Engine, particularly turbomachinery, comprising a sealing device including a support for an integrated channel dynamic sealing track

Abstract

Motor (10) comprising a rotor shaft, an air chamber, a lubricant chamber containing lubricant, and at least one sealing device (20) disposed between said chambers and comprising an annular radial seal (21) associated with a seal track (31) carried by a dynamic seal track support (30) integral with the rotor shaft (12). The dynamic seal track support (30) comprises at least one lubricant distribution channel (37) configured to recover lubricant contained in the lubricant chamber and project it by the effect of centrifugal force onto an internal heat exchange surface (35a) at a projection zone located axially outside the seal track (31) relative to the lubricant chamber (15). Figure for abbreviation: [Fig 3]

Description

Title of the invention: Engine, in particular a turbomachine, comprising a sealing device including a support for a dynamic sealing track with an integrated channel Technical field of the invention

[0001] 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.

[0002] More particularly, the invention relates to rolling bearings and in particular the dynamic sealing of a rotating shaft bearing enclosure of a turbomachine, known as a "labyrinth oil seal" in Anglo-Saxon terms. Prior art

[0003] In a known manner, a turbomachine includes a number of roller bearings which are intended to support the rotation of the turbomachine rotor, in particular with respect to a fixed support, such as a casing.

[0004] During 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 bearings within oil enclosures and to ensure that these oil enclosures are sealed against adjacent air enclosures of the engine, which must be free of oil.

[0005] More specifically, certain oil chambers are delimited between a shaft supported for rotation by the roller bearing and an annular cover of the fixed support attached to the turbomachine housing and disposed 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 adjacent air chamber. Typically, the dynamic seal is mounted inside a flange which is itself fixed to the cover.

[0006] Reference can be made in this regard to [Fig. 1] which illustrates part of a motor 1 comprising a rotor shaft 2 supported in rotation by a bearing 3 carried by a casing 4.

[0007] The turbomachine 1 further comprises an oil chamber 5 "H" and an air chamber 6 separate from the oil chamber 5 and in which the oil must not escape from the oil chamber 5.

[0008] The oil enclosure 5 is delimited radially by the rotor shaft 2 rotating around the axis of rotation XX and by an annular casing 7 or casing attached to the housing 4 of the motor 1.

[0009] The bearing housing 3 comprises an inner ring 3a, an outer ring 3b and a plurality of rolling elements 3c arranged between said rings 3a, 3b.

[0010] The 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.

[0011] The outer ring 3b of the bearing 3 is integral with a bearing support 8 integral with the annular casing 7.

[0012] The rolling elements 3c are here balls.

[0013] The bearing 3 is lubricated by oil injected into the oil chamber 5 in order to lubricate and cool the rolling elements 3c of the bearing 3. As illustrated in [Fig.1], the motor 1 includes a nozzle 9 configured to spray the oil onto the bearing 3.

[0014] The engine 1 further includes a sealing device E between the oil chamber 5 and the air chamber 6.

[0015] It is known to use dynamic joints for such an application.

[0016] Dynamic seals typically used in turbomachinery bearing oil chambers are segmented radial seals, abbreviated as JRS, comprising a plurality of ring segments distributed circumferentially around a seal track or dynamic sealing track rotating with the rotor shaft. These segments are in sliding contact with the dynamic sealing track. Friction between the seal segments and the dynamic sealing track generates heat that must be dissipated to maintain the mechanical integrity of these elements.

[0017] 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 a direct jet from the top of the stator.

[0018] The invention relates exclusively to the cooling systems for dynamic seals in which the oil is supplied by a centrifugal or centripetal scoop.

[0019] Another known solution for cooling the dynamic sealing annular track is to convey the oil through a system of channels after it has been captured by a centrifugal or centripetal annular oil recovery scoop, then the oil is projected by centrifugal force onto a deflector which guides it, by means of an appropriate slope, towards the area of ​​the sealing track to be cooled.

[0020] The deflector is generally mounted between the raceway of a dynamic seal and an inner ring of a bearing adjacent to the dynamic seal. The deflector ensures proper oil supply for cooling the raceway of dynamic seals requiring cooling.

