EP2377139A1 - Remote control device and remote-controlled circuit breaker including such a device - Google Patents

Abstract

The invention relates to a remote control device with an insulating housing (41) having at least one main surface and including an actuator (21) with a mobile portion, driving means (22) interacting with said mobile portion, and a rotary remote control shaft (23) coupled to said driving means for actuating a cut-off device (2), said remote control shaft (23) extending through the main surface in a direction substantially perpendicular to said main surface. In the remote control device, the driving means (22) includes a bistable driving mechanism (137) which is essentially mechanical and which is coupled to the mobile portion of the actuator, said bistable driving mechanism (137) including mobile elements translatably movable along a single driving axis and rotatably movable about said axis. The invention also relates to a remote-controlled circuit breaker comprising the remote control device.

Description

 REMOTE CONTROL DEVICE AND REMOTE CONTROL CIRCUIT BREAKER EQUIPPED WITH SUCH A DEVICE

TECHNICAL FIELD OF THE INVENTION

The present invention relates to the field of electrical installations, and in particular electrical safety equipment such as circuit breakers, and in particular the remote control devices of such devices. In particular, the invention falls within the field of remote control devices with an insulating housing that can be associated with at least one cut-off device mounted on a main face of said housing.

The present invention more specifically relates to a remote control device with an insulating housing having at least one main face, for controlling at least one cut-off device disposed against said main face, said remote control device comprising an electromechanical actuator equipped with a movable part, driving means cooperating with said movable part, and a rotary remote control shaft coupled to said drive means for actuating the at least one cut-off device, said remote control shaft passing through said main face in a direction substantially perpendicular to said main face.

STATE OF THE ART

Electrical installations frequently include remotely controlled switchgear, such as remote control switches, contactors or remote control circuit breakers. A remote controlled device of this type is generally equipped with at least one cut-off device, integrated or separable, mechanically coupled to a remote control device of said apparatus. The mechanical coupling between the remote control device and the cut-off device can be achieved by means of a remote control shaft.

European patent application EP 1487002 discloses such a remote control device comprising an electric motor for actuating a remote control shaft through drive means. In this remote control device, the drive means comprise movable elements, such as a worm and a gear, said drive means for providing the remote control shaft a mechanical pulse with a force and a speed sufficient to actuate the at least one cut-off device.

A disadvantage of the remote control devices of the prior art is that they have generally complex and inconvenient drive mechanisms, and may become faulty after a large number of switching operations.

STATEMENT OF THE INVENTION

The invention aims to remedy the technical problems of remote control devices of the prior art by proposing a remote control device with an insulating housing having at least one main face, for controlling at least one cut-off device disposed against said main face, said device remote control device comprising an electromechanical actuator equipped with a movable part, drive means cooperating with said movable part, and a rotary remote control shaft coupled to said drive means for actuating the at least one breaking device, said remote control shaft passing through said main face in a direction substantially perpendicular to said main face, said remote control device being characterized in that said drive means comprise a substantially mechanical bistable drive mechanism and coupled to said movable portion of the actuator , said mechanism bistable drive comprising movable elements displaceable in translation along a single drive axis and movable in rotation about said axis.

Preferably, the movable portion of the electromechanical actuator is a plunger displaceable in translation along an axis of actuation substantially parallel to the drive axis of the bistable drive mechanism. Advantageously, the actuating axis of the plunger core is substantially coincident with the drive axis of the bistable drive mechanism.

Preferably, the bistable drive mechanism comprises a pusher acting on a control arm, said pusher being movable in translation between at least two stable axial positions. Advantageously, the pusher is held in the stable axial positions by a restoring force exerted by means of the remote control shaft. According to one embodiment, the movable elements of the bistable drive mechanism comprise an axial transmission cam cooperating with the movable part and a cam follower coupled to the pusher, said cam and said cam follower respectively comprising a first and a second surface. cams adapted to convert an axial translation of the cam to the cam follower into a rotation of said cam follower.

Preferably, the cam follower is integral with the pusher.

According to one embodiment, the bistable drive mechanism comprises a cam body for housing and guiding the cam follower in translation and rotation. Advantageously, the cam body comprises along the drive axis:

a first part comprising on an internal surface at least one axial groove for receiving at least one radial projection of the cam follower making it possible to impede the rotation of said cam follower when said follower is in said first part, and

a second portion having an enlarged passage section with respect to a narrower passage section of the first portion for allowing rotation of said cam follower when the latter is in said second portion.

Preferably, the bistable drive mechanism further comprises a third cam surface formed on the cam body and adapted to cooperate with the second cam surface of the cam follower, the second and third cam surfaces being adapted to transforming an axial translation of the cam in a direction opposite to the cam follower into a rotation of said cam follower.

Advantageously, the third cam surface of the cam body is provided on a shoulder formed by the difference of the passage section between the first and the second portion of said cam body, the second cam surface of the cam follower being formed on one face. end of the at least one radial projection of the cam follower.

Advantageously, the cam and the cam follower respectively comprise a fourth and a fifth cam surface, in addition to the first and the second surfaces. camming, to contribute to the transformation of an axial translation of the cam towards the cam follower into a rotation of said cam follower.

Advantageously, the first and second cam surfaces are in radial extensions respectively of the fourth and fifth cam surfaces.

According to one embodiment, the cam surfaces have asymmetrical sawtooth cam profiles. Advantageously, each tooth of the cam profiles comprises a first ramp having a low inclination angle of less than 70 degrees, and a second ramp having a high inclination angle greater than 70 degrees, said angles being defined with respect to a plane perpendicular to the drive shaft.

According to one embodiment, the cam and the cam follower are substantially identical parts.

According to a particular embodiment, the electromechanical actuator is equipped with a reduced displacement part of an excitation coil, the mobile part being displaceable in translation along an actuating axis substantially perpendicular to a face of support of said reduced displacement part to be deployed through a through hole of said bearing face, the drive means cooperating with said movable part to drive in translation a mobile transmission element intended to be coupled to a movable contact said cut-off device, said drive means being designed to move the movable transmission element between a first and a second stable axial position respectively corresponding to the closing and opening of said movable contact, the insulating housing enclosing damping means for damping an impact of said movable portion on said reduced displacement portion when said moving part is moved into an extended position. Preferably, the damping means are disposed between first support means of the housing and the bearing face of the reduced displacement portion to allow movement of said reduced displacement portion along the actuating axis by crushing said means dampers such that said displacement of the reduced displacement portion contributes to driving the movable transmission member from one stable axial position to the other. According to another particular embodiment, the remote control device comprises a device for locking the remote control, said cutoff device being equipped with a lever operable between an open position and a closed position of electrical contacts and a triggering lever for opening said electrical contacts following an electrical fault, said locking device comprising a retractable piece for blocking the closing of said electrical contacts when the retractable part is in an extended position, said remote control locking device comprising, in in addition, an actuating lever intended to be coupled to said trigger lever, said actuating lever cooperating with said retractable part to control the release of the at least one cut-off device when the retractable part is maneuvered to its deployed position.

According to another particular embodiment, the remote control device comprises means for signaling states and / or defects of the at least one cut-off device, said signaling means comprising first detection means making it possible to detect positions of an operating lever, said remote control device comprising second detection means arranged to detect the position of the remote control shaft rotatably mounted about a remote control axis substantially perpendicular to said main face, said shaft for actuating contacts electrical devices of the at least one cut-off device.

The invention also relates to a remote control circuit breaker comprising a remote control device equipped with a remote control shaft coupled to at least one cut-off device, said remote-controlled circuit breaker being characterized in that said remote control device is a remote control device as previously described. said remote control device being coupled to said cutoff device through the remote control shaft.

The invention also relates to a remote control device for controlling the opening and closing of a movable contact of at least one cut-off device, said remote control device comprising:

an electromechanical actuator equipped with a reduced-displacement part, an excitation coil, and a movable part displaceable in translation along an actuating axis substantially perpendicular to a bearing face of said reduced displacement portion to be deployed through a through hole of said bearing face,

driving means cooperating with said movable part to drive in translation a mobile transmission element intended to be coupled to said mobile contact, said drive means being designed to move the mobile transmission element between a first and a second position axial axis respectively corresponding to the closing and opening of said movable contact, and

an insulating housing for housing said remote control device containing damping means for damping an impact of said moving part on said reduced displacement part when said moving part is moved into an extended position,

The remote control device according to the invention is characterized in that the damping means are disposed between first housing support means and the bearing surface of the reduced displacement portion to allow movement of said reduced displacement portion along the the axis of actuation by crushing said damping means so that said displacement of the reduced displacement portion contributes to the driving of the movable transmission element from one axial position stable to the other.

Preferably, the housing comprises second support means cooperating with a second bearing surface of the reduced displacement portion opposite to said first bearing face and for maintaining said reduced displacement portion in the housing.

Preferably, the mobile transmission element is displaceable in translation along a drive axis substantially parallel to the actuating axis.

According to one embodiment, the drive means are designed so that the mobile transmission element moves between the two stable axial positions by a passage beyond a limit axial position exceeding the stable axial positions, and the damping means are arranged for the displacement of said reduced displacement portion concomitant with the displacement of said movable part in its deployed position allow a drive of said movable transmission element beyond said limit axial position. Advantageously, the damping means have a crush thickness greater than or equal to the distance between the limit axial position and the second stable axial position, said crush thickness being defined relative to the impact force of the moving part on the part. reduced displacement.

Preferably, the first support means comprise a recess in which the damping means are arranged.

Preferably, the damping means are essentially formed in a flexible material. Advantageously, the flexible material is chosen from nitrile and silicone compounds.

According to one embodiment, the damping means comprise two cylindrical seals disposed on either side of the through hole of the bearing face of the reduced displacement portion.

The invention also relates to a remote control circuit breaker comprising a remote control device equipped with a remote control shaft coupled to at least one switching device, said circuit breaker being characterized in that said remote control device is a remote control device as described above, said remote control device comprising a movable transmission element cooperating with said remote control shaft.

The invention also relates to a device for locking a remote control for at least one switching device equipped with a lever operable between an open position and a closed position of electrical contacts and a trigger lever for opening said electrical contacts following an electrical fault, said locking device comprising a retractable piece for blocking the closing of said electrical contacts when the retractable part is in an extended position, said remote control locking device being characterized in that it comprises, in addition, an actuating lever intended to be coupled to said trigger lever, said actuating lever cooperating with said retractable part for controlling the tripping of the at least one cut-off device when the retractable part is maneuvered to its deployed position.

Preferably, the remote control comprises a rotary remote control shaft for actuating the at least one cut-off device and a control arm secured to said remote control shaft, said control arm comprising a tab intended to cooperate with a protuberance of the retractable part to stop the maneuvering of said retractable part towards its deployed position when the remote control shaft is in a position corresponding to the closing of the electrical contacts of a cut-off device.

According to one embodiment, the device for locking a remote control comprises a connecting piece equipped with coupling means with the handle that can occupy two positions respectively representative of the open position and the closed position of said handle, said connecting piece cooperating with a mechanical locking member of the retractable piece to mechanically lock said handle when it is in its open position.

Preferably, the retractable part is movable along a translation axis. Advantageously, the connecting piece is rotatably mounted about an axis of rotation. Preferably, the locking member of the retractable part comprises a lug, and in that the connecting piece comprises a slideway for receiving said lug when the connecting piece is in the position representative of the opening position of the handle and that the retractable part is maneuvered to its deployed position. Preferably, the slide of the connecting piece is oriented along an axis inscribed in a plane bearing the axis of translation of the locking member of the retractable part.

