Rotating oil distributor for a speed reducer

Abstract

The invention relates to a rotating oil distributor (10) for a speed reducer, the distributor (10) comprising: - a strainer (24) arranged across the distribution duct (16), suitable for filtering an oil flow (F) flowing through the distribution duct; and - a discharge duct (26) downstream of the strainer. The rotating oil distributor comprises a control device (30) for controlling a discharge flow (F') through the discharge duct, the control device comprising: - a shut-off member (32) mounted so as to be movable between an open position and a closed position, the shut-off member being designed so as to be urged towards its closed position by centrifugal force as the rotating oil distributor rotates; - a return member (34) arranged so as to urge the shut-off member (32) towards its open position.

Description

[0001] DESCRIPTION

[0002] TITLE: Oil distribution wheel for a speed reducer

[0003] Technical field of the invention

[0004] The invention relates to an oil distribution wheel for a speed reducer, in particular with an epicyclic or differential gear, for example installed in a double-flow turbomachine, in particular a turbomachine of an aircraft.

[0005] Prior art

[0006] The role of a mechanical reducer is to modify the speed and torque ratio between the input shaft and the output shaft of a mechanical system.

[0007] Newer generations of turbofan engines, particularly those with very high bypass ratios, incorporate a mechanical gearbox to drive the fan shaft. Typically, the gearbox's purpose is to transform the high rotational speed of the power turbine shaft into a slower rotational speed for the fan shaft.

[0008] Such a reduction gear comprises a central pinion, called the sun gear, a ring gear, and pinions called planet gears, which mesh between the sun gear and the ring gear. The planet gears are held by a frame called the planet carrier. The sun gear, ring gear, and planet carrier are planetary gears because their axes of revolution coincide with the longitudinal X-axis of the turbomachine. The planet gears each have a different axis of revolution, equally spaced on the same operating diameter around the axis of the planet gears. These axes are parallel to the longitudinal X-axis.

[0009] Several gearbox architectures exist. In state-of-the-art turbomachinery, gearboxes are of the planetary or epicyclic type. In other similar applications, differential or compound architectures exist.

[0010] - On a planetary reducer, the planet carrier is fixed and the ring forms the output shaft of the device which rotates in the opposite direction to the sun.

[0011] - On an epicyclic reducer, the ring is fixed and the planet carrier constitutes the output shaft of the device which rotates in the same direction as the solar.

[0012] - On a differential gearbox, no element is fixed in rotation. The ring rotates in the opposite direction to the solar and satellite carrier.

[0013] Gearboxes can consist of one or more meshing stages. This meshing is achieved in various ways, such as by contact, friction, or magnetic field. There are several types of contact meshing, including spur, helical, and herringbone gears.

[0014] The present request concerns the problem of lubrication of these complex rotating elements, in the specific case of an epicyclic type reducer with one or more stages, i.e. with rotating planet carrier and fixed ring gear, or differential, in which none of these elements is fixed in rotation.

[0015] For this purpose, it is known to employ oil supply and oil distribution devices within the gearbox, designated by the term centrifugal impellers. Examples of such centrifugal impellers are described, among others, in documents FR 2987416 A1, FR 3041054 A1 and EP 3822515 A1.

[0016] Such an impeller allows the oil distributed by one or more oil jets mounted on the engine frame (i.e., the fixed reference point) to be collected in a rotating oil collection cavity, or distributor, which includes an annular opening opposite said jets. The rotation of the impeller drives the oil from the distributor into one or more oil distribution circuits attached to the rotating reference point, which distribute the oil to the various mechanical components requiring lubrication (typically the gears and bearings of the planetary gears). The distribution circuits are oriented at least partially radially away from the axis of rotation, so that the rapid rotation creates centrifugal pressure in the oil column within the distribution circuits, ensuring the oil flows.

[0017] The advantages conferred by such systems include the possibility of transferring oil from the fixed reference point (engine frame) to the rotating reference point (satellite carrier), the absence of wear parts (no seals, no friction...) and performance independent of misalignments between the different components in the engine (frame, turbine, reducer...), which greatly improves the durability and reliability of these systems.

[0018] However, the use of an oil jet and an open oil receiving cavity creates a discontinuity in the oil flow insulation, allowing it to be contaminated by solid particles, for example, from the wear of a part in the engine's vicinity. Such solid particles can then enter the impeller at the cavity and follow the distribution circuit to the lubricated components, potentially leading to accelerated wear of these components.

