FR2940518A1 - CONTROL MECHANISM FOR REMOTE CONTROLABLE CUTTING DEVICE, CUTTING DEVICE AND REMOTE CONTROL CIRCUIT BREAKER EQUIPPED WITH SUCH A MECHANISM - Google Patents

Abstract

A control mechanism (25) with an insulating housing (301) equipped with two main faces (5), said mechanism comprising a handle (3), a support lever (317), a contact pressure spring, a breakable mechanical connection, a release lever, and a remote control mechanism acting on said support lever equipped with a remote control lever (351) rotatably mounted about a remote control axis (352) substantially perpendicular to the main faces to be coupled to a remote control device; remote control (1). The mechanism (25) comprises driving means secured to the remote control lever (351) and the support lever (317), said drive means being arranged so that any rotation of the remote control lever (351) is directly opposed to the resistance exerted by the contact pressure spring. A cutoff device (1) and a remotely controlled circuit breaker equipped with such a mechanism.

Description

TECHNICAL FIELD OF THE INVENTION The invention relates to the field of control mechanisms for cut-off devices comprising, in addition to the mechanism of the invention, a control mechanism for a remote control device, a switching device and a remote control circuit breaker. manual actuation and trigger mechanism, a remote control mechanism. The control mechanism which is the subject of the invention relates more particularly to the remote control means arranged in the breaking device and acting on at least one moving contact of said device.

The invention also falls within the field of cut-off devices and remote-controlled circuit breakers equipped with such a control mechanism. The invention relates in particular to a mechanism for controlling a remotely controllable electrical cut-off device with an insulating housing having two substantially parallel main faces and enclosing a fixed contact, a movable contact carried by a contact arm and triggering means, said mechanism control device comprising: - an operating handle pivotally mounted on said housing coupled to transmission means forming a toggle joint, - a support lever of said contact arm articulated on a pivot, - a contact pressure spring for holding said support lever in a a closing position of said contacts, - a breakable mechanical connection arranged between said support lever and said transmission means, - a release lever controlled by said triggering means to cause in the event of electrical fault the rupture of said breakable mechanical link 25 and cause an automatic triggering of said m control mechanism independently from the handle, and - a remote control mechanism acting on said lever support equipped with a rotatably mounted remote control lever about a substantially perpendicular axis to the main faces of remote control to be coupled to a remote control device. STATE OF THE ART Remote controlled circuit breakers combining at least one electrical cut-off device with a remote control device for remotely controlling the closing and opening of electrical contacts of said cut-off device are known. These remotely controlled circuit breakers are often used to centralize controls, such as controlling a lighting circuit or controlling programmable logic controllers of an electric machine. The control mechanism of the at least one cut-off device of these remote control circuit breakers generally comprise a remote control mechanism dedicated to the remote control of the opening and closing of the contacts. French patent application FR 2,535,520 describes such a remote-controlled circuit breaker whose cut-off device comprises a control mechanism associating a remote control mechanism with a trigger mechanism, the latter acting on the same movable contact independently. The remote control mechanism described in this patent application comprises a pivoting rocker cooperating with a spring, which itself cooperates with a support lever carrying a movable contact. The remote control mechanism is arranged so that, when actuated, the action line of the spring moves to cross a dead point between two stable positions of opening and closing of the movable contact. A disadvantage of the control mechanism of the cutting device of the prior art is that it has a complex and cumbersome remote control mechanism.

DISCLOSURE OF THE INVENTION The invention aims to remedy the technical problems of the control mechanisms for a remote control device of the prior art by proposing a control mechanism of a remote-controlled electrical cut-out device with an insulating casing having two main faces substantially parallel and containing a fixed contact, a movable contact carried by a contact arm and triggering means, said control mechanism comprising: - an operating lever pivotally mounted on said housing coupled to transmission means forming a toggle, - a support lever of said articulated contact arm on a pivot, - a contact pressure spring for holding said support lever in a closed position of said contacts, - a breakable mechanical connection arranged between said support lever and said transmission means, - a lever triggered by said triggering means p in the event of an electrical fault, to provoke the breaking of said breakable mechanical link and to cause an automatic triggering of said control mechanism independently of the lever, and - a remote control mechanism acting on said support lever equipped with a remote control lever rotatably mounted around a remote control shaft substantially perpendicular to the main faces intended to be coupled to a remote control device. The control mechanism according to the invention is characterized in that the remote control mechanism comprises drive means integral with said remote control lever and said remote control device. support lever, said drive means being arranged so that any rotation of the remote control lever directly opposes the resistance exerted by the contact pressure spring. Preferably, the drive means comprise a finger secured to the remote control lever cooperating with a ramp of the support lever.

