EP1117111B1 - Mit einem Gelenkparallelogramm versehene Antriebseinrichtung für ein Kontaktorgan eines elektrischen Schalters - Google Patents

Mit einem Gelenkparallelogramm versehene Antriebseinrichtung für ein Kontaktorgan eines elektrischen Schalters Download PDF

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Publication number
EP1117111B1
EP1117111B1 EP20000410150 EP00410150A EP1117111B1 EP 1117111 B1 EP1117111 B1 EP 1117111B1 EP 20000410150 EP20000410150 EP 20000410150 EP 00410150 A EP00410150 A EP 00410150A EP 1117111 B1 EP1117111 B1 EP 1117111B1
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EP
European Patent Office
Prior art keywords
lever
parallelogram
respect
axis
transmission
Prior art date
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Expired - Lifetime
Application number
EP20000410150
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English (en)
French (fr)
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EP1117111A1 (de
Inventor
Hugues Filiputti
Didier Fulchiron
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Schneider Electric Industries SAS
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Schneider Electric Industries SAS
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Publication of EP1117111A1 publication Critical patent/EP1117111A1/de
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Publication of EP1117111B1 publication Critical patent/EP1117111B1/de
Anticipated expiration legal-status Critical
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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
    • H01H3/3047—Power arrangements internal to the switch for operating the driving mechanism using spring motor adapted for operation of a three-position switch, e.g. on-off-earth
    • 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
    • H01H3/46—Driving mechanisms, i.e. for transmitting driving force to the contacts using rod or lever linkage, e.g. toggle

