PLANETARY REDUCTION UNIT FOR A TURBO ENGINE

Description

Technical field of the invention

[0001] The present invention relates to the field of planetary gear reducers for turbomachines, particularly aircraft. Technical background

[0002] The state of the art includes in particular documents WO-A1-2010 / 092263, FR-A1-2 987 416, EP-A1-1 464 869, FR-A1-3 041 054 FR-A1-2 853 382, ​​FR-A1-3 052 213, JP-A-2009 058002, US-A1-2013 / 023378 and US-A1-2011 / 252907, EP-A1-3 165 739.

[0003] The role of a mechanical reducer is to modify the speed ratio and torque between the input shaft and the output shaft of a mechanism.

[0004] New generations of dual-flow turbomachines, particularly those with a high bypass ratio, include a mechanical reducer to drive the shaft of a fan. Typically, the reducer's purpose is to transform the so-called fast rotation speed of a power turbine shaft into a slower rotation speed for the shaft driving the fan.

[0005] Such a reducer comprises a central pinion, called a sun gear, a crown gear and pinions called planet gears, which are meshed between the sun gear and the crown gear. The planet gears are held by a frame called a planet carrier. The sun gear, the crown gear and the planet carrier are planet gears because their axes of revolution coincide with the longitudinal axis X of the turbomachine. The planet gears each have a different axis of revolution equally distributed over the same operating diameter around the axis of the planet gears. These axes are parallel to the longitudinal axis X.

[0006] There are several gearbox architectures. In the state of the art of double-flow turbomachinery, gearboxes are of the planetary or epicyclic type. In other similar applications, there are so-called differential or "compound" architectures. ∘ On a planetary gearbox, the planet carrier is fixed and the crown constitutes the output shaft of the device which rotates in the opposite direction to the sun. ∘ On an epicyclic gearbox, the crown is fixed and the planet carrier constitutes the output shaft of the device which rotates in the same direction as the sun. ∘ On a differential gearbox, no element is fixed in rotation. The crown rotates in the opposite direction to the sun and the planet carrier.

[0007] Gearboxes can be composed of one or more meshing stages. This meshing is ensured in different ways such as by contact, friction or even by magnetic field.

[0008] There are several types of contact meshing such as straight or herringbone teeth.

[0009] The planet carrier of a reducer may be in the form of a cage in which the solar, the satellites, the guide bearings of the satellites as well as means of lubricating the satellites and the solar are housed. The solar comprises internal splines for coupling to a first shaft of the turbomachine and the cage of the planet carrier is integral with a cage holder which comprises a cylindrical portion comprising external splines for coupling to another shaft.

[0010] The connection of the cage to the cage carrier is generally rigid. Alternatively, a technology can be envisaged in which the cage is connected to the cage carrier by flexible connections, as described in EP-A1-1 464 869. In such a case, the cage carrier comprises an annular row of axial fingers which are connected by flexible connections to the cage. As mentioned above, a planetary gearbox has a fixed planet carrier connected to a stator element of the turbomachine by interface elements. The distribution of loads to the various planets of the gearbox requires a certain flexibility of these interface elements. This flexibility, however, goes against the dynamic situation of the gearbox in the engine.

[0011] The present invention proposes an improvement which provides a simple, effective and economical solution to this problem. Summary of the invention

[0012] The invention relates to an assembly comprising a planetary gear reducer planet carrier and an elastically deformable annular member and a stator element, for a turbomachine, in particular an aircraft turbomachine, the planet carrier having a generally annular shape around an axis X, and the annular member extending around the axis X, this member being fixed to said planet carrier and to the stator element in order to ensure a flexible connection between the planet carrier and said stator element, characterized in that the planet carrier carries a series of projecting teeth extending substantially radially outwards relative to said axis X, each of these teeth comprising first opposite lateral faces extending in planes passing through the axis X and capable of cooperating by abutment in the circumferential direction with said stator element, vibration damping systems, of the vibration damping pad and / or damping oil film type, being interposed between said first faces and said stator element.

