Motorised device comprising a member with eccentric movement

Abstract

The invention relates to a motorised device comprising a member (300) performing an eccentric movement coupled to an electric motor (200) via a torque-transmission means (100) consisting of two tubular integral portions (110, 150) coupled by an interlocking connection. The first integral portion (110) has a first cylindrical segment (111) supporting the rotor (220) of the electric motor (200) having an outer diameter (Dr), and a second cylindrical segment (112) supporting a rear bearing (240) having an outer diameter (Db), these segments (111, 112) being coaxial with a first longitudinal axis (102). The second integral portion (150) has a cylindrical segment (151) supporting a front bearing (245) having an outer diameter (Da)<sb / > coaxial with the first longitudinal axis (102), and a cylindrical drive segment (152), which is eccentric with respect to this longitudinal axis (102), having an outer diameter (De). The two integral portions (110, 150) are coupled by an interlocking connection consisting of a male guide segment (155) of outer diameter (Dc)<sb / > and of length (Le)<sb / > extending one of the integral portions (110, 150), engaged in a hollow female guide segment (115) of depth (Lc)<sb / > provided in the other one of these portions, where (Lc)<sb / > is greater than or equal to 1.5 times (Dc).

Description

MOTORIZED EQUIPMENT COMPRISING AN ECCENTRIC MOVEMENT MEMBER Field of invention

[0001] The present invention relates to the field of electrical equipment formed by an eccentric member driven by an electrical machine.

[0002] Driving an eccentric component causes significant mechanical stress due to the asymmetries of the rotating masses, particularly on the coupling of the motor shaft with the driven component.

[0003] Without limitation, an example of such equipment is a “Scroll” type compressor consisting of two spirals, one fixed, the other in orbital movement which creates the compression, the suction chamber is located around the two spirals and the discharge is located in the center where the gas escapes through an orifice.

[0004] Vane compressors are another example of such eccentrically moving electrical equipment. The principle consists of a cylindrical stator (housing) with a radial inlet and outlet, in which a circular rotor rotates, mounted eccentrically. The rotor or stator is equipped with slots in which the vanes can slide radially. As the rotor rotates, the vanes ensure the closure of the gap between the stator wall and the rotor wall. A gap then forms between the stator wall, the two vanes, and the rotor, which shrinks as the rotor rotates towards the compressed air outlet.

[0005] Another example of eccentric gear equipment is motors combined with a hypocycloidal reducer, as are epicyclic gear trains. State of the art

[0006] In the state of the art, equipment is known which uses a single motor shaft directly controlling the orbital movement of the eccentric member.

[0007] US5040958 discloses a scroll compressor comprising a stationary scroll element comprising a stationary end plate and a stationary spiral winding extending from the stationary end plate; an orbiting scroll element comprising an orbiting end plate and an orbiting spiral winding extending from the orbiting end plate and which orbits about the axis of the stationary scroll element and has an orbiting bearing, the windings of the stationary scroll element and the orbiting scroll element engaging each other to form a fluid compression chamber;

[0008] An anti-rotation device to prevent the orbiting scroll element from rotating about its own axis and to allow the orbiting scroll element to orbit about the axis of the fixed scroll element. A main shaft rotatable about its own axis and has a pivot having an axis spaced from the axis of the main shaft.An eccentric drive shaft having an axis spaced from the axis of the main shaft and orbiting about the axis of the main shaft, said eccentric drive shaft rotatably engageable with the orbital bearing so as to enable the eccentric drive shaft to drive the scroll member orbiting about the axis of the fixed scroll member, said eccentric drive shaft comprising a pivot bearing having an axis spaced from the axis of the eccentric drive shaft and rotatably engageable with the pivot axis such that the eccentric drive shaft rotates about the axis of the pivot axis, a distance between the axis of the eccentric drive shaft and the axis of the main shaft is adapted to be varied, and the main shaft drives the eccentric drive shaft in orbit about the axis of the main shaft.The rotational moment generated by the centrifugal force of the balance weight attracts the eccentric drive shaft toward the main shaft; limiting means for limiting a range of orbital motion of the eccentric drive shaft about the axis of the pivot axis, a distance between the limiting means and the axis of the main shaft is greater in a direction of a line extending between the axis of the main shaft and the axis of the eccentric drive shaft than a distance between the axis of the main shaft and the axis of the pivot axis.