Preferably, the remote control lever comprises an opening for inserting a remote control shaft of the remote control device according to the remote control axis, for rotatably coupling said remote control lever to said remote control shaft. Advantageously, the opening has a cruciform section.

Preferably, at least one side face of the housing comprises a bearing for receiving a remote control shaft of the remote control device. According to one embodiment, the control mechanism comprises a platen hinged to the pivot of the support lever, the contact pressure spring being arranged to exert a pressure between said platen and said support lever, and to allow a relative low pivoting movement. amplitude between said platen and said support lever. Advantageously, the breakable mechanical link is formed by a catch of the release lever cooperating with a hook pivotally mounted on an axis of the plate, and in that the transmission means are coupled to said hook at an intermediate point of articulation located between said axis and a spout of said hook.

The invention also relates to an insulating housing cut-off device having two substantially parallel main faces, said housing enclosing a movable contact carried by a contact arm and a control mechanism acting on said movable contact, said control mechanism comprising a control mechanism. remote control intended to be coupled to a remote control device, said cutoff device being characterized in that said control mechanism is a mechanism as described above, the remote control mechanism of the control mechanism comprising a remote control lever rotatably mounted around a remote control axis substantially perpendicular to said main faces. The invention also relates to a remote control circuit breaker comprising a remote control device and at least one cut-off device, said cut-off device comprising a control mechanism equipped with a remote control mechanism, said remote-controlled circuit breaker being characterized in that said control is a mechanism as described above, said remote control mechanism being coupled to said remote control device. Advantageously, said remote control mechanism is coupled to said remote control device through a remote control shaft. Advantageously, the remote control shaft has a cruciform cross section. 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 represented in the appended 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 drive means during the transition from a first stable axial position to a second stable axial position of the mobile transmission element. . 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. Fig. 17 is a perspective view of a cam or cam follower of a bistable drive mechanism according to an 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 cross-sectional and perspective views, respectively, of the bistable drive mechanism at different stages of operation. Figs. 19C-25C correspond to sections developed at a circumference C8 (see Fig. 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. FIG. 27 is a perspective view showing a connecting piece and a retractable part of the remote control locking device, as well as means for driving 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 Figures 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 With reference to FIGS. 1 to 3, the remote-controlled circuit breaker comprises a remote control unit 1 equipped with a remote control device associated with four unipolar cut-off 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 cut-off devices 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 1 l button or remotely from 220 volt control terminals or connectors. 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 part 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 control mechanism 25 can be actuated by means of the operating 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 shown 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 moving part, in this case a plunger core 45 displaceable in translation along an actuating axis 46. The electromagnet is actuated by an excitation current or control signal flowing in a excitation coil not shown and for deploying the plunger core and maintain it in this deployed position 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 casing 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 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 transmission element 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 second stable axial position of the mobile transmission element 151 are illustrated respectively in Figures 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 movable contact 27. In the embodiment shown in Figures 6A and 6B, the housing 41 contains damping means 57 disposed between the first support means 58 of said housing and the bearing surface 55 of the yoke 51 to allow a reduced displacement said yoke 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 includes 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 second means The supports thus make 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 movable transmission member, said limit 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 by means of an axial transmission cam 161 in a cam member 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 41 in its deployed position allow a drive of the movable transmission element 151 beyond the limit axial 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 mobile transmission element 151 is in the first stable axial position P1 as shown in FIG. 7A, said position corresponding to the closing of the moving contact 27. The plunger 45 is, in turn, in its retracted position. . 