Electromechanical actuator and system comprising such an actuator

Description

[0001] The present invention relates to an electromechanical actuator for a shutter, blind, or sun protection system. The electromechanical actuator comprises a gearbox with at least one epicyclic reduction stage.

[0002] The present invention also relates to a closure, shading or sun protection installation comprising a screen that can be rolled up on a winding tube driven in rotation by such an electromechanical actuator.

[0003] In general, the present invention relates to the field of blackout devices comprising a motorized drive device moving a screen, between at least a first position and at least a second position.

[0004] A motorized drive device includes an electromechanical actuator of a movable closing, obscuring or sun protection element such as a shutter, a door, a grille, a blind or any other equivalent material, hereafter referred to as a screen.

[0005] Electromechanical actuators for shutters, blinds, or sunshades are already known, comprising an electric motor and a gearbox. The gearbox includes an input shaft, a plurality of epicyclic reduction stages, a ring gear, and an output shaft. Each reduction stage includes a planetary gear, a plurality of sun gears, and a ring gear. At each reduction stage, the planetary gear meshes with each sun gear in the gearbox assembly. The ring gear has internal teeth. Each sun gear meshes with the internal teeth of the ring gear in the gearbox assembly. Furthermore, each sun gear is a single piece with teeth made from a single component. The planetary gear, sun gears, and ring gear are all made of the same metallic material.

[0006] However, these electromechanical actuators have the disadvantage of generating uneven contact pressure along the length of the engagement between each planetary gear and the planetary gear, or even a complete absence of contact pressure at one end of each planetary gear, particularly at the final reduction stage of the gearbox, when the gearbox input shaft is rotated by the electromechanical actuator's electric motor. The final reduction stage is the reduction stage located closest to an output shaft of the electromechanical actuator in an assembled configuration.

[0007] In addition, these electromechanical actuators have the disadvantage of using only a portion of the planetary gear's engagement length with the satellite gears to transmit force between the planetary gear and the satellite gears when the reducer's input shaft is driven into rotation by an activation of the electromechanical actuator's electric motor.

[0008] Therefore, wear on the teeth of each satellite gear is observed over only a portion of the engagement length of each satellite gear with the planetary gear.

[0009] Furthermore, such a non-uniform distribution of contact pressure along the length of contact of each satellite gear with the planetary gear generates excessive stress on one tooth of the planetary gear, which can cause breakage of the planetary gear teeth.

[0010] Moreover, such a construction of the reduction stages of the reducer and, more particularly, of the last reduction stage generates a non-optimal distribution of forces between two points of contact according to the length of engagement of each satellite pinion with the planetary pinion, when the input shaft of the reducer is driven in rotation by an activation of the electric motor of the electromechanical actuator.

[0011] To remedy such a situation, it can be considered, in a conventional way, to stiffen all the elements constituting the reducer, in particular the planetary pinion, the satellite pinions and the ring gear, so as to limit an angular deformation of these elements.

[0012] However, such a stiffening of the elements constituting the reducer does not resolve the previously mentioned drawbacks, since wear of the teeth of each satellite pinion can be observed.

[0013] Document WO 2006 / 107602 A2 describes an electromechanical actuator for a shutter, blind, or sun protection system. The electromechanical actuator comprises an electric motor and a gearbox. The gearbox has two epicyclic reduction stages. The first reduction stage includes a planetary gear, a ring gear, and a plurality of sun gears. The ring gear has internal teeth. The planetary gear is configured to cooperate with each sun gear in the gearbox assembly, and each sun gear meshes with the internal teeth of the ring gear in the gearbox assembly. The second reduction stage has the same characteristics as the first reduction stage. In addition, an output shaft from the electric motor is coupled to the planetary gear of the first reduction stage.

[0014] Document EP 3 203 112 A1 describes a gearbox configured for coupling to an electric motor. The gearbox comprises two epicyclic reduction stages. The first reduction stage includes a planetary gear, a ring gear, and a plurality of sun gears. The ring gear has a first internal tooth profile. The planetary gear is configured to cooperate with each sun gear in the gearbox assembly, and each sun gear meshes with the first internal tooth profile of the ring gear in the gearbox assembly. The second reduction stage includes a planetary gear, a ring gear (the same as that of the first reduction stage), a plurality of first sun gears, and a plurality of second sun gears. The ring gear has a second internal tooth profile.The planetary gear is configured to cooperate with each planetary gear in the assembled gearbox configuration, and each planetary gear meshes with the second internal tooth set of the ring gear in the assembled gearbox configuration. Furthermore, the electric motor is coupled to the planetary gear of the first reduction stage. Additionally, the first and second planetary gears of the second reduction stage constitute a first set of teeth and a second set of teeth. The first and second planetary gears are separated from each other along a direction parallel to a rotation axis of the gearbox and connected by an additional element.

[0015] The present invention aims to resolve the aforementioned drawbacks and to provide an electromechanical actuator for a closing, shading or solar protection installation comprising a reducer having at least one epicyclic reduction stage, as well as a closing, shading or solar protection installation comprising such an electromechanical actuator, allowing to improve a distribution of contact pressure, along a length of engagement of satellite gears with a planetary gear.

[0016] In this regard, the present invention relates, according to a first aspect, to an electromechanical actuator for a closing, shading or solar protection system comprising at least: an electric motor, and a gearbox, the gearbox comprising an input shaft, the reducer comprising at least one reduction stage of epicyclic type, said at least one reduction stage comprising at least: a planetary pinion, a ring gear, the ring gear comprising internal teeth, and a plurality of satellite pinions, the planetary pinion cooperating with each satellite pinion and each satellite pinion being meshed with the internal teeth of the ring gear.

[0017] According to the invention, each planetary gear comprises at least a first toothed portion and a second toothed portion. The first and second toothed portions of each planetary gear are separated from each other along a direction parallel to an axis of rotation of the gearbox, so as to allow an angular offset between them when the gearbox input shaft is rotated. The planetary gear and the planetary gears are made of a first material. The ring gear is made of a second material. The stiffness of the first material of the planetary gear and the planetary gears is greater than the stiffness of the second material of the ring gear, the stiffness of the first material of the planetary gear and the planetary gears and the stiffness of the second material of the ring gear being defined by the Young's moduli of these materials.The stiffness of the first material of the planetary gear and the planetary gears, and the stiffness of the second material of the ring gear, are expressed in megapascals (MPa). The Young's modulus of the first material of the planetary gear and the planetary gears is between 100,000 and 250,000 MPa, and the Young's modulus of the second material of the ring gear is between 1,000 and 20,000 MPa. Furthermore, the first material of the planetary gear and the planetary gears is metallic, and the second material of the ring gear is plastic. Therefore, the ring gear is deformed more than the planetary gear and the planetary gears when the input shaft of the gearbox is rotated.

[0018] Thus, the use of the first part of teeth separated from the second part of teeth for each satellite gear combined with the use of the first material for the planetary gear and the satellite gears and the second material for the ring gear, of different rigidities, makes it possible to guarantee a contact pressure distributed uniformly, following a grip length of each satellite gear with the planetary gear.

