End shield and rotor for a rotary electric machine

Abstract

The invention relates to an end shield (10) for a rotor (3) of a rotary electric machine (1) rotating about an axis of rotation (X), comprising an inner face (101) facing a rotor mass (30), an outer face (102) opposite the inner face (101), a radially outer edge face (103) extending between the inner face (101) and the outer face (102), the end shield (10) comprising one or more supply ducts (12) for a cooling fluid, at least one supply duct (12) successively comprising: - a collection zone (12a) on the inner face (101) of the end shield; - a first narrowing (13a) of a cross section of the supply duct; - an intake chamber (12c); - a second narrowing (13b) of the cross section of the supply duct; - an end portion (12b), in particular flared, in particular located on the edge face and / or on the outer face of the end shield, the second narrowing (13b) extending in particular along a substantially oblique elongation axis (Y).

Description

[0001] Description

[0002] Title: Flange and rotor of a rotating electrical machine

[0003] The present invention claims priority from French application 2414733 filed on December 19, 2024, the content of which (text, drawings and claims) is incorporated herein by reference.

[0004] technical field

[0005] The present invention relates to rotating electrical machines, and more particularly to those cooled by the circulation of a cooling fluid, notably a coolant such as oil, circulating at least partially within a rotor of the machine and, where applicable, within a shaft of the machine and / or within a rotor lamination pack of the rotor. The invention relates more particularly to the rotors of such machines, and even more specifically to the flanges.

[0006] The invention relates to synchronous or asynchronous machines, operating on alternating current. It relates in particular to traction or propulsion machines for electric (Battery Electric Vehicle) and / or hybrid (Hybrid Electric Vehicle - Plug-in Hybrid Electric Vehicle) motor vehicles, such as passenger cars, vans, trucks, or buses. The invention also applies to rotating electrical machines for industrial and / or power generation applications, particularly in the marine, aeronautical, or wind power sectors.

[0007] Previous technique

[0008] It is known to cool the hot spots of a rotating electrical machine, particularly the stator coil heads, by means of a cooling fluid ejected by the rotor onto them during machine operation. Flanges are arranged at the ends of the rotor mass, and the cooling fluid is ejected through channels formed in these flanges.

[0009] In applications US 2023 / 361640 and US 2023 / 299642, the conduits formed in the flanges have a single restriction and an outlet parallel to the rotor's axis of rotation. In applications EP 4 246 775, CN 115347729, FR 3 116 964, EP 4 395 134, US 2022 / 376587, US 2013 / 334912, US 2023 / 179065, CN 219247566 U, CN 204906112 U, EP 4 327 437, and JP 2012075244, there is also a single restriction at most in the flange, or even no restriction at all. Most often, there is no angled outlet. In JP 2010 / 239799, CN 206922591 U and CN 216121979 U, the outputs are perpendicular to the rotor's axis of rotation. In EP 4 391 313, US 5 889 342 and US 2021 / 281134, the outputs are parallel to the rotor's axis of rotation.

[0010] There is a need to simplify the manufacturing of rotating electrical machine flanges. There is also a need to further improve the cooling of rotating electrical machines cooled by circulating cooling fluid.

[0011] Description of the invention

[0012] The invention aims to meet all or part of these needs and achieves this, according to one of its aspects, by means of a rotor flange for an electric machine rotating about an axis of rotation X, comprising an inner face facing a rotor mass, an outer face opposite the inner face, a radially outer edge extending between the inner and outer faces, the flange comprising one or more supply channels for a cooling fluid, at least one supply channel comprising successively:

[0013] - a collection area on the inner face of the flask,

[0014] - an initial narrowing of a cross-section of the supply duct,

[0015] - an admission room,

[0016] - a second narrowing of the cross-section of the supply duct.

[0017] The flange may also include a flared terminal portion, particularly located on the edge and / or on the outer face of the flange.

[0018] The second narrowing can extend along an elongation axis Y substantially oblique to a plane perpendicular to the rotation axis X.

[0019] The flange according to the invention allows for the creation of shapes for channeling the cooling fluid, enabling the creation of several possible cooling circuits and directing the fluid towards the stator coil heads and a phase connector of the machine, thus improving heat dissipation. The flange according to the invention has the advantage of allowing the cooling of the hottest areas of the electric machine, for example, the stator coil heads and the phase connector, in order to extract the dissipated heat. The first and / or second constriction limits the flow rate of the cooling fluid, thereby promoting its even distribution within the rotor and on either side of it. This is particularly useful when the cooling fluid is supplied by a central, or even a single, power source.This method allows for improved cooling of the machine's electrical conductors, thanks to a good distribution of the cooling fluid over each conductor. Even with a low flow rate of cooling fluid, a very even distribution of the cooling fluid can be achieved around the rotor's axis of rotation across all the machine's electrical conductors.

[0020] The flange may also include a central bore.

[0021] A flange according to the invention does not have a complex shape, such as hidden cavities. Only simple shapes, such as grooves, holes, or chamfers, are used. Therefore, to manufacture a flange according to the invention, it is not necessary to perform sand casting or use intermediate parts, such as plugs, during the casting process.

[0022] The flange may have cavities that are fully visible from the outside. This improves fluid circulation in the pipes.

[0023] The flange can be a cast part, notably made of aluminum or aluminum alloy, particularly by die casting. The geometry of the flange according to the invention allows for very simple manufacturing without further machining or drilling, or with possible machining and drilling, but these are easy to perform. The flange can be made as a single piece.

[0024] Materials other than aluminum can be used.

[0025] Alternatively, the flange can be machined. Alternatively, it can be manufactured through a combination of machining and casting steps.

[0026] The flange according to the invention therefore has the advantage of being able to be manufactured more simply and less expensively than the flanges of the prior art.

[0027] Such a flange allows for efficient cooling of the electrical machine, and in particular of certain hot spots such as the stator coil heads. Specifically, the flared end of the supply conduit on the flange directs the cooling fluid as close as possible to the stator coil heads. The cooling fluid can be a liquid, such as water or oil. Alternatively, the cooling fluid can be a gas, such as air.

[0028] Summary of the invention

[0029] Supply pipes

[0030] The supply ducts can be oriented radially.

[0031] The flange may have a single supply channel, or between 1 and 8 supply channels, for example 2, 4, 6 or 8, or even between 1 and 6 supply channels, or even between 2 and 4, for example 2, 3 or 4 supply channels. In one embodiment, the flange has 3 supply channels.