Definitions

  • the invention relates to a drive mechanism for a movable contact member of a switchgear.
  • switchgear devices including a contact member is movable in translation, such as vacuum bulbs, for example.
  • switchgear whose movable contact is rotatable, but is coupled to an input member itself movable in translation.
  • the patent application FR-A-2 681 723 describes a mechanism with two parallelograms for controlling a vacuum bulb, driven by a spring.
  • the described mechanism allows only angular displacements of very small amplitude of the two parallelograms, which deform only very slightly between the open position and the closed position of the mechanism.
  • the gear ratio of the mechanism is almost constant.
  • the force applied by the mechanism to the bulb stem is in an almost constant relationship with the force applied by the spring.
  • the force applied by the spring to the mechanism decreases during the expansion in proportion to the elongation of the spring, the force applied by the mechanism to the stem of the bulb therefore also decreases during the closing movement.
  • An object of the present invention is to provide a drive mechanism of a switchgear such as a vacuum interrupter, which does not have the drawbacks identified above, and in particular provides a significant transmission ratio of forces in closing limit switch, so that the residual force of the partially disengaged closing spring at the end of the closing stroke is sufficient to ensure the contact pressure.
  • the decrease in the force applied by the spring and due to the partial expansion thereof during closure is at least partially offset by the increase in the transmission ratio.
  • the increase in the transmission ratio is continuous between the separation position and the contact position.
  • the transmission ratios referred to in this paper are static transmission ratios, as can be measured when the parts involved are immobile. More specifically, the transmission ratios considered can be measured in each position of the mechanism, by immobilizing the contact member or the drive member in the chosen position. This is the expression "in the absence of motion" used previously.
  • This increase contributes at least partially to the increase in the overall transmission ratio ⁇ .
  • This increase contributes at least partially to the increase in the overall transmission ratio ⁇ .
  • the first lever comprises a connecting member to the closing spring
  • the second lever comprises a connecting member to a closure lock adapted to prohibit the movement of the parallelogram from its open position. at its closed position.
  • the first lever comprises a connecting member to the closing spring
  • the second lever comprises a connecting member to means for applying an opening driving force.
  • the transmission means comprise means for guiding the drive member relative to the chassis, leaving the drive member at least one degree of freedom of translation relative to the frame.
  • the transmission means comprise means for guiding the drive member with respect to the transmission rod leaving the drive member at least one degree of freedom of translation by compared to the connecting rod.
  • the angle of rotation of the first and second levers between the open position and the closed position is important. The greater the angle of rotation, the easier it is to change the transmission ratios, as these vary with the angle of rotation.
  • the mechanism of the invention is thus compatible with a closed / open control and makes it easy to dimension independently of one another the closing spring and the opening spring.
  • a tripolar vacuum circuit breaker 10 comprises a frame consisting of parallel flanges 14 fixed to each other and held in position by spacers 16, 18.
  • the flanges 14 separate three polar compartments 20.
  • Each polar compartment receives a vacuum bulb 22 having a fixed contact 24 integral with an insulating jacket 26, and a movable contact 28.
  • a material support axis 30 of the fixed contact 24 is pivotally mounted relative to the two flanges 14 delimiting the compartment .
  • This support 30 has a bore 32 for guiding in translation for an end rod 34 of the fixed contact.
  • a contact pressure spring 36 with a coil is disposed between the support 30 and the body of the envelope.
  • the movable contact 28 comprises a rod whose head 40 leaves the envelope and forms a stirrup.
  • the movable contact defines a longitudinal geometrical axis which, when the movable contact is centered with respect to the envelope and located in the extension of the fixed contact, coincides with the radial geometrical axis of translation of the envelope defined by the bore 32
  • the stirrup 40 comprises two cheeks 44 each provided with a bore.
  • An axis 46 is disposed transversely in the stirrup and passes through the bores of the cheeks 44.
  • the shaft 46 supports a central roller 48 situated between the cheeks 44 and two lateral rollers 50 at its ends outside the cheeks 44.
  • the two flanges 14 flanking each pole comprise two oblong holes 52 similar located opposite each other.
  • Each oblong hole 52 defines a longitudinal axis which is arranged radially with respect to the geometric axis of pivoting of the support 30 of the envelope 26.
  • the longitudinal axis of the oblong 52 intersects the geometric axis pivoting of the support 30 and is perpendicular thereto.
  • the lateral rollers 50 of the axis 46 each cooperate with the oblong hole 52 formed in the corresponding flange 14 of the frame 12, so that the stirrup 40 is free to move in translation relative to the flanges 14 parallel to the longitudinal axes. oblongs, and to pivot around the rollers 50.
  • the drive mechanism of the movable contact comprises a lower stage, an upper stage and a control stage.
  • the lower stage comprises a switching rod 53 common to the three poles, consisting of a hexagonal shaft mounted in bearings supported by the flanges 14.
  • Each polar compartment 20 comprises an articulated parallelogram 56 consisting of a crank lever 58 secured to the bar 53, a control lever 60 pivoting about an axis 62 supported by the flanges 14 and a transmission rod 64.
  • the crank lever 58 consists of two identical and parallel flat parts located on each side. other of the transmission rod 64 and connected thereto via a pivot axis 66, so as to avoid cantilevers.
  • the control lever 60 consists of two identical and parallel flat parts located on either side of the transmission rod 64 and connected thereto via a pivot pin 68.
