Lubricating chamber for a mechanical system of a turbomachine

Abstract

The invention relates to a lubricating chamber (10) for a mechanical system (1), comprising: - a cylindrical body (12) extending along a longitudinal axis (C), - an annular inlet wall (14) for a lubricating fluid (15) and an annular outlet wall (16) for the lubricating fluid these walls being attached respectively to ends (12A, 12B) of the cylindrical body, - an internal cavity (18) delimited radially by the cylindrical body (12) and axially by the annular inlet (14) wall and outlet (16) wall, and housing the mechanical system (1) to be lubricated. According to the invention, the lubricating chamber (10) is rotatable about the longitudinal axis (C), and the outlet wall (16) is configured to discharge particles (5) entrained by the lubricating fluid (15) under a centrifugal effect, the particles (5) resulting from wear of the mechanical system (1) with which the lubricating fluid is in contact.

Description

[0001] DESCRIPTION

[0002] TITLE OF THE INVENTION: LUBRICATION UNIT FOR A MECHANICAL SYSTEM OF A TURBOMACHINE

[0003] TECHNICAL FIELD

[0004] The present invention relates to a lubrication chamber for a mechanical system. More specifically, the invention relates to the field of lubrication of a mechanical system of an aircraft.

[0005] PREVIOUS TECHNIQUE

[0006] Aircraft contain many moving mechanical parts, typically rotating parts such as gears or bearings.

[0007] Generally, these mechanical parts or systems require lubrication for proper operation. For this purpose, aircraft incorporate a fluid circuit (typically oil, coolant, or fuel) within a housing or casing containing the moving parts, which are immersed in this fluid. In general, the function of the fluid circuit is to lubricate and / or cool the moving parts.

[0008] Moving parts are subject to wear over their lifetime, for example due to friction resulting from contact between two gears or bearings, or due to intense shocks or friction between rotating parts due to intense and abnormal vibrations propagating in the casing.

[0009] Whatever its cause, wear and tear of parts leads to the formation of particles which detach from the parts and are carried by the fluid in the fluid circuit.

[0010] Since rotating parts are generally metallic, the particles resulting from wear are conductive and usually take the form of metal filings. Furthermore, these parts are most often made of a ferromagnetic metal such as iron, meaning it is attracted to a magnetic element like a magnet.

[0011] The detection of particles, and in particular metal filings and particles, is essential to detect potential damage to rotating mechanical parts, such as bearings, gears, mechanical transmission components... This detection is currently ensured by magnetic plugs, whether electric or not.

[0012] A magnetic plug, as is well known, consists of a head and a permanent magnet, formed by a magnetic bar, at one end. Such a magnetic plug is strategically positioned within the fluid circuit so that the magnet is immersed in the fluid. The magnetic interaction of the plug's magnet attracts and retains particles as the fluid circulates, thus capturing the particles carried by the lubricating fluid.

[0013] On-site operators must then periodically check the condition of these magnetic plugs, collect the particles trapped on the magnetic rod, and have these particles analyzed. From the results of these analyses, it is possible to identify the nature and geometry of the collected particles. Depending on the location of the plug sample, it is then possible to pinpoint the component(s) affected by wear and take the necessary measures to guarantee the aircraft's integrity and flight safety.

[0014] The mechanical magnetic stopper, being a simple magnet that captures particles, is controlled manually or visually by an operator during a maintenance operation.

[0015] The magnetic electric plug, on the other hand, consists of a magnet and two electrodes electrically insulated from each other. The accumulation of metal filings due to magnetic interaction closes a conductive bridge between the two electrodes. Appropriate electronics then allow a warning light to be displayed on the dashboard, thus alerting the pilot.

[0016] For these systems to work, the particles must be transported, notably by the lubricating fluid, to the magnetic stopper.

[0017] In the specific case of rotating shafts, the lubrication function requires that the lubricating fluid be kept within a rotating enclosure. Such an enclosure 10A is schematically illustrated in Figure 1, in which a mechanical system 1 to be lubricated is housed integrally with the closed rotating enclosure. A level of liquid 15, for example oil, is maintained by centrifugal force, and a minimum quantity of liquid is retained in the enclosure even when the shaft is stopped.

[0018] This lubrication function interferes with the detection of particles 5. Indeed, the retention of liquid 15, particularly oil, also generates the retention of any particles potentially produced within the enclosure. The particles or filings 5 ​​are trapped by centrifugal force within the rotating enclosure. They are therefore not transported to the magnetic plug. Consequently, they are not detected. One solution is the use of a rotating mechanical magnetic plug. Such a plug mounted on rotating parts is possible but very difficult to implement. The rotating mechanical magnetic plug will generate an imbalance. Furthermore, the centrifugal force induces significant liquid pressures, particularly oil pressures, which must be taken into account with regard to the static seals of the magnetic plug.In addition, a hatch in the fixed housing is needed to rotate the shaft to orient the magnetic plug in line with the hatch axis in order to access it.

[0019] If the function of the mechanical system to be lubricated is critical, it is necessary to use an electric magnetic plug.

[0020] Mounting an electric magnetic stopper on a rotating part is also possible but also very restrictive because it requires the use of a rotating collector which is bulky and unreliable.

[0021] The objective of the present invention is therefore to overcome these drawbacks.

[0022] SUMMARY OF THE INVENTION

[0023] To this end, the invention relates to a lubrication chamber for a mechanical system, in particular an aircraft turbomachine, the chamber comprising:

[0024] - a cylindrical body extending along a longitudinal axis,

[0025] - an annular inlet wall for a lubricating fluid and an annular outlet wall for the lubricating fluid, fixed respectively to a first end and a second end of the cylindrical body,

[0026] - an internal cavity delimited radially by the cylindrical body and axially by the annular inlet wall and the annular outlet wall, the mechanical system to be lubricated being housed in the internal cavity.

[0027] According to the invention, the lubrication chamber is mobile in rotation around the longitudinal axis, and the outlet wall is shaped to evacuate particles carried by the lubricating fluid under a centrifugal effect, the particles resulting from wear of the mechanical system with which said lubricating fluid is in contact.

[0028] The invention thus proposes a system that allows both the lubrication function to be maintained by ensuring a sufficient level of lubricating fluid in the enclosure and the removal of potential particles generated in the mechanical system.

[0029] Specifically, the invention allows, on the one hand, for the local concentration of wear particles in the rotating part of the housing and, on the other hand, for the circulation of the lubricating fluid through the bottom of the rotating part in order to carry away the particles stored there. Advantageously, when the rotation of the housing is stopped, the invention allows for the removal of residual particles by rinsing.