[0032] The flange can, for example, have an even number of feed leads, or alternatively, an odd number. The feed leads of a flange can, for example, be evenly distributed around the flange, for instance, at 180° when the flange has two leads, at 120° when the flange has three leads, and at 90° when the flange has four leads. The number of feed leads can depend on the number of rotor poles. For example, if the rotor has N poles, each flange can have N / 2 feed leads. Such a relationship between the number of rotor poles and the number of feed leads of a flange ensures the symmetry of the electric machine.

[0033] The flange according to the invention can, for example, be used for a 4, 6, or 8-pole machine. The flange can then have 2, 3, or 4 supply conduits, respectively. This flexibility of use optimizes the application of the same flange across a wide range of electrical machines, simplifying manufacturing and maintenance processes while reducing inventory management costs.

[0034] By "cross-section of the supply duct", we mean a section taken in the plane perpendicular to the direction of flow of the cooling fluid in the supply duct.

[0035] At least one, or even all, of the supply lines can be supplied with cooling fluid from a channel formed in a rotor lamination stack, in a rotor shaft, or between the rotor lamination stack and the shaft. In one embodiment, at least one, or even all, of the supply lines can be supplied with cooling fluid from a channel formed in a rotor lamination stack. Such a cooling fluid supply simplifies the design of the cooling circuit because fewer components need to be traversed by the fluid. As the circuit is thus shorter, its dimensioning is simplified.

[0036] The supply line(s) can be supplied with coolant via the shaft only. Alternatively, the supply lines can be supplied with coolant from the rotor lamination pack only.

[0037] The supply conduit(s) can be oriented radially.

[0038] The supply duct(s) may extend along an elongation direction comprising a first portion perpendicular to the axis of rotation X and a second portion inclined with respect to a plane perpendicular to the axis of rotation X. The second portion of the elongation direction may extend along a substantially straight elongation axis Y. The elongation axis Y is oblique. A "substantially straight elongation axis" is defined as an axis without curvature or bend, particularly a bend at a substantially right angle.

[0039] A length D of the feed channel is measured along its elongation direction between the periphery of the central bore of the flange and the flared end portion. The length D of the feed channel can be between 20 mm and 100 mm, preferably between 25 mm and 80 mm, for example, approximately 33 mm. Such a length simplifies the manufacturing of the feed channel.

[0040] The angle defined between the elongation axis Y and a plane perpendicular to the X axis of rotation of the machine can be between 0° and 90°, preferably between 5° and 80°, better between 10° and 70°, being for example on the order of 45°.

[0041] The angle can be chosen so that the cooling fluid is projected onto a particular area of ​​the electrical machine such as the casing, phase connectors or stator coil heads.

[0042] The feed channel(s) may be formed at least partially as a recess on one face of the flange facing the rotor mass. The feed channel(s) may also be formed at least partially within the thickness of the flange.

[0043] Flared terminal portion

[0044] The supply line(s) may terminate in flared end sections located at the periphery of the flange, through which the cooling fluid is projected onto a stator of the machine. Each supply line may terminate in a flared end section. The flared end section(s) may be oriented radially outwards.

[0045] The flared terminal portion(s) can increase the wetted surface area, cool the coil heads well and reduce the mass of the flange.

[0046] The flared end portion may be located on the edge and / or on the outer face of the flange. The flared end portion may not be located solely on the edge.

[0047] The flared end portion can be located after the second constriction, when moving in the direction of coolant flow. The flared end portion can be closer to the flange face than to the center bore of the flange. The collection area can be closer to the X-axis of rotation than the flared end portion. The flared end portion of the supply line can be located closer to the flange face than to the X-axis of rotation of the machine. The flared end portion of the supply line can be positioned between the flange face and the X-axis of rotation of the electric machine, in the first half from the face, preferably in the first third, preferably in the first quarter, or even in the first fifth from the face.The flared end portion of the conduit can be positioned between the flange edge and the periphery of the central bore of the flange, in the second half from the central bore, preferably in the last third, preferably in the last quarter, or even in the last fifth from the central bore. The flared end portion of the conduit can be positioned between the flange edge and the X-axis of rotation of the electrical machine in the second half from the X-axis, preferably in the last third, preferably in the last quarter, or even in the last fifth from the X-axis.

[0048] In one embodiment, the flared terminal portion of the supply conduit can be positioned on the edge of the flange. It may then not open onto the outer face of the flange.

[0049] In another embodiment, the flared terminal portion of the supply conduit can be disposed in a junction zone between the outer face and the edge of the flange.

[0050] The junction zone between the flange edge and the outer face can be a curved surface. When the flange is viewed in a cross-section containing the X-axis of rotation of the electrical machine, the junction zone can form an arc of a circle, for example a quarter circle.

[0051] Alternatively, the junction zone between the flange edge and the outer face can be an edge. The edge can be curved, particularly circular, when viewed along the rotor's axis of rotation.

[0052] The supply conduit(s) may terminate opposite the stator coil heads. The stator coil heads are the parts of the stator's electrical conductors that protrude from the stator core.

[0053] This duct arrangement prevents the ejection of cooling fluid into the machine's air gap, thus minimizing fluid entry into the gap. The presence of fluid in the air gap can increase torque loss due to drag. This design also prevents uncontrolled fluid leaks into the rotor.

[0054] The flared terminal portion can have an axial opening angle which can, for example, be between 0° and 40°, better between 0° and 10°, being for example on the order of 5°.

[0055] The flared terminal portion forms a flare angle P in a plane perpendicular to the axis of rotation X, that is to say a radial opening angle, the flare angle P being notably between 0° and 60°, better between 0° and 15°, being for example of the order of 10°.

[0056] The flared terminal portion may include a bottom wall extending parallel to a plane perpendicular to the axis of rotation X or with a slight angle ô relative to a plane perpendicular to the axis of rotation of the rotor, the angle ô being in particular between 2° and 30°, better between 10° and 20°, being in particular of the order of 15°.

[0057] The flared terminal portion may include a wall closest to the axis of rotation X which is inclined at an angle y with respect to the axis of rotation of the rotor, the angle y being in particular between 2° and 30°, better between 10° and 20°, being in particular of the order of 15°.

[0058] The flange can have a thickness that can be between 6 and 20 mm, or even between 10 mm and 15 mm, being for example around 12 mm.

[0059] Constrictions By "constriction", we mean that the cross-section of the supply conduit decreases and then increases as we move away from the axis of rotation X.

[0060] The first constriction can be formed, at least partially, as a recess in the thickness of the flange. The first constriction can be formed, at least partially, as a recess on a face of the flange facing the rotor mass.

[0061] Alternatively, the first constriction may include a 360° channel segment within the flange. The first constriction may, in particular, be cylindrical in shape.

