Device for guiding a shaft of an aircraft turbine engine

Abstract

The invention relates to a device for guiding a shaft of an aircraft turbine engine, the device comprising: - a rolling bearing (10, 11); - an annular bearing support (22); and - an oil film compression damping system (19) comprising: - two annular sealing segments (26, 27); and - a first oil supply circuit (33), this first circuit being connected to an annular supply groove (34), characterized in that the damping system further comprises: - a second oil supply circuit (41), this second circuit being connected to at least one annular temperature control groove (40) which is independent of the supply groove (34) and which runs around one of the sealing segments (26, 27).

Description

[0001] DESCRIPTION

[0002] TITLE: DEVICE FOR GUIDING AN AIRCRAFT TURBOMACHINE SHAFT

[0003] Technical field of the invention

[0004] The present invention relates to a device for guiding an aircraft turbomachine shaft and to an aircraft turbomachine comprising such a device.

[0005] Technical background

[0006] The state of the art includes in particular documents FR-A1 -2 876 758, FRAI -3 085 242, FR-A1 -3 088 680, US-A1 -202 / 284298, FR-A1 -3 093 531, FRAI -2 664 330, US-A1 -2017 / 248033 and US-A1 -2016 / 369652.

[0007] Generally, a turbomachine comprises rotating members such as shafts which are guided by guide bearings relative to a fixed structure of the turbomachine. Each of these guide bearings comprises an inner ring and an outer ring enclosing rolling elements, for example rollers or balls. Conventionally, the outer ring is mounted integrally on a bearing support of the turbomachine and the inner ring is mounted integrally on a rotating shaft of the turbomachine.

[0008] Some guide bearings may be associated with oil film compression damping systems, known as "squeeze film damper". An oil film is more or less trapped in an annular space which extends around the bearing so as to dampen the movements of the rotating shaft and reduce the vibrations of the latter which are transmitted to the bearing support and to the fixed structure of the turbomachine and to the aircraft. These damping systems also make it possible to reduce, by damping the rotor modes, the rotor / stator clearance consumption at each compressor and turbine stage, and consequently, to improve engine performance.Finally, damping systems help reduce the risk of non-synchronous vibrations or NSV (acronym for Non Synchronous Vibrations), which can damage the engine, especially when the shaft on which the damping system is placed is a supercritical rotor (having its first bending mode in the engine's operating range). Generally speaking, the oil film helps improve the dynamic response of the turbomachine at a given operating speed and therefore the performance of the turbomachine.

[0009] The annular space for the formation of the oil film is delimited on the one hand, radially between the outer ring of the guide bearing (which is locked in rotation) and the bearing support and on the other hand, axially by annular sealing segments. These segments keep the oil film under pressure (which provides the desired damping), while ensuring the evacuation of the oil.

[0010] Traditionally, sealing rings are elastically deformable, high-temperature resistant metallic annular elements with a straight or overlapping slot or cut in the tangential direction of the ring. This cut allows the oil to be evacuated, with an oil flow rate specified by the overall dynamics. This flow rate must be sufficient to evacuate the calories generated by damping in the oil film, but not too high so that the oil film remains under pressure.

[0011] As an indication, this flow rate can be of the order of a few tens of liters per hour, and the clearance at the cutting edge of each segment from a few tenths of a millimeter to a few millimeters. When mounted, these segments bear radially on the bearing support or a hoop mounted in this support, as well as axially on the walls of the grooves which are formed in the outer ring of the bearing (corresponding to the inner ring of the oil film) and which accommodate these segments. The oil can therefore only pass through the clearance tangential to the cutting edge of each segment.

[0012] The clearance at the ring cutting edge varies during operation, due to the thermal gradient between the ring (which can initially be considered at the oil temperature) and the bearing support or the hoop on which it rests. This thermal gradient changes during operation, due to the temperature conditions of the oil and parts during the different phases of the engine's mission:

[0013] - from start-up to take-off, the oil is hotter than the bearing support: the gradient between the oil (and therefore the segment, directly in contact with the oil), and the bearing support on which the segment rests, is negative. The segment being hotter than the support (because in contact with the oil), it will want to expand axially which will cause the clearance to close at the cut due to contact with the colder support;

[0014] - from takeoff to the end of the mission, the bearing support is hotter than the oil arriving in the film and therefore this gradient is positive. The segment being colder than the support (because in contact with the oil), it will want to compress axially which will cause an opening of the clearance at the cut due to the contact with the hotter support.

[0015] During a typical flight mission, for example, a thermal gradient of several tens of degrees can be observed between the oil and the temperature of the bearing support at the bearing. During very transient phases (rapid accelerations or decelerations) outside of the typical mission, this gradient can also vary significantly.