According to one embodiment, the slide of the connecting piece is oriented along an axis substantially perpendicular to the axis of rotation of said connecting piece. Advantageously, the slide of the connecting piece is oriented along an axis radially offset relative to the axis of rotation of said connecting piece.

According to one embodiment, the retractable part comprises at least one opening for passing the loop of a padlock and / or the wire of a sealing when said part is in its deployed position. According to one embodiment, the actuating lever comprises a trigger tab intended to be coupled with the trigger lever. Advantageously, the operating lever comprises a lever arm equipped with a lug cooperating with a drive arm of the retractable part to cause the triggering of the at least one cut-off device when the retractable part is maneuvered to the deployed position.

The invention also relates to a remote control device for controlling at least one cut-off device equipped with a trip lever for opening electrical contacts of said cut-off device following an electrical fault, said remote control device comprising a locking device remote control device, said remote control device being characterized in that said remote control locking device is a device as described above and comprises an actuating lever intended to be coupled to said trigger lever.

The invention also relates to a remote control device with an insulating housing having at least one main face, for controlling at least one cut-off device equipped with an operating handle and arranged against said main face, said remote control device comprising signaling means of states and / or defects of the at least one switching device, said signaling means comprising first detection means for detecting positions of said controller, said remote control device being characterized in that it comprises second means detection device arranged to detect the position of a remote control shaft rotatably mounted about a remote control axis substantially perpendicular to said main face, said shaft for actuating electrical contacts of the at least one cut-off device.

Preferably, the remote control device according to the invention comprises a connecting piece equipped with coupling means intended to establish a coupling with the handle of the at least one cut-off device, said connecting piece being able to occupy at least two representative positions respectively of an open position and a closed position of said handle, the first detection means being arranged to detect said positions of said connecting piece. Advantageously, the connecting piece can occupy a third position representative of an intermediate position of the lever associated with the welding of the electrical contacts of the at least one breaking device, the first detection means being arranged to distinguish said third position of the connecting piece from the position representative of the closed position of the joystick.

Preferably, the first detection means comprise a first non-contact position sensor for detecting positions of the connecting piece. Advantageously, the first detection means further comprise first electromechanical means for detecting positions of the connecting piece.

Preferably, the second detection means comprise a second non-contact position sensor for detecting the position of the remote control shaft. Advantageously, the second detection means further comprise second electromechanical means for detecting the position of the remote control shaft.

According to one embodiment, the first detection means are connected to processing means for providing a first fault signal when the handle of the at least one cut-off device is in the open position.

According to one embodiment, the second detection means are connected to processing means for providing a second signal of a state of closure of the electrical contacts of the at least one cut-off device. Advantageously, the processing means comprise a counter connected to the second detection means for counting a number of changes in states of closing or opening of the electrical contacts for a predetermined duration, and a processing module connected to said counter to provide a overheating signal when said number of state changes exceeds a predetermined limit.

Preferably, the processing means are connected to local or remote display means. Advantageously, the local display means comprise a lamp capable of emitting light of two different colors, continuously or intermittently with different time intervals.

BRIEF DESCRIPTION OF THE FIGURES Other advantages and features will emerge more clearly from the following description of particular embodiments of the invention, given by way of non-limiting examples, and shown in the accompanying figures.

Figures 1 and 2 are perspective views of a remote control circuit breaker according to the invention.

Figure 3 is a partially exploded view of said remote control circuit breaker to distinguish a remote control block and an electrical protection block.

Figure 4 is a partially exploded view of said remote control circuit breaker for viewing the interior of each block.

Figure 5 is a schematic view of the kinematic chain between an electromagnet of the remote control device and the electrical contacts of an associated cut-off device.

FIGS. 6A and 6B are sectional views of the remote control unit in which a movable transmission element of the drive means is respectively in a first stable axial position and in a second stable axial position.

Figs. 7A to 7D are sectional views of the remote control device illustrating the operation of the electromagnet and driving means when moving from a first stable axial position to a second stable axial position of the movable transmission member.

Figures 8 and 9 are schematic views of an electromagnetic actuator comprising damping means disposed on a bearing face of a yoke of the electromagnet traversed by a plunger.

Figures 10 and 11 are schematic views of an electromagnetic actuator of the same type as that of Figures 8 and 9, except that it comprises damping means disposed on a second bearing surface opposite to the first.

FIGS. 12A and 12B are schematic views of an electromagnetic actuator of the same type as that of FIGS. 10 and 11, except that it includes an impact zone of the plunger core on the cylinder head having a "V" shaped profile. . Figures 13 to 15 are schematic views in three different positions of an electromagnetic actuator in which a movable portion of the actuator comprises a portion of the yoke.

Fig. 16 is an exploded perspective view of a cam body, a cam and a cam follower of a bistable drive mechanism forming part of the drive means of the remote control device.

Figure 17 is a perspective view of a cam or cam follower of a bistable drive mechanism according to one embodiment in which these two parts are substantially identical.

Fig. 18 is a view of the cam surfaces of the cam or cam follower.

Figs. 19A-25A and Figs. 19B-25B are respectively sectional and perspective views of the bistable drive mechanism at different stages of operation. Figures 19C to 25C correspond to sections developed along a circumference C8 (see Figure 16) in each of these steps.

Fig. 26 is a perspective view of a portion of the remote control block's interior showing a remote control lockout device.

Figure 27 is a perspective view showing a connecting piece and a retractable part of the remote control locking device, as well as drive means of the remote control and the remote control mechanism of a cut-off device associated with said remote control.

Figure 28 is a view showing the elements of Figure 27, in which the operation of the retractable part to its deployed position is blocked.

Figure 29 is a view showing the elements of Figure 27, in which the retractable part has been operated in its extended position.

Fig. 30 is a perspective view of a portion of the remotely controlled circuit breaker internals showing elements of the remote controller and a state and fault signaling device. Fig. 31 is a perspective view of the internals of the remote control block showing mainly the state and fault signaling device.

Figure 32 schematically shows a portion of the processing implemented by the signaling means.

Figure 33 is a schematic view showing the kinematic chains of the remote control circuit breaker.

Figure 34 is a perspective view of the components of a kinematic chain between the electromagnet of the remote control device and the movable contacts of the cut-off devices associated with said remote control device.

Fig. 35 is an exploded view of the remote control and electrical protection blocks of the remotely controlled circuit breaker.

Figs. 36A and 36B show respectively a sectional view of the electrical protection block and a portion of the control mechanism of a cutoff device in an open position of the electrical contacts through the handle of said device.

Figs. 37A and 37B correspond to Figs. 36A and 36B in which the switchgear lever is in a closed position and the electrical contacts of said device are closed via the remote control device.

Figs. 38A and 38B correspond to Figs. 36A and 36B in which the switchgear lever is in a closed position and the electrical contacts of said device are open through the remote control device.

DETAILED DESCRIPTION OF AN EMBODIMENT

Referring to Figures 1 to 3, the remote control circuit breaker comprises a remote control unit 1 equipped with a remote control device associated with four unipolar cutoff devices 2. These four cut-off devices have separate insulators and form an electrical protection block. The remote control device is enclosed in a separate housing relative to the casings of the cut-off devices. The devices of cutoff comprise levers 3 pivotally mounted on their respective housings. These levers are coupled together by means of a bar 4 which is itself coupled to the remote control device 1. The remote control device and the cut-off devices are joined together in solidarity with the main faces 5 of their respective housings. A light 6 having the shape of a circular sector is arranged on each main face 5 of the cut-off devices 2 to allow access to trigger means of said devices. The remote-controlled circuit breaker also comprises a remote control locking device, or padlocking device, operable from a retractable part 7. The remote control device 1 furthermore comprises light display means 8 connected to state signaling means. and electrical faults. The remote control device furthermore comprises terminals or connectors 9 for remote signaling at 220 volts, as well as remote signaling terminals or connectors in 24 volts, not shown, housed in an opening 10. These signaling connectors enable signaling deported states and / or electrical faults. The remotely controlled circuit breaker can be operated locally from a command button 11 or remotely from the terminals or control connectors 12 at 220 volts. The remotely controlled circuit breaker also includes terminals or power connectors 13 220 volts.

With reference to FIGS. 3 to 5, the remote control device comprises an electromagnetic actuator, in particular an electromagnet 21, as well as drive means

22 coupled to a movable portion of the actuator. The remote control device 1 also comprises a remote control shaft 23 rotatable coupled to the drive means 22 and for actuating the breaking means of the cut-off device. The latter comprises a control mechanism 25, a fixed contact 26, triggering means, and a movable contact 27 carried by a contact arm. More specifically, the control mechanism of the cutoff device comprises a remote control mechanism acting on the contact arm, said remote control mechanism being equipped with a remote control lever 28 rotatably mounted about a remote control axis substantially perpendicular to the main faces . The remote control lever is coupled to the remote control shaft 23 of the remote control device. Thus, the control mechanism 25 of the cut-off device can be actuated by means of the remote control device 1 via the remote control shaft 23. Alternatively, the The control mechanism 25 can be actuated by means of the control lever 3 pivotally mounted on the housing.

With reference to FIGS. 3 and 4, the remote-controlled circuit-breaker is represented in partially exploded views making it possible to distinguish the remote control block 1 equipped with the remote control device and the electrical protection block equipped with at least one cut-off device 2. The device of FIG. remote control is housed in a housing 41 of the remote control unit. The shape and dimensions of this housing are standardized allowing it to be installed in a modular installation. In particular, the remote control unit and the at least one cut-off device comprise a fastening profile 42 on a rear face 43 allowing installation on a rail of a switchboard. The remote control device 1 allows the remote control of the cut-off devices 2 whose housings are contiguous by their main faces. As in the embodiment shown, the remote control device is integrated in a remote control block integral with the electrical protection block. Alternatively, the remote control device 1 can be separable from the cut-off device 2 and be in a remote control block separable from the electrical protection block with which it is associated.

Electromagnetic actuator of the remote control device (remote control unit):

With reference to FIGS. 6A and 6B, the remote control device 1 is represented in a sectional plane parallel to the main faces of the housing 41. The electromagnetic actuator or the electromagnet 21 of the remote control device 1 is equipped with a mobile part, in this case a plunger 45 movable in translation along an actuating axis 46. The electromagnet is actuated by an excitation current or control signal flowing in a not shown excitation coil and for deploying the plunger and maintain it in this deployed position as long as said excitation current flows in the coil. In the embodiment shown in Figures 6A and 6B, the plunger 45 is in the retracted position.

As shown in FIGS. 6A and 6B, the remote control device 1 is provided with the rotary remote control shaft 23 for actuating the at least one cut-off device arranged outside the remote control unit against a main face of the housing 41. This remote control shaft 23 is oriented in a direction substantially perpendicular to the main faces of the housing 41. The coupling between the electromagnet 21 and the remote control shaft 23 is via drive means. The electromagnet and the drive means of the remote control device are housed in the insulating housing 41.