[0021] Without a deflector, the oil could not be conveyed to the runway level dynamic sealing, rendering the cooling system inoperative.

[0022] The function of retaining the oil projected by centrifugal force is thus ensured by the deflector, which is 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.

[0023] French patent document FR 3 107 310 - A1 also describes an oil distribution device in a rolling bearing comprising an oil distribution ring forming a single, monobloc piece with a dynamic seal raceway. This piece includes a lubrication circuit forming a reciprocating path along the length of the sealing raceway and opening onto an external cylindrical surface of the distribution ring at the level of the inner ring of a rolling bearing. Oil circulates in the lubrication circuit. The monobloc piece is manufactured by additive manufacturing.

[0024] However, controlling the construction of the lubrication channels can prove difficult.

[0025] Furthermore, such a one-piece component is complex to manufacture and requires an oil jet upstream of the timing ring to supply oil to the lubrication circuit. Finally, since the timing ring includes a radial conduit opening onto the outer surface of said ring and into the lubrication circuit, there is a risk that oil may be found on the dynamic sealing surface.

[0026] There is a need to improve known sealing devices. Description of the invention

[0027] The present invention therefore aims to overcome the aforementioned drawbacks.

[0028] 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.

[0029] The invention also aims to avoid any contact between the oil and the dynamic sealing track and thus improve the sealing between the oil chamber and the air chamber.

[0030] The invention relates to 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 chamber, a lubricant chamber comprising lubricant, in particular oil, and at least one sealing device disposed between the air chamber and the lubricant chamber.

[0031] Said sealing device comprises an annular radial seal associated with a seal track or dynamic sealing track carried by a dynamic sealing track support integral with the rotor shaft, for example via a feed or lubrication ring.

[0032] Said dynamic sealing track support comprises an internal heat exchange surface and an external cylindrical surface surrounding said internal surface and comprising the sealing track.

[0033] The dynamic sealing track support includes at least one lubricant distribution channel configured to recover lubricant contained in the lubricant chamber and project it by the effect of centrifugal force onto the internal heat exchange surface of the dynamic sealing track support, at the level of a projection zone located axially outside the sealing track relative to the lubricant chamber.

[0034] Said internal heat exchange surface has an inclined slope with respect to the axis of rotation, configured to circulate the lubricant along said internal heat exchange surface towards the inside of the lubricant enclosure, so as to cool the seal track by conduction.

[0035] The circulation of the lubricant along the internal surface of the dynamic sealing track support from a projection zone located axially outside the sealing track relative to the lubricant chamber allows the sealing track to be efficiently cooled and thus the annular seal to function correctly.

[0036] The integration of one or more distribution channels directly onto the dynamic sealing track support makes it possible to eliminate any additional deflector and thus reduce the total mass of the sealing device.

[0037] The cooling of the joint track is achieved solely by conduction across the entire internal surface of the annular joint.

[0038] The distribution channel(s) allows the lubricant to be projected by centrifugal force onto the internal surface of the sealing track support at the level of the projection area.

[0039] The internal surface of the sealing track support is configured to allow oil to spread and circulate over the entire surface of the sealing track.

[0040] Indeed, the slope of the internal heat exchange surface allows the lubricant to flow along said internal surface and to be charged with heat from the joint track to be cooled.

[0041] The joint track is thus cooled by conduction from the internal heat exchange surface.

[0042] After circulating along said internal surface of the support, the heat-charged lubricant is projected by centrifugal force onto the walls of the lubricant enclosure.

[0043] The sealing device is thus intended to ensure a seal between the lubricant enclosure, in particular oil-filled, and the air enclosure which must be free of oil.

[0044] The joint track forms a contact surface in sliding radial contact with the annular seal.

[0045] Dynamic sealing is achieved between the cooperating cylindrical surfaces res- prospects of the segment ring and the contact surface of the joint track.

[0046] Thanks to the invention, it is possible to eliminate a part in the bearing housing whose role is to ensure the proper supply of oil for cooling the track of the dynamic seals which need to be cooled.

