EP3933153B1 - Electromechanical actuating device for a door with permanent magnets supported by at least one wheel of the clutch - Google Patents

Description

Technical field of the invention

The present invention relates to an electromechanical actuation device for an opening of the door or window type, the electromechanical actuation device being intended to rotate a rotor of a rotary mechanism of the opening such as a cylinder of a lock mechanism.

The invention applies in particular to the fields of locks which comprise a lock cylinder equipped with a rotor with, on the exterior side, an exterior lock entry allowing the introduction of a key admitted by the lock and, on the interior side , either an internal lock entry allowing the introduction of a key admitted by the lock, or a coupling member allowing the connection of the rotor with a manual button. The rotational actuation of the rotor of the lock cylinder via a key or the manual button makes it possible to control the movement of a spring bolt and/or a deadbolt of the lock in order to open or close the sash and/or lock or unlock the lock.

The opening may in particular concern a moving part of a window or a door. In the case of a window, the rotary mechanism to which the electromechanical actuation device is intended to be coupled in rotation can be the rotor of the handle of this window, whether it is an opening of the window according to a vertical axis or along two axes, respectively vertical and horizontal, as is the case for so-called tilt-and-turn windows.

State of the art

Conventionally, a door lock comprises a lock cylinder having a stator fixedly mounted on the opening and a rotor rotatably mounted in the stator so as to pass through the thickness of the opening. The rotational actuation of the rotor of the lock cylinder can actuate in translation a deadbolt of the lock, the latter being mobile in translation relative to the stator and capable of locking the lock by insertion into a striker secured to a fixed frame, or jamb, on which the sash is movably mounted. Such a deadbolt is capable of varying between a locking position where it is deployed and an unlocking position where it is retracted.

The door lock may also include a handle pivotally mounted on the opening or a rotary manual button to actuate at least one spring bolt movable in translation in the stator of the lock. Such a spring-loaded bolt is capable of varying between a closed position where it is deployed and an open position where it is retracted. Actuation of the handle or rotary manual button moves the spring-loaded bolt from the closed position to the open position, while the reverse movement can be done using a spring internal to the lock. Rotational actuation of the lock cylinder rotor can also be used to actuate this spring-loaded bolt. Conventionally, the spring bolt comprises a beveled portion, which by reaction against the fixed frame when closing the movable opening, causes retraction of the bolt in the opening against the action of the internal spring.

The rotor of the lock cylinder comprises, on the exterior side, an exterior lock entry allowing the insertion of a key admitted by the lock and, on the interior side, either an interior lock entry allowing the introduction of an accepted key by the lock, or a rotor coupling member allowing the installation of a manual button so as to couple in rotation the rotor of the lock cylinder with the manual button. The rotational actuation of the rotor of the lock cylinder via a key or the manual button makes it possible to control the movement of the spring bolt and/or the deadbolt of the lock, in particular in order to open or close the opening by moving the spring bolt and/or locking or unlocking the lock by moving the deadbolt.

There are electromechanical devices intended to operate such locks in a motorized manner, for example like the solution described in the document EP2762661A1 . These electromechanical lock actuation devices are intended to be fixed on the interior side of the opening in a manner cooperating with the rotor of the lock to be motorized with a view to its actuation to control its locking and/or unlocking by moving the deadbolt and/or to control its opening and/or closing by moving the spring bolt.

The electromechanical lock actuation devices generally comprise a frame to be fixed on one face of the opening whose lock is to be motorized and a drive member movable in rotation relative to the frame and intended to be coupled to one end of the rotor of the lock cylinder. They also include a source of electrical energy to power on the one hand an electric actuator adapted to rotate the drive member, and a programmable control unit capable of communicating with the outside, particularly with a view to receiving external instructions and transmitting outgoing information. The control unit controls the electric actuator taking into account, among other things, these instructions and this information.

Cooperation between the rotor of the lock cylinder and the internal drive member of the electromechanical lock actuation device can be achieved by placing one of the keys admitted by the lock cylinder at the level of the lock cylinder. interior entrance of the lock, this key then being engaged with the drive member to be integral in rotation with one and the other. Alternatively, the cooperation between the rotor of the lock cylinder and the internal drive member of the electromechanical lock actuation device can be done via the aforementioned coupling member, which can be made integral with the rotor of the lock. lock cylinder and is initially intended for the installation of the manual button also mentioned above. Once the manual button has been removed, the coupling member can be engaged with the internal drive member of the electromechanical actuation device so that these two elements are integral in rotation with each other.

To allow manual actuation of the drive member and/or to avoid damage to the actuator in the case where external forces are applied to the rotor of the lock cylinder, for example in the event of a break-in, most electromechanical devices also include a clutch interposed between the actuator and the drive member.

Such a clutch conventionally varies between at least one engaged configuration in which there is a mechanical transmission connection between the drive member and the actuator, and a disengaged configuration in which this mechanical transmission connection is absent.

The clutch can be designed so as to be able to adopt a first engaged configuration in which the actuator is capable of rotating the drive member in a first direction of rotation and a second engaged configuration in which the actuator is capable of rotating the drive member in a second direction of rotation opposite to the first direction of rotation.

The clutch can operate according to friction principles, for example by taking up the teachings of the document FR3028282A1 .

Alternatively, the clutch can be based on the known principle of a tilting yoke, which solution exploits the presence of a tilting support relative to the chassis. This type of solution is for example described in the documents FR2693757A1 And WO2017/114534A1 .

To be able to convert a movement of one of the wheels of the clutch into a tilting movement of the tilting support, while also allowing rotation of this wheel when the tilting support is blocked from rotating in the engaged configuration, it is known to arrange a clutch device between the tilting support and at least one of the clutch wheels. When the mechanical torque transmitted to the wheel equipped with such a clutch device is less than the release value provided by the clutch device, the tilting support is rotated in a movement resulting from the rotation of this wheel. On the other hand, when the mechanical torque becomes greater than the release value, rotation of the wheel becomes possible relative to the tilting support at the moment when the latter is blocked angularly, when one of the engaged configurations is adopted.

Conventionally, the design of such a clutch device is based on the use of the principle of mechanical friction, as is the case in the document WO2017/114534A1 . Certain known solutions use spring washers exerting axial pressure forces between the wheel concerned and the tilting support, these forces being applied to silicone washers.

A first disadvantage of this type of solution is that the principles of friction inevitably induce wear phenomena of the parts involved. This results in maintenance problems, or even malfunction, which is not practical and can be expensive.

Furthermore, the very principle of friction, and even more so as a consequence of these wear phenomena, the release value which defines the operation of the friction clutch device is not precise and is, on the contrary, susceptible to evolve over time in a random and uncontrolled manner. This can lead to malfunctions of the electromechanical device, such as for example the impossibility of being able to switch from a disengaged configuration to an engaged configuration, or excessive braking or even locking of the wheel concerned, these situations being not acceptable.

Another issue to resolve is to ensure that at the time manual actuation of the lock is desired, the clutch occupies the disengaged configuration with certainty. For this purpose, solutions have already been imagined using a magnetic force.

If the document WO2017/114534A1 provides a system delivering a magnetic force by electromagnet favoring the elimination of mechanical cooperation between the clutch wheel and the drive member, this solution does not ensure any maintenance in the disengaged configuration.

The document FR2693757A1 provides for the presence of a magnetic return system to magnetically bias the tilting support towards the angular position corresponding to the disengaged configuration. This system uses a permanent magnet carried by the chassis and a permanent magnet carried by the tilting support. But such an organization is only able to exercise its return function in a relatively small angular range of pivoting of the tilting support. As soon as the tilting support deviates a little too much from the configuration requested via the magnetic return, the magnetic force becomes too weak and is easily overcome. This risk is likely to appear in the event of strong vibrations or a significant shock suffered by the electromechanical device, for example very simply when the opening were to experience a slamming against the frame.