[0062] The cross-sectional area of ​​the first constriction can be between 0.06 mm 2 and 18 mm 2 , or even between 0.8 mm 2 and 3 mm 2 , for example, being on the order of 1 mm 2 .

[0063] The width of the first narrowing can be between 0.5 mm and 6 mm, or even between 0.8 mm and 3 mm, being for example on the order of 1 mm.

[0064] The length of the first narrowing can be between 0.2 mm and 3 mm, or even between 0.2 mm and 1 mm, for example being around 0.3 mm.

[0065] The first constriction can allow control of the fluid output flow, but without creating a direct outlet so as not to damage the coil heads.

[0066] The second constriction may be formed at least partially within the thickness of the flange. This second constriction may include a 360° channel section within the flange. The second constriction may also be cylindrical in shape.

[0067] The cross-sectional area of ​​the second constriction can be between 0.3 mm 2 and 30 mm 2 , ideally between 0.8 mm2 and 7 mm 2 for example, being on the order of 5 mm 2 .

[0068] The diameter of the second constriction can be between 0.6 mm and 6 mm, or even between 1 mm and 3 mm, for example being around 2.5 mm.

[0069] The length of the second narrowing can be between 1 mm and 20 mm, or even between 2 mm and 10 mm, for example being around 5.5 mm.

[0070] The second constriction can be used to direct the fluid towards the coil heads. The choice of diameters for the first and second constrictions allows for variation in the cooling fluid flow rate by adjusting the diameters and shapes of the constrictions.

[0071] The first constriction may be located in the first half of the supply channel, when moving in the direction of the flow of the cooling fluid.

[0072] The second constriction may be located in the second half of the supply channel, when moving in the direction of the flow of the cooling fluid.

[0073] The second narrowing can extend along an elongation axis Y inclined at an angle α with respect to a plane perpendicular to the rotation axis X. The angle α can for example be between 0° and 90°, better between 40° and 60°, or even between 42° and 55°, better between 44° and 50°, being for example on the order of 45°.

[0074] All second constrictions can extend along an elongation axis Y inclined at the same angle α.

[0075] In one embodiment, the flange may include several second constrictions, each extending along elongation axes Y inclined at a different angle with respect to a plane perpendicular to rotation axis X.

[0076] When the angles of the Y elongation axes are different, the volumes of the flared parts can be different in order to balance the flange, particularly in mass.

[0077] In one embodiment, the flange may, for example, include three supply channels, with three secondary constrictions inclined at angles a1, a2, and a3 respectively to a plane perpendicular to the rotation axis X. The angles a1, a2, and a3 may be different. A first angle a1 may, for example, be between 40° and 50°, or even between 42° and 48°, preferably between 44° and 46°, being, for example, approximately 45°. A second angle a2 may, for example, be between 0° and 40°, or even between 10° and 37°, preferably between 20° and 35°, being, for example, approximately 30°. A third angle a3 may, for example, be between 50° and 90°, or even between 53° and 80°, preferably between 56° and 70°, being, for example, approximately 60°.

[0078] The cooling fluid flowing from the flange through the first conduit at an angle of inclination a1 can, for example, provide more targeted cooling for the central part of the coil heads. The cooling fluid flowing from the flange through the second conduit at an angle of inclination a2 can, for example, provide more targeted cooling for the part of the coil heads closest to the stator, particularly near the stator laminations and stator slots. The cooling fluid flowing from the flange through the third conduit at an angle of inclination a3 can, for example, provide more targeted cooling for the ends of the coil heads, the winding interconnections (also called belts), and the phase connector.

[0079] The invention offers great flexibility in choosing the direction of the cooling fluid flow, allowing for easy targeting of different areas of the machine for cooling. Fluid distribution can thus be uniform throughout the cooling circuit, including in the collection zone and the intake chamber. This results in a homogeneous distribution of the cooling fluid mass and minimizes the impact on the dynamic balance of the rotor. The invention ensures uniform distribution, increases the wetted surface area, and thereby enhances heat transfer.

[0080] Admissions room

[0081] The intake duct(s) may each include an intake chamber. The intake chamber(s) may be formed at least partially as a recess on one face of the flange facing the rotor mass. The intake chamber(s) may be formed as a recess within the thickness of the flange, for example, in a trapezoidal shape.

[0082] The intake chamber(s) can channel the cooling fluid, create a fluid mist and prevent the fluid from flowing towards the air gap.

[0083] The intake chamber(s) can be configured to face rotor mass housings, for example, rotor housings containing permanent magnets. This allows the cooling fluid to come into contact with the permanent magnets, thus promoting their cooling.

[0084] The volume of an intake chamber can be between 50 mm3 and 700 mm 3 , or even between 100 mm 3 and 400 mm 3 , for example, being on the order of 206 mm 3 The depth of an intake chamber can be between 1 mm and 10 mm, preferably between 2 mm and 8 mm, with 5 mm being an example.

[0085] Collection area

[0086] The supply duct(s) may each include a collection zone. The collection zone(s) may be formed at least partially as a recess on one face of the flange facing the rotor mass. The collection zone(s) may also be formed as a recess within the thickness of the flange, for example, in a trapezoidal shape.

[0087] The volume of the collection zone can be less than or equal to the volume of the inlet chamber. The volume of fluid in the collection zone and in the inlet chamber can be proportional to the volume or cross-sectional area of ​​the constriction following it, in the direction of fluid flow. In other words, the volume of the collection zone can be proportional to the volume or cross-sectional area of ​​the first constriction, and the volume of the inlet chamber can be proportional to the volume or cross-sectional area of ​​the second constriction.

[0088] The volume of a collection zone can be between 50 and 600 mm³ 3 , or even between 100 and 300 mm 3 , for example, being on the order of 165 mm 3 .

[0089] The depth of a collection zone can be between 0.5 mm and 5 mm, better between 1.5 mm and 3 mm, being for example around 1.72 mm.

[0090] The collection zone(s) can be positioned closer to the flange edge than to the X-axis of rotation of the machine. The collection zone(s) can also be positioned between the flange edge and the X-axis of rotation of the electric machine, in the first half from the edge, preferably in the first third from the edge, or alternatively in the second third from the edge. The collection zone(s) can also be positioned between the flange edge and the periphery of the flange's center bore, in the second or third quarter from the center bore, or even in the second or third third from the center bore. Such an arrangement simplifies machining because the depth is reduced compared to a longer, angled outlet across the entire diameter of the flange.

