Gearbox for an electromechanical actuator, range of gearboxes, electromechanical actuator and associated shading device

Abstract

Electromechanical actuator gearbox, gearbox range, electromechanical actuator, and associated shading device. An electromechanical actuator gearbox comprises a housing (170) and an epicyclic reduction stage (180) with a sun pinion (32), a ring gear (37), planet gears (33) meshed with the sun pinion (32) and the ring gear (37), and a planet carrier (38) on which the planet gears (33) are mounted. A first guide surface (S1) of the sun pinion (32) and a second guide surface (S2) of the sun pinion (32) are provided on the planet carrier (38). The first guide surface (S1) has a first diameter. The second guide surface (S2) has a second diameter. The first and second diameters are different. The first and second guiding surfaces (S1, S2) are arranged on the same first side (32a) of the solar gable (32). Figure for the abbreviation: Figure 7.

Description

Description Title of the invention: Reducer of an electromechanical actuator, range of reducers, electromechanical actuator and device associated occultation

[0001] — The present invention relates to a reducer of an electromechanical actuator, in other words a reducer for an electromechanical actuator, as well as a range of reducers comprising at least two such reducers. The present invention also relates to an electromechanical actuator of a concealment device, in other words an electromechanical actuator for a blackout device, comprising such a reducer. The present invention finally relates to a device blackout comprising a screen driven in movement by such an electronic actuator electromechanical.

[0002] — Generally, the present invention relates to the field of devices occultation comprising a motorized drive device setting in motion a screen, between at least a first position and at least a second position.

[0003] A motorized drive device comprises an electromechanical actuator of a mobile element for closing, concealing or protecting the sun such as a shutter, a door, a grille, a blind or any other equivalent material, called by the screen suite.

[0004] Document EP 2 372 187 A1 is already known, which describes a reducer of an ac- electromechanical reducer. The reducer comprises a housing and a reduction stage epicyclic type. The reduction stage includes a sun pinion, a crown, a plurality of planet gears and a planet carrier. The sun gear comprises a shaft. The crown wheel has internal teeth. The sun gear is meshed with each planet gear. Each planet gear is meshed with the internal teeth of the crown. The planet gears are mounted on the planet carrier. The carrier- tellites comprises a first sun gear guide surface and a second sun gear guide surface. The first guide surface, provided on the planet carrier, is a mounting surface of a first bearing. The second guide surface, provided on the planet carrier, is a mounting surface of a second bearing. The first guide surface has a first diameter. The second guide surface has a second diameter. Furthermore, the first and second diameters are different. This reducer is generally satisfactory.

