CONTROL MECHANISM FOR AN ELECTRICAL SWITCHING DEVICE

Description

Technical field

[0001] The present invention relates to the field of current cut-off devices for a medium voltage electrical distribution apparatus, i.e. a voltage between 1 kV and 52 kV. The invention relates more particularly to a mechanism for controlling the closing and opening of such a current cut-off device. The electrical apparatus may be, for example, a switch. The electrical apparatus may also be a circuit breaker or a disconnector. Prior art

[0002] A medium voltage electrical device, such as a switch, includes a moving contact for each phase of the network. When the current is interrupted, the moving contacts are moved away from the fixed contacts placed opposite the moving contacts, so that the current is cut. In order to close the circuit to allow the electric current to pass, a control mechanism, such as that described in document FR 3 089 049 A1, is used to trigger the movement of the moving contacts. This movement of the moving contacts must be carried out in a few milliseconds at most, in order to avoid the creation of an electric arc when closing the circuit, as well as when opening the circuit.To obtain the contact movement speed corresponding to these movement times, the opening and closing mechanism includes springs which are stressed in an arming phase, then released in order to provide the energy necessary to move the moving elements.

[0003] The mechanical forces involved when moving the various moving parts of the mechanism can cause wear on the mechanism when opening and closing, which is detrimental to the lifespan of the electrical device.

[0004] It is therefore desirable to have a closing and opening control mechanism for a current cut-off device with improved mechanical reliability and an increased service life. Summary

[0005] To this end, the invention provides a mechanism for controlling the closing and opening of a current cut-off device, the mechanism comprising: a cocking lever, a cocking shaft pivotally connected to a frame, a first elastic member comprising a closing spiral spring comprising a central end secured to the cocking shaft and a peripheral end secured to a control crank connected to the current cut-off device, a cocking disc, integral with the cocking shaft, movable between a first position called the rest position and a second position called the cocking position, a loading pawl, pivotally connected to the cocking disc, the loading pawl being able to move from a first position called the drive position, in which the cocking lever drives the cocking disc via the loading pawl, to a second position called the free position, in which the cocking lever is free to rotate relative to the cocking disc, in which a rotation of the cocking lever in a first direction of rotation called the cocking direction moves the cocking disc from the first position to the second position by constraining the first elastic member,a holding stop configured to hold the cocking disc once the cocking disc has reached the second position and the torque applied to the cocking disc by the cocking lever becomes less than the torque provided by the first elastic member, a movable hooking device between a first position in which the control crank is held stationary and a second position in which the control crank can move under the action of the closing spiral spring, a closing lever, pivotally connected relative to the frame, configured to move the hooking device from the first position to the second position and thus cause the closing of the power cut-off device, a second elastic member configured to move the loading pawl from the drive position to the free position when the cocking disc is held by the holding stop, , wherein the loading pawl is configured to move the closing lever from the first position to the second position when the loading pawl moves from the drive position to the free position, so as to cause the current cut-off device to close.

[0006] When the cocking lever has rotated sufficiently, the cocking disc bears against the holding stop. The force applied by the first elastic member is thus taken up by the holding stop. The force exerted by the cocking lever on the loading pawl therefore decreases until it is practically zero, since the tension of the first elastic member is taken up by the holding stop. The force exerted by the second elastic member on the loading pawl then becomes greater than the holding force exerted by the cocking lever, which causes the loading pawl to pivot relative to the cocking disc and pivots the closing lever. The closing lever moves the hooking device of the control crank, and releases this control crank, which moves under the action of the closing spring.Moving the operating crank causes the moving electrical contacts of the current-cutting device to rotate. The electrical circuit is thus closed and allows current to flow into the electrical device. Since the arming disc is fixed and in contact with the holding stop when the current-cutting device is triggered to close, there are no mechanical shocks between the arming disc and the holding stop during the closing phase. Stress on the moving parts is reduced, increasing their longevity. The durability of the operating mechanism is improved.

[0007] The features listed in the following paragraphs can be implemented independently of each other or in any technically possible combination:

[0008] The frame is a frame of the control mechanism of the power cut-off device.

[0009] The cocking disc and the cocking shaft form a rigid assembly.

[0010] The assembly of the cocking disc and the cocking shaft is movable between a first position called the rest position and a second position called the cocking position.

[0011] The first elastic member further comprises an opening spiral spring comprising a central end secured to the cocking shaft and a peripheral end secured to the frame.

[0012] The opening spiral spring and the closing spiral spring are both elastically constrained when the rotation of the cocking lever moves the cocking disc from the first position, called the rest position, to the second position, called the cocking position.

[0013] The holding stop is configured to hold the cocking disc after the cocking disc has reached the second position and the torque applied to the cocking disc by the cocking lever becomes less than the torque provided by the opening spiral spring and the closing spiral spring.

[0014] The closing lever can move from a first position called the rest position, in which the latching device holds the control crank, so that the electric current does not flow in the current cut-off device, to a second position called the closing position, in which the latching device releases the control crank, so that the current cut-off device is put in a position in which the electric current can flow in the current cut-off device.

[0015] The device for hooking the closing and opening control mechanism of a current cut-off device comprises a rocker pivotally connected to the frame, the rocker being movable between a position for holding the control crank and a position for releasing the control crank, and the rocker is connected to the closing lever by a connecting rod.

[0016] THE control mechanism includes a closing disc secured to the control crank and pivotally connected to the cocking shaft.

[0017] The closing spiral spring comprises a central end secured to the cocking shaft and a peripheral end secured to the control crank.

[0018] The closing disc includes a retaining roller.

[0019] The hooking device comprises an activation lever capable of rotating around an axis.