[0016] The objective of the present invention is to provide an optimized damping device making it possible to reduce the thermal gradient between the sealing segments and the bearing support or the hoop with which they are in contact in the case of straight-cut sealing segments. Document FR-A1-2 876 758 describes an overlapping-cut sealing segment, which has oil passage notches at its outer periphery.

[0017] This solution reduces the rotating static force created by the single leak at the cut, but does not reduce the thermal gradient p recited. Furthermore, the production of the notches can be complex from an industrial point of view, with a cost two to three times higher than that of conventional straight-cut segments. Finally, the definition of the geometry of these notches (height and width) requires complex calculations and validation tests to ensure that the leakage flow generated by these segments is in line with expectations.

[0018] Summary of the invention

[0019] The invention relates to a device for guiding an aircraft turbomachine shaft, this device comprising:

[0020] - a rolling bearing comprising two rings, respectively the first ring and the second ring, between which rolling elements are mounted,

[0021] - an annular bearing support which extends around the bearing, and

[0022] - an oil film compression damping system mounted between the bearing support and the second ring, this damping system comprising:

[0023] - an annular hoop inserted between the bearing support and the second ring,

[0024] - two annular sealing segments, respectively upstream and downstream, which are housed in annular grooves formed in an external cylindrical surface of the second ring and which are capable of bearing radially on an internal cylindrical surface of the hoop, these external and internal surfaces defining between them an annular space for the formation of an oil film which is delimited axially by the sealing segments, each of these segments being split by a straight cut to allow the oil to be evacuated from this space, and

[0025] - a first oil supply circuit, this first circuit being connected to an annular supply groove which extends around the space and which is connected to this space by orifices formed in the hoop, characterized in that the damping system further comprises:

[0026] - a second oil supply circuit, this second circuit being connected to at least one annular temperature-setting groove which is independent of said supply groove and which extends around the space and in line with one of the sealing segments.

[0027] The invention thus proposes to equip the guide device with at least one temperature control groove, which is independent of the supply groove, and which is dedicated to reducing the aforementioned thermal gradient. It is therefore understood that the device comprises two oil circuits having different functions, compared to only one in the prior art. In the present application, the grooves are therefore distinguished by their functions. An oil supply groove has the function of supplying oil, while a temperature control groove has the function of regulating the temperature and therefore of supplying or removing calories, with the aim of limiting the occurrence of a thermal gradient in particular.

[0028] The oil which circulates in the first circuit, and in particular in the annular supply groove, in the orifices and in the space, thus does not circulate in the second circuit, in particular in the temperature setting groove, and vice versa.

[0029] The device according to the invention may comprise one or more of the following characteristics, taken in isolation from one another, or in combination with one another:

[0030] - the feed groove is formed in the annular support or in the hoop;

[0031] - the or each temperature-setting groove is formed in the annular support and / or in the hoop; - the feed groove has an axial extent greater than an axial extent of said orifices;

[0032] - the or each temperature-setting groove has an axial extent greater than an axial extent of the sealing segment around which it extends;

[0033] - the second oil supply circuit is connected to two temperature control grooves, respectively upstream and downstream, which are located respectively in line with said sealing segments;

[0034] - the or each temperature control groove is connected to at least one oil outlet orifice which is formed in the hoop;

[0035] - said at least one oil outlet orifice is axially offset from said space to prevent oil leaving this orifice from entering the space;

[0036] - the oil outlet orifice connected to the upstream temperature control groove opens upstream of the upstream sealing segment, or even upstream of the second ring;

[0037] - the oil outlet orifice connected to the downstream temperature control groove opens downstream of the downstream sealing segment;

[0038] - the or each temperature control groove is connected to at least one oil inlet orifice which is formed in the bearing support;

[0039] - the oil inlet and outlet ports of the or each temperature control groove are located at an angle to each other which is less than or equal to 30°, and preferably less than or equal to 20°; this angle is measured relative to the axis of the bearing;

[0040] - the oil inlet orifice of the or each temperature control groove is located in an angular zone extending between 12 o'clock and 1 o'clock around a main axis of the device by analogy with the dial of a clock according to a first configuration, or between 11 o'clock and 12 o'clock around the axis according to a second configuration, and the oil outlet orifice of the or each temperature control groove is located in an angular zone extending between 11 o'clock and 12 o'clock around the axis according to the first configuration, or between 12 o'clock and 1 o'clock around the axis according to the second configuration;

[0041] - the oil inlet and outlet ports of the or each temperature control groove are inclined relative to radial directions;