[0009] Patent EP2636903 describes a rotary compressor comprising a housing, a cylinder, a rotating shaft, a roller, and an eccentric cam. The cylinder may be installed inside the housing and configured to provide a space for compressing gas. The rotating shaft may be arranged while passing through the cylinder. The roller may be configured to compress gas by rotating along an inner circumferential surface of the cylinder. The eccentric cam may be integrally formed with the rotating shaft and arranged inside the roller. The eccentric cam may be arranged at an eccentric position in a shaft direction on an axial line of the rotating shaft. Disadvantages of the prior art

[0010] Prior art solutions have several drawbacks. Solutions providing a single, one-piece axle with an eccentric end require complex assembly and disassembly of the axle. These solutions do not allow for easy repair.

[0011] They also involve long, costly and complex machining operations: machining the raw bar will produce a significant quantity of shavings, particularly via a significant length of precise spans to be produced (machining, number of passes, hardening, grinding).

[0012] The assembly is complicated: the single axle receives a bearing at each end as well as a pack of rotor laminations in the center, it is then integrated into the system frame through the stator pre-assembled in the main housing, the rear bearing carrying the axle engaging in the main housing. The front bearing is carried by a secondary housing (compressor compartment) fixed on the main housing. This type of assembly is very restrictive for the sizing and size of the bearings on the one hand (which must be able to pass through the stator and therefore be smaller than its internal diameter), and on the other hand for the installation of the balancing means and masses.

[0013] Furthermore, solutions with a single axis pose a problem for the introduction of a motor control circuit board, unless a slot is provided to slide the circuit board around the axis, which reduces the available surface area on the circuit board. These prior art solutions then require the control electronics to be located at the rear of the system, resulting in greater bulk, a greater distance between the motor and the electronics (therefore complexity and costs on the electrical connections with the stator and on the position / speed sensor function) and the need to provide a specific liquid cooling circuit for the electronics at the rear. Solution provided by the invention

[0014] In order to overcome the drawbacks of the prior art, the present invention relates, in its most general sense, to equipment comprising a member performing an eccentric movement coupled to an electric motor, characterized in that said eccentric member is driven by said electric motor by a torque transfer means consisting of two tubular monobloc parts coupled by an embedded connection. The first monobloc part having a first cylindrical segment supporting the rotor of the electric motor having an external diameter D r a second cylindrical segment supporting a rear bearing having an outside diameter D b said segments being coaxialThe second single-piece part having a cylindrical segment supporting a front bearing having an external diameter D acoaxial with said segments of said first part a cylindrical drive segment, eccentric with respect to the longitudinal axis, having an external diameter D e Said two single-piece parts being coupled by an embedded connection constituted by: A male guide segment of external diameter D c and length L ENCASTREMENTprolongeant l’une desdites parties monoblocs (110, 150), engagé dans un segment de guidage femelle creux (115) de profondeur Lcprévu dans l’autre desdites parties, avec Lcsupérieur ou égal à 1,5 fois Dc Said two single-piece parts further comprising at least one angular and axial locking means.

[0015] According to variants: the first single-piece part also has an additional cylindrical segment supporting a sensor having an external diameter D s coaxial with the longitudinal axis, said first single-piece part further has an additional cylindrical segment supporting a rear balancing weight having an external diameter D mcoaxial with the longitudinal axissaid first one-piece part further has an annular shoulder adjacent to said cylindrical segment supporting the rotor of the electric motor, for the axial positioning of said rotorsaid second part further has an additional cylindrical segment supporting a front balancing weight having an outside diameter D M said additional segment being coaxial with the longitudinal axis when said two parts are coupled, said second part further has an additional cylindrical segment corresponding to the passage of the wall separating the motor from said driven member having an external diameter D a .said motor comprises a printed circuit arranged transversely between the rotor (220) and said second bearing, said printed circuit having a passage crossed by said torque transfer meansthe segment(s) crossing said passage of said printed circuit have the smallest diameterssaid segment carrying the sensor is the segment closest to said printed circuitat least one of said first and second parts is hollow, except for the front walls of said male and female guide segmentssaid angular locking means is constituted by cooperation of torque transmission flats.said axial locking means is constituted by an axial screw connecting said male guide segment and said female guide segment, the axial end of said male guide segment having an axial thread and the bottom of said female guide segment having a bore for the passage of said screw ensuring the locking of the axial end of said male guide segment against the bottom of said female guide segment. said equipment comprises a first casing cooled by fluid circulation, said first casing comprising said electric motor, and a second casing cooled by fluid circulation, comprising said eccentric driven member, and in that the fluid circulation circuits of said two casings open onto the adjacent faces in alignment when said casings are joined.comprises an intermediate casing comprising at least two fluid connections opening on one side at the level of the fluid connections of said first casing and on the other side at the level of the fluid connections of said second casing.said intermediate casing comprises at least two fixing meanssaid intermediate casing comprises at least one lifting eyelet.Detailed description of a non-limiting example of embodiment.