[0020] The activation lever is configured to selectively hold the closure disc in position against the effect of the closure spiral spring or release the closure disc so as to allow its rotation under the effect of the closure spiral spring.

[0021] For this, a first end of the activation lever is configured to be in contact with the closing disc and a second end of the activation lever is configured to be in contact with the rocker.

[0022] According to one aspect of the control mechanism, the loading pawl includes a first thrust zone configured to constrain the second elastic member when the cocking disc moves from the first position to the second position.

[0023] The second elastic member can thus exert sufficient force to pivot the loading pawl once the cocking disc is held by the holding stop.

[0024] The first thrust zone is distant from the second elastic member when the arming disc is in the first position called the rest position.

[0025] The first thrust zone is distant from the second elastic member over a first part of the movement path of the cocking disc from the first position called the rest position to the second position called the cocking position.

[0026] According to another aspect of the control mechanism, the loading pawl includes a second thrust zone configured to drive the closing lever when the loading pawl moves from the drive position to the free position.

[0027] The first thrust zone is formed by a first portion of a hook projecting from a body of the loading pawl.

[0028] The second thrust zone is formed by a second portion of the hook protruding from the loading pawl body.

[0029] The first thrust zone and the second thrust zone are arranged on opposite edges of the protruding hook of the loading pawl body.

[0030] According to one embodiment of the control mechanism, the closing lever comprises a support zone configured to receive a thrust from the second thrust zone of the loading pawl under the action of the second elastic member.

[0031] According to an exemplary embodiment, the support zone of the closing lever extends in a plane parallel to the pivot axis of the closing lever.

[0032] According to one aspect of the control mechanism, the pivot axis of the loading pawl relative to the cocking disc is parallel to the pivot axis of the cocking disc.

[0033] According to one aspect of the control mechanism, the distance between a distal end of the protruding hook of the loading pawl body and the pivot axis of the cocking disc is less than the distance between the distal end of the protruding hook of the loading pawl body and the pivot axis of the loading pawl relative to the cocking disc.

[0034] This arrangement allows the cocking disc to move from the rest position to the cocked position without the loading pawl contacting the closing lever, while still allowing the loading pawl to contact and pivot the closing lever when the loading pawl pivots from the drive position to the free position.

[0035] According to one embodiment of the control mechanism, the loading pawl comprises a housing configured to receive a drive pin of a cocking lever, so as to drive the loading pawl and move the cocking disc from the first position to the second position.

[0036] The presence of the housing and the pivot connection between the loading pawl and the cocking disc allows selective engagement of the cocking lever with the loading pawl.

[0037] The housing comprises an engagement wall extending in a direction substantially radial to the cocking disc, the drive pin being in contact with the engagement wall when driving the loading pawl.

[0038] The engagement wall extends in a direction substantially perpendicular to a straight line joining the engagement wall and the pivot axis of the loading pawl relative to the cocking disc. The engagement wall extends in a direction substantially parallel to the direction of extension of the drive pin.

[0039] Thus, the frictional force between the drive pin and the loading pawl exerts a high holding torque on the loading pawl relative to the cocking disc, which tends to prevent the loading pawl from pivoting relative to the cocking disc. This allows the drive pin to remain in contact with the loading pawl throughout its driving stroke.

[0040] According to one embodiment of the control mechanism, the second elastic member is a torsion spring.

[0041] The second elastic member is, for example, coaxial with the closing lever.

[0042] According to an exemplary embodiment, the second elastic member is mounted prestressed.

[0043] According to one embodiment of the control mechanism, the cocking disc comprises a roller configured to roll along the periphery of a latching lever when the cocking disc moves from the first position to the second position, the holding stop being defined by a portion of the periphery of the latching lever on which the roller can come to bear.

[0044] The profile given to the perimeter of the latching lever makes it possible to create a holding stop which does not limit the movement of the cocking disc when it moves from the rest position to the cocking position, but prevents the cocking disc from returning to the rest position once the cocking position is reached.

[0045] The axis of rotation of the cocking disc roller is parallel to the axis of rotation of the cocking disc.

[0046] The portion of the perimeter of the latching lever forming a holding stop for the roller of the cocking disc extends in a direction substantially parallel to the radial direction of the cocking disc.

[0047] The control mechanism includes an anti-rotation stop configured to prevent the latching lever from rotating when the cocking disc moves from the first position to the second position.

[0048] According to an example of implementation of the control mechanism, the rotation shaft of the roller of the cocking disc can slide in a slot of the cocking disc by constraining an elastic return element.

[0049] According to one aspect of the control mechanism, the cocking lever includes a rod configured to coaxially engage the cocking shaft.

[0050] The cocking lever includes a pin that extends along an axis parallel to the axis of the cocking lever.

[0051] The pin is connected to the cocking lever body by a lateral projection extending perpendicular to the cocking lever axis.

[0052] In the cocking lever engagement position, the cocking lever and cocking shaft are coaxial.

[0053] According to one embodiment, the cocking lever is configured to be manually driven by an operator. The cocking lever comprises a gripping rod extending perpendicular to the axis of the cocking lever.

[0054] According to another embodiment, the cocking lever is driven by an electric motor.

[0055] The control mechanism may include a first loading pawl return spring configured to maintain the loading pawl in the drive position when the cocking disc is in the first position, called the rest position.

[0056] The control mechanism may include a second loading pawl return spring configured to maintain the loading pawl in the free position when the cocking disc moves from the second position to the first position.

[0057] The disclosure also relates to a power cut-off device comprising a control mechanism as described above.