The electromagnet 21 of the remote control device further comprises a fixed or reduced displacement part of ferromagnetic material, in this case a cylinder head 51, and a not shown excitation coil. By reduced displacement is meant a displacement of small amplitude obtained by crushing damping means. In other words, the displacement of the yoke 51 is reduced compared to the displacement of the plunger 45. The latter is translational movable in response to an excitation current or control signal in the excitation coil. The plunger 45 is arranged to be displaced in translation and to be deployed through a through hole 53 of a bearing face 55 of the yoke 51, along the actuating axis 46 which is substantially perpendicular to said bearing face 55. The bearing face makes it possible to maintain the yoke 51 on first support means 58 formed in the housing.

The drive means of the remote control device, ensuring the coupling between the electromagnet 21 and the remote control shaft 23, cooperate with the plunger core 45 of the actuator to drive in translation a mobile transmission element referenced 151 and intended for to be coupled to the movable contact 27 of the at least one cut-off device 2. As explained in more detail in the following description, the drive means of the remote control device are designed to move in translation the movable member of transmission 151 along a drive axis 47 between a first stable axial position and a second stable axial position respectively corresponding to the closing and opening of the movable contact 27 of the at least one cut-off device 2. The first and the second stable axial position of the movable transmission element 151 is illustrated respectively in FIGS. 6A and 6B. As can be understood from FIG. 5, at each of these stable axial positions corresponds an angular position of the remote control shaft 23, an angular position of the control lever 28, and a closed or open position of the mobile contact 27. In the embodiment shown in FIGS. 6A and 6B, the housing 41 contains damping means 57 arranged between the first support means 58 of said housing and the bearing surface 55 of the yoke 51 to allow a reduced displacement of said cylinder head along the axis of actuation 46 by crushing said damping means. These damping means also make it possible to avoid any inadvertent tripping of the at least one cut-off device 2 associated with the remote control device.

The damping means 57 are arranged between the first support means 58 and the bearing face 55 so that the displacement of the yoke 51 contributes to driving the mobile transmission element from one stable axial position to the other. . In this way, the part of the energy dissipated in the impact of said plunger on an impact zone of the yoke 51, when said plunger reaches its deployed position, is used to move the yoke 51 along the axis of the cylinder. actuating 46 and for driving the movable transmission element 151 from one stable axial position to the other. Thus, the energy efficiency of the remote control device is optimized. In addition, the size of the remote control block is also optimized.

The damping means 57 can damp the shocks of the plunger on the bearing face 55 of the cylinder head when it deploys at the end of travel. The housing 41 also comprises second support means 59 cooperating with a second bearing face 60 of the yoke 51, said second bearing face being substantially opposite to the first bearing face 55. The first and the second means The support thus makes it possible to keep the electromagnet in the housing 41. They also make it possible to limit the reduced or damped displacement of the yoke 51 of the electromagnet along the actuating axis 46.

In the embodiment shown, the drive means are designed so that the movable transmission member 151 moves between the two stable axial positions by a passage beyond a limit axial position exceeding said two stable axial positions. The means ensuring the stable axial positioning of the mobile transmission element may be all the means known to those skilled in the art thanks to which this passage between the stable axial positions is through a forced passage in a transient position beyond the limiting axial position of said mobile transmission element, said limiting axial position exceeding the stable axial positions. For example, as described in more detail in the following description, the drive means may comprise a bistable drive mechanism 137 in which the movable transmission member 151 is a cam follower acting by the via an axial transmission cam 161 in a cam body 162.

In parallel with this configuration of drive means, the damping means 57 are arranged so that the movement of the yoke 51 concomitant with the displacement of the plunger core 41 in its extended position allows a drive of the mobile transmission element 151 beyond the axial limit position.

With this configuration, the passage of the movable transmission element 151 between the first stable axial position and the second stable axial position comprises the following steps. Initially, the movable transmission element 151 is in the first stable axial position P1 as shown in FIG. 7A, said position corresponding to the closing of the movable contact 27. The plunger 45 is, in turn, in its position retracted. By circulating an excitation current in the coil, the plunger 45 will begin to deploy and reach a position shown in Figure 7B. At this time, the drive means will start driving the movable transmission member 151 along the drive axis. In this position shown in FIG. 7B, the cam 161 thus comes into contact with the mobile transmission element or cam follower 151. Then, the plunger core 45 continues to unfold and drive the mobile transmission or follower element At the end of the stroke, the plunger core 45 strikes the impact zone carried by the first bearing face 55 of the cylinder head 51, which will cause the displacement of said cylinder head by crushing the damping means 57. this is shown in FIG. 7C, the moving transmission element or cam follower 151 thus achieving a position L corresponding to the limit axial position. Then, the excitation current is cut off and the plunger 45 retracts to reach its initial retracted position. At the same time, the moving transmission member or cam follower 151 moves in the opposite direction to reach the second stable axial position P2 as shown in FIG. 7D. This second stable axial position P2 corresponds to the opening of the movable contact 27. The damping means 57 may have a crush thickness greater than or equal to the distance between the stable axial position limit L and the second stable axial position P2. The crush thickness is defined with respect to the force of the impact or impact of said plunger 45 when it strikes the cylinder head 51. The first support means 58 comprise a recess 62 in which the damping means 57 are arranged so as to to keep these in place. The damping means 57 are generally formed essentially in a flexible material chosen from nitrile or silicone compounds. In the embodiment shown, the damping means 57 comprise two cylindrical seals arranged on either side of the through hole 53 of the bearing face 55 of the yoke 51.

In the embodiment shown in Figures 8 and 9, the actuator 21 comprises a yoke 51 of ferromagnetic material. Shocking means 70 of the electromagnetic actuator comprise a detachable portion 71 of the first bearing face 55. The damping means also comprise elastic means, in this case seals 72 made of elastic material, arranged between, on one side the cylinder head 51 or the support means of a housing not shown, and on the other side the detachable portion 71. The latter is movably mounted relative to the cylinder head 51, so that the impact of the plunger 45 on the zone of impact arranged on the first bearing surface 55 temporarily causes a relative displacement of said detachable portion 71 relative to the yoke 51 between a contact position and a detached position. By relative displacement is meant in the present case where the impact zone is disposed on the detachable portion 71, it is this detachable portion 71 which moves relative to the cylinder head 51. In another case presented in the following of the description, wherein the impact zone is disposed outside the detachable portion, it is the yoke which moves relative to said detachable portion.

As can be seen in FIGS. 8 and 9, the detachable portion 71 and the yoke 51 have complementary contact surfaces 75, 76 so that, when the detachable portion is in the position of contact, the air gap between said surfaces contact is minimum. In addition, the contact surfaces 75, 76 of the detachable portion and the yoke 51 form stops for holding the detachable portion 71 in the contact position. More specifically, in the contact position of the detachable portion 71, the elastic seals 72 exert a restoring force on the detachable portion 71, and the stops formed by the contact surfaces 75, 76 exert a counter-reaction force opposing this restoring force.

The operation of the damping means 70 of the electromagnetic actuator shown in FIGS. 8 and 9 is described below. When the actuator is in a stable state as shown in Figure 8, the detachable portion 71 is in a contact position and the gap formed by the contact surfaces 75, 76 is minimum. The detachable portion 71 is held in its contact position by the restoring pressure exerted by the elastic seals 72 and by the counteracting forces exerted by the abutments formed on the contact surfaces 75, 76. When the plunger 45 is displaced at the end of the stroke, that is to say in its deployed position, and that said core hits the impact zone, in this case the detachable portion 71, the latter is temporarily moved into a detached position as shown in FIG. 9.

In the embodiment shown in FIGS. 10 and 11, the electromagnetic actuator comprises damping means 80 cooperating with the second bearing face 60 of the cylinder head 51. As in the embodiment shown in FIGS. 8 and 9, the means dampers comprise a detachable portion 81 of the bearing face 60 mounted to move relative to the yoke 51, and spring blades 82 disposed between the yoke 51 and said detachable portion 81. In this embodiment, the damping means 80 act when the plunger 45 is moved into its retracted position and strikes an impact zone of the cylinder head arranged on the second bearing face 60. As for the mode shown in Figures 8 and 9, the detachable portion 81 and the yoke 51 have complementary contact surfaces 85, 86 forming stops to hold the detachable portion 81 in the contact position.

The operation of the damping means 80 of the electromagnetic actuator shown in FIGS. 10 and 11 is essentially the same as for the embodiment previously described. When the actuator is in a stable state as shown in Figure 10, the detachable portion 81 is in a contact position and the gap formed by the contact surfaces 85, 86 is minimum. When the plunger 45 is moved into a retracted position and said core hits the impact zone, the detachable portion 81 is temporarily moved to a detached position as shown in FIG.

In the embodiments shown in Figures 8 to 11, the detachable portion 71, 81 has a dimension along the axis of actuation substantially equal to the thickness of the bearing face 55, 60. In this way, when the detachable portion 71, 81 is in its position of contact, the portion of the bearing face 55, 60 having said detachable portion has a uniform thickness. An advantage of this embodiment is its simplicity of industrial production. In addition, in this embodiment, the insertion of the coils can take place before or after the introduction of the detachable portion 81.

In contrast, in the embodiment shown in FIGS. 12A and 12B, the detachable portion 91 of the damping means 90 has a dimension along the axis of actuation greater than the thickness of the bearing face 60. to arrange in a central part of the cylinder head 51 an impact zone having a "V" -shaped profile making it possible to minimize the magnetic losses when the plunger 45 is in an extended position. In addition, the dimensions of the movable portion 45 are reduced, compared to the embodiments of Figures 8 to 11, which reduces its weight and facilitate its setting in motion. Moreover, the "V" shape also makes it possible to optimize, within a certain limit, the variations of the magnetic force as a function of the value of the gap.

In the embodiments shown in Figures 8 to 12, the impact zone of the yoke 51 is disposed on the detachable portion 71, 81, 91 of the bearing face 55, 60. In these embodiments, the impact of the plunger core 45 on the impact zone temporarily causes a displacement of the detachable portion relative to the cylinder head.

In the embodiment shown in FIGS. 13 to 15, the actuator comprises a yoke made of ferromagnetic material formed, on the one hand, in a fixed or reduced displacement part 93, and on the other hand in a moving part 95. Fixed or reduced displacement portion 93 is provided with a bearing face 94. The fixed or reduced displacement portion 93 and the movable portion 95 both have an "E" shaped profile. The fixed or reduced displacement portion 93 of the yoke comprises three impact zones 96 disposed on the end faces of the branches of the "E". The damping means have detachable portions 97 formed in portions of the fixed or reduced displacement portion 93 linking the branches of the "E". The damping means comprise elastic means essentially consisting of a band of elastic material 92 disposed on the bearing face 94. In this configuration, the impact zones are formed outside the detachable portions 97 of the bearing face 94. .

The operation of the damping means of the electromagnetic actuator shown in Figures 13 to 15 is described below. Figure 13 shows the actuator when the moving part 95 is in an initial state. When an excitation current flows in the not shown coil, the moving part 95 moves in translation and hits the impact zones 96 of the fixed or reduced displacement part 93. Thus, the shock of the moving part 95 on the impact zones temporarily causes a displacement of the fixed or reduced displacement portion 93 of the cylinder head relative to the detachable portion. As can be seen in FIG. 14, the detachable portions 97 remain fixed, and the remainder of the fixed or reduced-displacement portion temporarily moves by pressing on the elastic band 92. Then, as can be seen in FIG. fixed or reduced displacement part 93 of the cylinder head is recalled thanks to the flexible material strip 98 in a stable position. Thus, the detachable portions 97 are found in a position of contact with respect to the fixed part or reduced displacement of the cylinder head. In this stable position, the gap formed by the contact surfaces of the detachable portions 97 and the fixed or reduced displacement portion 93 of the yoke is minimum.