[0005] However, this reducer has the disadvantage that the first and second guide surfaces, provided on the planet carrier, are arranged respectively on one side of the sun gear. In other words, the first guide surface, provided on the planet carrier, is arranged on a first side of the sun gear and the second guide surface, provided on the planet carrier, is arranged on a second side of the sun gear, the second side being opposite the first side of the sun gear. Furthermore, this reducer has the disadvantage that it must be designed and assembled from parts specific to the type of reducer to which it belongs. Thus, a manufacturer of electromechanical actuators must provide a specific reduction stage for each gearbox reference. Therefore, the cost price of the various reducers is relatively high due to the diversity of reduction stages to be manufactured. In addition, maintenance of these reducers requires a large stock of parts. The present invention aims to resolve the aforementioned drawbacks and to propose a reducer of an electromechanical actuator, a range of at least two such reducers, an electromechanical actuator of a concealment device comprising such a reducer, as well as a concealment device comprising such an electromechanical actuator, making it possible to optimize the design, manufacture and maintenance of the reducer. In this regard, the present invention aims, according to a first aspect, at a reducer of an electromechanical actuator, the reducer comprising at least: - a case, and - an epicyclic type reduction stage, the reduction stage comprising at least: - a sun gear, the sun gear comprising a shaft, - a crown, the crown comprising internal teeth, - a plurality of planet gears, the sun gear being meshed with each planet gear, each planet gear being meshed with the internal teeth of the crown, and - a planet carrier, the planet gears being mounted on the planet carrier, - the satellite carrier comprising at least: - a first guide surface of the sun gear, the first guide surface, provided on the planet carrier, having a first diameter, and - a second guide surface of the sun gear, the second guide surface, provided on the planet carrier, having a second diameter, the first and second diameters being different. According to the invention, the first and second guide surfaces, provided on the planet carrier, are arranged on the same first side of the sun gear. Thus, the first and second guide surfaces, provided on the planet carrier, for guiding the sun gear make the planet carrier compatible with two different assemblies within the reduction stage of a reducer. In this way, the planet carrier can be used in the reduction stage of a reducer of a first type, such as a reduction stage of a reducer comprising a sun pinion and helical-toothed planet gears, and in the reduction stage of a reducer of a second type, such as a reduction stage of a reducer comprising a sun pinion and straight-toothed planet gears, each type of reducer being able to have specific advantages, in terms of noise level or in terms of manufacturing cost. Furthermore, the present invention allows the same planet carrier to be used on a range of gearboxes of various types. This makes it possible to minimize the manufacturing cost and the number of parts to be stored for the maintenance of a range of several gearboxes. According to an advantageous characteristic of the invention, the first guide surface, provided on the planet carrier, is a mounting surface of a first bearing or a sliding rotary guide surface of the sun gear shaft. Furthermore, the second guide surface, provided on the planet carrier, is a sliding rotary guide surface of the sun gear shaft. According to another advantageous characteristic of the invention, the reduction stage further comprises the first bearing, the first bearing forming a bearing for the sun gear. According to another advantageous characteristic of the invention, the planet carrier further comprises at least a third guide surface for the sun gear and a fourth guide surface for the planet carrier relative to the housing. The third guide surface, provided on the planet carrier, has a third diameter. The fourth guide surface, provided on the planet carrier, has a fourth diameter. The third and fourth diameters are different. Furthermore, the third and fourth guide surfaces, provided on the planet carrier, are arranged on the same second side of the sun gear, the second side being opposite the first side of the sun gear. According to another advantageous characteristic of the invention, the housing comprises at least a first guide surface of a second bearing and a second guide surface of the planet carrier. The third guide surface, provided on the planet carrier, is a mounting surface of the second bearing or a sliding rotary guide surface of the sun gear shaft. Furthermore, the fourth guide surface, provided on the planet carrier, is a rotary support surface sliding against the second guide surface, provided on the housing. According to another advantageous characteristic of the invention, the reduction stage further comprises the second bearing, the second bearing forming a bearing for the planet carrier and for the sun gear. The first guide surface, provided on the housing, has a fifth diameter. The second guide surface, provided on the housing, has a sixth diameter. Furthermore, the fifth and sixth diameters are different. According to another advantageous characteristic of the invention, the first and second guide surfaces, provided on the planet carrier, are defined with the same tolerance. According to another advantageous characteristic of the invention, the sun gear and the planet gears have helical teeth. The reduction stage further comprises at least a first bearing and a second bearing. The first bearing forms a guide bearing for the sun gear and is mounted tightly against the first guide surface, provided on the planet carrier. The planet carrier further comprises at least a third guide surface of the planet carrier relative to the housing. The second bearing forms a guide bearing for the sun gear and for the planet carrier and is mounted tightly against the third guide surface, provided on the planet carrier. Furthermore, along a longitudinal axis of the sun gear, the first and third guide surfaces, provided on the planet carrier, are arranged on either side of the helical teeth of the sun gear. According to another advantageous characteristic of the invention, the sun gear and the planet gears have straight teeth. The second guide surface, provided on the planet carrier, receives a part of the sun gear in sliding rotating support. The housing comprises at least a first guide surface of the planet carrier. The reducer further comprises at least one universal joint, the universal joint being meshed with the sun gear. Furthermore, the first guide surface, provided on the housing, receives the universal joint in sliding rotating support. The present invention aims, according to a second aspect, at a range of at least two reducers for an electromechanical actuator, in which: - each reducer is in accordance with the invention and as mentioned above, - the sun gear and the satellite gears of the reduction stage of a first reducer in the range have helical teeth, - the sun gear and the satellite gears of the reduction stage of a second reducer in the range are straight-toothed, - the planet carrier of the first reducer is identical to the planet carrier of the second reducer, - the first guide surface, provided on the planet carrier, guides the sun gear of the first reducer, and - the second guide surface, provided on the planet carrier, guides the sun gear of the second reducer. Such a range of reducers is simpler to design and manufacture than those of the prior art. According to an advantageous characteristic of the invention, the first and second reducers are in accordance with the invention and as mentioned above. The housing of the first reducer is identical to the housing of the second reducer. The first guide surface, provided on the housing, guides the planet carrier in the first reducer. Furthermore, the second guide surface, provided on the housing, guides the planet carrier in the second reducer. According to another advantageous characteristic of the invention, the range comprises at least four reducers. The reduction stage of two reducers, among the four reducers, comprises a sun pinion and helical-toothed planet gears. The reduction stage of two other reducers, among the four reducers, comprises a sun pinion and straight-toothed planet gears. The reduction stage of one of the helical-toothed reducers and the reduction stage of one of the straight-toothed reducers have the same first reduction ratio. The reduction stage of another of the helical-toothed reducers and the reduction stage of another of the straight-toothed reducers have the same second reduction ratio. Furthermore, the second reduction ratio is different from the first reduction ratio. The present invention relates, according to a third aspect, to an electromechanical actuator of a concealment device, the electromechanical actuator comprising at least one casing, an electric motor and a reducer according to the invention and as mentioned above or belonging to a range of reducers according to the invention and as mentioned above. The reducer is coupled with the electric motor, either directly or via at least one additional member of the electromechanical actuator. Furthermore, the electric motor and the reducer are housed inside the casing. This electromechanical actuator has characteristics and advantages similar to those described previously, in relation to the reducer according to the invention. The present invention relates, according to a fourth aspect, to a concealment device comprising at least one screen and an electromechanical actuator in accordance with the invention and as mentioned above, the screen being driven in movement by the electromechanical actuator. This occultation device has characteristics and advantages similar to those described previously, in relation to the electromechanical actuator according to the invention. Other features and advantages of the invention will appear in the following description, given with reference to the appended drawings, given as non-limiting examples and in which: [Fig.1] [Fig.1] is a schematic cross-sectional view of an installation in accordance with the invention; [Fig.2] [Fig.2] is a schematic perspective view of the installation illustrated in [Fig.1]; [Fig.3] [Fig.3] is a schematic view in axial and partial section of the installation illustrated in figures 1 and 2, showing an electromechanical actuator of the installation, which is in accordance with the invention; [Fig.4] [Fig.4] is a partially exploded schematic perspective view of a reducer belonging to the electromechanical actuator of [Fig.3] and in accordance with a first embodiment of the invention; [Fig.5] [Fig.5] is an exploded perspective schematic view of a first reduction stage of the reducer of [Fig.4]; [Fig.6] [Fig.6] is a schematic view in axial section and in perspective of a planet carrier of the first reduction stage of the reducer of [Fig.5]; [Fig.7] [Fig.7] is a schematic axial sectional view of the first reduction stage of the reducer of [Fig.5]; [Fig.8] [Fig.8] is a schematic view similar to [Fig.5] showing, in exploded perspective, the first reduction stage of a reducer according to a second embodiment of the invention, which also includes the planet carrier of [Fig.6]; and [Fig.9] [Fig.9] is a schematic axial sectional view of the first reduction stage of the reducer of [Fig.8]. Firstly, with reference to figures | and 2, an installation 100 comprising a closing, concealing or solar protection device 3 according to an embodiment of the invention is described. This installation 100, installed in a building, not shown, comprises an opening 1, window or door, and is equipped with a screen 2 belonging to the closing, concealing or solar protection device 3, in particular a motorized roller shutter. The closing, concealing or sun protection device 3 is hereinafter called the “concealing device”. The concealing device 3 comprises the screen 2. The closing, concealing or sun protection device 3 may be a roller shutter, a canvas blind or one with adjustable slats, or even a rolling gate. The present invention applies to all types of concealing device. Here, the installation 100 comprises the occultation device 3. A roller shutter according to one embodiment of the invention is described with reference to figures | and 2. The occulting device 3 comprises a winding tube 4 and a motorized drive device 5. The motorized drive device 5 comprises an electromechanical actuator 11 illustrated in [Fig.3]. The screen 2 is configured to be moved, in other words is moved, by means of the motorized drive device 5 and, more particularly, of the electromechanical actuator 11. Here, the screen 2 of the occulting device 3 is wound onto the winding tube 4 driven by the motorized drive device 5. Thus, the screen 2 is movable between a wound position, in particular a high position, and an unwound position, in particular a low position. In other words, the screen 2 can be wound onto the winding tube 4. Furthermore, the winding tube 4 is arranged so as to be driven in rotation by the electromechanical actuator 11. Advantageously, the concealment device 3 further comprises a box 9. The screen 2 is arranged, in other words is configured to be arranged, at least partly inside a box 9, in particular in an assembled configuration of the concealing device 3. The screen 2 of the occultation device 3 is a closing, occultation and / or sun protection screen, winding and unwinding around the winding tube 4, the inner diameter of which is greater than the outer diameter of the electromechanical actuator 11, so that the electromechanical actuator 11 can be inserted into the winding tube 4, when assembling the occultation device 3. The occulting device 3 and, more particularly, the motorized drive device 5 comprises the electromechanical actuator 11, in particular of the tubular type. This makes it possible to rotate the winding tube 4 around an axis of rotation X, so as to move, in particular unroll or roll up, the screen 2 of the occulting device 3. Thus, the screen 2 can be rolled up and unrolled on the winding tube 4. In the assembled state, the electromechanical actuator 11 is inserted into the winding tube 4. Advantageously, the concealing device 3 further comprises two lateral slides 6. Each lateral slide 6 comprises a groove 41. Each groove 41 of one of the lateral slides 6 cooperates, in other words is configured to cooperate, with a lateral edge 2a of the screen 2, in particular in the assembled configuration of the concealing device 3, so as to guide the screen 2, during movement, in particular during winding and unwinding, of the screen 2, in particular around the winding tube 4. In a known manner, the roller shutter, which forms the concealment device 3, comprises an apron comprising horizontal slats hinged to each other, forming the screen 2 of the roller shutter 3, and guided by the two lateral slides 6. These slats are joined when the apron 2 of the roller shutter 3 reaches its lower unrolled position. In the case of a roller shutter, the high rolled-up position corresponds to the setting in support of a final end blade 8, for example L-shaped, of the apron 2 of the roller shutter 3 against an edge of the box 9 of the roller shutter 3 or to the stopping of the final end blade 8 in a programmed upper end-of-travel position. In addition, the lower unrolled position corresponds to the support of the final end blade 8 of the apron 2 of the roller shutter 3 against a threshold 7 of the opening 1 or to the stopping of the final end blade 8 in a programmed lower end-of-travel position. 