[0019] A known solution to this problem is shown in Figure 1. A wheel 10 is partially shown in cross-section along a radial plane. The wheel 10 includes an oil recovery cavity 12, having an opening 14 oriented radially towards the axis of rotation and facing at least one oil jet 15 designed to generate an oil jet J. An oil distribution conduit 16 extends from the cavity 12 and comprises a first, substantially radial portion 18 and a second, substantially axial portion 20, which opens through an oil distribution opening 22 onto the components to be lubricated. An oil flow F is formed from the cavity 14 into the distribution conduit 16, under the effect of the pressure generated by the centrifugal force resulting from the rotation of the wheel around the central axis A on the column of oil present in the first portion 18.

[0020] A strainer 24 is disposed in the distribution conduit 16 of the impeller 10, in the second substantially axial portion 20. The strainer 24 is arranged to filter the oil flow F and block the passage of fine particles through the distribution conduit 16.

[0021] In order to remove particles that could clog the strainer 24, a radial hole is drilled in the walls of the distribution circuit 16, upstream of the strainer 24, for example in the extension of the first portion 18, in order to create an evacuation conduit 26 for the filtered particles out of the distribution circuit.

[0022] An evacuation flow F' flows through said evacuation conduit 26 outside the frame and away from the parts to be lubricated.

[0023] This type of device satisfactorily fulfills the desired filtration function and prevents the strainer from clogging with filtered particles. However, it can still be improved.

[0024] Indeed, the presence of the drain pipe results in a continuous oil leakage rate when the rotating assembly is in motion due to the gearbox operation. On the one hand, this lost oil flow is carried along by the engine's rotating parts, generating power losses through turbulence. On the other hand, this oil loss must be taken into account when sizing the lubrication system, particularly for the onboard oil reservoirs and the corresponding distribution system, which leads to unnecessary additional costs and an unintended increase in the vehicle's weight.

[0025] Presentation of the invention

[0026] The invention aims to overcome these drawbacks. To this end, the invention relates to an oil distribution wheel for a speed reducer, the wheel comprising:

[0027] - a substantially annular frame with a central axis, the frame being intended to be fixed to a planetary carrier of the speed reducer,

[0028] - an oil receiving cavity opening in the frame through an opening oriented radially towards the central axis,

[0029] - at least one oil distribution conduit extending from the cavity and opening through a distribution port arranged to open opposite the lubricating components of the speed reducer,

[0030] - a strainer arranged across the distribution conduit, designed to filter an oil flow entering the distribution conduit, and - a drain conduit opening into the distribution conduit downstream of the strainer and discharging through a drain opening arranged to open away from the elements to be lubricated, characterized in that the impeller further comprises a device for controlling a drain flow through the drain conduit, said control device comprising:

[0031] - a movable shutting device between a passing position in which the shutting device allows the passage of the evacuation flow through the evacuation conduit and a blocking position in which the shutting device prevents the passage of the evacuation flow through the evacuation conduit, the shutting device being arranged to be forced towards its blocking position under the effect of a centrifugal force during the rotation of the impeller around the central axis,

[0032] - a return element arranged to force the sealing element towards its passing position. Such a wheel makes it possible to block the oil leakage flow during high-speed rotation of the speed reducer, i.e. when said leakage flow would be the highest, while allowing the oil and particles to evacuate at low speed and when stopped.

[0033] The said speed reducer is, for example, an epicyclic or differential gear reducer.

[0034] The intensity of the stress exerted by the return member can be selected so that the locking position of the locking member is reached only above a predetermined rotational speed of the wheel.

[0035] The diameters and / or effective flow sections of the second portion of the distribution conduit and the discharge conduit can be determined so as to have oil flow preferentially in the discharge conduit when it is not blocked by the sealing device.

[0036] Each distribution channel may comprise a first portion extending substantially radially from the cavity and a second portion extending substantially axially and opening through the distribution port, the strainer being fixed at the inlet of the second portion and extending axially partially across the first portion. This feature allows a portion of the strainer to be positioned across the oil flow in the first portion of the channel, thus facilitating the removal of filtered particles.

[0037] The exhaust duct can extend substantially axially from the distribution duct and preferably to the exhaust opening.

[0038] Such a feature allows the use of a radially moving switching element, using the mass of the element to actuate it under the effect of centrifugal force.