[0016] The present invention will be better understood on reading the following description, concerning a non-limiting example of embodiment illustrated by the appended drawings where:

[0017] represents an overall view of the motorization, in three-quarter perspective section from the front of an exemplary embodiment of a scroll compressor according to the invention,

[0018] represents an exploded view of an exemplary embodiment of a torque transfer means, provided with two single-piece parts, for a compressor according to the invention,

[0019] represents a sectional view of the first single-piece part of a torque transfer means according to the invention,

[0020] represents a sectional view of the second single-piece part of a torque transfer means according to the invention, in perspective of an exemplary embodiment of a compressor according to the invention,

[0021] represents an overall view of the motorization, in exploded three-quarter front perspective; of an exemplary embodiment of a scroll compressor according to the invention

[0022] represents an overall view of a scroll compressor according to the invention

[0023] represents a sectional view of an exemplary embodiment of a torque transfer means of a compressor according to the invention, provided with a position sensor opposite an electronic card,

[0024] represents an alternative embodiment of the first single-piece part of a torque transfer means of a compressor according to the invention.

[0025] represents another variant embodiment of the first single-piece part of a torque transfer means of a compressor according to the invention.

[0026] represents an alternative embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0027] represents another variant embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0028] represents another variant embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0029] represents another variant embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0030] represents another variant embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0031] represents another variant embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0032] represents another variant embodiment of the connection between the first and second single-piece parts of a torque transfer means of a compressor according to the invention.

[0033] represents an alternative embodiment of a position sensor of a torque transfer means of a compressor according to the invention. General principle

[0034] Figures 1 to 4 illustrate an example of application of a torque transmission means (100) according to the invention for driving a member (300) performing an eccentric movement by an electric motor (200).

[0035] The example described relates more specifically, but not exclusively, to an air compressor for supplying the braking system of a vehicle such as a truck or a coach and in particular on electrified vehicles.

[0036] For such applications, different constraints apply to the compressor design: in addition to high reliability and robustness for a safety application, application to a vehicle requires a reduced footprint. For an electric vehicle, the constraint also concerns lightness and high efficiency so as not to affect the vehicle's autonomy.

[0037] The invention aims to meet these constraints by proposing a system for coupling the motor (200) to the member (300) making it possible to reduce both the axial and radial size of the system, and also ensuring easy accessibility to the components of the electric motor (200) on the one hand and to the components of the member to be driven (300) in order to allow disassembly for maintenance, repair, testing, or even to offer a power range while keeping the part of the member to be driven (300), a compressor for example, unchanged and by selecting for the motor part (200) an active length of the rotor (220) and of the stator (210) adequate for the desired power.

[0038] The simplicity of the assembly also makes it possible to carry out tests of partial components or sub-assemblies during the various assembly stages in production, for example of the electronic card (250) or of the electric motor part (200) alone separated from the member (300) to be driven, or of the member part (300) to be driven separated from the electric motor (200).

[0039] It also allows the repair, maintenance or replacement of one of the defective parts (engine (200) or component (300) to be driven), or even replacement with a more suitable part.

[0040] These constraints also require perfect guidance of the torque transmission means (100) and control of the axial and radial clearances of the various components, particularly in a context of eccentric movement and unbalances which can cause accelerated fatigue of the torque transmission means (100).

[0041] To meet these objectives, the torque transmission means (100) is constituted by an assembly of two monobloc parts (110) and (150), presented separately in figures 2, 3 and 4. The first monobloc part (110) supports the rotor (220) of the electric motor (200) and the second monobloc part (150) drives the member (300).