Means for driving the remote control device (remote control unit):

As shown in FIGS. 5 to 7, the driving means 22 coupling between the plunger core 45 of the electromagnet 21 and the remote control shaft 23 comprise a bistable drive mechanism 137 including the movable transmission element. 151. The bistable nature of this drive mechanism 137 means that the movable transmission element 151 can be actuated between at least two stable axial positions. The first stable axial position P1 of the movable transmission member is illustrated in FIGS. 6A and 7A. The second stable axial position P2 is, for its part, represented in FIGS. 6B and 7D. The drive mechanism being an integral part of the drive means of the remote control device, the bistable character of this drive mechanism can be extended to all of said drive means. Thus, the two stable axial positions P1, P2 of the mobile transmission element 151 correspond to two stable angular positions of the remote control shaft 23.

The bistable character of the drive mechanism 137 makes it possible to use an electromagnet 21 of the monostable type. By electromagnet type monostable means that the plunger 45 of the electromagnet changes from a retracted position to the deployed position by the circulation of an excitation current, and the deployed position to the retracted position by the stopping said excitation current, or vice versa. In the embodiment shown, it is the circulation of the excitation current that allows the deployment of the plunger 45 and the passage of the movable transmission element 151 from one stable axial position to the other. Circulation of the excitation current is therefore implemented only during transient phases, and the maintenance in each of the stable axial positions of the mobile transmission element 151 requires no current. Thus, the electrical consumption and any electrical noise associated with the circulation of the excitation current in the electromagnet coil F are reduced.

As shown in Figure 3, the remote control shaft 23 passes through a main face 141 of the housing 41 of the remote control device. As can be seen in FIG. 4, this remote control shaft 23 is coupled, via the remote control lever 28, to the control mechanism 25 of the cut-off device 2. Thus, the remote control shaft 23 can be actuated between two stable angular positions, each of them corresponding to the opening and closing of the movable contact 27 of the at least one cut-off device 2 associated with the remote control device.

Advantageously, the control mechanism 25 of the at least one cut-off device 2 associated with the remote control device comprises a remote control mechanism between the remote control shaft 23 and the moving contact 27 which is of the monostable type. This is made possible by the bistable character of the drive mechanism 137 of the remote control device 1 to maintain the opening or closing of the movable contact 27 stably. Therefore, the use of a drive mechanism 137 of the bistable type remote control device and a remote control mechanism of the at least one monostable cutoff device makes it possible to switch the moving contact. 27 by means of a control mechanism 25 of the cut-off device which is simplified. For example, the remote control mechanism of the control mechanism 25 equipping the at least one cut-off device 2 can be in a stable state corresponding to the closing position of moving contacts and in an unstable state corresponding to a contact opening position. mobile. In this case, the bistable drive mechanism 137 is designed to allow application via the remote control shaft 23 a force sufficient to maintain the movable contact of the at least one open cutoff device. Note that the remote control device 1 may also be associated with a cut-off device equipped with a control mechanism comprising a bistable type remote control mechanism. This remote control mechanism of the control mechanism 25 equipping the at least one cut-off device is described in detail in the following description.

As can be seen in FIGS. 4 to 7, the mobile transmission element 151 of the bistable drive mechanism 137 is integral with a pusher 151 acting on a control arm 152 forming part of the drive means. In the following, the mobile transmission element is indifferently qualified as such or as a pusher, and this under the same reference numeral 151. The control arm 152 is pivotally mounted relative to the housing 41. The control arm 152 is fixed to the remote control shaft 23 so as to drive the latter in rotation. For this, the remote control shaft 23 has a cruciform cross section and the control arm 152 has an opening having the same section in which is inserted said arm. Thus, the pusher 151, which is movable in translation between at least the two stable axial positions P1, P2, makes it possible to drive the remote control shaft 23 in rotation.

The bistable drive mechanism 137 comprises movable elements including the pusher or mobile transmission element 151. A restoring force acting on the pusher 151 can be obtained via the remote control shaft 23, or more exactly by means of return means acting on said remote control shaft. These return means make it possible to maintain the pusher 151 in each of the stable axial positions P1, P2 by exerting a restoring force through the remote control shaft 23. These return means are generally deported outside the device remote control. In this case, these means of recall are part of at least a cutoff device 2 associated with the remote control device and will be described in detail later. In other embodiments not shown, this restoring force can be exerted by return means integrated in the remote control device.

The bistable drive mechanism 137 is generally an essentially mechanical mechanism, i.e. it does not require electricity or any liquid or gaseous fluid to operate. The bistable drive mechanism 137 essentially consists of movable elements displaceable in translation along the drive axis 47 and movable in rotation about said axis 47. In the embodiment shown, the drive shaft 47 is substantially coincides with the actuating axis 46 and substantially parallel to the main face of the housing 41.

As shown in FIGS. 5 to 7, and in more detail in FIGS. 16 to 18, the bistable drive mechanism 137 comprises an axial transmission cam 161 cooperating with the plunger 45 of the electromagnet 21. By axial transmission cam means a cam movable in translation for which the translational movement is along an axis of translation substantially coincident with the axis of rotation of a cam follower. This type of cam is often called "cam cloche". In this case, the axial transmission cam 161 is displaceable in translation along the drive axis 47.

As can be seen in FIG. 16, the bistable drive mechanism 137 also includes a barrel or cam body 162 including a first portion 163 in which the cam 161 is slidably disposed along the drive axis. This cam body 162 generally has a tubular shape. The translation displacement of the cam 161 in the cam body 162 can be achieved by means of axial grooves 164 disposed on the inner surface of the first portion 163 of the cam body 162. The axial grooves 164 are designed to receive radial projections. 165 disposed on an outer and lateral surface of the cam 161. Thus, the axial grooves 164 and the radial projections 165 not only allow to guide the cam 161 in translation along the drive axis 47, but also allow impede the rotation of said cam 161 about this axis. An end face 166 of the cam 161 cooperates with the plunger 45. On the other end face of the cam 161, and more exactly on the end faces of the radial projections 165 of this other end face, is provided in a first cam surface 167. In other words, this first cam surface is carried by each shoulder of the radial projections 165. More specifically, the first cam surface 167 is essentially formed by a succession of teeth 182 distributed around each other. a circumference of the cam, or more exactly by the end faces of said teeth.

The bistable drive mechanism 137 also comprises a cam follower 171 coupled to the pusher 151, and in this case secured to said pusher. In the same way as the cam 161, the cam follower 171 includes radial projections 175 intended to be engaged in the axial grooves 164 of the cam body 162.

As can be seen in FIG. 17, the cam and the cam follower are substantially identical pieces. This simplifies manufacturing and reduces associated costs. An end face 176 of the cam follower 171, that is to say the pusher 151, cooperates with the control arm 152 of the drive means. The cam follower 171 comprises, on the other end face facing the first cam surface 167, a second cam surface 177 intended to cooperate with this first cam surface 167. In the same way that for the first cam surface, the second cam surface 177 is provided on the end faces of the radial projections 175. In other words, this second cam surface 177 is essentially carried by each shoulder of the radial projections 175. More specifically, the second cam surface is essentially formed by a succession of teeth 182, or more exactly by the end faces of said teeth.

The first and second cam surfaces 167, 177 are adapted to translate an axial translation of the cam 161 to the cam follower 171 into a rotation of said cam follower. To allow rotation of the cam follower 171, a second portion 169 of the cam body 162 has an enlarged passage section with respect to the narrower passage section of the first portion 163. This passage section of the second portion

169 of the cam body 162 advantageously has a diameter equal, in the game, to that of a circle surrounding the radial projections 175 of the cam follower 171. In FIG. 16, the first part 163 of the cam body 162 has been shown in an exploded manner to display the two parts 163 and 169 of the cam body 162. Thus one can distinguish, on the one hand, a tubular casing 184 of large section passageway having a passage section corresponding to that of the second portion 169 of the cam body 162, and secondly, an insert 185 having a passage section corresponding to that of the first portion 163 of narrower passage section. The insert 185 shown in Figure 16 therefore just shows the two parts 163, 169 of the cam body 162, and corresponds to a portion forming with the tubular casing 184 a unitary unit.

The cam 161 and the cam follower 171 have an axial hole 168, 178 opening on the end face respectively bearing the first and the second cam surface 167, 177. This axial hole 168, 178 can accommodate spring means 179 , in this case a compression spring intended to provide a restoring force opposing the axial translation of the cam 161 towards the cam follower 171.

The cam body 162 has a third cam surface 192 provided on a shoulder or flange 193 formed by the passage sectional difference between the first and second portions 163, 169 of the cam body 162. This third cam surface 192 of FIG. Cam body 162 is intended to cooperate with the second cam surface 177 of the cam follower 171 as the cam 161 retracts. Thus, the second and third camming surfaces 177, 192 are designed to translate an axial translation of the cam 161 in a direction opposite to the cam follower 171 into a rotation of said cam follower.

The radial distance from the radial projections 165, 175 of the cam 161 and the cam follower 171 is generally substantially equal, with the clearance, to the width of the flange 193 formed by the difference in cross section between the first and the second portion 163 , 169 of the cam body 162. This configuration provides a better mechanical strength, which allows the bistable drive mechanisms 137 to collect greater efforts.

In addition to the first and second cam surfaces, the cam 161 and the cam follower 171 respectively have a fourth and a fifth cam surface respectively referenced 191, 194 also contributing to the transformation function of the axial translation of the cam. cam to the cam follower rotating said cam follower. These fourth and fifth cam surfaces 191, 194 are formed on a portion annular end faces of the cam 161 and the cam follower 171 carrying the first and the second cam surface 167, 177. In particular, the fourth and fifth cam surfaces 191, 194 are in the extension respectively of the first and fourth camming surfaces 167, 177. In other words, the first and fourth camming surfaces 167, 191, as well as the second and fifth camming surfaces 177, 194, have a radial continuity; which facilitates the manufacture of the cam and cam follower.

As shown in Fig. 17, the cam surfaces 167, 177, 192, 191, 194 generally have asymmetric profiles, such as, for example, sawtooth profiles. In other words, the profile of the cam surfaces comprises an alternation of first and second ramps 195, 196 oriented in an opposite direction and having different angles of inclination. These asymmetrical profiles maximize the contact area as cam surfaces of the cam follower and the cam body come into contact. Thus, the mechanical strength of the bistable drive mechanism 137 is improved.

As shown in FIG. 19C, a tooth of a cam profile comprises on the one hand a first ramp 195 having a low inclination angle ALPHA1 of less than 70 degrees, this angle being defined with respect to a plane perpendicular to the drive shaft 47. A tooth of a cam profile also comprises a second ramp 196 having a high angle of inclination ALP HA2 greater than 70 degrees, this angle being defined in the same way with respect to the same plane. perpendicular to the drive axis 47. The low inclination angle ALPHA1 of the first ramp 195 is advantageously between 20 and 70 degrees, preferably between 25 and 35 degrees, for example substantially equal to 28 degrees.