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 articulation 10, in particular a band-shaped attachment piece. The winding tube 4 is arranged inside the box 9 of the roller shutter 3. The apron 2 of the roller shutter 3 winds and unwinds around the winding tube 4 and is housed at least partly inside the box 9. Generally, the trunk 9 is arranged above the opening 1, or in the upper part of the opening 1. The motorized drive device 5 is controlled by a control unit. The control unit may be, for example, a local control unit 12. The local control unit 12 can be connected by wired or wireless connection to 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. The motorized drive device 5 is preferably configured to execute the movement commands, in particular unrolling or rolling up, of the screen 2 of the occulting device 3, which can be issued, in particular, by the local control unit 12 or the central control unit 13. The 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. The motorized drive device 5, including the electromechanical actuator 11, belonging to the installation 100 of FIGS. 1 and 2, will now be described in more detail and with reference to [Fig. 3]. The electromechanical actuator 11 comprises a casing 17, in particular tubular, an electric motor 16 and a reducer 19. The electric motor 16 and the reducer 19 are mounted, in other words are configured to be mounted, inside the housing 17, in particular in an assembled configuration of the electromechanical actuator 11. The electric motor 16 and the reducer 19 are represented respectively by their casings in [Fig. 3], without details on their internal constituent elements, except to show, in dotted lines, a brake 29 which is integrated into the reducer 19, as explained below. After. Advantageously, the electric motor 16 comprises a rotor and a stator, not shown and positioned coaxially around the 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. Advantageously, the electric motor 16 may be of the brushless type with electronic commutation, also called “BLDC” (acronym for the English term BrushLess Direct Current) or “synchronous with permanent magnets”, of the asynchronous type or of the direct current type. Means for controlling the electromechanical actuator 11, allowing the screen 2 of the occulting device 3 to be moved, are constituted by at least one control unit 15, in particular an electronic control unit. This control unit 15 is capable of putting the electric motor 16 of the electromechanical actuator 11 into operation, and, in particular, of allowing the electric motor 16 to be supplied with electrical energy. Thus, the control unit 15 controls, in particular, the electric motor 16, so as to open or close the screen 2, as described previously. The control means of the electromechanical actuator 11 comprise hardware and / or software means. By way of non-limiting example, the hardware means may comprise at least one microcontroller 31, illustrated in [Fig.3]. The motorized drive device 5 comprises the control unit 15. The control unit 15 is electrically connected to the electric motor 16. Advantageously, the control unit 15 further comprises a first communication module 27, as illustrated in [Fig. 3], 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. Advantageously, the first communication module 27 of the control unit 15 is of the wireless type. In particular, the first communication module 27 is configured to receive radio control orders. Advantageously, the first communication module 27 can also allow the reception of control orders transmitted by wired means. The control unit 15, the local control unit 12 and / or the central control unit 13 may be in communication with a remote weather station outside the building, including, in particular, one or more sensors which may be configured to determine, for example, a temperature, a brightness or even a wind speed. The control unit 15, the local control unit 12 and / or the central control unit 13 may 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 which can be connected to the server 28. The control unit 15 can be controlled from the local control unit 12 and / or the central control unit 13. The local control unit 12 and / or the central control unit 13 is provided with a control keyboard. The control keyboard of the local control unit 12 or the central control unit 13 comprises one or more selection elements 14 and, optionally, one or more display elements 34. By way of non-limiting examples, the selection elements may be push buttons or sensitive keys, the display elements may be light-emitting diodes, a display, for example LCD (acronym for the English term “Liquid Crystal Display”) or TFT (acronym for the English term “Thin Film Transistor”). The selection and display elements may also be implemented using a touch screen. Advantageously, the local control unit 12 and / or the central control unit 13 comprises at least one second communication module 36. Thus, the second communication module 36 of the local control unit 12 or of the central control unit 13 is configured to transmit, in other words emits, control commands, in particular by wireless means, for example radioelectric, or by wired means. Furthermore, the second communication module 36 of the local control unit 12 or of the central control unit 13 can also be configured to receive, in other words receives, control commands, in particular via the same means. The second communication module 36 of the local control unit 12 or of the central control unit 13 is configured to communicate, in other words communicates, with the first communication module 27 of the control unit 15. Thus, the second communication module 36 of the local control unit 12 or of the central control unit 13 exchanges control commands with the first communication module 27 of the control unit 15, either in a unidirectional manner or in a bidirectional manner. Advantageously, the local control unit 12 is a control point, which may be fixed or mobile. A fixed control point may be a control box intended to be fixed to a facade of a wall of the building or to a face of a fixed frame of a window or a door. A mobile control point may be a remote control, a smartphone or a tablet. Advantageously, the local control unit 12 or the central control unit 13 further comprises a controller 35. The motorized drive device 5, in particular the control unit 15, is preferably configured to execute movement control orders, in particular closing and opening, of the screen 2 of the occulting device 3. These control orders can be issued, in particular, by the local control unit 12 or by the central control unit 13. The motorized drive device 5 can be controlled by the user, for example by receiving a control command corresponding to pressing the or one of the selection elements 14 of the local control unit 12 or of the central control unit 13. 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 of the control unit 15, in particular from the microcontroller 31. The sensor and / or the clock can be integrated into the local control unit 12 or the central control unit 13. Here, the electromechanical actuator 11 further comprises an electrical power supply cable 18. Advantageously, the control unit 15 can be supplied with electrical energy by means of the electrical power supply cable 18 electrically connected to at least one electrical power supply source, not shown, which may be, for example, an electrical power supply network, in particular from the mains, and / or to a battery, which may be rechargeable, in particular by means of a photovoltaic panel or a charger, not shown. Thus, the electrical power supply cable 18 allows electrical energy to be supplied to the electromechanical actuator 11 from the electrical power supply source(s). The casing 17 is hollow. The casing 17 comprises a first end 17a and a second end 17b. The second end 17b is opposite the first end 17a. Advantageously, the electromechanical actuator 11 further comprises an output shaft 20. The output shaft 20 is arranged, in other words is configured to be arranged, at the second end 17b of the casing 17, in particular in the assembled configuration of the electromechanical actuator 11. Advantageously, the electromechanical actuator 11 further comprises a crown 30, which may also be called a sleeve. The crown 30 is arranged, in other words is configured to be arranged, at the first end 17a of the casing 17, in particular in the assembled configuration of the electromechanical actuator 11. Here, the casing 17 of the electromechanical actuator 11 is cylindrical in shape, in particular of revolution around the axis of rotation X, and is open at each of its ends 17a, 17b. Advantageously, the casing 17 is a tube. Here, the tube forming the casing 17 has a circular section. In an exemplary embodiment, the casing 17 is made of a metallic material. The material of the casing of the electromechanical actuator is not limiting and may be different. It may be, in particular, a plastic material. By way of non-limiting example, the brake 29 may be a spring brake, a cam brake, a magnetic brake or an electromagnetic brake. The brake 29 is configured to brake and / or to lock the output shaft 20 in rotation, so as to regulate the speed of rotation of the winding tube 4, during a movement of the screen 2, and to keep the winding tube 4 locked, when the electromechanical actuator 11 is electrically deactivated. Here and as visible in figures 3 and 4, the brake 29 is configured to be arranged, in other words is arranged, between two reduction stages of the reducer 19, in particular in the assembled configuration of the electromechanical actuator 11. Thus, the brake 29 is integrated into the reducer 19. Alternatively, not shown, the brake 29 is configured to be arranged, in other words is arranged, between the electric motor 16 and the reducer 19, that is to say at the output of the electric motor 16, in particular in the assembled configuration of the electromechanical actuator 11. According to another variant, not shown, the brake 29 is configured to be arranged, in other words is arranged, in particular in the assembled configuration of the electromechanical actuator 11, between the control unit 15 and the electric motor 16, in other words at the input of the electric motor 16. According to another variant, not shown, the brake 29 is configured to be arranged, in other words is arranged, in particular in the assembled configuration of the electromechanical actuator 11, between the reducer 19 and the output shaft 20, in other words at the output of the reducer 19. Advantageously, the brake 29 is mounted, in other words is configured to be mounted, inside the casing 17 of the electromechanical actuator 11, in particular in the assembled configuration of the electromechanical actuator 11. The reducer 19 is coupled, in other words is configured to be coupled, with the electric motor 16, in particular with the rotor of the electric motor 16 and in the assembled configuration of the electromechanical actuator 11, either directly or via at least one additional member 329, 29 of the electromechanical actuator 11, which may be, for example, a gimbal 329, or the brake 29, or the gimbal 329 and the brake 29. Advantageously, the electromechanical actuator 11 further comprises a device, not shown, for detecting the end of travel and / or an obstacle, this device being able to be mechanical or electronic. The winding tube 4 is rotated about the rotation axis X and the casing 17 of the electromechanical actuator 11 while being supported by two pivot connections. The first pivot connection is made at a first end of the winding tube 4 by means of the ring 30 inserted around the first end 17a of the casing 17 of the electromechanical actuator 11. The ring 30 thus makes it possible to produce a bearing. The second pivot connection, not shown in [Fig. 3], is made at a second end of the winding tube 4, not visible in this figure. Advantageously, the electromechanical actuator 11 further comprises a torque support 21. The torque support 21 closes, in other words is configured to close, the first end 17a of the casing 17, in particular in the assembled configuration of the electromechanical actuator 11. Thus, the torque support 21 is arranged, in other words is configured to be arranged, at the first end 17a of the casing 17. Advantageously, the torque support 21 projects at the level of the first end 17a of the casing 17 of the electromechanical actuator 11, in particular the end 17a of the casing 17 receiving the crown 30. Advantageously, the torque support 21 of the electromechanical actuator 11 is configured to fix the electromechanical actuator 11 to a frame 23, in particular to a cheek of the trunk 9. Thus, the torque support 21 makes it possible to absorb the forces exerted by the electromechanical actuator 11, in particular the torque exerted by the electromechanical actuator 11, relative to the structure of the building. The torque support 21 advantageously also makes it possible to absorb forces exerted by the winding tube 4, in particular the weight of the winding tube 4, of the electromechanical actuator 11 and of the screen 2, and to ensure that these forces are absorbed by the structure of the building. The torque support 21 is fixed, in other words is configured to be fixed, to the housing 17 by means of one or more fixing elements, in particular in the confi- assembled configuration of the electromechanical actuator 11. The fixing element(s) may be, in particular, bosses, fixing screws, elastic snap-fastening elements, ribs fitted into notches or a combination of these different fixing elements. Here and as illustrated in [Fig.3], the control unit 15 is arranged, in other words is integrated, inside the casing 17 of the electromechanical actuator 11. Alternatively, not shown, the control unit 15 is arranged outside the casing 17 of the electromechanical actuator 11 and, in particular, mounted on the frame 23 or in the torque support 21. Advantageously, the output shaft 20 of the electromechanical actuator 11 is arranged inside the winding tube 4 and at least partly outside the casing 17 of the electromechanical actuator 11. Advantageously, one end of the output shaft 20 projects relative to the casing 17 of the electromechanical actuator 11, in particular relative to the second end 17b of the casing 17 opposite the first end 17a. Advantageously, the output shaft 20 of the electromechanical actuator 11 is configured to drive in rotation a connecting element 22 connected to the winding tube 4. The connecting element 22 is, in the example of the figures, produced in the form of a wheel. When the electromechanical actuator 1 is operated, the electric motor 16 and the reduction gear 19 rotate the output shaft 20. In addition, the output shaft 20 of the electromechanical actuator 11 rotates the winding tube 4 via the connecting element 22. Thus, the winding tube 4 rotates the screen 2 of the occulting device 3, so as to open or close the opening 1. We will now describe, with reference to [Fig. 4], the reducer 19 of the electromechanical actuator 11, illustrated in [Fig. 3] and in accordance with a first embodiment of the invention. We denote by X19 an axis of rotation of the reducer 19. The axis of rotation X19 is superimposed on the axis of rotation X in the mounted configuration of the reducer 19 in the electromechanical actuator 11 and, in particular, of the electromechanical actuator 11 in the occulting device 3. The reducer 19 comprises a housing 170. The housing 170 of the reducer 19 is housed, in other words is configured to be housed, inside the casing 17, in particular in the assembled configuration of the electromechanical actuator 11. The reducer 19 further comprises at least one reduction stage 180, 182, 184 of the epicyclic type. Here and as illustrated in [Fig.3], the