[0091] The collection zone(s) can be configured to face rotor mass housings, including rotor housings without permanent magnets. The collection zones may not be interconnected; for example, each feed duct may have a flared collection zone. In the case of a flared collection zone, the area of ​​the flared collection zone, measured in a plane perpendicular to the rotor's axis of rotation, can be between 10 mm 2 and 50 mm 2 , ideally between 20 mm 2 and 40 mm 2 , for example, being on the order of 30 mm 2 .

[0092] Alternatively, the collection zones can be connected at an inner radial end by an annular bore. This annular bore reduces the number of outlets while ensuring efficient coolant delivery at the shaft-rotor mass interface, as well as to the trapezoidal recesses in the rotor mass, directing the coolant towards the coil heads. In the case of an annular bore, the difference between its inner and outer diameters can be between 1 mm and 6 mm, preferably between 2 mm and 5 mm, with a difference of approximately 3.5 mm.

[0093] The annular opening or the flared inlet portion(s) can be used to collect the cooling fluid from the rotor and distribute it to the various supply channels of the flange. This configuration promotes even distribution.

[0094] The annular recess may be delimited at least partially by the shaft. The annular recess may be delimited at least partially by the rotor mass. The annular recess may be delimited at least partially by the flange. In a preferred embodiment, the annular recess may be delimited by both the rotor mass and the flange.

[0095] When observing the flange along the axis of rotation of the electrical machine, the annular recess can be located between the shaft and the first constriction of the feed conduit.

[0096] The ratio between the volume of the collection zone and the volume of the first constriction can be between 20 and 500, or even between 60 and 250, for example, 103. The volume of the first constriction can be between 0.1 mm 3 and 30 mm 3 , or even between 1.3 mm 3 and 5 mm 3 , for example, being on the order of 1.6 mm 3 .

[0097] The ratio between the volume of the intake chamber and the volume of the second constriction can be between 1.2 and 180, or even between 3 and 13, for example, 8. The volume of the second constriction can be between 0.3 mm 3 and 565 mm 3 , or even between 8 mm 3 and 150 mm 3 , for example, being on the order of 27 mm 3 .

[0098] A ratio between the area of ​​a cross-section of the first constriction and the area of ​​a cross-section of the second constriction can be between 0.02 and 1, or even between 0.03 and 0.5, or even between 0.05 and 0.12, being for example 0.07.

[0099] The flange may contain multiple cavities, including non-through cavities. Non-through cavities can guide the fluid within the rotor. They also help reduce the flange's mass.

[0100] The flange may also feature ribs on either side of the cavities, which can increase its rigidity and allow it to withstand harsh operating conditions. These ribs can be oriented at various angles and positions to create ventilation that promotes stator cooling. Furthermore, the cavities between the ribs help reduce the flange's weight and mass.

[0101] The flange may have one or more indexing notches. These notches may be located on the edge of the flange, particularly near the flared end sections. The indexing notches allow the flange(s) to be angularly indexed to the rotor mass, thus ensuring proper alignment of the rotor mass with the flange's shape.

[0102] Rotor

[0103] The invention also relates, according to another aspect, to a rotating electrical machine rotor, comprising a rotor mass and at least one flange as defined above. The flange may be disposed at one end of the rotor mass.

[0104] The rotor mass may consist of a stack of rotor laminations.

[0105] In one embodiment, the invention relates to a rotor comprising a rotor mass and two flanges as defined above, each disposed at one end of the rotor mass. The two flanges may be identical to each other, which simplifies their manufacture.

[0106] In one embodiment, the flanges can be arranged symmetrically with respect to each other on either side of the rotor mass.

[0107] In one embodiment, the flanges can be arranged with an angular offset from each other on either side of the rotor mass. At least one axial distribution channel for the cooling fluid to the flange(s) can be formed in the rotor mass and / or between the rotor mass and the shaft, along the shaft. This axial distribution channel(s) can pass axially through at least a portion of the rotor mass.

[0108] The distribution channel between the shaft and the rotor mass limits the impact of mechanical stresses due to the thermal gradient on torque transmission at high speeds. This reduces manufacturing tolerances and shrink-fit requirements at the shaft-rotor mass interface.

[0109] Alternatively, the shaft can be traversed along its entire length by an internal channel for supplying the cooling fluid. This channel can extend axially. This internal channel can supply radial channels, for example, radial channels located at the rotor ends. The radial channels can thus supply the rotor flanges with cooling fluid.

[0110] Each feed duct and / or annular recess and / or feed duct collection area(s) may face at least one axial rotor mass distribution channel or a radial channel located at the end of the rotor.

[0111] The rotor may include at least a first and a second circulation of cooling fluid in the rotor mass, the first and second circulations being parallel to the axis of rotation of the rotor and in opposite directions.

[0112] A first circulation can be located between the shaft and the rotor mass. A second circulation can be located within the rotor mass. The second circulation can be provided in housings devoid of permanent magnets, and / or in housings of the rotor's permanent magnets.

[0113] The rotor optimizes the cooling performance of critical machine components by channeling the cooling fluid to recesses in the rotor mass and magnet housings, thereby optimizing magnet cooling through thermal conduction and convection. This magnet cooling ensures efficient heat dissipation at critical points in the rotor. The invention also allows for a wider range of magnets to be used and a reduction in their cost, facilitating the use of magnets without heavy rare earth elements, for example.

[0114] We will now describe an example of a complete cooling circuit. The cooling circuit is supplied with coolant from the shaft nose, on the side of a female spline. This coolant can originate from the male drive shaft on the reduction side of the electric machine. At mid-shaft length, the coolant flows radially through six shaft holes. It then enters six cavities formed on the inner diameter of the rotor. This creates a large heat exchange surface between the coolant and the rotor. The coolant continues its axial path between the shaft and the rotor to the rotor ends.Once the coolant reaches the ends of the interface between the shaft and the rotor mass, it makes a U-turn upon contact with the flange to pass through axial channels machined into the rotor mass, which are trapezoidal in shape in this example. The coolant is then collected by the two flanges, creating a targeted jet that directs the coolant as close as possible to the engine's hot spots, such as the coil heads and the phase connector.

[0115] The flange configuration allows for one or more coolant outlets with varying opening angles, optimized to cover the entire surface of the coil heads and the phase connector. This configuration features a closed outlet on the air gap side between the rotor and stator, with angled outlets that limit the presence of coolant in the air gap, thus reducing torque losses due to drag.

[0116] The rotor may include permanent magnets embedded within the rotor mass. It may also include permanent magnets, such as surface or embedded magnets. The rotor may be a flux-concentrating type. It may have one or more rows of magnets arranged in an I, U, or V configuration, for example, two or three rows.

