Engine, in particular for a turbomachine, comprising a sealing device comprising a dynamic sealing track support with an integrated channel

Abstract

An engine (10) comprising a rotor shaft, an air chamber, a lubricant chamber comprising lubricant and at least one sealing device (20) arranged between said chambers and comprising an annular radial seal (21) associated with a seal track (31) borne by a dynamic sealing track support (30) secured to the rotor shaft (12). The dynamic sealing track support (30) comprises at least one lubricant distribution channel (37) configured to recover lubricant contained in the lubricant chamber and spray it by the effect of centrifugal force onto an inner heat exchange surface (35a) in the region of a spray zone located axially to the outside of the seal track (31) with respect to the lubricant chamber (15).

Description

[0001] DESCRIPTION

[0002] TITLE: Engine, in particular a turbomachine, comprising a sealing device comprising a dynamic sealing track support with integrated channel

[0003] Technical field of the invention

[0004] The present invention relates to the field of engines equipped with dynamic sealing, in particular to dynamic seals requiring cooling with a dedicated cooling system.

[0005] More particularly, the invention relates to rolling bearings and in particular the dynamic sealing of a bearing enclosure for a rotating shaft of a turbomachine, known as a "labyrinth oil seal" in English terms.

[0006] State of the prior art

[0007] As is known, a turbomachine comprises a certain number of rolling bearings which are intended to support the rotation of the rotor of the turbomachine, in particular relative to a fixed support, such as a casing.

[0008] In operation, oil is typically injected onto the bearings of these bearings to lubricate and cool them. To prevent oil from spreading throughout the engine, it is necessary to confine the rolling bearings within oil chambers and to ensure that these oil chambers are sealed from air chambers adjacent to the engine, which must be free of oil.

[0009] More specifically, some oil chambers are delimited between a shaft supported in rotation by the rolling bearing and an annular cover of the fixed support linked to the casing of the turbomachine and arranged around the shaft. A dynamic annular seal is generally positioned between the shaft and the cover to ensure a seal between the oil chamber and an air chamber adjacent to the latter. Typically, the dynamic seal is mounted inside a flange itself fixed to the cover.

[0010] In this regard, reference may be made to Figure 1 which illustrates a part of a motor 1 comprising a rotor shaft 2 supported in rotation by a rolling bearing 3 carried by a casing 4.

[0011] The turbomachine 1 further comprises an oil enclosure 5 “H” and an air enclosure 6 separate from the oil enclosure 5 and in which the oil must not escape from the oil enclosure 5.

[0012] The oil chamber 5 is delimited, radially by the rotor shaft 2 rotating around the axis of rotation XX and by an annular casing 7 or casing secured to the casing 4 of the motor 1.

[0013] The rolling bearing 3 comprises an inner ring 3a, an outer ring 3b and a plurality of rolling elements 3c arranged between said rings 3a, 3b.

[0014] The rolling bearing 3 is mounted in the oil chamber 5 and the inner ring 3a is mounted, for example by shrink fitting, directly or indirectly on the rotor shaft 2.

[0015] The outer ring 3b of the rolling bearing 3 is secured to a rolling bearing support 8 secured to the annular casing 7.

[0016] The rolling elements 3c here are balls.

[0017] The rolling bearing 3 is lubricated by oil injected into the oil chamber 5 in order to lubricate and cool the rolling elements 3c of the rolling bearing 3. As illustrated in FIG. 1, the motor 1 comprises a nozzle 9 configured to spray the oil onto the rolling bearing 3.

[0018] The engine 1 further comprises a sealing device E between the oil chamber 5 and the air chamber 6.

[0019] It is known to use dynamic seals for such use.

[0020] The dynamic seals typically used in turbomachine bearing oil chambers are segmented radial seals, acronym JRS, comprising a plurality of ring segments distributed circumferentially around a seal race or dynamic seal race rotating with the rotor shaft. These segments are in sliding contact with the dynamic seal race. The friction between the seal segments and the dynamic seal race generates heat which must be dissipated in order to maintain the mechanical integrity of these elements.

[0021] In order to cool the track of a dynamic seal, it is known to integrate a dedicated nozzle to directly supply oil to the dynamic seal track. The present invention does not relate to such dynamic seal cooling systems where the oil is supplied by direct jet from the upper part of the stator.

