Supply and recovery of lubricating oil in the mechanical reducer of an aircraft turbine

Abstract

The present invention relates to the supply and recovery of lubricating oil in a mechanical reducer of an aircraft turbine. The present invention also relates to a lubricating oil distributor, a reducer, and an aircraft turbine, in particular for a mechanical reducer of an aircraft turbine. The distributor has a body with a generally annular shape around an axis X and includes first and second independent oil circuits. The first oil circuit includes a first oil inlet that is connected, through a first chamber, to a plurality of oil outlets distributed on the body around the axis X, and the second oil circuit includes a second oil inlet that is connected, through a second chamber, to a plurality of oil outlets distributed on the body around the axis X. The first chamber and the second chamber extend circumferentially around the axis X with different diameters. It is characterized in that the first oil circuit and the second oil circuit are formed in the body and are respectively a recovery circuit and an oil supply circuit for the teeth of the reducer.

Description

Field of the Invention

[0001] The present invention relates to the field of mechanical speed reducers for turbines, in particular aircraft turbines, and more particularly to the supply and recovery of lubricating oil in these speed reducers. Background of the Invention

[0002] The prior art particularly includes the documents WO-A1-2010 / 092263, FR-A1-2987416, EP-A1-2317181, US-A1-2011 / 124461 and FR-A1-3041054.

[0003] The function of a mechanical speed reducer is to change the speed and torque ratio between the input and output shafts of a mechanical system.

[0004] A new generation of twin-spool turbines, particularly those with a high bypass ratio, includes a mechanical speed reducer to drive the shaft of the fan. Generally, the purpose of the speed reducer is to convert the so-called fast rotational speed of the shaft of the power turbine into a slower rotational speed for the shaft driving the fan.

[0005] Such a speed reducer includes a central pinion called the sun gear, a ring gear, and pinions called planet gears that mesh between the sun gear and the ring gear. The planet gears are held by a frame called the planet carrier. The sun gear, the ring gear, and the planet carrier are planetary gears because their axes of rotation coincide with the longitudinal axis X of the turbine. The planet gears each have a different axis of rotation and are evenly distributed around the axis of the planet gears on the same operating diameter. These axes are parallel to the longitudinal axis X.

[0006] There are various speed reducer architectures. In the prior art of twin-spool turbines, the speed reducer is of the planetary or epicyclic type. In other similar applications, there are so-called differential architectures or compound architectures.

[0007] - In a planetary speed reducer, the planet carrier is fixed and the ring gear forms the output shaft of the device, which rotates in a direction opposite to that of the sun gear.

[0008] - In an epicyclic speed reducer, the ring gear is fixed and the planet carrier is the output shaft of the device, which rotates in the same direction as the sun gear.

[0009] - In a differential speed reducer, no element rotates fixed. The ring gear rotates in a direction opposite to that of the sun gear and the planet carrier.

[0010] The speed reducer can be composed of one or more meshing stages. This meshing is ensured in different ways (e.g., by contact, friction, or magnetic field).

[0011] There are various types of contact engagement, such as straight teeth, helical teeth or herringbone teeth.

[0012] The present invention provides an improved speed reducer through a simple, effective and economical solution to improve the supply and recovery of lubricating oil in the speed reducer. Summary of the Invention

[0013] The present invention relates to a lubricating oil distributor for a mechanical speed reducer, especially for a turbine of an aircraft. The distributor has a body with a generally annular shape around an axis X and includes an independent oil circuit formed in the body. It is characterized in that the circuit includes:

[0014] - An oil recovery circuit configured to recover oil and including a plurality of first oil inlets distributed on the body around the axis X and connected to at least one first oil outlet through a first annular chamber, and

[0015] - An oil supply circuit configured to supply oil, in particular, to the teeth of the speed reducer and including a second oil inlet connected to a plurality of second oil outlets distributed on the body around the axis X through a second annular chamber. The first chamber and the second chamber extend circumferentially around the axis X with different diameters.

[0016] Therefore, the distributor is designed to perform multiple functions of oil supply and recovery of lubricating oil from the speed reducer. These functions are provided by independent oil circuits. One oil circuit is dedicated to supplying the speed reducer for lubrication. Another oil circuit is dedicated to recovering the oil that has lubricated the speed reducer and discharging the oil for recirculation. The circuits are independent so that oil supply does not interfere with oil recovery and vice versa. This also limits or even prevents the risk of heating the lubricating oil by the recovered oil, which is hotter due to absorbing heat during the lubrication process of the speed reducer.

[0017] Quickly discharging the oil from the cavity of the speed reducer can improve its efficiency. In fact, the faster the heat generated by power transmission is discharged, the lower the operating temperature and the shorter the time the oil has to be heated.