[0030] The lubrication chamber according to the invention may comprise one or more of the following features, taken individually or in combination with each other in all technically possible combinations:

[0031] - the outlet wall comprises an annular flange radially delimited between an inner edge and an outer edge, and which presents a surface external to the internal cavity of the lubrication chamber; a cylindrical portion extending axially from the outer edge of the flange towards a free end;

[0032] - the outlet wall includes at least one assembly for evacuating particles carried by the lubricating fluid comprising: a scoop and a flange discharge conduit; the scoop being formed in the cylindrical portion of the outlet wall and shaped to concentrate the particles locally under the centrifugal effect; the flange discharge conduit having an internal passage for the circulation of the lubricating fluid, the conduit extending longitudinally from the outer edge of the flange radially towards the inner edge of the flange, the radial direction being perpendicular to the longitudinal axis, and comprising an inlet mouth communicating with the scoop and an outlet orifice for the evacuation of particles carried by the lubricating fluid, the conduit being arranged downstream of the outer surface of the flange;

[0033] - the discharge conduit has a peripheral wall extending from the outer surface of the flange, the peripheral wall at least partially delimiting the internal passage for the circulation of the lubricating fluid;

[0034] - the outer surface of the flange extends radially between the inner edge and the outer edge, at least partially delimiting the internal passage for the circulation of the lubricating fluid, and a through orifice is provided through the flange forming the inlet of the conduit;

[0035] - the outlet wall has an annular cover juxtaposed to the flange and arranged upstream of the flange, the annular cover being shaped to delimit at least partially the internal passage for the circulation of the lubricating fluid and to form the mouth of the discharge conduit;

[0036] - the annular cover extends radially between an inner rim and an outer rim, the outer rim of the annular cover being closer to the longitudinal axis than the outer edge of the annular flange;

[0037] - the scoop extends circumferentially over an angular sector of the cylindrical portion of the outlet wall between a first end and a second end;

[0038] - the inlet of the evacuation duct communicating with the scoop is arranged between the first end and the second end, the first end and the second end each being closer to the longitudinal axis than the inlet of the evacuation duct;

[0039] - the inlet of the evacuation conduit communicating with the scoop is arranged near the second end, the first end being closer to the longitudinal axis than the second end of the scoop;

[0040] - the scoop has a flared shape along the circumferential direction from the first end to the second end;

[0041] - the cylindrical portion of the outlet wall extends axially from the outer edge of the flange towards the peripheral wall of the evacuation duct, the cylindrical portion flaring out from the free end of the cylindrical portion towards the peripheral wall of the evacuation duct;

[0042] - the outlet wall has several assemblies for evacuating particles carried by the lubricating fluid, the assemblies being distributed angularly around the longitudinal axis;

[0043] - the evacuation assemblies are regularly distributed angularly around the longitudinal axis.

[0044] The invention also relates to a turbomachine, in particular an aircraft turbomachine, comprising a lubrication chamber according to the invention and as described above and a mechanical system to be lubricated housed in the lubrication chamber.

[0045] The invention also relates to an aircraft comprising a lubrication chamber according to the invention and as described above and a mechanical system to be lubricated housed in the lubrication chamber.

[0046] BRIEF DESCRIPTION OF THE DRAWINGS

[0047] The present invention will be better understood and other details, features, and advantages of the present invention will become more apparent upon reading the following description of a non-limiting example, with reference to the accompanying drawings in which:

[0048] - Figure 1, already described, is a schematic longitudinal cross-sectional view of a rotating lubrication chamber according to the prior art; - Figure 2 represents a schematic cross-sectional view of an aircraft, in particular a helicopter, to which the invention applies;

[0049] - Figure 3 is a schematic longitudinal cross-sectional view of a lubrication chamber according to the invention;

[0050] - Figure 4 is a three-dimensional schematic view of the upstream side of an annular outlet wall of the lubrication chamber of Figure 3 according to a first embodiment;

[0051] - Figure 5 represents a schematic three-dimensional view of the downstream side of the annular outlet wall of Figure 4;

[0052] - Figure 6 illustrates an enlarged local cross-sectional view of the exit annular wall of Figure 4;

[0053] - Figure 7 represents Figure 6 during lubrication;

[0054] - Figure 8 illustrates an enlarged front view of a scoop from Figure 4;

[0055] - Figure 9 represents the annular outlet wall of Figure 5 during particle recovery;

[0056] - Figure 10 is a three-dimensional schematic view of the upstream side of a first part of an annular outlet wall of the lubrication chamber of Figure 3 according to a second embodiment;

[0057] - Figure 11 is a three-dimensional schematic view of the upstream side of an assembled annular outlet wall of the lubrication chamber of Figure 3 according to the second embodiment;

[0058] - Figure 12 illustrates an enlarged local cross-sectional view of the exit annular wall of Figure 11;

[0059] - Figure 13 represents Figure 12 during lubrication;

[0060] - Figure 14 illustrates an enlarged front view of a scoop from Figure 10;

[0061] - Figure 15 represents a local enlarged view of the first part of an annular outlet wall of Figure 10 during particle recovery;

[0062] - Figure 16 schematically represents a front view of the first part of an annular outlet wall of Figure 10 during the rotation of the lubrication chamber; and

[0063] Figure 17 schematically represents a front view of the first part of an annular outlet wall of Figure 10 when the rotation of the lubrication chamber is stopped. Elements having the same function in the different implementations are referred to by the same reference numerals in the figures. In the figures, the scales and proportions are not strictly to scale for illustrative and clarity purposes. Furthermore, in the description and claims, the terminology axial, radial, and transverse will be adopted, without limitation, with reference to the trihedral axis A, R, T indicated in the figures, the axial axis A being parallel to the longitudinal axis of the lubrication chamber according to the invention.

[0064] Thus, the terms "axial" and "axially" are defined with respect to the axial axis A, which is parallel to the longitudinal axis C of the lubrication chamber. The terms "radial" and "radially" are defined with respect to the axis R, which is perpendicular to the longitudinal axis C of the lubrication chamber.

[0065] In the description, and unless otherwise stated, the terms "internal" and "external" are used without limitation with reference to the radial distance from the longitudinal axis around which the lubrication chamber extends, the term "internal" defining an area radially closer to the longitudinal axis of the lubrication chamber, as opposed to the term "external".

[0066] DESCRIPTION OF IMPLEMENTATION METHODS

[0067] The invention applies to any type of aircraft comprising a turbomachine and in particular to a helicopter as schematically illustrated in Figure 2.