[0042] The term “monobloc” means that each of the parts (110, 150) is manufactured without assembly, from a single material, for example by machining a raw part, by casting, and any other process avoiding assembly of separate components.

[0043] An important aspect of the invention concerns the coupling of these two parts (110, 150) which must make it possible to transmit a high torque between the motor (200) and the member (300), resist the stresses resulting from eccentric movements, while allowing uncoupling to facilitate assembly and allow disassembly.

[0044] The electric machine has a first casing (510) in which the motor is housed, and a second casing (520) in which the member to be driven (300) is housed, the two being joined by an intermediate casing (530) to form a sealed housing (500) closed by a cover (540). In the remainder of this description, the term "rear" will refer to the side closest to the motor (200) and "front" to the side closest to the member to be driven (300).

[0045] Details of the production of the first single-block part (110)

[0046] This first single-piece part (110) is intended to support the rotor (220) of the motor (200). For this purpose, it is constituted by a part having a cylindrical outer casing, with a plurality of stages of different diameters: a first cylindrical segment (111) supporting the rotor (220) of the electric motor (200) having an outer diameter D r. The length of this first cylindrical segment (111) corresponding to the axial length of the rotor (220). The rotor (220) is fitted on this first segment (111) in a known manner. a second cylindrical segment (112) supporting a rear bearing (240) having an outside diameter D b This rear bearing (240) ensures the guidance of the torque transmission means (100) relative to the housing (500) of the equipment.

[0047] These two cylindrical segments (111, 112) are coaxial.

[0048] The first cylindrical segment (111) supporting the rotor (220) of the electric motor is preceded by a cylindrical segment (116), whose external diameter D s is less than the outer diameter D r . It allows the positioning of an annular position sensor (260).

[0049] An intermediate segment (114) of diameter D m, located between the first cylindrical segment (111) and the second cylindrical segment (112), is intended to receive an asymmetrical balancing weight (124) compensating for the imbalance caused by the driven eccentric movement.

[0050] Optionally and as illustrated in figures 8a and 8b, the balancing weight (124) is integrated into the rotor sheet metal pack (220) carried by the first single-piece part (110), or else formed in a radial extension of the first single-piece part (110).

[0051] Preferably, but not limited to, the section of this intermediate segment (114) is greater than the section of the first cylindrical segment (111) and / or the section of the second cylindrical segment (112), in order to form shoulders against which the rotor (220) is respectively fitted and against which the rear bearing (240), mounted by sliding, bears axially.

[0052] Optionally, an elastic axial preload means (241), a spring washer for example, can be integrated between the rear bearing (240) and the shoulder of the intermediate cylindrical segment (114), in particular to guarantee an increased service life of the guide elements. Details of the installation of the built-in connection

[0053] This first part (110) has a hollow guide segment (115) for receiving a complementary male guide segment (155) of the second part (150) and forming an embedded connection having high axial, tangential and radial stiffness.

[0054] In the example described, it has a base (118) forming a front stop for said complementary male guide segment (155). This base (118) has a central bore (119) for passage by a screw (180) constituting a locking means (195) ensuring the connection and axial locking of the two single-piece parts (110, 150).

[0055] The first part (110) also has an anti-rotation means consisting, in the example described, of two flats (120, 121), complementary to two diametrically opposed flats (171), only one of which is visible, provided on the complementary male guide segment (155).

[0056] These flats are in the example described symmetrical with respect to an axial plane; they can advantageously be asymmetrical to allow only one single assembly possibility. It is also possible to provide on each part only one anti-rotation means, for example a single flat.

[0057] Alternatively and as illustrated in figures 9a and 9b, the anti-rotation of the two monobloc parts (110, 150) can be achieved by means of a groove (148) or spline (149) system located at the cavity (176) of the first monobloc part and the base (126) of the second monobloc part.

[0058] Alternatively and as illustrated in the anti-rotation of the two monobloc parts (110, 150) can be achieved by means of a key (147) carried by the cylindrical segment (155), this key collaborating with a counterbore (146) located on the cylindrical segment (115) for locking the first and second monobloc parts.

[0059] Alternatively and as illustrated in the, the anti-rotation of the two parts (110, 150) can be achieved by means of an elastic pin (145) radially passing through the first and second one-piece parts at the cavity (126) and the base (176).