There is therefore a need to reliably and certainly avoid, especially in the event of vibrations or shocks suffered, any risk of the clutch passing from the disengaged configuration to one of the engaged configurations, which could risk making the whole non-operational.

If the above issues have been presented in connection with the particular case of a lock-type rotary mechanism and a door-type opening, the fact remains that they can quite easily arise for other types of rotary mechanisms. 'a door or for a window.

Object of the invention

The present invention aims to propose an electromechanical actuation device for a door or window type opening which responds to the problems raised by the state of the art as presented above, in particular which is reliable, requires little maintenance, is economical, and avoids any risk of malfunction, particularly but not exclusively in the event of shock or vibration.

• un châssis destiné à être fixé sur une face de l'ouvrant,
• un organe d'entrainement, mobile en rotation par rapport au châssis, et apte à être couplé en rotation avec le rotor du mécanisme rotatif lorsque le châssis est fixé sur la face de l'ouvrant,

• un actionneur comprenant un moteur électrique et permettant d'entrainer en rotation électriquement l'organe d'entrainement sélectivement dans un premier sens de rotation et dans un deuxième sens de rotation,
• un embrayage liant le moteur électrique à l'organe d'entrainement, dans lequel l'embrayage comprend :
• une roue menante rotative par rapport au châssis et entraînée en rotation par l'actionneur,
• une roue menée liée en rotation avec l'organe d'entrainement,
• un support basculant apte à basculer de manière bidirectionnelle par rapport au châssis autour d'un axe de basculement,
• un dispositif d'accouplement comprenant au moins une roue satellite en prise avec la roue menante et mobile en rotation par rapport au support basculant selon un axe de rotation excentré par rapport à l'axe de basculement, l'axe de rotation de ladite au moins une roue satellite se déplaçant autour de l'axe de basculement conjointement avec le support basculant,

dans lequel l'embrayage varie, par basculement du support basculant, entre :

• une première configuration embrayée dans laquelle une roue satellite du dispositif d'accouplement est en prise avec la roue menée dans une première zone circonférentielle de la roue menée de manière que l'actionneur entraine, par l'intermédiaire de l'embrayage, le rotor du mécanisme rotatif dans le premier sens de rotation,
• une deuxième configuration embrayée dans laquelle une roue satellite du dispositif d'accouplement est en prise avec la roue menée dans une deuxième zone circonférentielle de la roue menée de manière que l'actionneur entraine, par l'intermédiaire de l'embrayage, le rotor du mécanisme rotatif dans le deuxième sens de rotation,
• une configuration débrayée dans laquelle aucune roue satellite du dispositif d'accouplement n'est en prise avec la roue menée,

dans lequel au moins une roue magnétiquement active choisie dans le groupe constitué de la roue menante et de ladite au moins une roue satellite du dispositif d'accouplement porte au moins un aimant permanent agencé d'une manière telle que ledit au moins un aimant permanent est mobile en rotation par rapport au support basculant conjointement avec la roue magnétiquement active qui porte ledit au moins un aimant permanent, l'au moins un aimant permanent coopérant magnétiquement avec le support basculant et/ou l'au moins un aimant permanent coopérant magnétiquement avec un organe magnétique solidaire du châssis.This goal can be achieved by providing an electromechanical actuation device for an opening of the door or window type, the electromechanical actuation device being intended to rotate a rotor of a rotary mechanism of the opening such that 'a cylinder of a lock mechanism, the electromechanical actuation device comprising:

• a frame intended to be fixed on one side of the opening,
• a drive member, movable in rotation relative to the chassis, and capable of be coupled in rotation with the rotor of the rotating mechanism when the frame is fixed on the face of the opening,

• an actuator comprising an electric motor and making it possible to electrically rotate the drive member selectively in a first direction of rotation and in a second direction of rotation,
• a clutch connecting the electric motor to the drive member, in which the clutch comprises:
• a driving wheel rotating relative to the chassis and rotated by the actuator,
• a driven wheel linked in rotation with the drive member,
• a tilting support capable of tilting bidirectionally relative to the chassis around a tilting axis,
• a coupling device comprising at least one satellite wheel engaged with the driving wheel and movable in rotation relative to the tilting support along an axis of rotation eccentric with respect to the axis of tilting, the axis of rotation of said at least a satellite wheel moving around the tilting axis jointly with the tilting support,

in which the clutch varies, by tilting the tilting support, between:

• a first engaged configuration in which a satellite wheel of the coupling device is engaged with the driven wheel in a first circumferential zone of the driven wheel so that the actuator drives, via the clutch, the rotor of the rotating mechanism in the first direction of rotation,
• a second engaged configuration in which a satellite wheel of the coupling device is engaged with the driven wheel in a second circumferential zone of the driven wheel so that the actuator drives, via the clutch, the rotor of the rotating mechanism in the second direction of rotation,
• a disengaged configuration in which no satellite wheel of the coupling device is engaged with the driven wheel,

in which at least one magnetically active wheel chosen from the group consisting of the driving wheel and said at least one satellite wheel of the coupling device carries at least one permanent magnet arranged in such a way that said at least one permanent magnet is movable in rotation relative to the tilting support together with the magnetically active wheel which carries said at least one permanent magnet, the at least one permanent magnet cooperating magnetically with the tilting support and/or the at least one permanent magnet cooperating magnetically with a magnetic member secured to the chassis.

Some preferred but non-limiting aspects are as follows.

According to one embodiment, the tilting axis around which the tilting support tilts relative to the chassis coincides with the axis of the driving wheel.

According to one embodiment, said at least one permanent magnet generates a globally oriented magnetic field, in the vicinity of at least one of the axial faces of the magnetically active wheel which carries it, substantially parallel to the axis of rotation of the magnetically active wheel which carries said at least one permanent magnet.

According to one embodiment, the coupling device comprises first and second separate satellite wheels, mounted to rotate relative to the tilting support around first and second axes of rotation arranged on either side of the driving wheel and in engagement with the driving wheel, the first satellite wheel being engaged with the driven wheel in its first circumferential zone in the first engaged configuration, the second satellite wheel being engaged with the driven wheel in its second circumferential zone in the second engaged configuration, no first and second satellite wheels not being engaged with the driven wheel in the disengaged configuration, and in which at least one magnetically active wheel chosen from the first satellite wheel and the second satellite wheel carries at least one magnetic assembly including at least two permanent magnets arranged at respective locations distributed angularly around the axis of rotation of the magnetically active wheel which carries said magnetic assembly, the location of each of the permanent magnets of said magnetic assembly being radially offset relative to the axis of rotation of the magnetically active wheel which carries it so that the permanent magnet is movable in rotation relative to the tilting support jointly with the magnetically active wheel which carries it.

According to one embodiment, each of the first and second satellite wheels comprises such a magnetic assembly, which comprises a plurality of permanent magnets angularly distributed around the axis of rotation of the corresponding magnetically active wheel.

According to one embodiment, each magnetic assembly comprises at least four distinct permanent magnets distributed angularly at constant pitches around the axis of rotation of the magnetically active wheel which carries said magnetic assembly.