As can be seen in FIG. 19C, the ramps of steep inclination 196 have an inclination angle ALPH A2 advantageously between 70 and 90 degrees, preferably between 75 and 85 degrees, for example substantially equal to 78 °. This makes it possible to prevent jamming of the cam as it moves away from the cam follower, since the bearing forces of the teeth of said cam follower on the teeth of the cam comprise a component which participates in the cam follower. ejection of the cam at the moment when the follower lands on the Teeth of the cam body 162. In other embodiments not shown, the ramps of steep inclination 196 may have an angle of inclination ALPHA2 substantially equal to 90 degrees.

The profiles of the first, second and third cam surfaces 167, 177, 192 are discontinuous, that is to say they comprise a succession of toothed portions and spaces or depressions distributed around them a circumference of the cam 161, the cam follower 171 or the cam member 162. For the cam 161 and the cam follower 171, each toothed portion corresponds to an end face of a radial projection 165, 175 For the cam body, each toothed portion corresponds to a portion of the flange 193 between two axial grooves 164. The profiles of the fourth and fifth cam surfaces 191, 194 are, for their part, continuous, that is, that is to say that they comprise a succession of teeth distributed continuously around a circumference of the cam 161 or the cam follower 171.

The cam surfaces cooperating with each other advantageously have complementary profiles. This maximizes the contact area between the cam surfaces and the mechanical strength is improved.

The total number of teeth on the first or the second cam surface 167, 177 is generally equal to half the number of teeth on the fourth or fifth cam surface 191, 194. This total number is advantageously equal to a multiple of number of axial grooves 164 or the number of radial projections 165, 175. In the embodiment shown, the number of teeth distributed around a circumference of the fourth or fifth cam surface 191, 194 is 10. In With regard to the first and second cam surfaces 167, 177, each toothed portion carried by the end faces of the radial projections 165, 175 comprises a half-tooth, that is to say a tooth whose width corresponds to at half that of the complete teeth of the fourth and fifth cam surfaces 191, 194. With respect to the third cam surface 192, each toothed portion between two axial grooves 164 includes a complete tooth and a half tooth.

Thanks to this configuration of the cam surfaces, the drive means 25 make it possible to apply to the remote control shaft 23 a torque greater than 0.02 Nm, 0.05 Nm, for example 0.1 Nm. This torque corresponds to the force to be applied to open the contacts of the at least one cut-off device associated with the remote control device. This force is generally tenfold as a function of the number of poles of the at least one cut-off device.

In the following, the operation of the drive mechanism is presented in more detail with reference to Figures 19 to 25.

When the plunger 45 is in a retracted position, the cam follower 171 is held by the contact pressure spring A3 (Fig. 33) in the first stable axial position Pl. This first stable axial position of the cam follower 171 is shown schematically in FIGS. 19A to 19C.

At first, the cam 161, driven by the plunger 45 of the electromagnet, will come into contact with the cam follower 171 and then axially push said cam follower 171, as shown in FIGS. 2OC. As long as the cam follower 171 is at least partly in the first portion 163 of the cam body 162, the radial projections 175 of said cam follower 171 and the axial grooves 164 of the cam body 162 impede any rotation of said cam follower, and the latter can move only in translation under the thrust exerted by the cam. During this phase in which the rotation of the cam follower 171 is impeded, the first and second cam surfaces 167, 177 are in a partial contact position, as opposed to a maximum contact position in which the major part, or even the all, cam surfaces are in contact. In this position of partial contact between the cam 161 and the cam follower 171, the axial distance between said cam and said cam follower is not minimal. Once the cam follower 171 is outside the first portion 163 of the cam body 162, the rotation of said cam follower is no longer hampered.

As shown in Figs. 21A-2C, the translation movement of the cam 161 which urges the cam follower 171 causes a first rotation ROTI of said cam follower by sliding of the second camming surface 177 on the first cam surface 167, and the fifth cam surface 194 on the fourth cam surface 191. This first rotation ROTI was made possible by the alignment of the ramps 195 of the surfaces 167, 191 of the cam with the ramps 195 respectively of the cam surfaces of the Also, this first ROTI rotation has been made possible as soon as the teeth on the cam surfaces of the cam protrude from the top of the teeth on the third cam surface 192 of the cam body. This first rotation ROTI continues until the first and second cam surfaces 167, 177, as well as the fourth and fifth cam surfaces 191, 194, are in maximum contact positions, corresponding to an axial distance between said cam and said cam follower. At this time, the ramps 196 of cam surfaces 177, 194 of the cam follower abut in that of the cam surfaces 167, 191 of the cam. At the end of this first rotation ROTI, the drive mechanism 137 is in the state shown schematically in FIGS. 22A to 22C. Note that the radial projections 175 of the cam follower 171 are no longer aligned with the axial grooves 164 of the cam body 162 and that said cam follower has made a rotation corresponding to half the width of a tooth.

As shown in Figs. 23A-23C, as the cam 161 retracts or moves in a direction opposite to the cam follower 171, the radial projections

175 of said cam follower, which are no longer aligned with the axial grooves 164 of the cam body 162, abut against the shoulder of said cam body by preventing any translation of the cam follower in the opposite direction. The second cam surface 177 of the cam follower 171, formed on the end faces of the radial projections 175, thus cooperates with the third cam surface 192 formed on the shoulder of the cam body 162.

Under the impulse of the restoring force exerted through the remote control shaft 23, the second cam surface 177 of the cam follower 171 slides on the third cam surface 192 of the cam body 162 driving said cam cam follower in a second rotation ROT2 in the same direction as the first. In this way, the second and third camming surfaces 177, 192 make it possible to transform the axial translation of the cam 161 in an opposite direction relative to the cam follower 171 in the second rotation ROT2 of said cam follower. This second rotation continues until the second and third camming surfaces 177, 192 are in maximum contact positions corresponding to a second stable axial position P2 of said cam follower. At the end of this second rotation ROT2, the radial projections 175 of the cam follower 171 are not still not aligned with the axial grooves 164 of the cam body 162. This second stable axial position of the cam follower 171 is schematically shown in Figs. 23A-23C. Note that the radial projections 175 of the cam follower 171 are still not aligned with the axial grooves 164 of the cam body 162 and that said cam follower has made a rotation corresponding to half the width of a tooth.

In summary, to move from the first stable axial position P1 shown in FIGS. 19A to 19C to the second stable axial position P2 shown in FIGS. 23A to 23C, in a first step the plunger 45 is deployed to drive the follower cam 171 and the pusher 151 integral with said follower in a first sliding rotation of the second cam surface 177 on the first 167, and the fifth cam surface 194 on the fourth 191. At the end of this first rotation, the cam follower 171 is in the position shown in Figs. 22A-22C. In a second step, the plunger 45 retracts allowing the spring 179 to drive the cam 161 in translation in the same direction as said plunger. As a result, the cam follower 171 and the pusher 151 integral with said follower are driven in a second rotation by sliding the second camming surface 177 on the third 192. Just before this second rotation, the cam follower 171 is in the second position. position shown in Figs. 22A to 22C. At the end of this second rotation, the radial projections 175 of the cam follower 171 are not aligned with the axial grooves 164 of the cam body 162, and said cam follower is thus held in the second portion 169 of the cam body. 162 and in the second stable axial position P2 shown in Figures 23A to 23C.

This second stable axial position P2 may correspond to an angular position of the remote control lever 28, which itself corresponds to an open position of the electrical contacts of the at least one cut-off device 2 associated with the remote control device. Thus, in the preferred case of an electromagnet of the monostable type, the plunger being in a retracted position, no excitation current is required to maintain the electrical contacts of the associated breaking device in an open position.

To move from the second stable axial position P2 to the first P1, the process is substantially the same. At first, the plunger 45 is deployed to driving the cam follower 171 and the pusher 151 integral with said follower in a third rotation ROT3 by sliding the second camming surface 177 on the first 167, and the fifth camming surface 194 on the fourth 191. This third rotation is permitted in that the first and the second cam surfaces 167, 177, as well as the fourth and fifth cam surfaces 191, 194 are not initially in a maximum contact position. At the end of this third rotation ROT3, the cam follower 171 is in the position shown in FIGS. 24A to 24C. Note that the radial projections 175 of the cam follower 171 are still not aligned with the axial grooves 164 of the cam body 162. In a second step, the plunger 45 retracts allowing the spring 179 to drive the cam 161 in translation in the same direction as said plunger. As a result, the cam follower 171 and the pusher 151 integral with said follower are driven in a fourth rotation ROT4 by sliding the second cam surface 177 on the third 192. Just after this fourth rotation ROT4, the cam follower 161 is in the position shown in Figs. 25A to 25C. At the end of this fourth rotation, the radial projections 175 of the cam follower 171 are aligned with the axial grooves 164 of the cam body 162, and the cam follower is thus driven in translation in the first portion 163 of the cam body. 162 to the first stable axial position Pl shown in Figs. 19A-19C.

Between the first and the second rotation ROTI, ROT2 on the one hand, and between the third and the fourth rotation ROT3, ROT4 on the other hand, the cam follower 171 and the pusher 151 integral with said follower can be driven beyond an axial limit position exceeding the first and second stable axial position P1, P2. The distance between this limit axial position and the second stable axial position P2 substantially corresponds to the height of the teeth of the cam surfaces.

The electromagnet 21 is advantageously designed to maintain, in the absence of activation current, the plunger 45 and the cam 161 in the retracted position. In this way, the maintenance in the first and second stable axial position Pl, P2 of the cam follower 171 and the pusher 151 to which it is coupled is independent of the position of the cam 161 and the plunger 45 cooperating with this cam. Thus, maintaining in the stable axial positions P1, P2 of the cam follower 171 and the pusher 151 to which it is coupled does not requires no excitation current, which optimizes energy consumption and minimizes the defects related to the circulation of an excitation current.

Furthermore, the passage between the first and second stable axial position Pl, P2, in one direction and the other, is done by means of an activation current whose intensity can be chosen to apply a torque to the remote control shaft sufficient to open the contacts of the at least one cut-off device associated with the remote control device.

In the remote control device presented, the movable elements of the bistable mechanism 137, that is to say essentially the cam 161 and the cam follower 171, are displaceable in translation along a single drive axis 47 substantially coinciding with the actuating axis 46 of the plunger 45. These movable elements are also movable in rotation about the same axis 46, 47. With this configuration in which the displacements of the movable elements are made in translation along a single axis or in rotation around this same axis, the bistable drive mechanism 137 is simplified and compact. This simplification makes the remote control device particularly enduring, that is to say that it can be operated a large number of times while maintaining a good level of reliability. This endurance is also due to the fact that the driving force of the bistable mechanism is distributed over several teeth of the cam and the cam follower. The remote control device is generally designed to allow a large number of switches, that is to say more than 20000 switches, or even more than 40000 switches, for example 50000 switches.

Remote control locking device (remote control unit)

As can be seen in FIGS. 1 and 2, the remote-controlled circuit-breaker comprises a remote control locking device or padlocking device that can be operated from the retractable part 7. In this case, the retractable part 7 is a drawer mounted to be movable in translation. on the housing 41. In the embodiment shown, the remote control locking device is essentially disposed in the remote control device. The remote control device 1 and the at least one cut-off device 2 associated with said remote control device are juxtaposed by their main faces 141, 5. In the remote control locking device shown in FIG. 26, the main face of the remote control device against which is affixed at least one cut-off device has been erased in order to display the remote control locking device. To better distinguish the elements of this remote control locking device, the electromagnet 21 and the drive means 22 of the remote control device have also been erased from this figure 26.