[0039] The return mechanism can be a spring, one end of which is fixed to the frame and the other end to the shutter. This design allows for a substantially linear return force to be applied to the shutter, making it easier to adjust the force required to reach the locking position only above a predetermined rotational speed.

[0040] The sealing member can be a movable plug mounted to slide in a substantially radial switching conduit, intersecting the discharge conduit, the return member being disposed in the switching conduit, fixed by a first end to a radially internal end of the switching conduit and by a second end to the movable plug.

[0041] The sealing member can be a movable plug mounted to slide in a substantially radial switching conduit, intersecting the evacuation conduit, the return member being disposed compressed in the switching conduit, supported by a first end against a radially external end of the switching conduit and by a second end against the movable plug.

[0042] These characteristics allow for a reliable and robust structure of the sealing and return mechanisms, which offer good durability and simple manufacturing.

[0043] The sealing member may include a butterfly mounted in the evacuation conduit, movable in rotation about a substantially circumferential axis between the blocking position in which the butterfly extends entirely across the evacuation conduit and the passing position in which a circulation space is left free between the butterfly and the walls of the evacuation conduit, the return member being arranged to force the butterfly towards its passing position, the sealing member also including a ballast fixed to the butterfly away from the axis of rotation, so that the centrifugal force during the rotation of the wheel about the central axis forces the butterfly towards its blocking position.

[0044] This feature allows the use of a rotating part for the sealing mechanism, which reduces the risk of blockage compared to a sliding stopper.

[0045] The sealing element may include a flapper fixed to the frame external to the evacuation duct, mounted to rotate freely around a circumferential axis between the blocking position in which the flapper is pressed against and blocks the evacuation opening and the passing position in which the flapper is away from the evacuation opening, the return element being arranged to force the flapper towards its passing position, the sealing element also including a weight fixed to the flapper away from the axis of rotation, so that the centrifugal force during the rotation of the wheel around the central axis forces the flapper towards its blocking position.

[0046] This feature allows the sealing and return mechanisms to be located outside the oil circulation network.

[0047] The sealing member may include a radially movable plug, the discharge conduit opening into the distribution conduit by a substantially radial inlet arranged to form a seat for said plug, the plug bearing against said seat and sealing the inlet of the discharge conduit in the blocking position and being away from the seat and allowing the passage of oil through the inlet of the discharge conduit in the passing position, the return member being an elastic spring mounted compressed between the seat and the plug.

[0048] This characteristic allows for a compact and robust structure of the closing and return mechanisms.

[0049] The invention also relates to an assembly for an aircraft turbomachine, comprising

[0050] - a speed reducer,

[0051] - at least one oil nozzle intended to be mounted on a fixed structure of the turbomachine, adapted to project at least one jet of oil,

[0052] - an oil distribution wheel as described above, the wheel's frame being fixed to a planet carrier of the speed reducer, the wheel and the planet carrier being free to rotate about the central axis, the wheel's cavity being positioned opposite at least one nozzle to collect at least one jet of oil, the distribution opening facing the components to be lubricated in the reducer and the discharge opening facing away from the components to be lubricated. The speed reducer is, for example, an epicyclic or differential gear reducer.

[0053] Brief description of the figures

[0054] [FIG. 1] is a partial cross-sectional view in a radial plane of a prior art oil distribution wheel,

[0055] [FIG. 2] [FIG. 3] are partial cross-sectional views in a radial plane of an oil distribution wheel according to a first embodiment of the invention, respectively in a passing position and in a blocking position of a sealing element,

[0056] [FIG. 4] is a partial cross-sectional view in a radial plane of an oil distribution wheel according to a second embodiment of the invention, in a through position of a sealing member,

[0057] [FIG. 5] [FIG. 6] are partial cross-sectional views in a radial plane of an oil distribution wheel according to a third embodiment of the invention, respectively in a passing position and in a blocking position of a sealing element, and

[0058] [FIG. 7] [FIG. 8] are cross-sectional diagrams in a radial plane of an oil distribution wheel according to a fourth embodiment of the invention, respectively in a passing position and in a blocking position of a sealing element.

[0059] Detailed description of the invention An oil distribution wheel 10 for an epicyclic or differential gear reducer according to a first embodiment of the invention is shown in figures 2 and 3. The wheel 10 is fixedly mounted on a planet carrier of the gear reducer, so that the rotational movement of the planet carrier drives the wheel 10 in rotation.

[0060] The spinning wheel 10 is shown partially in cross-section along a radial plane.