[0019] In this way, the uniform distribution of contact pressure, along the engagement length of each satellite gear with the planetary gear, is achieved by separating the first and second tooth segments of each satellite gear. This separation of the first and second tooth segments of each satellite gear allows for an angular offset between them when the input shaft of the gearbox is rotated, particularly during activation of the electromechanical actuator's electric motor.

[0020] Furthermore, the uniform distribution of contact pressure, along the engagement length of each planet gear with the planet gear, is achieved by the difference in material between the ring gear and the planet gear and the planet gears, and more specifically, by the flexibility of the ring gear made of the second material compared to the rigidity of the planet gear and the planet gears made of the first material. This difference in material between the ring gear and the planet gears allows for greater deformation of the ring gear when an input shaft of the gearbox is rotated, particularly during activation of the electromechanical actuator's electric motor.

[0021] Moreover, such a construction of the reduction stage of the reducer means that the first and second parts of the teeth of each satellite pinion follow the deformation of the ring gear when the input shaft of the reducer is driven in rotation, in particular during an activation of the electric motor of the electromechanical actuator.

[0022] In this way, such a construction of the reduction stage of the reducer makes it possible to prevent at least one of the planetary gears from becoming slanted relative to its axis of rotation, when the input shaft of the reducer is driven in rotation, in particular during an activation of the electric motor of the electromechanical actuator.

[0023] According to one embodiment, the metallic material of the planetary gear and satellite gears is sintered steel.

[0024] Alternatively, the metallic material of the planetary gear and satellite gears is machined steel.

[0025] According to an advantageous feature of the invention, the plastic material of the crown is a polyamide.

[0026] According to another advantageous feature of the invention, the first and second toothing parts of each satellite pinion are distinct, so as to form respectively a first part and a second part.

[0027] According to another advantageous feature of the invention, the first toothed portion comprises a first contact zone. The second toothed portion comprises a second contact zone. Furthermore, the first contact zone of the first toothed portion bears against the second contact zone of the second toothed portion, so as to form a gap between the teeth of the first toothed portion and the teeth of the second toothed portion.

[0028] According to another advantageous feature of the invention, each of the first and second contact zones of the first and second toothed parts is closer to an axis of rotation of the reducer than the teeth of the first and second toothed parts of each satellite pinion in contact with the teeth of the internal teeth of the ring gear.

[0029] According to another advantageous feature of the invention, the first and second toothing parts of each satellite pinion are meshed with the internal teeth of the crown.

[0030] The present invention relates, according to a second aspect, to a closure, shading or sun protection installation comprising a screen that can be rolled up on a winding tube driven in rotation by an electromechanical actuator according to the invention.

[0031] This installation has characteristics and advantages similar to those described previously in relation to the electromechanical actuator according to the invention, as mentioned above.

[0032] Other features and advantages of the invention will become apparent in the description below.

[0033] The attached drawings are given as non-exhaustive examples: [ Fig 1 ] there figure 1 is a schematic cross-sectional view of an installation conforming to a first embodiment of the invention; [ Fig 2 ] there figure 2 is a schematic perspective view of the installation illustrated in the figure 1 ; Fig 3 ] there figure 3 is a schematic view in axial and partial cross-section of the installation illustrated in figures 1 And 2 showing an electromechanical actuator of the installation; [ Fig 4 ] there figure 4 is a schematic view of a reducer of the electromechanical actuator illustrated in the figure 3 ; Fig 5 ] there figure 5 is a schematic, perspective, and exploded view of the reducer illustrated in the figure 4 ; Fig 6 ] there figure 6 is a partial schematic view of the reducer illustrated in figures 4 And 5 ; Fig 7 ] there figure 7 is a partial schematic view of a third reduction stage of the reducer illustrated in figures 4 à 6 , representing an angular offset of a first part of the teeth of a planetary gear relative to a second part of the teeth of said planetary gear; Fig 8 ] there figure 8 is a view analogous to the figure 4 illustrating a reducer of an electromechanical actuator according to a second embodiment; and [ Fig 9 ] there figure 9 is a schematic exploded view of the reducer illustrated in the figure 8 .

[0034] First, we describe, with reference to figures 1 And 2 , an installation 100 conforming to a first embodiment of the invention and installed in a building comprising an opening 1, window or door, equipped with a screen 2 belonging to a blackout device 3, in particular a motorized roller shutter.

[0035] The shading device 3 can be a roller shutter, a fabric blind or a blind with adjustable slats, or even a rolling gate. The present invention applies to all types of shading devices.

[0036] Here, installation 100 includes the blackout device 3.

[0037] We describe, with reference to figures 1 And 2 , a roller shutter conforming to an embodiment of the invention.

[0038] The screen 2 of the shading device 3 is wound on a winding tube 4 driven by a motorized drive device 5. The screen 2 is movable between a wound position, in particular high, and an unwound position, in particular low.

[0039] Here, installation 100 includes the motorized drive device 5.

[0040] The movable screen 2 of the shading device 3 is a closing, shading and / or sun protection screen, which rolls up onto the winding tube 4 whose inner diameter is substantially greater than the outer diameter of an electromechanical actuator 11, so that the electromechanical actuator 11 can be inserted into the winding tube 4, when assembling the shading device 3.

[0041] The motorized drive device 5 includes the electromechanical actuator 11, in particular of tubular type, enabling the winding tube 4 to be rotated, so as to move, in particular unwind or wind, the screen 2 of the occulting device 3.

[0042] The blackout device 3 includes the winding tube 4 for winding the screen 2. In the mounted state, the electromechanical actuator 11 is inserted into the winding tube 4.

[0043] As is known, the roller shutter, which forms the blackout device 3, has a curtain comprising horizontal slats hinged to each other, forming the screen 2 of the roller shutter 3, and guided by two lateral slides 6. These slats are joined when the curtain 2 of the roller shutter 3 reaches its lower unrolled position.

[0044] In the case of a roller shutter, the raised position corresponds to the end slat 8, for example L-shaped, of the curtain 2 of the roller shutter 3 pressing against an edge of the roller shutter housing 9, or to the end slat 8 stopping in a programmed upper limit position. Furthermore, the lowered position corresponds to the end slat 8 of the curtain 2 of the roller shutter 3 pressing against a threshold 7 of the opening 1, or to the end slat 8 stopping in a programmed lower limit position.

[0045] The first slat of the roller shutter 3, opposite the final end slat 8, is connected to the winding tube 4 by means of at least one joint 10, in particular a band-shaped attachment piece.

[0046] The winding tube 4 is located inside the box 9 of the roller shutter 3. The curtain 2 of the roller shutter 3 winds and unwinds around the winding tube 4 and is housed at least partly inside the box 9.

[0047] Generally, the chest 9 is located above opening 1, or in the upper part of opening 1.

[0048] The motorized drive device 5 is controlled by a control unit. The control unit can be, for example, a local control unit 12.

[0049] The local control unit 12 can be connected via wired or wireless link with a central control unit 13. The central control unit 13 controls the local control unit 12, as well as other similar local control units distributed throughout the building.

[0050] The motorized drive device 5 is preferably configured to execute movement commands, including unwinding or rolling, of the screen 2 of the shading device 3, which may be issued, in particular, by the local control unit 12 or the central control unit 13.