• le support basculant comporte un élément magnétique susceptible de coopérer magnétiquement avec chaque aimant permanent porté par chaque roue magnétiquement active, lorsque l'élément magnétique est situé dans le champ magnétique généré par l'aimant permanent correspondant, d'une manière créant une force magnétique d'interaction entre l'élément magnétique et l'aimant permanent considéré,
• l'embrayage comprend un dispositif magnétique d'embrayage associé à chaque roue magnétiquement active,
• chaque dispositif magnétique d'embrayage est constitué par l'élément magnétique et le au moins un aimant permanent porté par la roue magnétiquement active associée,
• le dispositif magnétique d'embrayage résultant de la force magnétique d'interaction entre chaque aimant permanent porté par la roue magnétiquement active associée et l'élément magnétique,
• chaque dispositif magnétique d'embrayage applique un couple magnétique de rappel, autour de l'axe de rotation de la roue magnétiquement active associée audit dispositif magnétique d'embrayage, entre le support basculant et la roue magnétiquement active associée audit dispositif magnétique d'embrayage, le couple magnétique de rappel ayant une valeur nominale prédéterminée dépendant de la force magnétique d'interaction entre chaque aimant permanent porté par la roue magnétiquement active associée et l'élément magnétique,
• chaque dispositif magnétique d'embrayage assure que le support basculant et la roue magnétiquement active associée audit dispositif magnétique d'embrayage sont couplés en rotation lorsque le couple mécanique appliqué à ladite roue magnétiquement active associée est inférieur à la valeur nominale, et que le support basculant et ladite roue magnétiquement active associée sont découplés en rotation lorsque le couple mécanique appliqué à ladite roue magnétiquement active associée est supérieur ou égal à la valeur nominale.

According to one embodiment, the electromechanical actuation device is such that:

• the tilting support comprises a magnetic element capable of magnetically cooperating with each permanent magnet carried by each magnetically active wheel, when the magnetic element is located in the magnetic field generated by the corresponding permanent magnet, in a manner creating a magnetic force d the interaction between the magnetic element and the permanent magnet considered,
• the clutch comprises a magnetic clutch device associated with each magnetically active wheel,
• each magnetic clutch device is constituted by the magnetic element and the at least one permanent magnet carried by the associated magnetically active wheel,
• the magnetic clutch device resulting from the magnetic force of interaction between each permanent magnet carried by the associated magnetically active wheel and the magnetic element,
• each magnetic clutch device applies a magnetic return torque, around the axis of rotation of the magnetically active wheel associated with said magnetic clutch device, between the tilting support and the magnetically active wheel associated with said magnetic clutch device, the magnetic return torque having a predetermined nominal value depending on the magnetic force of interaction between each permanent magnet carried by the associated magnetically active wheel and the magnetic element,
• each magnetic clutch device ensures that the tilting support and the magnetically active wheel associated with said magnetic clutch device are coupled in rotation when the mechanical torque applied to said associated magnetically active wheel is less than the nominal value, and that the tilting support and said associated magnetically active wheel are decoupled in rotation when the mechanical torque applied to said associated magnetically active wheel is greater than or equal to the nominal value.

According to one embodiment, for each magnetically active wheel, at least two permanent magnets are located, whatever the angular position of the magnetically active wheel considered relative to the tilting support, directly above the magnetic element with interposition of a predetermined air gap counted parallel to the axis of rotation of said magnetically active wheel and between 0.6 and 1 mm, and more preferably substantially equal to 0.8 mm.

According to one embodiment, the magnetic element of the tilting support is constituted by a plate comprising a ferromagnetic material arranged directly above at least one of the axial faces of each magnetically active wheel with the interposition of a predetermined interval included between 0.2 and 0.6 mm, and more preferably substantially equal to 0.4 mm.

• le châssis comporte au moins un organe magnétique statique susceptible d'être positionné, lorsque l'embrayage occupe sa configuration débrayée, dans le champ magnétique généré par au moins un aimant permanent de l'au moins une roue magnétiquement active, créant une force magnétique de rappel entre l'organe magnétique statique et cet aimant permanent,
• un dispositif magnétique de rappel est constitué par ledit au moins un organe magnétique statique et le au moins un aimant permanent coopérant magnétiquement avec ledit au moins un organe magnétique statique, le dispositif magnétique de rappel résultant de l'ensemble des forces magnétiques de rappel présentes,
• le dispositif magnétique de rappel applique un couple magnétique de rappel, autour de l'axe de basculement, entre le support basculant et le châssis, ce couple mécanique de rappel ayant une valeur seuil prédéterminée dépendant des forces magnétiques de rappel appliquées,
• le support basculant est stabilisé, dans le châssis, dans une position angulaire correspondant à la configuration débrayée de l'embrayage, sous l'effet du couple magnétique de rappel,
• lors de l'activation de l'actionneur, le support basculant bascule autour de l'axe de basculement par rapport au châssis, en fonction du sens de rotation du moteur électrique, en surmontant la valeur seuil prédéterminée du couple mécanique de rappel, jusqu'à l'adoption de l'une parmi la première configuration embrayée et la deuxième configuration embrayée.

According to one embodiment, the electromechanical actuation device is such that:

• the chassis comprises at least one static magnetic member capable of being positioned, when the clutch occupies its disengaged configuration, in the magnetic field generated by at least one permanent magnet of the at least one magnetically active wheel, creating a magnetic force of return between the static magnetic member and this permanent magnet,
• a magnetic return device is constituted by said at least one static magnetic member and the at least one permanent magnet cooperating magnetically with said at least one static magnetic member, the magnetic return device resulting from all of the magnetic return forces present,
• the magnetic return device applies a magnetic return torque, around the tilting axis, between the tilting support and the chassis, this mechanical return torque having a predetermined threshold value depending on the magnetic return forces applied,
• the tilting support is stabilized, in the chassis, in an angular position corresponding to the disengaged configuration of the clutch, under the effect of the magnetic return torque,
• when activating the actuator, the tilting support tilts around the tilting axis relative to the chassis, depending on the direction of rotation of the electric motor, overcoming the predetermined threshold value of the mechanical return torque, up to to the adoption of one of the first engaged configuration and the second engaged configuration.

According to one embodiment, the chassis carries two distinct static magnetic members respectively associated with two magnetically active wheels constituted respectively by the first and second satellite wheels, and in which for each magnetically active wheel, at least one of its permanent magnets comes position itself opposite the associated static magnetic member, when the tilting support occupies an angular position relative to the chassis corresponding to the disengaged configuration of the clutch, with the interposition of a predetermined air gap counted parallel to the tilting axis of between 0.6 and 1 mm, and more preferably substantially equal to 0.8 mm.

According to one embodiment, whatever the angular position of the tilting support between its extreme positions corresponding to the first and second engaged configurations of the clutch, the at least one static magnetic member is offset transversely by a distance between 1 and 2 mm relative to the plumb of the magnetic element of the tilting support considered parallel to the tilting axis, avoiding magnetic interaction between the at least one static magnetic member and the magnetic element.

According to one embodiment, in each of the first and second engaged configurations of the clutch, the trajectory taken by each permanent magnet carried by the at least one magnetically active wheel during the rotation of said magnetically active wheel relative to the tilting support under the effect of the drive by the actuator is transversely offset by a minimum distance of between 3 and 5 mm relative to the plumb of at least one static magnetic member considered parallel to the axis of rotation of said magnetically wheel active.

According to one embodiment, the at least one static magnetic member comprises at least one permanent magnet whose magnetic pole is opposite the magnetic pole of the at least one permanent magnet carried by the at least one magnetically active wheel.

Summary description of the drawings

• [Fig. 1] La figure 1 est une vue en perspective d'un exemple de serrure montée sur un ouvrant de porte.
• [Fig. 2] La figure 2 est une vue de face partielle d'un exemple de dispositif électromécanique d'actionnement selon l'invention, dans la configuration débrayée.
• [Fig. 3] La figure 3 est une vue en perspective et en éclaté de l'embrayage utilisé dans le dispositif de la figure 2.
• [Fig. 4] La figure 4 est une vue en perspective des éléments de la figure 2.
• [Fig. 5] La figure 5 est une vue schématique illustrant l'embrayage dans la configuration débrayée et la roue de l'organe d'entrainement.
• [Fig. 6] La figure 6 est une vue en perspective montrant le dispositif des figures précédentes au niveau d'une roue de l'embrayage, lequel est dans la configuration débrayée.
• [Fig. 7] La figure 7 est une vue identique à la figure 2, mais dans l'une des deux configurations embrayées.
• [Fig. 8] La figure 8 est une vue schématique illustrant l'embrayage dans l'une des configurations embrayées et la roue de l'organe d'entrainement.