[0068] In this example, the helicopter 100 comprises a fuselage 101 and is equipped with a main rotor 102 associated with a rotating wing for lift and propulsion, as well as a tail rotor 103 for anti-torque. The rotors 102 and 103 are driven by a propulsion system or group 104.

[0069] The propulsion system 104 includes a main gearbox 105 or MGB whose function is to transmit power from the main turboshaft engine to the rotors 102, 103 to set them in motion. The main gearbox 105 conventionally comprises gears forming one or more reduction stages. A first drive shaft 106 connects the main gearbox 105 to the main rotor 102.

[0070] The propulsion system 104 further comprises a main engine, specifically a turbomachine 107, to provide the power necessary for the helicopter's flight. In this turbomachine, all compressor and turbine stages are mounted on a single shaft forming an output shaft. The output shaft of the turbomachine 107 is connected to a second drive shaft 108 via a freewheel 109. The freewheel 109 allows the turbomachine output shaft 107 and the second drive shaft 108 to be rotationally coupled in a first direction of rotation, and to be rotationally decoupled in a second, opposite direction of rotation. The second drive shaft 108 is coupled to the main gearbox 105. A third drive shaft 110 connects the main gearbox 105 to the tail rotor 103.

[0071] Generally, the turbomachine 107 is equipped with a free turbine 111.

[0072] The free wheel 109 allows the main rotor 102 of the helicopter to rotate without driving the free turbine 111 of the turbomachine 107 into autorotation.

[0073] This freewheel 109 is housed in a closed rotating enclosure, ensuring proper lubrication and correct operation even when the oil supply to the enclosure is interrupted. Since this freewheel 109 is a critical component for aircraft operation, particularly during autorotation, any potential damage must be detected as early as possible.

[0074] The aim of the invention is to provide a lubrication chamber that allows both the lubrication function to be maintained by ensuring an adequate oil level while also ensuring the removal of potential particles resulting from wear of the mechanical system housed in the lubrication chamber, in particular the freewheel, with which the lubricating fluid has been in contact.

[0075] Such a lubrication chamber 10 according to the invention for a turbomachine will now be detailed with reference to figures 3 to 17.

[0076] Such a lubrication chamber is particularly suitable for lubricating a mechanical system 1 of a turbomachine.

[0077] For example, mechanical system 1 is a speed reducer of a turbomachine. However, the invention also applies to any mechanical system of an aircraft, in particular a mechanical system related to an aircraft turbomachine, for example in the case of hybridization with the use of an associated electric machine and gas turbine involving the use of a freewheel.

[0078] Thus, according to another example, mechanical system 1 is a freewheel, specifically of a helicopter, as described previously.

[0079] To ensure lubrication of the mechanical system 1 within the lubrication chamber 10, the turbomachine typically includes a lubrication system (not shown). For example, the lubrication system comprises a main lubrication circuit and an auxiliary lubrication circuit for the mechanical system 1, with both the main and auxiliary circuits connected to the lubrication chamber 10. The lubrication system may further include a device for injecting the lubricating fluid 15 into the lubrication chamber 10. The injection device is connected to both the main and auxiliary circuits. The fluid injection is illustrated by arrow FE.

[0080] The main circuit typically includes a feed pump connected to a main reservoir (not shown). The feed pump is configured, for example, to draw the lubricating fluid 15 from the main reservoir and to supply the injection device with lubricating fluid 15.

[0081] The main circuit further includes a return circuit connected to the main reservoir. The return circuit includes a recovery pump configured to recover the lubricating fluid 15 exiting the lubrication chamber and return it to the main reservoir.

[0082] Figure 3 schematically represents in longitudinal section a lubrication chamber according to the invention.

[0083] The lubrication chamber 10 according to the invention is rotatable about an axis of rotation. Figure 3 illustrates the lubrication chamber 10 in operation, i.e., rotating about the axis of rotation.

[0084] The lubrication chamber 10 comprises a cylindrical body 12, an annular inlet wall 14 of a lubricating fluid 15 and an annular outlet wall 16 of the lubricating fluid.

[0085] As previously stated, the fluid 15 is introduced into the lubrication chamber 10 through the inlet annular wall 14 by an injection device as represented by arrow FE and is evacuated from the lubrication chamber 10 through the outlet annular wall 16 by overflow during the rotation of the lubrication chamber 10 as represented by arrows Fs.

[0086] The lubricating fluid 15 is, for example, fuel, oil, coolant, or any other suitable lubricating fluid for lubricating the mechanical system 1. Preferably, the lubricating fluid 15 is oil.

[0087] The cylindrical body 12 extends along a longitudinal axis C between a first end 12A and a second end 12B.

[0088] The longitudinal axis C coincides with the axis of rotation of the lubrication chamber. In the illustrated examples, the longitudinal axis C is parallel to the axial direction A. The longitudinal axis of the cylindrical body is also the longitudinal axis of the lubrication chamber.

[0089] The cylindrical body 12 is hollow. The lubrication chamber 10 comprises an internal cavity 18 radially delimited by the cylindrical body 12.

[0090] The mechanical system 1 to be lubricated is housed in the internal cavity.

[0091] The mechanical system 1 is fixed to the rotating lubrication chamber 10.

[0092] The internal cavity 18 is further delimited axially by the annular entrance wall 14 or upstream wall and the annular exit wall 16 or downstream wall.

[0093] In the present invention, and generally, the terms "upstream" and "downstream" are defined with respect to a main direction F of circulation of the lubrication fluid 15 inside the lubrication enclosure 10, and here along the axial direction A which coincides with the longitudinal axis C, i.e. from right to left with reference to Figure 3.

[0094] The annular inlet wall 14 of the lubricating fluid is fixed to the first end 12A cylindrical body by any suitable fastening means.

[0095] Advantageously, the annular entrance wall 14 has a principal axis parallel, and preferably coaxial, to the longitudinal axis C of the internal cavity.

[0096] The annular entrance wall 14 extends radially between an inner edge 14A and an outer edge 14B.

[0097] As previously stated in the description, and unless otherwise specified, the terms "internal" and "external" are used without limitation to refer to the radial distance from the longitudinal axis C around which the lubrication chamber extends. The term "internal" defines an area radially closer to the longitudinal axis of the lubrication chamber, as opposed to the term "external." Therefore, the internal edge 14A is radially closer to the longitudinal axis C of the lubrication chamber than the external edge 14B.

[0098] The inlet annular wall 14 has an inlet orifice 142 for the lubricating fluid. The inlet orifice 142 is circumferentially delimited by the inner edge 14A of the inlet annular wall.