[0051] Installation 100 comprises either the local control unit 12, or the central control unit 13, or the local control unit 12 and the central control unit 13.

[0052] We now describe, in more detail and with reference to the figure 3 , the motorized drive device 5, including the electromechanical actuator 11, belonging to installation 100 of the figures 1 And 2 .

[0053] The electromechanical actuator 11 includes an electric motor 16.

[0054] Advantageously, the electric motor 16 comprises a rotor and a stator, not shown and positioned coaxially around an axis of rotation X, which is also the axis of rotation of the winding tube 4 in the mounted configuration of the motorized drive device 5.

[0055] Control means for the electromechanical actuator 11, enabling the movement of the screen 2 of the occulting device 3, are constituted by at least one electronic control unit 15. This electronic control unit 15 is capable of activating the electric motor 16 of the electromechanical actuator 11, and, in particular, enabling the supply of electrical energy to the electric motor 16.

[0056] Thus, the electronic control unit 15 controls, in particular, the electric motor 16, so as to open or close the screen 2, as described previously.

[0057] The control means for the electromechanical actuator 11 include hardware and / or software means.

[0058] As a non-limiting example, the material means may include at least one microcontroller 31.

[0059] The electronic control unit 15 includes at least a first communication module 27, in particular for receiving control orders, the control orders being issued by an order transmitter, such as the local control unit 12 or the central control unit 13, these orders being intended to control the motorized drive device 5.

[0060] Advantageously, the first communication module 27 of the electronic control unit 15 is wireless. In particular, the first communication module 27 is configured to receive radio control commands.

[0061] Advantageously, the first communication module 27 can also allow the reception of command orders transmitted by wired means.

[0062] The electronic control unit 15, the local control unit 12 and / or the central control unit 13 can be in communication with a remote weather station outside the building, including, in particular, one or more sensors that can be configured to determine, for example, temperature, brightness or wind speed.

[0063] The electronic control unit 15, the local control unit 12 and / or the central control unit 13 can also be in communication with a server 28, so as to control the electromechanical actuator 11 according to data made available remotely via a communication network, in particular an internet network that can be connected to the server 28.

[0064] The electronic control unit 15 can be operated from the local control unit 12 or central control unit 13. The local control unit 12 or central control unit 13 is equipped with a control keypad. The control keypad of the local control unit 12 or central control unit 13 includes one or more selection elements 14 and, optionally, one or more display elements 34.

[0065] By way of example, and not exhaustively, selection elements can be push buttons or touch-sensitive keys, and display elements can be light-emitting diodes, an LCD (Liquid Crystal Display) or TFT (Thin Film Transistor) display. Selection and display elements can also be implemented using a touchscreen.

[0066] The local control unit 12 or central control unit 13 includes at least one second communication module 36.

[0067] Thus, the second communication module 36 of the local control unit 12 or central control unit 13 is configured to transmit, in other words, sends out, control orders, in particular by wireless means, for example radioelectric, or by wired means.

[0068] In addition, the second communication module 36 of the local control unit 12 or central control unit 13 can also be configured to receive, in other words receives, control orders, in particular through the same means.

[0069] The second communication module 36 of the local control unit 12 or central control unit 13 is configured to communicate, in other words, communicates, with the first communication module 27 of the electronic control unit 15.

[0070] Thus, the second communication module 36 of the local control unit 12 or central control unit 13 exchanges control orders with the first communication module 27 of the electronic control unit 15, either unidirectionally or bidirectionally.

[0071] Advantageously, the local control unit 12 is a control point, which can be fixed or mobile. A fixed control point can be a control box intended to be mounted on a building wall or on the face of a window or door frame. A mobile control point can be a remote control, a smartphone, or a tablet.

[0072] Advantageously, the local control unit 12 or central control unit 13 also includes a controller 35.

[0073] The motorized drive device 5, in particular the electronic control unit 15, is preferably configured to execute movement commands, including closing and opening, of the screen 2 of the shading device 3. These commands can be issued, in particular, by the local control unit 12 or by the central control unit 13.

[0074] The motorized drive device 5 can be controlled by the user, for example by receiving a command order corresponding to a press on the or one of the selection elements 14 of the local control unit 12 or central control unit 13.

[0075] The motorized drive device 5 can also be controlled automatically, for example by receiving a control command corresponding to at least one signal from at least one sensor and / or a signal from a clock in the electronic control unit 15, in particular the microcontroller 31. The sensor and / or the clock can be integrated into the local control unit 12 or the central control unit 13.

[0076] The electromechanical actuator 11 is powered by electrical energy from a mains power supply network, or by means of a battery, which can be recharged, for example, by a photovoltaic panel.

[0077] Here, the electromechanical actuator 11 includes a power supply cable 18 enabling its supply of electrical energy from a mains power supply network.

[0078] A housing 17 of the electromechanical actuator 11 is preferably cylindrical in shape.

[0079] In one embodiment, the housing 17 is made of a metallic material.

[0080] The material of the electromechanical actuator housing is not limited and can vary. In particular, it can be a plastic material.

[0081] The electromechanical actuator 11 also includes a reducer 19.

[0082] Advantageously, the electromechanical actuator 11 also includes a brake 29 and an output shaft 20.

[0083] As a non-limiting example, brake 29 can be a spring brake, a cam brake or an electromagnetic brake.

[0084] Here and as can be seen at the figure 3 , the brake 29 is located between the electric motor 16 and the reducer 19, that is to say at the output of the electric motor 16.

[0085] Alternatively, not shown, the brake 29 can be positioned at the output of the reducer 19, in other words between the reducer 19 and the output shaft 20.

[0086] The electromechanical actuator 11 may also include a limit switch and / or obstacle detection device, which may be mechanical or electronic.

[0087] Advantageously, the electric motor 16, the brake 29 and the reducer 19 are mounted inside the housing 17 of the electromechanical actuator 11.

[0088] The winding tube 4 is driven in rotation around the axis of rotation X and the housing 17 of the electromechanical actuator 11, supported by two pivot joints. The first pivot joint is formed at one end of the winding tube 4 by means of a ring 30 inserted around one end 17a of the housing 17 of the electromechanical actuator 11. The ring 30 thus provides a bearing. The second pivot joint, not shown in the figure 3 , is carried out at a second end of the winding tube 4, not visible in this figure.

[0089] Advantageously, the electromechanical actuator 11 includes a torque support 21. The torque support 21 is projecting at the first end 17a of the housing 17 of the electromechanical actuator 11, in particular the end 17a of the housing 17 receiving the ring 30. The torque support 21 of the electromechanical actuator 11 thus makes it possible to fix the electromechanical actuator 11 on a frame 23, in particular to a side of the housing 9.

[0090] In addition, the torque support 21 of the electromechanical actuator 11 can allow the first end 17a of the housing 17 to be closed.

[0091] Furthermore, the torque support 21 of the electromechanical actuator 11 can support the electronic control unit 15. The electronic control unit 15 can be supplied with electrical energy by means of the power supply cable 18.

[0092] Here, and as illustrated in the figure 3 , the electronic control unit 15 is thus arranged, in other words integrated, inside the housing 17 of the electromechanical actuator 11.