[0018] In the case of planetary type operation, that is, in the case of having a fixed planet carrier and a rotating ring gear, it is impossible to centrifuge the oil around the sun gear. This may lead to so-called agitation or even violent churning, which corresponds to the accumulation of hot oil in the speed reducer.

[0019] Thus, the present invention is compatible with planetary speed reducers having a fixed planet carrier and a rotating ring gear. The present invention is also compatible with any type of teeth (spur, helical, herringbone). The present invention is also compatible with any type of planet carrier, whether integral or of the cage / and cage carrier type. Finally, the present invention is compatible with any type of planetary gear bearing, whether the planetary gear bearing is constituted by rolling elements, hydrodynamic bearings, etc.

[0020] The distributor according to the present invention may include one or more of the following features, which are adopted independently of each other or in combination with each other:

[0021] - The circuit includes an additional oil supply circuit, which is independent and is configured to supply oil to the bearings of the speed reducer in particular. The additional supply circuit includes at least one third oil inlet, which is connected to a plurality of third oil outlets distributed on the body around the axis X through a third annular chamber.

[0022] - The body of the distributor is made as a single piece.

[0023] - The first oil outlet of the recovery circuit, the second oil inlet of the supply circuit, and the third oil inlet of another supply circuit are oriented in the radial direction with respect to the axis X.

[0024] - Each chamber is of the closed type, as opposed to, for example, a groove, the inner or outer periphery of which is open.

[0025] - The first chamber, the second chamber, and / or the third chamber are formed by coaxially and tightly connected tubular rings.

[0026] - The first outlet of the recovery circuit, the second outlet of the supply circuit, and the third outlet of the additional supply circuit are axially oriented in the same direction.

[0027] - The inlet of the third circuit is located near the outlet of the first circuit.

[0028] - The distributor includes bosses distributed on the body around the axis X. Each of these bosses includes: a first inlet of the recovery circuit; and one of the second outlets of the supply circuit.

[0029] - The diameter of the chamber of the additional supply circuit is greater than the diameter of the chamber of the supply circuit, and the diameter of the chamber of the supply circuit is preferably greater than the diameter of the chamber of the recovery circuit.

[0030] The present invention also relates to a mechanical reducer for an aircraft turbine, the reducer comprising: a cage defining a housing for receiving a central sun gear having a rotational axis X; planetary gears arranged around the sun gear; deflectors fixed to the cage and arranged between the planetary gears; a distributor as described above attached and fixed to the cage and connected to the deflectors, the distributor being configured to supply lubricating oil to the teeth of the sun gear and the planetary gears or even to the planetary gear bearings and to recover at least a portion of the oil through the said deflectors.

[0031] Advantageously, each of the deflectors includes a block having two opposite sides with a substantially curved shape that extend around the planetary gears, and oil inlet holes are located on the two opposite sides and are in fluid communication with an oil recovery circuit for recovering oil from the teeth of the reducer.

[0032] Preferably, the oil inlet holes are connected through an internal passage of the block to an oil outlet port of the block of the deflector, and the internal passage of the block is shaped to convey the recovered oil to the port by means of the centrifugal force exerted on the projected oil by the planetary gears arranged on either side of the deflector.

[0033] The present invention also relates to a deflector for a mechanical reducer for a turbine of an aircraft in particular, the deflector being for insertion between two adjacent planetary gears of the reducer, the deflector including a block having a first lubricating oil circuit including at least one oil inlet port and at least one oil outlet hole or port for lubricating the reducer, characterized in that it further includes a second independent lubricating oil circuit including at least an oil inlet hole and at least one oil outlet port for oil recirculation.

[0034] Thus, the deflector combines multiple functions, including the supply and recovery of lubricating oil for the reducer. Each of these functions is provided by an oil circuit. The first oil circuit is dedicated to supplying the reducer for lubrication. The second oil circuit is dedicated to recovering the oil that has lubricated the reducer and discharging the oil for recirculation. The circuits are independent so that oil supply does not interfere with oil recovery and vice versa. This also limits or even prevents the risk of heating the lubricating oil by the recovered oil, which is hotter due to absorbing heat during the lubrication of the reducer.

[0035] The present invention is compatible with planetary speed reducers having a fixed planet carrier and a rotating ring gear. The present invention is also compatible with any type of gear (spur gear, herringbone gear). The present invention is also compatible with any type of planet carrier, whether integral or of the cage / cage carrier type. Finally, the present invention is compatible with any type of planetary gear bearing, whether the planetary gear bearing is constituted by rolling elements, hydrodynamic bearings, etc.