[0047] Indeed, the invention makes it possible to do without a part, i.e. the deflector, by adapting an existing part.

[0048] This makes it possible to reduce the overall mass of the sealing device while maintaining good heat exchange between the oil and the sealing track.

[0049] Advantageously, the internal heat exchange surface of the dynamic sealing track support extends over 360°.

[0050] The dynamic sealing track support is preferably devoid of any opening onto the external surface of the dynamic sealing track support including the sealing track, so that the lubricant circulating on the internal heat exchange surface cannot end up on the external surface, or even the sealing track.

[0051] In other words, the lubricant circulates only under the seal track, along the internal surface of the second part of the dynamic sealing track support.

[0052] In other words, the oil is not in direct contact with the annular seal.

[0053] Indeed, the air chamber must remain free of lubricant because any rise of lubrication Breaking down in certain engine compartments would be detrimental to the proper functioning of the engine.

[0054] Advantageously, the external cylindrical surface of the sealing track support is parallel to the axis of rotation.

[0055] According to one embodiment, the dynamic sealing track support has a generally annular shape around the axis of rotation and has a tapered cross-section, for example, pinhead-shaped, comprising a radial base integral with 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 housing, and a second axial portion extending to a free end from the outer end of the first axial portion towards the interior of the lubricant housing. The first and second axial portions define between them an annular cavity extending over 360°. The second axial portion comprises the internal heat exchange surface and the external surface bearing the sealing track.

[0056] In other words, the first and second axial parts extend along two opposite axial directions.

[0057] For example, the first axial part is radially delimited by a surface internal cylindrical surface and external cylindrical surface.

[0058] Each cylindrical surface of the first axial part has a slope inclined towards the lubricant chamber.

[0059] Advantageously, the thickness of the second axial part of the dynamic sealing track support is progressively decreasing from towards the free end of the second axial part.

[0060] For example, the lubricant distribution channel(s) extend from the radial base along the first axial part towards the outer end of said first axial part.

[0061] 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.

[0062] For example, the lubricant distribution channels are regularly spaced around the axis of rotation.

[0063] 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 change along the axial axis. Alternatively, the channels could have a cross-section other than circular.

[0064] For example, each lubricant distribution channel is made directly on the dynamic sealing track support by additive manufacturing.

[0065] Advantageously the channel or channels are made of material, i.e. monobloc, with the body of the dynamic sealing track support.

[0066] According to one embodiment, the engine includes an annular recovery scoop extending around the shaft and disposed in the lubricant housing and configured to collect the lubricant projected by the centrifugal force, the lubricant then being able to be captured by the distribution channel(s) and to circulate in said channels until it is projected by the centrifugal force onto the internal heat exchange surface.

[0067] For example, the joint track may be treated or include a special outer coating to improve sliding between the seal and the joint track and minimize wear on said annular seal.

[0068] 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 by means of a circumferential spring and one or more axial springs, in an annular flange mounted inside a casing attached to the housing.

[0069] According to one embodiment, the motor comprises at least one bearing mounted in the housing and supporting the rotor shaft, the dynamic sealing track support is rotationally fixed to the rotor shaft.

[0070] For example, the bearing includes an inner ring, an outer ring and a plurality of rolling elements arranged between said rings.

[0071] The bearing is advantageously mounted in the lubricant housing and the inner ring is mounted, for example by shrink fitting, directly or indirectly on the rotor shaft.

[0072] For example, the outer ring of the bearing is integral with a bearing support integral with the annular casing.

[0073] Without limitation, the rolling elements are rollers. Alternatively, other types of rolling elements could also be provided, or the bearing could be a plain bearing, without rolling elements.

[0074] For example, the bearing is lubricated by the lubricant, in particular oil supplied into the lubricant chamber in order to lubricate and cool the rolling elements of the bearing.

[0075] For example, the inner ring of the bearing includes a feed ramp configured to bring oil onto the raceway.

[0076] Alternatively, any other system could be provided for lubricating the bearing. The lubrication of the bearing is carried out in a manner known per se and will not be described further in the remainder of this description.

[0077] For example, the sealing device further includes a labyrinth seal disposed on the inner side of the annular seal relative to the lubricant housing, 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.