[0061] The wheel 10 comprises a frame 1 1 substantially annular around a central axis A, which is the axis of rotation of the wheel 10 during its movement accompanying the planet carrier of the reducer, said central axis A being coincident with the axis of rotation of the planet carrier.

[0062] The terms "axial", "radial" and "circumferential", as well as the terms "internal" and "external", are understood in relation to the central axis A.

[0063] The term "substantially" is used relative to a direction to indicate a small angular deviation from said direction, for example less than or equal to 10° and especially less than or equal to 5°.

[0064] As previously described, the wheel 10 includes an oil recovery cavity 12, having an opening 14 oriented radially towards the axis of rotation and facing at least one oil jet 15 suitable for generating an oil jet J. A plurality of oil distribution channels 16 extend from the cavity 12, each distribution channel 16 comprising a first substantially radial portion 18 and a second substantially axial portion 20, which opens through an oil distribution opening 22 opposite the parts to be lubricated.

[0065] An oil flow F is formed from cavity 14 into distribution conduit 16, under the effect of the pressure generated by the centrifugal force resulting from the rotation of the impeller around the central axis A on the column of oil present in the first portion 18.

[0066] A strainer 24 is disposed in the distribution conduit 16 of the impeller 10, in the second substantially axial portion 20. The strainer 24 is arranged to filter the oil flow F and block the passage of fine particles through the distribution conduit 16.

[0067] According to the first embodiment of the invention, the wheel 10 includes an evacuation conduit 26 which opens into the distribution conduit 16 downstream of the strainer 24 and extends substantially axially to an evacuation opening 28 arranged away from the elements to be lubricated.

[0068] For example, the drain duct 26 extends in a direction opposite to the direction of the second portion 20 of the distribution duct, so that the drain opening 28 opens on the side of the frame 11 opposite to the distribution opening 22.

[0069] Advantageously, the strainer 24 is fixed at the inlet of the second portion 20 and extending axially partially across the first portion 18, so that the passage of the oil flow F' through the first portion 18 to the discharge conduit 26 partially passes through the strainer 24 to detach the said filtered particles.

[0070] According to the invention, the wheel 10 includes a control device 30 intended to control the flow of an evacuation flow F' of oil through the evacuation conduit 26 to the evacuation opening 28.

[0071] The said control device 30 includes a sealing element 32 for the evacuation conduit 26 and a return element 34.

[0072] In general, the sealing member 32 is mounted movable between a passing position in which the sealing member 32 allows the passage of the evacuation flow F' through the evacuation conduit 26 and a blocking position in which the sealing member 32 prevents the passage of the evacuation flow F' through the evacuation conduit 26.

[0073] The sealing member 32 is arranged to be forced towards its locking position by the effect of the centrifugal force exerted by the rotation of the wheel 10 around the central axis A.

[0074] Conversely, the return member 34 is arranged to urge the obturating member 32 towards its passing position.

[0075] The competition between the forces exerted by the return member 34 and the centrifugal force allows the locking member 32 to adopt its passing position below a certain predetermined critical rotation speed of the wheel 10 and to adopt its locking position beyond this predetermined critical rotation speed of the wheel 10. The determination of this critical transition rotation speed depends on the exact respective natures of the locking member 32 and the return member 34.

[0076] The diameters and / or effective flow cross-sections of the second portion 20 of the distribution conduit 16 and of the discharge conduit 26 are advantageously determined so as to have oil flow preferentially in the discharge conduit 26 when it is not closed by the sealing device 32. Particular care is taken to ensure that the pressure drop of the discharge flow F' is lower than the pressure drop of the distribution flow F. Thus, at low rotational speeds of the impeller 10, the oil preferentially flows through the discharge conduit and carries away the particles filtered by the strainer 24. At high rotational speeds, the discharge conduit 36 ​​is closed and the oil flows through the second portion 20 of the distribution conduit 16, is filtered by the strainer 24, and lubricates the components requiring lubrication, such as the gears of the gearbox's satellites, when this is most necessary.

[0077] In the first embodiment shown in figures 2 and 3, the sealing member 32 is a movable plug mounted to slide in a substantially radial switching conduit 36, intersecting the evacuation conduit 26.

[0078] The plug has a substantially cylindrical shape, with a diameter substantially equal to the diameter of the switching conduit 36 ​​and a height greater than a diameter of the evacuation conduit 26 at the intersection with the switching conduit 36, so that the plug can block the passage of the evacuation flow F' through the intersection between the evacuation conduit 26 and the switching conduit 36.