[0099] The inlet port 142 is configured to be fluidically connected to the injection device to supply lubrication fluid 15 to the lubrication chamber.

[0100] The annular outlet wall 16 of the lubricating fluid is fixed to the second end 12B of the cylindrical body by any suitable fastening means.

[0101] Advantageously, the annular outlet wall 16 has a principal axis parallel to, and preferably coaxial with, the longitudinal axis C of the internal cavity. Figures 4 to 14 describe embodiments of such an annular outlet wall 16 of a lubrication chamber 10 according to the invention. More specifically, Figures 4 to 9 represent a first embodiment and Figures 10 to 17, a second embodiment.

[0102] According to the invention, the outlet wall 16 is shaped to evacuate particles 5 carried along by the lubricating fluid 15 under a centrifugal effect. As explained previously, the particles 5 result from wear of the mechanical system 1 with which the lubricating fluid 15 is in contact.

[0103] With reference to figures 4 to 17, the outlet wall 16 comprises an annular flange 22, a cylindrical portion 24 and at least one evacuation assembly 26 for particles carried by the lubricating fluid 15.

[0104] The annular flange 22 is radially delimited between an inner edge 22A and an outer edge 22B.

[0105] In addition, the annular flange 22 extends axially between an upstream surface 22C and a downstream surface 22D.

[0106] The downstream surface 22D is an external surface to the internal cavity 18 of the lubrication chamber 10.

[0107] With reference to figures 4 to 9, according to the first embodiment, the upstream surface 22C is an internal surface to the internal cavity 18 of the lubrication chamber 10. In the illustrated example, the upstream surface 22C axially delimits the internal cavity 18 of the lubrication chamber 10.

[0108] Preferably, the upstream surface 22C and the downstream surface 22D are substantially flat. The upstream 22C and downstream 22D surfaces are substantially parallel to each other. Preferably, each extends in a plane transverse to the main axis, parallel to the longitudinal axis C of the lubrication chamber.

[0109] Of course, depending on the possible variations, only one of the upstream surfaces 22C and downstream surfaces 22D may be substantially flat, or neither of the upstream surfaces 22C and downstream surfaces 22D may be substantially flat. In another example, at least one of the upstream surfaces 22C and downstream surfaces 22D may be frustoconical.

[0110] The annular outlet wall 16 has a lubrication fluid outlet 162 through which the fluid can overflow during the rotation of the lubrication chamber. More specifically, the annular flange 22 has a lubrication fluid outlet 162. The outlet 162 is a through-hole, meaning that it opens on one side into the upstream surface 22C and on the other side into the downstream surface 22D.

[0111] The outlet orifice 162 is circumferentially delimited by the inner edge 22A of the annular flange 22.

[0112] The outlet port 162 is configured to be fluidly connected to the lubrication system and in particular to a recovery tank (not shown) of the lubrication fluid 15 which may possibly exit through the outlet port under centrifugal force during the rotation of the lubrication enclosure as illustrated by the arrows Fs.

[0113] The cylindrical portion 24 extends axially from the outer edge 22B of the flange 22 towards a free end 24A upstream of the flange 22.

[0114] The cylindrical portion 24 extends radially between an internal circumferential surface 24C and an external circumferential surface 24D.

[0115] Furthermore, the outlet wall 16 advantageously includes a retaining flange 28 extending radially outwards from the free end 24A of the cylindrical portion 24 of the outlet wall. The retaining flange 28 is shaped to fix the outlet wall to the cylindrical body 12 of the lubrication chamber 10 by any suitable fastening means.

[0116] In the example illustrated in the figures, the fixing flange 28 includes several through holes 282. For example, each through hole 282 is intended to receive, for example, a fixing screw also passing through a complementary fixing flange of the cylindrical body 12 of the lubrication chamber 10 for securing by a screw-nut system.

[0117] As previously stated, the outlet wall 16 includes at least one evacuation assembly 26 for particles carried by the lubricating fluid 15.

[0118] Preferably, the outlet wall 16 includes several evacuation sets 26 for particles carried by the lubricating fluid, the sets being distributed angularly around the main axis of the outlet wall 16, coinciding with the longitudinal axis C of the enclosure 10.

[0119] Advantageously, the evacuation assemblies 26 are regularly distributed angularly around the longitudinal axis C.

[0120] For example, the outlet wall 16 has seven particle evacuation sets 26 according to the first embodiment illustrated in figures 4 to 9.

[0121] Each particle evacuation assembly 26 comprises a scoop 30 and an associated discharge conduit 40 from the flange. The scoop 30 is formed in the cylindrical portion 24 of the outlet wall 16, and more specifically in the inner surface 24C of the cylindrical portion 24.

[0122] The scoop 30 is advantageously shaped to concentrate the particles 5 locally under the centrifugal effect for the purpose of their evacuation from the lubrication chamber 10.

[0123] The scoop 30 extends circumferentially over an angular sector of the cylindrical portion 24 of the outlet wall 16 between a first end 30A and a second end 30B.

[0124] The 40 outlet conduit from flange 22 has an internal passage 402 for the circulation of the lubricating fluid 15.

[0125] The conduit 40 extends longitudinally from the outer edge 22B of the flange radially towards the inner edge 22A of the flange.

[0126] In particular, according to the illustrated example, the conduit 40 extends longitudinally in the radial direction R between the outer edge 22B and the inner edge 22A of the flange.

[0127] Alternatively, the conduit 40 can extend longitudinally in a direction inclined relative to the radial direction R between the outer edge 22B and the inner edge 22A of the flange.

[0128] The conduit 40 includes an inlet mouth 404 communicating with the scoop 30 and an outlet orifice 406 for the evacuation of particles 5 carried by the lubricating fluid 15.

[0129] The conduit 40 is arranged downstream of the outer surface 22D of the flange 22.

[0130] In the example illustrated in Figures 4 to 9, relating to the first embodiment, the discharge conduit 40 has a peripheral wall 408 extending from the outer surface 22D of the flange. More precisely, the peripheral wall 408 of the discharge conduit 40 extends downstream of the outer surface 22D of the flange along the axial direction A. The peripheral wall 408 at least partially delimits the internal passage 402 for the circulation of the lubricating fluid 15.

