Electrical device equipped with a component that exhibits eccentric motion

Abstract

The present invention relates to an electric device comprising a member (300) that performs an eccentric motion and is coupled to an electric motor (200) via torque transmission means (100) consisting of two tubular integral parts (110, 150) coupled by an interlock connection. The first integral part (110) supports the rotor (220) of the electric motor (200) and has a first cylindrical segment (111) having an outer diameter D r and supports a rear bearing (240) and has a second cylindrical segment (112) having an outer diameter D b . These segments (111, 112) are coaxial with a first longitudinal axis (102). The second integral part (150) supports a front bearing (245) and has a cylindrical segment (151) having an outer diameter D a and is coaxial with the first longitudinal axis (102), and has a cylindrical drive segment (152) that is eccentric with respect to this longitudinal axis (102) and has an outer diameter D e . The two integral parts (110, 150) are coupled by an interlock connection, and the interlock connection extends to one of the integral parts (110, 150) and engages a male guide segment (155) having an outer diameter (D c ) and a length (L e ) in a hollow female guide segment (115) having a depth (L c ) provided in the other of these parts, and (L c ) is 1.5 times or more of (D c ).

Description

[Technical Field]

[0001] The present invention relates to the field of electric devices formed by eccentric members driven by electromechanisms.

[0002] Driving an eccentric member generates high mechanical stress, particularly at the connection point between the motor shaft and the driven member, due to the asymmetry of the rotational mass.

[0003] A non-limiting example of such a device is a scroll compressor consisting of two spirals, one fixed and the other performing orbital motion that produces compression, with the intake chamber located around the two spirals, the discharge section located in the center, and the gas escaping through a hole.

[0004] A vane compressor is another example of such an electric device involving eccentric motion. The principle involves a cylindrical stator (housing) with radial inlets and outlets, within which an eccentrically mounted circular rotor rotates. The rotor or stator has slots through which vanes can slide radially. As the rotor rotates, the vanes ensure the closure of the gap between the stator wall and the rotor wall. In this case, a gap is formed between the stator wall, the two vanes, and the rotor, which narrows as the rotor rotates toward the compressed air outlet.

[0005] The motor associated with the internal cycloidal gearbox consists of another example of a device having an eccentric member and an external cycloidal gear train. [Background technology]

[0006] In the prior art, devices are known that implement a single drive shaft to directly control the orbital motion of an eccentric member.

[0007] U.S. Patent No. 5040958 describes a scroll compressor comprising a fixed scroll element having a fixed end plate and a fixed spiral wrap extending from the fixed end plate, and a revolving scroll element having a revolving end plate and a revolving spiral wrap extending from the revolving end plate, revolving around the axis of the fixed scroll member, and having a revolving bearing, wherein the wrap of the fixed scroll member and the wrap of the revolving scroll member engage with each other to form a fluid compression chamber.

[0008] A rotation prevention device for preventing the rotation of the orbiting scroll member allows the orbiting scroll member to orbit around the axis of the stationary scroll member. The main shaft is rotatable on its own axis and has a pivot pin with an axis spaced apart from the axis of the main shaft. The eccentric drive shaft has an axis spaced apart from the axis of the main shaft and orbits around the axis of the main shaft, and the eccentric drive shaft can rotationally engage with an orbiting bearing so as to enable the eccentric drive shaft to drive the orbiting scroll member around the axis of the stationary scroll member, and the eccentric drive shaft has a pivot bearing with an axis spaced apart from the axis of the eccentric drive shaft and can rotationally engage with the pivot pin so as to enable the eccentric drive shaft to rotate around the axis of the pivot pin, and the distance between the axis of the eccentric drive shaft and the axis of the main shaft is adapted to vary, and the main shaft drives the eccentric drive shaft to orbit around the axis of the main shaft. The rotational moment generated by the centrifugal force of the balance weight pulls the eccentric drive shaft toward the main shaft. The distance between the limiting means that restricts the orbital range of motion of the eccentric drive shaft around the axis of the pivot pin and the axis of the main shaft is greater in the direction of the line connecting the axis of the main shaft and the axis of the eccentric drive shaft than the distance between the axis of the main shaft and the axis of the pivot pin.