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 follower 151 moves in opposite directions 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 limit position 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 FIGS. , the actuator 21 comprises a yoke 51 of ferromagnetic material. Damping 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 joints 72 of elastic material disposed between, on one side the yoke 51 or the support means of a not shown housing, and on the other side the detachable portion 71 The latter is mounted movable relative to the yoke 51, so that the impact of the plunger 45 on the impact zone arranged on the first bearing face 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 to this recall 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 impacts the impact zone, the detachable portion 81 is temporarily moved to a detached position as shown in FIG. 11. In the embodiments shown in the 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. Furthermore, in this embodiment, the insertion of the coils can take place, before or after the introduction of the detachable portion 81. On the contrary, in the embodiment shown in FIGS. 12A and 12B, the portion detachable 91 damping means 90 has a dimension along the axis of actuation greater than the thickness of the bearing face 60. This configuration allows to arrange in a central portion of the cylinder head 51 an impact zone having a V-shaped profile for minimizing 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 has three impact zones 96 disposed on the end faces of the branches of the E. The damping means comprise detachable portions 97 formed in portions of the fixed or reduced displacement portion 93 linking the branches of 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 ensuring the 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 character 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 Figures 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 type shot. By electromagnet of the monostable type, it is meant that the plunger core 45 of the electromagnet changes from a retracted position to the deployed position by the circulation of an excitation current, and from 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. The 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 power consumption and any electrical noise associated with the circulation of the excitation current in the coil of the electromagnet 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 movable contact 27 with the aid 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 rotate the remote control shaft 23. The bistable drive mechanism 137 comprises movable elements including the pusher or movable transmission element 151. A restoring force acting on the pusher 151 can be obtained via the remote control shaft 23, or more precisely by 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 via the remote control shaft 23. These return means are generally deported outside the device remote control. In this case, these return means are part of the at least one cut-off 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 Figures 5 to 7, and in more detail in Figures 16 to 18, the bistable drive mechanism 137 comprises an axial transmission cam 161 cooperating with the plunger core 45 of the electromagnet 21. Axially transmitting cam means a cam movable in translation for which the translation movement is along an axis of translation substantially coinciding with the axis 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 cam or barrel 162. comprising 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 translational 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 to hinder 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 parts. 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 the 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 thus just shows the two parts 163, 169 of the cam body 162, and corresponds to a portion forming with the tubular casing 184 a unit 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 for providing a biasing force against the axial translation of the cam 161 to 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 the second portion 163, 169 of the cam body 162. This third cam surface 192 of the cam body 162 is intended to cooperate with the second cam surface 177 of the cam body 162. follower 171, when 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 an annular portion of the end faces of the cam 161 and the cam follower 171 carrying the first and second cam surfaces 167, 177. In particular, the fourth and fifth the fifth camming surface 191, 194 are in the extension respectively of the first and the second camming surfaces 167, 177. In other words, the first and the fourth camming surfaces 167, 191, as well as the second and the fifth cam surface 177, 194 has a radial continuity, which facilitates the manufacture of the cam and the 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 relative 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 ALPHA2 greater than 70 degrees, this angle being defined in the same way with respect to the same perpendicular plane to the drive shaft 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 ALPHA2 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 instant 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, or greater than 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 Figs. 19 to 25. When the plunger 45 is in a retracted position, the cam follower 171 is held by the pressure spring of contact A3 (FIG. 33) in the first stable axial position P1. This first stable axial position of the cam follower 171 is shown schematically in Figs. 19A-19C. In a first step, the cam 161, driven by the plunger core 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. 20C. 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-21C, the translational movement of the cam 161 which urges the cam follower 171 causes a first rotation ROT1 of said cam follower by sliding of the second cam surface 177 on the first surface of the cam. cam 167, and the fifth cam surface 194 on the fourth cam surface 191. This first rotation ROT1 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 surfaces of the cam. cam follower 177, 194. In addition, this first rotation ROT1 was 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 body of the cam. cam. This first rotation ROT1 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 ROT1, 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, come to rest on the shoulder of said cam body by preventing any displacement 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 still not aligned with the axial grooves 164 of the cam body 162. This second stable axial position of the cam follower 171 is shown schematically on the Figures 23A to 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-19C to the second stable axial position P2 shown in Figs. 23A-23C, in a first step the plunger 45 is expanded to drive the cam follower 171 and the pusher 151 secured to 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 follower cam 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 pass from the second stable axial position P2 to the first P1, the process is substantially the same. In a first step, the plunger 45 is expanded to drive the cam follower 171 and the pusher 151 integral with said follower in a third rotation ROT3 by sliding the second cam surface 177 on the first one 167, and the fifth surface of cam 194 on the fourth 191. This third rotation is enabled by the fact that the first and second cam surfaces 167, 177, as well as the fourth and fifth cam surfaces 191, 194, are not initially in a position maximum contact. 