[0036] The deflector according to the present invention may include one or more of the following features, which are adopted independently of each other or in combination with each other:

[0037] - The oil inlet port of the first circuit and the oil outlet port of the second circuit are positioned close to each other and on the same face of the block.

[0038] - The oil inlet port of the first circuit and the oil outlet port of the second circuit are oriented in a substantially parallel direction.

[0039] - The deflector includes a radially inner end and a radially outer end. The radially inner end is for orientation towards the main rotation axis of the speed reducer, and the radially outer end is for radial orientation opposite to this axis. The oil inlet port of the first circuit and the oil outlet port of the second circuit are located at the radially inner end.

[0040] - The first circuit includes an outlet and an oil projection hole, which are located at the radially inner end.

[0041] - The first circuit may include an oil outlet port or hole, which is located at the radially outer end.

[0042] - The block includes two opposite sides having a substantially curved shape, and the oil inlet holes of the second circuit are located on the two opposite sides.

[0043] - The oil inlet holes are located at the radially inner end.

[0044] - Each of the ports includes a tubular water seal and a fluid connection nozzle.

[0045] The present invention also relates to a planet carrier of a mechanical speed reducer, in particular of a turbine of an aircraft, the planet carrier including: a cage that defines a receiving portion for receiving a central sun gear having a rotation axis X; planetary gears that are arranged around the sun gear; and deflectors as described above, each of which is fixed to the cage and inserted between two adjacent planetary gears.

[0046] Furthermore, the present invention relates to a mechanical speed reducer, in particular of a turbine of an aircraft, the mechanical speed reducer including at least one element as described above (deflector, distributor, planet carrier, etc.).

[0047] Finally, the present invention relates to a turbine comprising at least one element (deflector, distributor, planet carrier, reducer, etc.) as described above.

[0048] The features of the different aspects of the present invention may be combined with each other. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] Other features and advantages will appear from the following description of non - exhaustive embodiments of the present invention and with reference to the drawings, in which:

[0050] Figure 1 is a schematic cross - sectional view of a turbine using the present invention,

[0051] Figure 2 is a partial cross - sectional view of a mechanical reducer,

[0052] Figure 3 is a cross - sectional view of a mechanical reducer integrating multiple aspects of the present invention,

[0053] Figure 4 is for Figure 3 a perspective view of a lubricating oil distributor of the reducer in

[0054] Figure 5 is Figure 3 a partial cross - sectional perspective view of the reducer of Figure 4 and shows the connection of the distributor of

[0055] Figure 6 is Figure 3 a perspective view of the deflector of the reducer of

[0056] Figure 7 is Figure 6 another perspective view of the deflector of

[0057] Figure 8 is Figure 3 a partial cross - sectional view of the reducer of

[0058] Figure 9 is similar to Figure 3 the view of DETAILED DESCRIPTION OF THE INVENTION

[0059] Figure 1The turbine 1 is described, which conventionally includes a rotational axis X, a fan S, a low-pressure compressor 1a, a high-pressure compressor 1b, a combustion annular chamber 1c, a high-pressure turbine 1d, a low-pressure turbine 1e, and an exhaust nozzle 1h. The high-pressure compressor 1b and the high-pressure turbine 1d are connected by a high-pressure shaft 2 and together with this high-pressure shaft 2 form a high-pressure (HP) body. The low-pressure compressor 1a and the low-pressure turbine 1e are connected by a low-pressure shaft 3 and together with this low-pressure shaft 3 form a low-pressure (LP) body.

[0060] The fan S is driven by a fan shaft 4, and the fan shaft 4 is driven by the LP shaft 3 by means of a speed reducer 6. This speed reducer 6 is generally of the planetary type or the epicyclic type.

[0061] The speed reducer related to the planetary type is described below, in which the ring gear is rotatably movable.

[0062] The speed reducer 6 is positioned in the upstream part of the turbine. A fixed structure is arranged to form a housing E around the speed reducer 6, and this fixed structure schematically includes an upstream part 5a and a downstream part 5b here, and the upstream part 5a and the downstream part 5b constitute the engine housing or stator 5. Here, the housing E is closed upstream by a seal at the position of the bearing allowing the fan shaft 4 to pass through, and is closed downstream by a seal at the position enabling the LP shaft 3 to pass through.