[0009] European Patent No. 2636903 describes a rotary compressor comprising a housing, a cylinder, a rotating shaft, rollers, and an eccentric cam. The cylinder may be installed inside the housing and configured to provide space for compressing gas. The rotating shaft may be positioned to pass through the cylinder. The rollers may be configured to compress gas by rotating along the inner circumferential surface of the cylinder. The eccentric cam may be formed integrally with the rotating shaft and positioned inside the rollers. The eccentric cam may be positioned axially eccentric on the axis of the rotating shaft.

[0010] Disadvantages of prior art Conventional solutions have several drawbacks. Solutions that provide a single, integrated shaft with eccentric ends involve complex work for assembling and disassembling the shaft. These solutions are not easy to repair.

[0011] Furthermore, these methods involve lengthy, costly, and complex machining operations. Machining a raw bar, in particular, generates a large amount of chips over the considerable span length that must be performed (machining, number of passes, hardening, grinding).

[0012] The assembly is complex. A single shaft receives bearings at each end and a bundle of rotor stacks in the center, and is then incorporated into the system frame via a pre-assembled stator within the main housing. The rear bearing supports the shaft that engages within the main housing. The front bearing is supported in a sub-housing (compressor chamber) attached to the main housing. This type of assembly is very restrictive, on the one hand, in terms of bearing size and dimensions (they must be able to pass through the stator and therefore must be smaller than its inner diameter), and on the other hand, in terms of the implementation of balancing means and weights.

[0013] Furthermore, single-axis solutions present problems in inserting the motor's printed drive circuit board unless slots are provided for sliding the circuit board around the axis, reducing the available surface area on the printed circuit board. These conventional solutions mean that the control electronics must be placed at the rear of the system, resulting in a larger volume, a greater distance between the motor and the electronics (and thus increased complexity and cost regarding electrical connections to the stator and position / speed sensor functions), and the need to provide a specific liquid cooling circuit for the rear electronics.

[0014] Means for solving the problem To address the shortcomings of the background technology, the present invention relates, in its most general sense, to an apparatus comprising a member that performs eccentric motion coupled to an electric motor, wherein the eccentric member is driven by the electric motor via a torque transmission means consisting of two tubular integrated portions coupled by an interlock connection. -The first integrated part is • Supports the rotor of the electric motor, outer diameter D r A first cylindrical segment having, • Supports the rear bearing, outer diameter D b It has a second cylindrical segment having, • The segment in question is coaxial. -The second integrated part is • Supports the front bearing, outer diameter D a A cylindrical segment having and being coaxial with the segment of the first part, • Eccentric with respect to the longitudinal axis, outer diameter D e It has a cylindrical drive segment. -These two integrated parts are joined by an interlocking connection, and the interlocking connection is • A depth L extending from one of the integrated parts (110, 150) and provided on the other of the integrated part c The outer diameter D engages with the hollow female guide segment (115). c and consists of a male guide segment of length L, L cis 1.5 times or more of D c and above. · The two integral parts further include at least one angular locking means and an axial locking means.

[0015] According to a modification - The first integral part supports a sensor and further has an additional cylindrical segment having an outer diameter D s and being coaxial with the longitudinal axis. - The first integral part supports a rear balance weight and further has an additional cylindrical segment having an outer diameter D m and being coaxial with the longitudinal axis. - The first integral part supports a rotor of an electric motor for axial positioning of the rotor and further has an annular shoulder adjacent to the cylindrical segment. - The second part supports a front balance weight and further has an additional cylindrical segment having an outer diameter D M and the additional segment is coaxial with the longitudinal axis when the two parts are joined. - The second part coincides with a passage of a wall separating the motor from the driven member and further has an additional cylindrical segment having an outer diameter D a and above. - The motor includes a printed circuit board disposed laterally between the rotor (220) and the second bearing, and the printed circuit board has a passage through which the torque transmission means passes. - One or more segments passing through the passage of the printed circuit board have a minimum diameter. - The sensor-carrying segment is the segment closest to the printed circuit board. - At least one of the first part and the second part is hollow except for the front walls of the male guide segment and the female guide segment. - The angular locking means consists of cooperating torque transmission flat surfaces. - The axial locking means consists of an axial screw connecting the male guide segment and the female guide segment, the axial end of the male guide segment having an axial thread, and the bottom of the female guide segment having a bore for the passage of the axial screw, ensuring that the axial end of the male guide segment is blocked against the bottom of the female guide segment. - The device comprises a first casing cooled by fluid circulation, the first casing comprising the electric motor, and a second casing cooled by fluid circulation comprising the eccentric driven member, characterized in that the fluid circulation circuits of the two casings open to adjacent surfaces in an aligned manner when the casings are joined together. - The intermediate casing includes at least two fluid connection points, one of which is open at the fluid connection point of the first casing and the other of which is open at the fluid connection point of the second casing. - The intermediate casing comprises at least two fastening means. - The intermediate casing is provided with at least one lifting eyelet. [Brief explanation of the drawing]