[0042] -- the first and second rings are respectively inner and outer rings, or conversely outer and inner rings;

[0043] -- the device comprises a main axis around which the bearing extends;

[0044] -- the section of each segment extends in a plane parallel to said axis;

[0045] - the second ring of the guide device is associated with a flexible cage and comprises an openwork annular veil connected to an annular fixing flange;

[0046] -- the oil pressure in the first supply circuit is higher than the oil pressure in the second supply circuit;

[0047] -- the oil pressure in the temperature control groove(s) is between 1.5 and 10 bars;

[0048] -- each of the segments defines a cutting clearance which is between 0.05 and 5 mm in the mounting position in the device;

[0049] - the or each temperature control groove has an axial extent which represents one to five times an axial extent of the segment associated with this groove;

[0050] -- the oil film or the space for forming this oil film has a radial thickness of between 0.05 and 1 mm;

[0051] -- the axial distance between the segments or the length of the oil film or the oil film formation space, is between 10 and 50mm;

[0052] -- the oil film or oil film formation space has a diameter of between 100 and 500 mm;

[0053] -- the or each feed groove is of the centered type and is located midway between the sealing segments;

[0054] - the or each feed groove is of the off-center type and is located close to one of the sealing segments; - when the feed groove is of the centered type, the device comprises exactly two temperature-setting grooves;

[0055] - when the feed throat is of the off-center type, the device includes a single temperature setting throat.

[0056] The invention further relates to an aircraft turbomachine, comprising a device as described above.

[0057] Brief description of the figures

[0058] 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:

[0059] [Fig.1] Figure 1 is a half schematic view in axial section of an aircraft turbomachine,

[0060] [Fig.2] Figure 2 is a schematic view in axial section and in perspective of a guiding device according to the prior art,

[0061] [Fig.3] Figure 3 is a schematic cross-sectional view of the guide device of Figure 2,

[0062] [Fig.4] Figure 4 is a schematic axial sectional view of the guide device of Figure 2,

[0063] [Fig.5] Figure 5 is a schematic perspective view of a straight-cut sealing segment,

[0064] [Fig.6] Figure 6 is a schematic perspective view of a lap-cut sealing segment,

[0065] [Fig.7] Figure 7 is a schematic axial sectional view similar to that of Figure 4 and illustrates an embodiment of a guidance device according to the invention,

[0066] [Fig.8] Figure 8 is a view similar to that of Figure 7 and illustrates an alternative embodiment of the invention,

[0067] [Fig.9] Figure 9 is a view similar to that of Figure 7 and illustrates another alternative embodiment of the invention, and [Fig.10] Figure 10 is a very schematic view of a temperature-setting groove of a guide device according to the invention, and shows the positions of the oil inlet and outlet ports of this groove.

[0068] Detailed description of the invention

[0069] Figure 1 is a partial axial sectional view of a turbomachine 1 with longitudinal axis X to which the invention applies. The turbomachine 1 shown is a double-flow turbomachine intended to be mounted on an aircraft.

[0070] Conventionally, the turbomachine 1 comprises a rotating shaft which is guided in rotation via one or more guide bearings relative to a fixed part of the turbomachine. The rotating shaft may be a low-pressure shaft of the turbomachine. The rotating shaft may also be a high-pressure shaft or any shaft driven in rotation using a guide bearing within the turbomachine.

[0071] With reference to Figure 1, the low pressure shaft 2 drives for example a fan 3 arranged upstream of the turbomachine 1. The turbomachine 1 comprises downstream of the fan 3 and successively, a compressor assembly (low pressure compressor 4a and high pressure compressor 4b), a combustion chamber 5, and a turbine assembly (high pressure turbine 6a and low pressure turbine 6b), which form a gas generator.

[0072] In the present invention, the terms “upstream” and “downstream” are defined in relation to the circulation of gases in the turbomachine and here along the longitudinal axis X.

[0073] The low-pressure shaft 2 connects the low-pressure compressor 4a of the compressor assembly and the low-pressure turbine 6b of the turbine assembly, to form a low-pressure spool. The turbomachine 1 may also comprise a high-pressure spool which comprises the high-pressure compressor 4b of the compressor assembly connecting the high-pressure turbine 6a of the turbine assembly via a high-pressure shaft 7.

[0074] The low pressure shaft 2 is centered on the longitudinal axis X and is guided at its upstream end by an upstream guide bearing 10 and at its downstream end by a downstream guide bearing 11. The guide bearings 10, 11 are each housed in an enclosure of a fixed casing 12 relative to which the low pressure shaft 2 rotates.