[0013] The present invention therefore applies in the context of a so-called planetary reducer, that is to say one whose planet carrier is connected to a stator element of the turbomachine and is therefore fixed in the engine reference frame. This solution is compatible with any type of toothing of the sun gear, the planets and the crown. The solution proposed below is compatible with any type of planet carrier, whether it is a single-piece or a cage and cage carrier type. This solution is finally compatible with any type of planet bearing, whether it is composed of rolling elements, a hydrodynamic bearing, etc.

[0014] In the present invention, the planet carrier is connected to the stator element by a flexible connection comprising an elastic member. This elastic member can be designed to provide flexibility in the axial, radial and torsional directions to the connection. This flexible connection also ensures transmission of forces between the planet carrier and the stator element. Beyond a certain threshold of torsional force and therefore of torque around the X axis, the elastic member is likely to break. To avoid this, the planet carrier comprises teeth which are capable of cooperating by abutment in the circumferential direction with the stator element. These teeth are thus intended to take over the transmission of forces in the aforementioned case where the torsional forces transmitted by the planet carrier would be too great and likely to damage the elastic member.The teeth are advantageously free to move radially and axially relative to the stator element.

[0015] The damping systems make it possible to absorb the vibrations to which the planet carrier is subjected during operation. The cage carrier according to the invention may comprise the following features in combination with each other as defined in the dependent claims: the planet carrier is in one piece or comprises a cage and a cage holder, the cage holder comprises an annular body extending around the X axis and carrying the series of teeth as well as a series of projecting fingers extending along the X axis and distributed around this X axis, each of these fingers comprising at its free end opposite the body a recess for mounting a bearing shaft for the purpose of connecting the cage holder to the cage, this cage comprising at its periphery axial housings in which the fingers are received and which are crossed by the bearing shafts, the teeth and the fingers are at least partly formed in a single piece with the body; this makes it possible to simplify the manufacture and assembly of the cage holder, the planet carrier comprises an internal conduit for circulating oil and supplying oil to said first lateral faces with a view to forming a damping oil film at each of these faces;a damping film of the "squeeze film" type is thus obtained, well known in the field of turbomachines for absorbing vibrations and preventing their transmission between two parts; in the case of using elastomer pads, the damping film is not necessarily necessary, said elastic member has a general U-shape in longitudinal section, the opening of which is oriented radially outwards, this member comprising a first annular flange applied axially and fixed to the planet carrier, and a second annular flange applied axially and fixed to the stator element; the member thus has a simple shape; this shape is however not limiting;

[0016] The present invention also relates to a turbomachine module, comprising an assembly as described above, the stator element comprising two annular shells, respectively external and internal, extending around each other and around said axis X, the shells being connected to each other by arms, the internal shell extending at least partly around said planet carrier and comprising at its internal periphery a series of housings extending substantially radially and in which the teeth of the planet carrier are engaged, these teeth being able to move radially in these housings and their first lateral faces being able to abut in the circumferential direction on second lateral faces opposite the housings.

[0017] The module according to the invention may comprise the following features in combination with each other as defined in the dependent claims: the stator element may comprise damping pads on said second lateral faces (made of polymer or any other vibration-absorbing material), and / or an internal duct for circulating oil and supplying oil to said second lateral faces for the purpose of forming a damping oil film between said first and second lateral faces; a damping film of the "squeeze film" type is thus obtained, as mentioned above, said arms comprise leading edges located in a plane P2 perpendicular to said axis X and trailing edges located in a plane P2' perpendicular to said axis X, the housings and the fingers being located in a plane P1 located between the planes P2 and P2'; this may make it possible to optimize the size of the module. Brief description of the figures