[0016] The present invention will be better understood by reading the following description relating to non-limiting exemplary embodiments illustrated by the accompanying drawings. [Figure 1] An overview of the motorization is shown in a front three-quarter perspective cross-sectional view of an exemplary embodiment of the scroll compressor according to the present invention. [Figure 2] This is an exploded view of an exemplary embodiment of a torque transmission means comprising two integrated parts for a compressor according to the present invention. [Figure 3] This shows a cross-sectional view of the first integrated portion of the torque transmission means according to the present invention. [Figure 4] This shows a perspective view of an exemplary embodiment of a compressor according to the present invention, and a cross-sectional view of a second integrated portion of the torque transmission means according to the present invention. [Figure 5]An exploded three-quarter front perspective view of an exemplary embodiment of a scroll compressor according to the present invention shows an overview of the motorization. [Figure 6] An overview of the spiral compressor according to the present invention is shown. [Figure 7] A cross-sectional view of an exemplary embodiment of a torque transmission means for a compressor according to the present invention, which includes a position sensor facing an electronic card, is shown. [Figure 8a] A modified example of the first integrated portion of the torque transmission means for a compressor according to the present invention is shown. [Figure 8b] A modified example of another embodiment of the first integral portion of the torque transmission means of the compressor according to the present invention is shown. [Figure 9a] This shows a modified embodiment of the connection between the first integrated part and the second integrated part of the torque transmission means of the compressor according to the present invention. [Figure 9b] This shows a modified example of another embodiment of the connection between the first and second integral parts of the torque transmission means of the compressor according to the present invention. [Figure 10] This shows a modified example of another embodiment of the connection between the first and second integral parts of the torque transmission means of the compressor according to the present invention. [Figure 11] This shows a modified example of another embodiment of the connection between the first and second integral parts of the torque transmission means of the compressor according to the present invention. [Figure 12] This shows a modified example of another embodiment of the connection between the first and second integral parts of the torque transmission means of the compressor according to the present invention. [Figure 13] This shows a modified example of another embodiment of the connection between the first and second integral parts of the torque transmission means of the compressor according to the present invention. [Figure 14] This shows a modified example of another embodiment of the connection between the first and second integral parts of the torque transmission means of the compressor according to the present invention. [Figure 15] A modified example of an embodiment of the position sensor for the torque transmission means of a compressor according to the present invention is shown.

[0017] general principle Figures 1-4 illustrate examples of applications of the torque transmission means (100) according to the present invention for driving a member (300) that performs eccentric motion by an electric motor (200).

[0018] The examples disclosed relate, more specifically, to air compressors for supplying air to the braking systems of vehicles such as trucks or buses, particularly electric vehicles.

[0019] In these applications, various constraints apply to the design of the compressor. Specifically, in addition to high reliability and robustness for safety applications, volume reduction is required for vehicle applications. In the case of electric vehicles, constraints also relate to being lightweight and highly efficient so as not to impair the vehicle's range.

[0020] The present invention aims to address these constraints by proposing a system for coupling a motor (200) to a component (300), enabling a reduction in both the axial and radial volume of the system, and ensuring easy access to the components of the electric motor (200) and the components of the driven component (300) in order to enable disassembly for maintenance, repair, and testing, or further, to keep the driven component (300), such as a compressor, immutable and to provide a power range by selecting effective lengths of rotor (220) and stator (210) suitable for the desired power for the motor component (200).

[0021] Furthermore, the ease of assembly allows for testing of partial components or subassemblies, such as only the electronic card (250) or the electric motor portion (200) separated from the driven member (300), or only the driven member portion (300) separated from the electric motor (200), during different assembly processes in manufacturing.

[0022] Furthermore, it allows for the repair, maintenance, or replacement of one of the defective parts (motor (200) or driven component (300)), or even replacement with a more appropriate part.

[0023] These constraints also require complete guidance of the torque transmission means (100), as well as control of the axial and radial clearances of the different components, particularly in eccentric motion and unbalanced conditions that can accelerate fatigue of the torque transmission means (100).