  • the connecting rod 64 is provided with an oblong slot 70 whose longitudinal geometric axis is perpendicular to that of the oblong holes of the flanges 14 and intersects the geometric axis of the axis 66 and that of the axis 68.
  • the axes 66, 68, 62 and the shaft 53 are all parallel to each other and perpendicular to the flanges 14. The rod 64 is thus able to move parallel to itself when the switching rod 53 pivots.
  • the central roller 48 of the shaft 46 cooperates with the oblong slot 70 of the rod 64.
  • the pin 46 cooperates with both the oblong slot 70 and with the oblong holes 52, so that its position is always determined. by the position of the intersection between the oblong holes 52 and the oblong slot 70.
  • the crank lever 58 is provided with an anchor 72.
  • the control lever 60 is provided with an axle 74 on which are mounted two coaxial rollers: a central roller 76, called an opening roller, located between the two flat pieces of the control lever, and a lateral roller 77, said closing roller, located on the outside of one of the lateral flat parts of the lever 60.
  • the upper stage of the mechanism comprises two hexagonal shafts common to the three poles and pivotally mounted relative to the flanges, namely: a camshaft 80 and an arming shaft 82.
  • the arming shaft 82 is provided, for each pole, with an arming crank 84 supporting an arming cam 83 and a percussion pin 85.
  • the arming shaft 82 is rotated by means not shown, for example a motor and / or a manually operated pumping lever.
  • the coupling between the arming shaft 82 and the drive means comprises a free wheel (not shown) which couples the driving means to the shaft when the drive means transmit to the shaft a driving torque. clockwise, and disconnect the drive means otherwise.
  • the arming shaft 82 is furthermore provided with a second freewheel (not shown) with respect to one of the flanges 14, which prevents the rotation of the shaft 82 in the anticlockwise direction and allows the rotation of the shaft in the clockwise.
  • the camshaft 80 is provided with three identical multi-function cams 88, one per pole 20.
  • Each multifunctional cam 88 has a first concave active surface 90 adapted to cooperate with the opening roller 76, as well as a second active surface. staircase consisting of an arcuate surface 92 centered on the geometric axis of the shaft and a locking stop 94.
  • Each cam 88 also comprises a roller 96 intended to cooperate with the cam 83 of the crank. arming 84.
  • the multi-function cam of the central pole is biased clockwise in the figures by an opening spring 98 fixed to an anchor 100 held in one of the lateral flanges and to an anchor 102 fixed to the cam and eccentric relative to its axis of rotation 80.
  • the multifunctional cams of the two lateral poles are each provided with a closing spring 106, one end of which is attached to the cam 88 via an anchor 108 coaxial with the dowels 102 side cams, and the other end is attached to the pin 72 of the crank lever 58.
  • a closing spring 106 one end of which is attached to the cam 88 via an anchor 108 coaxial with the dowels 102 side cams, and the other end is attached to the pin 72 of the crank lever 58.
  • the opening springs 98 and closing springs 106 are traction springs, that is to say springs whose potential energy increases when they are stretched.
  • the movement of the cams 88 is limited in the clockwise direction by a limit stop 110.
  • the control stage is located between the flanges of the central pole. It combines an opening command and a closing command.
  • the opening control comprises, between the flanges of the central pole, a half-moon opening latch 116 formed on a rotary axis 118 supported by bearings mounted on the flanges of the central pole.
  • This latch is intended to cooperate with the second active surface of the multifunctional cam 88 of the central pole. It is recalled in the opposite direction of the clockwise in the figures by a return spring 120.
  • the latch 116 is connected to a trigger member for its manual trigger or electrical fault.
  • the closure control comprises, for each pole 20, the percussion pin 85 and a locking latch 126 constituted by a lever mounted idle on a bearing 128 carried by the hexagonal shaft 80.
  • the locking latch 126 is recalled in clockwise in Figures 2 to 5 by a return spring not shown.
  • the lock 126 has a arm defining a bearing 130 cooperating with the pin 85 and a second arm defining a convex surface and a resting surface, both surfaces being intended to cooperate with the closing roller 77 of the control lever 60.
  • the movement of the lock 126 in the clockwise is limited by a stop not shown.
  • the end position in the clockwise direction is a so-called locking position, shown in FIG.
  • the circuit breaker 10 in its disarmed open state is shown in FIG. 2.
  • the closing latch 126 In this position, the closing latch 126 is in its locking position, at the end-of-travel stop in the clockwise direction.
  • the closing roller 77 bears on the convex surface of the latch 126 in such a way that the moment, with respect to the axis of rotation of the latch 126, of the force applied by the roller 77 on the latch 126, tends to rotate the latch 126. clockwise.
  • the position of the lock 126 is stable.
  • the latch 126 prevents the rotation of the control lever 60 in the clockwise direction.
  • the opening spring 98 and the closing springs 106 are very weakly bandaged and recall the multi-function cams 88 and with them the camshaft 80, in the clockwise direction, the concave surface 90 being in contact with the opening roller 76.
  • the closing spring 106 also tends to turn the crank lever 58 clockwise, but this movement is blocked due to the interaction between the control lever 60 and the closing latch 126.
  • the transmission rod 64 is in a high position and maintains the axis 46, the stirrup 40 and the movable contact 28 in an open separation position.
  • the opening lock 116 rests on the arc 92.
  • the arming of the mechanism is produced by the rotation of the arming shaft 82 in the clockwise direction.
  • the arming cam 84 contacts the arming roller 96 and drives the multi-function cams 88 and the camshaft 80 counterclockwise.
  • the closing latch 126 prevents any rotation of the control lever 60 in the clockwise direction, so that the parallelogram 56 remains in its open position.
  • the closing spring 106 and the opening springs 98 are bound due to the rotation of the pins 108 and 102 which move away from the pins 72 and 100.