reducer comprises three reduction stages 180, 182, 184, hereinafter referred to as first reduction stage 180, second reduction stage 182 and third reduction stage 184. Here and as illustrated in [Fig.4], the reducer 19 comprises two sub-assemblies 192, 194, hereinafter called first sub-assembly 192 and second sub-assembly 194. The first sub-assembly 192 comprises the first reduction stage 180 of the reducer 19. The second sub-assembly 194 comprises the second reduction stage 182 and the third reduction stage 184 of the reducer 19. Each of the first, second and third reduction stages 180, 182, 184 is of the epicyclic type. The number of reduction stages of the reducer is not limiting. The number of reduction stages can be one, two or greater than or equal to four. Here, the first subassembly 192 is arranged at a first end 19a of the reducer 19 facing the electric motor 16, in particular in the assembled configuration of the electromechanical actuator 11. The second subassembly 194 is arranged at a second end 19b of the reducer 19 facing the output shaft 20 of the electromechanical actuator 11, in particular in the assembled configuration of the electromechanical actuator 11. The first end 19a is opposite the second end 19b. By convention, the first end 19a is considered to be the front end of the reducer 19 and the second end 19b is considered to be the rear end thereof. By convention, the front side or end of a part of the reducer 19 is its side or end facing the electric motor 16 in the mounted configuration of the reducer 19 in the electromechanical actuator 11 and the rear side or end of a part of the reducer 19 is its side or end facing the output shaft 20 in the mounted configuration of the reducer 19 in the electromechanical actuator 11. Here and as illustrated in figures 3 and 4, the brake 29 is arranged, in the direction of the axis of rotation X19, between the first and second sub-assemblies 192, 194 and, more particularly, between the first reduction stage 180 belonging to the first sub-assembly 192 and the second reduction stage 182 belonging to the second sub-assembly 194. At the level of the reducer 19 and the brake 29, the housing 170 is cut into three parts, namely a first part 172, which forms a housing for the first subassembly 192, a second part 174, which forms a housing for the second subassembly 194, and a third part 176, located between the first and second parts 172, 174, in the direction of the axis of rotation X19, and which forms a housing for the brake 29. The first portion 172 of the housing 170 may also be referred to as the inlet cover and the second portion 174 may also be referred to as the outlet cover. Each of the first, second and third reduction stages 180, 182, 184 comprises a sun gear and a plurality of planet gears. Only the sun gear 32 and the planet gears 33 of the first reduction stage 180 are shown in Figures 5 and 7. The sun gear 32 is meshed with each planet gear 33. Preferably, the satellite pinions 33 of the first reduction stage 180 are identical. Advantageously, the satellite pinions 33 of the first reduction stage 180 are regularly distributed around the axis of rotation X19 of the reducer 19. They may be, for example, three in number as shown in the figures and, in this case, distributed at 120°, around the axis of rotation X19. Advantageously, the satellite pinions of the second and third reduction stages 182, 184 are regularly distributed around the axis of rotation X19. They can also be, for example, three in number and distributed at 120° around the axis of rotation X19. The number of planet gears in a reduction stage is not limited and can be different. The number of planet gears in a reduction stage can be two, four or more. The three reduction stages do not necessarily have the same number of planet gears. Each of the first, second and third reduction stages 180, 182, 184 comprises a crown and a planet carrier. Only the crown 37 and the planet carrier 38 of the first reduction stage 180 are shown in Figures 5 to 7. The planet carrier 38 can also be called a barrel. The planet pinions 33 are mounted on the planet carrier 38. The crown 37 is integral, around the axis of rotation X19, with the housing 170 and, more particularly, with the first part 172 of the housing 170. Advantageously, the first part 172 of the housing 170, belonging to the first reduction stage 180, comprises first fixing lugs 173, in particular two in number and distributed at 180° relative to each other around the axis of rotation X19. The crown 37 further comprises first clearances 373, in particular two in number and distributed at 180° relative to each other around the axis of rotation X19 and arranged on an outer face of the crown 37. Furthermore, the crown 37 is locked in rotation relative to the first part 172 of the housing 170 by positioning each of the first fixing lugs 173 of the first part 172 of the housing 170 inside one of the first clearances 373 of the crown 37, in particular in an assembled configuration of the reducer 19 and, more particularly, of the first reduction stage 180. Thus, the crown 37 and the first part 172 of the case 170 are indexed and held in position between them radially around the axis of rotation X19. Advantageously, the second part 174 of the housing 170, belonging to the second subassembly 194, comprises second fixing lugs 175, in particular two in number and distributed at 180° relative to each other around the axis of rotation X19. Furthermore, the second part 174 of the housing 170 is held in position relative to the first part 172 of the housing 170 by the interlocking of the first fixing lugs 173 and the second fixing lugs 175, in particular in the assembled configuration of the reducer 19. Thus, the first and second parts 172, 174 of the housing 170 are indexed and held in position between them radially around the axis of rotation X19, as well as held in position between them axially in the direction of the axis of rotation X19. Here, the first fixing lugs 173 and the second fixing lugs 175 are elastic snap-fastening fixing elements. Advantageously, the third part 176 of the housing 170, belonging to the brake 29, comprises second clearances 293, in particular two in number and distributed at 180° relative to each other around the axis of rotation X19 and arranged on an outer face of the brake 29. In addition, the third part 176 of the housing 170, arranged between the first and second parts 172, 174 of the housing 170, is locked in rotation and in translation relative to the first and second parts 172, 174 of the housing 170 by positioning each of the first and second fixing lugs 173, 175 inside one of the second clearances 293 of the third part 176 of the housing 170, in particular in the assembled configuration of the reducer 19. Thus, the third part 176 of the housing 170 is indexed and held in position radially around the axis of rotation X19 and axially in the direction of the axis of rotation X19 relative to the first and second parts 172, 174 of the housing 170. The number of first fixing lugs of the first part of the case, the number of first crown clearances, the number of second fixing lugs of the second part of the case and the number of second clearances of the third part of the case are not limiting and may be different. They may, for example, be greater than or equal to three. Advantageously, the number of first fixing lugs 173 of the first part 172 of the housing 170, the number of first clearances 373 of the crown 37, the number of second fixing lugs 175 of the second part 174 of the housing 170 and the number of second clearances 293 of the third part 176 of the housing 170 are identical and these elements are distributed identically around the axis of rotation X19. Advantageously, the crown 37 comprises projecting elements 377, in par- particular two in number and distributed at 180° relative to each other around the axis of rotation X19. Only one of these projecting elements 377 is visible in Figures 4, 5 and 8. The third part 176 of the housing 170, belonging to the brake 29, comprises notches 297, in particular two in number and distributed at 180° relative to each other around the axis of rotation X19. In addition, the crown 37 is locked in rotation relative to the third part 176 of the housing 170 by positioning each of the projecting elements 377 of the crown 37 inside one of the notches 297 of the third part 176 of the housing 170, in particular in the assembled configuration of the reducer 19. Thus, the crown 37 and the third part 176 of the case 170 are indexed to each other radially around the axis of rotation X19. The number of protruding elements of the crown and the number of notches of the third part of the case are not limiting and may be different. They may, for example, be greater than or equal to three. Advantageously, the number of projecting elements 377 of the crown 37 and the number of notches 297 of the third part 176 of the housing 170 are identical and distributed identically around the axis of rotation X19. Here, the projecting elements 377 of the crown 37 are angularly offset, in particular by 90°, relative to the first clearances 373 of the crown 37, around the axis of rotation X19. Similarly, the notches 297 of the third part 176 of the housing 170 are angularly offset, in particular by 90°, relative to the second clearances 293 of the third part 176 of the housing 170, around the axis of rotation X19. We will now describe, with reference to Figures 4 to 7, the first reduction stage 180 of the reducer 19, illustrated in [Fig.4] and in accordance with the first embodiment of the invention. We note X38 a central axis of the planet carrier 38. The central axis X38 is superimposed on the rotation axis X19 in the mounted configuration of the reducer 19 and superimposed on the rotation axis X in the mounted configuration of the reducer 19 in the electromechanical actuator 11 and, in particular, of the reducer 19 and of the electromechanical actuator 11 in the occulting device 3. Advantageously, the sun pinion 32 comprises a first annular part 322. Advantageously, the first annular part 322 carries a toothing 324. Here, the toothing 324 of the sun pinion 32 is helical. The sun gear 32 further comprises a shaft 326. The shaft 326 of the sun gear 32 allows mounting and centering of the sun gear 32 on the planet carrier 38. The shaft 326 of the sun gear 32 extends along a first longitudinal axis X326. The first longitudinal axis X326 is a central axis of the sun gear 32. Here, the shaft 326 of the sun gear 32 is received in a central recess of the first annular part 322 of the sun gear 32. Furthermore, the first annular part 322 and the shaft 326 are integral in rotation, around the first longitudinal axis X326. Advantageously, the first reduction stage 180 further comprises a torque transmission element 328. Here, the shaft 326 is equipped, on a first end 326a, called the front end facing the first end 19a of the reducer 19, with the torque transmission element 328. The torque transmission element 328 is integral with the shaft 326, rotating around the first longitudinal axis X326. In the mounted configuration of the sun gear 32 in the planet carrier 38, the central axis X38 and the first longitudinal axis X326 are superimposed. Advantageously, the electromechanical actuator 11, in particular the reducer 19, further comprises the universal joint 329. The universal joint 329 is meshed with the sun gear 32. Furthermore, a first guide surface S178, provided on the housing 170, receives the universal joint 329 in sliding rotating support. Here, the universal joint 329 is engaged, that is to say integral in rotation about the first longitudinal axis X326, with the torque transmission element 328. Advantageously, the universal joint 329 is equipped, on its front side facing the electric motor 16 in the mounted configuration of the reducer 19 in the electromechanical actuator 11, with an imprint 329a, in particular non-circular, which may be, for example, in the shape of a cross, a star, a slot, or be produced by means of several holes, which may be two or more in number. Here, the imprint 329a is configured to receive, in other words receives, one end of an output shaft, not shown, of the electric motor 16, in particular in the assembled configuration of the electromechanical actuator 11. Alternatively, not shown, the imprint 329a is configured to receive, in other words receives, one end of an output shaft of the brake 29, in particular in the assembled configuration of the electromechanical actuator 11. Furthermore, in this case, one end of an input shaft of the brake 29 is coupled with one end of an output shaft of the electric motor 16, in particular in the assembled configuration of the electromechanical actuator 11. Thus, the universal joint 329, the torque transmission element 328, the shaft 326 and the first annular part 322 of the sun gear 32 make it possible to transmit a rotational movement to the teeth 324 of the sun gear 32 from the output shaft of the electric motor 16. Advantageously, each satellite pinion 33 comprises a second annular part 332. Advantageously, the second annular part 332 carries a first toothing 334. The first toothing 334 of each sun pinion 33 is engaged with the toothing 324 of the sun pinion 32. Here, the first toothing 334 of each sun gear 33 is helical. In addition, the first toothing 334 of each sun gear 33 is complementary to the toothing 324 of the sun gear 32. The crown 37 comprises an internal toothing 375. Each satellite pinion 33 is meshed with the internal toothing 375 of the crown 37. Here, the internal toothing 375 of the crown 37 is straight. Advantageously, the second annular part 332 carries a second toothing 335. The second toothing 335 of each sun pinion 33 is engaged with the internal toothing 375 of the crown 37. Here, the second toothing 335 of each sun pinion 33 is straight. In addition, the second toothing 335 of each sun pinion 33 is complementary to the internal toothing 375 of the crown 37. Advantageously, each planet gear 33 further comprises a shaft 336. The shaft 336 of each planet gear 33 allows mounting and centering of one of the planet gears 33 on the planet carrier 38. The shaft 336 of each planet gear 33 extends along a second longitudinal axis X336. Each second longitudinal axis X336 is a central axis of one of the planet gears 33. Each second longitudinal axis X336 is parallel to the first longitudinal axis X326 of the sun gear 32. Here, the shaft 336 of each planetary pinion 33 is received in a central recess of the second annular part 332 of the corresponding planetary pinion 33. Furthermore, the second annular part 332 and the shaft 336 of each planetary pinion 33 are integral in rotation, around the second longitudinal axis X336. In the mounted configuration of each sun gear 33 in the planet carrier 38, each second longitudinal axis X336 of one of the planet gears 33 is radially offset relative to the first longitudinal axis X326 of the sun gear 32 by a non-zero gap e23. The distance e23 is defined by the geometry of the planet carrier 38 and allows the meshing of the teeth 324 of the sun gear 32 with the first teeth 334 of each planet gear 33. Thus, the planet gears 33 are eccentric relative to the axis of rotation X19 of the reducer 19 and, more particularly, relative to the first longitudinal axis X326 of the sun gear 32, by the non-zero gap e23. The gap e23 is measured radially to the axis of rotation X19, between the first longitudinal axis X326 of the sun gear 32 and each of the second longitudinal axes X336 of the planet gears 33, in the confi- assembled gear box 19. Here, the toothing 324 of the sun gear 32 and the first toothing 334 of each satellite gear 33 are double helical toothings. These are herringbone toothings which comprise two toothed zones, with opposite orientations relative