[0117] Permanent magnets can be made without heavy rare earth elements, which is less expensive. They can also have lower thermal resistance, made possible by improved cooling.

[0118] The rotor mass can consist of a stack of laminations. The housings for the permanent magnets can be made entirely by cutting out of the laminations. Each lamination in the stack can be a single piece.

[0119] The cooling fluid can flow axially into the permanent magnet housings and reach the flanges, for example, into the housings of the row closest to the air gap, such as in a V-shaped arrangement. Alternatively, the cooling fluid can flow axially into rotor housings without permanent magnets. For example, the rotor mass may have, for one pole, a first row of housings with at least three housings arranged in a U-shape, with at least one central housing and two lateral housings, the central housing of the first row being without a permanent magnet. The cooling fluid can flow into the central rotor housings before reaching the flanges. The central housings may be trapezoidal in shape.

[0120] Alternatively, it could be a wound or squirrel-cage rotor, or a variable reluctance rotor.

[0121] The number of poles P in the rotor is for example between 4 and 48, being for example 4, 6, 8, 10 or 12.

[0122] The rotor diameter can be less than 400 mm, preferably less than 300 mm, and greater than 50 mm, preferably greater than 70 mm, being for example between 100 and 200 mm.

[0123] Each sheet is, for example, cut from a sheet of magnetic steel or steel containing magnetic steel, such as steel 0.1 to 1.5 mm thick. The sheets can be coated with an electrically insulating varnish on their opposite faces before being assembled in the stack. Electrical insulation can also be achieved by heat-treating the sheets, if necessary.

[0124] The shaft can be made of a magnetic material, which advantageously reduces the risk of saturation in the rotor mass and improves the electromagnetic performance of the rotor.

[0125] Alternatively, the rotor includes a non-magnetic shaft on which the rotor mass is mounted. The shaft may be made at least partially from a material from the following, non-exhaustive list: steel, stainless steel, titanium, or any other non-magnetic material.

[0126] In one embodiment, the rotor mass can be positioned directly on the non-magnetic shaft, for example without an intermediate rim. Alternatively, particularly when the shaft is not non-magnetic, the rotor can have a rim surrounding the rotor shaft and bearing against it.

[0127] The rotor can be cantilevered or not, relative to the bearings used to guide the shaft. The rotor can be made of several sections aligned along the axial direction, for example at least two sections, or even four sections. Each section can be angularly offset from the adjacent pieces (a "step skew").

[0128] The cooling fluid can circulate within the permanent magnet housings, or between the shaft and the lamination pack. The cooling fluid can be in direct contact with the rotor's permanent magnets on a portion of their external surface, thus optimally capturing and dissipating heat and protecting the rotor's permanent magnets. "Direct contact" refers to physical contact with the external surface of the permanent magnets, which may optionally be coated with a protective varnish.

[0129] Rotor cooling is improved, thanks to efficient cooling of the magnets while minimizing magnetic field disturbance, which can allow for a wider range of magnets to be used, and a reduction in their cost.

[0130] Machine and stator

[0131] The invention also relates to a rotating electrical machine, comprising a rotor as defined above and a stator. The supply conduit(s) open, in particular, opposite the stator coil heads.

[0132] The machine can be used as a motor or as a generator. The machine can be a reluctance machine. It can function as a synchronous motor or, alternatively, a synchronous generator. Alternatively, it can function as an asynchronous machine.

[0133] The machine's maximum rotational speed can be high, for example, exceeding 10,000 rpm, ideally exceeding 12,000 rpm, and in the range of 14,000 to 15,000 rpm, or even 20,000, 24,000, or 25,000 rpm. Alternatively, the machine's maximum rotational speed can be lower than 100,000 rpm, or even 60,000 rpm, or even lower than 40,000 rpm, and ideally lower than 30,000 rpm.

[0134] The invention may be particularly suitable for high-power machines. The machine may comprise a single inner rotor or, alternatively, an inner rotor and an outer rotor, arranged radially on either side of the stator and coupled in rotation.

[0135] The machine can be inserted alone into a housing or inserted into a gearbox housing. In this case, it is inserted into a housing that also contains a gearbox.

[0136] The machine includes a stator. The stator has teeth that define slots. The stator may contain electrical conductors, at least some of them, or even most of them, which may be U-shaped or I-shaped. The winding may be direct current.

[0137] The machine may include a shaft through which, at least part of its length, an internal channel for supplying the cooling fluid is carried.

[0138] The machine may include a shaft through which, along at least part of its length, an internal channel supplies the cooling fluid. The shaft may not be traversed along its entire length by a unidirectional flow of cooling fluid. Instead, it may be traversed by a flow of cooling fluid over approximately half its length. The internal channel of the shaft may include a first axial portion over half the shaft's length, and a second radial portion configured to conduct the cooling fluid from the first portion to the lamination pack, and in particular to the axial distribution channel for the cooling fluid formed within the rotor lamination pack or between the rotor lamination pack and the shaft, along the shaft.

[0139] The stator may include coils arranged in a distributed manner within the slots, with electrical conductors arranged in a row within the slots. "Distributed" means that at least one of the coils passes successively through two non-adjacent slots.

[0140] Electrical conductors may not be arranged randomly in the slots but in an ordered manner. They are stacked in the slots in a non-random way, for example, in aligned rows. The stacking of electrical conductors is, for example, a hexagonal grid in the case of conductors with a circular cross-section. The stator may contain electrical conductors housed in the slots. At least some, if not most, electrical conductors may be pin-shaped, U-shaped, or I-shaped. The pin may be U-shaped (or "U-pin") or straight, being I-shaped (or "I-pin").

[0141] The electrical conductors can thus form a distributed winding. The winding may not be concentrated or wound on a tooth.

[0142] In one embodiment, the stator has a concentrated winding. The stator may have teeth and coils arranged on the teeth. The stator can thus be wound on teeth, in other words, with a non-distributed winding.

[0143] The stator teeth may have polar flares. Alternatively, the stator teeth may lack polar flares.

[0144] The stator may include an outer casing surrounding the cylinder head.

[0145] The stator teeth can be made with a stack of magnetic sheets, each coated with an insulating varnish, in order to limit losses by induced currents.

[0146] Processes

[0147] The invention also relates, independently or in combination with the above, to a method of manufacturing a flange as defined above, in which the flange is made by casting.

[0148] The flange can be manufactured without further machining. This simplifies the process and allows for more economical production of the flange.

[0149] The conduit(s) can be made using drawers arranged in the mold.