[0079] This position of the plug across the intersection of the switching conduit 36 ​​and the evacuation conduit 26, shown in figure 3, constitutes the blocking position of the sealing member 32.

[0080] The switching conduit 36 ​​extends, for example, substantially perpendicularly to the evacuation conduit 26, and includes a portion of housing which extends radially inwards beyond the intersection, over a length sufficient to receive at least partially the plug, so as to leave at least part of the intersection between the evacuation conduit 26 and the switching conduit 36 ​​free and allow the passage of evacuation flow F'.

[0081] The position of the plug received at least partially in the portion of housing 38, shown in figure 2, corresponds to the passing position of the locking member 34.

[0082] The return member 34 is a spring, one end of which is fixed to the frame 11 and the other end is fixed to the sealing member 32.

[0083] More specifically, the return member 34 is disposed in the switching conduit 36, fixed by a first end to a radially internal end of the switching conduit 36 ​​and by a second end to the movable plug.

[0084] Thus, the return member 34 exerts an elastic return force on the movable plug that depends linearly on the deformation exerted on the return member 34 by the movement of the plug in the switching conduit 36. The return member 34 has a rest length that is sufficiently small so that in the absence of any other force exerted on the movable plug, the latter is in the passing position.

[0085] In the passing position shown in Figure 2, the rotation of the wheel is sufficiently small, or even zero, so that the centrifugal force exerted by the rotation is sufficiently less than the said elastic restoring force so that the plug is globally stressed by the resultant of these forces in the direction of the portion of housing 38.

[0086] In the blocking position, shown in Figure 3, the centrifugal force is sufficient to extend the return member 34 until the plug is across the intersection, in equilibrium of the two forces, or even in contact with the radially external end of the switching conduit 38. For this, the radially external end of the switching conduit 38 is provided close enough to the intersection so that the length of the plug allows the intersection to be blocked when it is in contact with this radially external end.

[0087] This ensures that the plug remains in a locking position at high rotational speeds, without protruding beyond the intersection under very high loads at very high speeds. According to a variant (not shown) of this embodiment, the housing portion 38 is radially external to the intersection between the discharge conduit 26 and the switching conduit 36, with the return element 34 disposed within this housing portion, compressed between the plug and the radially external end of the housing portion 38. In this case, the return element has a sufficiently long rest length so that, in the absence of other forces applied to the plug, it pushes the plug against the radially internal end of the switching conduit, thus leaving the intersection free for the passage of the discharge flow F'.

[0088] When the rotational speed of the wheel is sufficient, the centrifugal force applied to the movable plug compresses the spring and stresses the plug across the intersection, blocking the evacuation flow F'.

[0089] According to a second embodiment shown in Figure 4, the sealing member 32 comprises a butterfly 40 mounted in the discharge conduit 26, which is free to rotate about a substantially circumferential axis X. The operation of the impeller 10 according to this second embodiment is identical to that according to the first embodiment, except for the following.

[0090] The butterfly 40 is a plate, for example metallic, substantially flat having a contour identical to the transverse contour of the evacuation conduit at the axis of rotation X, so that the butterfly 40 blocks the evacuation conduit 26 and prevents the passage of the evacuation flow F' when it extends perpendicularly to the local direction of the evacuation conduit 26. This position of the butterfly 40 constitutes the blocking position of the sealing member 32.

[0091] The passing position of the obturator 32, shown in Figure 4, corresponds to the position of the butterfly 40 in which a circulation space is left free between the butterfly 40 and the walls of the evacuation conduit 26, the butterfly 40 extending in a plane forming a non-right angle with the local direction of the evacuation conduit 26.

[0092] The sealing member 32 also includes a weight 42 fixed to the butterfly 40 away from the axis of rotation X, so that the centrifugal force during the rotation of the wheel 10 around the central axis A forces the butterfly 40 towards its locking position, in which the weight 42 is located as far outwards as possible in the radial direction.

[0093] The return element 34 is arranged to move the butterfly 40 towards its passing position, that is to say to move it away from the blocking position.

[0094] The return element can, for example, be a spiral spring attached at one end to the butterfly valve 40, away from the axis of rotation X, and at the other end to a radially internal wall of the exhaust duct 26. This spring is under tension and thus forces the butterfly valve 40 towards this wall, causing the butterfly valve 40 to rotate away from its locked position. Alternatively, the return element can be, for example, a spring exerting a rotational torque on the butterfly valve 40, mounted at the axis of rotation X of the butterfly valve 40 and arranged to force it away from its locked position.