[0022] The invention relates exclusively to dynamic seal cooling systems in which the oil is supplied by a centrifugal or centripetal scoop.

[0023] Another known solution for cooling the dynamic sealing ring track is to route the oil through a system of channels after being captured by a centrifugal or centripetal oil recovery annular scoop, then the oil is projected by centrifugal force onto a deflector which guides it, thanks to an adequate slope towards the area of ​​the sealing ring to be cooled.

[0024] The deflector is usually mounted between the raceway of a dynamic seal and an inner ring of a bearing adjacent to the dynamic seal. The deflector ensures the proper supply of oil for cooling the raceway of dynamic seals requiring cooling.

[0025] Without a baffle, oil could not be routed to the dynamic seal track, rendering cooling non-functional.

[0026] The function of retaining the oil projected by centrifugation is thus ensured by the deflector generally mounted on the sealing track support. The oil flows over the rotating deflector, the internal slope of which is oriented so that the oil is directed towards the dynamic sealing track.

[0027] Document FR 3 107 310 - A1 is also known, which describes an oil distribution device in a rolling bearing comprising an oil distribution ring forming a single monobloc part with a track of a dynamic seal. Said part comprises a lubrication circuit forming a round trip along the length of the sealing track and opening onto an external cylindrical surface of the distribution ring at the level of the internal ring of a rolling bearing. Oil circulates in the lubrication circuit. The monobloc part is produced by additive manufacturing.

[0028] However, controlling the completion of the lubrication channels can be difficult.

[0029] Furthermore, such a single-piece part is complex to produce and requires an oil nozzle upstream of the distribution ring to bring the oil into the lubrication circuit. Finally, since the distribution ring comprises a radial conduit opening onto the external surface of said ring and into the lubrication circuit, there is a risk that the oil will be on the dynamic sealing track.

[0030] There is a need to improve known sealing devices.

[0031] Statement of the invention

[0032] The present invention therefore aims to overcome the aforementioned drawbacks.

[0033] The aim of the invention is therefore to simplify the support of the sealing track of a segmented radial seal while improving the heat exchange between the oil and the track of the segmented radial seal.

[0034] The invention also aims to avoid any contact between the oil and the dynamic sealing track and thus improve the sealing between the oil enclosure and the air enclosure.

[0035] The subject of the invention is an engine, in particular a turbomachine, comprising a rotor shaft mounted to rotate about an axis of rotation, in particular in a casing, an air enclosure, a lubricant enclosure comprising lubricant, in particular oil, and at least one sealing device arranged between the air enclosure and the lubricant enclosure.

[0036] Said sealing device comprises an annular radial seal associated with a seal track or dynamic sealing track carried by a dynamic sealing track support secured to the rotor shaft, for example by means of a supply or lubrication ring.

[0037] Said dynamic sealing track support comprises an internal heat exchange surface and a cylindrical external surface surrounding said internal surface and comprising the seal track.

[0038] The dynamic sealing track support comprises at least one lubricant distribution channel configured to recover lubricant contained in the lubricant enclosure and project it by the effect of centrifugal force onto the internal heat exchange surface of the dynamic sealing track support, at a projection zone located axially outside the seal track relative to the lubricant enclosure.

[0039] Said internal heat exchange surface has a slope inclined relative to the axis of rotation, configured to circulate the lubricant along said internal heat exchange surface towards the interior of the lubricant enclosure, so as to cool the seal track by conduction.

[0040] The circulation of lubricant along the inner surface of the dynamic seal raceway support from a projection area located axially outside the seal raceway relative to the lubricant enclosure allows the seal raceway to be effectively cooled and thus the annular seal to function properly.

[0041] The integration of one or more distribution channels directly on the dynamic sealing track support makes it possible to eliminate any additional deflector and thus reduce the total mass of the sealing device.

[0042] Cooling of the seal track is achieved solely by conduction across the entire internal surface of the annular seal.

[0043] The distribution channel(s) allows the lubricant to be projected by centrifugal force onto the internal surface of the sealing track support at the projection zone.

[0044] The inner surface of the seal raceway support is configured to allow oil to spread and circulate over the entire surface of the seal raceway.