[0024] To achieve these objectives, the torque transmission means (100) consists of an assembly of two integral parts (110) and (150), shown separately in Figures 2, 3, and 4. The first integral part (110) supports the rotor (220) of the electric motor (200), and the second integral part (150) drives the member (300).

[0025] "One-piece" is understood to mean the fact that each part (110, 150) is manufactured from a single material component without assembly, for example by machining a blank, by casting, and by any other method that avoids the assembly of separate components.

[0026] An important aspect of the present invention relates to the coupling of these two parts (110, 150), which must be able to transmit high torque between the motor (200) and the member (300) and withstand stress resulting from eccentric motion, while also being able to be disengaged to facilitate assembly and disassembly.

[0027] The electromachine has a first casing (510) housing a motor and a second casing (520) housing a driven member (300), the two casings joined by an intermediate casing (530) and closed by a cover (540) to form a leak-proof housing (500). In the following description, “rear” refers to the side closest to the motor (200) and “front” refers to the side closest to the driven member (300).

[0028] Details of the embodiment of the first integral part (110) This first integrated part (110) is intended to support the rotor (220) of the motor (200). For this purpose, it consists of a part having a cylindrical outer sleeve with multiple steps of different diameters. - Supports the rotor (220) of the electric motor (200), with an outer diameter D r A first cylindrical segment (111) having the length of the first cylindrical segment (111) corresponds to the axial length of the rotor (220). The rotor (220) is attached to the first segment (111) in a known manner. - Supports the rear bearing (240), outer diameter D b A second cylindrical segment (112) is provided. This rear bearing (240) guides the torque transmission means (100) relative to the housing (500) of the device.

[0029] These two cylindrical segments (111, 112) are coaxial.

[0030] In front of the first cylindrical segment (111) that supports the rotor (220) of the electric motor, the outer diameter D r Smaller outer diameter D s A cylindrical segment (116) is provided, which allows the ring-shaped position sensor (260) to be positioned.

[0031] Diameter D located between the first cylindrical segment (111) and the second cylindrical segment (112) m The intermediate segment (114) is intended to accept an asymmetrical balance weight (124) to compensate for the imbalance caused by the driven eccentric motion.

[0032] Optionally, as shown in Figures 8a and 8b, the balance weight (124) is integrated into a bundle of stacked rotors (220) supported by the first integral portion (110), or formed on the radial extension of the first integral portion (110).

[0033] Preferably, but not limited to the above, the cross-section of the intermediate segment (114) is larger than the cross-section of the first cylindrical segment (111) and / or the cross-section of the second cylindrical segment (112), thereby forming shoulders to which the rotors (220) are attached and to which the rear bearings (240), which are mounted by sliding, are supported in the axial direction.

[0034] Optionally, to ensure a longer service life for the guide element, an elastic axial preloading means (241), such as a spring washer, can be integrated between the rear bearing (240) and the shoulder of the intermediate cylindrical segment (114).

[0035] Details of the interlock connection configuration The first portion (110) has a hollow guide segment (115) for receiving a complementary male guide segment (155) of the second portion (150) and for forming an interlocking connection with high axial, tangential, and radial rigidity.

[0036] In the disclosed example, the guide segment has a bottom (118) that forms a forward stopper for the complementary male guide segment (155). The bottom (118) has a central bore (119) through which a screw (180) passes and constitutes a locking means (195) that ensures connection and axial locking of the two integral parts (110, 150).

[0037] The first part (110) also has, in the disclosed example, a rotation prevention means provided on a complementary male guide segment (155) and consisting of two complementary flat surfaces (120, 121) to two diametrically opposed flat surfaces (171) (only one of which is shown in Figure 2).

[0038] In the disclosed examples, these planar surfaces are symmetrical with respect to the axial plane. Advantageously, they may be asymmetrical to allow for only one assembly possibility. It is also possible to provide each part with only one anti-rotation means, for example, a single planar surface.

[0039] Alternatively, as shown in Figures 9a and 9b, rotation prevention of the two integral parts (110, 150) can be achieved by a system of channels (148) or splines (149) located in the gap (176) of the first integral part and the base (126) of the second integral part.

[0040] Alternatively, as shown in Figure 10, preventing rotation of the two integrated parts (110, 150) can be achieved by a key (147) supported by a cylindrical segment (115), which cooperates with a counterbore (146) located on the cylindrical segment (155) to lock the first and second integrated parts.