  • the camshaft 80 reaches an extreme position shown in FIG. 3, when the arming cam 84 and the arming roller 96 reach a respective neutral position. In this position, the opening latch 116 has been released by the cam 92, so that the latch 116 has pivoted in the locking position under the action of its return spring 120.
  • the camshaft 80 ceases to be a receiver and becomes a motor, under the effect of the closing and opening springs 106.
  • the multifunctional cam 88 pivots under the bias of the opening springs 98 and closure 106, until the opening lock 116 is encountered.
  • the movement of the arming roller 96 is transmitted to the cam 84 and the arming shaft 82 rotates clockwise.
  • the pin 85 then hits the bearing 130 of the locking latch 126 and drives the latter counterclockwise, as shown in Figure 4.
  • the locking latch 126 then releases the roller 77 of the control lever 60, so that the parallelogram 56 is deformed by pivoting the control lever 60 and the crank lever 58 clockwise under the bias of the closing spring 106, the multifunctional cam 88 remaining locked in the clockwise direction by the lock of opening 116.
  • the transmission rod 64 moves while remaining perpendicular to the oblong holes 52. It drives the axis 46, the stirrup 40 which it is secured and the movable contact 28 secured to the stirrup until reaching a closed contact position shown in Figure 5, wherein the movable contact 28 is in contact with the fixed contact 24 and the contact pressure spring 36 is compressed about halfway.
  • the control roller 74 holds the closing latch 126 against the force of the return spring of the latch 126.
  • the closing spring 106 is partially disbursed, because of the mutual approximation of the pins 72 and 108.
  • the springs opening 98 of the lateral poles remain bandaged, because of the immobility of the pins 100 relative to the pins 102
  • the direction of the resultant of the forces applied by the closing spring 106 on the parallelogram 56 is defined by the geometric axis of the closing spring 106 which passes through the pin 72 and the pin 108 and is parallel to the 2 to 5, the point of application of the resultant forces applied by the closing spring 106 on the parallelogram 56 is located on the pin 72.
  • the direction of the forces transmitted by the transmission rod 64 to the axis 46 secured to the yoke 40 during closure is substantially perpendicular to the longitudinal axis of the oblong slot 70 and parallel to the longitudinal axis of the holes oblongs 52.
  • the downstream static transmission ratio defined by the ratio: ⁇ 1 F / C 1 , where F is the modulus of the resultant of the forces transmitted by the transmission link 64 to the axis 46 when a torque whose moment relative to the axis of the first lever is equal to C 1 absolute is applied to the shaft 53 of the parallelogram 56, increases, so that the ratio ⁇ 1 is higher at the end of the closing stroke than at the beginning.
  • the increase in the static transmission ratio can be easily modified, in particular by modifying the positioning of the geometric axis of the closing spring. To do this, simply change the respective location of the pins 72 and 108, for example by moving the pin 108 on the multifunction cam.
  • the opening of the circuit breaker 10 is initiated by the rotation of the opening lock 116, in response to a manual or automatic trip command.
  • the pivoting of the half-moon 116 releases the multifunctional cam 88 from the central pole, and with it the camshaft 80.
  • the multifunctional cam 88 and the camshaft 80 pivot in clockwise.
  • the concave surface 90 of the multi-function cam 88 comes into contact with the opening roller 76 and pivots the control lever 60 in a clockwise direction, causing the parallelogram 56 to fold.
  • the transmission link 64 drives the pin 46 into position. translation in the direction of the opening.
  • the opening movement ends when the multifunctional cam 88 encounters the end stop 110.
  • the circuit breaker is then returned to the position shown in FIG.
  • the invention is not limited to the embodiment described above. In particular, it applies as well to a three-phase switchgear as to a single-phase switchgear. Various variants are possible.
  • the figure shows a second embodiment of the invention, which differs from the first mode only by the shape of the light 270 of the transmission rod.
  • the curved shape chosen makes it possible to influence the transmission ratio during the closing and opening stroke.
  • FIGS. 7 and 8 show schematically a variant according to a third embodiment of the invention, comprising a vacuum interrupter 222 and a parallelogram mechanism comprising a crank lever 258, a control lever 260 and a transmission rod 264 provided a light 270.
  • This variant differs from the first embodiment in that the axis of the connecting rod 264, that is to say the geometrical axis perpendicular and secant with the two pivot axes of the connecting rod 264, is parallel to the axis of the vacuum interrupter 222.
  • the lever arm of the closing spring is relatively small because of its angle of inclination ⁇ with respect to the crank lever, whereas its voltage is maximum.
  • the angle of inclination ⁇ of the spring relative to the crank lever approaches the right angle so that the transmission ratio ⁇ 1 increases.
  • the ratio ⁇ 2 also increases, so that in this embodiment also the overall transmission ratio ⁇ increases.
  • FIG. 9 represents a variant according to a fourth embodiment of the invention that makes it possible to control the opening and closing of a circuit breaker whose movable contact member 328 comprises contact fingers 328a mounted pivotally relative to each other. to an axis 328b fixed to a support 328c which pivots itself relative to an axis 328d fixed to the frame of the mechanism.
  • a contact spring 336 provides the contact pressure in the closed position.
  • the drive mechanism, and in particular the parallelogram 356, is similar to that of the first embodiment.
  • the link between the parallelogram 356 and the contact member 328 is provided by a link 346.
  • control of the mechanism may call for a separation between the arming and the triggering of the closure. It suffices for this to be omitted by the closing pin 85 on the arming shaft, and an independent means is used to rotate the locking latch.
  • opening and closing springs may vary.
  • the opening spring or springs can be indifferently placed on the central pole and / or on the lateral poles. The same is true of the closing spring or springs.
  • Anchors 102 and 108 are not necessarily coaxial.
  • the closing command is not necessarily duplicated on each of the poles.
  • the opening control can be arranged on a lateral pole. It can also be duplicated on each of the poles.