[0131] In the illustrated example, the cross-section of the internal passage 402 of the duct advantageously has a rectangular shape. In this case, the peripheral wall 408 comprises two end portions 408B connected by a central portion 408C. The central portion 408C extends in a plane substantially parallel to the outer surface 22D of the flange, while the end portions 408B extend from the outer surface 22D of the flange in a direction substantially perpendicular to the outer surface 22D of the flange. In other words, the peripheral wall 408 has a U-shaped cross-section. Alternatively, the cross-section of the internal passage 402 of the duct may have another shape, for example, circular or partially circular.

[0132] Advantageously, the outer surface 22D of the flange 22 extends radially in continuous material between the inner edge 22A and the outer edge 22B, thus at least partially defining the internal passage 402 for the circulation of the lubricating fluid 15. More precisely, such an outer surface 22D of the flange 22 defines the upstream end of the internal passage 402 for the circulation of the lubricating fluid, while the peripheral wall 408 of the conduit defines it downstream and in a transverse direction T, perpendicular to the radial axis R. In this case, a through orifice 50 is provided through the flange 22, forming the inlet 404 of the conduit to communicate with the scoop 30. Thus, the through orifice 50 opens upstream of the inner surface 22C of the flange into the scoop 30 and downstream of the outer surface 22D into the conduit 40 evacuation.

[0133] The through orifice 50 is advantageously provided radially near the outer edge 22B of the flange, and more precisely as close as possible to the inner surface 24C of the cylindrical portion 24 at the level of the scoop 30 so as to collect the particles 5 transported by the lubricating fluid and concentrated in the scoop.

[0134] As illustrated in Figure 7, such an outer surface 22D, and in particular an extension of the outer surface towards the outer edge 22B which partially delimits the internal passage 402 for the circulation of the lubricating fluid 15, forms a barrier 22E that forces the circulation of the lubricating fluid through the bottom of the rotating housing, and more specifically, as close as possible to the cylindrical portion 24. The lubricating fluid is thus forced to pass through the orifice 50, then "goes up" the conduit 40 towards the longitudinal axis C, and finally overflows outwards through the outlet 406 of the conduit. This forced circulation through the conduit allows for its rinsing by removing the particles 5 to the outside of the rotating lubrication housing 10.

[0135] In Figure 7, arrow F1 illustrates the level of the lubricating fluid 15 in the housing during its rotation. Arrows F2 illustrate the forced circulation of the lubricating fluid, and arrow F3 schematically shows the overflow of the lubricating fluid 15 to the outside of the housing 10 through the outlet 406 of the conduit 40.

[0136] In such a case, the discharge conduit 40 is juxtaposed to the outer surface 22D of the flange, improving the compactness of the outlet wall 16 of the lubrication chamber 10. As previously stated, the scoop 30 is advantageously shaped to locally concentrate the particles 5 under the centrifugal effect for the purpose of their evacuation from the lubrication chamber 10.

[0137] It extends circumferentially over an angular sector of the cylindrical portion 24 of the outlet wall 16 between a first end 30A and a second end 30B. In order to locally concentrate the particles 5 under centrifugal force, the scoop 30 includes an intermediate portion 30C which is radially further from the longitudinal axis C than at least one of the ends of the scoop 30 as illustrated in Figure 8. Figure 8 shows an enlarged front view of an example of a scoop 30. This intermediate portion 30C, which concentrates the particles 5 to be evacuated, is advantageously arranged opposite the inlet 404 of the discharge duct 40. More precisely, the inlet 404 of the discharge duct 40 communicates directly with the intermediate portion 30C of the scoop 30.

[0138] According to the first embodiment illustrated in figures 4 to 9, the inlet mouth 404 of the evacuation conduit 40 communicating with the scoop 30 is arranged between the first end 30A and the second end 30B.

[0139] According to the illustrated example, the inlet mouth 404 is further centered between the first end 30A and the second end 30B.

[0140] According to the illustrated example, the first end 30A and the second end 30B of the scoop are each closer to the longitudinal axis C than the inlet 404 of the discharge duct. In other words, the scoop 30 includes a first slope P1 between the first end 30A and the intermediate portion 30C, and a second slope P2 between the second end 30B and the intermediate portion 30C, in order to concentrate the particles in the intermediate portion 30C under centrifugal force when the lubrication chamber 10 rotates about its longitudinal axis C. The two slopes P1 and P2 are shown schematically in Figure 4 by arrows. The slopes can be linear, as illustrated in Figure 4, or curvilinear, as in the example shown in Figure 8.

[0141] The slopes P1 and P2 can have the same value but opposite directions. Alternatively, the slopes P1 and P2 can have different values.

[0142] The intermediate portion 30C is thus arranged between the first end 30A and the second end 30B of the scoop opposite the inlet mouth 404 of the discharge conduit 40. More precisely, the inlet mouth 404 of the discharge conduit 40 communicates directly with the intermediate portion 30C of the scoop 30. The inlet mouth 404, and in particular the through orifice 50, is advantageously provided as close as possible radially to the inner surface 24C of the cylindrical portion 24 at the level of the intermediate portion 30C of the scoop 30 so as to collect the particles 5 transported by the lubricating fluid and concentrated in the intermediate portion 30C.

[0143] Preferably, the inlet opening 404, and in particular the through orifice 50, has a perimeter of which at least a portion is radially further away from the longitudinal axis C than the portion of the inner surface 24C forming the intermediate portion 30C of the scoop 30 in order to allow more easily the circulation of the fluid in the conduit 40 and the evacuation of the particles 5 outside the lubrication enclosure 10. Alternatively, the scoop 30 may have other shapes.

[0144] For example, the scoop may have a single slope. In this case, the intermediate portion 30C is arranged at one of the two ends 30A, 30B of the scoop.

[0145] Advantageously, the cylindrical portion 24 of the outlet wall extends axially from the outer edge 82B of the flange towards the peripheral wall 408 of the discharge conduit 40. The cylindrical portion 24 advantageously flares out from its free end 24A towards the peripheral wall 408 of the discharge conduit, i.e., from upstream to downstream, in order to reinforce the forced circulation of the lubricating fluid 15 and particles 5 within the conduit for their removal from the lubrication chamber. Thus, the cylindrical portion has a slope represented by an arrow P in Figure 6. In other words, the cylindrical portion is radially further from the longitudinal axis C towards the peripheral wall than towards its free end 24A.

[0146] The geometry of the outlet wall 16 according to this first embodiment advantageously allows the particles to be concentrated locally in the cylindrical portion 24, and in particular in the scoops 30 by centrifugal effect when the enclosure 10 is rotating, and forces the circulation of the lubricating liquid through the cylindrical portion 24 in order to carry away the particles stored there.