[0058] The disclosure also relates to an electrical apparatus comprising a current cut-off device as described above, the cut-off device being arranged to selectively allow or prohibit the passage of current in the electrical apparatus. Brief description of the drawings

[0059] Other features, details and advantages will become apparent upon reading the detailed description below, and upon analyzing the attached drawings, in which: [ Fig. 1 ] is a schematic representation of an electrical device incorporating a control mechanism according to the invention, [ Fig. 2 ] is a partial side view of a control mechanism according to the invention, the control mechanism being placed in a first position, [ Fig. 3 ] is another partial side view of the control mechanism of the figure 2 , the control mechanism being placed in a second position, [ Fig. 4 ] is another partial side view of the control mechanism of the figure 2 , the control mechanism being placed in a third position, [ Fig. 5 ] is another partial side view of the control mechanism of the figure 2, the control mechanism being placed in a fourth position, [ Fig. 6 ] is another partial side view of the control mechanism of the figure 2 , the control mechanism being placed in a fifth position, [ Fig. 7 ] is another partial side view of the control mechanism of the figure 2 , the control mechanism being placed in a sixth position, [ Fig. 8 ] is a partial perspective view of the control mechanism of the figures 2 to 7 , [ Fig. 9 ] is another partial perspective view of the control mechanism of the figures 2 to 7 , [ Fig. 10 ] is a side view of the control mechanism shown in figure 9 . Description of the embodiments

[0060] To facilitate reading the figures, the different elements are not necessarily represented to scale. In these figures, identical elements bear the same references. Some elements or parameters may be indexed, i.e. designated for example by first element or second element, or first parameter and second parameter, etc. This indexing is intended to differentiate similar, but not identical, elements or parameters. This indexing does not imply a priority of one element or parameter over another and the names may be interchanged. When it is specified that a subsystem includes a given element, this does not exclude the presence of other elements in this subsystem.

[0061] It has been represented on the figure 1an electrical appliance 10 comprising a current cut-off device 50. The current cut-off device 50 is arranged to selectively authorize or prohibit the passage of current in the electrical appliance 10.

[0062] The electrical apparatus 10 comprises three electrical conductors 11, 12, 13 corresponding respectively to the three phases of a medium voltage electrical circuit. Each electrical conductor 11, 12, 13 comprises respectively a movable contact 21, 22, 23 and a fixed contact 24, 25, 26. The movable contacts 21, 22, 23 of the current cut-off device 50 are movable in rotation between a position in which the movable contacts 21, 22, 23 are respectively distant from the fixed contacts 24, 25, 26, and a position in which the movable contacts 21, 22, 23 are respectively in contact with the fixed contacts 24, 25, 26.

[0063] The power cut-off device 50 comprising a control mechanism 100 which will be described below.

[0064] The mechanism 100 for controlling the closing and opening of a current cut-off device 50 comprises: a cocking lever 111, a cocking shaft 300 pivotally connected to a frame 200, a first elastic member 104 comprising a closing spiral spring 106 comprising a central end 106a secured to the cocking shaft 300 and a peripheral end 106b secured to a control crank 250 connected to the current cut-off device 50, a cocking disc 107, secured to the cocking shaft 300, movable between a first position P1 called the rest position and a second position P2 called the cocking position, a loading pawl 213, pivotally connected to the cocking disc 107, the loading pawl 213 being able to pass from a first position P'1 called the drive position, in which the cocking lever 111 drives the cocking disc 107 via the loading pawl 213, at a second position P'2 called free position,in which the cocking lever 111 is free to rotate relative to the cocking disc 107, a rotation of the cocking lever 111 in a first direction of rotation called the cocking direction causing the cocking disc 107 to pass from the first position P1 to the second position P2 by constraining the first elastic member 104, a holding stop 217 configured to hold the cocking disc 107 once the cocking disc 107 has reached the second position P2 and the torque applied to the cocking disc 107 by the cocking lever 111 becomes less than the torque supplied by the first elastic member 104, a hooking device 80 movable between a first position in which the control crank 250 is kept stationary and a second position in which the control crank can move under the action of the closing spiral spring 106, a closing lever 109, in pivot connection relative to the frame 200,configured to move the hooking device 80 from the first position to the second position and thus cause the closing of the current cut-off device 50, a second elastic member 112 configured to move the loading pawl 213 from the drive position P'1 to the free position P'2 when the arming disc 107 is held by the holding stop 217, , and the loading pawl 213 is configured to move the closing lever 109 from the first position to the second position when the loading pawl 213 moves from the drive position P'1 to the free position P'2, so as to cause the closing of the current cut-off device 50.

[0065] Once the cocking lever 111 has rotated sufficiently during the cocking operation, the force applied by the first elastic member 104 can thus be taken up by the holding stop 217, because the cocking disc 107 can bear on the holding stop 217. The force exerted by the cocking lever 111 on the loading pawl 213 therefore decreases until it is practically zero. The force exerted by the second elastic member 112 on the loading pawl 213 then becomes greater than the holding force exerted by the cocking lever 111, this holding force resulting from the friction between the cocking lever 111 and the loading pawl 213. The loading pawl 213 can thus pivot relative to the cocking disc 107 under the action of the second elastic member 112, and trigger the rotation of the closing lever 109.The closing lever 109 causes the latching device 80 to be released, which allows the control crank 250 to be released and causes the movable electrical contacts of the current cut-off device 50 to rotate. The electrical circuit is thus closed, which allows the passage of electric current into the electrical appliance 10. Since the arming disc 107 is fixed and in contact with the holding stop 217 when the closing of the current cut-off device 50 is triggered, there are no mechanical shocks between the arming disc 107 and the holding stop 217 during the closing phase of the electrical circuit. The mechanical stresses on the parts of the control mechanism 100 are reduced, and this increases their longevity. The durability of the control mechanism 100 is improved.