[0095] According to a third embodiment shown in figures 5 and 6, the sealing member 32 includes a valve 44 fixed to the frame 11 externally to the evacuation conduit 26.

[0096] The operation of the spinning wheel 10 according to this third embodiment is identical to that according to the first embodiment, with the exception of the following.

[0097] In this embodiment, the evacuation conduit 26 extends substantially radially, at least with regard to the part opening through the evacuation opening 28, which is oriented radially.

[0098] The valve 44 is mounted on the frame 11, which is movable in rotation around a substantially circumferential axis X between the blocking position, shown in Figure 6, in which the valve 44 is against and closes the evacuation opening 28, and the passing position, shown in Figure 5, in which the valve 44 is away from the evacuation opening 28.

[0099] The sealing member 32 also includes a weight 46 fixed to the valve 44 at an angle to the axis of rotation X, such that the centrifugal force during the rotation of the impeller 10 around the central axis A forces the valve 44 towards its blocking position. The weight 46 is, for example, located at an edge of the valve 44 on the side opposite the discharge opening 28 relative to the axis of rotation X of the valve 44, so that the centrifugal force forces the weight radially outwards, which drives the part of the valve 44 blocking the discharge opening 28 radially inwards, against the discharge opening.

[0100] The return element 34, for example a spring, is arranged to force the flap 44 towards its open position. For example, one end of the spring is fixed to the flap 44 near the weight 48, and the other end of the spring is fixed to the frame 11 at a point 48 located radially inward with respect to the flap 44. The spring is under tension and exerts a restoring force on the end of the flap 44, moving the weight radially inward and, by rotation, the part of the flap closing the discharge opening 28 radially outward, away from the discharge opening 28.

[0101] According to a fourth embodiment shown in figures 7 and 8, the sealing member 32 includes a plug 50 mounted movably radially in the evacuation conduit 26.

[0102] The operation of the spinning wheel 10 according to this fourth embodiment is identical to that according to the first embodiment, with the exception of the following.

[0103] In this embodiment, the evacuation conduit 26 extends substantially radially, at least with regard to the part opening into the distribution conduit.

[0104] The opening of the evacuation conduit 26 in the distribution conduit 16 is arranged to form a seat 52 for the plug 50, which acts as a valve closing the inlet of the evacuation conduit 26 when it is forced against the seat 52 by the centrifugal force associated with the rotation of the wheel 10.

[0105] The plug 50 and the seat 52, for example, have identical conical or frustoconical profiles to provide respective contact surfaces that block the flow of oil. The return element 34 is a helical spring mounted radially between the plug 50 and the seat 52, so as to be compressed by the movement of the plug 50 towards the seat 52 under the effect of centrifugal force during the rotation of the impeller 10 around the central axis A, and thus to force the plug 50 away from the seat 52.

[0106] The passing position is shown in Figure 7, and corresponds to the case where the rotation is slow or zero. The centrifugal force is then insufficient to force the plug 50 against the seat 52 and the passage of the discharge flow F' into the discharge conduit 26 is permitted.

[0107] The blocking position is shown in Figure 8 and corresponds to the case where the rotation is faster than the critical rotational speed. The centrifugal force is then sufficient to force the plug 50 into a tight contact with the seat 52, and the passage of the discharge flow F' into the discharge conduit 26 is thus blocked. The oil is then redirected into the second portion 20 of the distribution conduit 16, through the strainer 24.

Claims

DEMANDS 1. Oil distribution wheel (10) for a speed reducer, the wheel (10) comprising: - a frame (11) substantially annular having a central axis (A), the frame (11) being intended to be fixed to a planetary carrier of the speed reducer, - an oil receiving cavity (12) opening in the frame (11) through an opening (14) oriented radially in the direction of the central axis (A), - at least one oil distribution conduit (16) extending from the cavity (14) and opening through a distribution opening (22) arranged to open opposite the lubricated elements of the speed reducer, - a strainer (24) arranged across the distribution conduit (16), designed to filter an oil flow (F) flowing into the distribution conduit (16), and - a discharge conduit (26) opening into the distribution conduit (16) downstream of the strainer (24) and discharging through a discharge opening (28) arranged to open away from the elements to be lubricated, characterized in that the impeller (10) further comprises a control device (30) for a discharge flow (F') through the discharge conduit, said control device comprising: - a sealing member (32) mounted movable between a passing position in which the sealing member (32) allows the passage of the evacuation flow (F') through the evacuation conduit and a blocking position in which the sealing member prevents the passage of the evacuation flow (F') through the evacuation conduit, the sealing member being arranged to be forced towards its blocking position under the effect of a centrifugal force during the rotation of the impeller around the central axis (A), - a return member (34) arranged to urge the obturating member (32) towards its passing position.