[0078] The labyrinth seal is, for example, carried by an axial part of an annular flange carrying the annular seal. Brief description of the drawings

[0079] Other objects, features and advantages of the invention will become apparent from the following description, given solely by way of non-limiting example, and made with reference to the indexed drawings in which:

[0080] [Fig.1], is a schematic axial cross-sectional view of an engine according to the prior art;

[0081] [Fig.2], is a schematic axial cross-sectional view of a turbomachine comprising a cooling device for a track of a dynamic seal according to the invention; and

[0082] [Fig.3] is a detailed view of [Fig. 1].

[0083] Detailed description of at least one embodiment

[0084] In the following description, the terms "axial" and "radial" are defined with respect to an axis of rotation XI-XI of a rotor of a turbomachine engine 10.

[0085] In general, the invention relates to any motor comprising at least one segmented rotor seal requiring cooling.

[0086] As illustrated in [Fig.2], the turbomachine 10 comprises a rotor shaft 12 supported in rotation by a bearing 13 carried by a casing (not shown).

[0087] The turbomachine 10 further comprises an oil chamber 15 and an air chamber 16 separate from the oil chamber 15 and in which a lubricant, in particular oil, must not escape from the oil chamber 15.

[0088] The oil enclosure 15 is delimited radially by the rotor shaft 12 rotating around the axis of rotation XI-XI and by an annular casing (not shown) or casing integral with the housing of the turbomachine 10.

[0089] The bearing 13 comprises an inner ring 13a, an outer ring 13b and a plurality of rolling elements 13c arranged between said rings 13a, 13b.

[0090] The 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 feed ring 14.

[0091] Alternatively, the inner ring of the bearing could be mounted directly on the rotor shaft 12, without an intermediate element.

[0092] The outer ring 13b of the bearing 13 is integral with a bearing support (not shown) which is integral with the annular casing.

[0093] Without limitation, the rolling elements 13c are rollers. Alternatively, other types of rolling elements could be used, or the bearing could be a plain bearing without rolling elements.

[0094] The bearing 13 is lubricated by a lubricant, in particular oil supplied to the oil chamber 15 in order to lubricate and cool the rolling elements 13c of the bearing 13. As illustrated in [Fig.2], turbomachine 10 includes a centrifugal scoop (not shown) for collecting the oil and supplying a feed ramp 14a made in the feed ring 14.

[0095] Alternatively, any other system could be provided for lubricating the bearing 13. The lubrication of the bearing 13 is carried out in a manner known per se and will not be further described in the rest of the description.

[0096] The turbomachine 10 further includes a sealing device 20 intended to ensure a seal between the oil chamber 15 and the air chamber 16 which must be free of oil.

[0097] The sealing device 20 is disposed between the rotor shaft 12 and the turbine housing 10, in particular the oil chamber casing 15, at the separation between the oil chamber 15 and the air chamber 16.

[0098] For this purpose, the sealing device 20 includes in particular an annular radial seal 21.

[0099] The annular joint 21 is composed of a static ring of ring segments (not visible in the figures), in particular made of carbon, held together by means of a circumferential spring 22.

[0100] The annular seal 21 is held in an annular flange 23 mounted inside the casing.

[0101] The flange 23 includes a part 23a of L-shaped cross-section which receives the annular seal 21.

[0102] The annular seal 21 is held in the flange 23 by the circumferential spring 22 and by axial springs 24.

[0103] The axial springs 24 are axially supported on a support 25 held on the flange 23 by a stop joint 26.

[0104] The ring of segments 21 is blocked tangentially by pins 27.

[0105] The annular seal 21 is associated with a sealing track 31 or dynamic sealing track which is rotating and carried by the rotor shaft 12.

[0106] The joint track 31 forms a contact surface in sliding radial contact with the annular seal 21.

[0107] The joint track 31 may be treated or include a special outer coating to improve sliding between the seal 21 and the joint track 31 and minimize wear of said annular seal 21.

[0108] The sealing device 20 also includes a labyrinth seal 28 disposed downstream of the annular seal 21, mounted radially between the rotor shaft 12 and the housing. The labyrinth seal 28 is in radial contact with the sealing track 31.