[0045] In fact, the slope of the internal heat exchange surface allows the lubricant to flow along said internal surface and to be charged with calories coming from the seal track to be cooled.

[0046] The seal track is thus cooled by conduction from the internal heat exchange surface.

[0047] After circulating along said internal surface of the support, the lubricant loaded with calories is projected by centrifugal force onto the walls of the lubricant enclosure.

[0048] The sealing device is thus intended to ensure a seal between the lubricant enclosure, in particular the oil enclosure, and the air enclosure which must be free of oil.

[0049] The seal raceway forms a contact surface in sliding radial contact with the annular seal.

[0050] The dynamic sealing is achieved between the respective cooperating cylindrical surfaces of the ring of segments and the contact surface of the seal raceway.

[0051] Thanks to the invention, it is possible to eliminate a part in the rolling bearing enclosure whose role is to ensure the correct supply of oil for cooling the track of the dynamic seals requiring cooling.

[0052] In fact, the invention makes it possible to do without a part, i.e. the deflector, by adapting an existing part.

[0053] This allows the overall mass of the sealing device to be reduced while maintaining good heat exchange between the oil and the seal raceway.

[0054] Advantageously, the internal heat exchange surface of the dynamic sealing track support extends over 360°.

[0055] The dynamic sealing track support is preferably devoid of any orifice opening onto the external surface of the dynamic sealing track support comprising the seal track, so that the lubricant circulating on the internal heat exchange surface cannot end up on the external surface, or even the seal track.

[0056] In other words, the lubricant flows only under the seal raceway, along the inner surface of the second part of the dynamic seal raceway support.

[0057] In other words, the oil is not in direct contact with the O-ring.

[0058] In fact, the air chamber must remain free of lubricant because any rise of lubricant in certain compartments of the engine would be detrimental to the proper functioning of the engine.

[0059] Advantageously, the external cylindrical surface of the sealing track support is parallel to the axis of rotation.

[0060] According to one embodiment, the dynamic sealing track support has a generally annular shape around the axis of rotation and has a tapered section, for example, in the shape of a pinhead, comprising a radial base secured to the rotor shaft and a tapered axial portion. Said tapered axial portion comprises a first axial portion extending axially from the radial base to an outer end of the first axial portion located axially outside the annular seal relative to the lubricant enclosure and a second axial portion extending to a free end from the outer end of the first axial portion in the direction of the interior of the lubricant enclosure, the first and second axial portions delimiting between them an annular cavity extending over 360°, the second axial portion comprising the internal heat exchange surface and the external surface carrying the seal track.

[0061] In other words, the first and second axial parts extend in two opposite axial directions.

[0062] For example, the first axial part is radially delimited by a cylindrical internal surface and a cylindrical external surface.

[0063] Each cylindrical surface of the first axial part has a slope inclined towards the lubricant enclosure.

[0064] Advantageously, the thickness of the second axial part of the dynamic sealing track support decreases progressively from towards the free end of the second axial part.

[0065] For example, the lubricant distribution channel(s) extend from the radial base along the first axial portion towards the outer end of said first axial portion.

[0066] Advantageously, each lubricant distribution channel comprises a first radial portion and a second axial portion. The first radial portion extends from the base in a radial direction, preferably substantially oblique, and the second axial portion extends from the first portion in an inclined axial direction.

[0067] For example, the lubricant distribution channels are regularly spaced around the axis of rotation.

[0068] For example, the dynamic sealing track support may comprise up to ten channels. The channels may have a circular cross-section. Their cross-section may also vary along the axial axis. Alternatively, the channels could have a cross-section other than circular.

[0069] For example, each lubricant distribution channel is made directly on the dynamic sealing track support by additive manufacturing.

[0070] Advantageously, the channel(s) are made in one piece, i.e. in one piece, with the body of the dynamic sealing track support.

[0071] According to one embodiment, the engine comprises an annular recovery scoop extending around the shaft and arranged in the lubricant enclosure and configured to collect the lubricant projected by centrifugal force, the lubricant then being able to be captured by the distribution channel(s) and to circulate in said channels until being projected by centrifugal force onto the internal heat exchange surface.

[0072] For example, the seal raceway may be treated or include a particular outer coating to improve sliding between the seal and the seal raceway and minimize wear of said annular seal.