[0093] Alternatively, not shown, the electronic control unit 15 is located outside the housing 17 of the electromechanical actuator 11 and, in particular, mounted on the frame 23 or in the torque support 21.

[0094] Advantageously, the output shaft 20 of the electromechanical actuator 11 is disposed inside the winding tube 4 and at least partly outside the housing 17 of the electromechanical actuator 11.

[0095] Advantageously, one end of the output shaft 20 is projecting from the housing 17 of the electromechanical actuator 11, in particular from a second end 17b of the housing 17 opposite to the first end 17a.

[0096] Advantageously, the output shaft 20 of the electromechanical actuator 11 is configured to drive in rotation a linking element 22 connected to the winding tube 4. The linking element 22 is made in the form of a wheel.

[0097] When the electromechanical actuator 11 is switched on, the electric motor 16 and the reducer 19 drive the output shaft 20 in rotation. In addition, the output shaft 20 of the electromechanical actuator 11 drives the winding tube 4 in rotation via the connecting element 22.

[0098] Thus, the winding tube 4 causes the screen 2 of the occulting device 3 to rotate, so as to open or close the opening 1.

[0099] We now describe, with reference to figures 4 à 7 , the reducer 19 of the electromechanical actuator 11, illustrated in the figure 3 and conforming to a first embodiment of the invention.

[0100] The reducer 19 includes at least one reduction stage 25a, 25b, 25c of epicycloidal type.

[0101] Here and as illustrated in the figure 5 The reducer 19 comprises three reduction stages 25a, 25b, 25c. Each of the three reduction stages 25a, 25b, 25c is of the epicyclic type. The three reduction stages 25a, 25b, 25c are hereafter referred to as the first reduction stage 25a, the second reduction stage 25b, and the third reduction stage 25c.

[0102] The number of reduction stages in the reducer is not limited. The number of reduction stages can be one, two, or four or more.

[0103] Here, the first reduction stage 25a is arranged at a first end 19a of the reducer 19 facing the electric motor 16, in an assembled configuration of the electromechanical actuator 11. The third reduction stage 25c is arranged at a second end 19b of the reducer 19 facing the output shaft 20 of the electromechanical actuator 11, in the assembled configuration of the electromechanical actuator 11. In addition, the second reduction stage 25b is arranged between the first reduction stage 25a and the third reduction stage 25c.

[0104] The third reduction stage 25c comprises at least one planetary pinion 32c and a plurality of satellite pinions 33c.

[0105] In the case illustrated in the figure 5 , each reduction stage 25a, 25b, 25c comprises at least one planetary pinion 32a, 32b, 32c and a plurality of satellite pinions 33a, 33b, 33c.

[0106] The planetary gear 32a and the satellite gears 33a of the first reduction stage 25a are hereafter referred to as the first planetary gear and the first satellite gears. The planetary gear 32b and the satellite gears 33b of the second reduction stage 25b are hereafter referred to as the second planetary gear and the second satellite gears. Furthermore, the planetary gear 32c and the satellite gears 33c of the third reduction stage 25c are hereafter referred to as the third planetary gear and the third satellite gears.

[0107] Here and as illustrated in the figure 5 The first reduction stage 25a comprises nine first planetary gears 33a regularly distributed, in particular in groups of three, around a rotation axis X19 of the reducer 19. Only six first planetary gears 33a are visible at the figure 5 The second reduction stage 25b comprises three second satellite gears 33b regularly spaced around the rotation axis X19, of which only two are visible at the figure 5 In addition, the third reduction stage 25c includes five third satellite gears 33c regularly spaced around the rotation axis X19.

[0108] The number of planetary gears in a reduction stage is not limited and can vary. A reduction stage can have two or more planetary gears.

[0109] Advantageously, the third planetary pinion 32c of the third reduction stage 25c includes a 45c tooth profile.

[0110] In the case illustrated in the figure 5 , the planetary pinion 32a, 32b, 32c of each reduction stage 25a, 25b, 25c includes a toothing 45a, 45b, 45c.

[0111] In the third reduction stage 25c, the third planetary pinion 32c is configured to cooperate and, in particular, is meshed, in other words configured to mesh, with each third satellite pinion 33c, in the assembled configuration of the reducer 19.

[0112] Similarly, in each of the first and second reduction stages 25a, 25b, the planetary pinion 32a, 32b is meshed, in other words configured to mesh, with each satellite pinion 33a, 33b, in the assembled configuration of the reducer 19.

[0113] Thus, the third planetary gear 32c of the third reduction stage 25c and, in the present case, the planetary gear 32a, 32b, 32c of each reduction stage 25a, 25b, 25c, is meshed, in other words configured to mesh, with each satellite gear 33a, 33b, 33c of this reduction stage 25a, 25b, 25c, in the assembled configuration of the reducer 19.

[0114] Alternatively, not shown, the third planetary pinion 32c of the third reduction stage 25c can be a smooth roller configured to cooperate by friction with each third satellite pinion 33c, in the assembled configuration of the reducer 19.

[0115] Advantageously, the third satellite pinions 33c of the third reduction stage 25c are identical.

[0116] Advantageously, in each of the first and second reduction stages 25a, 25b, the first and second planetary gears 33a, 33b of each reduction stage 25a, 25b are identical, in particular at least by groups of planetary gears of a reduction stage, as shown in the first reduction stage 25a in the figure 5 .

[0117] The third satellite gears 33c of the third reduction stage 25c are eccentric with respect to the rotation axis X19 of the reducer 19 and, more particularly, with respect to the third planetary gear 32c of this reduction stage 25c.

[0118] Similarly, in each of the first and second reduction stages 25a, 25b, the first and second satellite gears 33a, 33b of each reduction stage 25a, 25b are eccentric with respect to the axis of rotation X19 of the reducer 19 and, more particularly, with respect to the first or second planetary gear 32a, 32b of this reduction stage 25a, 25b.

[0119] Thus, for a given reduction stage 25a, 25b, 25c, an axis of rotation of each satellite pinion 33a, 33b, 33c is parallel to the axis of rotation X19 of the reducer 19 and, more particularly, to an axis of rotation of the planetary pinion 32a, 32b, 32c.

[0120] The axes of rotation of each satellite gear 33a, 33b, 33c and of the associated planetary gear 32a, 32b, 32c are not shown, in order to simplify the reading of the figures 5 And 6 except for the X33c rotation axis of a third satellite pinion 33c visible at the figure 7 .

[0121] The reducer 19 includes an input shaft 24.

[0122] Here and as illustrated in the figure 5 , the first planetary pinion 32a of the first reduction stage 25a constitutes the input shaft 24 of the reducer 19.

[0123] In an alternative, not shown, the first planetary pinion 32a of the first reduction stage 25a is carried by the input shaft 24 of the reducer 19.

[0124] The reducer 19 also includes an output shaft 26.

[0125] Here and as illustrated in figures 5 And 6 , the output shaft 20 of the electromechanical actuator 11 constitutes the output shaft 26 of the reducer 19.

[0126] Alternatively, not shown, the output shaft 20 of the electromechanical actuator 11 is carried by the output shaft 26 of the reducer 19.

[0127] Advantageously, the input shaft 24 and the output shaft 26 of the reducer 19 are coaxial, in an assembled configuration of the reducer 19.