to the first longitudinal axis X326 for the sun gear 32 and relative to the second longitudinal axis X336 for each satellite gear 33. Alternatively, not shown, the teeth 324 of the sun gear 32 and the first teeth 334 of each satellite gear 33 are simple helical teeth. In this case, the first reduction stage 180 of the reducer 19 comprises stops, for the two directions of rotation of the rotor of the electric motor 16, so as to absorb axial forces on the sun gear 32 and the satellite gears 33. These stops can be produced by first and second bearings 42, 44 supporting the sun gear 32 with regard to the latter and the shape of the satellite gears 33 with regard to the latter. Here and as illustrated in figures 4, 5 and 7, the sun gear 32 constitutes the input shaft of the reducer 19. Advantageously, the reducer 19 further comprises an output shaft, not shown. Here, the output shaft of the reducer 19 is arranged, in other words is configured to be arranged, inside the output shaft 20 of the electromechanical actuator 11, in particular in the assembled configuration of the electromechanical actuator 11. Alternatively, not shown, the output shaft of the reducer 19 constitutes the output shaft 20 of the electromechanical actuator 11. Advantageously, the input shaft and the output shaft of the reducer 19 are coaxial, in other words are configured to be coaxial, in particular in the assembled configuration of the reducer 19. Thus, the input and output shafts of the reducer 19 are arranged along the same axis of rotation, which is also the axis of rotation X19 of the reducer 19, in particular in the assembled configuration of the reducer 19. Here and as illustrated in [Fig.7], each satellite pinion 33 of the first reduction stage 180 is meshed, in other words is configured to be meshed, by its second toothing 335 with the internal toothing 375 of the crown 37, in particular in the assembled configuration of the reducer 19. The crown 37 therefore belongs to the first reduction stage 180. Advantageously, the planet carrier 38 defines a first volume V32, called central, which allows the reception of the sun gear 32, and second volumes V33, called peripheral, in the exemplary embodiment three in number, which each allow the reception of a satellite gear 33. Here, the first volume V32 is centered on the central axis X38 and, when the sun gear 32 is in place in the first volume V32, the sun gear 32 is centered on the first longitudinal axis X326. Furthermore, each second volume V33 is centered on one of the second longitudinal axes X336, when each satellite gear 33 is in place in one of the second volumes V33. Advantageously, the planet carrier 38 has a front side 38a and a rear side 38b. The rear side 38b is opposite the front side 38a. The front side 38a of the planet carrier 38 is defined as facing the electric motor 16 and the rear side 38b of the planet carrier 38 is defined as facing the output shaft 20 and, in this case, the brake 29, in the assembled configuration of the electromechanical actuator 11. Advantageously, the planet carrier 38 comprises, on its rear side 38b, a housing 382. Here, the housing 382 of the planet carrier 38 is complementary to the external shape of an input shaft 292 of the brake 29. Thus, the cooperation of the housing 382 of the planet carrier 38 and the input shaft 292 of the brake 29 makes it possible to transmit to the brake 29 a rotational movement from the first reduction stage 180. Here, the housing 382 comprises a toothing. Furthermore, the toothing of the housing 382 is straight. As a variant, not shown, the housing 382 of the planet carrier 38 is complementary to the external shape of an input shaft of the second reduction stage 182. Thus, the cooperation of the housing 382 of the planet carrier 38 and the input shaft of the second reduction stage 182 makes it possible to transmit to the second reduction stage 182 a rotational movement from the first reduction stage 180. In this first embodiment, the first reduction stage 180 further comprises the first bearing 42 and the second bearing 44. Furthermore, the first and second bearings 42, 44 center the sun gear 32 inside the planet carrier 38, in particular in the first volume V32 of the planet carrier 38. Advantageously, the first bearing 42 forms a guide bearing for the sun gear 32. Furthermore, the second bearing 44 forms a guide bearing for the sun gear 32 and for the planet carrier 38. In the mounted configuration of the first and second bearings 42, 44 on the planet carrier 38, the first bearing 42 is mounted near the rear side 38b of the planet carrier 38 and the second bearing 44 is mounted near the front side 38a of the planet carrier 38. Here, the first bearing 42 has an outer radial surface S42, which has an outer diameter d42. Advantageously, the second bearing 44 comprises a first part 44a and a second part 44b. Furthermore, the first and second parts 44a, 44b have different diameters d44a, d44b. Thus, the second bearing 44 has an external radial surface S44, which is formed by the union of two respective external radial surfaces S44a, S44b of the first and second parts 44a, 44b. In this way, the outer radial surface S44 of the second bearing 44 is stepped. Here, a first external radial surface S44a of the first part 44a has a diameter d44a which is strictly less than a diameter d44b of a second external radial surface S44b of the second part 44b. With the same conventions as for the sides of the planet carrier 38, the second part 44b is the front part and the first part 44a is the rear part of the second bearing 44. Advantageously, in the assembled configuration of the reducer 19, the first part 44a of the second bearing 44 is engaged in the planet carrier 38, through its front side 38a, being oriented towards its rear side 38b, and the second part 44b of the second bearing 44 projects from the front side 38a of the planet carrier 38. The planet carrier 38 comprises a first guide surface S1 of the sun gear 32 and a second guide surface S2 of the sun gear 32. The first guide surface S1, provided on the planet carrier 38, has a first diameter d1. The second guide surface S2, also provided on the planet carrier 38, has a second diameter d2. The first and second diameters d1, d2 are different. Furthermore, the first and second guide surfaces S1, S2, provided on the planet carrier 38, are arranged on the same first side 32a of the sun gear 32, in particular along the direction of the central axis 38 and in the assembled configuration of the reduction gear 19. The first guide surface S1, provided on the planet carrier 38, is a mounting surface of the first bearing 42. The first bearing 42 forms a bearing for the sun gear 32. Furthermore, the second guide surface S2, provided on the planet carrier 38, is a sliding rotary guide surface of the shaft 326 of the sun gear 39 Advantageously, the planet carrier 38 defines a third volume V42, which allows the reception of the first bearing 42. Advantageously, the third volume V42 of the planet carrier 38 is delimited, radially outwards relative to the central axis X38, by the first guide surface S1, provided on the planet carrier 38. Here, the first guide surface S1, provided on the planet carrier 38, is a concave surface. More particularly, the first guide surface S1, provided on the planet carrier 38, is cylindrical, with a right generator and has a circular section centered on the central axis X38. Advantageously, the first diameter d! is determined as a function of the external diameter d42 of the first bearing 42, such that, when the first bearing 42 is in place in the third volume V42 of the planet carrier 38, the first bearing 42 is mounted tightly against the first guide surface S1, provided on the planet carrier 38, and therefore immobilized on the planet carrier 38. Here, the first diameter dl is less than the outer diameter d42. By way of non-limiting example, the first bearing 42 is force-fitted into the third volume V42 of the planet carrier 38. Alternatively, the first diameter d1 and the outer diameter d42 may be equal. We note d326 a diameter of the shaft 326 of the sun gear 32. Advantageously, an internal diameter of the first bearing 42 is determined to be greater than or equal to the diameter d326 of the shaft 326 of the sun gear 32, so as to allow sliding rotary guidance between the shaft 326 and the first bearing 42. In practice, the inner diameter of the first bearing 42 is determined between 100% and 103%, preferably between 101% and 103%, of the diameter d326 of the shaft 326. Thus, the first bearing 42 constitutes a first support and centering bearing for the sun gear 32 inside the planet carrier 38, in particular in the first volume V32 of the planet carrier 38, and close to the rear side 38b of the planet carrier 38. Furthermore, the first bearing 42 is fixed in the planet carrier 38, due to its tight mounting against the first guide surface SI, provided on the planet carrier 38. Furthermore, the first bearing 42 allows rotation of the sun gear 32 inside the planet carrier 38, due to the sliding rotary guidance which exists between an external radial surface of the shaft 326 and an internal radial surface of the first bearing 42. Advantageously, the planet carrier 38 further comprises a third guide surface S'1 for the sun gear 32 and a fourth guide surface S'2 for the planet carrier 38 relative to the housing 170. The third guide surface S'1, provided on the planet carrier 38, has a third diameter of 1. The fourth guide surface S'2, provided on the planet carrier 38, has a fourth diameter of 2. Furthermore, the third and fourth guide surfaces S'1, S'2, provided on the planet carrier 38, are arranged on the same second side 32b of the sun gear 32, the second side 32b being opposite the first side 32a of the sun gear 32, in particular in the direction of the central axis 38 and in the assembled configuration of the reduction gear 19. Advantageously, the planet carrier 38 defines, in particular near its side before 38a, a fourth volume V44, which allows the partial reception of the second pad 44. Advantageously, the fourth volume V44 of the planet carrier 38 is delimited, radially outwards with respect to the central axis X38, by the third guide surface S'1, provided on the planet carrier 38. Here, the third guide surface S'1, provided on the planet carrier 38, is a concave surface. More particularly, the third guide surface S'1, provided on the planet carrier 38, is cylindrical, with a right generatrix and has a circular section centered on the central axis X38. Advantageously, the third guide surface S'1, provided on the planet carrier 38, is a mounting surface for the second bearing 44. Furthermore, the second bearing 44 forms a bearing for the planet carrier 38 and for the sun gear 32. As seen in [Fig.7], only the first part 44a of the second bearing 44 is received in the fourth volume V44 of the planet carrier 38. Furthermore, the first part Ada of the second bearing 44 surrounds a portion of the shaft 326 located between the annular part 322 of the sun gear 32 and the torque transmission element 328. Advantageously, the third diameter d'1 is determined as a function of the outside diameter of the first part 44a of the second bearing 44, that is to say the diameter d44a of the surface S44a of the first part 44a of the second bearing 44, such that, when the first part 44a of the second bearing 44 is in place in the fourth volume V44 of the planet carrier 38, the second bearing 44 is mounted tightly against the third guide surface S'1, arranged on the planet carrier 38, and therefore immobilized on the planet carrier 38. Here, the third diameter d1 is less than the diameter d44a of the first part 44a of the second bearing 44. By way of non-limiting example, the second bearing 44 is force-fitted into the fourth volume V44 of the planet carrier 38. Alternatively, the third diameter d1 and the diameter d44a of the first portion 44a of the second bearing 44 may be equal. Advantageously, an internal diameter of the first part 44a of the second bearing 44 is determined to be greater than or equal to the diameter d326 of the shaft 326, so as to allow sliding rotary guidance between the shaft 326 and the second bearing 44. In practice, the inner diameter of the first part 44a of the second bearing 44 is determined between 100% and 103%, preferably between 101% and 103%, of the diameter d326 of the shaft 326. Thus, the second bearing 44 constitutes a second bearing for supporting and centering the sun gear 32 inside the planet carrier 38, in particular in the first volume V32 of the satellite carrier 38, and near the front side 38a of the satellite carrier 38. Furthermore, the second bearing 44 is fixed in the planet carrier 38, due to its tight mounting against the third guide surface S'1, provided on the planet carrier 38. Furthermore, the second bearing 44 allows rotation of the sun gear 32 inside the planet carrier 38, due to the sliding rotary guidance which exists between the external radial surface of the shaft 326 and an internal radial surface of the first part 44a of the second bearing 44. In practice, the inner diameters of the first and second bearings 42, 44 may be equal, since they contribute to the same function of supporting and centering the shaft 326 of the sun gear 32 with the possibility of relative rotary and sliding movement. Advantageously, the housing 170 comprises a first guide surface S178 of the second bearing 44 and a second guide surface S'178 of the planet carrier 38. The first guide surface S178, provided on the housing 170, has a fifth diameter d178. Furthermore, the second guide surface S'178, provided on the housing 170, has a sixth diameter of 178. As seen in [Fig.7], the housing 170, more particularly its first part 172, comprises a rib 178. The rib 178 of the housing 170 is internal to the housing 170 and stepped. Furthermore, the rib 178 of the housing 170 radially surrounds the front side 38a of the planet carrier 38, as well as the second bearing 44. Here, the first guide surface S178, provided on the housing 170, is arranged on the rib 178, in other words defined by this rib 178. Furthermore, the first guide surface S178, provided on the housing 170, guides a rotational movement of this second bearing 44, around the rotation axis X19, relative to the housing 170, which is fixed when the reducer 19 is in operation. During operation of the reducer 19, the planet carrier 38 rotates around the rotation axis X19 under the action of the torque exerted by the planet pinions 33, due to the meshing of their first toothing 334 with the toothing 324 of the sun pinion 32 and the internal toothing 375 of the crown 37. The internal toothing 375 of the crown 37 is fixed like the housing 170, with which it is integral. The rotation of the planet carrier 38 is transmitted to the second bearing 44, due to the tight mounting of its first part 44a in the fourth volume V44 of the planet carrier 38. The second bearing 44 can therefore rotate around the axis of rotation X19, since it is integral with the planet carrier 38, and the planet carrier 38 is supported and guided in rotation relative to the housing 170, on its front side 38a. Here, the first guide surface S178, provided on the housing 170, is a surface concave. More particularly, the first guide surface S178, provided on the housing 170, is cylindrical, with a right generatrix and has a circular section centered on the axis of rotation X19. Advantageously, the fifth diameter d178 of the first guide surface S178, provided on the housing 170, is determined to be greater than or equal to the diameter of the second part 44b of the second bearing 44, i.e. to the diameter d44b of the surface S44b of the second part 44b of the second bearing 44, so as to allow sliding rotary guidance between the second part 44b of the second bearing 44 and the housing 170, in other