[0073] According to one embodiment, the annular seal is composed of a static ring of ring segments, in particular made of carbon, held together, for example using a circumferential spring and one or more axial springs, in an annular flange mounted inside an envelope secured to the casing.

[0074] According to one embodiment, the motor comprises at least one rolling bearing mounted in the casing and supporting the rotor shaft, the dynamic sealing track support being rotationally secured to the rotor shaft.

[0075] For example, the rolling bearing comprises an inner ring, an outer ring and a plurality of rolling elements disposed between said rings.

[0076] The rolling bearing is advantageously mounted in the lubricant enclosure and the inner ring is mounted, for example by shrink fitting, directly or indirectly on the rotor shaft.

[0077] For example, the outer ring of the rolling bearing is secured to a rolling bearing support secured to the annular casing.

[0078] In a non-limiting manner, the rolling elements are rollers. Alternatively, other types of rolling elements could also be provided or the rolling bearing could be a plain bearing, without rolling elements.

[0079] For example, the rolling bearing is lubricated by the lubricant, including oil supplied into the lubricant chamber to lubricate and cool the rolling elements of the rolling bearing.

[0080] For example, the inner ring of the rolling bearing includes a feed ramp configured to deliver oil to the raceway.

[0081] Alternatively, any other system could be provided for lubricating the rolling bearing. The lubrication of the rolling bearing is carried out in a manner known per se and will not be described further in the remainder of the description.

[0082] For example, the sealing device further comprises a labyrinth seal disposed on the inner side of the annular seal relative to the lubricant chamber, mounted radially between the rotor shaft and the housing, the labyrinth seal being in radial contact with the outer surface of the dynamic sealing track support carrying the seal track.

[0083] The labyrinth seal is, for example, carried by an axial part of an annular flange carrying the annular seal.

[0084] Brief description of the drawings

[0085] Other aims, characteristics and advantages of the invention will appear on reading the following description, given solely by way of non-limiting example, and made with reference to the indexed drawings in which:

[0086] [Fig 1], is a schematic axial sectional view of an engine according to the prior art;

[0087] [Fig 2] is a schematic axial sectional view of a turbomachine comprising a device for cooling a track of a dynamic seal according to the invention; and

[0088] [Fig 3] is a detail view of Figure 1.

[0089] Detailed description of at least one embodiment

[0090] In the remainder of the description, the terms “axial” and “radial” are defined relative to an axis of rotation Xl -Xl of a rotor of a turbomachine engine 10.

[0091] Generally, the invention relates to any motor comprising at least one segmented rotor seal requiring cooling.

[0092] As illustrated in Figure 2, the turbomachine 10 comprises a rotor shaft 12 supported in rotation by a rolling bearing 13 carried by a casing (not shown).

[0093] The turbomachine 10 further comprises an oil enclosure 15 and an air enclosure 16 separate from the oil enclosure 15 and in which a lubricant, in particular oil, must not escape from the oil enclosure 15.

[0094] The oil enclosure 15 is delimited, radially by the rotor shaft 12 rotating around the axis of rotation Xl -Xl and by an annular casing (not shown) or casing secured to the casing of the turbomachine 10.

[0095] The rolling bearing 13 comprises an inner ring 13a, an outer ring 13b and a plurality of rolling elements 13c arranged between said rings 13a, 13b.

[0096] The rolling bearing 13 is mounted in the oil chamber 15 and the inner ring 13a is mounted, for example by shrink fitting indirectly on the rotor shaft 12 via a supply ring 14.

[0097] Alternatively, it could be provided that the inner ring of the rolling bearing is mounted directly on the rotor shaft 12, without an intermediate element.

[0098] The outer ring 13b of the rolling bearing 13 is secured to a rolling bearing support (not shown) secured to the annular casing.

[0099] In a non-limiting manner, the rolling elements 13c are here rollers. Alternatively, other types of rolling elements could also be provided or the rolling bearing could be a plain bearing, without rolling elements.

[0100] The rolling bearing 13 is lubricated by a lubricant, in particular oil supplied into the oil chamber 15 in order to lubricate and cool the rolling elements 13c of the rolling bearing.