[0075] With reference to figures 2 to 4, each bearing 10, 11 comprises an annular inner ring 13 mounted on the rotating shaft (low pressure shaft 2) and an annular outer ring 14 connected to a fixed structure secured to the fixed casing 12 of the turbomachine 1. The inner ring 13 is for example shrunk onto the low pressure shaft 2 so as to prevent any translation and any rotation of the inner ring 13 relative to the low pressure shaft 2. The outer ring 14 is advantageously fixed to the fixed structure using an anti-rotation device to block it in rotation relative to the latter. The anti-rotation device is generally formed of a radial spacer 15 which is housed, on the one hand in a notch of the external ring 14 which opens to the outside, and on the other hand in a hole (not shown) of the fixed structure secured to the fixed casing 12. The external ring 14 surrounds and is arranged at a radial distance from the internal ring 13.

[0076] In the present invention, the terms "radial" and "radially" are defined with respect to a radial axis R perpendicular to the longitudinal axis X.

[0077] Between the inner and outer rings 13, 14 are arranged rolling elements 16 such as rollers or balls, which provide the connection between the rotating shaft and the fixed structure of the turbomachine. The inner and outer rings 13, 14 comprise internal surfaces 17, 18 which form internal raceways for the rolling elements 16.

[0078] In Figures 2 to 4, we also see that the bearing 10, 11 is equipped with a damping system. The latter comprises a damping film which is an oil film 19 and which circulates between the outer ring 14 and the fixed structure of the turbomachine. This oil film 19 makes it possible to limit, dampen or even regulate the vibrations of the turbomachine 1 during operation. Indeed, the turbomachine 1 is known to vibrate according to at least one given vibration mode during the rotation of one or more rotating shaft(s). These vibrations are due for example to the balancing defects in the turbomachine 1 and the unbalances generated as a result of these balancing defects.

[0079] The oil film 19 is intended to occupy an annular damping space 20. In the case of Figure 4, the space 20 is located radially between the outer ring 14 of the guide bearing and an annular hoop 21 (i.e., a hooped annular part) mounted in an annular bearing support 22 which is part of the fixed structure or which is fixed to this fixed structure. In other words, the hoop 21 surrounds the outer ring 14 of the bearing 10, 11 and is itself surrounded by the bearing support 22.

[0080] The bearing support 22 comprises an inner cylindrical surface 22a which faces an outer cylindrical surface 21a of the hoop 21. The hoop 21 comprises an inner cylindrical surface 21b which faces an outer cylindrical surface 14a of the outer ring 14 of the bearing 10, 11. The surfaces 22a and 21a are in contact with each other. The surfaces 21b and 14a are radially spaced from each other and the radial clearance between these surfaces 21b and 14a is predetermined to define the radial dimension of the space 20 for forming the oil film 19.

[0081] The damping space 20 is also axially delimited by sealing segments 24 which regulate or allow the "leakage" of oil from the damping film to the outside of the space 20. These segments control the leakage rate of the damping film in order to ensure effective damping of vibrations. In the present invention, the terms "axial" and "axially" are defined with respect to the longitudinal axis X.

[0082] A first annular segment 26 is located upstream of the space 20 and a second annular segment 27 is located downstream of the space 20. The segments 26, 27 extend radially between the outer ring 14 and the hoop 21. The outer ring 14 comprises a first annular groove 28, upstream, and a second annular groove 29, downstream, intended to receive the segments 26, 27 respectively. The grooves 28, 29 are formed in the surface 14a of the outer ring 14 and are arranged axially at a distance from each other. The segments 26, 27 extend radially from their grooves 28, 29 and are capable of bearing radially on the surface 21b of the hoop. They are further intended to bear on the side walls of the grooves (the upstream segment 26 on the upstream wall of the upstream groove 28, and the downstream segment 27 on the downstream wall of the downstream groove 29) due to the pressure exerted by the oil in the film during operation.

[0083] The segments 26, 27 are split and each comprise a cut or slot 30 which forms ends 31 facing each other (see figure 5). This cut is called a straight cut. Each end 31 is defined in a plane which is parallel to a plane RX. The plane RX is formed by the longitudinal axes X and radial R. The segments 26, 27 have a generally square or rectangular section.