[0041] Alternatively, as shown in Figure 11, rotation prevention of the two parts (110, 150) can be achieved by an elastic pin (145) that radially penetrates the first and second integral parts in the gap (126) and base (176).

[0042] An important consideration is the long centering of the two integral parts (110, 150) necessary to avoid the need for additional guides. This long centering is ensured by the fact that the hollow guide segment (115) of the first integral part (110) has an inner diameter corresponding to the outer diameter of the complementary male guide segment (155) of the second integral part (150), and preferably has an H7g6 type mating, referring to the mating table proposed by the specification of standard ISO 286-1 dated April 15, 2010.

[0043] Alternatively, the mating may be a tighter type, such as H7m6 or H7p6, in which the two parts (110, 150) are press-fitted together while maintaining a state that allows for disassembly, for example, by heating.

[0044] To achieve long centering of two integrated parts 110 and 150, length L c and diameter D c The length ratio between them is greater than 1.5, and is typically 2. -Lc This corresponds to the length of the tubular interaction between the hollow guide segment (115) of the first integrated portion (110) and the complementary male guide segment (155) of the second integrated portion (150). -D c This corresponds to the inner diameter of the hollow guide segment (115) of the first integrated portion (110) and the outer diameter of the complementary male guide segment (155) of the second integrated portion (150).

[0045] The hollow guide segment (115) of the first integral portion (110) opens into an asymmetric inlet gap (126) having a larger cross-section than the cross-section of the hollow guide segment (115), and two peripheral flat surfaces (120, 121) are connected by two semi-tubular segments. The complementary male guide segment (155) of the second integral portion (150) has an asymmetric base (176) behind the complementary male guide segment (155) of the second integral portion (150) having a cross-section and axial length complementary to the cross-section of the asymmetric inlet gap (126).

[0046] Details of the second integral part (150) embodiment This second integrated part (150) is intended to drive a member (300) located within the housing (500). For this purpose, it consists of a part having a cylindrical outer sleeve with multiple steps of different diameters. - Supports the front bearing (245), outer diameter D a A cylindrical segment (151) is provided, and is coaxial with the segments (111, 112) of the first integral portion (110). The front bearing (245) is press-fitted on one side into this cylindrical segment (151) and on the other side into a passage in the wall (531) of the intermediate casing (530). - Eccentric with respect to the longitudinal axis (102), outer diameter D e A cylindrical drive segment (152) having, -Disk shoulder portion (163) that forms an axial stopper portion for positioning the front bearing (245).

[0047] The rear surface of the disc shoulder (163) defines a cylindrical surface (153) that cooperates with a gasket (532) for a passage in the wall (531) of the intermediate casing (530). This disc shoulder (163) extends rearward toward the motor by a base (156) and a complementary male guide segment (155).

[0048] The complementary male guide segment (155) is at least partially solid. Solidity is understood as the fact that segment (155) is not open.

[0049] The front end (157) of the complementary male guide segment (155) has a hole with an axial thread (158) for locking by the aforementioned screw (180), forming a locking means (195) that ensures the connection and axial locking of the two parts (110, 150).

[0050] Alternatively, as shown in Figure 12, axial locking of the two integral parts (110, 150) can be achieved by a threaded surface (144) located at the end of a cylindrical segment (155), which passes axially through the intermediate cylindrical segment (114) of the first integral part (110), and this threaded surface (144) cooperates with a nut (143) to lock the first and second integral parts.

[0051] Alternatively, as shown in Figure 13, axial locking of the two parts (110, 150) can be achieved by a smooth surface (142) located at the end of a cylindrical segment (155), which passes axially through an intermediate cylindrical segment (114) of the first integral part (110), and which has a groove suitable for receiving a retaining ring (or retaining ring) (141) for locking the first integral part and the second integral part.

[0052] Advantageously, particularly to further reduce manufacturing costs, the axial locking and anti-rotation of the first and second integral parts can be achieved by a single specific screw (180), as shown in Figure 14. On the one hand, friction between the threads of the screw and the tapping of the screw hole in the segment (155) of the second integral part (150), and on the other hand, friction between the screw head and the front surface (113) of the passage (119) of the first integral part (110) allows torque transmission to perform the anti-rotation function.

[0053] The second integrated section (150) can be partially hollow, except for the lateral partition (162) that ensures leak prevention, along with the gasket (532), in order to lighten the assembly.