[0150] In another embodiment, the flange can be manufactured with further machining, in particular with a drilling step of the feed channel.

[0151] Preferably, the manufacturing process for a flange according to the invention does not involve a molding step using a lost mold. The flange can be manufactured without the use of an intermediate part such as a cap. The manufacturing process according to the invention is thus simpler and more economical to implement than prior art processes.

[0152] The manufacturing process according to the invention makes it possible to produce a flange with a wide variety of cooling fluid supply channels. Thanks to this process, it is possible to vary the inclination, width, and / or shape of the channel without complicating the flange manufacturing process.

[0153] The invention also relates, independently or in combination with the above, to a method of cooling a rotating electrical machine as defined above, in which the cooling fluid is circulated in opposite directions within the rotor, and then the cooling fluid is projected onto the coil heads of the stator.

[0154] The invention also relates, according to another of its aspects, independently or in combination with the above, to a vehicle comprising an electric machine as described above.

[0155] The vehicle can be a hybrid. For example, it may have an internal combustion engine, such as a gasoline engine, in addition to an electric motor. Alternatively, the vehicle may be fully electric. In this case, it may consist solely of an electric motor.

[0156] Brief description of the drawings

[0157] The invention will be better understood upon reading the detailed description that follows, the non-limiting examples of its implementation, and upon examination of the accompanying drawings, in which:

[0158] [Fig la] Figure la is a perspective view of a flange according to the invention, from the side of its inner face turned towards the rotor mass.

[0159] [Fig 1b] Figure 1b is another perspective view of the flange of figure 1a, from the side of its outer face.

[0160] [Fig le] Figure le is a cross-sectional view along CC of the flange of figures la and 1b.

[0161] [Fig Id] Figures Id and le are schematic and partial views, respectively in section and perspective, of the flange of figures la and 1b.

[0162] [Fig 2] Figures 2a to 2c are schematic and partial views, respectively in section, perspective and front, of a variant embodiment of the flange.

[0163] [Fig 3a] Figure 3a is a perspective view of an alternative embodiment of the flange, from the side of its inner face facing the rotor mass. [Fig 3b] Figure 3b is another perspective view of the flange of Figure 3a, from the side of its outer face.

[0164] [Fig 4] Figures 4a to 4c illustrate the different supply conduits of the flange in figures 3a and 3b.

[0165] [Fig 5] Figures 5a to 5c illustrate the different projection directions through the supply channels of the flange in Figures 3a and 3b.

[0166] [Fig 6a] Figure 6a illustrates the circulation of cooling fluid in a machine comprising two flanges of figures 3a and 3b.

[0167] [Fig 6b] Figure 6b is a view along the radial axis of the machine in Figure 6a.

[0168] [Fig 6c] Figure 6c is a perspective view of the cooling fluid circulation in the machine of Figure 6a.

[0169] [Fig 7] Figures 7a and 7b illustrate variant embodiments of the flange for a 4-pole rotor and an 8-pole rotor respectively.

[0170] [Fig 8a] Figure 8a is a perspective view of an alternative embodiment of the flange, from the side of its inner face turned towards the rotor mass.

[0171] [Fig 8b] Figure 8b is another perspective view of the flange of figure 8a, from the side of its outer face.

[0172] [Fig 9] Figures 9a and 9b illustrate the different projection directions through the supply channels of the flange in figures 8a and 8b.

[0173] [Fig 10] Figures 10a to 10c are schematic and partial views, respectively in section, perspective and front, of the flange of figures 8a and 8b.

[0174] [Fig 1 la] Figure 1 la is a perspective view of an alternative embodiment of the flange, from the side of its inner face turned towards the rotor mass.

[0175] [Fig 11b] Figure 11b is another perspective view of the flange of figure 1a, from the side of its outer face.

[0176] [Fig 12] Figures 12a to 12c are schematic and partial views, respectively in section, perspective and front, of the flange of figures 11a and 11b.

[0177] [Fig 12d] Figures 12d and 12e are views analogous to figures 12a and 12b of an alternative embodiment.

[0178] [Fig 13a] Figure 13a illustrates the circulation of cooling fluid in a machine comprising two flanges of Figures 1a and 11b. [Fig 13b] Figure 13b is a radial view of the machine of the figure

[0179] 13a.

[0180] [Fig 13c] Figure 13c is a perspective view of the cooling fluid circulation in the machine of Figure 13a.

[0181] [Fig 14a] Figure 14a is a perspective view of an alternative embodiment of the flange, from the side of its inner face turned towards the rotor mass.

[0182] [Fig 14b] Figure 14b is another perspective view of the flange of figure 14a, from the side of its outer face.

[0183] [Fig 15] Figures 15a to 15c are schematic and partial views, respectively in section, perspective and front, of the flange of figures 14a and 14b.

[0184] [Fig 16] Figures 16a and 16b are views analogous to figures 15a and 15b of an alternative embodiment.

[0185] Detailed description

[0186] In the figures and throughout the description, the same references represent identical or similar elements.

[0187] Figures 1a to 1e, Figure 2 and Figures 3a to 6c illustrate respectively a flange 10 for a rotor 3 of an electrical machine rotating 1 around an axis of rotation X. The flange 10 has an inner face 101 turned towards a rotor mass 30, an outer face 102 opposite the inner face 101, a radially outer slice 103 extending between the inner face 101 and the outer face 102, and a central bore 105.

[0188] The flange 10 also includes three supply conduits 12 for a cooling fluid, at 120° to each other.

[0189] Alternatively, as illustrated in Figure 7, a flange may have two 12 supply conduits at 180°, as seen in Figure 7a, or four 12 supply conduits at 90°, as illustrated in Figure 7b.

[0190] Each supply conduit 12 successively presents:

[0191] - a collection area 12a on the inner face 101 of the flange,

[0192] - a first narrowing 13a of a cross-section of the supply duct 12,

[0193] - an admission chamber 12c,

[0194] - a second narrowing 13b of the cross-section of the supply duct 12,

[0195] - a flared terminal portion 12b, located on the edge and on the outer face of the flange, the second narrowing 13b extending along a substantially oblique elongation axis Y.

[0196] The supply channels 12 are formed at least partially in a hollow on one face of the flange turned towards the rotor mass, in the thickness of the flange, as can be seen in figures 1 and 2a.

[0197] The supply conduits 12 extend along an elongation direction comprising a first portion perpendicular to the axis of rotation X and a second portion inclined with respect to a plane perpendicular to the axis of rotation X, which extends along the elongation axis Y substantially straight and oblique.