words to determine a first operating clearance between the second part 44b of the second bearing 44 and the housing 170. In practice, the fifth diameter d178 of the first guide surface S178, provided on the housing 170, is determined between 100% and 102% of the diameter d44b of the surface S44b of the second part 44b of the second bearing 44, Thus, the second bearing 44 constitutes a third bearing for supporting and centering the planet carrier 38 in the housing 170 and close to the front side 38a of the planet carrier 38. Furthermore, the second bearing 44 is fixed in the planet carrier 38, due to its tight mounting against the third guide surface S'1, provided on the planet carrier 38. Furthermore, the second bearing 44 allows rotation of the planet carrier 38 inside the housing 170, due to the sliding rotary guidance which exists between the first guide surface S178, provided on the housing 170, and the third guide surface S'1, provided on the planet carrier 38. In this way, the third guide surface S'1, provided on the planet carrier 38, allows the second bearing 44 to fulfill a triple function, of sliding rotary guidance of the sun gear 32 relative to the planet carrier 38 and of sliding rotary guidance of the planet carrier 38 relative to the housing 170, therefore of guidance of the sun gear 32 relative to the housing 170. Consequently, the third guide surface S'1, provided on the planet carrier 38, is at the same time a guide surface of the sun gear 32 relative to the planet carrier 38, a guide surface of the planet carrier 38 relative to the housing 170 and a guide surface of the sun gear 32 relative to the housing 170. Here, the second guide surface S'178, provided on the housing 170, is arranged on the rib 178. Here, the second guide surface S'178, provided on the housing 170, is a concave surface. More particularly, the second guide surface S'178, provided on the housing 170, is cylindrical, with a right generatrix and has a circular section centered on the axis of rotation X19. Here, the second guide surface S' 178, provided on the housing 170, surrounds the front side 38a of the planet carrier 38. Here, the fourth guide surface S'2, provided on the planet carrier 38, is a convex surface. More particularly, the fourth guide surface S'2, provided on the planet carrier 38, is cylindrical, with a right generatrix and has a circular section centered on the central axis X38. Advantageously, the fourth guide surface S'2, provided on the planet carrier 38, is a rotary support surface sliding against the second guide surface S'178, provided on the housing 170. The fourth diameter d'2 of the fourth guide surface S'2, provided on the planet carrier 38, is adapted to the sixth diameter d'178 of the second guide surface S'178, provided on the housing 170, so that the fourth guide surface S'2, provided on the planet carrier 38, is in sliding rotary contact against the second guide surface S'178, provided on the housing 170, during rotation of the planet carrier 38. Here, the fourth guide surface S'2, provided on the planet carrier 38, constitutes a sliding rotary support surface of the planet carrier 38 inside the housing 170. Advantageously, the sixth diameter d'178 of the second guide surface S'178, provided on the housing 170, is determined to be greater than or equal to the fourth diameter d'2 of the fourth guide surface S'2, provided on the planet carrier 38, so as to allow sliding rotary guidance between the planet carrier 38 and the housing 170, in other words to determine a second operating clearance between the planet carrier 38 and the housing 170. In practice, the sixth diameter d'178 of the second guide surface S'178, provided on the housing 170, is determined between 100% and 104%, preferably between 101% and 104%, of the fourth diameter d'2 of the fourth guide surface S'2, provided on the planet carrier 38. Advantageously, the second operating clearance between the planet carrier 38 and the housing 170 is greater than the first operating clearance between the second part 44b of the second bearing 44 and the housing 170. Thus, such a difference between the first and second operating clearances makes it possible to avoid a hyperstatic situation, in particular in the case where the sun gear 32 and the satellite gears 33 have helical teeth, in particular for the teeth 324 of the sun gear 32 and for the first teeth 334 of each satellite gear 33. The fifth and sixth diameters d178, d'178 are different. This corresponds to the stepped character of the rib 178. In other words, the fifth and sixth diameters d178, d'178 are fifth and sixth diameters of the reducer 19 which are defined by the box 170 and which are different. Advantageously, the fifth diameter d178 is strictly less than the sixth diameter d178. Advantageously, the third and fourth diameters of 1, 2 are specific to the planet carrier 38 and are different. Advantageously, the third diameter of 1 is strictly less than the fourth diameter of 2. Here, the third guide surface S'1, provided on the planet carrier 38, is provided at the same level as the fourth guide surface S'2, provided on the planet carrier 38, along the central axis X38. In other words, the third and fourth guide surfaces S'1, S'2, provided on the planet carrier 38, are respectively the internal and external radial surfaces of a tubular portion 386 of the planet carrier 38, which defines its front side 38a. The first guide surface S1, provided on the planet carrier 38, and the third guide surface S'1, provided on the planet carrier 38, are respectively provided near the rear 38b and front 38a sides of the planet carrier 38. In the assembled configuration of the reducer 19, these first and third surfaces SI, S'1, provided on the planet carrier 38, are arranged on either side of the toothing 324 of the sun gear 32, along the first longitudinal axis X326. As a result, the first and second bearings 42, 44 are located on either side of the toothing 324 of the sun gear 32, along the axis of rotation X19. Thus, the first and second bearings 42, 44 can effectively limit possible centering defects of the sun gear 32 with respect to the central axis X38, in particular due to interactions between the toothing 324 of the sun gear 32 and the first toothing 334 of each satellite gear 33. In this way, in this first embodiment, the first and second bearings 42, 44 make it possible to precisely center the sun gear 32 in the first volume V32. Furthermore, the helical toothing 324 of the sun gear 32 and the first helical toothing 334 of each of the planet gears 33 allow smooth transmission of the torque around the axis of rotation X19. This allows the planet carrier 38 to rotate around the axis of rotation X19 with minimal noise and vibration. The reduction gear 19 of this first embodiment can therefore be described as silent. Here, in the first embodiment, the second guide surface S'178, arranged on the housing 170, is not brought into contact with the fourth guide surface S'2, arranged on the planet carrier 38, so as to avoid a hyperstatic situation which could generate operating noises of the reducer 19 and parasitic efforts inside it. In the second embodiment of the invention shown in Figures 8 and 9, elements similar to those of the first embodiment bear the same references. If a reference is used in the remainder of the description without being shown in these Figures 8 and 9 or shown in these Figures 8 and 9 without being mentioned in the description, it designates the same element as that bearing the same reference in the first embodiment. In the following, we mainly describe what distinguishes this second embodiment from the first embodiment. The reducer 19 of the second embodiment is simpler to manufacture and more economical than the previous reducer 19 of the first embodiment, because, on the one hand, the teeth 324 of the sun gear 32 and the first teeth 334 of each of the planet gears 33 are straight teeth and, on the other hand, the first reduction stage 180 is without bearings, such as the first and second bearings 42, 44 of the first embodiment. This reducer 19 of the second embodiment can thus be noisier in operation than the reducer 19 of the first embodiment. The planet carrier 38 of the reducer 19 of this second embodiment is the same as that of the reducer 19 of the first embodiment. Here, the sun gear 32 is centered in the first volume V32 of the planet carrier 38 without bearing. To do this, the planet carrier 38 defines a fifth volume V326, as illustrated in [Fig.6], which allows the reception of the shaft 326 of the sun gear 32 and, more particularly, of a second rear end 326b of the shaft 326, which is opposite its first front end 326a. The second guide surface S2, provided on the planet carrier 38, receives the second rear end 326b of the shaft 326 in sliding rotating support. Advantageously, the fifth volume V326 of the planet carrier 38 is delimited, radially outwards relative to the central axis X38, by the second guide surface S2, provided on the planet carrier 38. Here, the second guide surface S2, provided on the planet carrier 38, is a concave surface. More particularly, the second guide surface S2, provided on the planet carrier 38, is cylindrical, with a right generatrix and has a circular section centered on the central axis X38. Here, the second diameter d2 is strictly less than the first diameter dl. Advantageously, the planet carrier 38 further comprises a shoulder 384. Here, the shoulder 384 is annular, faces the first end 38a of the planet carrier 38 and is defined between the third and fifth volumes V42, V326 of the planet carrier 38. Furthermore, along the central axis X38, the fifth volume V326 is defined between the third volume V42 and the rear side 38b of the planet carrier 38. Furthermore, the universal joint 329 is mounted directly on the first front end 326a of the shaft 326. In other words, the reducer 19 is devoid of a torque transmission element between the universal joint 329 and the shaft 326. The universal joint 329 and the shaft 326 are secured in rotation around the first longitudinal axis X326. Advantageously, the housing 170 of the reducer 19 of the second embodiment is the same as that of the reducer 19 of the first embodiment. Advantageously, the universal joint 329 further comprises a collar 329b. The collar 329b comprises an external radial surface S329b. Furthermore, in the assembled configuration of the reducer 19, the external radial surface S329b of the collar 329 is arranged radially inside the first guide surface S178, provided on the housing 170. Here, the first guide surface S178, provided on the housing 170, is defined by the rib 178 of the housing 170, as in the first embodiment. We note d329b the external diameter of the collar 329b, that is to say the diameter of the external radial surface S329b. Here, the first guide surface S178, provided on the housing 170, constitutes a guide bearing with sliding support of the collar 329b. Advantageously, the fifth diameter d178 of the first guide surface S178, provided on the housing 170, is determined to be greater than or equal to the external diameter d329b of the collar 329b, so as to allow sliding rotary guidance between the collar 329b and the housing 170. In practice, the fifth diameter d178 of the first guide surface S178, provided on the housing 170, is determined between 100% and 106% of the external diameter d329b of the collar 329b. Here, the outer diameter d329b of the collar 329b is less than the diameter d44b of the second part 44b of the second bearing 44, Alternatively, the outer diameter d329b of the collar 329b and the diameter d44b of the second part 44b of the second bearing 44 may be equal. Advantageously, in the second embodiment, as in the first embodiment, the second guide surface S'178, provided on the housing 170, surrounds the front side 38a of the planet carrier 38 and the fourth guide surface S'2, provided on the planet carrier 38, constitutes a sliding rotary guide surface of the planet carrier 38 inside the housing 170. Advantageously, in the first embodiment, the first guide surface S178, provided on the housing 170, constitutes a sliding rotary guide surface of the sun gear 32 and the planet carrier 38, through the second bearing 44. Furthermore, in the second embodiment, the first guide surface S178, arranged on the housing 170, constitutes a sliding rotary guide surface of the sun gear 32, through the gimbal 329 and, more particularly, through the toothing 324 of the sun gear 32 and an internal toothing of the gimbal 329. In the second embodiment, the second guide surface S'178, arranged on the housing 170, constitutes a direct sliding rotary guide surface of the planet carrier 38, receiving in sliding support the fourth guide surface S'2. Advantageously, in the second embodiment, the gimbal 329 comprises a rear portion 329c. Furthermore, the rear portion 329c of the gimbal 329 is engaged in the planet carrier 38 and, more particularly, in the tubular portion 386, in other words in the fourth volume V44, by the front side 38a of the planet carrier 38. Here, the rear portion 329c of the gimbal 329 has a diameter d329c strictly less than the third diameter d1 of the third guide surface S'1, arranged on the planet carrier 38. This avoids interference between the planet carrier 38 and the gimbal 329, in particular on the front side 38a of the planet carrier 38. Alternatively, not shown, the diameter d329c of the rear portion 329c of the universal joint 329 is determined relative to the third diameter d1 of the third guide surface S'1, provided on the planet carrier 38, so as to allow sliding rotary guidance between the third guide surface S'1, provided on the planet carrier 38, and an external radial surface S329c of the rear portion 329c of the universal joint 329. This contributes to the rotational guidance of the sun gear 32 relative to the planet carrier 38. In this case, the third diameter d1 of the third guide surface S'1, provided on the planet carrier 38, is determined between 100% and 103% of the diameter d329c of the rear portion 329c of the universal joint 329. Advantageously, in the second embodiment, the second rear end 326b of the shaft 326 of the sun gear 32 and the universal joint 329 are arranged respectively near the rear 38b and front 38a sides of the planet carrier 38. Furthermore, in the assembled configuration of the reducer 19, the second rear end 326b of the shaft 326 of the sun gear 32 and the universal joint 329 are located on either side of the toothing 324 of the sun gear 32, along the first longitudinal axis X326. Thus, the second rear end 326b of the shaft 326 of the sun gear 32 and the universal joint 329 can limit possible centering defects of the sun gear 32 with respect to the central axis X38, although to a lesser extent than the first and third guide surfaces S1, S'1, provided on the planet carrier 38, which interact with the first and second bearings 42, 44 in the first embodiment. In this way, the centering of the shaft 326 of the sun gear 32 relative to the central axis X38 is more precise in the first embodiment, in the presence of the first and second bearings 42, 44 in the planet carrier 38, than in the second embodiment, in the absence of the first and second bearings 42, 44 in the planet carrier 38. Advantageously, the crown 37 of the reducer 19 of the second embodiment is the same as that of the reducer 19 of the first embodiment. Advantageously, in the first and second embodiments, the planet carrier 38 is also guided in rotation around the axis of rotation X19 by interacting with the crown 37. Advantageously, the crown 37 further comprises a surface S37. Here, the surface S37, formed on the crown 37, is a concave surface. More particularly, the surface S37, formed on the crown 37, is cylindrical, with a right generatrix and has a circular section centered on the axis of