[0066] The frame 200 is a frame of the control mechanism 100 of the current cut-off device 50. The frame 200 is rigid and mechanically supports the various parts of the control mechanism 100. The frame 200 is shown schematically in the figure 8 , and is not shown in the other figures.

[0067] The cocking disc 107 and the cocking shaft 300 form a rigid assembly. The cocking disc 107 can be fixed to the cocking shaft 300, for example, by crimping or by welding.

[0068] The arming disc 107 has the general shape of an openwork disc. The arming disc 107 extends in a plane perpendicular to the axis of rotation D1 of the arming shaft 300. The arming disc 107 is for example formed from a flat sheet metal.

[0069] The assembly of the arming disc 107 and the arming shaft 300 is movable between a first position P1, called the rest position, and a second position P2 called the arming position.

[0070] The cocking lever 111 comprises a rod 111d configured to engage coaxially in the cocking shaft 300. The cylindrical body 111a of the cocking lever 111 is extended by the rod 111d. The cocking shaft 300 comprises at one axial end a cylindrical chamber capable of receiving the rod 111d.

[0071] In the engagement position of the cocking lever 111, the cocking lever 111 and the cocking shaft 300 are coaxial, as shown in the figure 8 . The axis D1 is the common axis of the cocking lever 111 and the cocking shaft 300.

[0072] The cocking lever 111 comprises a pin 111c which extends along an axis parallel to the axis of the cocking lever 111. The axis of the pin 111c is distant from the axis D1. The pin 111c is connected to the body 111a of the cocking lever 111 by a lateral projection 111b extending perpendicular to the axis of the cocking lever 111.

[0073] The drive pin 111c allows the cocking disc 107 to be rotated, via the loading pawl 213.

[0074] According to the illustrated embodiment, the arming lever 111 is configured to be manually driven by an operator. When the operator wishes to close the electrical circuit of the electrical device 10, he inserts the arming lever 111 into the arming shaft 300 in order to operate the control mechanism 100.

[0075] The cocking lever 111 comprises a gripping rod extending perpendicular to the axis of the cocking lever 111. The gripping rod, not shown in the figures, has a length providing a sufficient lever arm so that the operation of the control mechanism 100 is easy for the operator. The operation of the cocking lever, by means of the gripping rod, moves the assembly of the cocking disc 107 and the cocking shaft 300 from the first position P1, called the rest position, to the second position P2, called the cocking position. Once the circuit has been closed, the cocking lever 111 can be released from the cocking shaft 300.

[0076] According to another embodiment, not shown, the cocking lever 111 is driven by an electric motor. In this case, the operator activates the control of the electric motor to trigger the operation of the control mechanism. The operating principle of the control mechanism 100 remains identical. In this embodiment, the cocking lever 111 is permanently connected to the cocking shaft 300.

[0077] The loading pawl 213 is configured to pivot relative to the cocking disc 107, along a pivot axis D2. The pivot axis D2 of the loading pawl 213 relative to the cocking disc 107 is parallel to the pivot axis D1 of the cocking disc 107.

[0078] The loading pawl 213 is fixed in translation relative to the cocking disc 107. The loading pawl 213 is flat. The loading pawl 213 is for example formed in a flat sheet.

[0079] The first elastic member 104 comprises a closing spiral spring 106 comprising a central end 106a secured to the cocking shaft 300 and a peripheral end 106b secured to a control crank 250.

[0080] By the fact that two parts are integral with each other, we mean that these two parts are rigidly linked to each other.

[0081] As illustrated in the figure 10 , the central end 106a is embedded in a slot 300a extending radially towards the center of the shaft 300.

[0082] The first elastic member 104 further comprises an opening spiral spring comprising a central end secured to the arming shaft 300 and a peripheral end secured to the frame 200.

[0083] The opening spiral spring and the closing spiral spring 106 are both tensioned during rotation of the cocking shaft 300.

[0084] The holding stop 217 is configured to hold the cocking disc 107 once the cocking disc 107 has reached the second position P2 and the torque applied to the cocking disc 107 by the cocking lever 111 becomes less than the torque applied by the opening spiral spring and the closing spiral spring 106.

[0085] The closing lever 109 can move from a first position P"1 called the rest position, in which the latching device 80 holds the control crank 250, so that the electric current does not flow in the current cut-off device 50, to a second position P"2 called the closing position, in which the latching device 80 releases the control crank 250, so that the current cut-off device 50 is put in a position in which the electric current can flow in the current cut-off device 50.

[0086] In the first position P"1 called the rest position, the closing spring 106 is held under stress. In the second position P"2 called the closing position, the closing spring 106 is released, so that the elastic potential energy accumulated by the closing spring 106 during the arming operation makes it possible to actuate the movable contacts of the current cut-off device 50 and thus close the electrical circuit. For this, the movable contacts 21, 22, 23 each corresponding to a phase of the electrical circuit pivot jointly so as to each come into contact respectively with a fixed contact 24, 25, 26.

[0087] The internal components establishing a kinematic connection between the control crank 250 and the moving contacts 21, 22, 23 have not been shown in detail, and are shown diagrammatically on the figure 10 by the dotted line with the sign 90.

[0088] THE figures 9 And 10illustrates more particularly the components carrying out the movement of the movable contacts of the current cut-off device 50.

[0089] The hooking device 80 of the mechanism 100 for controlling the closing and opening of a current cut-off device 50, detailed on the figure 9 , includes a rocker 115 in pivot connection with respect to the frame 200.

[0090] The rocker 115 is movable between a position for holding the control crank 250 and a position for releasing the control crank 250.

[0091] The rocker 115 is connected to the closing lever 109 by a connecting rod 120.