[0063] Figure 2 The speed reducer 6 is shown, and this speed reducer 6 can take the form of different architectures according to whether certain parts are stationary or rotating. On the inlet side, the speed reducer 6 is connected to the LP shaft 3, for example, by an internal spline 7a. Thus, the LP shaft 3 drives the planet pinions known as the sun gear 7. Conventionally, the rotational axis of the sun gear 7 is the same as the rotational axis X of the turbine, and this sun gear 7 drives a series of pinions known as planet gears 8, which are evenly distributed around the rotational axis X at the same diameter. This diameter is equal to twice the operating center distance between the sun gear 7 and the planet gears 8. For this type of application, the number of planet gears 8 is generally limited between three and seven.

[0064] A set of planet gears 8 is held by a frame known as a planet carrier 10. Each planet gear 8 rotates around its own axis Y and meshes with a ring gear 9.

[0065] In this planetary configuration, the set of planet gears 8 is held by the planet carrier 10 fixed to the engine housing or stator 5. Each planet gear drives the ring gear, and this ring gear is connected to the fan shaft 4 by a ring gear carrier 12.

[0066] Each planetary gear 8 is rotatably mounted by means of a bearing 11 (e.g., of the rolling bearing type or hydrodynamic bearing type). Each bearing 11 is mounted on one of the axles 10b of the planet carrier 10, and all the axles are positioned relative to one another by means of one or more structural frames 10a of the planet carrier 10. There are a plurality of axles 10b and bearings 11, the number of axles 10b and bearings 11 being equal to the number of planetary gears. For reasons of operation, assembly, manufacture, inspection, repair or spare parts, the axles 10b and the frames 10a can be divided into a plurality of parts.

[0067] For the same reasons as above, the teeth of the speed reducer can be divided into a plurality of helical portions, each helical portion having a median plane P. In the example shown, the ring gear is divided into two ring gear halves:

[0068] - an upstream ring gear half 9a, which consists of a rim 9aa and a mounting flange half 9ab. On the rim 9aa is the upstream helical portion of the teeth of the speed reducer. This upstream helical portion meshes with the helical portion of the planetary gear 8, which helical portion of the planetary gear 8 meshes with the helical portion of the sun gear 7.

[0069] - a rear ring gear half 9b, which consists of a rim 9ba and a mounting flange half 9bb. On the rim 9ba is the downstream helical portion of the teeth of the speed reducer. This downstream helical portion meshes with the helical portion of the planetary gear 8, which helical portion of the planetary gear 8 meshes with the helical portion of the sun gear 7.

[0070] The mounting flange half 9ab of the upstream ring gear 9a and the mounting flange half 9bb of the downstream ring gear 9b form the mounting flange 9c of the ring gear. The ring gear 9 is attached to the ring gear carrier by assembling the mounting flange 9c of the ring gear and the mounting flange 12a of the ring gear carrier using, for example, a bolt assembly.

[0071] Figure 2 The arrows in show the oil flow in the speed reducer 6. Oil enters the speed reducer 6 from the stator component 5 through various devices into the distributor 13, which devices will not be specified in this view as they are specific to one or more types of architectures. The distributor is divided into two parts, each part generally being repeated by the same number of planetary gears. The injector 13a has the function of lubricating the teeth, and the arm 13b has the function of lubricating the bearings. Oil is supplied to the injector 13a to come out through the end 13c to lubricate the teeth. Oil is also supplied to the arm 13b and flows through the supply port 13d of the bearing. Then, the oil flows through the shaft into the buffer 10c and out through the hole 10d to lubricate the bearings of the planetary gears.

[0072] Figure 3 An embodiment of the speed reducer 6 is shown that includes multiple aspects of the present invention.

[0073] One of these aspects relates to a lubricant dispenser and will be described in particular with reference to Figure 4 、 Figure 5 and Figure 9 below. Another aspect of the invention relates to a deflector and will be described with reference to Figures 5 to 8 below.

[0074] The speed reducer 6 includes a planet carrier 10 of the type having a cage 14 and a cage frame 15, and the cage 14 and the cage frame 15 are connected by a ball-and-socket joint.

[0075] The cage 14 includes two radial annular walls 14a, 14b extending around an axis X, and these walls 14a, 14b are parallel and are an upstream radial wall 14a and a downstream radial wall 14b respectively. The walls 14a, 14b are connected to each other at the outer peripheries of the walls 14a, 14b by pairs of bridging members 14c, 14d evenly distributed around the axis X. These pairs of bridging members provide a structural connection between the walls 14a, 14b. Each pair of bridging members includes two bridging members, which are a radially outer bridging member 14c and a radially inner bridging member 14d respectively, and the radially outer bridging member 14c and the radially inner bridging member 14d extend substantially parallel to each other along the axis X at a radial distance from each other.