[0101] 13. As illustrated in Figure 2, turbomachine 10 comprises a centrifugal scoop (not shown) intended to recover the oil and feed a feed ramp 14a made in the feed ring

[0102] 14. Alternatively, any other system could be provided for lubricating the rolling bearing 13. The lubrication of the rolling bearing 13 is carried out in a manner known per se and will not be described further in the remainder of the description.

[0103] The turbomachine 10 further comprises a sealing device 20 intended to ensure a seal between the oil enclosure 15 and the air enclosure 16 which must be free of oil.

[0104] The sealing device 20 is arranged between the rotor shaft 12 and the turbomachine casing 10, in particular the casing of the oil enclosure 15, at the separation between the oil enclosure 15 and the air enclosure 16.

[0105] For this purpose, the sealing device 20 comprises in particular an annular radial seal 21.

[0106] The annular seal 21 is composed of a static ring of ring segments (not visible in the figures), in particular made of carbon, held together using a circumferential spring 22.

[0107] The annular seal 21 is held in an annular flange 23 mounted inside the casing.

[0108] The flange 23 comprises a part 23a of L-shaped section which receives the annular seal 21.

[0109] The annular seal 21 is held in the flange 23 by the circumferential spring 22 and by axial springs 24.

[0110] The axial springs 24 are axially supported on a support 25 held on the flange 23 by a stop joint 26.

[0111] The ring of segments 21 is blocked tangentially by pins 27.

[0112] The annular seal 21 is associated with a seal track 31 or dynamic sealing track which is rotating and carried by the rotor shaft 12.

[0113] The seal track 31 forms a contact surface in sliding radial contact with the annular seal 21.

[0114] The seal track 31 may be treated or comprise a particular external coating to improve the sliding between the seal 21 and the seal track 31 and minimize the wear of said annular seal 21. The sealing device 20 also comprises a labyrinth seal 28 arranged downstream of the annular seal 21, mounted radially between the rotor shaft 12 and the casing. The labyrinth seal 28 is in radial contact with the seal track 31.

[0115] The labyrinth seal 28 is carried by a second axial part 23b of the annular flange 23.

[0116] The dynamic sealing is achieved between the respective cooperating cylindrical surfaces of the ring of segments 21 and the contact surface of the seal track 31.

[0117] In a non-limiting manner, bearing grooves could be provided on the contact surface of the joint track 31 in order to improve the bearing capacity.

[0118] The annular casing fixes the static part of the sealing device 20 on the casing of the turbomachine 10.

[0119] The sealing device 20 further comprises a dynamic sealing track support 30.

[0120] The dynamic sealing track support 30 is rotationally secured to the rotor shaft 12, in particular via the feed ring 14, and located downstream of the rolling bearing 13.

[0121] The dynamic sealing track support 30 has a generally annular shape around the axis XI-XI and has a tapered pinhead-shaped section.

[0122] The dynamic sealing track support 30 comprises a radial base 32 secured to the rotor shaft 12, in particular to the feed ring 14, and a tapered axial part 33 comprising a first axial part 34 extending axially from the radial base 32 to an outer end 34e of the first axial part 34 located axially outside the annular seal 21 relative to the lubricant enclosure 15.

[0123] The tapered axial portion 33 further comprises a second axial portion 35 extending to a free end 35i from the outer end 34e of the first axial portion 34 towards the lubricant enclosure 15.

[0124] The first and second axial parts 34, 35 extend in two opposite axial directions and delimit between them an annular cavity 36 extending over 360°.

[0125] The first axial portion 34 is radially delimited by a cylindrical inner surface 34a and a cylindrical outer surface 34b. Each cylindrical surface 34a, 34b of the first axial portion 34 has a slope inclined towards the lubricant enclosure 15.

[0126] The second axial portion 35 is radially delimited by a cylindrical internal surface 35a and a cylindrical external surface 35b.

[0127] The outer cylindrical surface 35b carries the seal track 31.

[0128] In other words, the seal track 31 radially in contact with the annular seal 21 is carried by the external cylindrical surface 35b of the second axial part 35.

[0129] Generally, the seal track 31 is formed on the cylindrical outer surface 35b of the dynamic seal track support 30.

[0130] The external cylindrical surface 35b of the second axial part 35 is parallel to the axis of rotation XI-XI and the internal cylindrical surface 35a of the second axial part 35 has a slope inclined relative to the axis of rotation Xl-Xl, so that the thickness of the second axial part 35 decreases progressively in the direction of the free end 35i of the second axial part 35.