[0128] Thus, the input and output shafts 24, 26 of the reducer 19 are arranged along the same axis of rotation X19, which is also the axis of rotation of the reducer 19, in the assembled configuration of the reducer 19.

[0129] The reducer 19 includes at least one ring 37a, 37c.

[0130] Here and as illustrated in the figure 5 The reducer 19 comprises two rings 37a, 37c. The two rings 37a, 37c are hereafter referred to as the first ring 37a and the second ring 37c.

[0131] Each of the first and second crowns 37a, 37c includes an internal dentition 38a, 38c.

[0132] The internal dentition 38a of the first crown 37a is also referred to hereafter as the first internal dentition. Furthermore, the internal dentition 38c of the second crown 37c is also referred to hereafter as the second internal dentition.

[0133] Here and as illustrated in the figure 5 , the third satellite pinions 33c of the third reduction stage 25c cooperate, in other words are configured to cooperate, with the second ring 37c, in the assembled configuration of the reducer 19. The second ring 37c therefore belongs to the third reduction stage 25c.

[0134] Each third satellite pinion 33c of the third reduction stage 25c is meshed, or rather configured to mesh, with the second internal toothing 38c of the second ring gear 37c, in the assembled configuration of the reducer 19.

[0135] Thus, each third satellite pinion 33c of the third reduction stage 25c is in mesh, in other words is configured to be in mesh, with the second internal toothing 38c of the second ring gear 37c, in the assembled configuration of the reducer 19.

[0136] Furthermore, at least some of the first and second planetary gears 33a, 33b of the first and second reduction stages 25a, 25b cooperate, or are configured to cooperate, with the first ring gear 37a in the assembled configuration of the reducer 19, according to a type of epicyclic gear train formed by the reduction stage 25a, 25b. The first ring gear 37a therefore belongs to both the first reduction stage 25a and the second reduction stage 25b.

[0137] Thus, the first internal toothing 38a of the first ring gear 37a meshes, on the one hand, with a portion of the first planetary gears 33a of the first reduction stage 25a and, on the other hand, with the second planetary gears 33b of the second reduction stage 25b, in the assembled configuration of the reducer 19, as illustrated in the figure 5 .

[0138] Here and as illustrated in the figure 5 The epicyclic gear train type formed by the first reduction stage 25a is type 1. Furthermore, the epicyclic gear train type formed by the second reduction stage 25b is type 2.

[0139] The first or second satellite pinion 33a, 33b of the first or second reduction stage 25a, 25b is meshed, in other words is configured to mesh, with the first internal toothing 38a of the first ring gear 37a, in the assembled configuration of the reducer 19.

[0140] Thus, the first or second satellite pinion 33a, 33b of the first or second reduction stage 25a, 25b is meshed, in other words is configured to mesh, with the first internal toothing 38a of the first ring gear 37a, in the assembled configuration of the reducer 19.

[0141] Alternatively, and not shown, the reducer 19 comprises a single ring gear. In this case, the planetary gears 33a, 33b, 33c of each reduction stage 25a, 25b, 25c cooperate, that is to say, are configured to cooperate, with the ring gear in the assembled configuration of the reducer 19. Thus, the planetary gears 33a, 33b, 33c of each reduction stage 25a, 25b, 25c mesh with the internal teeth of the single ring gear in the assembled configuration of the reducer 19. In this case, this single ring gear belongs to the different reduction stages 25a, 25b, 25c.

[0142] Advantageously, the third stage of the 25c reduction includes a 43c satellite carrier. The 43c satellite carrier of the third stage of the 25c reduction is also subsequently referred to as the third satellite carrier.

[0143] Similarly, each of the first and second reduction stages 25a, 25b includes a satellite carrier 43a, 43b. The satellite carrier 43a of the first reduction stage 25a is also referred to hereafter as the first satellite carrier. Furthermore, the satellite carrier 43b of the second reduction stage 25b is also referred to hereafter as the second satellite carrier.

[0144] Each third satellite pinion 33c of the third reduction stage 25c comprises at least a first toothed portion 39 and a second toothed portion 40. The first and second toothed portions 39, 40 of each third satellite pinion 33c are separated from each other, along a direction parallel to the axis of rotation X19 of the reducer 19, in other words not fixed to each other by an additional element, so as to allow an angular offset α between them, when the input shaft 24 of the reducer 19 is driven in rotation.

[0145] In the third reduction stage 25c, the third planetary gear 32c and the third satellite gears 33c are made of a first material. In addition, the second ring gear 37c is made of a second material.

[0146] Advantageously, the first material of the third planetary gear 32c and the third satellite gears 33c is more rigid than the second material of the second ring gear 37c.

[0147] Thus, the use of the first toothed part 39 separated from the second toothed part 40 for each third satellite pinion 33c combined with the use of the first material for the third planetary pinion 32c and the third satellite pinions 33c and the second material for the second ring gear 37c, of different rigidities, in the third reduction stage 25c, makes it possible to guarantee a contact pressure distributed uniformly, following a grip length L33 of each third satellite pinion 33c with the third planetary pinion 32c.

[0148] In this way, the uniform distribution of contact pressure, along the engagement length L33 of each third satellite gear 33c with the third planetary gear 32c, is achieved by separating the first and second toothed sections 39, 40 of each third satellite gear 33c. This separation of the first and second toothed sections 39, 40 of each third satellite gear 33c allows for the angular offset α between them when the input shaft 24 of the reducer 19 is driven in rotation, particularly during activation of the electric motor 16 of the electromechanical actuator 11, especially in the vicinity of a contact zone of each third satellite gear 33c with the second ring gear 37c. This angular offset α is visible at the figure 7 .

[0149] This uniform distribution of contact pressure also makes it possible to increase the length of the third satellite gears 33c, so as to reduce the stress exerted on them and on the third planetary gear 32c, and to compensate for a torsional stiffness of the output shaft 26 of the reducer 19 and, more particularly, of the output shaft 20 of the electromechanical actuator 11.

[0150] Furthermore, the uniform distribution of contact pressure, along the engagement length L33 of each third planetary gear 33c with the third planetary gear 32c, is achieved by the difference in material composition of the second ring gear 37c compared to the third planetary gear 32c and the third planetary gears 33c, and more specifically, by the flexibility of the second ring gear 37c, made of the second material, compared to the rigidity of the third planetary gear 32c and the third planetary gears 33c, made of the first material. This difference in material composition of the second ring gear 37c compared to the third planetary gear 32c and the third planetary gears 33c allows for increased deformation of the second ring gear 37c when the input shaft 24 of the gearbox 19 is rotated, particularly during activation of the electric motor 16 of the electromechanical actuator 11.

[0151] This uniform distribution of contact pressure means that the stress exerted on the second ring 37c is lower than that exerted on the third satellite gears 33c and the third planetary gear 32c.

[0152] In this way, the second 37c crown can be made from a material that is easier to shape during its manufacture.

[0153] Moreover, such a construction of the third reduction stage 25c of the reducer 19 entails that the first and second toothing parts 39, 40 of each third satellite pinion 33c follow the deformation of the second ring 37c, when the input shaft 24 of the reducer 19 is driven in rotation, in particular during an activation of the electric motor 16 of the electromechanical actuator 11.