[0060] An important consideration concerns the long centering of the two monobloc 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 monobloc part (110) has an internal diameter corresponding to the external diameter of the complementary male guide segment (155) of the second monobloc part (150), with, preferably, an adjustment of type H7g6, referring to the adjustment table proposed by the specifications of standard ISO 286-1 of April 15, 2010.

[0061] Alternatively, the fit can be tighter, of the H7m6 or H7p6 type with force fitting of the two parts (110, 150), disassembly remaining possible, for example with heating.

[0062] To obtain the long centering of the two single-piece parts (110, 150), the length ratio between the length L c and the diameter D cis greater than 1.5, and typically 2.L c corresponds to the tubular interaction length between the hollow guide segment (115) of the first monobloc part (110) and the complementary male guide segment (155) of the second monobloc part (150),D c corresponds to the inner diameter of the hollow guide segment (115) of the first monobloc part (110) and to the outer diameter of the complementary male guide segment (155) of the second monobloc part (150).

[0063] The hollow guide segment (115) of the first one-piece part (110) opens into an asymmetrical inlet cavity (126) having a section greater than the section of the hollow guide segment (115), with two peripheral flats (120, 121) connected by two semi-tubular segments. The complementary male guide segment (155) of the second one-piece part (150) has, at the rear of the complementary male guide segment (155) of the second one-piece part (150), an asymmetrical base (176) of cross-section and axial length complementary to the section of this asymmetrical inlet cavity (126).

[0064] Details of the second monobloc part (150)

[0065] This second single-piece part (150) is intended to drive the member (300) arranged in the housing (500). For this purpose, it is constituted by a part having a cylindrical outer casing, with a plurality of stages of different diameters: a cylindrical segment (151) supporting a front bearing (245) having an outer diameter D a , coaxial with the segments (111, 112) of the first one-piece part (110). The front bearing (245) is force-fitted onto this cylindrical segment (151) on the one hand, and onto the through passage of the wall (531) of the intermediate casing (530) on the other hand. a cylindrical drive segment (152), eccentric with respect to the longitudinal axis (102), having an outside diameter D e ,a disc shoulder (163) forming an axial stop for the positioning of the front bearing (245).

[0066] The rear face of the disc shoulder (163) defines a cylindrical surface (153) cooperating with a seal (532) for passing through the wall (531) of the intermediate casing (530). This disc shoulder (163) is extended rearwardly, in the direction of the engine, by the base (156) and the complementary male guide segment (155).

[0067] The complementary male guide segment (155) is full, at least partially. Full means that the segment (155) is not open.

[0068] The front end (157) of the complementary male guide segment (155) having a hole having an axial thread (158) for locking by the aforementioned screw (180) constituting a locking means (195) ensuring the connection and axial locking of the two parts (110, 150).

[0069] Alternatively and as illustrated in the, the axial locking of the two monobloc parts (110, 150) can be achieved by means of a threaded bearing surface (144) located at the end of the cylindrical segment (155), this threaded bearing surface axially passing through the intermediate cylindrical segment (114) of the first monobloc part (110), this threaded bearing surface (144) collaborating with a nut (143) for locking the first and second monobloc parts.

[0070] Alternatively and as illustrated in the, the axial locking of the two parts (110, 150) can be achieved by means of a smooth bearing surface (142) located at the end of the cylindrical segment (155), this smooth bearing surface axially passing through the intermediate cylindrical segment (114) of the first monobloc part (110), this smooth bearing surface being equipped with a groove capable of receiving a stop ring (or circlip) (141) for locking the first and second monobloc parts.

[0071] Advantageously, in particular to further reduce manufacturing costs, the axial locking and anti-rotation of the first and second monobloc parts can be achieved, as illustrated in the, by a single, specific screw (180). The friction between the threads of the screw and the tapping of the threaded hole of the segment (155) of the second monobloc part (150) on the one hand, and between the screw head and the front face (113) of the passage (119) of the first monobloc part (110) on the other hand, allows the transmission of the torque to serve the anti-rotation function.

[0072] The second single-piece part (150) may be partially hollow, except for a transverse partition (162) guaranteeing sealing, in collaboration with the seal (532), in order to lighten the assembly.