[0018] Other characteristics and advantages will emerge from the following description of a non-limiting embodiment of the invention with reference to the appended drawings in which: [ Fig. 1 ] there figure 1 is a schematic axial sectional view of a turbomachine using the invention, [ Fig. 2 ] there figure 2 is a schematic axial sectional view of an epicyclic gear reducer, [ Fig. 3 ] there figure 3 is a perspective view of a cage and cage carrier assembly forming a reducer planet carrier, [ Fig. 4 ] there figure 4 is an axial sectional view of the planet carrier of the figure 3 , [ Fig. 5 ] there Figure 5 is a larger scale view of a detail of the figure 4 , [ Fig. 6 ] there figure 6 is an axial sectional view of a turbomachine module, comprising a reducer, a stator element, and an elastic member for connecting the reducer to the stator element according to the invention, [ Fig. 7 ] there figure 7 is an exploded perspective view of part of the module of the figure 6 , [ Fig. 8 ] there figure 8 is a perspective view of part of the module of the figure 6 , [ Fig. 9 ] there figure 9 is a cross-sectional view of a portion of the module of the figure 6 , [ Fig. 10 ] there figure 10 is a longitudinal sectional and perspective view of part of the module of the figure 6 , [ Fig. 11 ] there figure 11 is a larger scale view of a detail of the figure 9 and shows a finger equipped with vibration damping pads, [ Fig. 12 ] there figure 12 is a perspective view of the finger and skates of the figure 11 , [ Fig. 13 ] there figure 13 is a view similar to that of the figure 11 and shows an alternative embodiment of the vibration damping device equipped with a aforementioned “squeeze film” system, and [ Fig. 14 ] there figure 14 is a view similar to that of the figure 11 and shows another variant embodiment of the vibration damping device equipped with a aforementioned “squeeze film” system. Detailed description of the invention

[0019] There figure 1 describes a turbomachine 1 which comprises, in a conventional manner, a fan S, a low-pressure compressor 1a, a high-pressure compressor 1b, an annular combustion chamber 1c, a high-pressure turbine 1d, a low-pressure turbine 1e and an exhaust nozzle 1h. The high-pressure compressor 1b and the high-pressure turbine 1d are connected by a high-pressure shaft 2 and form with it a high-pressure (HP) body. The low-pressure compressor 1a and the low-pressure turbine 1e are connected by a low-pressure shaft 3 and form with it a low-pressure (LP) body.

[0020] The blower S is driven by a blower shaft 4 which is connected to the LP shaft 3 by means of a reducer 10. This reducer is generally of the planetary or epicyclic type.

[0021] Although the following description concerns a planetary or epicyclic type reducer, it also applies to a mechanical differential in which its three essential components, namely the planet carrier, the crown and the sun gear, are mobile in rotation, the rotation speed of one of these components depending in particular on the difference in speeds of the other two components.

[0022] The reducer 10 is positioned in the front part of the turbomachine. A fixed structure comprising schematically, here, an upstream part 5a and a downstream part 5b which composes the motor casing or stator 5 is arranged so as to form an enclosure E surrounding the reducer 10. This enclosure E is here closed upstream by seals at the level of a bearing allowing the fan shaft 4 to pass through, and downstream by seals at the level of the passage of the LP shaft 3.

[0023] There figure 2shows part of a reducer 10 which can take the form of different architectures depending on whether certain parts are fixed or rotating. At the input, the reducer 10 is connected to the LP shaft 3, for example via splines 7. Thus, the LP shaft 3 drives a planetary pinion called the sun gear 11. Conventionally, the sun gear 11, whose axis of rotation coincides with the X axis of the turbomachine, drives a series of pinions called satellites 12, which are equally distributed over the same diameter around the axis of rotation X. This diameter is equal to twice the operating center distance between the sun gear 11 and satellites 12. The number of satellites 12 is generally defined between three and seven for this type of application.

[0024] The set of satellites 12 is held by a frame called a planet carrier 13. Each satellite 12 rotates around its own Y axis, and meshes with the crown 14.