[0154] In this way, such a construction of the third reduction stage 25c of the reducer 19 makes it possible to prevent at least one of the third satellite gears 33c from becoming slanted relative to its axis of rotation, when the input shaft 24 of the reducer 19 is driven in rotation, in particular during an activation of the electric motor 16 of the electromechanical actuator 11.

[0155] The stiffness of the first material of the third planetary gear 32c and of the third satellite gears 33c and that of the second material of the second ring gear 37c can be defined by their Young's moduli and expressed in megapascals (MPa).

[0156] The first material of the third planetary gear 32c and the third satellite gears 33c is metallic. Furthermore, the second material of the second ring gear 37c is plastic.

[0157] Thus, the use of the first toothed part 39 separated from the second toothed part 40 for each third satellite pinion 33c combined with the use of a metallic material for the third planetary pinion 32c and the third satellite pinions 33c and a plastic material for the second ring gear 37c, in the third reduction stage 25c, makes it possible to guarantee a contact pressure distributed uniformly, according to the grip length L33 of each third satellite pinion 33c with the third planetary pinion 32c.

[0158] In addition, the uniform distribution of contact pressure, according to the grip length L33 of each third satellite pinion 33c with the third planetary pinion 32c, is obtained by the flexibility of the second ring 37c, made of a plastic material, compared to the rigidity of the third planetary pinion 32c and the third satellite pinions 33c, made of a metallic material.

[0159] In one embodiment example, the metallic material of the third planetary gear 32c and the third satellite gears 33c is sintered steel.

[0160] Alternatively, the metallic material of the third planetary gear 32c and the third satellite gears 33c is cut steel, in other words machined steel.

[0161] Advantageously, the plastic material of the second 37c ring is a polyamide and, more particularly, a polyhexamethylene adipamide, commonly designated by the acronym PA6.6.

[0162] The Young's modulus Y1 of the first material of the third planetary gear 32c and the third satellite gears 33c is between 100,000 and 250,000 MPa. Furthermore, the Young's modulus Y2 of the second material of the second ring gear 37c is between 1,000 and 20,000 MPa.

[0163] Advantageously, the first and second toothing parts 39, 40 of each third satellite pinion 33c are distinct, so as to form respectively a first part and a second part.

[0164] Thus, the first and second toothing parts 39, 40 of each third satellite pinion 33c are formed by two distinct and separate parts.

[0165] Advantageously, each third satellite pinion 33c has a first part of teeth 39 and a second part of teeth 40 that are identical.

[0166] Advantageously, in the assembled configuration of the reducer 19, a space 41 is provided between the first toothed part 39 and the second toothed part 40, following a direction parallel to the axis of rotation X19 of the reducer 19.

[0167] Advantageously, the first toothed part 39 includes a first contact zone 46. In addition, the second toothed part 40 includes a second contact zone 47. In the assembled configuration of the reducer 19, the first contact zone 46 of the first toothed part 39 is in contact with the second contact zone 47 of the second toothed part 40, so as to form the space 41 between the teeth of the first toothed part 39 and the teeth of the second toothed part 40.

[0168] Thus, such a construction of each third satellite pinion 33c makes it possible to compensate for a torsional stiffness of the third reduction stage 25c.

[0169] In this way, the larger the space 41 between the first part of the teeth 39 and the second part of the teeth 40, the larger an angular offset α between them can be made up for.

[0170] Here and as illustrated in the figure 6 The first contact area 46 of the first toothed section 39 is a first shoulder. The second contact area 47 of the second toothed section 40 is a second shoulder. In the assembled configuration of the reducer 19, the first shoulder 46 of the first toothed section 39 bears against the second shoulder 47 of the second toothed section 40, thus forming the gap 41 between the teeth of the first toothed section 39 and the teeth of the second toothed section 40.

[0171] Advantageously, each of the first and second contact zones 46, 47 of the first and second toothed parts 39, 40 is closer to the axis of rotation X19 of the reducer 19 than the teeth of the first and second toothed parts 39, 40 of each third planetary pinion 33c meshing with the teeth of the second internal toothing 38c of the second ring gear 37c, in the assembled configuration of the reducer 19.

[0172] Thus, such an arrangement of the first and second contact zones 46, 47 close to the axis of rotation X19 of the reducer 19 makes it possible to minimize a friction torque generated between the first and second parts of teeth 39, 40, when the input shaft 24 of the reducer 19 is driven in rotation, in particular during an activation of the electric motor 16 of the electromechanical actuator 11.

[0173] In this way, the third stage of reduction 25c can present a maximized yield.

[0174] Advantageously, the space 41 between the first toothed portion 39 and the second toothed portion 40 of each third planetary gear 33c is arranged in a plane orthogonal, not shown, to the axis of rotation X33c of the third planetary gear 33c. This plane is not shown to facilitate reading the figure 6 .

[0175] The space 41 between the first toothed part 39 and the second toothed part 40 of each third satellite pinion 33c is annular in shape.

[0176] Advantageously, each of the first and second toothing parts 39, 40 of each third satellite pinion 33c is a single piece.

[0177] In the assembled configuration of the reducer 19, the first and second toothing parts 39, 40 of each third satellite pinion 33c are meshed, in other words configured to mesh, with the second internal toothing 38c of the second ring 37c.

[0178] Thus, each third satellite pinion 33c of the third reduction stage 25c is in mesh, in other words configured to be in mesh, with the second internal toothing 38c of the second ring gear 37c, in the assembled configuration of the reducer 19.

[0179] In this way, each third satellite pinion 33c of the third reduction stage 25c is meshed, in other words configured to mesh, with the same internal teeth 38c of the second ring 37c, in the assembled configuration of the reducer 19.

[0180] In other words, the second internal toothing 38c of the second ring gear 37c comprises a single part. Furthermore, each third planetary pinion 33c of the third reduction stage 25c is meshed, or configured to mesh, with this single part of the second internal toothing 38c of the second ring gear 37c, in the assembled configuration of the reducer 19.

[0181] Advantageously, the first and second toothed sections 39, 40 of each third planetary gear 33c are mounted to rotate freely around a shaft 42, in particular around the axis of rotation of the third planetary gear 33c, as illustrated in the figure 5 Furthermore, the shaft 42 of each third satellite pinion 33c is linked to the third planet carrier 43c.

[0182] Thus, the first and second toothing parts 39, 40 of each third satellite pinion 33c are fixed to the shaft 42.

[0183] In this way, the shaft 42 forms an indirect link between the first and second toothing parts 39, 40 of each third satellite pinion 33c.

[0184] In this case, the third satellite pinions 33c are said to be mounted at fixed center distances via the shafts 42 of the third satellite carrier 43c.

[0185] In an alternative, not shown, the first and second toothed parts 39, 40 of each third planetary pinion 33c are mounted floating inside the third planetary carrier 43c, in other words without a connecting shaft 42 between the first and second toothed parts 39, 40 and the third planetary carrier 43c.

[0186] Advantageously, the third satellite gears 33c are regularly distributed angularly with respect to the third planet carrier 43c, around the rotation axis X19 of the reducer 19.