[0131] The dynamic sealing track support 30 further comprises one or more oil distribution channels 37 added to said support 30, for example by additive manufacturing.

[0132] The channels 37 extend axially from the radial base 32 along the first axial portion 34 towards the outer end 34e of said first axial portion 34 at a projection zone located axially outside the seal track 31 relative to the lubricant enclosure 15. As illustrated, said projection zone is located axially upstream of the seal track 31. However, in a variant configuration symmetrical to that illustrated in which the outside of the seal is located on the downstream side, said projection zone would be located axially downstream of the seal track 31. Thus, the projection zone is defined as a function of the lubricant enclosure 15.

[0133] The path of the oil in the dynamic sealing track support 30 is represented by the arrow H.

[0134] The oil present in the oil chamber 15, for example recovered by centrifugal force using an annular recovery scoop (not shown) extending around the shaft 12 and configured to collect the oil projected by the centrifugal force, is captured by the channels 37 and circulates to the outer end 34e of the first axial part 34.

[0135] The oil is then projected by centrifugal force onto the internal surface 35a of the second axial part 35.

[0136] The cylindrical internal surface 35a of the second axial part 35 forms a heat exchange surface extending over 360°.

[0137] The slope of the inner surface 35a of the second axial part 35 allows the oil to flow along said inner surface 35a towards the inside of the lubricant enclosure 15 and to be charged with calories coming from the seal track 31 to be cooled. The seal track 31 is thus cooled by conduction of the inner surface 35a of the second axial part 35.

[0138] The circulation of the oil along the inner surface 35a of the second axial portion 35 from the projection area located axially outside the seal raceway 31 relative to the lubricant enclosure 15 allows the seal raceway 31 to be efficiently cooled and thus the annular seal to operate correctly.

[0139] After having circulated along said internal surface 35a, the oil loaded with calories is projected by centrifugal force onto the walls of the oil enclosure 15.

[0140] In a non-limiting manner, each channel 37 comprises a first radial part 37a, slightly oblique, and a second axial part 37b, slightly inclined relative to the axis of rotation X l -Xl.

[0141] The first radial part 37a of the channels 37 is made in the radial base 32 and the second axial part 37b of the channels 37 is made in the first axial part 34.

[0142] The channels 37 can be regularly spaced around the axis of rotation Xl -X l

[0143] The joint track support 30 may comprise up to ten channels 37.

[0144] The channels 37 have a circular cross-section. Their cross-section may also change along the axial axis. Alternatively, the channels 37 could have a cross-section other than circular.

[0145] The second axial part 35 is devoid of any through orifice, so that the oil circulating on its internal surface 35a cannot end up on the external surface 35b, or even the seal track 31.

[0146] In other words, the oil circulates only under the seal track 31, along the internal surface 35a of the second part 35 of the dynamic sealing track support 30 towards the lubricant enclosure 15.

[0147] In other words, the oil is not in direct contact with the annular seal 21, nor with the seal track 31.

[0148] In fact, the air enclosure must remain free of oil because any rise of oil in certain compartments of the turbomachine would be detrimental to the proper functioning of the turbomachine.

[0149] The integration of the distribution channels directly on the dynamic sealing track support 30 makes it possible to eliminate any additional deflector and thus reduce the total mass of the sealing device.

[0150] Cooling of the seal track 31 is achieved solely by conduction across the entire internal surface of the annular seal 21.

[0151] The distribution channels 37 make it possible to project the oil by centrifugal force axially onto the internal surface 35a of the second part 35 of the sealing track support 30 upstream of the annular seal 21.

[0152] The inner surface 35a of the second portion 35 of the sealing track support 30 is configured to allow spreading and circulation of the oil over the entire surface of the seal track 31.

[0153] Advantages of the present invention include compactness of the dynamic sealing track support, elimination of parts resulting in weight reduction and increased efficiency of the dynamic seal.