[0025] At the output of reducer 10, we have: o In an epicyclic configuration, the set of planet gears 12 rotates the planet carrier 13 around the axis X of the turbomachine. The ring gear 14 is fixed to the engine casing or stator 5 via a ring gear carrier 15 and the planet carrier 13 is fixed to the fan shaft 4. ∘ In a planetary configuration, the set of planet gears 12 is held by a planet carrier 13 which is fixed to the engine casing or stator 5. Each planet gear drives the ring gear which is attached to the fan shaft 4 via a ring gear carrier 15.

[0026] Each satellite 12 is mounted to rotate freely using a bearing 8, for example of the rolling bearing or hydrodynamic bearing type. Each bearing 8 is mounted on one of the axes 13a of the planet carrier 13 and all the axes are positioned relative to each other using one or more structural frames of the planet carrier 13. There are a number of axes and bearings equal to the number of satellites. For reasons of operation, assembly, manufacturing, control, repair or replacement, the axes 13a and the frame can be separated into several parts.

[0027] For the same reasons mentioned above, the teeth of a reducer can be separated into several helices. In our example we detail the operation of a 10 multi-helix reducer with a crown separated into two half-crowns: o A front half-crown 14a consisting of a rim 14aa and a half-fixing flange 14ab. On the rim 14aa is the front helix of the gear teeth. This front helix meshes with that of the satellite 12 which meshes with that of the sun gear 11. o A rear half-crown 14b consisting of a rim 14ba and a half-fixing flange 14bb. On the rim 14ba is the rear helix of the gear teeth. This rear helix meshes with that of the satellite 12 which meshes with that of the sun gear 11.

[0028] The half-flange 14ab of the front crown 14a and the half-flange 14bb of the rear crown 14b form the crown fixing flange 14c. The crown 14 is fixed to the crown carrier 15 by assembling the crown fixing flange 14c and the crown carrier fixing flange 15a using a bolted assembly for example. In the following, a half-flange may be called a flange.

[0029] The arrows of the figure 2 describe the routing of the oil in the reducer 10. The oil arrives in the reducer 10 from the stator part 5 in the distributor 16 by different means which will not be specified in this view because they are specific to one or more types of architecture. The distributor 16 is separated into two parts, generally each repeated by the same number of satellites. The injectors 17a have the function of lubricating the teeth, and the arms 17b have the function of lubricating the bearings 8. The oil is brought towards the injector 17a to exit through the end 17c in order to lubricate the teeth. The oil is also supplied to each arm 17b and circulates via the supply port 17d of the bearing 8. The oil then circulates through the axis 13a in one or more buffer zones 13b and then exits through orifices 13c in order to lubricate the bearings 8 of the satellites.

[0030] THE figures 3 to 5represent a planet carrier 30 of a planetary reducer, this planet carrier 30 being able to be of the monobloc type or with a cage and cage carrier as in the example shown.

[0031] The 30 satellite carrier figures 3 X to 5 comprises a cage 34 and a cage holder 42 connected by bearing links.

[0032] The cage 34 comprises two annular walls 36, 38 perpendicular to the axis X and connected at their external periphery by a cylindrical wall 40.

[0033] The cylindrical wall 40 is here of the double-skin type and comprises an outer skin 40a interrupted by the slots 43 and an inner skin 40b interrupted by the same slots 43. The outer skin 40a separated by five slots 43 forms five outer bridges and the inner skin 40b separated by five slots 43 forms five inner bridges. Each pair of inner and outer bridges form a yoke to accommodate a finger 44 of the cage holder 42. Otherwise, the bridges of each pair define between them a housing 46 for receiving a finger 44 of the cage holder 42. The bridges provide the structural connection between the walls 36 and 38. Slots 48 of oblong shape are made in at least one of the walls 36 and 38 so as to allow the finger 44 to pass between the inner and outer bridges.