With reference to this FIG. 26, the remote control locking device comprises the retractable part 7 mounted in translation on the housing 41. The main function of this retractable part 7 is to block the closing of the electrical contacts of the at least one breaking device. associated with the remote control device. This retractable part 7 also makes it possible to maintain the opening of the electrical contacts when it is in its deployed position. For this, the retractable part 7 has an opening 200 for passing a loop of a padlock when said part is in its deployed position. More specifically, the size of the opening is defined so that the presence of a padlock loop can maintain the retractable part 7 in its deployed position.

In another embodiment not shown, the retractable part could include an opening for passing a sealing wire. It could also include two openings, one dedicated to the handle of a padlock and the other dedicated to a lead wire.

The remote control locking device further comprises an actuating lever 201 for coupling to a trigger lever of the at least one cutoff device associated with the remote control device. This actuating lever, arranged between the retractable part and the release lever, makes it possible to transform the translation movement of the retractable part into a pivoting movement of the release lever. More specifically, the actuating lever 201 comprises a release tab 202 intended to cooperate with the trigger lever. This trigger tab 202 may be a needle that can be inserted into a port of the trigger lever. As can be seen in FIGS. 1 to 3, the triggering lever of the at least one cutoff device 2 associated with the remote control device is accessible through a slot 6 formed on the main face 5 of said cutoff device. This light 6 is generally present on both sides of the cut-off devices 2. The light 6 generally has a shape of circular sector centered on the axis of the trigger lever. This light thus allows access to the trip lever via the release tab 202 of the actuating lever 201.

As can be seen in FIG. 26, the actuating lever 201 is coupled to the retractable part 7 via a driving arm 203 of said retractable part 7 cooperating with a lug 204 of a lever arm 205 of said operating lever. The actuating lever 201 comprises an axis, not visible, disposed behind a tab 208 of said lever and substantially perpendicular to the main faces. This axis cooperates with a non-visible bearing housing to allow rotation of the actuating lever 201. As shown in Figure 27, the retractable part 7 has a recess 207 for the passage of this axis. The presence of this axis makes it possible to guide the trigger tab 202 of the actuating lever 201 in an arcuate movement to pivot the release lever of the cut-off device attached to the remote control device.

Thus, by pulling on the retractable part 7 to maneuver it to its deployed position, the drive arm 203 of said retractable part drives the pin 204 of the actuating lever 201 in a substantially translational movement. During the displacement of the lug 204, the actuating lever 201 is rotated so as to move the trigger lug 202 in a circular arc following the light 6 and driving the trigger lever of the adjoining cut-off device. to the remote control device.

More specifically, the pivoting of the tripping lever of the cut-off device attached to the remote control device is obtained when the retractable part 7 is in a first intermediate position between an initial or retracted position and its extended position, that is to say before that the retractable part 7 reaches its deployed position. In the case where the remote control device is associated with several cut-off devices, the cut-off devices which are not contiguous against said remote control device are triggered by means of their respective tripping levers which are mechanically interconnected. The contacts of the cut-off devices can also be manually opened through the bar 4 mounted integrally on the handles 3 of all of said cut-off devices.

The remote control locking device further comprises means for blocking the retractable part 7 so as not to be able to condemn the remote control when the electrical contacts of a cut-off device are soldered. These locking means interact with the drive means of the remote control device, in particular with the control arm 152 integral with the rotary remote control shaft 23 whose angular position depends on the position of the movable contact of the at least one control device. cut. More specifically, these locking means comprise a lug 206 secured to the control arm 152 and a protrusion 209, in this case a lug, secured to the retractable part 7. When the remote control shaft 23 is in a position corresponding to the closing the electrical contacts, the tab 206 acts as a stop for stopping the maneuver of the retractable part 7 to its deployed position, the protrusion 209 of said retractable piece acting as a stop. These locking means are independent of the actuating lever 201 intended to be coupled with the release lever of the at least one cut-off device. The implementation of these locking means can be envisaged for any remote control locking device using other locking means, for example via the handles of the cut-off devices.

The remote control locking device comprises a connecting piece 211 equipped with coupling means with the handle 3 of the at least one cut-off device 2. These coupling means essentially comprise a drive lug 213 of the connecting piece 211 which is inserted in a groove 215 of the bar 4 integral with the set of levers 3. Thus, the connecting piece 211 is integral with the handle 3 of all the cut-off devices associated with the remote control device. The connecting piece 211 is designed to occupy at least two positions representative of the open position and the closed position of said handle, and optionally intermediate positions as described below. In the embodiment shown, the connecting piece 211 is rotatably mounted about an axis of rotation substantially coinciding with a pivot axis of the handle 3 of the at least one cut-off device associated with the remote control device.

As can be seen in FIGS. 28 and 29, the connecting piece 211 comprises blocking means, in this case a slideway 217. These locking means of the connecting piece cooperate with a mechanical locking member of the retractable part. 7, in this case a lug 218, for mechanically locking said connecting piece when it is in its position representative of the opening position of the handle and when the retractable part 7 is manceuvrée to its deployed position.

In the embodiment shown, the slideway 217 of the connecting piece 211 is oriented along an axis substantially perpendicular to the axis of rotation of said connecting piece. Whatever the position of the connecting piece 211, the axis of the slide 217 is in a plane bearing the axis of translation of the lug 218. Thus, the sliding of the lug 218 in the slide 217 n ' is possible when the connecting piece 211 is in its angular position representative of the opening position of the handle 3 and wherein the axis of the slide 217 is substantially coincident with the axis of translation of the lug 218.

Thus, when the connecting piece 211 is in its position representative of the opening position of the handle 3 of the at least one cut-off device 2, and when the retractable part 7 is moved towards its deployed position, the lug 218 is moves in translation along the axis of the slide 217 and comes to slide in said slide which allows to hinder any rotation of said connecting piece. The lever 3 of the at least one cut-off device associated with the remote control device being integral with the connecting piece 211, the blocking of said connecting piece 211 is accompanied by the blocking of said knobs 3. When the retractable piece reaches its deployed position the opening 200 is sufficiently disengaged and the insertion of the padlock loop into the opening 200 becomes possible. A clip 219 of the retractable part 7 makes it possible to block said piece in its deployed position in a notch of the casing 41 (FIG. 26) in order to pass the handle of the padlock. A second notch keeps it in the retracted position. With this configuration, the user has both hands to pass the padlock handle and close it.

In the case where the lever 3 of the at least one cut-off device 2 associated with the remote control device 1 is initially in a closed position of the contacts, the operation of the retractable part 7 towards its deployed position is initially carried out by the first intermediate position for triggering the at least one cut-off device. Thus, the lever 3 of the at least one cut-off device passes from the closed position to the open position of the contacts, by driving the connecting piece 211 in rotation to its position representative of said open position. At this moment, the translation of the lug 218 of the retractable part 7 is no longer impeded, and said retractable part can be maneuvered to its deployed position in which the insertion of the handle of a padlock into the opening 200 becomes possible.

In the case where the electrical contacts of a cut-off device are welded, for example as a result of an electrical fault, the handle 3 of said device can not be returned to its open position. Insofar as the mechanical coupling between the lever 3 of each cut-off device and the connecting piece 211 is perfect, that is to say that by applying a force anywhere on the bar 4 all the levers are moved in the same way, the connecting piece 211 is always in a position hindering the translation of the lug 218 and it is not possible to maneuver the retractable part 7 to its extended position. In addition, the remote shaft 23 is in an angular position for which the tab 206 of the control arm 152 blocks the protrusion 209 of the retractable part 7, which reinforces the impossibility of any maneuver of said retractable part in its retracted position. In the case where the mechanical coupling between the lever 3 of each cut-off device and the connecting piece 211 is not perfect, it is only the angular position of the remote control shaft 23 that blocks the maneuver of the part retractable 7 in its deployed position through the lug 206 and the protrusion 209. Thus, whatever the strength of the mechanical coupling between the handle 3 of each cut-off device and the connecting piece 211, the welding of a pair of contacts of a cutoff device systematically prevents the operation of the retractable part 7 in its deployed position and thus the locking of said remote control device by inserting the handle of a padlock in the opening 200. By way of example, considering the embodiment of FIG. 1 having four cut-off devices 2, if the fourth cut-off device has a contact welding problem, it may be possible to open the contacts of the first switchgear device. cut that is attached to the remote control device, applying a force on the bar 4 at said first cut-off device and partially disengaging said bar relative to all of the knobs 3. In this case, the connecting piece 211 n is more in a position hindering the translation of the lug 218, and it is only the angular position of the remote control shaft 23 that blocks the operation of the retractable part 7 in its deployed position through the tab 206 and protrusion 209.

In all cases of welding a pair of contacts, the retractable part 7 can be operated to its first intermediate position, which can trigger the other cut-off devices.

More precisely, between this first intermediate position and the deployed position, there is a second intermediate position of the retractable part 7 in which the translation of the lug 218 is impeded by the non-alignment of the slideway 217 with the translation axis of said lug. The lever 3 of the at least one cutoff device is thus in a median position between the open position and the closed position of the handle, and the slideway 217 of the connecting piece 211 is not aligned with the translation axis of the pin 218. Thus, in case of welding of the electrical contacts, it is not possible to maneuver the retractable part 7 to its deployed position, and the insertion of the handle of a padlock in the opening 200 is prevented.

An advantage of the remote control locking device according to the invention is that it is not subject to the mechanical strength of the retractable part or any coupling means between said retractable part and the handle of the at least one associated cut-off device to the remote control device.

Means for signaling states and electrical faults (remote control unit)

The remote-controlled circuit breaker, and in particular the remote control device 1 of said circuit breaker, comprises signaling means making it possible to signal, on the one hand, the states of opening or closing of the electrical contacts of the at least one cut-off device 2 associated with the remote control device and, on the other hand, the presence of an electrical fault. The signaling means are connected to local display means 8, signaling connectors 9, and non-visible connectors behind the opening 10, said connectors allowing remote monitoring.

The signaling means comprise first detection means arranged to detect positions of the lever 3 of the at least one cutoff device 2 associated with the remote control device, and second detection means arranged to detect the position of the remote control shaft. 23 rotatably mounted around the remote control shaft. In the embodiment shown, the signaling means are arranged in the remote control unit 1 of the circuit breaker. The signaling means comprise processing means 280 arranged between, on one side, the first and second detection means and, on the other side, the local display means 8 as well as the connectors enabling remote monitoring.

In the embodiment shown in FIGS. 30 and 31, the first detection means make it possible to obtain a first signal SD representative of the presence of any electrical fault that may successively trigger the at least one cut-off device 2 and one positioning the handle 3 of said device in an open position. Such electrical faults may be the presence of a short circuit or the presence of a current overcurrent. In addition, the first detection means make it possible to obtain a first signal SD representative of a positioning of the handle 3 of said device in an open position, even in the absence of an electrical fault.

The first detection means could also make it possible to obtain a signal representative of a defect related to the welding of the electrical contacts of a cut-off device. Indeed, in the embodiment shown, the at least one cut-off device 2 associated with the remote control device 1 is designed so that, in the case where the electrical contacts of a device are soldered, the lever 3 of said cut-off device 2 can be moved to an intermediate position between the open position and the closed position. When soldering the electrical contacts, the positioning of the handle 3 in this intermediate position is generally obtained, either following a attempting to open said contacts via the remote control device 1, either via the handle 3, or following a tripping of an electrical fault cut-off device. The first detection means could therefore be designed to detect this intermediate position of the joystick. In the embodiment shown, the first detection means are designed to simply distinguish this intermediate position of the lever 3 from its closed position.