[0187] Advantageously, the third planetary pinion 32c, the third planet carrier 43c and the second ring 37c are coaxial, in the assembled configuration of the reducer 19.

[0188] Advantageously, the third planet carrier 43c of the third reduction stage 25c is integral with the output shaft 26 of the reducer 19.

[0189] Thus, the third planet carrier 43c of the third reduction stage 25c is driven in rotation, in particular via the output shaft 26 of the reducer 19, when the input shaft 24 of the reducer 19 is driven in rotation, in particular during an activation of the electric motor 16 of the electromechanical actuator 11.

[0190] Here and as illustrated in figures 5 And 6 The third planet carrier 43c of the third reduction stage 25c and the output shaft 26 of the reducer 19, and more specifically the output shaft 20 of the electromechanical actuator 11, form a single piece, which can be manufactured, for example, by molding. This piece can be made, in particular, of a plastic or metallic material.

[0191] In an alternative, not shown, the third planet carrier 43c of the third reduction stage 25c and the output shaft 26 of the reducer 19 and, more particularly, the output shaft 20 of the electromechanical actuator 11 form two separate parts.

[0192] In this case, in the assembled configuration of the electromechanical actuator 11, the two parts are connected, in other words configured to be connected, together by means of fastening elements, which can be removed.

[0193] By way of non-limiting examples, the fastening elements can be of the elastic snap-fit ​​type or by screwing.

[0194] Advantageously, the third satellite carrier 43c includes a tray 44.

[0195] Advantageously, the shafts 42 of the third satellite pinions 33c are arranged in projection on the same side of the plate 44 of the third satellite carrier 43c.

[0196] Thus, each third satellite pinion 33c of the third reduction stage 25c is mounted in cantilever relative to the plate 44 of the third satellite carrier 43c.

[0197] Advantageously, the reducer 19 comprises a first cover 48a and a second cover 48b. The first cover 48a is located at the first end 19a of the reducer 19. Furthermore, the second cover 48b is located at the second end 19b of the reducer 19.

[0198] Advantageously, in the assembled configuration of the reducer 19, the first cover 48a is fixed to the first ring 37a by means of first fixing elements 49.

[0199] Advantageously, in the assembled configuration of the reducer 19, the first ring 37a is fixed to the second ring 37c by means of second fixing elements 50.

[0200] Advantageously, in the assembled configuration of the reducer 19, the second ring 37c is fixed to the second cover 48b by means of third fixing elements 51.

[0201] Advantageously, the first, second and third fixing elements 49, 50, 51 are elastic snap-fit ​​fixing elements.

[0202] Here, the first, second and third fixing elements 49, 50, 51 are respectively two in number and arranged diametrically opposite with respect to the axis of rotation X19 of the reducer 19, in other words at 180° to each other, around the axis of rotation X19 of the reducer 19.

[0203] The number and type of the first, second, and third fastening elements are not limited. For example, there could be three of them, arranged at 120° angles to each other around the axis of rotation of the gearbox. They could also be, for example, screw-type fastening elements.

[0204] Advantageously, the reducer 19 also includes a retaining ring 52. The retaining ring 52 is fixed, or rather configured to be fixed, to the housing 17 of the electromechanical actuator 11 by means of at least one retaining element, not shown.

[0205] Here and as illustrated in the figure 5 , the fixing ring 52 is disposed between the first ring 37a and the second ring 37c, in the assembled configuration of the reducer 19.

[0206] Here, the fixing ring 52 is fixed to the housing 17 by means of a fixing screw, not shown, passing through a through hole, not shown, provided in the housing 17 and screwing into a fixing hole 53 of the fixing ring 52.

[0207] The number and type of fasteners for the retaining ring to the housing are not limited. There may be, for example, two or more. They may also be, for example, riveted fasteners.

[0208] In the second embodiment, represented in figures 8 And 9The elements analogous to those of the first embodiment bear the same references and function as explained above. What follows mainly describes what distinguishes this second embodiment from the previous one. In what follows, when a reference sign is used without being reproduced on one of the figures 8 And 9 , it corresponds to the object bearing the same reference on one of the figures 1 à 7 .

[0209] We now describe, with reference to figures 8 And 9 , the reducer 19 of the electromechanical actuator 11 according to the second embodiment of the invention.

[0210] As in the first embodiment, the reducer 19 comprises three reduction stages 25a, 25b, 25c. Each of the three reduction stages 25a, 25b, 25c is of the epicycloidal type.

[0211] To figures 8 And 9The first planetary gears 33a and the first planet carrier 43a of the first reduction stage 25a are not visible. Similarly, the input shaft 24 of the reducer 19 is not shown in the figures 8 And 9 .

[0212] Here and as illustrated in the figure 9 , the brake 29 is disposed between two of the reduction stages 25a, 25b, 25c of the reducer 19 and, more particularly, between the first reduction stage 25a and the second reduction stage 25b.

[0213] Advantageously, the first planetary gear 32a is meshed, in other words is configured to mesh, with a first gear, not shown, of the brake input 29, in the assembled configuration of the reducer 19. In addition, the second planetary gear 32b is connected, in other words configured to be connected, to the brake 29, for example meshed with a second gear, not shown, of the brake output 29, in the assembled configuration of the reducer 19.

[0214] Advantageously, the reducer 19 comprises three rings 37a, 37b, 37c. The three rings 37a, 37b, 37c are hereafter referred to as first ring 37a, second ring 37b and third ring 37c.

[0215] Each of the first, second and third crowns 37a, 37b, 37c includes an internal dentition 38a, 38b, 38c, not shown in figures 8 And 9 .

[0216] The internal dentition 38a of the first crown 37a can also be called the first internal dentition. The internal dentition 38b of the second crown 37b can also be called the second internal dentition. Furthermore, the internal dentition 38c of the third crown 37c can also be called the third internal dentition.

[0217] Thus, the reducer 19 comprises as many rings 37a, 37b, 37c as there are reduction stages 25a, 25b, 25c and each ring 37a, 37b, 37c belongs respectively to a reduction stage 25a, 25b, 25c.

[0218] In this case, in the assembled configuration of the reducer 19, each ring 37a, 37b, 37c cooperates, in other words is configured to cooperate, only with the satellite gears 33a, 33b, 33c of one of the reduction stages 25a, 25b, 25c.

[0219] Here, in the third reduction stage 25c, the third planetary gear 32c and the third satellite gears 33c are made of a first material. Furthermore, the third ring gear 37c is made of a second material. The first material of the third planetary gear 32c and the third satellite gears 33c is more rigid than the second material of the third ring gear 37c.

[0220] Here, the third planetary pinion 32c, the third planet carrier 43c and the third ring gear 37c are coaxial, in the assembled configuration of the reducer 19.

[0221] Here, the second lid 48b is integrated into the second crown 37b.

[0222] Thus, the second lid 48b and the second crown 37b form a single piece, which can be produced, for example, by molding.

[0223] Advantageously, in the assembled configuration of the reducer 19, the first ring 37a is fixed to the brake 29 by means of the second fixing elements 50.

[0224] Advantageously, in the assembled configuration of the reducer 19, the brake 29 is fixed to the second ring 37b by means of the third fixing elements 51.

