Lubrication wheel for turbomachinery speed reducer

Abstract

This facilitates the manufacture of wheels and makes it easier to envision alternative manufacturing methods for wheels other than additive manufacturing. [Solution] A lubrication wheel (230) for a turbomachinery reduction gear (110), comprising: - an annular oil passage cavity (238) extending around an axis (A); - an annular slot (248) for supplying to the cavity (238); - tubes (143, 145) for passing oil from the cavity (238) into the tubes (143, 145) by centrifugal force; and - a frustoconical rim (300) for collecting oil at the level of the slot (248), wherein the wheel (230) is formed by an assembly of at least two parts.

Description

Technical Field

[0001] The present invention relates in particular to a lubricating wheel for a turbomachine, particularly for a reduction gear of an aircraft, as well as to a reduction gear and a turbomachine comprising such a wheel.

Background Art

[0002] The prior art in this field includes in particular the documents of French Patent Application Publication No. 3,036,763 A1, French Patent Application Publication No. 3,047,279 A1, French Patent Application Publication No. 3,041,054 A1, French Patent Application Publication No. 3,065,268 A1, French Patent Application Publication No. 3,065,270 A1, French Patent Application Publication No. 3,065,773 A1, International Publication No. 2015 / 008000 A1 and International Publication No. 2018 / 185186 A1.

[0003] The role of a mechanical reduction gear is to modify the speed and the torque ratio between the input shaft and the output shaft of a mechanical system.

[0004] A new generation of dual-flow turbomachines, particularly those having a very high bypass ratio, comprises a mechanical reduction gear for driving the fan shaft.

[0005] The usual purpose of a reduction gear is to convert the rotational speed, called the shaft of a high-speed power turbine, to a slower rotational speed for the shaft driving the fan.

[0006] Such a reduction gear comprises a central pinion called a sun gear, a ring gear, and pinions called planet gears engaged between the sun gear and the ring gear. The planet gears are held by a frame called a planet carrier. The sun gear, the ring gear, and the planet carrier are planetary because their axes of rotation coincide with the longitudinal axis of the turbomachine. Each of the planet gears has different axes of rotation equally spaced on the same operating diameter centered on the axis of the planet gear. These axes are parallel to the longitudinal axis.

[0007] There are several gearbox architectures. In the conventional technology for dual-flow turbomachines, the gearbox is either planetary or epicycle. In other similar applications, there are architectures called differential or "composite."

[0008] - In a planetary gearbox, the planetary carriers are stationary, and the ring gear is the output shaft of the device, rotating in the opposite direction to the sun gear.

[0009] - In an epicycle reducer, the ring gear is stationary, and the planetary carrier is the output shaft of the device, rotating in the same direction as the sun gear.

[0010] - In a compound gearbox, the elements are not mounted in rotation. The ring gear rotates in the opposite direction to the sun gear and planetary carriers.

[0011] A gearbox may consist of one or more transmission stages. This transmission is guaranteed by various means, such as contact, friction, or a magnetic field.

[0012] Contact transmissions come in several types, including straight, helical, or herringbone-shaped.

[0013] There are several solutions for lubricating such gearboxes.

[0014] Figure 1 shows a planetary carrier 10 as described in French Patent Application Publication No. 3 036 763A1. This planetary carrier 10 comprises a cylindrical body 12 with one longitudinal end connected to an annular wall 14 that supports parallel axles 16 for rotating a planetary gear 18. The axles 16 are distributed at equal intervals around the rotation axis A of the planetary carrier and are fixed to the aforementioned annular wall 14 at one of their longitudinal ends. Lubrication wheels 20 are attached to and fixed to the opposing longitudinal ends of the axles 16.

[0015] In the illustrated diagram, the lubrication wheel 20 is fixed to the planetary carrier 10 by connection to the axle 16 that supports the planetary gear 18. Thus, the lubrication wheel 20 is designed to rotate around axis A during operation by being fixed to the rotor of the reduction gear.

[0016] The lubrication wheel 20 is generally annular in shape with respect to axis A, and its outer circumference is equipped with a hydraulic connection of the planetary gear 18 to the axle 16. The wheel 20 is equipped with means for lubricating, on the one hand, a bearing mounted between the axle 16 and the planetary gear 18, and on the other hand, means for lubricating the gear teeth of the planetary gear 18 and the sun gear 22. These lubrication means are located on the inner circumference of the wheel 20 and are provided with an annular groove 24 that opens radially inward, i.e., toward axis A.