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 Figures 25A-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 translated into 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 ROT1, ROT2 on the one hand, and between the third and 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 P1, 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, the maintaining in the stable axial positions P1, P2 of the cam follower 171 and the pusher 151 to which it is coupled does not require an excitation current, which makes it possible to optimize the energy consumption and to minimize the defects related to the circulation of an excitation current. Furthermore, the passage between the first and the second stable axial position P1, P2, in one direction and the other, is done through 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 control circuit breaker comprises a remote control locking device or lockout device that can be operated from the retractable part 7. In this case, the retractable part 7 is a slide mounted movably 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 trigger 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 by via a drive 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 the retractable part 7 to move 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 movement of the lug 204, the actuating lever 201 is rotated so as to move the trigger tab 202 in a circular arc following the light 6 and causing the trigger lever of the 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 to stop the operation of the retractable part 7 to its extended 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 moved 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 lever 3 of the at least one cut-off device 2, and when the retractable part 7 is moved towards its deployed position, the pin 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 shifters 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 manipulated towards 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 operate the retractable part 7 to its extended position. In addition, the remote shaft 23 is in an angular position for which the lug 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 which blocks the maneuvering of the workpiece. 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 cut-off device systematically prevents the operation of the retractable part 7 in its deployed position and thus the locking of said remote control device by the insertion of the handle of a padlock in the opening 200. for example, considering the embodiment of Figure 1 having four cut-off devices 2, if the fourth cut-off device has a contact welding problem, it may be possible to opening the contacts of the first cut-off device which is attached to the remote control device, by applying a force on the strip 4 at said first cut-off device and partially disconnecting said strip with respect to all the knobs 3. In this case , the connecting piece 211 is no longer in a position hindering the translation of the pin 218, and it is only the angular position of the remote control shaft 23 which blocks the operation of the retractable piece 7 in its position deployed in the case of the lug 206 and the protrusion 209. In all cases of welding a pair of contacts, the retractable part 7 can be maneuvered to its first intermediate position, which makes it possible to trigger the other breaking 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 20 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 lug 218. Thus, in the case of welding of the electrical contacts, it is not possible to operate 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 electrical states and 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 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 an attempt to open said contacts via the remote control device 1, or via the handle 3, or to 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 to 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 3, the lateral protuberance 252 is pressed on the actuating member 253, which allows the first electromechanical means to provide another SD signal representative of said closed position of the joystick and therefore the absence of a defect electric. When the connecting piece 211 is in an angular position representative of the opening of the lever 3, the lateral protuberance 252 no longer presses on the actuating member 253, and the other signal SD is representative of said position of opening 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 24 volt voltage signals on the remote signaling connectors housed in the aperture 10 (FIG. 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 that if it was performed through the drive means 22 or the plunger 45 of the electromagnet 21 of the remote control device 1. As can be seen in Figure 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 closure of said contacts, the end of the second positioning element 263 carrying the permanent magnet moves to be in facing relation with the sensor 261, which makes it possible to generate a second signal OF 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 crowded 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 20 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 open 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. 2 comprises, in an insulating housing 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 lever 3 is equipped with an internal base coupled to transmission means, in this case a transmission rod 313. An articulation 314 between the base of the lever 3 and the rod 313 is eccentric with respect to the fixed pivot axis 312 of said handle, so that said link 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 trigger means 305 of a pole of the cut-off device, or other poles A9, A10 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 controller 3. The movement of the release lever 321 to the triggered position under the action of the trigger causes the momentary break 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 connection 325 comprises a hook 331 pivotally mounted on an axis 332 of the plate 319. Opposite the axis 332, the hook spout cooperates in the locked position of the breakable mechanical connection 325 with a notch 333 retaining located on the upper arm of the release lever 321. The transmission rod 313 is coupled to the hook 331 at a hinge point 336 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 may be circular or of complex shape, centered on the axis 332. The intermediate hinge point 336 is situated 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 magneto trigger thermal.