2. Wheel (10) according to claim 1, in which each distribution conduit (16) comprises a first portion (18) extending substantially radially from the cavity (14) and a second portion (20) extending substantially axially and opening through the distribution opening (22), the strainer (24) being fixed at the level of the inlet of the second portion (20) and extending axially partially across the first portion (18).

3. Wheel (10) according to claim 1 or 2, in which the discharge conduit (26) extends substantially axially from the distribution conduit (16) and preferably to the discharge opening (28).

4. Wheel (10) according to any one of claims 1 to 3, wherein the return member (34) is a spring having a first end fixed to the frame (11) and a second end fixed to the sealing member (32).

5. A wheel (10) according to any one of claims 1 to 4, wherein the sealing member (32) is a movable plug mounted to slide in a substantially radial switching conduit (36), intersecting the discharge conduit (26), the return member (34) being disposed in the switching conduit (36), fixed by a first end to a radially internal end of the switching conduit (36) and by a second end to the movable plug.

6. A wheel (10) according to any one of claims 1 to 4, wherein the sealing member (32) is a movable plug mounted to slide in a substantially radial switching conduit (36), intersecting the discharge conduit (26), the return member (34) being disposed compressed in the switching conduit (26), bearing by a first end against a radially external end of the switching conduit (36) and by a second end against the movable plug.

7. A wheel (10) according to any one of claims 1 to 4, wherein the sealing member (32) comprises a butterfly (40) mounted in the discharge conduit (26), movable in rotation about a substantially circumferential axis (X) between the blocking position in which the butterfly (40) extends entirely across the discharge conduit (26) and the passing position in which a circulation space is left free between the butterfly (40) and the walls of the discharge conduit (26), the return member (34) being arranged to urge the butterfly (40) towards its passing position, the sealing member (32) also comprising a weight (42) fixed to the butterfly (34) away from the axis of rotation (X), so that the centrifugal force during the rotation of the wheel (10) about the central axis (A) urges the butterfly (40) towards its blocking position.

8. A wheel (10) according to claim 1 or 2, wherein the closing member (32) comprises a flapper (44) fixed to the frame (11) externally to the discharge conduit (26), mounted to rotate about a circumferential axis (X) between the blocking position in which the flapper (44) is pressed against and closes the discharge opening (28) and the passing position in which the flapper (44) is away from the discharge opening (28), the return member (34) being arranged to actuate the flapper (44) towards its passing position, the closing member (32) also comprising a weight (46) fixed to the flapper (44) away from the axis rotation (X), so that the centrifugal force during the rotation of the wheel (10) around the central axis (A) forces the valve (44) towards its locking position.

9. Impeller (10) according to claim 1 or 2, wherein the sealing member (32) comprises a radially movable plug (50), the discharge conduit (26) opening into the distribution conduit (16) by a substantially radial inlet arranged to form a seat (52) for said plug (50), the plug (50) bearing against said seat (52) and sealing the inlet of the discharge conduit (26) in the blocking position and being away from the seat (52) and allowing the passage of oil through the inlet of the discharge conduit (26) in the passing position, the return member (34) being an elastic spring mounted compressed between the seat (52) and the plug (50).

10. Assembly for an aircraft turbomachine, comprising: - a speed reducer, - at least one oil nozzle (15) intended to be mounted on a fixed structure of the turbomachine, adapted to project at least one jet of oil (J), - an oil distribution wheel (10) according to any one of claims 1 to 9, the frame (11) of said wheel being fixed to a planet carrier of the speed reducer, the wheel (10) and the planet carrier being movable in rotation about the central axis (A), the cavity (12) of the wheel (11) being disposed opposite at least one nozzle (15) in order to collect at least one jet of oil (J), the distribution opening (22) opening opposite elements to be lubricated of the reducer and the discharge opening (28) opening away from the elements to be lubricated.

Images