[0054] In an advantageous embodiment, the second integral portion (150) has three hollow sections whose diameter decreases from front to rear, and the walls have a thickness optimized to accommodate weight reduction of the part as well as mechanical resistance to torsion and axial deformation.

[0055] Diameter D is located between the cylindrical segment (151) and the eccentric cylindrical segment (152) that support the front bearing 245. M The intermediate segment (154) is intended to receive an asymmetrical balance weight 174 that compensates for the imbalance caused by the driven eccentric motion, and this weight 174 cooperates with the weight 124 of the first integral part 110. For this purpose, the balance weight (174) has an outer radius R M It has a projection (177) that protrudes across the angular sector, and its center is located on the axis (102).

[0056] The anti-rotation means, in particular, in the example described, ensure the angular indexing of the balance weight (124, 174) according to an angular reference common to the angular reference of the driven eccentric member (300). For this purpose, the intermediate cylindrical segment (114) of the first integral part (110) has a flat surface that cooperates with the corresponding flat surface (121) of the weight (124) for angular indexing with respect to the flat surface (120, 125). For this purpose, the cylindrical segment (151) has an indexing pin (159) that cooperates with the elliptical hole (175) of the weight (174) for angular indexing with respect to the flat surface (171), with only one of the flat surfaces shown in [Figure 2].

[0057] The segment (152) is eccentric with respect to the eccentric axis (101), and the eccentric axis (101) is located at a distance d laterally with respect to the longitudinal axis (102). ex It is offset by only a small amount and cooperates with the eccentrically moving part of the driven member (300), such as a vane pump or scroll pump.

[0058] Details of the Housing (500) Embodiment The housing (500) is formed by an assembly of a first casing (510) housing the electric motor (200), an intermediate casing (530), and a second casing (520) housing the driven components (300).

[0059] The assembly uses a gasket (532) and a lateral partition (162) to form a leak-proof housing (500) having a wall (531) that fluidly isolates the electric motor (200) from the driven member (300), and the dynamic gasket (532) cooperates with the cylindrical segment (153) of a second non-opening integral portion (150). Only two bearings (240, 245) guide the torque transmission means (100) relative to the housing (500). - A rear bearing (240) mounted within the cover (540) of the first casing (510) and on the segment (112) of the first integral part (110). - A front bearing (245) mounted within the wall (531) of the intermediate casing (530) and on the segment (151) of the second integral portion (150).

[0060] The interlocking connection formed by the tubular interaction region between the hollow guide segment (115) of the first integral part (110) and the complementary male guide segment (155) of the second integral part (150) is necessarily located between the rear bearing (240) and the front bearing (245).

[0061] Despite using torque transmission means (100) in two sections (110, 150), providing only two guide bearings ensures a robust and economical balanced guide, limiting the risk of high stress.

[0062] The intermediate casing (530) has a set of fastening means, or several sets of fastening means that allow for an increase in the range of applications. This intermediate component is located near the center of gravity of the device and may also include lifting grips, such as lifting eyelets (538), for handling the compressor assembly.

[0063] It should be noted that the first casing (510) that receives the electric motor (200) can be composed of an assembly of several parts. For example, the jacket of the motor (515) can be assembled together with an interface component (516) that receives an electronic card (250) to form the first casing. This method is particularly advantageous for reducing manufacturing costs when multiple lengths of electric motors (200) are envisioned to meet different specifications while retaining most of the system components.

[0064] Details of the embodiment of the electronic card (250) The electric motor (200) consists of a rotor (220) and a wound stator (210) in a known manner and is controlled by an electronic card (250) positioned laterally between a wall (531) and the rotor (210) and protected in a leak-proof manner behind a gasket (532). The electronic card (250) is penetrated by a cutout (251) with a diameter larger than the diameter of the segments (111, 116, 155, 176) through which it passes during assembly or disassembly.

[0065] To ensure cooling of the components of the electronic card (250), it is advantageous to ensure thermal coupling with the first casing (510), especially when the casing (510) is connected to a cooling fluid circulation circuit.

[0066] A sensor (260) attached to a segment (116) of the first integral portion (110) that passes through the electronic card (250) is axially positioned relative to the electronic card (250) and enables electromagnetic or optionally optical interaction with a probe positioned on the card (250). Instead of a permanent magnet solution, the sensor (260) can be a magnet-free inductive or variable reluctance sensor, achieved by the cooperation of a ferromagnetic target (261) attached to an additional cylindrical segment (116) of the first integral portion (110) and a probe on the electronic card, as shown in Figure 15.