[0076] Each pair of bridging members forms a U-shaped clip to accommodate the fingers 15a of the cage frame 15. In other words, each pair of bridging members defines a receiving portion for the fingers 15a of the cage frame 15 between the bridging members. An oblong opening 14e is formed in the rear wall 14b such that the fingers 15a can pass between the bridging members 14c, 14d. The wall 14a may include a similar opening axially aligned with the opening 14e of the wall 14b.

[0077] The number of fingers 15a is equal to the number of pairs of bridging members 14c, 14d, and in the illustrated example this number is 5. These fingers 15a project axially upstream from a ring 15b of the cage frame 15 extending around the axis X. The fingers 15a of the cage frame 15 are engaged in the receiving portion between the bridging members by axially translating through the opening 14e in the rear wall 14b from the rear.

[0078] Each finger 15a includes, substantially in the middle of the finger, a mounting notch for a bearing (not shown), the mounting notch of the bearing being adapted to be traversed by a cylindrical pin 17 carried by each pair of bridging members 14c, 14d. Each pin 17 passes through the accommodation portion between the bridging members and has a substantially radial orientation with respect to the axis X. Each pin 17 includes a cylindrical body 17a which is connected at one end (here the radially outer end) to a collar 17b. The pin 17 is here engaged by radially translating it from the outside through a radial hole in the bridging members 14c, 14d, the collar 17b of the pin 17 being adapted to make radial contact with the flat face 14ca of the outer bridging member 14c. After the pin 17 has been inserted into the hole in the bridging member until the collar 17b is placed on the outer bridging member, the collar 17b is fixed to the bridging member, for example by screwing.

[0079] As shown, in the assembled position, the ring 15b of the cage 15 is axially spaced from the downstream wall 14b facing the cage 14 by a predetermined distance L1 ( Figure 3 ).

[0080] The cage 14 defines an internal accommodation portion for accommodating a sun gear 7, a planetary gear 8 and a deflector 18 having an axis X, the planetary gear 8 being arranged around the sun gear 7 and meshing with the sun gear 7, the deflector 18 being described below with reference to Figures 5 to 9 in detail.

[0081] The speed reducer 6 includes an improved lubricating oil distributor 13 which is clearly shown in Figure 4 ).

[0082] The distributor 13 is generally of an annular shape around the axis X and is made as a single piece. The distributor 13 is attached to the planet carrier 10 and may for this purpose include a bracket (not shown) on the cage 14 of the planet carrier.

[0083] The distributor 13 includes separate oil circuits 20, 21, 23 which include:

[0084] - a first oil circuit 20 which includes a first oil inlet 20a which is connected, via a first annular chamber 20b, to a plurality of oil outlets 20c distributed on a first circumference C1 around the axis X,

[0085] - a second oil circuit 21 which includes a second oil inlet 21a which is connected, via a second annular chamber 21b, to a plurality of oil outlets 21c distributed on a second circumference C2 around the axis X, and

[0086] - A third independent oil circuit 23 for recovering oil from the speed reducer, the third oil circuit including a plurality of oil inlets 23a distributed on a third circumference C6 around the axis X and connected to at least one oil outlet 23c through a third annular chamber 23b.

[0087] As Figure 4 shown, the inlets 23a and the outlet 20c are preferably formed in the bosses 25 of the distributor 13. These bosses 25 are evenly distributed around the axis X on the same axial side (here the upstream axial side) of the distributor 13.

[0088] The circumference C1 has a diameter D1, the circumference C2 has a diameter D2, and the circumference C6 has a diameter D6.

[0089] D2 is greater than D1. D6 is here similar to or even exactly the same as D1, but may be different from D1.

[0090] In the example shown, D1, D2, and D6 are each greater than D5, which is the inner diameter of the ring 15b. The distributor 13 is smaller in diameter than D5, which allows the assembly / dismantling of the distributor without contacting the rest. Due to the pins 17 and the deflector 18, the cage 14 and the cage frame 15 are first installed, then the sun gear 7, the planet gears 8, the axle 10b, and finally the distributor 13.

[0091] The chambers 20b, 21b, 23b are formed by coaxially and tightly connected tubular rings, i.e., the tubular walls of these chambers are fused together. These chambers have an axial cross-section of any overall shape, and the channel cross-section of the chambers is substantially constant over the entire angular range of the chambers. In the example shown, the chambers 21b, 23b have a cross-section with a semi-circular overall shape, and the chamber 20b has a cross-section with a rectangular overall shape. We also see that these chambers are arranged in a radially stepped manner, where the chamber 21b extends around the chamber 20b, and the chamber 20b extends around the chamber 23b (see Figure 5 ).