Landscapes

  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)

Claims (8)

  1. Antriebsmechanismus für ein Kontaktstück (28, 328) eines elektrischen Schaltgeräts (10) mit einem Chassis, welches Kontaktstück (28, 328) mit einem Antriebselement (46, 346) verbunden ist und zusammen mit diesem zwischen einer Trennstellung und einer Kontaktstellung relativ zum Chassis verschoben werden kann, wobei der Mechanismus
    • ein Gelenkparallelogramm (56, 256) mit einem ersten Hebel (58), der um eine in Bezug zum Chassis ortsfeste, erste geometrische Achse (53) verschwenkt werden kann, einem zweiten Hebel (60), der um eine in Bezug zum Chassis ortsfeste, zweite geometrische Achse (62) verschwenkt werden kann, einer Übertragungsstange (64), die um eine, in Bezug zum zweiten Hebel ortsfeste, dritte geometrische Achse (68) sowie um eine, in Bezug zum ersten Hebel ortsfeste, vierte geometrische Achse (66) verschwenkt werden kann, wobei die vier geometrischen Achsen (53, 62, 68, 66) parallel zueinander angeordnet sind, der Abstand zwischen der ersten (53) und der zweiten (62) geometrischen Achse dem Abstand zwischen der dritten (68) und der vierten (66) geometrischen Achse entspricht, der Abstand zwischen der ersten (53) und der vierten (66) geometrischen Achse dem Abstand zwischen der zweiten (62) und der dritten (68) geometrischen Achse entspricht und das Parallelogramm (56) durch Verschwenken des ersten Hebels um die erste Achse (53) und des zweiten Hebels um die zweite Achse (62) von einer Ausschaltstellung in eine Einschaltstellung übergehen kann,
    • eine Einschaltfeder (106), die in der Lage ist, eine Antriebskraft auf das Parallelogramm (56) auszuüben, die bestrebt ist, dieses Parallelogramm von seiner Ausschaltstellung in seine Einschaltstellung zu überführen,
    • sowie Übertragungsmittel zur Übertragung der Bewegung der Übertragungsstange (64) auf das Antriebselement (46) umfasst, derart dass die durch den Übergang des Parallelogramms von seiner Ausschaltstellung in seine Einschaltstellung erzeugte Bewegung der Übertragungsstange (64) das Antriebselement (46) von der Trennstellung in die Kontaktstellung überführt,
    dadurch gekennzeichnet, dass
    • die Einschaltfeder (106) und die Übertragungsmittel so angeordnet sind, dass der Mechanismus ein statisches Gesamt-Übertragungsverhältnis entsprechend τ = F/R erzeugt,
    wobei F dem Betrag der Resultierenden der von der Übertragungsstange auf das Antriebselement übertragenen Kräfte entspricht, wenn die Feder das Parallelogramm im bewegungslosen Zustand mit einer Resultierenden R beaufschlagt, welches Verhältnis in der Kontaktstellung größer ist als in der Trennstellung.
  2. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Übertragungsmittel so ausgelegt sind, dass der Mechanismus ein statisches Ausgangs-Übertragungsverhältnis entsprechend dem Verhältnis τ1 = F / C1 erzeugt, wobei F dem Betrag der Resultierenden der von der Übertragungsstange (64) auf das Antriebselement (46) übertragenen Kräfte entspricht, wenn im bewegungslosen Zustand ein Drehmoment auf die Achse (53) des Parallelogramms wirkt, dessen Absolutwert in Bezug zur Achse (53) des ersten Hebels dem Wert C1 entspricht, welches Verhältnis in der Kontaktstellung größer ist als in der Trennstellung.
  3. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Einschaltfeder so ausgelegt ist, dass der Mechanismus ein statisches Eingangs-Übertragungsverhältnis entsprechend dem Verhältnis τ0 = C0 / R erzeugt, wobei R dem Betrag der Resultierenden der von der Einschaltfeder (106) auf das Parallelogramm übertragenen Kräfte und C0 in Bezug zur ersten geometrischen Achse (53) dem Absolutwert des Drehmoments der Resultierenden der von der Einschaltfeder (106) im bewegungslosen Zustand auf das Parallelogramm übertragenen Kräfte entspricht, welches Verhältnis in der Kontaktstellung des Antriebselements größer ist als in der Trennstellung des Antriebselements.
  4. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass der erste Hebel (58) ein Verbindungselement (72) zur Verbindung mit der Einschaltfeder (106) und der zweite Hebel (60) ein Verbindungselement (77) zur Verbindung mit einer Einschaltklinke (126) umfasst, die in der Lage ist, die Verschiebung des Parallelogramms (56) von seiner Ausschaltstellung in seine Einschaltstellung zu verhindern.
  5. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass der erste Hebel (58) ein Verbindungselement (72) zur Verbindung mit der Einschaltfeder (106) und dass der zweite Hebel (60) ein Verbindungselement (76) zur Verbindung mit Mitteln (90) zur Ausübung einer Ausschalt-Antriebskraft umfasst.
  6. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Übertragungsmittel Führungsmittel (52) zur Führung des Antriebselements (46) relativ zum Chassis umfassen, die dem Antriebselement (46) mindestens einen Translationsfreiheitsgrad in Bezug zum Chassis erlauben.
  7. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Übertragungsmittel Führungsmittel (70) zur Führung des Antriebselements (46) relativ zur Übertragungsstange (64) umfassen, die dem Antriebselement (46) mindestens einen Translationsfreiheitsgrad in Bezug zur Übertragungsstange (64) erlauben.
  8. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass der Verdrehwinkel des ersten und des zweiten Hebels zwischen der Ausschaltstellung des Parallelogramms und der Einschaltstellung des Parallelogramms groß ist.
EP20000410150 2000-01-10 2000-12-07 Mit einem Gelenkparallelogramm versehene Antriebseinrichtung für ein Kontaktorgan eines elektrischen Schalters Expired - Lifetime EP1117111B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0000229A FR2803685B1 (fr) 2000-01-10 2000-01-10 Mecanisme a parallelogramme articule pour l'entrainement d'un organe de contact d'un appareil electrique de coupure
FR0000229 2000-01-10