rotation X19. We note d37 the diameter of the surface S37, arranged on the crown 37. Advantageously, the planet carrier 38 further comprises a fifth surface $3. Here, the fifth surface S3, arranged on the planet carrier 38, is a convex surface. More particularly, the fifth surface S3, arranged on the planet carrier 38, is cylindrical, with a right generatrix and has a circular section centered on the central axis X38. We note d3 the diameter of the fifth surface 53, arranged on the planet carrier 38. Advantageously, in the assembled configuration of the reducer 19, the fifth surface S3, provided on the planet carrier 38, is arranged, along the axis of rotation X19 and along the central axis X38 which are coincident, at the same level as the surface S37, provided on the crown 37. Advantageously, the diameter d37 of the surface S37, provided on the crown 37, is determined to be greater than or equal to the diameter d3 of the fifth surface S3, provided on the planet carrier 38, so as to allow sliding rotary guidance between the crown 37 and the planet carrier 38. In practice, the diameter d37 of the surface S37, provided on the crown 37, is determined between 100% and 103% of the diameter d3 of the fifth surface S3, provided on the planet carrier 38. Thus, the surface S37, provided on the crown 37, and the fifth surface S3, provided on the planet carrier 38, constitute a fourth bearing for supporting and centering the planet carrier 38 in the housing 170, in particular near the rear side 38a of the planet carrier 38. Advantageously, this fourth bearing is common to the first and second embodiments. This is consistent with the fact that the crown 37 and the planet carrier 38 are the same in the first and second embodiments. Advantageously, the fifth surface S3, provided on the planet carrier 38, is provided on the rear side 38b of the planet carrier 38. Advantageously, in the first embodiment, the guidance of the planet carrier 38 relative to the housing 170 is implemented, on the one hand, by the surface S44b of the second part 44b of the second bearing 44 pressing against the first guide surface S178, provided on the housing 170 and, on the other hand, by the fifth surface S3, provided on the planet carrier 38, pressing against the surface S37, provided on the ring 37. Furthermore, in the second embodiment, the guidance of the planet carrier 38 relative to the housing 170 is implemented, on the one hand, by the fourth guide surface S'2, provided on the planet carrier 38, pressing against the second guide surface S'178, provided on the housing 170, and, on the other hand, by the in support of the fifth surface S3, formed on the satellite carrier 38, against the surface S37, formed on the crown 37. Advantageously, the first and second guide surfaces S1, S2, provided on the planet carrier 38, are defined with the same tolerance, in particular for the respective first and second diameters d1, d2. This tolerance may be one tenth of a millimeter for the planet carrier 38 whose maximum external diameter is between twenty millimeters and twenty-five millimeters, preferably equal to twenty-two millimeters. Advantageously, the maximum external diameter of the planet carrier 38 is equal to the fourth diameter of 2 of the fourth guide surface S'2, provided on the planet carrier 38. Advantageously, the first and second guide surfaces S178, S°178, provided on the housing 170, are also defined with the same tolerance, in particular for the fifth and sixth diameters d178, d'178. This tolerance may be one tenth of a millimeter for the housing 170 where the third and fourth diameters d178, d'178 are respectively equal to approximately fifteen millimeters and twenty-two millimeters. Advantageously, the third and fourth guide surfaces S'1, S'2, provided on the planet carrier 38, are also defined with the same tolerance, in particular for the third and fourth diameters of 1, d'2. This tolerance may be one tenth of a millimeter for the planet carrier 38 where the third and fourth diameters of 1, d'2 are respectively equal to approximately ten millimeters and twenty-two millimeters. Thus, the present invention makes it possible to design and manufacture a range of reducers 19 for different electromechanical actuators 11, in particular taking into account the type of electric motor 16, the configuration of use, the level of noise and cost price considered for each reducer 19. Indeed, it is possible to favor a reducer 19 of the type of that of the first embodiment, illustrated in figures 4 to 7, when it is appropriate for the electromechanical actuator 11 to be silent and / or particularly precise, or a reducer 19 of the type of that of the second embodiment, illustrated in figures 6, 8 and 9, when the cost price of the electromechanical actuator 11 is essential. The different reducers 19 of this range may, for the same reduction stage, have different types of teeth, such as helical or straight, and may or may not include bearings of the type of the first and second bearings 42, 44. Reducers 19 of two different types have in common the same planet carrier 38 and, advantageously, the same housing 170 and the same crown 37, for the same reduction stage 180. Advantageously, the sun gear 32 and the planet gears 33 of the reduction stage 180 of a first reducer 19 of the range have helical teeth 324, 334, in particular for the teeth 324 of the sun gear 32 and for the first teeth 334 of each planet gear 33. The sun gear 32 and the planet gears 33 of the reduction stage 180 of a second reducer 19 of the range have straight teeth 324, 334, in particular for the teeth 324 of the sun gear 32 and for the first teeth 334 of each planet gear 33. The planet carrier 38 of the first reducer 19 is identical to the planet carrier 38 of the second reducer 19. The first guide surface S1, provided on the planet carrier 38, guides the sun gear 32 of the first reducer 19. In addition, the second guide surface S2, provided on the planet carrier 38, guides the sun gear 32 of the second reducer 19. Advantageously, the housing 170 of the first reducer 19 is identical to the housing 170 of the second reducer 19. The first guide surface S178, provided on the housing 170, guides the planet carrier 38 in the first reducer 19. Furthermore, the second guide surface S'178, provided on the housing 170, guides the planet carrier 38 in the second reducer 19. For example, the first reduction stage 180 of a reducer 19 according to the first embodiment of the invention, with helical teeth for the teeth 324 of the sun pinion 32 and for the first teeth 334 of each of the planet gears 33, can be constructed, with a first reduction coefficient K1 equal to approximately 9.7, by providing nine teeth on the teeth 324 of the sun pinion 32, twenty teeth on the first teeth 334 of each planet gear 33, ten teeth on the second teeth 335 of each planet gear 33 and thirty-nine teeth on the internal teeth 375 of the crown 37. In comparison, the first reduction stage 180 of a reducer 19 according to the second embodiment of the invention with straight teeth, for the teeth 324 of the sun pinion 32 and for the first and second teeth 334, 335 of each of the planet gears 33, can be constructed with the same first reduction coefficient K1, by providing nine teeth on the toothing 324 of the sun gear 32, twenty-two teeth on the first toothing 334 of each planet gear 33, eleven teeth on the second toothing 335 of each planet gear 33 and thirty-nine teeth on the internal toothing 375 of the crown 37. In the first reduction stage 180 of these two first reducers 19, the planet carrier 38, the housing 170 and the crown 37 are the same. In particular, the gap e23 is the same in the first reduction stage 180 of these two first reducers 19. Alternatively, by varying the gap e23, i.e. by changing the planet carrier 38, it is possible to construct the first reduction stage 180 of two second reducers 19 with a second reduction coefficient K2 equal to approximately 7, while retaining the same sun gear 32 and the same crown 37 as those of the first two reducers 19 for the first reduction stage 180 of each of the second reducers 19. In this case, it is appropriate to change the number of teeth of the first and second toothings 334, 335 of each planet pinion 33, making them equal to eighteen and thirteen respectively. In the first reduction stage 180 of these two second reducers 19, which have the second reduction coefficient K2, the planet carrier 38, the housing 170 and the crown 37 are the same.In particular, the gap e23 is the same in the first reduction stage 180 of these two second reducers 19, even if this gap e23 is reduced compared to that of the first reduction stage 180 of the first two reducers 19 which have the first reduction coefficient K1. In other words, it is possible to switch from a first configuration for the first reduction stage 180, with helical teeth 324, 334 for the sun gear 32 and the planet gears 33, in particular for the teeth 324 of the sun gear 32 and for the first teeth 334 of each planet gear 33, and the first and second bearings 42, 44, having a first reduction ratio K1 to a second configuration for the first reduction stage 180, with helical teeth 324, 334 for the sun gear 32 and the planet gears 33, in particular for the teeth 324 of the sun gear 32 and for the first teeth 334 of each planet gear 33, and the first and second bearings 42, 44, having a second reduction ratio K2 by changing the planet carrier 38 and a change in the number of teeth of the first and second toothings 334, 335 of each planet gear 33,which respectively go from twenty-two teeth to eighteen teeth and from eleven teeth to thirteen teeth. In the same way, it is possible to go from a first configuration for the first reduction stage 180, with a right toothing 324, 334 for the sun pinion 32 and the satellite pinions 33, in particular for the toothing 324 of the sun pinion 32 and for the first toothing 334 of each pinion, satellite 33, and without first and second bearings 42, 44, having a first reduction ratio K1 to a second configuration for the first reduction stage 180, with a right toothing 324, 334 for the sun pinion 32 and the satellite pinions 33, in particular for the toothing 324 of the sun pinion 32 and for the first toothing 334 of each satellite pinion 33, and without first and second bearings 42, 44, having a second reduction ratio K2 by a change of the planet carrier 38 and the number of teeth of the first and second toothings 334, 335 of each satellite pinion 33, which change respectively from twenty-two teeth to eighteen teeth and from eleven teeth to thirteen teeth. It is thus possible to create a range of at least four reducers 19, with two reducers 19 which each comprise a sun gear 32 and planet gears 33 having a helical toothing 324, 334 for the sun gear 32 and the planet gears 33, in particular for the toothing 324 of the sun gear 32 and for the first toothing 334 of each planet gear 33, and two reducers 19 which each comprise a sun gear 32 and planet gears 33 having a straight toothing 324, 334 for the sun gear 32 and the planet gears 33, in particular for the toothing 324 of the sun gear 32 and for the first toothing 334 of each planet gear 33.One of the reducers 19 with a helical toothing 324, 334 for the sun gear 32 and the planet gears 33, in particular for the toothing 324 of the sun gear 32 and for the first toothing 334 of each planet gear 33, and one of the reducers 19 with a straight toothing 324, 334 for the sun gear 32 and the planet gears 33, in particular for the toothing 324 of the sun gear 32 and for the first toothing 334 of each planet gear 33, have the same first reduction ratio K1 for the first reduction stage 180, in the example equal to approximately 9.7.Furthermore, another reduction gear 19 with helical teeth 324, 334 for the sun gear 32 and the planet gears 33, in particular for the teeth 324 of the sun gear 32 and for the first toothing 334 of each planet gear 33, and another reduction gear 19 with straight teeth 324, 334 for the sun gear 32 and the planet gears 33, in particular for the teeth 324 of the sun gear 32 and for the first toothing 334 of each planet gear 33, have a second same reduction ratio K2 for the first reduction stage 180, in the example equal to approximately 7. The reduction gears 19 which have the same reduction ratios K1, K2 for the first reduction stage 180 have identical planet carriers 38 and, preferably, housings 170 and 37 identical crowns. Advantageously, for the first reduction stage 180 of the two reducers 19 where the sun gear 32 and the satellite gears 33 have helical teeth and where the first and second reduction ratios K1, K2 are different, the sun gear 32 is identical. Furthermore, for the first reduction stage 180 of the other two re- ductors 19 where the sun gear 32 and the satellite gears 33 have straight teeth and where the first and second reduction ratios K1, K2 are different, the sun gear 32 is identical. Advantageously, the crown 37 of the first reduction stage 180 of each of the four reducers 19 has the same internal toothing 375. The numbers of teeth indicated above are not exhaustive. The teeth may have different numbers of teeth. By virtue of the present invention, the first and second guide surfaces provided on the planet carrier for guiding the sun gear make the planet carrier compatible with two different assemblies, namely with bearings and without bearings, for a sun gear and planet gears with helical teeth or straight teeth of the same reduction stage. Furthermore, the first and second guide surfaces provided on the housing also make the housing compatible with two different assemblies, namely with bearings and without bearings, for a sun gear and helical or straight toothed planet gears of the same reduction stage. The same applies to the first and second guide surfaces provided on the front side of the planet carrier and which can cooperate respectively with the housing or with one of the bearings. The present invention therefore provides great versatility to the planet carrier and, preferably, to the housing and the crown of the reducer according to the invention. This makes it possible to share these components within a range of reducers, therefore within a range of electromechanical actuators. Many modifications can be made to the embodiments described above without departing from the scope of the invention. Alternatively, not shown, the present invention may be implemented at the second reduction stage 182 or the third reduction stage 184. Alternatively, not shown, the first reduction stage 180 of the reducer 19 may be without the first and second bearings 42, 44 in the first embodiment, where the sun gear 32 and the planet gears 33 have helical teeth, in particular for the teeth 324 of the sun gear 32 and for the first teeth 334 of each planet gear 33. In this case, the shaft 326 of the sun gear 32 of the first reduction stage 180 of the reducer 19 has a diameter d326 of different value between the first embodiment and the second embodiment. Advantageously, the value of the diameter d326 in the case of the first embodiment is greater than the value of the diameter d326 in the case of the second embodiment. Furthermore, the difference in the value of the diameter d326 of the shaft 326 of the sun gear 32 between the first and second embodiments makes it possible to produce a keying during the assembly of the first reduction stage 180 of the reducer 19, so as to avoid an assembly error linked to an inversion of the references of sun gears 32 between the first and second embodiments. Alternatively, not shown, the first and second parts 44a, 44b of the second bearing 44 have identical diameters d44a, d44b. Furthermore, the contemplated embodiments and variations may be combined to generate new embodiments of the invention, without departing from the scope of the invention.