Other aspects, aims, advantages and characteristics of the invention will appear better on reading the following detailed description of preferred embodiments thereof, given by way of non-limiting example, and made with reference to the appended drawings. on which ones :

• [ Fig. 1 ] There figure 1 is a perspective view of an example of a lock mounted on a door opening.
• [ Fig. 2 ] There figure 2 is a partial front view of an example of an electromechanical actuation device according to the invention, in the disengaged configuration.
• [ Fig. 3 ] There Figure 3 is a perspective and exploded view of the clutch used in the device of the figure 2 .
• [ Fig. 4 ] There Figure 4 is a perspective view of the elements of the figure 2 .
• [ Fig. 5 ] There Figure 5 is a schematic view illustrating the clutch in the disengaged configuration and the wheel of the drive member.
• [ Fig. 6 ] There Figure 6 is a perspective view showing the device of the preceding figures at the level of a clutch wheel, which is in the disengaged configuration.
• [ Fig. 7 ] There Figure 7 is a view identical to the figure 2 , but in one of the two engaged configurations.
• [ Fig. 8 ] There figure 8 is a schematic view illustrating the clutch in one of the engaged configurations and the wheel of the drive member.

detailed description

On the figures 1 to 8 and in the remainder of the description, the same references represent identical or similar elements. Furthermore, the different embodiments and variants are not exclusive of each other and can be combined with each other.

The electromechanical actuation device 10 which is visible on the figures 2 to 8 is intended to be mounted on a face 201 of an opening 200 of the door or window type. The electromechanical actuation device 10 is intended to rotate a rotor of a rotary mechanism of the sash.

In the particular example which is not limiting to the field of application, the opening 200 is a door and the rotary mechanism of which a rotor is to be driven thanks to the electromechanical actuation device 10 is a cylinder of a lock mechanism.

Consequently, in the example illustrated here, the opening 200 is for example a door pivotally mounted on a fixed frame or jamb (not shown) connecting the opening 200 to a fixed wall. For example, the face 201 corresponds to a face of the opening 200 intended to be positioned on the interior side of the room closed by the opening 200 and the fixed wall. As can be seen, the opening 200 is here equipped with a lock 100, having a lock cylinder whose rotor is to be driven via the electromechanical actuation device 10. Alternatively, without limitation, the opening 200 could be a window casement, pivoting or sliding, or tilt-and-turn mounting. The principles are in fact identical between a motorized rotary mechanism in the form of a rotor of a lock cylinder of a door lock (to lock and unlock the lock) and a motorized rotary mechanism in the form of a window handle (to lock and unlock the window), in order to carry out these operations without having to overcome the motorization due to the automatic disengagement. It does not matter if, in the case of a tilt-and-turn window, turning the handle also causes the tilt-and-turn opening and closing. of the window by a mechanical return of the rotation of the handle. The disengagement obtained by the electromechanical actuation device 10 is necessary to be able to manually carry out the rotary movement of the lock in the case of the door from the outside via a key or from the inside via the actuation button for this purpose , or to manually perform the rotary movement of the window handle on the interior side.

The lock 100 comprises, in a known manner, for example as described in the document EP2762661A1 , a lock cylinder having a stator mounted on the opening 200 and a rotor rotatably mounted in the stator so as to pass through the thickness of the opening 200. The lock 100 comprises at least one primary lock equipped with a bolt with spring 104 (also known under the terminology "end of stroke bolt" or even "closing bolt") mechanically coupled to the rotor of the lock cylinder and capable of varying, for example by rotation of the rotor, between a closed position in in which the spring bolt 104 is deployed towards the outside of the lock 100 and an open position in which the spring bolt 104 is retracted towards the inside of the lock 100. The lock 100 also includes a spring (not visible in the figures) urging the spring bolt 104 towards the closed position and such that the passage from the closed position to the open position by rotation of the rotor is practiced in opposition to the action of this spring. As visible at figure 1 , the spring bolt 104 comprises a beveled portion, which by reaction against the fixed frame when closing the opening 200, causes a retraction of the spring bolt 104 in the opening 200 against the action of the internal spring, implying also the passage from the closed position to the open position without requiring rotation of the rotor for this purpose.

In this particular example, in the closed position, because it is deployed, the spring bolt 104 is able to be inserted into a striker secured to the fixed frame on which the opening 200 is mounted in order to maintain the opening 200 closed relative to the fixed wall. On the other hand, in its open position, because it is retracted, the spring bolt 104 is no longer inserted in the striker and the opening of the sash 200 is possible.

The lock 100 may also include a secondary lock equipped with a deadbolt 103 (otherwise known under the terminology "bit") mechanically coupled to the rotor 101 of the lock cylinder and capable of varying, by rotation of the rotor 101, between a position of locking in which the deadbolt 103 is deployed relative to the rest of the lock 100 and a locking position in which the deadbolt 103 is retracted into the lock 100. On a certain angular travel, the rotational actuation of the rotor 101 actuates this deadbolt 103 in translation from one position to another. The deadbolt 103 is also able to be inserted in a retractable manner, in the locking position, in a recess of the striker secured to the fixed frame on which the opening 200 is mounted, in order to lock or unlock the lock 100.

The arrangement of such bolts 103, 104 is for example described in the document FR2795120A1 . The lock 100 may also include a handle 105 pivotally mounted on the opening 200 to actuate at least the spring bolt 104.

The rotor of the lock cylinder may comprise, on the exterior side, an exterior lock entry allowing the introduction of a key admitted by the lock 100.

The rotor of the lock cylinder may comprise, on the interior side, either an interior entry allowing the introduction of a key (not shown) admitted by the lock 100, or a coupling member 107, an example of which is visible on the figure 1 , adapted to be rotated, for example by a manual button (not shown). The coupling member 107 is for example a cylinder tail or fork.

For motorized drive via the electromechanical actuation device 10, the rotational coupling with the rotor of the lock cylinder of the lock 100 can be done either via the key previously inserted in the interior entrance of the lock 100, or via the coupling member 107, subject to prior removal of the aforementioned manual button.

The rotational actuation of the rotor of the lock 100 in a motorized manner makes it possible to control the movement of the spring bolt 104 between the opening and closing positions in order, respectively, to open and close the opening 200 and/or to control the movement of the deadbolt 103 between the locking and unlocking positions in order, respectively, to lock and unlock the lock 100 and therefore the opening 200 relative to the fixed frame.

The electromechanical actuation device 10 comprises a frame 11 in one or more parts, intended to be fixed on the face 201 of the opening 200. The frame 11 is provided with a proximal face 12 and fixing elements 13 allowing to fix the frame 11 on the opening 200 in a manner placing the proximal face 12 of the frame 11 against the face 201 of the opening 200. The fixing elements 13 are for example in the form of holes each adapted to the installation of a screw retaining the frame 11 against the opening 200 by engaging in the opening 200. It is possible to provide the presence of a damping material between the face 201 of the opening 200 and the proximal face 12 of the frame 11, to ensure a damped mechanical connection between the electromechanical actuation device 10 and the opening 200 for vibrational and mechanical decoupling.

The electromechanical actuation device 10 comprises a drive member 14 movable in rotation relative to the chassis 11 and intended to be coupled to one end of the rotor of the lock cylinder of the lock 100, in particular at its end on the interior side , when the frame 11 is fixed on the face 201 of the opening 200. This mechanical coupling can, as explained previously, be carried out via a key previously inserted into the interior entrance of the lock 100 or via the coupling member 107. Depending on the variant selected, the drive member 14 is adapted accordingly and comprises rotational coupling elements suitable for cooperation either with the key or with the member coupling 107.