In the embodiment shown in FIGS. 30 and 31, the first detection means are arranged to detect the positions of the connection piece 211. This connecting piece 211 is pivotally mounted about an axis substantially coinciding with the axis pivoting of the handle 3. This connecting piece 211 is equipped with coupling means with the handle 3 of the at least one cut-off device 2 associated with the remote control device. These coupling means comprise the drive lug 213 described above. More specifically, the coupling between the handle 3 and the connecting piece 211 is obtained by insertion of this drive lug 213 in the groove 215 of the bar 4 which is integral with the handle 3 of the at least one cut-off device 2. Thus, the first detection means are designed to detect angular positions of said connecting piece 211 corresponding to the opening or closing positions of the handle 3. The connecting piece 211 can therefore occupy at least two representative positions respectively of an open position and a closed position of the handle 3, and a third position representative of the intermediate position of the handle when soldering the electrical contacts. In the embodiment shown in FIGS. 30 and 31, the first detection means are therefore designed to discern the position of the connecting piece 211 representative of the closure of the handle, with respect to its position representative of the position of opening of the joystick and at its third position representative of the intermediate position of the joystick.

The first detection means comprise a first sensor 241, in this case a non-contact position sensor or proximity sensor. In the embodiment shown in FIGS. 30 and 31, this first sensor 241 is a Hall effect sensor disposed on an electronic circuit 242, in this case a printed circuit, carrying the processing means 280, as well as all the means electronic operation of the remote control. However, any non-contact position detector available those skilled in the art could be used in place of this Hall effect sensor. The connecting piece 211 comprises, meanwhile, a first positioning element 243 eccentric with respect to the axis of rotation of said connecting piece and extending towards the first sensor 241. In the embodiment shown in the figures 30 and 31, this first positioning element 243 has the shape of a cylinder whose main axis extends parallel to the remote control axis. A permanent magnet, not visible, is disposed at the end of the first positioning element 243 vis-a-vis with the electronic circuit 242 carrying the first sensor 241 and the processing means 280. This permanent magnet is generally made of rare earth to allow the emission of a strong magnetic field. This magnet is often mounted inside the positioning element 243 and held in said element by unrepresented molded clips and support.

When the lever 3 drives the connecting piece 211 from the position representative of the closing of the handle to the position representative of the opening of said handle, the end of the first positioning member 243 carrying the permanent magnet moves to leave a position facing the sensor 241, which makes it possible to generate a first signal SD representative of the opening of the handle and the presence of an electrical fault.

The first detection means further comprise first electromechanical means 251 cooperating with the connecting piece 211, and in particular with a lateral protuberance 252 mounted on the first positioning element 243 of said connecting piece. These first electromechanical means 251 consist essentially of a switch provided with an actuating member 253 cooperating with the lateral protuberance 252 of the first positioning element 243.

When the connecting piece 211 is in an angular position representative of the closure of the handle 3, the lateral protuberance 252 presses on the actuating member 253, which allows the first electromechanical means to provide another signal SD representative of said closed position of the controller and therefore the absence of an electrical fault. When the connecting piece 211 is in an angular position representative of the opening of the handle 3, the lateral protuberance 252 more press the actuating member 253, and the other SD signal is representative of said open position of the joystick and therefore the presence of an electrical fault.

The electronic circuit 242 and the circuits of the first electromechanical means 251 are electrically isolated, that is to say that they have a galvanic separation. The first sensor 241 is used by the electronic circuit 242 to generate voltage signals

24 volts on remote signaling connectors housed in aperture 10 (Figure 2).

The first electromechanical means 251 are in direct connection with the remote signaling connectors 9 (FIG. 1) to generate 220 volts voltage signals. This makes it possible not to have a voltage of 220 volts on the electronic circuit 242. In this way, the isolation distances are reduced, which makes it possible to minimize the size of the electronic circuit and its components.

In the embodiment shown in FIGS. 30 and 31, the second detection means make it possible to obtain a signal OF representative of the closure of the electrical contacts of the at least one cutoff device 2 associated with the remote control device. More specifically, these second detection means are arranged to detect angular positions of the remote control shaft 23 which are directly related to the opening and closing states of the electrical contacts.

Indeed, in the at least one cutoff device 2 associated with the remote control device, the remote control shaft 23 is integral with a remote control mechanism of said cutoff device for actuating the movable contact 27. As described in FIG. In more detail in the following description, this remote control mechanism of the cut-off device 2 comprises a remote control lever 351 and drive means secured to both the remote control lever 351 and the support lever 317 carrying the movable contact 27. In addition, these drive means are arranged so that any rotation of the remote control lever 351 opposes the resistance exerted by a contact pressure spring. With this configuration, the displacement of the movable contact is directly related to the rotation of the remote control shaft 23. Thus, the detection of the state of the electrical contacts through this remote control shaft 23 is more direct and more Reliable if performed by means of the driving means 22 or the plunger 45 of the electromagnet 21 of the remote control device 1. As can be seen in FIG. 31, the second detection means comprise a second sensor 261, in this case a non-contact position sensor or proximity sensor. In this embodiment, the second sensor 261 is a Hall effect sensor disposed on the electronic circuit 242 carrying the processing means 280. However, any contactless position detector at the disposal of the person skilled in the art could have be used in place of the Hall effect sensor. As can be seen in FIG. 31, the remote control shaft 23 comprises, meanwhile, a second positioning element 263 eccentric with respect to the remote control axis and extending towards the second sensor 261. In the embodiment shown, this second positioning element 263 has the shape of a cylinder whose axis extends parallel to the remote control axis. A permanent magnet, not visible, is disposed at the end of the second positioning member 263 vis-a-vis with the electronic circuit 242 carrying the sensor 261 and the processing means 280. This magnet is generally made of rare earth and mounted in the second positioning element 263 in the same way as that of the first positioning element 243.

When the remote control shaft 23 moves from a position representative of the opening of the contacts to a position representative of the closing of said contacts, the end of the second positioning element 263 carrying the permanent magnet moves to be in contact with screw with the sensor 261, which generates a second OF signal representative of the closure of said contacts.

As can be seen in FIG. 31, the second detection means further comprise second electromechanical means 271 cooperating with the remote control shaft 23 via transmission means, in this case a flexible blade 272. These second electromechanical means 271 essentially consist of a switch provided with an actuating member 273 cooperating with the end of the flexible blade 272. When the remote control shaft passes into an angular position representative of the closure of the electrical contacts, the second positioning element 263 presses on the flexible blade 272, and the end of said blade in turn presses on the actuating member 273, which allows the second electromechanical means to provide another signal OF representative of closing said electrical contacts. The electronic circuit 242 and the circuits of the second electromechanical means 271 are electrically isolated, that is to say that they have a galvanic separation. The second sensor 261 is used by the electronic circuit 242 to generate 24 volt voltage signals on the remote signaling connectors housed in the aperture 10 (FIG. 2). The second electromechanical means 271 are in direct connection with the remote signaling connectors 9 (FIG. 1) for generating 220 volts voltage signals. This makes it possible not to have a voltage of 220 volts on the electronic circuit 242. In this way, the isolation distances are reduced, which makes it possible to minimize the size of the electronic circuit and its components.

In the embodiment shown, the detection means are compact and are made from elements having several functions. This makes them easy to integrate into a congested environment.

As shown in FIG. 32, the processing means 280 comprise a counter 281 connected to the second detection means 261 making it possible to count the number of commutations during a given time. A processing module 282 connected to this counter 281 makes it possible, when this number exceeds a predetermined limit corresponding to a start of heating of the remote control device, to send to the local display means 8 or to any other remote display means, a signal to indicate the presence of this heating.

In the embodiment shown, the local display means 8 are in the form of a lamp that can emit light of different colors, in this case red or green, and can light continuously or intermittently with different time intervals.

By way of example, when the electrical contacts 26, 27 of the at least one cut-off device 2 associated with the remote control device 1 are open and the lever is in its closed position, the lamp 8 emits a flashing green light. with long time intervals indicating that said contacts are ready to be closed via the remote control device 1. Following closure of these contacts via the remote control device 1, the lamp 8 emits a continuous green light . In the presence of an electrical fault or when the handle 3 is moved to its position the lamp 8 emits a flashing red light with average time intervals. A permanent red light signal is emitted in the case where the contacts are welded and the lever 3 is operated to its open position stopping in its intermediate position. Finally, in case of heating or overheating of the remote control device 1 after exceeding the limit of activation of the remote control, the lamp 8 emits a flashing red light with small time intervals.

Since the signaling of a state of closure of the electrical contacts is decoupled with respect to the signaling of an electrical fault, the risks of a misinterpretation of the information thus reported are reduced.

Cut-off device (electrical protection block)

The remote-controlled circuit-breaker shown in FIG. 33 and FIGS. 35 to 38 comprises, in the electrical protection block, at least one cut-off device 2. As can be seen in FIG. 35, this cut-off device 2 comprises, in a housing insulation 301, the fixed contact 26, the movable contact 27 carried by a contact arm 303, the control mechanism 25 and triggering means.

In FIG. 33 representing the kinematic chains of the breaking device 2, each component of the control mechanism 25 is represented by one or more solid lines referenced numerically, the envelope or the box is represented by a hatched rectangle, and the joints are represented by circles. The straight and curved arrows indicate, respectively, efforts and couples respectively.

With reference to FIGS. 33 and 35, the control mechanism 25 of the cut-off device 2 is designed to actuate the contact arm 303 whose free end carries the movable contact 27. The contact arm 303 can be directly actuated by the User A8, through the handle 3. An opening is formed in the front face of the housing 301 for the passage of the lever 3 pivotally mounted limited on an axis 312. The lever 3 is operable between a closed position in which contacts 26, 27 are open or closed by the remote control, and an open position corresponding to the separation of said contacts. The handle 3 is equipped with an internal base coupled to transmission means, in this case a transmission rod 313. A hinge 314 between the base of the handle 3 and the rod 313 is eccentric with respect to the fixed pivot axis 312 of said handle, so that said rod forms a toggle device.

The lever 3 is biased counterclockwise to the open position by a return spring A1. The fixed contact 26 is secured to the casing of the magnetic release 305. The contact arm 303 is fixed to a support lever 317 made of material insulation, articulated on a pivot 318 of a rotary plate 319. In the closed position of the contacts 26, 27, a contact pressure spring A3, inserted on the pivot 318 allows a small amplitude relative pivoting movement between the plate 319 and the support lever 317.

The contact arm 303 can also be directly actuated by the thermal type 304 and electromagnetic type triggering means 305 of a pole of the cut-off device, or other poles A9, AlO of the same cut-off device. A release lever 321 driven by a striker 316, A7 of the electromagnetic release 305, and a bimetallic strip 322, A5 of the thermal release 304, is pivotally mounted on an axis 323 carried by the plate 319 with a predetermined offset with respect to the pivot 318 of the support lever 317.