[0084] In the current technique shown in Figure 6, the segments 26, 27 can also be split and each comprise an overlapping cut 30. In this case, each end comprises a tongue extending in a circumferential direction (transverse axis T). The transverse axis T is perpendicular to the longitudinal axis X and radial axis R. The two tongues each have a surface intended to bear axially against each other and an axially opposite surface which is flush with one side of the segment. The segments 26, 27 can also be provided with notches 32 on their external periphery. These notches are regularly distributed around the axis of the segment (parallel to the longitudinal axis X in the installation situation) and make it possible to evacuate the power dissipated by damping in the oil film 19. In the present invention, the segments 26, 27 are of the straight-cut type as illustrated in Figure 4.The clearance at the J-section, i.e. the distance between the circumferential ends of a segment, when mounted in the device, is preferably between 0.5 and 5 mm.

[0085] Turbomachine 1 is also equipped with a first supply circuit

[0086] 33 which is connected to a power source (not shown) so as to supply pressurized oil to the space 20 and to form the oil film 19 in this space. This first circuit 33 can also supply oil to the guide bearings for their lubrication.

[0087] For this, as illustrated in Figure 4, the bearing support 22 comprises an annular supply groove 34 which extends around the space 19 and which is connected to this space by orifices 35 formed in the hoop 21. The groove 34 is connected to a pipe 36 which is shown schematically here. The groove

[0088] 34 extends around the space 19, between the segments 26, 27, and at a predetermined axial position with respect to these segments 26, 27. The groove 34, the orifices 35 and the conduit 36 ​​are part of the supply circuit 33.

[0089] The orifices 35 are calibrated and their number is between 1 and 12. They are preferably regularly distributed around the X axis.

[0090] In the example shown in Figure 4, the groove 34 is of the off-center type or the supply of the oil film 19 is of the off-center type. H is defined as a median plane perpendicular to X and passing substantially through the middle of the oil film. It can be seen that the groove 34 is not crossed by this plane H and is on the contrary at a distance from this plane H and here downstream of this plane, close to the downstream segment 27.

[0091] Alternatively, the feed groove could be of the centered type or the feed of the oil film 19 could be of the centered type. For this, the groove would be crossed by the plane H and would therefore be substantially halfway between the segments 26, 27.

[0092] Figure 4 further shows the circulation of the oil in the circuit 33, from the pipe 36 to the groove 34 (arrow F1), through the orifices 35 of the hoop 21, then from the space 20 through the straight sections of the segments 26, 27. At the level of the orifices 35, the external surface 14a of the ring 14 may comprise an annular groove 37 for recovering the oil leaving the orifices 35 and for distributing this oil in the space 20 all around the axis X.

[0093] The thermal gradient between the segments 26, 27 and the hoop 21 on which they rest radially is not measured in operation and is therefore poorly known. It can be between 5 and 100°C for example. This gradient is nevertheless used as a hypothesis for defining the tangential clearance known as “cut clearance” of the segments 26, 27.

[0094] In the presence of a negative gradient (the segment temperature is similar to the oil temperature and is higher than the temperature of the hoop), the segment will want to lengthen by thermal expansion, and its slot will therefore close due to the imposed gradient.

[0095] There are three distinct cases. In the first case, we observe an operation that does not affect the film's operation; the segment closes at the cutting clearance, but the closing clearance imposed by this gradient is less than the cutting clearance, and the oil can therefore be evacuated normally. This case does not affect the film's operation.

[0096] In a second case where the clearance at the cutting edge (tangential clearance) is poorly defined or the thermal gradient used to define this clearance is underestimated, the segment will want to close beyond the value of the expected clearance. As a result, the oil in the oil film 19 will no longer be able to be evacuated, and will therefore rise very sharply in temperature (due to the calories generated by damping the oil film), which will reduce its viscosity, and therefore the damping power of the film. In the case of a gradient that is much too high and a segment that is closed for a prolonged period, there may also be a risk of coking of the oil, making the film absolutely non-functional, and then requiring disassembly to clean it. In the third case where the negative thermal gradient is even higher in absolute value than that of the second case, the segment will want to close even more.Due to the presence of radial clearance between the segment 26, 27 and the groove 28, 29 which accommodates the segment, the two ends of the segment will want to press radially against the bottom of the groove. As a result, the oil will be evacuated via the space left between the outer diameter of the segment and the hoop, which can lead to very significant leaks, greater than in the case of normal operation. If these leaks are too significant, it will not be possible to achieve sufficient supply pressure in the oil film, which will reduce the damping provided by it.

[0097] Furthermore, in the second and third cases, once the return to a positive gradient, the segment will want to find its position with an open clearance. These two cases with these compression / decompression cycles of the segment, repeated at each mission of the aircraft (or for transient variations outside the classic mission of the aircraft), can therefore generate a risk of plasticization of the segment, which would therefore keep its deformed shape instead of its initial shape, and would therefore no longer be functional.