[0034] The cylindrical wall 40 of the cage 34 thus comprises an annular row of housings 46. These housings 46 receive the axial fingers 44 secured to an annular body 50 of the cage holder 42. The body 50 is located at an axial end of the cage holder 42. The fingers 44 extend axially from the body 50 and are engaged by axial translation in the housings 46.

[0035] The thickness and width or radial section of the fingers 44, of the bridges, as well as the diameter of the axes 52 connecting these fingers to the bridges, are determined by calculation. The remaining space is best occupied between each satellite by controlling the thickness / width ratios. The slots 48 are only the resultant and have the same width as the space left between the outer and inner bridges.

[0036] Each finger 44 comprises, substantially in its middle, a recess 54 for mounting a bearing 56 intended to be crossed by the cylindrical axis 52 carried by the cage 34.

[0037] The recess 54 has a substantially radial orientation relative to the axis X. It has a generally cylindrical shape. The cage 34 and the axis 52 have a thickness, measured in a radial direction relative to the axis X, which is less than the inter-bridge distance or the radial thickness of the oblong slot 48, so as to be able to be engaged in this housing concomitantly with the finger 44 supporting these parts.

[0038] Each housing 46 is crossed by an axis 52 which has a substantially radial orientation relative to the axis X. Each axis 52 comprises a cylindrical body connected at an axial end, here radially internal, to a collar 52b. The axis 52 is here engaged by radial translation from the outside through radial orifices of the bridges, its collar 52b being intended to come into radial support on a flat face 58 of the external bridge of the cage 34. After insertion of the axis 52 into the orifices of the bridges, until the collar 52b is placed in support on the external bridge, the collar 52b is fixed to this bridge for example by screwing.

[0039] THE figures 6 to 12 represent a first embodiment of the invention which relates to an assembly comprising a planet carrier 130 and an elastically deformable annular member 160 for connecting this planet carrier to a stator element 162 of a turbomachine.

[0040] It is therefore understood that the invention applies to a speed reducer 110 with a planetary gear set, this type of reducer comprising a planet carrier which is fixed in the motor reference frame. In the present case, the planet carrier 130 is connected to the stator element 162 by a flexible connection formed by the member 160.

[0041] The stator element 162 is an input casing in the example shown. This input casing comprises two annular shells, respectively outer 162b and inner 162a, extending around each other and around the axis X. The shells are connected to each other by arms 164 extending radially relative to the axis X.

[0042] An inlet casing is, as its name indicates, arranged at the inlet of the engine and more precisely upstream of a compressor of the turbomachine and generally downstream of the fan S. The shells 162a, 162b define between them an annular flow vein for a gas flow, called the primary flow, for supplying the compressor.

[0043] In the example shown, the internal ferrule 162a comprises an annular fixing flange 162a1 at its upstream end and an annular fixing flange 162a2 at its downstream end.

[0044] The inner ferrule 162a further comprises at its inner periphery radial housings 166 for receiving teeth 180 of the cage holder 142. The housings 166 are here formed in projecting studs 168 located on the radially inner surface of the ferrule. The studs 168 are located on the same circumference centered on the axis X and each comprise an axial notch passing axially through them and opening radially inwards. These notches define the aforementioned housings 166 which are therefore open in the axial direction as well as in the radial direction inwards. They are delimited in the circumferential direction by lateral faces 168a facing the stud 168 as well as by a radially external face 168b formed by the bottom of the notch ( figure 11 ). Each of these faces 168a extends in a plane passing through the X axis.

[0045] The member 160 has a general U-shaped section whose opening is oriented radially outwards. This member comprises a first annular flange 170, here upstream, applied axially and fixed to the planet carrier 130, and a second annular flange 172, here downstream, configured to be applied axially and fixed to the stator element 162 and more precisely to its flange 162a2.