[0092] The control mechanism 100 comprises a closing disc 108 secured to the control crank 250 and pivotally connected to the cocking shaft 300. The subassembly formed by the closing disc 108 and the control crank 250 is thus pivotally connected to the cocking shaft 300. The closing disc 108 and the control crank 250 both pivot relative to the cocking shaft 300, and are axially offset from each other along the cocking shaft 300.

[0093] The closing spiral spring 106, visible on the figure 10 , comprises a central end 106a secured to the arming shaft 300 and a peripheral end 106b secured to the control crank 250.

[0094] The closing disc 108 comprises a retaining roller 230. The retaining roller 230 can slide in a radial slot 108c of the closing disc 108.

[0095] The closing disc 108 and the cocking disc 107 are coaxial and are offset from each other along the cocking shaft 300. Comparison of the figures 8 And 9 illustrates this offset along the axial extension direction of the arming shaft 300.

[0096] The hooking device 80 comprises an activation lever 215 capable of performing a rotational movement around an axis D7.

[0097] The activation lever 215 is configured to selectively hold the closure disc 108 in position against the effect of the closure spiral spring 106 or release the closure disc 108 so as to allow its rotation under the effect of the closure spiral spring 106.

[0098] For this, a first end 215a of the activation lever 215 is configured to be in contact with the closing disc 108 and a second end 215b of the activation lever 215 is configured to be in contact with the rocker 115.

[0099] The control crank 250 is integral with the closing disc 108 and the assembly is pivotally connected to the cocking shaft 300.

[0100] The rocker 115 includes a hooking zone 115b of the connecting rod 120, visible on the figures 2 to 6 .

[0101] As can be seen on the figure 9 , the rocker 115 also comprises a half-moon 117, that is to say a portion in the shape of a half-cylinder which can pivot around an axis D6.

[0102] The activation lever 215 has a general L-shape with a first end 215a and a second end 215b. Depending on the angular position of the rocker 115, the activation lever 215 is held by the half-moon 117 at its second end 215b, or can be released from the half-moon 117. In the position of the figure 9 , the holding roller 230 is supported on the lever 215 at its first end 215a, and the lever 215 is supported against the half-moon portion 117 of the rocker 115 at its second end 215b. The lever 215 being blocked by the half-moon 117 of the rocker 115, the lever 215 cannot rotate under the effect of the torque applied by the closing spring 106. In other words, the hooking device 80 blocks the rotation of the assembly of the closing disc 108 and the control crank 250 under the action of the closing spring 106. figure 9represents the movable hooking device 80 in the first position, in which the control crank 250 is held stationary. When the closing lever 109 rotates the rocker 115 via the connecting rod 120, the second end 215b of the activation lever 215 is released from the half-moon 117. The activation lever 215 can then pivot relative to the axis D7 under the effect of the torque applied at the first end 215a by the holding roller 230, under the effect of the tension state of the closing spring 106.

[0103] The sign F6 schematizes the direction of rotation of the activation lever 215 under the effect of the torque applied by the closing spring 106 via the roller 230. The assembly formed by the closing disc 108 and the control crank 250 pivots in the direction of rotation indicated by the sign F7.

[0104] The control crank 250 thus pivots the contacts 21, 22, 23, which allows the current to pass into the electrical device 10. For this, an opening 250a of the control crank 250, in the form of a slot, actuates a kinematic link 90 connected to the contacts 21, 22, 23.

[0105] The kinematic connection 90 between the control crank 250 and the contacts 21, 22, 23 has not been shown in detail, and is shown schematically on the figure 10 .

[0106] THE figures 2 to 6 more particularly illustrate components of the control mechanism 100 making it possible to control the hooking device 80 to release the control crank 250.

[0107] The loading pawl 213 comprises a first thrust zone 213f configured to constrain the second elastic member 112 when the cocking disc 107 moves from the first position P1 to the second position P2.

[0108] The second elastic member 112 can thus exert sufficient force to pivot the loading pawl 213 once the cocking disc 107 is held by the holding stop 217.

[0109] The first thrust zone 213f is distant from the second elastic member 112 when the arming disc 107 is in the first position P1 called the rest position.

[0110] The first thrust zone 213f is distant from the second elastic member 112 over a first part of the movement path of the arming disc 107 from the first position P1, called the rest position, to the second position P2, called the arming position.

[0111] In other words, the loading pawl 213 is not in contact with the second elastic member 112 when the cocking disc 107 is in the first position P1, nor during an initial phase of the movement stroke of the cocking disc 107. figure 2 corresponds to this state.

[0112] The loading pawl 213 comprises a second thrust zone 213g configured to drive the closing lever 109 when the loading pawl 213 moves from the driving position P'1 to the free position P'2.

[0113] The second thrust zone 213g is configured to exert a thrust on the closing lever 109 when the loading pawl 213 moves from the drive position P'1 to the free position P'2, so as to pivot the closing lever 109. The closing lever 109 can pivot about the pivot axis D3.

[0114] The first thrust zone 213f is formed by a first portion of a hook 213d projecting from a body 213c of the loading pawl 213. The second thrust zone 213g is formed by a second portion of the hook 213d projecting from the body 213c of the loading pawl 213.

[0115] The first thrust zone 213f and the second thrust zone 213g are arranged on opposite edges of the hook 213d projecting from the body 213c of the loading pawl 213.

[0116] The closing lever 109 comprises a support zone 109a configured to receive a thrust from the second thrust zone 213g of the loading pawl 213 under the action of the second elastic member 112.

[0117] The support zone 109a of the closing lever 109 extends in a plane parallel to the pivot axis D3 of the closing lever 109. According to the example illustrated, the support zone 109a of the closing lever 109 extends in a plane passing through the pivot axis D3.