The electromechanical actuation device 10 may also include a rotary operating button (not shown) adapted for manual grip and for manually driving the drive member 14, ultimately making it possible to manually rotate the rotor of the lock cylinder of the lock when it is coupled in rotation to the drive member 14.

The electromechanical actuation device 10 comprises an actuator 15 comprising an electric motor and making it possible to electrically rotate the drive member 14 either in a first direction of rotation adapted to move the spring bolt 104 from its closed position towards its open position and/or move the deadbolt 103 from the locking position to the unlocking position, i.e. in a second direction of rotation opposite to the first direction of rotation authorizing passage of the spring bolt 104 from position d opening to the closed position and/or controlling the movement of the deadbolt 103 from its unlocking position to the locking position.

In order to be able to manually rotate the rotor of the lock cylinder of the lock via the operating button of the electromechanical actuation device 10 or by the external key, it is necessary to uncouple the drive member 14 by relative to the actuator 15. The electromechanical actuation device 10 comprises, for this purpose, a clutch 16 connecting the electric motor of the actuator 15 to the drive member 14.

The electromechanical actuation device 10 comprises an independent electrical energy source, for example from a battery, accumulator or pile, to power the actuator 15 on the one hand, and an electronic control unit on the other hand programmable, of microcontroller type, suitable for communication with the outside via means of communication of the radio frequency type, wifi, Bluetooth, or equivalent such as for example ZIGBEE, Zwave or proprietary protocols, in particular with a view to receiving external instructions and the transmission of outgoing information. The electronic control unit ensures control of the actuator 15 based on these instructions and this information and as a function of possible sensors integrated in the electromechanical actuation device 10, for example force sensors, pressure sensors. position sensors, distance sensors, speed sensors or presence sensors. The electrical energy source can also be used to power these various sensors if necessary. The electronic control unit contains all the algorithms necessary for the operation of the assembly, these algorithms developing the control strategy of the different actuators including actuator 15, based on external instructions and information received from the various sensors mentioned above. . These arrangements are classic in the field and within the reach of those skilled in the art who are able to adapt these elements.

The clutch 16 varies between a disengaged configuration and two different engaged configurations adapted to rotation of the drive member 14 by the actuator 15. In the disengaged configuration, the electric motor of the actuator 15 is not not coupled to the drive member 14. Conversely, in a first engaged configuration, the electric motor of the actuator 15 is coupled to the drive member 14 to ensure rotational drive of the drive member 14 electrically via the electric motor of the actuator 15 in the first direction of rotation. In a second engaged configuration, the electric motor of the actuator 15 is coupled to the drive member 14 to ensure the rotational drive of the drive member 14 electrically via the electric motor of the actuator 15 in the second direction of rotation.

As is visible on the figures 2 to 8 , the clutch 16 comprises a driving wheel 17 rotating relative to the chassis 11 and rotated by the actuator 15. Typically, the driving wheel 17 is mounted to rotate freely on the chassis 11 and is itself rotated by the output of a speed reducer whose input is rotated by an output shaft of the electric motor of the actuator 15.

The clutch 16 also comprises a driven wheel 18 linked in rotation with the drive member 14. Typically, the driven wheel 18 is integral in rotation with the drive member 14 around the axis of rotation of the drive member 14 relative to the chassis 11, this axis of rotation being moreover intended to be substantially aligned, in use, with the axis rotation of the rotor of the rotating mechanism of the sash. For example, the driven wheel 18 can be formed by elements coming from one piece with the rest of the drive member 14.

The clutch 16 also comprises a tilting support 19 capable of tilting in a bidirectional manner relative to the chassis 11 around a tilting axis 20. According to an embodiment facilitating the transmission of movements and limiting internal losses, the axis of tilting 20 around which the tilting support 19 tilts relative to the chassis 11 coincides with the axis of the driving wheel 17. It remains, however, that it would be possible to provide for the tilting axis 20 to be positioned between the driving wheel 17 and the driven wheel 18, for example by being positioned on a straight line passing through the axis of rotation of the driving wheel 17 and through the axis of rotation 22 of the driven wheel 18. The tilting axis 20 is parallel to the axis of rotation of the driving wheel 17 and parallel to the axis of rotation 22 of the driven wheel 18.

With a view to manual training, it can be provided that the previously mentioned rotary operating button, which is not illustrated as such, is integral with a drive wheel 23 positioned around the electric motor of the actuator 15. This drive wheel 23, when it is rotated by manual force via the rotary operating button which comes to cover the drive wheel 23, rotates the driven wheel 18 via an intermediate wheel absent in the figures, engaged both with the drive wheel 23 and with the driven wheel 18. In other words, the axis of the operating button is offset relative to the axis of the organ drive 14. The fact that the drive wheel 23 and the actuator 15 are housed in the rotary operated button makes it possible to optimize the overall size and makes it possible to avoid finger trapping phenomena for a hand operating the handle 105. Transmission from the drive wheel 23 to the driven wheel 18 is particularly possible when the clutch 16 has previously been placed in the disengaged configuration.

According to a particular embodiment, the electromechanical actuation device 10 comprises a mechanical torque limiting mechanism 24 which varies between a deactivated configuration in which the operating button is coupled in rotation with the drive wheel 23 and an activated configuration. in which the operating button and the drive wheel 23 are separated in rotation. The activated configuration is automatically adopted as soon as a mechanical torque having a value greater than a predetermined value for which the mechanical torque limiting mechanism 24 is designed is applied manually to the operating button and the deactivated configuration is automatically adopted otherwise, that is to say as long as the mechanical torque applied manually to the operating button is less than or equal to this value predetermined.

The presence of the mechanical torque limiting mechanism 24 is advantageous to avoid any risk of deterioration of the transmission between the operating button and the drive member 14 when very high forces are applied to the operating button, particularly in the event of break-in, or in the event of seizure of the rotor of the rotating mechanism.

According to a non-limiting embodiment, the mechanical torque limiting mechanism 24 comprises at least one radially movable detent projection 25 capable of inserting retractably into a complementary locking notch formed in the operating button. Each latching projection 25 is urged radially towards the inside of the locking notch thanks to elastic means 26. The elastic means 26 are for example constituted by an oblong-shaped part visible on the figure 2 made of an elastically deformable material, the two latching projections 25 being arranged projecting from the two long edges of this part. The shape and material of the oblong part make it possible in particular to adjust the predetermined value beyond which the operating button is uncoupled in rotation relative to the drive wheel 23.

The clutch 16 also comprises a coupling device carried by the tilting support 19, generally positioned between the driving wheel 17 and the driven wheel 18 and capable of carrying out selective coupling of the driving wheel 17 to the driven wheel 18. More precisely, this coupling device comprises at least one satellite wheel 27 engaged with the driving wheel 17 permanently and movable in rotation relative to the tilting support 19 along an axis of rotation 28 eccentric with respect to the tilting axis 20. axis of rotation 28 of said at least one satellite wheel 27 thus moves around the axis of tilting 20 jointly with the tilting support 19. By tilting, the tilting support 19 causes the axis of rotation 28 of each satellite wheel to move 27 following a circular translation segment, the angle covered being equal to the tilting angle of the tilting support 19 relative to the chassis 11. It is understood here that the number of satellite wheel 27 can be equal to 1, but more preferably greater than or equal to 2 in order to limit the angular amplitude of tilting of the tilting support 19 to pass from the first engaged configuration to the second engaged configuration and vice versa. The satellite wheel 27 can be offset from the tilting support 19 on which it is mounted along the axis of rotation 28. A silicone washer (not shown), allowing the free rotation of the satellite wheel relative to the tilting support 19 can be provided between the satellite wheel 27 and the tilting support 19.

By the preceding arrangements, the clutch 16 can vary between the first engaged configuration, the second engaged configuration and the disengaged configuration, by a simple angular tilting movement of the tilting support 19 around the tilting axis 20 relative to the chassis 11 .