[0046] The external periphery of the flange 172 may comprise axial orifices 172a for the passage of fixing means of the screw-nut type for example. Advantageously, this flange 172 comprises a cylindrical rib 172b oriented downstream and configured to cooperate with an internal cylindrical surface of the flange 162a2 to ensure the centering of the member 160 with respect to the element 162 ( figure 10 ).

[0047] The external periphery of the flange 170 may comprise axial orifices 170a for the passage of screws which are screwed into threaded orifices 174 of the planet carrier 130. Advantageously, the flange 170 comprises a cylindrical rib 170b oriented upstream and configured to cooperate with an internal cylindrical surface of the planet carrier 130 to ensure the centering of the member 160 with respect to the planet carrier 130 ( figure 10 ).

[0048] The planet carrier 130 is of the type shown in figures 3 to 5and comprises a cage 134 and a cage holder 142. As mentioned with reference to these figures, the cage holder 142 comprises an annular body 150 extending around the axis X and carrying a series of projecting fingers 144 extending along the axis X and distributed around this axis X. Each finger 144 comprises at its free end opposite the body a recess 154 for mounting an axis 152 for the purpose of connecting the cage holder 142 to the cage 134, this cage 134 comprising at its periphery axial housings 146 in which the fingers 144 are received and which are crossed by the axes 152.

[0049] In the embodiment shown, the body 150 further carries a series of projecting teeth 180 extending substantially radially outwards relative to the axis X, and intended to be housed in the aforementioned housings 166 of the stator element 162. The teeth 180 and the fingers 144 are here formed in a single piece with the body.

[0050] The teeth 180 and the tapped holes 174 are here substantially located in the same plane P1 perpendicular to the axis X ( figures 6 And 10 ). The arms 164 have leading and trailing edges arranged respectively in planes P2 and P2' perpendicular to the X axis, the plane P1 being located between these planes P2 and P2'.

[0051] Each tooth 180 comprises two opposite lateral faces 180a, 180b capable of cooperating by abutment in the circumferential direction with the lateral faces 168a opposite the stator element 162 ( figure 11 ). Each of these faces 180a, 180b extends in a plane passing through the X axis.

[0052] As seen in the figure 11 , the faces 180a, 180b are not directly in contact with the faces 168a but are spaced in the circumferential direction from these faces. In the example shown, a pad 182 is attached to each of the faces 180a, 180b, for example in a recess of this face.

[0053] The function of the pad 182 is to isolate the tooth 180 and therefore the planet carrier 130 from the stator element 162 to prevent the transmission of vibrations between these parts during operation. The pad 182 is advantageously designed to dampen the vibrations to which the planet carrier is subjected during operation to prevent them from being transmitted to the element 162. The pad 182 may be made of any material suitable for performing this function, for example elastomer, composite, etc.

[0054] As seen in the figure 11 , the radially external end of each tooth 180 is located at a radial distance from the face 168b so that the tooth can slide in the radial direction in the housing 166. The pads 182 carried by the tooth 180 then slide on the lateral faces 168a of the housing 166.

[0055] As can be seen in the figures 7 to 9, the number of teeth 180 is different from the number of fingers 144. The number of teeth 180 is here 8 and is here greater than the number of fingers 144 which is here 5. Advantageously, the number of teeth 180 is equal to the number of arms 164 of the stator element 162 and the teeth are arranged according to these arms 164. In the example shown in figure 9 , the teeth 180 are regularly distributed and diametrically opposed two by two. This is the same for the arms of the element 162. Each tooth 180 is located in a plane P3 passing through the X axis and each arm is located in a plane P4 passing through the X axis. Each plane P3 is located halfway between two adjacent planes P4. Each plane P4 is located halfway between two adjacent planes P3.

[0056] THE figures 13 and 14show alternative embodiments of the invention in which the pads 182 are associated (but could be replaced) with damping oil films. Oil films are thus intended to be formed between the faces 168a, 180a, 180b, or between the pads 182 and the faces 168a. For this, the stator element 162 may comprise an internal conduit 190 for circulating oil and supplying oil to the faces 168a, 180a, 180b, as shown in figure 13 . In the variant shown in the figure 14 , the planet carrier 130 comprises an internal conduit 192 for circulating oil and supplying oil to the faces 168a, 180a, 180b.