[0225] Thanks to the present invention, regardless of the embodiment, the use of the first part of teeth separated from the second part of teeth for each satellite pinion of one of the reduction stages combined with the use of the first material for the planetary pinion and the satellite pinions and the second material for the ring gear, of different rigidities, in particular in the same reduction stage, makes it possible to guarantee a contact pressure distributed uniformly, along a length of engagement of each satellite pinion with the planetary pinion.

[0226] Numerous modifications can be made to the embodiment examples described above without departing from the scope of the invention as defined by the claims.

[0227] Alternatively, and not shown, each third satellite gear 33c comprises at least one third toothed section. Furthermore, the third toothed section of each third satellite gear 33c is separated from the second toothed section, the second toothed section being itself separated from the first toothed section, as described previously.

[0228] Alternatively, the first material of the third planetary gear 32c and the third satellite gears 33c is a metallic material. Furthermore, the second material of the second ring gear 37c is also a metallic material. The first metallic material of the third planetary gear 32c and the third satellite gears 33c is more rigid than the second metallic material of the second ring gear 37c.

[0229] In one example of the realization of this variant, the first and second metallic materials are sintered steel.

[0230] In another example of the realization of this variant, the first and second metallic materials are a so-called free-cutting steel.

[0231] According to another variant, the first material of the third planetary gear 32c and the third satellite gears 33c is a plastic material. Furthermore, the second material of the second ring gear 37c is also a plastic material. The first plastic material of the third planetary gear 32c and the third satellite gears 33c is more rigid than the second plastic material of the second ring gear 37c.

[0232] In this case, the first and second plastic materials can be chosen, for example, from the following families of materials: polyoxymethylene, commonly designated by the acronym POM, polyamide, commonly designated by the acronym PA, or polyethylene, commonly designated by the acronym PE, with or without the presence of filler.

[0233] Alternatively, and not shown, each first or second planetary gear 33a, 33b of the first or second reduction stage 25a, 25b may comprise at least a first toothed portion 39 and a second toothed portion 40. The first and second toothed portions 39, 40 of each first or second planetary gear 33a, 33b are separated from each other. In this case, in the first or second reduction stage 25a, 25b, the first or second planetary gear 32a, 32b and the first or second planetary gears 33a, 33b are made of a first material. In addition, the first ring gear 37a is made of a second material. The first material of the first or second planetary gear 32a, 32b and of the first or second planetary gears 33a, 33b is more rigid than the second material of the first ring gear 37a.Thus, the characteristics described above in relation to the third reduction stage 25c and the second ring 37c are applicable either to the first reduction stage 25a, or to the second reduction stage 25b, or to the first and second reduction stages 25a, 25b, as well as to the first ring 37a. In this way, for a plurality of reduction stages 25a, 25b, 25c of the reducer 19, or for each reduction stage 25a, 25b, 25c of the reducer 19, each planetary gear 33a, 33b, 33c of the same reduction stage 25a, 25b, 25c comprises the first toothed portion 39 and the second toothed portion 40. The first and second toothed portions 39, 40 of each planetary gear 33a, 33b, 33c are separated from each other. Furthermore, the planetary gear 32a, 32b, 32c and the planetary gears 33a, 33b, 33c of the same reduction stage 25a, 25b, 25c are made of the first material.And, the crown 37a, 37c associated with this same reduction stage 25a, 25b, 25c is made of the second material.

[0234] Furthermore, the envisaged embodiments and variants can be combined to generate new embodiments of the invention, without departing from the scope of the invention as defined by the claims.

Claims

1. An electromechanical actuator (11) for a closure, concealment or solar protection installation (100) comprising at least: an electric motor (16), and a gearbox (19), the gearbox (19) comprising an input shaft (24), the gearbox (19) comprising at least one epicyclic type reduction stage (25a, 25b, 25c), said at least one reduction stage (25c) comprising at least: a sun gear (32c), a ring gear (37c), the ring gear (37c) comprising an internal toothing (38c), and a plurality of planet gears (33c), the sun gear (32c) cooperating with each planet gear (33c) and each planet gear (33c) being meshed with the internal toothing (38c) of the ring gear (37c), characterized in that: each planet gear (33c) comprises at least a first toothed part (39) and a second toothed part (40), the first and second toothed parts (39, 40) of each planet gear (33c) being separated relative to one another, according to a direction parallel to an axis of rotation (X19) of the gearbox (19), so as to allow an angular offset (α) between them, when the input shaft (24) of the gearbox (19) is driven in rotation, the sun gear (32c) and the planet gears (33c) are realized in a first material, the ring gear (37c) is realized in a second material, the rigidity of the first material of the sun gear (32c) and of the planet gears (33c) is greater than the rigidity of the second material of the ring gear (37c), the rigidity of the first material of the sun gear (32c) and of the planet gears (33c) and the rigidity of the second material of the ring gear (37c) being defined by the Young's modulus of these materials, the rigidity of the first material of the sun gear (32c) and of the planet gears (33c) and the rigidity of the second material of the ring gear (37c) are expressed in megapascals, the Young's modulus of the first material of the sun gear (32c) and of the planet gears (33c) being between 100000 and 250000 MPa and the Young's modulus of the second material of the ring gear (37c) being between 1000 and 20000 MPa, and the first material of the sun gear (32c) and of the planet gears (33c) is a metallic material and the second material of the ring gear (37c) is a plastic material, such that the ring gear (37c) is deformed to a greater extent, relative to the sun gear (32c) and to the planet gears (33c), when the input shaft (24) of the gearbox (19) is driven in rotation.

2. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to claim 1, characterized in that the metallic material of the sun gear (32c) and of the planet gears (33c) is a sintered steel.

3. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to claim 1, characterized in that the metallic material of the sun gear (32c) and of the planet gears (33c) is a machined steel.

4. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to any one of claims 1 to 3, characterized in that the plastic material of the ring gear (37c) is a polyamide.

5. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to any one of claims 1 to 4, characterized in that the first and second toothed parts (39, 40) of each planet gear (33c) are distinct, so as to form respectively a first piece and a second piece.

6. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to claim 5, characterized in that the first toothed part (39) comprises a first contact zone (46), in that the second toothed part (40) comprises a second contact zone (47) and in that the first contact zone (46) of the first toothed part (39) is in abutment against the second contact zone (47) of the second toothed part (40), so as to form a space (41) between the teeth of the first toothed part (39) and the teeth of the second toothed part (40).

7. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to claim 6, characterized in that each of the first and second contact zones (46, 47) of the first and second toothed parts (39, 40) is closer to the axis of rotation (X19) of the gearbox (19) than the teeth of the first and second toothed parts (39, 40) of each planet gear (33c) meshing with the teeth of the internal toothing (38c) of the ring gear (37c).

8. The electromechanical actuator (11) for a closure, concealment or solar protection installation (100) according to any one of claims 1 to 7, characterized in that the first and second toothed parts (39, 40) of each planet gear (33c) are meshed with the internal toothing (38c) of the ring gear (37c).

9. A closure, concealment or solar protection installation (100) comprising a screen (2) that can be wound onto a winding tube (4) driven in rotation by an electromechanical actuator (11) according to any one of claims 1 to 8.