开关操作棒

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US4137436A (en) * 1976-07-21 1979-01-30 General Electric Company Means for manually slow-closing a circuit breaker that has a spring-actuated operating device
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JPS58113943U (ja) * 1982-01-28 1983-08-04 三菱電機株式会社 気中しや断器
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FR2613123B1 (fr) * 1987-03-27 1989-06-09 Merlin Gerin Mecanisme de commande d'un interrupteur a trois positions
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US5004875A (en) * 1988-10-11 1991-04-02 Siemens Energy & Automation, Inc. Stored energy contact operating mechanism
FR2660109B1 (fr) * 1990-03-23 1992-06-05 Merlin Gerin Mecanisme de commande d'un interrupteur a trois positions.

Also Published As

Publication number Publication date
US5444202A (en) 1995-08-22
EP0586733A1 (fr) 1994-03-16
JP3401621B2 (ja) 2003-04-28
ATE141712T1 (de) 1996-09-15
JPH06196037A (ja) 1994-07-15
DE59206960D1 (de) 1996-09-26
ES2090439T3 (es) 1996-10-16

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