[0098] The consequences in the second and third cases are to have a non-functional film or one with degraded (or very degraded) operation compared to its nominal operation, with a reduction or even a loss of the damping provided by this film.

[0099] The consequences are as follows:

[0100] - increased vibrations,

[0101] - deterioration of the relative clearance consumption between the rotor and the stator at the different compressor and turbine stages, and deterioration of performance, or even an increase in the risk of pumping,

[0102] - occurrence of non-synchronous vibrations (NSV), which can damage the motor, especially if the film is placed on a supercritical rotor.

[0103] There is therefore a need to reduce or at least control this thermal gradient, which is proposed by the invention. The present invention thus proposes adding a second oil supply circuit, which is dedicated to heating the segments 26, 27. For this, the second circuit is connected to at least one annular heating groove which extends around the space 20 and in line with one of the segments 26, 27.

[0104] Figures 7 to 9 illustrate several embodiments of the guide device according to the invention. The differences between these embodiments are based in particular on the number and position of the heating grooves 40, and on the position of the feed groove 34.

[0105] Although this is not necessarily visible or described in the following, the guide device according to the invention may comprise all or part of the characteristics of a guide device of the prior art, such as that illustrated in Figures 2 to 5 and described in the above. In particular, its outer ring 14 could be associated with a flexible cage C1 or squirrel cage, that is to say an openwork cage connected to an annular fixing flange C2, as illustrated in Figure 2.

[0106] Figure 7 illustrates a first embodiment of a guide device according to the invention, in which the temperature-setting grooves 40 are formed in the bearing support 22 and in particular in the internal surface 22a of the support 22. This is also the case for the supply groove 34 which is formed in the support 22 and in particular in the internal surface 22a of the support 22.

[0107] The groove 34 is here of the centered type and is therefore crossed by the plane H. The grooves 40 are two in number and are respectively an upstream groove located upstream of the plane H and a downstream groove located downstream of the plane H.

[0108] The groove 34 has, for example, a rectangular or square cross-section.

[0109] In the example shown, the groove 34 has an axial extent greater than an axial extent of the orifices 35. The upstream groove 40 extends around the space 20 and around and in line with the upstream segment 26. The downstream groove 40 extends around the space 20 and around and in line with the downstream segment 27.

[0110] Each groove 40 has, for example, a rectangular or square cross-section. The shape and dimensions of the grooves 40 are identical and each defines a volume which may be less than the volume defined by the groove 34.

[0111] In the example shown, each groove 40 has an axial extent greater than an axial extent of the segment 26, 27 around which it extends. Each groove 40 preferably has an axial extent representing one to five times the axial extent of the corresponding segment, and preferably two to five times.

[0112] The grooves 40 are part of a circuit 41 which comprises one or more pipes 42 for supplying oil to the grooves 40. Each of the grooves 40 is supplied with oil by a pipe 42 in the example shown, the pipes being independent of the pipe 36.

[0113] The number of pipes 42 which supply a groove 40 is for example between 1 and 3. The pipes 42 supplying the same groove 40 are preferably regularly distributed around the axis X.

[0114] Each pipe 42 has one end which opens into the corresponding groove 40 to form an oil inlet orifice 43. The hoop 21 comprises at least one radial orifice, and preferably a single radial orifice, which forms an oil outlet orifice 44.

[0115] With regard to the upstream groove 40a, the oil outlet orifice 44 communicates with the upstream end of the groove 40 and is located upstream of the segment 26, or even upstream of the ring 14. The arrows show the path of the oil in this zone.

[0116] With regard to the downstream groove 40b, the oil outlet orifice 44 communicates with the downstream end of the groove 40b and is located downstream of the segment 27. The arrows show the path of the oil in this zone. The circuits 33, 41 are preferably independent. This means that the oil which circulates in the first supply circuit 33, and in particular in the annular supply groove 34, in the orifices 35 and in the space 20, does not circulate in the second supply circuit 41, in particular in the temperature-setting groove 40 and the oil outlet orifice 44, and vice versa.

[0117] In the embodiment variant of Figure 8, the groove 34 is of the off-center type and is distant from the plane H. It is located downstream of the plane H and close to the segment 27. It can be considered as extending partly around and in line with the segment 27. In this case, there is no temperature-setting groove 40 in this area. Indeed, a closure of this segment, due to the appearance of a temperature gradient with the hoop, would be less problematic, because this would promote the circulation of oil towards the opposite segment, which would increase the damping.

[0118] The guide device of Figure 8 thus comprises a single groove 40, 40a which is located upstream of the plane H and around the segment 26. In the example shown, this groove 40 is formed in the hoop 21 and in particular in the external surface 21 of the hoop 21. The supply pipe 42 of this groove 40 is similar to that of the supply pipe of the groove 40a in Figure 7.