In the disengaged configuration as visible on the figures 2 , 5, 6 no satellite wheel 27 of the coupling device is engaged with the driven wheel 18.

In the first engaged configuration as visible on the Figure 7 , resulting from a tilting movement of the tilting support 19 in the first direction S1 indicated on the Figure 7 , a satellite wheel 27 of the coupling device is engaged with the driven wheel 18 in a first circumferential zone 181 of the driven wheel 18 so that the actuator 15 drives, via the clutch 16, the rotor of the rotary mechanism in the first direction of rotation P1, mentioned previously.

Conversely, in the second engaged configuration illustrated on the figure 8 , which results from a tilting movement of the tilting support 19 in the second direction S2 opposite the first direction S1, a satellite wheel 27 of the coupling device is engaged with the driven wheel 18 in a second circumferential zone 182 of the wheel carried out 18 so that the actuator 15 drives, via the clutch 16, the rotor of the rotary mechanism in the second direction of rotation P2, mentioned previously.

It is understood from the above that the same satellite wheel 27 can possibly, in a manner not shown, be used for each of the first and second engaged configurations. Alternatively, as shown and for the advantages already mentioned, two separate satellite wheels 271, 272 can be provided, each being permanently engaged with the driving wheel 17 but only the satellite wheel 271, mounted on the tilting support 19 by its axis of rotation 28, is engaged with the first circumferential zone 181 of the driven wheel 18 in the first engaged configuration and only the satellite wheel 272, mounted on the tilting support 19 by its axis of rotation 28, is engaged with the second circumferential zone 182 of the driven wheel 18 in the second engaged configuration. None of the satellite wheels 271, 272 is engaged with the driven wheel 18 in the disengaged configuration (for example figure 2 ).

At least one magnetically active wheel chosen from the group consisting of the driving wheel 17 and said at least one satellite wheel 27 of the coupling device carries at least one permanent magnet 29 arranged in such a way that said at least one permanent magnet 29 is mobile in rotation relative to the tilting support 19 together with the magnetically active wheel which carries said at least one permanent magnet 29.

A permanent magnet can typically be a neodymium magnet composed of an alloy of neodymium, iron and boron, or based on ferrite, or an alloy of iron with essentially aluminum, nickel and cobalt

The fact of providing at least one permanent magnet 29 on said at least a magnetically active wheel as defined above, where each permanent magnet 29 can therefore cooperate magnetically with the tilting support 19 and/or with a magnetic member integral with the chassis 11 as will be developed further, makes it possible to propose an electromechanical actuation device 10 which is reliable, which requires little maintenance, which is economical, and which avoids any risk of malfunction, in particular but not exclusively in the event of shock or vibration.

The different wheels used for the operation of the clutch 16 are here toothed wheels adapted to engage by mutual engagement interspersed with the teeth of two wheels cooperating with each other. But alternatively it could be wheels cooperating with each other only by friction, adhesion depending on Coulomb's law.

Each permanent magnet 29 generates a globally oriented magnetic field, in the vicinity of at least one of the axial faces of the magnetically active wheel which carries it, substantially parallel to the axis of rotation 21, 28 of the magnetically active wheel which carries it. door.

According to one embodiment, the coupling device comprises the first and second satellite wheels 271, 272 mentioned above, which are mounted to rotate relative to the tilting support 19 around first and second axes of rotation 28 arranged, as is visible on the figures, on either side of the driving wheel 17 and in engagement with the driving wheel 17.

According to another preferred embodiment, at least one magnetically active wheel chosen from the first satellite wheel 271 and the second satellite wheel 272 carries at least one magnetic assembly including at least two permanent magnets 29 arranged at respective locations distributed angularly around the axis of rotation 28 of the magnetically active wheel which carries said magnetic assembly. The location of each of the permanent magnets 29 of said magnetic assembly is radially offset relative to the axis of rotation 28 of the magnetically active wheel which carries it so that the permanent magnet 29 is movable in rotation relative to the tilting support 19 jointly with the magnetically active wheel that carries it.

In the non-limiting example as illustrated, the first satellite wheel 271 carries a magnetic assembly including four permanent magnets 29 arranged at respective locations distributed angularly at constant pitches around the axis of rotation 28 of the first satellite wheel 271 which wears this magnetic set. The second satellite wheel 272 also carries a magnetic assembly including four permanent magnets 29 arranged at respective locations angularly at constant pitches around the axis of rotation 28 of the second satellite wheel 272 which carries this magnetic assembly.

The fact that the permanent magnets 29 are discrete and distributed angularly around the axis of rotation 28 of the first satellite wheel 271, respectively around the axis of rotation 28 of the second satellite wheel 272, ensures the presence of one of the permanent magnets in cooperation with the tilting support 19, whatever the angle of rotation of the satellite wheel 271 or the satellite wheel 272 when the latter is stopped.

According to an alternative embodiment, the permanent magnet(s) 29 are mounted on the driving wheel 17, in place of the satellite wheels 271, 272.

There Figure 3 provides details on the organization of the clutch 16, which includes a tilting support 19 comprising a first plate 191 and a second plate 192 arranged parallel to each other at a distance from each other. Two cylindrical axes 193 project from the first plate 191 towards the second plate 192. They are each secured at their remote end to the second plate 192, creating a single piece assembly. Each of the cylindrical axes 193 plays the role of the aforementioned rotation axis 28 for the two satellite wheels 271, 272, which are mounted axially on a respective cylindrical axis 193 in an axial position placed between the two plates 191, 192. The first plate comprises an opening 194, which allows the component part of the drive shaft of the driving wheel 17 to pass on either side of the first plate 191, so that the driving wheel 17 is also positioned between the two plates 191, 192.

According to an advantageous embodiment, the tilting support 19 comprises an element sensitive to a magnetic field, called a magnetic element, capable of magnetically cooperating with each permanent magnet 29 carried by each magnetically active wheel, when the magnetic element is located in the magnetic field generated by the corresponding permanent magnet 29, in a manner creating a magnetic force of interaction between the magnetic element and the permanent magnet 29 considered. This makes it possible to create at lower cost, in a low manner and without mechanical friction, magnetic forces which can be used for magnetic clutch purposes, as explained below. This interaction force can in particular have the same effects as the mechanical friction applied to the silicone washers by means of the spring washers described in the document WO2017/114534A1 .

The clutch 16 can thus comprise a magnetic clutch device associated with each magnetically active wheel where each magnetic clutch device is constituted by the magnetic element and the at least one permanent magnet 29 carried by the associated magnetically active wheel. The magnetic clutch device results in fact from the magnetic force of interaction between each permanent magnet 29 carried by the associated magnetically active wheel (the driving wheel 17 and/or at least one of the satellite wheels 271, 272) and the magnetic element. Each magnetic clutch device applies a magnetic return torque, around the axis of rotation 21, 28 of the magnetically active wheel associated with this magnetic clutch device, between the tilting support 19 and the magnetically active wheel associated with said device magnetic clutch, the magnetic return torque having a predetermined nominal value depending on the magnetic force of interaction between each permanent magnet 29 carried by the associated magnetically active wheel and the magnetic element.

Thus, each magnetic clutch device ensures that the tilting support 19 and the magnetically active wheel associated with this magnetic clutch device are coupled in rotation when the mechanical torque applied to the associated magnetically active wheel is less than the nominal value, and that the tilting support 19 and the associated magnetically active wheel are decoupled in rotation when the mechanical torque applied to the associated magnetically active wheel is greater than or equal to the nominal value.

Such magnetic forces make it possible to convert a rotation of the driving wheel 17 into a movement of the tilting support 19 and of the satellite wheels 271, 272 as long as one of the satellite wheels 271, 272 is not engaged with the driven wheel 18 , then allow the tilting support 19 to stop its tilting while the driving wheel 17 continues to drive the satellite wheels 271, 272 in rotation by tilting ratio 19, and the driven wheel 18 relative to the chassis 11, exceeding the nominal magnetic torque values mentioned above.