[0198] A length D of the supply conduit is measured along its elongation direction between the periphery of the central bore of the flange and the flared end portion. The length D of the supply conduit can be on the order of 33 mm.

[0199] The angle defined between the elongation axis Y of the supply conduit and a plane perpendicular to the X axis of rotation of the machine is on the order of 45°.

[0200] The supply conduits 12 open through flared terminal portions 12b arranged at the periphery of the flange and oriented radially outwards, through which the cooling fluid is projected onto a stator of the machine.

[0201] Each flared terminal portion 12b is located on the edge 103 and on the outer face of the flange 102, in a junction zone between the outer face and the edge of the flange, after the second narrowing 13b, when moving in the direction of the flow of the cooling fluid.

[0202] The flared terminal portion 12b forms a flare angle P in a plane perpendicular to the axis of rotation X, that is to say a radial opening angle, as seen in figures 1 and 2b, the flare angle P being for example of the order of 10°.

[0203] The flared terminal portion 12b also has an axial opening angle. For this purpose, the flared terminal portion 12b may include a bottom wall 15a extending substantially parallel to a plane perpendicular to the axis of rotation X with a slight angle ô with respect to a plane perpendicular to the axis of rotation of the rotor, the angle ô being in particular on the order of 15°, as illustrated in figure Id.

[0204] The flared terminal portion 12b finally includes a wall 15b closest to the axis of rotation X which is inclined at an angle y with respect to the axis of rotation of the rotor, the angle y being on the order of 15°. In the variant of figure 2, the angle ô is substantially zero.

[0205] The first constriction 13a is formed in the hollow in the thickness of the flange, on the face 101 of the flange turned towards the rotor mass, as illustrated in figures Id and 2c.

[0206] A width 1 of the first narrowing 13a is, for example, on the order of 1 mm. A length La of the first narrowing 13a is, for example, on the order of 0.3 mm. A cross-sectional area of ​​the first narrowing is, for example, on the order of 1 mm². 2 .

[0207] The second constriction 13b is formed in the thickness of the flange, comprising a portion of channel formed at 360° in the flange and being cylindrical in shape.

[0208] A diameter d of the second constriction 13b is, for example, on the order of 2.5 mm. A length Lb of the second constriction 13b is, for example, on the order of 5.5 mm. Thus, a cross-sectional area of ​​the second constriction 13b is, for example, on the order of 5 mm². 2 .

[0209] In the example illustrated in Figure 2a, the second narrowing extends along the elongation axis Y inclined at an angle α with respect to a plane perpendicular to the rotation axis X. The angle α is, for example, on the order of 45°.

[0210] In the embodiment shown in figures 3a to 6c, the flange has several second constrictions 13b extending each along elongation axes inclined each at a different angle with respect to a plane perpendicular to the rotation axis X.

[0211] In this embodiment, the flange 10 comprises three supply conduits 12, with three second constrictions 13b, inclined respectively at angles a1a, a2, a3 with respect to a plane perpendicular to the axis of rotation X, which are different, as illustrated in Figure 4. The first angle a1a is, for example, on the order of 45°. The second angle a2 is, for example, on the order of 30°. The third angle a3 is, for example, on the order of 60°.

[0212] The supply conduits 12 open opposite the stator coil heads, as illustrated in Figure 5. The cooling fluid flowing from the flange 10 through the first conduit at an angle of inclination α1 provides more focused cooling for the central part of the coil heads, as shown in Figure 5a. The cooling fluid flowing from the flange through the second conduit at an angle of inclination α2 provides more focused cooling for the part of the coil heads closest to the stator, as shown in Figure 5b. The cooling fluid flowing from the flange through the third conduit at an angle of inclination α3 provides more focused cooling for the ends of the coil heads, the winding interconnections (also called belts), and the phase connector, as shown in Figure 5c.

[0213] Furthermore, the supply conduits 12 each have an intake chamber 12c. The intake chambers 12c are formed in a recess on the face 101 of the flange facing the rotor mass, being trapezoidal in shape.

[0214] The intake chambers 12c are configured to face housings in the rotor mass 30 containing permanent magnets 5, as shown in Figure 5. The volume of an intake chamber is, for example, on the order of 206 mm³ 3 . A depth pc of an intake chamber is for example on the order of 5 mm.

[0215] Furthermore, each of the supply conduits 12 includes a collection zone 12a. The collection zones 12a are located closer to the edge of the flange than to the axis of rotation X of the machine and are formed as a recess on the face 101 of the flange facing the rotor mass, being trapezoidal in shape. The volume of a collection zone 12a is, for example, approximately 165 mm³ 3 . A depth pa of a collection zone 12a is for example on the order of 1.72 mm.

[0216] The collection areas 12a are configured to be positioned opposite rotor mass housings devoid of permanent magnets, as seen in Figure 5.

[0217] In the examples illustrated in figures 1a to 6c, the collection zones 12a are not connected to each other; each supply conduit 12 has a flared collection zone 12a. In this example, the collection zones are radially closed trapezoidal in shape.

[0218] Alternatively, the collection zones 12a can be connected to each other at an inner radial end by an annular recess 12d, as illustrated in the embodiment shown in Figures 8a to 10. The difference between the inner and outer diameters of this annular recess 12d is, for example, on the order of 3.5 mm. The annular recess 12d is delimited by the rotor mass and the flange.

[0219] Furthermore, in all the illustrated embodiments, the flange 10 has a plurality of cavities 35, which may be through-holes. Finally, in all the illustrated embodiments, the flange 10 has indexing notches 37, which are arranged on the edge 103 of the flange 10, near the flared end portions 12b.

[0220] The indexing notches allow the flanges to be angularly indexed on the rotor mass and thus ensure the correct alignment of the rotor mass with the shapes of the flange, as we will see later.

[0221] Figures 6a and 6b illustrate a rotating electrical machine 1 comprising a rotor 3 and a stator 2, with the supply conduits 12 opening opposite the coil heads 4 of the stator 2. The rotor 3 comprises a rotor mass 30 and two flanges 10, as illustrated individually in Figures 3a to 5, each located at one end of the rotor mass. The two flanges are identical and arranged with an angular offset from each other on either side of the rotor mass.

[0222] The machine 1 includes a shaft 6 through which, for approximately half its length, an internal channel 51 carries the cooling fluid. The internal channel 51 of the shaft 6 has a first axial portion over half the length of the shaft, and a second radial portion configured to conduct the cooling fluid from the first portion to the rotor mass 30, and in particular to an axial cooling fluid distribution channel formed between the rotor mass 30 and the shaft 6, along the latter, as illustrated in Figure 6a.