[0073] According to an advantageous embodiment, the second single-piece part (150) has three hollow sections of decreasing diameter from front to rear, with a wall having an optimized thickness to reconcile the lightening of the part and the mechanical resistance in torsion and axial deformation.

[0074] An intermediate segment (154) of diameter D M , located between the cylindrical segment (151) carrying the front bearing (245) and the eccentric cylindrical segment (152), is intended to receive an asymmetrical balancing weight (174) compensating for the imbalance caused by the driven eccentric movement, this weight (174) collaborating with the weight (124) of the first single-piece part (110). For this purpose, said balancing weight (174) has a protrusion (177) extending over an angular sector of external radius R M and whose center is located on the axis (102).

[0075] The anti-rotation means, in particular, in the example described, the flats (120, 121, 171) ensure the angular indexing of the balancing weights (124, 174) according to an angular reference, common with the angular reference of the driven eccentric member (300). For this purpose, the intermediate cylindrical segment (114) of the first single-piece part (110) comprises a flat collaborating with a corresponding flat (125) of the weight (124) for its angular indexing relative to the flats (120, 121). For this purpose, the cylindrical segment (151) comprises an indexing pin (159) collaborating with an oblong hole (175) of the weight (174) for its angular indexing relative to the flats (171), only one of these flats being visible in.

[0076] The segment (152) is off-center and concentric with an eccentric axis (101), said eccentric axis (101) being offset transversely with respect to the longitudinal axis (102) by a distance d exand cooperates with the eccentrically moving part of the driven member (300), for example the member of a vane pump or a scroll-type volute pump. Details of the case construction (500)

[0077] The housing (500) is formed by the assembly of the first casing (510) in which the electric motor (200) is housed, an intermediate casing (530) and a second casing (520) in which the member (300) to be driven is housed.

[0078] The assembly forms a sealed housing (500) with a wall (531) fluidly isolating the electric motor (200) from the member (300) to be driven, using the seal (532) and the transverse partition (162), the dynamic seal (532) collaborating with the cylindrical segment (153) of the second non-opening monobloc part (150). Only two bearings (240, 245) ensure the guidance of the torque transmission means (100) relative to the housing (500), the rear bearing (240) being mounted in the cover (540) of the first casing (510) and on the segment (112) of the first monobloc part (110) the front bearing (245) being mounted in the wall (531) of the intermediate casing (530) and on the segment (151) of the second monobloc part (150).

[0079] The embedded connection formed by the tubular interaction zone between the hollow guide segment (115) of the first monobloc part (110) and the complementary male guide segment (155) of the second monobloc part (150) is imperatively located between the rear bearing (240) and the front bearing (245).

[0080] By providing only two guide bearings despite the use of a torque transmission means (100) in two parts (110, 150), robust, economical and isostatic guidance is ensured, limiting the risk of high stresses.

[0081] The intermediate casing (530) has a series of fixing means, or several series of fixing means allowing for a variety of usage contexts. This intermediate part is close to the center of gravity of the equipment: it can also be provided with a lifting socket, for handling the entire compressor, for example a lifting eyelet (538).

[0082] It should be noted that the first casing (510) receiving the electric motor (200) may be made up of an assembly of several parts. For example, the motor sleeve (515) may be assembled to the interface part (516), receiving the electronic card (250), to form the first casing. This means of production is particularly advantageous for reducing manufacturing costs when multiple lengths of electric motors (200) are envisaged to meet different specifications while retaining the majority of the system components.

[0083] Details of the electrical card (250)

[0084] The electric motor (200) is constituted in a known manner by a rotor (220) and a wound stator (210), controlled by an electronic card (250) arranged transversely between the wall (531) and the rotor (210), protected in a sealed manner behind the seal (532). The electronic card (250) is pierced by a cutout (251) of a diameter greater than those of the segments (111, 116, 155, 176) which pass through it during assembly or disassembly.

[0085] To ensure the cooling of the components of the electronic card (250), it is advantageous to ensure thermal coupling with the first casing (510), in particular when the casing (510) is connected to a circuit for circulating a cooling fluid.