[0118] The closing lever 109 has the general shape of an angular sector whose apex substantially coincides with the axis of rotation D3.

[0119] The control mechanism 100 comprises a rocker 115 configured to drive the latching device 80 and thus cause the closing of the power cut-off device 50. The rocker 115 is pivotally connected relative to the frame 200. The rocker 115 is connected to the closing lever 109 by a connecting rod 120. The rocker 115 is configured to drive the latching device 80 and thus cause the closing of the power cut-off device 50.

[0120] The rocker 115 has an elongated shape, and can pivot around an axis D6 distant from each end of the rocker 115.

[0121] The loading pawl 213 moves from the first position P'1, called the drive position, to the second position P'2, called the free position, by a pivoting movement. The angular amplitude a of the pivoting travel of the loading pawl 213 relative to the cocking disc 107 is between 5° and 40°. This angular amplitude a of the movement of the loading pawl 213 around the axis D2 is shown diagrammatically in figure 6 .

[0122] As shown in the figure 7 , the distance L1 between a distal end 213h of the hook 213d projecting from the body 213c of the loading pawl 213 and the pivot axis D1 of the cocking disc 107 is less than the distance L2 between the distal end 213h of the hook 213d projecting from the body 213c of the loading pawl 213 and the pivot axis D2 of the loading pawl 213 relative to the cocking disc 107.

[0123] Thanks to this arrangement, the cocking disc 107 can move from the rest position P1 to the cocking position P2 without the loading pawl 213 touching the closing lever 109. Conversely, when the loading pawl 213 pivots from the driving position P'1 to the free position P'2 under the action of the second elastic member 112, the loading pawl 213 encounters the closing lever 109 and pivots it. The closing lever 109 thus pivots the rocker 115, under the effect of the traction generated by the connecting rod 120.

[0124] On the figure 7 , the sign T1 schematizes the trajectory of the distal end 213h of the hook 213d during the rotation of the cocking disc 107 around the axis D1. The sign T2 schematizes the trajectory of the distal end 213h of the hook 213d during the rotation of the loading pawl 213 around the axis D2.

[0125] The hatched area designated by the sign A indicates the area in which the trajectory T2 is further from the axis D1 than the trajectory T1, which allows the loading pawl 213 not to touch the closing lever 109 when rotating the cocking disc in the direction of rotation indicated by the arrow F2, and to actuate the closing lever 109 when rotating the loading pawl 213 in the direction of rotation indicated by the arrow F4.

[0126] The loading pawl 213 comprises a housing 213e configured to receive the drive pin 111c of the cocking lever 111, so as to drive the loading pawl 213 and move the cocking disc 107 from the first position P1 to the second position P2.

[0127] The presence of the housing 213e and the pivot connection between the loading pawl 213 and the cocking disc 107 allows selective engagement of the cocking lever 111 with the loading pawl 213. Thus, depending on the angular position of the loading pawl 213 relative to the cocking disc 107, the drive pin 111c of the cocking lever 111 can either engage in the housing 213e and allow the cocking lever 111 to drive the cocking disc 107, or leave the drive pin 111 free relative to the cocking disc 107.

[0128] The housing 213e comprises an engagement wall 213b extending in a direction A1 substantially radial to the arming disc 107. The drive pin 111c is in contact with the engagement wall 213b when the loading pawl 213 is driven.

[0129] As highlighted on the Figure 5, the engagement wall 213b extends in a direction A1 substantially perpendicular to a straight line A2 joining the engagement wall 213b and the pivot axis D2 of the loading pawl 213 relative to the cocking disc 107. The engagement wall 213b thus extends in a direction A1 substantially parallel to the direction of extension of the drive pin 111c.

[0130] Thus, when the drive pin 111c drives the cocking disc 107 via the loading pawl 213, the friction force between the drive pin 111c and the loading pawl 213 exerts a high holding torque of the loading pawl 213 relative to the cocking disc 107, which tends to prevent pivoting of the loading pawl 213 relative to the cocking disc 107. This allows the drive pin 111c to remain in contact with the loading pawl 213 as long as the cocking lever 111 exerts a driving torque on the loading pawl 213, that is to say throughout the drive stroke of the cocking disc 107.

[0131] The second elastic member 112 is a torsion spring. The second elastic member 112 is here coaxial with the closing lever 109. The torsion spring 112 comprises two rectilinear strands connected by a winding of concentric turns. The second elastic member 112 is for example mounted prestressed.

[0132] The arming disc 107 comprises a roller 220 configured to roll along the periphery of a latching lever 214 when the arming disc 107 moves from the first position P1 to the second position P2. The holding stop 217 is defined by a portion of the periphery of the latching lever 214 on which the roller 220 can come to bear.

[0133] The profile given to the periphery of the latching lever 214 makes it possible to create a holding stop which does not limit the movement of the arming disc 107 when it passes from the rest position P1 to the arming position P2, but prevents the arming disc 107 from returning to the rest position P1 once the arming position P2 is reached.

[0134] The latching lever 214 has a generally elongated shape, and can pivot about an axis D5 distant from each end. A portion 214c of the periphery of the latching lever 214 forms a rolling surface for the roller 220, in the manner of a cam track.

[0135] The roller 220 has an axis of rotation D4. The axis of rotation D4 of the roller 220 of the cocking disc 107 is parallel to the axis of rotation D1 of the cocking disc 107.

[0136] The portion of the periphery of the latching lever 214 forming a holding stop 217 for the roller 220 of the cocking disc 107 extends in a direction A3 substantially parallel to a radial direction of the cocking disc 107.

[0137] The control mechanism 100 comprises an anti-rotation stop 125 configured to prevent the latching lever 214 from rotating when the cocking disc 107 moves from the first position P1 to the second position P2.