Claims

1. An electric device comprising a torque transmission means (100), an electric motor (200), and a member (300) that performs eccentric motion and is coupled to the electric motor (200), The eccentric member (300) is The torque transmission means (100), consisting of two tubular integrated portions (110, 150) connected by an interlock connection, is driven by the electric motor (200). The first integrated portion (110) is - Supports the rotor (220) of the electric motor (200), with an outer diameter D ｒ A first cylindrical segment (111) having, - Supports the rear bearing (240), with an outer diameter D ｂ It has a second cylindrical segment (112) having, The segments (111, 112) are coaxial with the first longitudinal axis (102), The second integrated portion (150) is - Supports the front bearing (245), outer diameter D ａ A cylindrical segment (151) having a first longitudinal axis (102) and being coaxial with the first longitudinal axis (102), - Eccentric with respect to the longitudinal axis (102), outer diameter D ｅ It has a cylindrical drive segment (152) having, The two integrated parts (110, 150) are connected by an interlock connection, and the interlock connection is - A depth L extending from one of the integrated portions (110, 150) and provided in the other portion ｃ A hollow female guide segment (115) engages with an outer diameter Dcet and length L. ｃ It consists of the male guide segment (155), L ｃ D ｃ It is more than 1.5 times, - The two integrated parts (110, 150) are at least A device further comprising one angle locking means (190) and an axial locking means (195).

2. The first integral part (110) supports the sensor (260) and has an outer diameter D ｓ and further includes an additional cylindrical segment (116) that is coaxial with the longitudinal axis (102), the electric device according to claim 1, characterized in that.

3. The first integrated portion (110) supports the rear balance weight (124), and has an outer diameter D ｍ The electric motor according to claim 1 or 2, further comprising an additional cylindrical segment (114) having a longitudinal axis (102) and being coaxial with the longitudinal axis (102).

4. The electric motor according to claim 1 or 2, wherein the first integrated portion (110) further has an annular shoulder adjacent to the cylindrical segment (111) that supports the rotor (220) of the electric motor (200) for axial positioning of the rotor (220).

5. The second portion (150) supports the front balance weight (174), and has an outer diameter D Ｍ It further has an additional cylindrical segment (154) having, the additional segment (154) being coaxial with the eccentric axis (101) when the two parts (110, 150) are joined, and the balance weight (174) having an outer radius R Ｍ The electric motor according to any one of claims 1 to 3, characterized in that it has a projection (177) that protrudes across the angular sector, and its center is located on the longitudinal axis (102).

6. The electric motor according to claim 1, wherein the second portion (150) further has an additional cylindrical segment (153) corresponding to a passage in a wall (531) separating the motor (200) from the driven member (300), and the gasket (532) cooperates with the cylindrical segment (153) and the wall (531).

7. The electric motor according to claim 1, wherein the motor (200) comprises a printed circuit board (250) arranged laterally between the rotor (220) and the second bearing (245), and the printed circuit board (250) has a passage (251) through which the torque transmission means (100) passes.

8. The electric motor according to claim 7, characterized in that one or more segments (155) passing through the passage (251) of the printed circuit board (250) have the smallest diameter.

9. The electric motor device according to claims 2 and 8, characterized in that the segment (116) supporting the sensor (260) is the segment closest to the printed circuit board (250).

10. The electric motor according to claim 1, characterized in that at least one of the first integrated portion and the second integrated portion (110, 150) is hollow to provide leak prevention, except for the lateral partition (162).

11. The electric motor device according to claim 1, characterized in that the angle locking means (190) consists of cooperating torque transmission flat surfaces (120, 121, 171).

12. The electric motor according to claim 1, wherein the axial locking means (195) comprises an axial screw (180) connecting the male guide segment (155) and the female guide segment (115), the axial end (157) of the male guide segment (155) has an axial thread (158), and the bottom (118) of the female guide segment (115) has a bore for the passage of the screw (180), ensuring that the axial end (157) of the male guide segment (155) is blocked against the bottom (118) of the female guide segment (115).

13. The electric motor device according to claim 12, characterized by comprising an intermediate casing (530) having at least two fastening means (535, 536).

14. The electric motor device according to claim 1, characterized in that the intermediate casing (530) comprises at least one lifting eyelet (538).

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