Claims

CLAIMS 1. Engine, in particular a turbomachine (10), comprising a rotor shaft (12) mounted to rotate about an axis of rotation (Xl-Xl), an air chamber (16), a lubricant chamber (15) comprising lubricant, in particular oil, and at least one sealing device (20) arranged between the air chamber (16) and the lubricant chamber (15), said sealing device (20) comprising an annular radial seal (21) associated with a seal track (31) carried by a dynamic sealing track support (30) secured to the rotor shaft (12), said dynamic sealing track support (30) comprising an internal heat exchange surface (35a) and a cylindrical external surface (35b) surrounding said internal surface (35a) and comprising the seal track (31),characterized in that the dynamic sealing track support (30) comprises at least one lubricant distribution channel (37) configured to recover lubricant contained in the lubricant enclosure (15) and project it by the effect of centrifugal force onto the internal heat exchange surface (35a) of the dynamic sealing track support (30), at a projection zone located axially outside the seal track (31) relative to the lubricant enclosure (15), and in that said internal heat exchange surface (35a) has a slope inclined relative to the axis of rotation (Xl-Xl), configured to circulate the lubricant along said internal heat exchange surface (35a) towards the interior of the lubricant enclosure (15) so as to cool the seal track (31) by conduction., 2. Engine according to claim 1, wherein the internal heat exchange surface (35a) of the dynamic sealing track support (30) extends over 360°.

3. Engine according to claim 1 or 2, in which the dynamic sealing track support (30) is devoid of any orifice opening onto the external surface (35b) of the dynamic sealing track support (30) comprising the seal track (31).

4. Motor according to any one of the preceding claims, wherein the external cylindrical surface (35b) of the sealing track support (30) is parallel to the axis of rotation (Xl-Xl).

5. Engine according to any one of the preceding claims, in which the dynamic sealing track support (30) has a generally annular shape around the axis of rotation (Xl-Xl) and has a section of shape tapered comprising a radial base (32) integral with the rotor shaft (12) and a tapered axial portion (33), said tapered axial portion (33) comprising a first axial portion (34) extending axially from the radial base (32) to an outer end (34e) of the first axial portion (34) located axially outside the annular seal (21) relative to the lubricant enclosure (15) and a second axial portion (35) extending to a free end (35i) from the outer end (34e) of the first axial portion (34) towards the inside of the lubricant enclosure (15), the first and second axial portions (34, 35) delimiting between them an annular cavity (36) extending over 360°, the second axial part (35) comprising the internal heat exchange surface (35a) and the external surface (35b) carrying the seal track (31).

6. Engine according to claim 5, wherein the thickness of the second axial part (35) of the dynamic sealing track support (30) decreases progressively in the direction of the free end (35i) of the second axial part (35).

7. Engine according to claim 5 or 6, wherein the lubricant distribution channel(s) (37) extend from the radial base (32) along the first axial portion (34) towards the outer end (34e) of said first axial portion (34).

8. Engine according to claim 7, wherein each lubricant distribution channel (37) comprises a first radial portion (37a) and a second axial portion (37b).

9. Engine according to any one of the preceding claims, in which the lubricant distribution channels (37) are regularly spaced around the axis of rotation (Xl -Xl).

10. Engine according to any one of the preceding claims, in which each lubricant distribution channel (27) is produced in the dynamic sealing track support (30) by additive manufacturing. 1 1. Engine according to any one of the preceding claims, comprising an annular recovery scoop extending around the shaft (12) and arranged in the lubricant enclosure (15) and configured to collect the lubricant projected by centrifugal force, the lubricant then being able to be captured by the distribution channel(s) (37) and to circulate in said channels (37) until it is projected by centrifugal force onto the internal surface (35a) heat exchange.

12. Motor according to any one of the preceding claims, in which the annular seal (21) is composed of a static ring of ring segments, in particular made of carbon, held together in an annular flange (23) mounted inside an envelope secured to the motor casing.

13. Motor according to any one of the preceding claims, comprising at least one rolling bearing (13) mounted in the casing and supporting the rotor shaft (12), the dynamic sealing track support (30) being rotationally secured to the rotor shaft (12).

14. Motor according to any one of the preceding claims, in which the sealing device (20) also comprises a labyrinth seal (28) arranged on the inner side of the annular seal (21) relative to the lubricant enclosure (15), mounted radially between the rotor shaft (12) and the casing, the labyrinth seal (28) being in radial contact with the external surface (35a) of the dynamic sealing track support (30) carrying the seal track

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