[0109] The labyrinth seal 28 is supported by a second axial part 23b of the annular flange 23.

[0110] Dynamic sealing is achieved between the respective cooperating cylindrical surfaces of the segment ring 21 and the contact surface of the seal track 31.

[0111] Without limiting the possibility of limitation, bearing grooves could be provided on the contact surface of the joint track 31 in order to improve the bearing capacity.

[0112] The annular envelope fixes the static part of the sealing device 20 onto the housing of the turbomachine 10.

[0113] The sealing device 20 further includes a support 30 for a dynamic sealing track.

[0114] The dynamic sealing track support 30 is rotationally fixed to the shaft rotor 12, in particular via the feed ring 14, and located downstream of the bearing 13.

[0115] The dynamic sealing track support 30 has a general annular shape around the Xl-Xl axis and has a pinhead-shaped tapered section.

[0116] The dynamic sealing track support 30 includes a radial base 32 integral with the rotor shaft 12, in particular with the feed ring 14, and a 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 housing 15.

[0117] The tapered axial portion 33 further includes a second axial portion 35 extending to a free end 35i from the outer end 34e of the first axial portion 34 in the direction of the lubricant housing 15.

[0118] The first and second axial parts 34, 35 extend along two opposite axial directions and delimit between them an annular cavity 36 extending over 360°.

[0119] The first axial part 34 is radially delimited by an internal cylindrical surface 34a and an external cylindrical surface 34b. Each cylindrical surface 34a, 34b of the first axial part 34 has a slope inclined towards the lubricant chamber 15.

[0120] The second axial part 35 is radially delimited by an internal cylindrical surface 35a and an external cylindrical surface 35b.

[0121] The external cylindrical surface 35b carries the joint track 31.

[0122] In other words, the joint track 31 radially in contact with the annular joint 21 is carried by the external cylindrical surface 35b of the second axial part 35.

[0123] Generally, the sealing track 31 is formed on the cylindrical outer surface 35b of the dynamic sealing track support 30.

[0124] The external cylindrical surface 35b of the second axial part 35 is parallel to the axis of rotation Xl-Xl and the internal cylindrical surface 35a of the second axial part 35 has an inclined slope with respect to the axis of rotation Xl-Xl, so that the thickness of the second axial part 35 is gradually decreasing towards the free end 35i of the second axial part 35.

[0125] The dynamic sealing track support 30 further includes one or more oil distribution channels 37 added to said support 30 for example by additive manufacturing.

[0126] 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 housing 15. As illustrated, said zone of The projection area is located axially upstream of the joint track 31. However, in a variant of the configuration symmetrical to that illustrated in which the outside of the joint is located on the downstream side, said projection area would be located axially downstream of the joint track 31. Thus, the projection area is defined in relation to the lubricant enclosure 15.

[0127] The path of the oil in the support 30 of the dynamic sealing track is represented by the arrow H.

[0128] The oil present in the oil chamber 15, for example recovered by centrifugal force by means of 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 flows to the outer end 34e of the first axial part 34.

[0129] The oil is then projected by centrifugal force onto the internal surface 35a of the second axial part 35.

[0130] The cylindrical internal surface 35a of the second axial part 35 forms a heat exchange surface extending over 360°.

[0131] The slope of the internal surface 35a of the second axial part 35 allows the oil to flow along said internal surface 35a towards the interior of the lubricant housing 15 and to absorb heat from the sealing track 31 to be cooled. The sealing track 31 is thus cooled by conduction from the internal surface 35a of the second axial part 35.

[0132] The circulation of oil along the internal surface 35a of the second axial part 35 from the projection area located axially outside the seal track 31 relative to the lubricant housing 15 allows the seal track 31 to be efficiently cooled and thus the annular seal to function correctly.

[0133] After circulating along said internal surface 35a, the calorie-charged oil is projected by centrifugal force onto the walls of the oil enclosure 15.

[0134] Without limitation, each channel 37 comprises a first radial portion 37a, slightly oblique, and a second axial portion 37b, slightly inclined with respect to the axis of rotation XI-XL

[0135] 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.