[0092] The first chamber 20b extends substantially on a circumference C4 with a diameter D4, and the diameter D4 is between D1 and D2. The second chamber 21b extends on another circumference C4' with a diameter D4', and the diameter D4' is between D1 and D2. The third chamber 23b extends substantially on another circumference C4" with a diameter D4", and the diameter D4" is between D1 and D2. D4" is less than D4', and D4' is less than D4. The circumferences C4, C4', and C4" are centered on the axis X.

[0093] As Figure 3 and Figure 5As shown, the chambers 20b, 21b, 23b extend in a plane P2 perpendicular to the axis X, which plane P2 passes between the cage 14 on the one hand and the ring 15b of the cage 15 on the other hand. It can also be seen that the diameter D4” is greater than the diameter D3’ of the section 3b to avoid any risk of contact during operation.

[0094] The inlets 20a, 21a and the outlet 23c can be oriented in the radial direction with respect to the axis X. Preferably, the outlet 23c is located at the 6 o'clock position of the dial analogous to a clock, such that the oil flows by gravity from the distributor 13 to the recirculation system.

[0095] Preferably, the plane P3 is located between the cage 14 and the ring 15b of the cage 15.

[0096] Advantageously, the distributor 13 is configured to be fluidly connected at the inlet and outlet of the distributor 13 by a male-female plug member (i.e., a connector that only requires axial translation of the male connector into the female connector). Even though the coupling member will be represented below as a male coupling member and is used to cooperate with a female coupling member, alternatively, the coupling member can be replaced by a female coupling member for cooperating with a male coupling member, and vice versa. The male-female connection can be sealed with an O-ring or the like.

[0097] The inlets 20a, 21a and the outlet 23c can each include a female connector to accommodate the male connector of a hose connected to a lubricating oil source.

[0098] For the outlet 20c, as shown in the example, the outlets 20c each include a female connector 20ca that is used to accommodate the male connector of one of the deflectors 18. These outlets 20c are all axially oriented forward in the same direction here.

[0099] Regarding the outlet 21c, in the example shown, the outlet 21c each includes a female connector that is used to accommodate the male connector from one of the lubricating and cooling cores 22.

[0100] The function of the core 22 is to lubricate and cool the axles 10b of the planetary gears 8, where the axles 10b are centered and guided by the bearings 11 of the rollers 11a here.

[0101] In the example of the illustrated embodiment, each axle 10b is guided by a double-roller bearing 11 (i.e., having two rows of rollers 11a). The two rows of rollers extend around the same axis: this axis is the same as the axis labeled Y of the axle 10b of the planetary gear 8.

[0102] The outlet 21c is all axially oriented forward in the same direction here. The connections of these outlets are connected to the chamber 21b by ducts 21d having an approximately L shape.

[0103] In the case of the inlets 23a, in the example shown, each of the inlets 23a includes a female connector for receiving a male connector from one of the deflectors 18. These inlets 23a are all axially oriented forward in the same direction here.

[0104] Finally, as Figure 5 shown, the passage 21d is connected to the ring by means of a thread located on the outer periphery of the ring forming the chamber 21b, while the inlets 23a and the outlet 20c are formed directly on the ring forming the chamber.

[0105] Figures 5 to 9 An embodiment of the deflector 18 is shown. As described above, the speed reducer 6 includes a plurality of deflectors 18 which are received in the cage 14 and are each arranged between two adjacent planetary gears 8. Therefore, the number of deflectors 18 in the speed reducer 6 is equal to the number of planetary gears 8 in the speed reducer.

[0106] The main function of the deflector 18 is to guide the lubricating oil to the teeth and prevent the recirculation of oil between the planetary gears. Therefore, it is called an "inter-planetary gear deflector". Thus, the deflector 18 is shaped to match the peripheral shape of the planetary gear 8.

[0107] As shown in the figure, in addition to extending between two adjacent planetary gears 8, each deflector 18 is located between the sun gear 7 positioned radially inwardly on the one hand and a pair of bridging members 14c, 14d positioned radially outwardly on the other hand.

[0108] Each deflector 18 includes a block which includes a first side surface 18a which is cylindrical and concave and has a radius of curvature R1 measured from an axis G1 which coincides with the axis of rotation Y of the planetary gear 8 ( Figure 8 ). The block includes a second side surface 18b opposite the first surface 18a which is cylindrical and concave and has a radius of curvature R1 measured from an axis G2 parallel to G1 which coincides with the axis of rotation Y of another planetary gear 8.