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 bimetallic strip 322, A5 in case 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 for receiving the remote control shaft 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. Referring to Figures 34 and 35, the remote control lever 351 includes 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. all along said shaft and therefore for all the poles, that is to say, cut-off devices 2. This ensures simultaneous control of all the poles, that is to say of all 2. This allows, in addition, to ensure a sufficient opening distance between the contacts and identical 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 so that any rotation of the remote control lever opposes the resistance. exerted by the contact pressure spring (s) A3 visible in FIG. 33. This arrangement gives the remote control mechanism a monostable character, ie the mechanism comprises a single stable position corresponding to in this case at 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 integral with said remote control lever 351. Thus, any rotation of the remote control shaft 23 in the counterclockwise direction allows the finger 357 to cooperating with the ramp 358 of the support lever 317 and driving 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 (11)

CLAIMS 1. Control mechanism (25) of a remotely controllable electric cut-off device (2) with an insulating housing (301) having two substantially parallel main faces (5) and enclosing a fixed contact (26), a movable contact (27). ) carried by a contact arm and triggering means (304, 305), said control mechanism comprising: an operating lever (3) pivotally mounted on said housing coupled to transmission means (313) forming a toggle joint, a support lever (317) of said articulated contact arm on a pivot (318), a contact pressure spring (A3) for holding said support lever in a closed position of said contacts, a breakable mechanical connection (325) arranged between said lever support and said transmission means, a trip lever (321) controlled by said triggering means (304, 305) to cause in the event of an electrical fault the breakage of said brisab mechanical linkage and causing an automatic triggering of said control mechanism independently of the joystick, and a remote control mechanism acting on said support lever equipped with a remote control lever (351) rotatably mounted about a remote control axis (352) substantially perpendicular to the main faces intended to be coupled to a remote control device (1), characterized in that said remote control mechanism comprises drive means integral with said remote control lever (351) and said support lever (317), said drive means being arranged so that any rotation of the remote control lever (351) directly opposes the resistance exerted by the contact pressure spring (A3). 2. Device according to claim 1, characterized in that the drive means comprise a finger (357) integral with the remote control lever (351) cooperating with a ramp (358) of the support lever (317). 47 3. Control mechanism according to one of claims 1 or 2, characterized in that the remote control lever (351) comprises an opening (354) for inserting a remote control shaft (23) of the remote control device (1) according to the remote control shaft (352) for rotatably coupling said remote control lever to said remote control shaft. 4. Control mechanism according to claim 3, characterized in that the opening (354) has a cruciform section. 5. Control mechanism according to one of claims 1 to 4, characterized in that at least one side face of the housing comprises a bearing (353) for receiving a remote control shaft (23) of the remote control device (1) . 6. Control mechanism according to one of claims 1 to 5, characterized in that it comprises a plate (319) articulated on the pivot (318) of the support lever (317), the contact pressure spring (A3) being arranged to exert a pressure between said platen and said support lever, and allow a small amplitude relative pivoting movement between said platen and said support lever. 7. Control mechanism according to claim 6, characterized in that the breakable mechanical connection (325) is formed by a detent (333) of the release lever (321) cooperating with a hook (331) pivotally mounted on a axis (332) of the plate (319), and in that the transmission means (313) are coupled to said hook at an intermediate point of articulation located between said axis and a spout of said hook. 8. insulating box cutoff device (301) having two substantially parallel main faces (5), said housing enclosing a movable contact (27) carried by a contact arm and a control mechanism (25) acting on said movable contact, said control mechanism comprising a remote control mechanism for coupling to a remote control device (1), characterized in that said control mechanism is a mechanism according to one of the preceding claims, the remote control mechanism of the control mechanism comprising a remote control lever (351) rotatably mounted about a remote control axis (352) substantially perpendicular to said main faces. 9. Remote controlled circuit breaker comprising a remote control device (1) and at least one cut-off device (2), said cut-off device comprising a control mechanism (25) equipped with a remote control mechanism, characterized in that said control is a mechanism according to one of claims 1 to 7, said remote control mechanism being coupled to said remote control device (1). 10. remote-controlled circuit breaker according to claim 9, characterized in that said remote control mechanism is coupled to said remote control device (1) through a remote control shaft (23). Remote-controlled circuit breaker according to claim 10, characterized in that the remote control shaft (23) has a cruciform cross-section.