[0119] The circuit 33 is similar to that of Figure 4. The groove 34, the orifices 35 and the pipe 36 of the circuit 33 of Figure 8 are similar to the upstream groove 40a, the orifices 35, and the pipe 36 connected to this groove of Figure 4.

[0120] The embodiment variant of Figure 9 differs from the embodiment of Figure 7 in that the grooves 40 are formed in the hoop 21 and not the support 22 and in particular in the external surface 21a of the hoop 21.

[0121] The circuits 36, 41 are preferably independent and can supply oil, for example from the same oil source, at different pressures. The oil supply pressure of the second circuit 41 is preferably lower than that of the first circuit 36. For this, the circuit 41 can be connected to the oil source by a pump providing a pressure lower than that provided by another pump connecting the circuit 36 ​​to the oil source. Alternatively, the circuits 36, 41 could be connected to the oil source by the same pump and the circuit 41 could be configured to reduce the pressure of the oil supplied by the pump, for example by controlled pressure losses in the pipe 42.

[0122] The oil pressure in the circuit 41 or the or each groove 40 is preferably between 1.5 and 10 bars. The oil pressure in the circuit 36 ​​or the groove 34 is preferably greater than 10 bars.

[0123] Figure 10 shows very schematically one of the temperature-setting grooves 40 and the respective positions of its oil inlet and outlet orifices 43, 44.

[0124] The oil inlet and outlet ports 43, 44 of the or each heating groove 40 are located at an angle to each other which is less than or equal to 30°, and preferably less than or equal to 20° (measured around the X axis).

[0125] In the example shown, the oil inlet orifice 43 is formed by the outlet of the pipe 42 in the groove 40 and is for example located close to the 12 o'clock position (12 o'clock) by analogy with the dial of a clock (around the X axis). In the example shown, the oil inlet orifice 43 is located in an angular zone extending between 12 o'clock and 1 o'clock around the X axis. The oil outlet orifice 44 is formed by the aforementioned orifice and is located at 11 o'clock and 12 o'clock around the X axis.

[0126] Alternatively, it is the oil outlet orifice 44 which could be located in the angular zone extending between 12 o'clock and 1 o'clock, and the oil inlet orifice 43 could be located in the angular zone extending between 11 o'clock and 12 o'clock around the X axis.

[0127] As another possible variant, depending on the integration constraints, the ports can be located at different azimuths, keeping the "clocking" (relative azimuthal position) between the oil inlet and oil outlet ports (+ / - 1 h), with for example inclined ports (instead of purely radial) to force the direction of the oil flow circulation between the oil inlet port and the oil outlet port, coupled with the supply pressure imposed on this oil flow.

[0128] The segments 26, 27 are for example made of a metal alloy. An example of a metal alloy is a mixture of copper or iron.

[0129] The oil film 19 preferably has a radial thickness of between 0.05 and 1 mm. The segments 26, 27 are separated from each other by a distance of between 10 and 50 mm, which corresponds to the length of the oil film. The oil film 19 may be located at an implantation radius (measured relative to the X axis) which is between 100 and 500 mm.

[0130] In operation, at the start of the mission, oil is therefore intended to arrive both in the space 20 for the formation of the oil film 19 and in the temperature-regulating groove(s) 40. This oil will therefore increase the temperature of the hoop 21 more quickly, and therefore mathematically reduce the gradient between the segment(s) 26, 27 and the hoop 21.

[0131] The oil arriving in this groove 40 is then discharged via the outlet orifice 44, in order to ensure that the oil travels around the entire circumference of the groove 40 (arrows in figure 10).

[0132] The aforementioned dimensions of the groove(s) 40, their shape (rectangular or not), as well as the inlet and outlet orifices 43, 44 can be defined via standard thermal calculations.

[0133] The invention therefore proposes a simple and passive way of reducing the thermal gradient between the segments 26, 27 and the hoop 21 or the bearing support 22 on which the segments rest radially, which will therefore reduce the risk of “over-closing” of the segment in the event of tangential clearance at the cut or thermal gradient underestimated during design.

[0134] This ensures better control of the film damping whatever the engine operating phase, and this reduced gradient variation makes it possible to minimize the evolution of this clearance at the cut, which guarantees less variation in the leakage flow and therefore better control / robustness on the damping of the oil film.

[0135] Unlike the above, the bearing support 22 and the shaft 13 could have an inverse arrangement, the bearing support 22 being located inside the bearing 10, 11 and the shaft 13 being located outside the bearing 10, 11.