[0147] Indeed, the scoops 30, under the centrifugal effect, allow the particles to be concentrated at the mouth 404 of the conduits 40. Also under the centrifugal effect, the particles 5 accumulate in the bottom of the conduits 40, that is to say against the outer edge of the flange and the cylindrical portion 24.

[0148] As previously mentioned, the dam 22E forces the circulation of the lubricating fluid through the cylindrical portion 24 and the outer edge of the flange into the conduits 40. The lubricating fluid is forced through the opening 404 in the direction of the longitudinal axis C and finally overflows outwards through the outlet 406 of the conduit. This forced circulation through the conduit 40 flushes it by removing the particles 5 to the outside of the rotating lubrication housing 10, as illustrated in Figure 7.

[0149] Furthermore, during the phase of stopping the rotation of the lubrication chamber, the geometry of the outlet wall 16 allows the particles to be flushed out of the conduits by gravity, as illustrated in Figure 9.

[0150] Particles 5 that are not removed during steady-state operation, i.e., at constant rotational speed, are removed during shutdown phases. Indeed, when the rotational speed drops to zero, the upper conduits 40 (Figure 9) empty themselves of the lubricating fluid they contain by gravity. The arrows F4 illustrate this flushing of the conduits 40 and the removal of the lubricating fluid. The lubricating fluid then carries the residual particles outside the enclosure, allowing them to be drawn towards a magnetic plug at the next start-up.

[0151] A second embodiment is illustrated in figures 10 to 17.

[0152] The outlet wall 16 according to this second embodiment differs from the outlet wall 16 according to the first embodiment in that the outlet wall 16 is formed of two parts cooperating with each other: a first part similar to the outlet wall of the first embodiment in which only the flange is modified, and a cover 70.

[0153] In this second embodiment, the outlet wall 16 comprises an annular flange 82, a cylindrical portion 24, a cover 70 and at least one evacuation assembly 26 for particles carried by the lubricating fluid 15.

[0154] The annular flange 82 is radially delimited between an inner edge 82A and an outer edge 82B.

[0155] In addition, the annular flange 82 extends axially between an upstream surface 82C and a downstream surface 82D.

[0156] The downstream surface 82D is an external surface to the internal cavity 18 of the lubrication chamber 10.

[0157] The cylindrical portion 24 extends axially from the outer edge 82B of the flange 82 towards a free end 24A upstream of the flange 22.

[0158] The cylindrical portion 24 extends radially between an internal circumferential surface 24C and an external circumferential surface 24D. In addition, the outlet wall 16 advantageously includes a fixing rim 28 as described previously in the first embodiment.

[0159] The cover 70 is annular in shape and has a main axis coaxial with the main axis of the flange and therefore coaxial with the longitudinal axis C of the lubrication chamber 10. The cover 70 is radially delimited by an internal rim 70A and an external rim 70B.

[0160] In addition, the cover 70 extends axially between an upstream surface 70C and a downstream surface 70D.

[0161] Preferably, the upstream surface 70C and the downstream surface 70D are substantially flat. The upstream 70C and downstream 70D surfaces are substantially parallel to each other. Preferably, each extends in a plane transverse to the main axis, parallel to the longitudinal axis C of the lubrication chamber.

[0162] The downstream surface 70D is arranged opposite the upstream surface 82C of the flange.

[0163] The cover 70 is thus advantageously shaped to be inserted into the cylindrical portion 24 such that the downstream surface 70D is juxtaposed with the upstream surface 82C of the flange. For this purpose, the outer rim 70B of the cover is radially closer to the longitudinal axis C than the cylindrical portion 24 and the outer rim 82B of the flange 82.

[0164] In the illustrated example, the upstream surface 70C of the cover 70 is an internal surface to the internal cavity 18 of the lubrication chamber 10. The upstream surface 70C axially delimits the internal cavity 18 of the lubrication chamber 10.

[0165] The annular outlet wall 16 has an outlet 162 for the lubricating fluid. More specifically, the outlet 162 is circumferentially delimited by the inner edge 82A of the annular flange 82 and the inner rim 70A of the cover 70.

[0166] Advantageously, the inner edge 82A of the annular flange 82 and the inner rim 70A of the cover 70 have a similar contour in both shape and size.

[0167] The outlet 162 is through, that is to say it opens on one side into the upstream surface 70C of the cover and on the other side into the downstream surface 82D of the flange.

[0168] The through-hole 162 can be radially delimited by a cylindrical piece connecting the inner edge 82A of the annular flange 82 to the inner rim 70A of the cover 70. This piece can be shrink-fitted to the annular flange 82 and the cover 70. Alternatively, this piece can be formed continuously with the annular flange 82 and / or the cover 70. Advantageously, the cover 70 and the annular flange 82 form a single piece. For example, the single piece is formed continuously by 3D printing or additive manufacturing. In another example, the cover 70 is attached to the annular flange 82 (or vice versa) by brazing or any other suitable method.

[0169] As previously stated, the outlet wall 16 includes at least one evacuation assembly 26 for particles carried by the lubricating fluid 15.

[0170] Preferably, the outlet wall 16 includes several evacuation sets 26 for particles carried by the lubricating fluid, the sets being distributed angularly around the main axis of the outlet wall 16, coinciding with the longitudinal axis C of the enclosure 10.

[0171] Advantageously, the evacuation assemblies 26 are regularly distributed angularly around the longitudinal axis C.

[0172] According to the example illustrated in figures 10 to 17, the outlet wall 16 has six particle evacuation sets 26.

[0173] As in the first embodiment, each particle evacuation assembly 26 comprises a scoop 30 and an associated discharge conduit 40 from the flange. The scoop 30 is formed in the cylindrical portion 24 of the outlet wall 16, and more precisely in the inner surface 24C of the cylindrical portion 24.

[0174] The scoop 30 is advantageously shaped to concentrate the particles 5 locally under the centrifugal effect for the purpose of their evacuation from the lubrication chamber 10.

[0175] The scoop 30 extends circumferentially over an angular sector of the cylindrical portion 24 of the outlet wall 16 between a first end 30A and a second end 30B.

[0176] One of the differences between the first and second embodiments is that in this second embodiment, the conduit 40 is provided in the flange 82. It is formed in the flange 82. The discharge conduit 40 of the flange 82 has an internal passage 402 for the circulation of the lubricating fluid 15.