[0138] The anti-rotation stop 125 here has a half-moon shape. One end 214a of the hooking lever 214, opposite the holding stop 217 relative to the pivot axis D5 of the hooking lever 214, bears on the anti-rotation stop 125, which prevents the hooking lever 214 from rotating under the thrust exerted by the roller 220.

[0139] The rotation shaft of the roller 220 can slide in a slot 107c of the arming disc 107 by constraining an elastic return element.

[0140] The control mechanism 100 comprises a first return spring 221 of the loading pawl 213 configured to maintain the loading pawl 213 in the drive position P'1 when the cocking disc 107 is in the first position P1 called the rest position.

[0141] The control mechanism 100 comprises a second return spring 222 of the loading pawl 213 configured to maintain the loading pawl 213 in the free position P'2 when the cocking disc 107 moves from the second position P2 to the first position P1.

[0142] The pivot axes D1, D2, D3, D4, D5, D6 and D7 are parallel to each other.

[0143] THE figures 2 to 6represent different successive phases of an operation of the control mechanism 100 aimed at closing the electrical circuit of the electrical device 10 in order to allow current to flow. Views 2 to 6 are in chronological order.

[0144] There figure 2 illustrates the initial position of the various parts of the control mechanism 100 at the start of the maneuver aimed at closing the electrical circuit.

[0145] The cocking lever 111 is already inserted into the cocking shaft 300, the step of inserting the cocking lever 111 into the cocking shaft 300 has not been shown.

[0146] On the figure 2, the first return spring 221 is in contact with the loading pawl 213, and maintains the loading pawl 213 in the driving position P'1. The driving pin 111c of the cocking lever 111 is engaged in the housing 213e of the loading pawl 213, and the edge of the pin 111c bears against the surface 213b of the loading pawl 213.

[0147] Arrow F1 indicates the torque applied to the cocking lever 111 by the operator performing the circuit closing operation. Arrow F2 indicates the direction of rotation of the cocking disc 107 resulting from the torque applied to the cocking lever 111.

[0148] The roller 220 rolls around the perimeter of the latching lever 214 during the movement of the cocking disc 107.

[0149] The hook 213d of the loading ratchet 213 is distant from the second elastic member 112.

[0150] There figure 3illustrates the position of the various parts of the control mechanism 100 at the end of the movement stroke of the cocking lever 111, i.e. when the movement amplitude is maximum. In this position, the operator exerts a torque on the cocking lever 111 so as to maintain the cocking disc 107 in the position corresponding to the maximum movement, against the effect of the first elastic member 104. The second elastic member 112 is constrained by the loading pawl 213. In fact, the first thrust zone 213f of the hook 213d is engaged with a strand of the second elastic member 112.The second elastic member 112 exerts on the loading pawl 213 a force tending to rotate the latter in an anti-clockwise direction according to the viewing angle of the figure, but such a rotational movement is not possible because the friction force exerted between the pin 111c and the loading pawl 213, at the level of the bearing surface 213b, generates a torque greater than that generated by the second elastic member 112. The arrow F1 indicates, as previously, the torque applied by the operator to the cocking lever 111.

[0151] A clearance, designated by the sign j, exists between the roller 220 and the end of the lever 214 forming the holding stop 217. The roller 220 is opposite the holding stop 217, without being in contact with it. The clearance j characterizes the overtravel of the cocking disc 107 relative to the minimum travel allowing the roller 220 to come to bear on the holding stop 217.

[0152] There figure 4illustrates the position of the various parts once the operator has begun to release the force applied to the cocking lever 11.

[0153] The torque applied by the operator to the cocking lever 111 becomes less than the torque exerted by the first elastic member 104. The cocking disc 107 rotates in the direction of rotation indicated by the arrow F3, i.e. the counterclockwise direction in the figure, until the roller 220 comes to bear on the stop surface 217. The stop surface 217 thus takes up the torque exerted by the first elastic member 104. The holding torque of the loading pawl 213, generated by the friction force between the drive pin 111c and the engagement wall 213b, becomes less than the torque exerted by the second elastic member 112. The loading pawl 213 can therefore begin to pivot.

[0154] There Figure 5illustrates the position of the various parts during the pivoting of the loading pawl 213.

[0155] Under the effect of the thrust of the second elastic member 112, the loading pawl 213 pivots around its pivot axis D2, as indicated by the arrow F4. The second thrust zone 213g of the loading pawl 213 approaches the support zone 109a of the closing lever 109.

[0156] The arming disc 107 is stationary, the roller 220 still resting on the holding stop 217.

[0157] There figure 6 illustrates the position of the various parts at the end of pivoting of the loading pawl 213, and shows the pivoting of the control lever 109 and the associated triggering of the hooking device 80.

[0158] The second thrust zone 213g exerts a thrust on the bearing surface 109a, which causes the closing lever 109 to pivot, as shown diagrammatically by the arrow F5. The closing lever 109 rotates the rocker 115, via the connecting rod 120.

[0159] The rocker 115 activates the hooking device 80, i.e. releases the activation lever 215, which allows the control crank 250 to trigger the rotation of the three movable contacts 21, 22, 23.

[0160] The cocking disc 107 is stationary, the roller 220 still resting on the holding stop 217. The arrow F4 indicates, as previously, the direction of pivoting of the loading pawl 213.

[0161] The triggering of the closing of the contacts 21, 22, 23 can only be obtained if the roller 220 exceeds the holding stop 217, that is to say only if the displacement stroke applied to the arming lever corresponds to the total intended stroke. Thus, an untimely closing by a small amplitude displacement is not possible.

[0162] The operation is identical for the embodiment variants in which the cocking lever 111 is set in motion by an electric motor. An electronic control module manages the application of the torque and the amplitude of movement of the electric motor.