According to one embodiment, for each magnetically active wheel, at least two permanent magnets 29 are located, whatever the angular position of the magnetically active wheel considered relative to the tilting support 19, directly above the magnetic element with interposition of a predetermined air gap counted parallel to the axis of rotation 21, 28 of said magnetically active wheel 17, 271, 272 and between 0.6 and 1 mm, and more preferably substantially equal to 0.8 mm.

For simplicity, good efficiency and reduced cost, the magnetic element of the tilting support 19 is constituted by a plate comprising a ferromagnetic material arranged directly above at least one of the axial faces of each magnetically active wheel 17 , 271, 272 with the interposition of a predetermined interval of between 0.2 and 0.6 mm, and more preferably substantially equal to 0.4 mm. Such a ferromagnetic material is for example cobalt or iron. The plate made of ferromagnetic material may in particular consist of the first plate 191 and/or the second plate 192. The material is typically a DX51D type steel.

According to a non-limiting embodiment, the chassis 11 comprises at least one static magnetic member 30 capable of being positioned, when the clutch 16 occupies its disengaged configuration, in the magnetic field generated by at least one permanent magnet 29 of the at least one magnetically active wheel, creating a magnetic restoring force between the static magnetic member 30 and this permanent magnet 29.

This makes it possible to create at lower cost, in a low manner and without mechanical friction, magnetic forces which can be used for the purpose of magnetic balancing of the tilting support 19 in a position corresponding to the disengaged configuration, as explained below. After.

Thus, a magnetic return device is constituted by said at least one static magnetic member 30 and the at least one permanent magnet 29 cooperating magnetically with the at least one static magnetic member 30. The magnetic return device results from all the forces return magnetics thus present by this phenomenon. The magnetic return device applies a magnetic return torque, around the tilting axis 20, between the tilting support 19 and the chassis 11, this mechanical return torque having a predetermined threshold value depending on the magnetic return forces applied. Thus, the tilting support 19 is stabilized, in the chassis 11, in an angular position corresponding to the disengaged configuration of the clutch 16, under the effect of the magnetic return torque.

When the actuator 15 is activated, the tilting support 19 tilts around the pivot axis 20 relative to the chassis 11, depending on the direction of rotation of the electric motor, overcoming the predetermined threshold value of the mechanical torque of recall, until the adoption of one of the first engaged configuration and the second engaged configuration.

The fact that the at least one permanent magnet 29 is carried by one of the satellite wheels 271, 272, rather than by the tilting support 19, ensures excellent stability, and this over an angular range of the tilting support 19 which is significantly greater . This increases reliability or any risk of malfunction in the event of a large shock or strong vibrations.

According to a non-limiting embodiment, and according to illustrated arrangements, the chassis 11 carries two distinct static magnetic members 30 respectively associated with two magnetically active wheels constituted respectively by the first and second satellite wheels 271, 272. This ensures the principle balancing at two different locations, and moreover advantageously positioned on either side of the tilting axis 20 of the tilting support 19. The reliability and guarantee of the support provided are reinforced.

In practice, it may be advantageous for each magnetically active wheel, at least one of its permanent magnets 29 to be positioned opposite the associated static magnetic member 30, when the tilting support 19 occupies a position angular relative to the chassis 11 corresponding to the disengaged configuration of the clutch 16, with the interposition of a predetermined air gap counted parallel to the tilting axis 20 of between 0.6 and 1 mm, and more preferably substantially equal to 0, 8mm.

As illustrated in the figures, whatever the angular position of the tilting support 19 between its extreme positions corresponding to the first and second engaged configurations of the clutch 16, the at least one static magnetic member 30 is offset transversely by a distance 31 between 1 and 2 mm relative to the plumb of the magnetic element of the tilting support 19 considered parallel to the tilting axis 20, avoiding magnetic interaction between the at least one static magnetic member 30 and the magnetic element .

According to a preferred embodiment, in each of the first and second engaged configurations of the clutch 16, the trajectory taken by each permanent magnet 29 carried by the at least one magnetically active wheel during the rotation of said magnetically active wheel relative to the tilting support 19 under the effect of the drive by the actuator 15 is transversely offset by a minimum distance 32 included between 3 and 5 mm relative to the plumb of at least one static magnetic member 30 considered parallel to the axis of rotation 21, 28 of said magnetically active wheel.

Preferably, the at least one static magnetic member 30 comprises at least one permanent magnet whose magnetic pole is opposite the magnetic pole of the at least one permanent magnet 29 carried by the at least one magnetically active wheel. Thus, the static magnetic member 30 and the permanent magnet 29 attract each other.

• par coopération avec l'élément magnétique du support basculant 19, il assure le couple de friction nécessaire au déplacement du support basculant 19 vers l'une ou l'autre des configurations embrayées ou débrayée ;
• par coopération avec l'organe magnétique statique, il assure le maintien statique du support basculant 19 dans la configuration débrayée.

The embodiments presented above can be combined advantageously. In this case, the same permanent magnet 29 provides a double function:

• by cooperation with the magnetic element of the tilting support 19, it ensures the friction torque necessary for moving the tilting support 19 towards one or the other of the engaged or disengaged configurations;
• by cooperation with the static magnetic member, it ensures the static maintenance of the tilting support 19 in the disengaged configuration.

Claims (14)

1. An electromechanical actuating device (10) for a door or window type-opening leaf (200), the electromechanical actuating device (10) being intended to drive in rotation a rotor of a rotary mechanism of the opening leaf such as a cylinder of a latch mechanism, the electromechanical actuating device (10) comprising:

   - a frame (11) intended to be fastened to a face (201) of the opening leaf (200),

   - a drive member (14), movable in rotation relative to the frame (11), and capable of being coupled in rotation to the rotor of the rotary mechanism when the frame (11) is fastened to the face (201) of the opening leaf (200),

   - an actuator (15) comprising an electric motor and allowing electrically driving in rotation the drive member (14) selectively in a first direction of rotation (P1) and a second direction of rotation (P2),

   - a clutch (16) connecting the electric motor to the drive member (14), wherein the clutch (16) comprises:

   - a driving gear (17) rotatable relative to the frame (11) and driven in rotation by the actuator (15),

   - a driven gear (18) connected in rotation to the drive member (14),

   - a tilting support (19) capable of bidirectionally tilting relative to the frame (11) about a tilting axis (20),

   - a coupling device comprising at least one planet gear (27) engaged with the driving gear (17) and movable in rotation relative to the tilting support (19) according to an axis of rotation (28) eccentric relative to the tilting axis (20), the axis of rotation (28) of said at least one planet gear (27) being displaced about the tilting axis (20) together with the tilting support (19), wherein the clutch (16) varies, by tilting the tilting support (19), between:

   - a first engaged configuration in which a planet gear (27) of the coupling device is engaged with the driven gear (18) in a first circumferential area (181) of the driven gear (18) so that the actuator (15) drives, via the clutch (16), the rotor of the rotary mechanism in the first direction of rotation (P1),

   - a second engaged configuration in which a planet gear (27) of the coupling device is engaged with the driven gear (18) in a second circumferential area (182) of the driven gear (18) so that the actuator (15) drives, via the clutch (16), the rotor of the rotary mechanism in the second direction of rotation (P2),