[0109] Each block of the deflector 18 further includes an upstream flat surface 18c and a downstream flat surface 18d. The upstream flat surface 18c is substantially radial when the deflector is mounted in the cage 14 of the speed reducer, and the downstream flat surface 18d is also substantially radial. The block further includes a radially outward flat surface 18e and a radially inward surface 18f. The radially outward flat surface 18e is intended to be oriented on one side of the pair of bridging members 14c, 14d, and the radially inward surface 18f is intended to be oriented on the side of the sun gear 7. The surface 18f is cylindrical and concave, and has a radius of curvature R3 measured from an axis that coincides with the axis X of the sun gear. Thus, the surface 18f has the function of guiding the lubricating oil of the teeth of the sun gear.

[0110] The deflector 18 extends between the radial walls 14a, 14b of the cage 14 and has surfaces 18c, 18d that are supported on the inner surfaces opposite to these walls 14a, 14b. The deflector 18 is fixed to the cage 14, for example, by screws.

[0111] Each deflector 18 has two independent integrated oil circuits 35, 36, which include:

[0112] - A first lubricating oil circuit 36, which includes at least one oil inlet port 36a and at least one oil outlet hole 36b or port for lubricating the speed reducer.

[0113] - A second oil recovery circuit 35, which is independent of the first circuit 36, and the second oil recovery circuit 35 includes at least one oil inlet hole 35a and at least one oil outlet port 35b for oil recirculation.

[0114] The first circuit 36 includes an oil inlet 36a connected to at least one oil outlet hole 36b by drilling. In the example shown, the oil inlet 36a is located on the downstream side 18d and includes a tube that is designed to form a convex connector and cooperate with the outlet 20c of the above distributor 13 through a male-female plug. Although the connector will be represented below as a convex connector and is used to cooperate with a concave connector, alternatively, the connector can be replaced by a concave connector for cooperating with a convex connector, and vice versa ( Figure 3 ). Here, the hole 36b is positioned near the surface 18f of the deflector and is oriented towards the teeth of at least the planetary gear 8 and the sun gear 7.

[0115] Each deflector 18 may include at least one oil outlet port 36c forming a concave connector for receiving a sealed fluid connection sleeve 37 ( Figure 3 and Figure 5)。Like the inlet 36a, the sleeve 37 can be removed and replaced with a male connector. Here, the port 36c is located on the radial outer face 18e of each deflector. Figure 3 It is shown that half of the sleeve 37 is engaged in the port 36c by a male-female plug and the other half is engaged in a female hole located on the radial inner end of the body 17a of the pin 17 carried by a pair of bridging members 14c, 14d by a male-female plug.

[0116] The second circuit 35 includes an oil inlet hole 35a which, in the example shown, is located on the faces 18a, 18b. Thus, during operation, the oil flowing on these faces 18a, 18b is recovered for recirculation, which avoids the oil being projected again onto the adjacent planetary gears 8.

[0117] The second circuit 35 also includes an oil outlet port 35b located on the downstream face 18d and a tube designed to form a male connector and to cooperate with the inlet 23a of the above-mentioned distributor 13 by a male-female plug. Even if the connector is represented below as a male connector and is intended to cooperate with a female connector, alternatively, the connector can be replaced with a female connector for cooperating with a male connector and vice versa.

[0118] As can be seen from the figure, the oil inlet port 36a of the first circuit 36 and the oil outlet port 35b of the second circuit 35 are positioned close to each other and are located on the same face 18d of the block of the deflector 18. Here, these ports 36a, 35b are positioned close to the side face 18f of the deflector and are oriented in a substantially parallel direction.

[0119] Figure 8 The rotational directions of the sun gear 7 (arrow F1) and the planetary gear 8 (arrow F2) are shown, the orientation of the oil projected from the hole 36b of the first circuit 36 of the deflector 18 (arrow F3), and the oil flow (arrow F4) after lubrication and after recovering the oil in the second circuit 35 of the deflector 18. Figure 8 and Figure 9 It is shown that the circuit 35 is preferably configured to utilize the direction of the centrifugal oil around the planetary gears to save the energy of the oil during oil recovery.

[0120] Thus, during operation, it is understood that the lubricating oil is first supplied by the distributor 13 to a part of the core 22 and the axle 10b of the planetary gear 8 for lubricating the bearing 11, and to the first circuit 36 of the deflector 18 for lubricating the teeth of the sun gear 7 and the planetary gear 8. The lubricating oil from the speed reducer 6 is projected onto the surfaces 18a, 18b of the deflector 18 and flows through the holes 35a into the second circuit 35 of the deflector. This oil is conveyed to the port 35b where it is discharged by the distributor 13 for recirculation.

[0121] The aim of the present text is to collect and discharge the oil as quickly as possible after its use in the gears.