A breakable mechanical connection 325 is formed between the transmission rod 313 and the drive plate 319 of the contact arm 303. In the locked position, the link 325 allows the manual control of the control mechanism 25 by the lever 3. The movement of the release lever 321 to the triggered position under the action of the trigger causes the momentary rupture of the breakable mechanical link 325, causing the automatic triggering of the control mechanism 25, independently of the joystick. The trip lever is associated with a return spring A6, in this case a torsion spring, intended to ensure the automatic restoration of the breakable mechanical link 325 when the lever 3 is actuated to the open position, following a triggering the control mechanism 25 on default.

More specifically, the breakable mechanical link 325 comprises a hook 331 pivotably mounted on an axis 332 of the plate 319. Opposite the axis 332, the spout of the hook cooperates in the locked position of the breakable mechanical connection 325 with a notch 333 retaining located on the upper arm of the trip lever 321.

The transmission rod 313 is coupled to the hook 331 at a hinge point 336 that can move when triggered in a light 337 of the plate 319. The light 337 is blind or open, and is shaped in a sector, which can be circular or complex in shape, centered on the axis 332. The intermediate point of articulation

336 is located between the axis 332 and the spout of the hook 331. The breakable mechanical connection constitutes a reduction stage in the kinematic chain of the control mechanism 25, allowing a reduction of the triggering force from the magnetothermal release.

The bimetallic strip 322, A5 of the thermal trip unit 304 cooperates with the trip lever 321 by means of a rotary slide valve 341 with unidirectional transmission. The spool 341 is formed by an angled lever having one end freely coupled to the lower arm of the release lever 321 at an articulation point 342. A curved intermediate portion of the spool 341 rests on a boss 343 of the housing, so as to drive the latter to the triggered position when deflection to the right of the bimetal 322, A5 in the event of circulation of an overload current in the pole. During this thermal tripping phase, the spool 341 constitutes a rigid kinematic connection between the bimetallic strip 322, A5 and the triggering lever 321. The absence of parasitic friction between the spool 341 and the triggering lever 321 makes it possible to significantly reduce tripping force transmitted by bimetallic strip 322, A5.

The control mechanism 25 of the cut-off device further comprises a remote control mechanism acting on the support lever. This remote control mechanism is shown separately from the rest of the control mechanism in Figure 34.

As can be seen in FIGS. 34 and 35, the remote control mechanism is equipped with a remote control lever 351 rotatably mounted about a remote control axis 352 substantially perpendicular to the main faces of the case 301, said remote control lever being intended for be coupled to a remote control device. The housing comprises on at least one of these main faces a bearing 353 intended to receive the shaft remote control 23 of the remote control device. This bearing makes it possible to center the remote control shaft 23 on the remote control shaft 352 without hindering its rotation.

With reference to FIGS. 34 and 35, the remote control lever 351 comprises an opening

354 for receiving the remote control shaft 23, so as to couple said remote control shaft 23 to said lever. Thus the remote control lever 351 is rotated by the remote control shaft 23. This opening 354, and the remote control shaft 23, advantageously have a cruciform section. This makes it possible to obtain a better coupling between these two elements. Rotors can advantageously be used on the branches of the cruciform section to reinforce the coupling between the remote control shaft 23 and the remote control lever 351.

With this configuration, the transmission via the remote control shaft is rigid along said shaft and therefore for all the poles, that is to say, cut-off devices 2. This allows ensure a simultaneous control of all the poles, that is to say, all the cut-off devices 2. This allows, in addition, to ensure a sufficient opening distance between the contacts and for each pole.

The opening 354 for receiving the remote control shaft 23 can be adjusted to the outside diameter of said shaft in order to guarantee a minimum pressure of the gases generated by the electric arc, to limit any leakage of said gases into the neighboring cut-off devices, and to avoid the initiation of an electric arc between different cut-off devices.

As shown in FIGS. 34 and 35, the remote control mechanism comprises drive means integral with the remote control lever 351 and the support lever 317. In other words, each element of the drive means is integral with either the remote control lever 351 or the support lever 317, and said elements cooperate with each other to drive said support lever through said remote control lever. These drive means comprise a finger 357 integral with the remote control lever 351 cooperating with a ramp 358 of the support lever 317. More specifically, the finger 357 is equipped, on a free end, with a contact surface cooperating with the ramp 358. The ramp 358 is, for its part, disposed along an arm 359 of the support lever 317. Thus, the drive means of the remote control mechanism are arranged to that any rotation of the remote control lever opposes the resistance exerted by the contact pressure spring (s) A3 visible (s) in Figure 33.

This arrangement gives the remote control mechanism a monostable character, that is to say that the mechanism has a single stable position corresponding in this case to the closed position of the contacts. The mechanical forces for keeping the contacts 26, 27 of the cut-off device 2 in an open position correspond to those exerted by the contact pressure spring A3 or the contact pressure springs in the case of a plurality of poles or 2. These forces are therefore fully transmitted through the remote control device 1. Moreover, the monostable nature of the remote control mechanism simplifies the internal architecture of the cut-off device and the remote-controlled circuit breaker incorporating this device. or this plurality of cut-off devices. This helps make the cinematic remote control chain more enduring.

When the handle 3 is in an open position, the support lever 317 is in a position as shown in Figs. 36A and 36B. In this position, any rotation of the remote control shaft 23 pivots the remote control lever 351 in the vacuum, that is to say that the ramp 358 of the support lever 317 is sufficiently far away from the finger 357 that said finger can not actuate the support lever 317. With the manual opening command via the handle 3, the opening angle of the movable contact is generally greater than the opening angle obtained during a remote opening.

In this way we obtain a sufficient isolation distance between the separable contacts, to obtain a sectioning and to ensure the safety of operators when said separable contacts are open. In this opening position of the handle 3, the remote control mechanism can not act on the support lever 317 and the contacts 26, 27 remain open. To activate the remote control mechanism, it is therefore necessary to position the handle 3 in its closed position.

When the handle 3 is in a closed position, the support lever 317 is in a position as shown in Figs. 37A and 37B. In this position, the ramp 358 of the support lever 317 is closer to the finger 357 secured to said remote control lever 351. Thus, any rotation of the remote control shaft 23 in the opposite direction of the clockwise allows the finger 357 to cooperate with the ramp 358 of the support lever 317 and to drive said support lever into an open position of the contacts shown in Figures 38A and 38B. The actuation of the remote control device is opposed to the pressure exerted by the contact pressure springs of each pole. This remotely controlled opening of the contacts is maintained by means of the remote control device, and in particular by the drive mechanism of this remote control device which is designed to accommodate a mechanical force at least equal to the pressure exerted by the pressure springs. A3 contact of each cutoff device 2 or each pole.

Claims

An insulating housing remote control device (41) having at least one main face (141) for controlling at least one cut-off device (2) disposed against said main face, said remote control device comprising an electromechanical actuator (21) equipped a moving part (45), driving means

(22) cooperating with said movable part, and a rotary control shaft (23) coupled to said drive means for actuating the at least one cut-off device (2), said remote control shaft (23) passing through said face main body (141) in a direction substantially perpendicular to said main face, characterized in that said drive means (22) comprise a substantially mechanical bistable drive mechanism (137) coupled to said movable portion (45) of the actuator, said bistable drive mechanism (137) comprising movable elements displaceable in translation along a single drive axis (47) and movable in rotation about said axis.

2. Device according to claim 1, characterized in that the movable part (45) of the electromechanical actuator (21) is a plunger displaceable in translation along an actuation axis (46) substantially parallel to the axis of drive (47) of the bistable drive mechanism (137).

3. Device according to claim 2, characterized in that the actuating axis (46) of the plunger core (45) is substantially coincident with the drive axis (47) of the bistable drive mechanism (137).

4. Device according to one of claims 1 to 3, characterized in that the bistable drive mechanism (137) comprises a pusher (151) acting on a control arm (152), said pusher being movable in translation between minus two stable axial positions (P1, P2).

5. Device according to claim 4, characterized in that the pusher (151) is held in the stable axial positions (P1, P2) by a restoring force exerted through the remote control shaft (23).

6. Device according to one of claims 4 or 5, characterized in that the movable elements of the bistable drive mechanism comprise an axial transmission cam (161) cooperating with the movable part (45) and a cam follower (171). ) coupled to the pusher, said cam and said cam follower respectively having a first and a second cam surface (167, 177) adapted to translate an axial translation of the cam (161) to the cam follower (171) in rotation said cam follower.

7. Device according to claim 6, characterized in that the cam follower (171) is integral with the pusher (151).

8. Device according to one of claims 6 or 7, characterized in that the bistable drive mechanism (137) comprises a cam body (162) for housing and guiding the cam follower (171) in translation and in rotation .

9. Device according to claim 8, characterized in that the cam body (162) comprises along the drive shaft (47):

a first portion (163) having on an inner surface at least one axial groove (164) for receiving at least one radial projection (175) of the cam follower (171) for hindering the rotation of said cam follower when said follower is in said first part, and

a second portion (169) having an enlarged passage section with respect to a narrower passage section of the first portion (163) for allowing rotation of said cam follower (171) when the latter is in said second portion.

10. Device according to one of claims 6 to 9, characterized in that the cam (161) and the cam follower (171) are substantially identical parts.

11. Device according to any one of claims 1 to 10, characterized in that the electromechanical actuator (21) is equipped with a reduced displacement portion (51), and an excitation coil, the movable portion (45) being displaceable in translation along an actuating axis (46) substantially perpendicular to a bearing face (55) of said reduced displacement portion to be deployed through a through hole (53) of said bearing face, in that the drive means cooperate with said movable part to drive in translation a movable transmission element (151) intended to be coupled to a movable contact (27). ) of said cutoff device (2), said drive means being adapted to move the movable transmission element between a first and a second stable axial position (P1, P2) respectively corresponding to the closing and opening of said contact mobile (27), and in that the insulating housing (41) encloses damping means (57) for damping an impact of said moving part on said reduced displacement part when said movable part is moved in a positive position. we deployed.

12. Device according to claim 11, characterized in that the damping means are disposed between first support means (58) of the housing (41) and the bearing face (55) of the reduced displacement portion (51) to allow a displacement of said reduced displacement portion along the actuating axis (46) by crushing said damping means (57) so that said displacement of the reduced displacement portion contributes to the driving of the movable member; transmission (151) from one stable axial position to the other.

13. Device according to any one of claims 1 to 12, characterized in that it comprises a device for locking the remote control, the cut-off device (2) being equipped with a handle (3) operable between a position d opening and closing position of electrical contacts and a trip lever for opening said electrical contacts due to an electrical fault, said locking device comprising a retractable part (7) for blocking the closing of said electrical contacts when the retractable part is in an extended position, said remote control locking device further comprising an actuating lever (201) to be coupled to said trigger lever, said actuating lever (201) cooperating with said retractable part (7) to order triggering the at least one cut-off device when the retractable part (7) is maneuvered to its deployed position.

14. Device according to any one of claims 1 to 13, characterized in that it comprises means for signaling states and / or defects of the at least one switching device (2), said signaling means comprising first detecting means (241, 251) for detecting positions of an operating handle (3), said remote control device having second detecting means (261, 271) arranged to detect the position of the remote control shaft (23) rotatably mounted about a remote control axis substantially perpendicular to said main face (141), said shaft for actuating electrical contacts (26, 27) of the at least one cut-off device (2).

15. Remote controlled circuit breaker comprising a remote control device equipped with a remote control shaft (23) coupled to at least one cut-off device (2), characterized in that said remote control device is a device according to one of the preceding claims, said remote control device being coupled to said cutoff device through the remote control shaft.

26361 M