   - a disengaged configuration in which no planet gear (27) of the coupling device is engaged with the driven gear (18),
   characterized in that at least one magnetically active gear selected from the group consisting of the driving gear (17) and said at least one planet gear (27) of the coupling device carries at least one permanent magnet (29) arranged in such a manner that said at least one permanent magnet (29) is movable in rotation relative to the tilting support (19) together with the magnetically active gear which carries said at least one permanent magnet (29), the at least one permanent magnet (29) magnetically cooperating with the tilting support (19) and/or the at least one permanent magnet (29) magnetically cooperating with a magnetic member secured to the frame (11).
2. The electromechanical actuating device (10) according to claim 1, wherein the tilting axis (20) about which the tilting support (19) tilts relative to the frame (11) is coincident with the axis (21) of the driving gear (17).
3. The electromechanical actuating device (10) according to any of claims 1 or 2, wherein said at least one permanent magnet (29) generates a generally oriented magnetic field, in the vicinity of at least one of the axial faces of the magnetically active gear carrying it, substantially parallel to the axis of rotation (21, 28) of the magnetically active gear which carries said at least one permanent magnet (29).
4. The electromechanical actuating device (10) according to any of claims 1 to 3, wherein the coupling device comprises distinct first and second planet gears (271, 272), mounted in rotation relative to the tilting support (19) about the first and second axes of rotation (28) disposed on either side of the driving gear (17) and engaged with the driving gear (17), the first planet gear (271) being engaged with the driven gear (18) in its first circumferential area (181) in the first engaged configuration, the second planet gear (272) being engaged with the driven gear (18) in its second circumferential area (182) in the second engaged configuration, none of the first and second planet gears (271, 272) being engaged with the driven gear (18) in the disengaged configuration, and wherein at least one magnetically active gear selected from the first planet gear (271) and the second planet gear (272) carries at least one magnetic assembly including at least two permanent magnets (29) arranged at respective locations angularly distributed about the axis of rotation (28) of the magnetically active gear which carries said magnetic assembly, the location of each of the permanent magnets (29) of said magnetic assembly being radially offset relative to the axis of rotation (28) of the magnetically active gear carrying it so that the permanent magnet (29) is movable in rotation relative to the tilting support (19) together with the magnetically active gear carrying it.
5. The electromechanical actuating device (10) according to claim 4, wherein each of the first and second planet gears (271, 272) comprises such a magnetic assembly, which comprises a plurality of permanent magnets (29) angularly distributed about the axis of rotation (28) of the corresponding magnetically active gear.
6. The electromechanical actuating device (10) according to any of claims 4 or 5, wherein each magnetic assembly comprises at least four distinct permanent magnets (29) angularly distributed with constant pitches about the axis of rotation (20) of the magnetically active gear which carries said magnetic assembly.
7. The electromechanical actuating device (10) according to any of claims 1 to 6, wherein:

   - the tilting support (19) includes a magnetic element likely to magnetically cooperate with each permanent magnet (29) carried by each magnetically active gear, when the magnetic element is located in the magnetic field generated by the corresponding permanent magnet (29), in a manner creating a magnetic force of interaction between the magnetic element and the relevant permanent magnet (29),

   - the clutch (16) comprises a magnetic clutch device associated with each magnetically active gear,

   - each magnetic clutch device consists of the magnetic element and the at least one permanent magnet (29) carried by the associated magnetically active gear,

   - the magnetic clutch device resulting from the magnetic force of interaction between each permanent magnet (29) carried by the associated magnetically active gear and the magnetic element,

   - each magnetic clutch device applies a magnetic restoring torque, about the axis of rotation (21) of the associated magnetically active gear to said magnetic clutch device, between the tilting support (19) and the magnetically active gear associated with said magnetic clutch device, the magnetic restoring torque having a predetermined nominal value depending on the magnetic force of interaction between each permanent magnet (29) carried by the associated magnetically active gear and the magnetic element,

   - each magnetic clutch device ensures that the tilting support (19) and the magnetically active gear associated with said magnetic clutch device are coupled in rotation when the mechanical torque applied to said associated magnetically active gear is lower than the nominal value, and that the tilting support (19) and said associated magnetically active gear are decoupled in rotation when the mechanical torque applied to said associated magnetically active gear is larger than or equal to the nominal value.
8. The electromechanical actuating device (10) according to claim 7, wherein for each magnetically active gear, at least two permanent magnets (29) are located, regardless of the angular position of the relevant magnetically active gear relative to the tilting support (19), in vertical alignment with the magnetic element with the interposition of a predetermined air gap counted parallel to the axis of rotation (28) of said magnetically active gear and comprised between 0.6 and 1 mm, and more preferably substantially equal to 0.8 mm.
9. The electromechanical actuating device (10) according to any of claims 7 or 8, wherein the magnetic element of the tilting support (19) consists of a plate (191, 192) comprising a ferromagnetic material arranged in vertical alignment with at least one of the axial faces of each magnetically active gear with the interposition of a predetermined interval comprised between 0.2 and 0.6 mm, and more preferably substantially equal to 0.4 mm.
10. The electromechanical actuating device (10) according to any one of claims 1 to 9, wherein:

    - the frame (11) includes at least one static magnetic member (30) likely to be positioned, when the clutch (16) occupies its disengaged configuration, in the magnetic field generated by at least one permanent magnet (29) of the at least one magnetically active gear, creating a magnetic restoring force between the static magnetic member (30) and this permanent magnet (29),

    - a magnetic restoring device consists of said at least one static magnetic member (30) and the at least one permanent magnet (29) magnetically cooperating with said at least one static magnetic member (30), the magnetic restoring device resulting from the set of the present magnetic restoring forces,

    - the magnetic restoring device applies a magnetic restoring torque, about the tilting axis (20), between the tilting support (19) and the frame (11), this mechanical restoring torque having a predetermined threshold value depending on the applied magnetic restoring forces,

    - the tilting support (19) is stabilized, in the frame (11), in an angular position corresponding to the disengaged configuration of the clutch (16), under the effect of the magnetic restoring torque,

    - during the activation of the actuator (15), the tilting support (19) tilts about the tilting axis (20) relative to the frame (11), depending on the direction of rotation of the electric motor, by overcoming the predetermined threshold value of the mechanical restoring torque, until assuming one of the first engaged configuration and the second engaged configuration.
11. The electromechanical actuating device (10) according to any of claims 4 to 6 and claim 10, wherein the frame (11) carries two distinct static magnetic members (30) respectively associated with two magnetically active gears respectively consisting of the first and second planet gears (271, 272), and wherein for each magnetically active gear, at least one of its permanent magnets (29) is positioned facing the associated static magnetic member (30), when the tilting support (19) occupies an angular position relative to the frame (11) corresponding to the disengaged configuration of the clutch (16), with the interposition of a predetermined air gap counted parallel to the tilting axis (20) comprised between 0.6 and 1 mm, and more preferably substantially equal to 0.8 mm.
12. The electromechanical actuating device (10) according to any of claims 7 to 9 and according to any of claims 10 or 11, wherein regardless of the angular position of the tilting support (19) between its extreme positions corresponding to the first and second engaged configurations of the clutch (16), the at least one static magnetic member (30) is transversely offset by a distance (31) comprised between 1 and 2 mm relative to the vertical axis of the magnetic element of the tilting support (19) considered parallel to the tilting axis (20), avoiding a magnetic interaction between the at least one static magnetic member (30) and the magnetic element.
13. The electromechanical actuating device (10) according to any of claims 1 to 12, wherein in each of the first and second engaged configurations of the clutch (16), the trajectory taken by each permanent magnet (29) carried by the at least one magnetically active gear during the rotation of said magnetically active gear relative to the tilting support (19) as a result of driving by the actuator (15) is transversely offset by a minimum distance (32) comprised between 3 and 5 mm relative to the vertical axis of the at least one static magnetic member (30) considered parallel to the axis of rotation (21, 28) of said magnetically active gear.
14. The electromechanical actuating device (10) according to any of claims 10 to 13, wherein the at least one static magnetic member (30) comprises at least one permanent magnet whose magnetic pole is opposite to the magnetic pole of the at least one permanent magnet (29) carried by the at least one magnetically active gear.

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