Claims

1. Mechanism (100) for controlling the closing and opening of a current switching device (50), the mechanism (100) comprising: - an arming lever (111), - an arming shaft (300) in pivot connection in relation to a frame (200), - a first elastic member (104) including a closing spiral spring (106) comprising a central end (106a) secured to the arming shaft (300) and a peripheral end (106b) secured to a control crank (250) connected to the current switching device (50), - an arming disc (107), secured to the arming shaft (300), movable between a first position (P1) called the rest position and a second position (P2) called the arming position, - a loading pawl (213), in pivot connection in relation to the arming disc (107), the loading pawl (213) being able to go from a first position (P'1) called the driving position, wherein the arming lever (111) drives the arming disc (107) via the loading pawl (213), to a second position (P'2) called the free position, wherein the arming lever (111) is free to rotate in relation to the arming disc (107), wherein a rotation of the arming lever (111) according to a first direction of rotation called the arming direction makes the arming disc (107) go from the first position (P1) to the second position (P2) by constraining the first elastic member (104), - a retaining stop (217) configured to retain the arming disc (107) once the arming disc (107) has reached the second position (P2) and the torque applied to the arming disc (107) by the arming lever (111) becomes less than the torque provided by the first elastic member (104), - a fastening device (80) movable between a first position wherein the control crank (250) is retained immobile and a second position in which the control crank (250) may move under the action of the closing spiral spring (106), characterised by: - a closing lever (109), in pivot connection in relation to the frame (200), configured to make the fastening device (80) go from the first position to the second position and thus cause the closing of the current switching device (50), - a second elastic member (112) configured to make the loading pawl (213) go from the driving position (P'1) to the free position (P'2) when the arming disc (107) is retained by the retaining stop (217), control mechanism (100) wherein the loading pawl (213) is configured to drive the closing lever (109) when the loading pawl (213) goes from the driving position (P'1) to the free position (P'2), so as to cause the current switching device (50) to close.

2. Control mechanism (100) according to claim 1, wherein the loading pawl (213) comprises a first thrust area (213f) configured to constrain the second elastic member (112) when the arming disc (107) goes from the first position (P1) to the second position (P2).

3. Control mechanism (100) according to the preceding claim, wherein the loading pawl (213) comprises a second thrust area (213g) configured to drive the closing lever (109) when the loading pawl (213) goes from the driving position (P'1) to the free position (P'2).

4. Control mechanism (100) according to the preceding claim, wherein the closing lever (109) comprises a bearing area (109a) configured to receive a thrust of the second thrust area (213g) of the loading pawl (213) under the action of the second elastic member (112), and wherein the bearing area (109a) of the closing lever (109) extends in a plane parallel to the pivot axis (D3) of the closing lever (109).

5. Control mechanism (100) according to the preceding claim, wherein the fastening device (80) comprises a rocker (115) in pivot connection in relation to the frame (200), the rocker (115) being movable between a position for retaining the control crank (250) and a position for releasing the control crank (250), and wherein the rocker (115) is connected to the closing lever (109) by a connecting rod (120).

6. Control mechanism (100) according to one of claims 3 to 5, wherein the first thrust area (213f) is formed by a first portion of a hook (213d) protruding from a body (213c) of the loading pawl (213), wherein the second thrust area (213g) is formed by a second portion of the hook (213d) protruding from the body (213c) of the loading pawl (213), and wherein the distance (L1) between a distal end (213h) of the hook (213d) protruding from the body (213c) of the loading pawl (213) and the pivot axis (D1) of the arming disc (107) is less than the distance (L2) between the distal end (213h) of the hook (213d) protruding from the body (213c) of the loading pawl (213) and the pivot axis (D2) of the loading pawl (213) in relation to the arming disc (107).

7. Control mechanism (100) according to one of the preceding claims, wherein the loading pawl (213) includes a housing (213e) configured to receive a driving pin (111c) of an arming lever (111), so as to drive the loading pawl (213) and to make the arming disc (107) go from the first position (P1) to the second position (P2).

8. Control mechanism (100) according to the preceding claim, wherein the housing (213e) comprises an engagement wall (213b) extending in a direction substantially radial to the arming disc (107), the driving pin (111c) being in contact with the engagement wall (213b) during the driving of the loading pawl (213).

9. Control mechanism (100) according to one of the preceding claims, wherein the second elastic member (112) is a torsion spring, and wherein the second elastic member (112) is coaxial with the closing lever (109).

10. Control mechanism (100) according to one of the preceding claims, wherein the arming disc (107) comprises a roller (220) configured to roll along the perimeter of an fastening lever (214) when the arming disc (107) goes from the first position (P1) to the second position (P2), the retaining stop (217) being defined by a portion of the perimeter of the fastening lever (214) whereon the roller (220) is able to bear, and wherein the axis of rotation (D3) of the roller (220) of the arming disc (107) is parallel to the axis of rotation (D1) of the arming disc (107).

11. Control mechanism (100) according to one of the preceding claims, wherein the control mechanism (100) comprises a first return spring (221) of the loading pawl (213) configured to retain the loading pawl (213) in the driving position (P'1) when the arming disc (107) is in the first position (P1) called the rest position, and wherein the control mechanism (100) comprises a second return spring (222) of the loading pawl (213) configured to retain the loading pawl (213) in the free position (P'2) when the arming disc (107) goes from the second position (P2) to the first position (P1).

12. Current switching device (50) including a control mechanism (100) according to one of the preceding claims.

13. Electrical device (10) including a current switching device (50) according to the preceding claim, the current switching device (50) being arranged to selectively allow or prohibit the flow of current through the electrical device (10).