[0057] There figure 10shows, by means of dotted arrows, the transmission of forces in operation between the planet carrier 130 and in particular the cage carrier 142 and the stator element 162. Forces, in particular torsional forces, pass from the cage carrier 142 via the member 160, which can deform elastically, to the stator element 162. In the event that these forces exceed a certain threshold and risk damaging the element 162, the cage carrier 142 would bear in the circumferential direction on the element 162 by means of the teeth 180 and the studs 168, which would make it possible to transmit these forces directly from the cage carrier to the element 162 without stressing the member 160.

Claims

1. An assembly comprising a planet carrier (130) for a planetary gear (110), an elastically deformable annular member (160) and a stator element (162), for a turbomachine, in particular for an aircraft, - the planet carrier (130) having a generally annular shape around an axis X, and - the annular member (160) extending around the axis X, this member being secured to the planet carrier and to said stator element (162) in order to ensure a flexible connection between the planet carrier and said stator element, characterized in that the planet carrier carries a series of protruding teeth (180) extending substantially radially outwards with respect to said axis X, each of these teeth comprising first lateral faces (180a, 180b) opposed in planes passing through the axis X and adapted to cooperate by abutment in the circumferential direction with said stator element, vibration damping systems, of the type vibration damping pads (182) and / or damping oil film, being interposed between said first faces and said stator element.

2. The assembly according to the preceding claim, wherein the planet carrier (130) is a single piece or comprises a cage (134) and a cage carrier (142).

3. The assembly according to the preceding claim, wherein the cage carrier (142) comprises an annular body (150) extending around the axis X and carrying the series of teeth (180) as well as a series of protruding fingers (144) extending along the axis X and distributed around this axis X, each of these fingers comprising at its free end opposite the body a recess (154) for mounting a shaft (152) in order to connect the cage holder to the cage, this cage (134) comprising at its periphery axial housings (146) in which the fingers (144) are received and which are traversed by the shafts (152).

4. The assembly according to the preceding claim, wherein the teeth (180) and the fingers (144) are at least partly formed in one piece with the body (150).

5. The assembly according to one of the preceding claims, wherein the planet carrier (130) comprises an internal conduit (192) for circulating oil and supplying oil to said first lateral faces (180a, 180b) in order to form a damping oil film at each of these faces.

6. The assembly according to one of the preceding claims, wherein said member (160) has a generally U-shaped cross-section with the opening facing radially outwards, this member comprising a first annular flange (170) applied axially and secured to the planet carrier (130), and a second annular flange (172) applied axially and secured to the stator element (162).

7. A turbomachine module, comprising an assembly according to one of the preceding claims, the stator element (162) comprising two annular shells, respectively external (162b) and internal (162a), extending around each other and around said axis X, the shells being connected to each other by arms (164), the internal shell extending at least partly around said planet carrier (130) and comprising at its internal periphery a series of housings (166) extending substantially radially and in which the teeth (180) of the planet carrier are engaged, these teeth being capable of moving radially in these housings and their first lateral faces (180a, 180b) being capable of abutting in the circumferential direction against second lateral faces (168a) opposite the housings.

8. The module according to claim 7, wherein the stator element (162) comprises damping pads on said second lateral faces (168a), and / or an internal conduit (190) for circulating oil and supplying oil to said second lateral faces (168a) in order to form a damping oil film between said first and second lateral faces (168a, 180a, 180b).

9. The module according to claim 7 or 8, wherein said arms (164) comprise leading edges located in a plane P2 perpendicular to said axis X and trailing edges located in a plane P2' perpendicular to said axis X, the housings (166) and the fingers (180) being located in a plane P1 located between the planes P2 and P2'.