[0177] In the example illustrated in Figures 10 to 17, relating to the second embodiment, the flange 82 comprises at least one open cavity 90 delimited by a peripheral wall 92. The peripheral wall 92 of the open cavity 90 extends downstream of the outer surface 82D of the flange 82 in the axial direction A. The peripheral wall 92 at least partially delimits the internal passage 402 for the circulation of the lubricating fluid 15 in the conduit 40. Thus, the peripheral wall 92 of the open cavity 90 forms at least partially a peripheral wall 408 of the conduit 40 and thus at least partially delimits the internal passage 402 for the circulation of the lubricating fluid 15. The open cavity 90 forms at least partially the internal passage 402 for the circulation of the lubricating fluid 15.

[0178] The open cavity 90 and the conduit 40 extend longitudinally from the outer edge 82B of the flange radially towards the inner edge 82A of the flange.

[0179] In particular, according to the illustrated example, the conduit 40 extends longitudinally in a direction inclined relative to the radial direction R between the outer edge 22B and the inner edge 22A of the flange.

[0180] Alternatively, the conduit 40 can extend longitudinally in the radial direction R between the outer edge 22B and the inner edge 22A of the flange.

[0181] In the illustrated example, the cross-section of the internal passage 402 of the conduit advantageously has a rectangular shape. In this case, the peripheral wall 408 comprises two end portions 408B connected by a central portion 408C. The central portion 408C extends in a plane substantially parallel to the outer surface 22D of the flange, while the end portions 408B extend from the outer surface 22D of the flange in a direction substantially perpendicular to the outer surface 22D of the flange. In other words, the peripheral wall 408 has a U-shaped cross-section.

[0182] Alternatively, the internal passage section 402 of the conduit may have another shape, for example circular or partially circular.

[0183] The annular cover 70 is shaped to delimit at least partially the internal passage 402 for the circulation of the lubricating fluid 15. More specifically, the outer surface 70D of the cover 70 delimits upstream the internal passage 402 for the circulation of the lubricating fluid while the peripheral wall 408 of the conduit delimits it downstream and in a transverse direction T perpendicular to the radial axis R.

[0184] The annular cover 70 is shaped to form an opening 404 for the discharge conduit 40, which communicates with the scoop 30. To this end, the outer rim 70B of the annular cover 70 is closer to the longitudinal axis C than the outer rim 82B of the annular flange 82, allowing a passage between the scoop 30 and the conduit 40, thus forming the opening 404 of the conduit. The conduit 40 further includes an outlet 406 for the discharge of particles 5 carried by the lubricating fluid 15.

[0185] The annular cover 70 thus forms a barrier 70E, forcing the circulation of the lubricating fluid through the bottom of the rotating housing, specifically as close as possible to the cylindrical portion 24. The lubricating fluid is thus forced to pass through the opening 404, then "ascends" the conduit 40 towards the longitudinal axis C, and finally overflows outwards through the outlet 406 of the conduit. This forced circulation through the conduit allows for its rinsing by removing the particles 5 to the outside of the rotating lubrication housing 10.

[0186] In Figure 13, arrow F1 illustrates the level of the lubricating fluid 15 in the housing during its rotation. Arrows F2 illustrate the forced circulation of the lubricating fluid, and arrow F3 schematically shows the overflow of the lubricating fluid 15 to the outside of the housing 10 through the outlet 406 of the conduit 40.

[0187] As previously stated, the scoop 30 is advantageously shaped to locally concentrate the particles 5 under the centrifugal effect for the purpose of their evacuation from the lubrication chamber 10.

[0188] As with the first embodiment, the scoop 30 extends circumferentially over an angular sector of the cylindrical portion 24 of the outlet wall 16 between a first end 30A and a second end 30B.

[0189] In order to concentrate the particles 5 locally under centrifugal force, the second end 30B is radially further from the longitudinal axis C than the first end 30A of the scoop 30 as illustrated in Figure 14. Figure 14 is an enlarged front view of an example of a scoop 30. In other words, the scoop 30 includes a slope between the first end 30A and the second end 30B. This slope can be linear or curvilinear, as in the example shown in Figure 14.

[0190] This second end 30B, concentrating the particles 5 to be evacuated, is advantageously arranged in relation to the inlet mouth 404 of the evacuation conduit 40. More precisely, the inlet mouth 404 of the evacuation conduit 40 communicates directly with the second end 30B of the scoop 30.

[0191] According to the example illustrated in Figure 10, the scoop 30 has a flared shape in the circumferential direction from the first end 30A to the second end 30B. In other words, the scoop is wider at the second end 30B than at the first end 30A in the axial direction.

[0192] Alternatively, scoop 30 may have other shapes. According to one alternative, scoop 30 may have a shape similar to that described previously in the first embodiment.

[0193] Similarly, the shape of the scoop in this second embodiment can be applied to the first embodiment.

[0194] Advantageously, the cylindrical portion 24 of the outlet wall extends axially from the outer edge 82B of the flange towards the peripheral wall 408 of the discharge conduit 40. The cylindrical portion 24 advantageously flares out from its free end 24A towards the peripheral wall 408 of the discharge conduit, i.e., from upstream to downstream, in order to reinforce the forced circulation of the lubricating fluid 15 and particles 5 within the conduit for their removal from the lubrication chamber. Thus, the cylindrical portion has a slope represented by an arrow P in Figure 12. In other words, the cylindrical portion is radially further from the longitudinal axis C towards the peripheral wall than towards its free end 24A.

[0195] As with the first embodiment, the geometry of the outlet wall 16 according to this second embodiment advantageously allows the particles to be concentrated locally in the cylindrical portion 24, and in particular in the scoops 30 by centrifugal effect when the enclosure 10 is rotating, and forces the circulation of the lubricating liquid through the cylindrical portion 24 in order to carry away the particles stored there (figure 13).

[0196] Indeed, the scoops 30, under the centrifugal effect, allow the particles to be concentrated at the mouth 404 of the conduits 40. Also under the centrifugal effect, the particles 5 accumulate in the bottom of the conduits 40, that is to say against the outer edge of the flange and the cylindrical portion 24.

[0197] As previously mentioned, the dam 70E forces the circulation of the lubricating fluid through the cylindrical portion 24 and the outer edge of the flange into the conduits 40, as illustrated in Figures 13 and 15. In Figure 15, the cover has been omitted for clarity. The lubricating fluid 15 is forced through the opening 404 in the direction of the longitudinal axis C and finally overflows outwards through the outlet 406 of the conduit. This forced circulation through the conduit 40 flushes it by removing the particles 5 from the outside of the rotating lubrication housing 10, as illustrated in Figures 13, 15, and 17.

[0198] Figure 16 shows the outlet wall 16 from the front when the enclosure is rotating. The lubricating fluid 15 fills the cavity by centrifugal force, ensuring good lubrication of the mechanical system to be lubricated until it reaches the orifice 162 of the outlet wall where the excess fluid can be discharged by overflow.