[0136] The channels 37 can be regularly spaced around the axis of rotation XI-XI

[0137] The joint track support 30 can include up to ten channels 37.

[0138] 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.

[0139] 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 sealing track 31.

[0140] In other words, the oil flows only under the sealing track 31, along the internal surface 35a of the second part 35 of the support 30 of the dynamic sealing track towards the lubricant chamber 15.

[0141] In other words, the oil is not in direct contact with the annular seal 21, nor with the sealing track 31.

[0142] Indeed, the air enclosure must remain free of oil because any oil rising into certain compartments of the turbomachine would be detrimental to the proper functioning of the turbomachine.

[0143] Integrating the distribution channels directly onto the support 30 of the dynamic sealing track eliminates the need for any additional deflector and thus reduces the total mass of the sealing device.

[0144] The cooling of the joint track 31 is achieved solely by conduction across the entire internal surface of the annular joint 21.

[0145] The distribution channels 37 allow the oil to be projected by centrifugal force axially onto the internal surface 35a of the second part 35 of the support 30 of the sealing track upstream of the annular seal 21.

[0146] The internal surface 35a of the second part 35 of the sealing track support 30 is configured to allow spreading and circulation of the oil over the entire surface of the sealing track 31.

[0147] The advantages of the present invention include the compactness of the dynamic sealing track support, the elimination of parts generating a reduction in weight and the increase in the efficiency of the dynamic seal.

Claims

Demands

1. Engine, in particular a turbomachine (10), comprising a rotor shaft (12) mounted for rotation about an axis of rotation (XI-XI), an air chamber (16), a lubricant chamber (15) comprising lubricant, in particular oil, and at least one sealing device (20) disposed between the air chamber (16) and the lubricant chamber (15), said sealing device (20) comprising an annular radial seal (21) associated with a sealing track (31) carried by a dynamic sealing track support (30) integral with the rotor shaft (12), said dynamic sealing track support (30) comprising an internal heat exchange surface (35a) and an external cylindrical surface (35b) surrounding said internal surface (35a) and comprising the sealing 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 chamber (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 chamber (15), and in that said internal heat exchange surface (35a) has an inclined slope relative to the axis of rotation (XI-XI), configured to circulate the lubricant along said internal heat exchange surface (35a) towards the interior of the lubricant chamber (15) so as to cool the seal track (31) by conduction.

2. Motor according to claim 1, wherein the internal heat exchange surface (35a) of the dynamic sealing track support (30) extends over 360°.

3. Motor according to claim 1 or 2, wherein the dynamic sealing track support (30) is devoid of any 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. Motor according to any one of the preceding claims, wherein the dynamic sealing track support (30) has a shape general annular shape around the axis of rotation (XI-XI) and has a tapered cross-section 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 housing (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 interior of the lubricant housing (15), the first and second axial portions (34, 35) defining 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 joint track (31).

6. Motor according to claim 5, wherein the thickness of the second axial part (35) of the dynamic sealing track support (30) is progressively decreasing towards the free end (35i) of the second axial part (35).

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

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

9. Motor according to any one of the preceding claims, wherein the lubricant distribution channels (37) are regularly spaced around the axis of rotation (XI-XI).

10. Motor according to any one of the preceding claims, wherein each lubricant distribution channel (27) is made in the dynamic sealing track support (30) by additive manufacturing.

11. Engine according to any one of the preceding claims, comprising an annular recovery scoop extending around the shaft (12) and disposed in the lubricant housing (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 flow in said channels (37) until it is projected by centrifugal force onto the internal heat exchange surface (35a).

12. Engine according to any one of the preceding claims, wherein 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 a casing integral with the engine housing.

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

14. Motor according to any one of the preceding claims, wherein the sealing device (20) also comprises a labyrinth seal (28) disposed on the inner side of the annular seal (21) relative to the lubricant housing (15), mounted radially between the rotor shaft (12) and the housing, the labyrinth seal (28) being in radial contact with the outer surface (35a) of the dynamic sealing track support (30) carrying the seal track (31).

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