[0086] The sensor (260) mounted on the segment (116) of the first single-piece part (110) passing through the electronic card (250) is arranged axially opposite the electronic card (250), so as to allow electromagnetic or possibly optical interaction with a probe arranged on the card (250). Alternatively to a permanent magnet solution, the sensor (260) may be an inductive or variable reluctance sensor without a magnet produced by the cooperation of a ferromagnetic target (261), mounted on the additional cylindrical segment (116) of the first single-piece part (110), with a probe of the electronic card, as shown in the.

Claims

Motorized equipment comprising a member (300) performing an eccentric movement coupled to an electric motor (200) characterized in that said eccentric member (300) is driven by said electric motor (200) by a torque transmission means (100) consisting of two tubular monobloc parts (110, 150) coupled by an embedded connection, the first monobloc part (110) having a first cylindrical segment (111) supporting the rotor (220) of the electric motor (200) having an external diameter D r , a second cylindrical segment (112) supporting a rear bearing (240) having an outside diameter D b , said segments (111, 112) being coaxial with a first longitudinal axis (102), the second single-piece part (150) having a cylindrical segment (151) supporting a front bearing (245) having an outside diameter D acoaxial with said first longitudinal axis (102), a cylindrical drive segment (152), eccentric with respect to said longitudinal axis (102), having an external diameter D e , said two single-piece parts (110, 150) being coupled by an embedded connection constituted by: a male guide segment (155) of external diameter D c and length L cprolongeant l’une desdites parties monoblocs (110, 150), engagé dans un segment de guidage femelle creux (115) de profondeur Lcprévu dans l’autre desdites parties, avec Lcsupérieur ou égal à 1,5 fois Dc, said two single-piece parts (110, 150) further comprising at least one angular (190) and axial (195) locking means. Motorized equipment according to claim 1 characterized in that said first single-piece part (110) further has an additional cylindrical segment (116) supporting a sensor (260) having an external diameter D s coaxial with the longitudinal axis (102). Motorized equipment according to claim 1 or 2 characterized in that said first one-piece part (110) further has an additional cylindrical segment (114) supporting a rear balancing weight (124) having an external diameter D m coaxial with the longitudinal axis (102). Motorized equipment according to claim 1 or 2 characterized in that said first monobloc part (110) further has an annular shoulder adjacent to said cylindrical segment (111) supporting the rotor (220) of the electric motor (200), for the axial positioning of said rotor (220). Motorized equipment according to any one of claims 1 to 3 characterized in that said second part (150) further has an additional cylindrical segment (154) supporting a front balancing weight (174) having an external diameter D Msaid additional segment (154) being coaxial with the eccentric axis (101) when said two parts (110, 150) are coupled, said balancing weight (174) having a protrusion (177) extending over an angular sector of external radius R M and centered on the longitudinal axis (102). Motorized equipment according to claim 1 characterized in that said second part (150) further has an additional cylindrical segment (153) corresponding to the passage of the wall (531) separating the motor (200) from said driven member (300) and in that a seal (532) collaborates with the cylindrical segment (153) and the wall (531). Motorized equipment according to claim 1 characterized in that said motor (200) comprises a printed circuit (250) arranged transversely between the rotor (220) and said second bearing (245), said printed circuit (250) having a passage (251) crossed by said torque transmission means (100). Motorized equipment according to claim 7 characterized in that the segment(s) (155) passing through said passage (251) of said printed circuit (250) have the smallest diameters. Motorized equipment according to claim 2 and the preceding claim characterized in that said segment (116) carrying the sensor (260) is the segment closest to said printed circuit (250). Motorized equipment according to claim 1 characterized in that at least one of said first and second single-piece parts (110, 150) is hollow, except for a transverse partition (162), to ensure sealing. Motorized equipment according to claim 1 characterized in that said angular locking means (190) is constituted by cooperation of flats (120, 121, 171) for transmitting the torque. Motorized equipment according to claim 1 characterized in that said axial locking means (195) is constituted by an axial screw (180) connecting said male guide segment (155) and said female guide segment (115), the axial end (157) of said male guide segment (155) having an axial thread (158) and the bottom (118) of said female guide segment (115) having a bore for the passage of said screw (180) ensuring the locking of the axial end (157) of said male guide segment (155) against the bottom (118) of said female guide segment (115). Motorized equipment according to the preceding claim, characterized in that it comprises an intermediate casing (530) having at least two fixing means (535, 536). Motorized equipment according to claim 1 characterized in that said intermediate casing (530) comprises at least one lifting eyelet (538).

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