[0122] For a planetary type speed reducer, the aim of the present invention is to provide an oil distributor which supplies oil to the teeth of the planetary gears and the bearings of the planetary gears and which also enables the recovery of the oil in order to effectively drain this oil.

[0123] To this end, the distributor includes an oil supply circuit independent of the oil discharge circuit.

[0124] It should be understood that this enables a more effective discharge of the oil compared to the architectures of the prior art, where the oil is recovered after flowing through the crankcase and transitioning to the low point (6 o'clock).

Claims

1. An oil distributor (13) for a lubricating oil of a mechanical speed reducer (6) of a turbine (1), the oil distributor having a body of generally annular shape about an axis X and comprising separate oil circuits formed in the body, characterized in that, The oil circuit includes: - an oil recovery circuit (23), which is configured and dedicated only to recovering oil, and includes a plurality of first oil inlets (23a) distributed around the axis X on the body and connected to at least one first oil outlet (23c) through a first annular chamber (23b), and - an oil supply circuit (20), which is configured and dedicated only to supplying oil to the teeth of the mechanical reducer, and includes a second oil inlet (20a) connected to a plurality of second oil outlets (20c) distributed around the axis X on the body through a second annular chamber (20b), and the first annular chamber and the second annular chamber extend circumferentially around the axis X with different diameters, wherein the oil recovery circuit and the oil supply circuit are independent so that oil recovery is not hindered by oil supply and vice versa.

2. The lubricating oil dispenser (13) according to claim 1, wherein, The oil circuit includes an additional oil supply circuit (21), which is independent and configured to supply oil to the bearings of the mechanical reducer, and the additional oil supply circuit (21) includes at least one third oil inlet (21a) connected to a plurality of third oil outlets (21c) distributed around the axis X on the body through a third annular chamber (21b).

3. The lubricant dispenser (13) according to claim 2, wherein, The first oil outlet (23c) of the oil recovery circuit (23), the second oil inlet (20a) of the oil supply circuit, and the third oil inlet (21a) of the additional oil supply circuit (21) are oriented in the radial direction with respect to the axis X.

4. The lubricant dispenser (13) according to claim 2 or 3, wherein, The first oil outlet (23c) of the oil recovery circuit (23), the second oil outlet (20c) of the oil supply circuit, and the third oil outlet (21c) of the additional oil supply circuit (21) are axially oriented in the same direction.

5. The lubricating oil dispenser (13) according to claim 2 or 3, wherein, The lubricating oil distributor includes bosses (25) distributed around the axis X on the body, and each of these bosses includes one of the first oil outlets (23c) of the oil recovery circuit (23) and one of the second oil outlets (20c) of the oil supply circuit (20).

6. The lubricant dispenser (13) according to claim 2 or 3, wherein, The diameter of the third annular chamber (21b) of the additional oil supply circuit (21) is larger than the diameter of the second annular chamber (20b) of the oil supply circuit (20), and the diameter of the second annular chamber of the oil supply circuit is itself larger than the diameter of the first annular chamber (23b) of the oil recovery circuit (23).

7. The lubricant dispenser (13) according to any one of claims 1 to 3, wherein, The body is made as an integral part.

8. The lubricant dispenser (13) according to claim 1, wherein, The turbine is a turbine of an aircraft.

9. A mechanical speed reducer (6) for an aircraft turbine, the mechanical speed reducer comprising: A cage (14) that defines a receiving portion for receiving a central sun gear (7) having a rotational axis X; planetary gears (8) arranged around the central sun gear; a deflector (18) fixed to the cage and arranged between the planetary gears; and a lubricant distributor (13) according to any one of claims 1 to 8, the lubricant distributor being attached and fixed to the cage and the lubricant distributor being connected to the deflector (18), the lubricant distributor being configured to supply lubricant to the teeth of the central sun gear and the planetary gears and to recover at least a portion of the lubricant through the deflector (18).

10. The mechanical speed reducer (6) according to claim 9, wherein, Each of the deflectors (18) includes a block having two opposite sides (18a, 18b) of generally curved shape that extend around the planetary gears, and oil inlet holes (35a) are positioned in the two opposite sides and are in fluid communication with the oil recovery circuit (23) for recovering oil from the teeth of the mechanical speed reducer.

11. The mechanical speed reducer according to claim 10, wherein, The oil inlet holes (35a) are connected through an internal passage of the block to an oil outlet port (35b) of the block of the deflector, the internal passage of the block being shaped to convey the recovered oil to the oil outlet port by means of the centrifugal force exerted on the projected oil by the planetary gears disposed on either side of the deflector.

12. An aircraft turbine including the mechanical speed reducer (6) according to claim 11, the mechanical speed reducer being equipped with a planet carrier (10).

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