[0199] Furthermore, in the phase of stopping the rotation of the lubrication chamber, the geometry of the outlet wall 16 allows the particles to be flushed out of the conduits by gravity as illustrated in Figure 17.

[0200] The particles 5 that are not removed during steady-state operation, i.e., at constant rotational speed, are removed during shutdown phases. Indeed, when the rotational speed drops to zero, the conduits 40 in the upper part (Figure 17) empty themselves by gravity of the lubricating fluid they contain. The lubricating fluid then carries the residual particles outside the enclosure, allowing them to be drawn towards a magnetic plug at the next start-up.

[0201] Furthermore, the geometry of the outlet wall 16 according to this second embodiment improves the rinsing of the conduits 40 and increases the removal rate of particles 5. The scoops 30 are asymmetrical centrifugal concentration cells for the filings, relative to the conduit inlet 404. Under nominal rotation, the particles 5 are concentrated at the conduit inlet 404 and in the scoops 30 (Figure 16).

[0202] During the transitional shutdown phase, the centrifugal lubricating fluid ring ruptures before the rotation comes to a complete stop (Figure 17). The lubricating fluid reservoir 100 is therefore stationary during this transitional shutdown phase, while the housing 10, and consequently the outlet wall 16, advantageously continues to rotate by inertia: the scoops 30 make several passes through the lubricating fluid reservoir 100, drawing a small quantity of lubricating fluid with each pass. When the scoop 30, loaded with lubricating fluid, continues to rotate and reaches a sufficient height, it empties by gravity through the conduit. This emptying carries away the particles and rinses the conduits outwards from the rotating housing 10.

Claims

DEMANDS 1. Lubrication chamber (10) for a mechanical system (1), in particular an aircraft turbomachine, the chamber comprising: - a cylindrical body (12) extending along a longitudinal axis (C), - an annular inlet wall (14) of a lubricating fluid (15) and an annular outlet wall (16) of the lubricating fluid fixed respectively to a first end (12A) and to a second end (12B) of the cylindrical body, - an internal cavity (18) delimited radially by the cylindrical body (12) and axially by the annular inlet wall (14) and the annular outlet wall (16), the mechanical system (1) to be lubricated being housed in the internal cavity (18), characterized in that the lubrication chamber (10) is mobile in rotation about the longitudinal axis (C), and in that the outlet wall (16) is shaped to evacuate particles (5) carried by the lubricating fluid (15) under a centrifugal effect, the particles (5) resulting from wear of the mechanical system (1) with which said lubricating fluid is in contact.

2. Lubrication chamber according to claim 1, wherein the outlet wall (16) comprises: - an annular flange (22; 82) radially delimited between an inner edge (22A; 82A) and an outer edge (22B; 82B), and presents an outer surface (22D; 82D) to the internal cavity (18) of the lubrication chamber, - a cylindrical portion (24) extending axially from the outer edge of the flange towards a free end, - and at least one evacuation assembly (26) for particles (5) carried along by the lubricating fluid (15) comprising: -- a scoop (30) formed in the cylindrical portion (24) of the outlet wall (16) and shaped to locally concentrate the particles under centrifugal force, -- a discharge conduit (40) from the flange (22; 82) having an internal passage (402) for the circulation of the lubricating fluid, the conduit (40) extending longitudinally from the outer edge (22B; 82B) of the flange radially towards the inner edge (22A; 82A) of the flange, the radial direction (R) being perpendicular to the longitudinal axis (C), and comprising an inlet opening (404) communicating with the scoop (30) and an outlet orifice (406) for the discharge of particles (5) carried by the lubricating fluid, the conduit (40) being arranged downstream of the outer surface (22D; 82D) of the flange (22).

3. Lubrication chamber according to claim 2, in which the discharge conduit (40) has a peripheral wall (408) extending from the outer surface (22D; 82D) of the flange, the peripheral wall (408) delimiting at least partially the internal passage (402) for the circulation of the lubricating fluid (15).

4. Lubrication chamber according to claim 3, in which the outer surface (22D) of the flange extends radially between the inner edge (22A) and the outer edge (22B) delimiting at least partially the internal passage (402) for the circulation of the lubricating fluid (15), and a through orifice (50) is provided through the flange forming the inlet mouth (404) of the conduit.

5. Lubrication chamber according to claim 3, in which the outlet wall (16) has an annular cover (70) juxtaposed to the flange (82) and arranged upstream of the flange, the annular cover (70) being shaped to delimit at least partially the internal passage (402) for the circulation of the lubricating fluid (15) and to form the mouth (404) of the discharge conduit.

6. Lubrication chamber according to claim 5, in which the annular cover (70) extends radially between an inner rim (70A) and an outer rim (70B), the outer rim (70B) of the annular cover being closer to the longitudinal axis (C) than the outer rim (82B) of the annular flange (82).

7. Lubrication chamber according to any one of claims 2 to 6, in which the scoop (30) extends circumferentially over an angular sector of the cylindrical portion (24) of the outlet wall (16) between a first end (30A) and a second end (30B).

8. Lubrication chamber according to claim 7, in which the inlet mouth (404) of the discharge conduit (40) communicating with the scoop (30) is arranged between the first end (30A) and the second end (30B), the first end (30A) and the second end (30B) each being closer to the longitudinal axis (C) than the inlet mouth (404) of the discharge conduit.

9. Lubrication chamber according to claim 7, in which the inlet mouth (404) of the discharge conduit (40) communicating with the scoop (30) is arranged near the second end (30B), the first end (30A) being closer to the longitudinal axis (C) than the second end (30B) of the scoop.

10. Lubrication chamber according to any one of claims 8 or 9, wherein the scoop (30) has a flared shape in the circumferential direction from the first end (30A) to the second end (30B).

11. Lubrication chamber according to any one of claims 3 to 9, wherein the cylindrical portion (24) of the outlet wall extends axially from the outer edge of the flange to the peripheral wall of the discharge conduit, the cylindrical portion flaring out from the free end of the cylindrical portion towards the peripheral wall of the discharge conduit.

12. Lubrication chamber according to any one of claims 2 to 11, in which the outlet wall comprises several evacuation assemblies (26) for the particles (5) carried by the lubricating fluid (15), the assemblies being distributed angularly around the longitudinal axis (C).

13. Lubrication chamber according to claim 12, in which the evacuation assemblies (26) are regularly distributed angularly around the longitudinal axis (C).

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