[0223] Furthermore, an axial channel for distributing the cooling fluid to the flanges 10 is formed in the rotor mass 30, passing axially through the rotor mass 30. Thus, the rotor has a first and a second cooling fluid circulation within the rotor mass 30, the first and second circulations being parallel to the rotor's axis of rotation X and in opposite directions. The first circulation is between the shaft 6 and the rotor mass 30. The second circulation is located within the rotor mass 30.

[0224] In this example, the second circulation is provided in housings without permanent magnets. For each rotor pole, the rotor mass has a first row of housings consisting of three U-shaped housings: a central housing and two lateral housings. The central housing of the first row is without a permanent magnet. The cooling fluid flows into the central housings of the rotor before reaching the flanges. In total, the rotor 3 has three primary circulations between the shaft 6 and the rotor mass 30, which are angularly offset, as well as three secondary circulations passing through the rotor, also angularly offset, and three fluid outlets located at the flanges, as illustrated in Figure 6a.

[0225] We will now describe the complete cooling circuit for this embodiment. The cooling circuit is supplied with coolant from the nose of shaft 6, on the side of one of its female splines. This coolant originates from the male drive shaft on the reduction side of the electric machine. At mid-length of shaft 6, the coolant flows radially through six holes in the shaft. It enters six cavities formed on the inner diameter of the rotor mass 30. This creates a large heat exchange surface between the coolant and the rotor mass 30. The coolant continues its path axially between the shaft and the rotor mass to the ends of the rotor mass 30.Once the coolant reaches the ends of the interface between the shaft 6 and the rotor mass 30, it reverses direction upon contact with the flange 10 to pass through axial channels formed in the rotor mass 30, which are trapezoidal in shape in this example. The coolant is then collected by the two flanges 10, creating a focused jet that directs the coolant as close as possible to the hot spots of the motor, such as the coil heads and the phase connector.

[0226] In the embodiment illustrated in Figures 11a to 13c, the second circulation is provided in the housings of the rotor's permanent magnets. The cooling fluid flows axially in housings with permanent magnets, more precisely in the housings of the row closest to the air gap, namely the V-shaped row, as shown in Figure 13b. In total, the rotor 3 has three first circulations between the shaft 6 and the rotor mass 30, which are angularly offset, as well as three second circulations passing through the rotor, also angularly offset, and three fluid outlets located at the flanges, as illustrated in Figure 13a.

[0227] Figures 12d and 12e illustrate an alternative embodiment of Figures 12a and 12b. In this alternative, the second narrowing 13b terminates on the outer face 102 of the flange. The flare 12b is present but could be omitted.

[0228] In the embodiment illustrated in Figures 14a to 15, the second circulation is provided successively in housings without permanent magnets and then in housings containing the rotor's permanent magnets. Figures 16a and 16b illustrate an alternative embodiment of Figures 15a and 15b. In this alternative, the second constriction 13b terminates on the outer face 102 of the flange. The flare 12b is present but could be omitted.

[0229] Of course, we do not depart from the scope of the present invention if the shapes and dimensions of the supply conduits, collection areas, first constrictions, intake chambers, second constrictions, and flared terminal portions are modified.

Claims

Demands 1. Rotor flange (10) of an electrical machine rotating (1) about an axis of rotation (X), comprising an inner face (101) facing a rotor mass (30), an outer face (102) opposite the inner face (101), a radially outer edge (103) extending between the inner face (101) and the outer face (102), the flange (10) comprising one or more supply channels (12) for a cooling fluid, at least one supply channel (12) comprising successively: - a collection area (12a) on the inner face (101) of the flange, - a first narrowing (13a) of a cross-section of the supply duct, - an admission chamber (12c), - a second narrowing (13b) of the cross-section of the supply conduit.

2. Flange according to the preceding claim, the second narrowing (13b) extending along an elongation axis (Y) substantially oblique with respect to a plane perpendicular to the axis of rotation (X).

3. Flange according to any one of the preceding claims, comprising a flared terminal portion (12b), in particular located on the edge and / or on the outer face of the flange.

4. Flange according to the preceding claim, the flared terminal portion (12b) forming a flare angle (P) in a plane perpendicular to the axis of rotation (X), the flare angle P being in particular between 0° and 60°, better between 0° and 15°, being for example of the order of 10°.

5. Flange according to any one of the preceding claims, a cross-sectional area of ​​the first constriction (13a) being between 0.06 mm 2 and 18 mm 2 , or even between 0.8 mm 2 and 3 mm 2 , for example, being on the order of 1 mm2 .

6. Flange according to any one of the preceding claims, a cross-sectional area of ​​the second constriction (13b) being between 0.3 mm 2 and 30 mm 2 , ideally between 0.8 mm 2 and 7 mm 2 for example, being on the order of 5 mm 2 .

7. Flange according to the preceding claim 2, the elongation axis (Y) being inclined at an angle α with respect to a plane perpendicular to the axis of rotation (X), the angle (α) being between 40° and 60°, or even between 42° and 55°, better between 44° and 50°, being for example around 45°.

8. Flange according to any one of the preceding claims, comprising several second constrictions (13b) each extending along elongation axes (Y) each inclined at a different angle (al, a2, a3) with respect to a plane perpendicular to the axis of rotation (X).

9. Flange according to any one of the preceding claims, the collection area(s) (12a) being arranged closer to the edge (103) of the flange (10) than to the axis of rotation (X) of the machine.

10. Flange according to any one of the preceding claims, comprising a plurality of cavities (35), in particular through cavities.

11. Rotor (3) of a rotating electrical machine, comprising a rotor mass (30) and at least one flange (10) according to any one of the preceding claims, at least one axial channel for distributing the cooling fluid to the flange(s) (10) being formed in the rotor mass (30) and / or between the rotor mass (30) and the shaft (6), along the latter.

12. Rotor according to the preceding claim, comprising at least a first and a second circulation of cooling fluid in the rotor mass (30), the first and second circulations being parallel to the axis of rotation (X) of the rotor and in opposite directions.

13. Rotating electrical machine (1) comprising a rotor (3) according to one of the two preceding claims, and a stator (2), the supply conduit(s) (12) opening in particular opposite coil heads (4) of the stator (2).

14. Machine according to the preceding claim, comprising a shaft (6) through which, at least part of its length, an internal channel (51) for supplying the cooling fluid passes.

15. Method for cooling a rotating electrical machine (1) as defined in any one of the two preceding claims, in which the cooling fluid is circulated in opposite directions within the rotor (13), and then the cooling fluid is projected onto the coil heads (4) of the stator (2).

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