Publications (2)

Publication Number Publication Date
EP1117111A1 EP1117111A1 (de) 2001-07-18
EP1117111B1 true EP1117111B1 (de) 2006-07-26

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EP (1) EP1117111B1 (de)
DE (1) DE60029555T2 (de)
ES (1) ES2265900T3 (de)
FR (1) FR2803685B1 (de)

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CN102184799A (zh) * 2011-01-07 2011-09-14 无锡市锡山湖光电器有限公司 真空馈电开关的手动分闸自动复位装置
CN105742087A (zh) * 2016-04-26 2016-07-06 亚洲电力设备(深圳)股份有限公司 一种大电流隔离开关
DE102020203288A1 (de) 2020-03-13 2021-09-16 Siemens Aktiengesellschaft Stromunterbrechervorrichtung mit mehreren Schalteinheiten

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NL280737A (de) * 1961-07-10
FR2696866B1 (fr) * 1992-10-13 1994-12-02 Merlin Gerin Mécanisme d'actionnement d'un interrupteur à trois positions.

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FR2803685B1 (fr) 2002-03-01
DE60029555D1 (de) 2006-09-07
DE60029555T2 (de) 2007-08-09
ES2265900T3 (es) 2007-03-01
FR2803685A1 (fr) 2001-07-13
EP1117111A1 (de) 2001-07-18

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