Claims

CLAIMS 1. Device for guiding an aircraft turbomachine shaft, this device comprising: - a rolling bearing (10, 11) comprising two rings (13, 14), respectively first ring and second ring, between which rolling elements (16) are mounted, - an annular bearing support (22) which extends around the bearing (10, 11), and - an oil film compression damping system (19) mounted between the bearing support (22) and the second ring (14), this damping system comprising: - an annular hoop (21) interposed between the bearing support (22) and the second ring (14), - two annular sealing segments (26, 27), respectively upstream and downstream, which are housed in annular grooves (28, 29) formed in an external cylindrical surface (14a) of the second ring (14) and which are capable of bearing radially on an internal cylindrical surface (21b) of the hoop (21), these external and internal surfaces (14a, 21b) defining between them an annular space (20) for the formation of an oil film (19) which is delimited axially by the sealing segments (26, 27), each of these segments being split by a straight cut to allow the oil to be evacuated from this space, and - a first oil supply circuit (33), this first circuit being connected to an annular supply groove (34) which extends around the space (20) and which is connected to this space by orifices (35) formed in the hoop (21), characterized in that the damping system further comprises: - a second oil supply circuit (41), this second circuit being connected to at least one annular temperature-setting groove (40) which is independent of said supply groove (34) and which extends around the space (20) and in line with one of the sealing segments (26, 27).

2. Device according to claim 1, in which the feed groove (34) is formed in the annular support (22) or in the hoop (21).

3. Device according to claim 1 or 2, in which the or each temperature-setting groove (40) is formed in the annular support (22) and / or in the hoop (21).

4. Device according to one of the preceding claims, in which the feed groove (34) has an axial extent greater than an axial extent of said orifices (35).

5. Device according to one of the preceding claims, in which the or each temperature-setting groove (40) has an axial extent greater than an axial extent of the sealing segment (26, 27) around which it extends.

6. Device according to one of the preceding claims, in which the second oil supply circuit (41) is connected to two temperature-setting grooves (40a, 40b), respectively upstream and downstream, which are located respectively in line with said sealing segments (26, 27).

7. Device according to one of the preceding claims, in which the or each temperature-setting groove (40) is connected to at least one oil outlet orifice (44) which is formed in the hoop (21).

8. Device according to claim 7, wherein said at least one oil outlet orifice (44) is axially offset from said space (20) to prevent oil leaving this orifice (44) from entering the space (20).

9. Device according to all of claims 6 and 7, or 6, 7 and 8, in which the oil outlet orifice (44) connected to the upstream temperature setting groove (40a) opens upstream of the upstream sealing segment (26), or even upstream of the second ring (24).

10. Device according to all of claims 6 and 7, or 6, 7 and 8, or claim 9, in which the oil outlet orifice (44) connected to the downstream temperature setting groove (40b) opens downstream of the downstream sealing segment (27).

11. Device according to one of claims 7 to 10, in which the or each temperature-setting groove (40) is connected to at least one oil inlet orifice (43) which is formed in the bearing support (22).

12. Device according to claim 11, in which the oil inlet and outlet orifices (43, 44) of the or each temperature-setting groove (40) are located at an angle to each other which is less than or equal to 30°, and preferably less than or equal to 20°.

13. Device according to claim 11 or 12, in which the oil inlet orifice (43) of the or each temperature-setting groove (40) is located in an angular zone extending between 12 o'clock and 1 o'clock around a main axis of the device by analogy with the dial of a clock according to a first configuration, or between 11 o'clock and 12 o'clock around the axis according to a second configuration, and the oil outlet orifice (44) of the or each temperature-setting groove (40) is located in an angular zone extending between 11 o'clock and 12 o'clock around the axis according to the first configuration, or between 12 o'clock and 1 o'clock around the axis according to the second configuration.

14. Device according to one of the preceding claims, in which the oil inlet and outlet orifices of the or each heating groove are inclined relative to radial directions.

15. Device according to one of the preceding claims, in which the second ring of the guide device is associated with a flexible cage and comprises an openwork annular web connected to an annular fixing flange.

16. Device according to one of the preceding claims, in which the or each temperature-setting groove has an axial extent which represents one to five times an axial extent of the segment associated with this groove.

17. Device according to one of the preceding claims, wherein when each feed groove is of the centered type, the device comprises exactly two temperature setting grooves.

18. Device according to one of claims 1 to 16, wherein when the feed groove is of the off-center type, the device comprises a single temperature setting groove.

19. Aircraft turbomachine, comprising a shaft guided in rotation by a device according to one of the preceding claims.

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