Claims

Claims

1. Reducer (19) of an electromechanical actuator (11), the reducer (19) comprising at least: - a housing (170), and - an epicyclic type reduction stage (180), the reduction stage (180) comprising at least: - a sun gear (32), the sun gear (32) comprising a shaft {326), - a crown (37), the crown (37) comprising internal teeth (375), - a plurality of satellite pinions (33), the sun pinion (32) being meshed with each satellite pinion (33), each satellite pinion (33) being meshed with the internal teeth (375) of the crown (37), and - a planet carrier (38), the planet gears (33) being mounted on the satellite carrier (38), the planet carrier (38) comprising at least: - a first guide surface (S1) of the sun gear (32), the first guide surface (S1), provided on the planet carrier (38), having a first diameter (d1), and - a second guide surface (S2) of the sun gear (32), the second guide surface (S2), provided on the planet carrier (38), having a second diameter (d2), the first and second diameters (d1, d2) being different, characterized in that the first and second guide surfaces (S1, S2), arranged on the planet carrier (38), are arranged in the same first side (32a) of the sun pinion (32).

2. Reducer (19) of an electromechanical actuator (11) according to re- dication 1, characterized in that the first guide surface (S1), provided on the carrier- satellites (38), is a mounting surface of a first bearing (42) or a sliding rotary guide surface of the pinion shaft (326) solar (32), and in that the second guide surface (S2), provided on the carrier- satellites (38), is a sliding rotary guide surface of the shaft (326) of the sun pinion (32).

3. Reducer (19) of an electromechanical actuator (11) according to re- dication 2, characterized in that the reduction stage (180) further comprises the first bearing (42), the first bearing (42) forming a bearing for the sun gable (32).

4. Reducer (19) of an electromechanical actuator (11) according to one any of claims | to 3, characterized in that the planet carrier (38) further comprises at least: - a third guide surface (S'1) of the sun gear (32), and - a fourth guide surface (S'2) of the planet carrier (38) by report to the case (170), in that the third guide surface (S'1), provided on the carrier- satellites (38), has a third diameter (d'1), in that the fourth guide surface (S'2), provided on the carrier- satellites (38), has a fourth diameter (d'2), in that the third and fourth diameters (d'1, d'2) are different, and in that the third and fourth guide surfaces (S'1, S'2), arranged on the planet carrier (38), are arranged in the same second side (32b) of the sun gear (32), the second side (32b) being opposite the first side (32a) of the sun gear (32).

5. Reducer (19) of an electromechanical actuator (11) according to reven- dication 4, characterized in that the housing (170) comprises at least: - a first guide surface (S178) of a second bearing (44), And - a second guide surface (S'178) of the planet carrier (38), in that the third guide surface (S'1), provided on the carrier- satellites (38), is a mounting surface of the second bearing (44) or a sliding rotary guide surface of the pinion shaft (326) solar (32), and in that the fourth guide surface (S'2), provided on the planet carrier (38), is a rotating bearing surface sliding against the second guide surface (S'178), provided on the housing (170).

6. Reducer (19) of an electromechanical actuator (11) according to reven- dication 5, characterized in that the reduction stage (180) further comprises the second bearing (44), the second bearing (44) forming a bearing for the planet carrier (38) and for the sun gear (32), in that the first guide surface (S178), provided on the housing (170), has a fifth diameter (d178), in that the second guide surface (S'178), provided on the case (170), has a sixth diameter (d'178), and in that the fifth and sixth diameters (d178, d'178) are different.

7. Reducer (19) of an electromechanical actuator (11) according to one any of claims | to 6, characterized in that the first and second guide surfaces (S1, S2), provided on the carrier- tellites (38), are defined with the same tolerance.

8. Reducer (19) of an electromechanical actuator (11) according to one any of claims | to 7, characterized in that the sun gear (32) and the satellite gears (33) are helical teeth (324, 334), in that the reduction stage (180) further comprises at least: - a first pad (42), and - a second pad (44), in that the first bearing (42) forms a guide bearing for the sun gear (32) and is mounted tightly against the first surface of guide (S1), arranged on the planet carrier (38), in that the planet carrier (38) further comprises at least one third guide surface (S'1) of the planet carrier (38) relative to the case (170), in that the second bearing (44) forms a guide bearing for the sun gear (32) and for the planet carrier (38) and is mounted tightly against the third guide surface (S'1), provided on the carrier- satellites (38), and in that, along a longitudinal axis (X326) of the sun gear (32), the first and third guide surfaces (S1, S'1), provided on the planet carrier (38), are arranged on either side of the teeth (324) helical of the sun pinion (32).

9. Reducer (19) of an electromechanical actuator (11) according to one any of claims 1, 2, 4, 5 and 7, characterized in that the sun gear (32) and the satellite gears (33) are right teeth (324, 334), in that the second guide surface (S2), provided on the carrier- satellites (38), receives in sliding rotating support a part (326b) of the sun gable (32), in that the housing (170) comprises at least a first surface of guidance (S178) of the planet carrier (38), in that the reducer (19) further comprises at least one universal joint (329), the universal joint (329) being meshed with the sun gear (32), and in that the first guide surface (S178), provided on the housing (170), receives in sliding rotating support the cardan (329).

10. Range of at least two reducers (19) for an electro-actuator mechanical (11) characterized in that each reducer (19) conforms to any one of the re- sales | at 9, in that the sun gear (32) and the satellite gears (33) of the stage reduction (180) of a first reducer (19) of the range are at helical teeth (324, 334), in that the sun gear (32) and the satellite gears (33) of the stage reduction (180) of a second reducer (19) of the range are at right teeth (324, 334), in that the planet carrier (38) of the first reducer (19) is identical to the planet carrier (38) of the second reducer (19), in that the first guide surface (S1), provided on the carrier- satellites (38), guides the sun gear (32) of the first reducer (19), and in that the second guide surface (S2), provided on the carrier- satellites (38), guides the sun gear (32) of the second reducer (19).

11. Range of at least two reducers (19) for an electro-actuator mechanical (11) according to claim 10, characterized in that the first and second reducers (19) are in accordance with the claim 5, in that the housing (170) of the first reducer (19) is identical to the housing (170) of the second reducer (19), in that the first guide surface (S178), provided on the housing (170), guides the planet carrier (38) in the first reducer (19), and in that the second guide surface (S'178), provided on the housing (170), guides the planet carrier (38) in the second reducer (19).

12. Range of at least two reducers (19) for an electro-actuator mechanical (11) according to claim 10 or according to claim 11, characterized in that the range comprises at least four reducers (19), in that the reduction stage (180) of two reducers (19), among the four reducers (19), includes a sun gear (32) and pinions satellites (33) with helical teeth (324, 334), in that the reduction stage (180) of two other reducers (19), among the four reducers (19), includes a sun gear (32) and satellite pinions (33) with straight teeth (324, 334), in that the reduction stage (180) of one of the reducers (19) to helical toothing (324, 334) and the reduction stage (180) of one of the reducers (19) with straight teeth (324, 334) have the same first ratio reduction (K1), in that the reduction stage (180) of another of the reducers (19) to helical toothing (324, 334) and the reduction stage (180) of another reducers (19) with straight teeth (324, 334) have the same second reduction ratio (K2), and in that the second reduction ratio (K2) is different from the first reduction ratio (K1).

13. Electromechanical actuator (11) of a concealment device (3), the electromechanical actuator (11) comprising at least: - a casing (17), - an electric motor (16), and - a reducer (19), the reducer (19) being coupled with the motor electrical (16), either directly or through an ad- additional (329, 29) of the electromechanical actuator (11), the electric motor (16) and the reducer (19) being housed inside the casing (17), characterized in that the reducer (19) conforms to any one of claims 1 to 9 or belongs to a range of reducers (19) according to any one of claims 10 to 12.

14. Concealing device (3), the occultation device (3) comprising at least: - a screen (2), and - an electromechanical actuator (11), the screen (2) being driven in de- placement by the electromechanical actuator (11), characterized in that the electromechanical actuator (11) conforms to claim 13.