[0017] A lubricant nozzle, supported by the stator of a gearbox or turbomachinery, is positioned radially inward of the wheel (not shown in Figure 1) and sprays lubricant directly radially outward into the wheel groove 24 to supply the lubrication means.

[0018] The lubricant is supplied to the nozzle by a pump in the turbomachinery's lubrication unit, supplying a predetermined flow rate of lubricant to the nozzle. In the current technology described above, the lubricant sprayed into the groove is transported to the lubrication means solely by centrifugal force.

[0019] Therefore, the wheel uses the centrifugal force generated during operation to distribute oil under the pressure of the gearbox.

[0020] In the document of French Patent Application Publication No. 3 103 241, the wheel comprises an annular cavity on its inner circumference, which is supplied with oil by a nozzle that sprays oil axially into the cavity through an annular slot in the wheel. The cavity is in fluid communication with radial pipes for transporting the oil by centrifugal effect to the elements of a gearbox that require lubrication. [Prior art documents] [Patent Documents]

[0021] [Patent Document 1] French Patent Application Publication No. 3,036,763 [Patent Document 2] French Patent Application Publication No. 3,047,279 [Patent Document 3] French Patent Application Publication No. 3,041,054 [Patent Document 4] French Patent Application Publication No. 3,065,268 [Patent Document 5] French Patent Application Publication No. 3,065,270 [Patent Document 6] French Patent Application Publication No. 3,065,773 [Patent Document 7] International Publication No. 2015 / 008000 [Patent Document 8] International Publication No. 2018 / 185186 [Patent Document 9] French Patent Application Publication No. 3,103,241 [Summary of the Invention] [Problems to be Solved by the Invention]

[0022] This application focuses on the latter technology and particularly proposes improvements to facilitate manufacturing. The wheel actually has an inner circumference of a relatively complex shape that is difficult to obtain from a metal casting. One solution is to use additive manufacturing, but this is expensive and difficult to industrialize. <00,00097> Furthermore, when the rotational speed of the wheel is low, since the centrifugal force received by the oil during operation is low, the oil can flow slowly through the radial pipes of the wheel. If the flow of oil supplied by the nozzle exceeds the oil flow rate in the pipe due to the centrifugal effect, the oil is stored in the cavity, which can be processed to optimize lubrication.

[0024] The present invention provides solutions to at least some of the above-mentioned problems, and is simple, effective, and economical. [Means for solving the problem]

[0025] The present invention relates to a lubrication wheel for turbomachinery, particularly for aircraft reduction gears, configured to rotate about an axis, and having a substantially annular shape about the axis, -On its inner circumference, there is an annular oil passage cavity extending around the aforementioned axis, -On its inner circumference, there is an annular oil supply slot that extends around the axis and opens axially into the cavity for the purpose of supplying oil, - An oil passage pipe extending radially with respect to the axis, the radially inner end of which is connected to the cavity for oil to pass through due to centrifugal force from the cavity into the pipe, We propose a wheel characterized in that the inner circumference of the wheel has a frustoconical rim for collecting oil at the height of the slot, and this frustoconical rim is formed by a first annular portion that extends around the axis and is axially mounted and fixed in an annular body defining at least a portion of the cavity and tube.

[0026] A frustoconical rim is configured to guide and contain oil while allowing oil retention, particularly when the flow rate of oil supplied to the wheel is greater than the flow rate of oil circulating through its pipe. The rim can project axially upstream of the oil supply to the slot. It may also project radially toward the inner circumference of the slot and cavity. The rim design improves oil supply, but may require a unique wheel design, particularly to manage assembly and seals. Furthermore, the wheel is formed by assembling at least one annular section and an annular body, the section comprising a frustoconical rim. This facilitates the manufacture of the wheel and makes it easier to envision other manufacturing methods of the wheel other than additive manufacturing.

[0027] The spinning wheels according to the present invention may, either separately from each other or combined with each other, include one or more of the following characteristics.

[0028] - The frustum element is a surface or formed by a surface, - The frustum element is formed by the inclined edges of the fins, and these fins have the function of ensuring the entrainment of oil around the axis. - The cavity comprises a frustoconical element extending around the axis on its inner circumference, with one longitudinal end of its smaller diameter connected to the longitudinal end of the smaller diameter of the frustoconical rim. - The frustum element is formed by the body or the first part, - The cavity is defined axially by two annular side walls, the first of which has an inner circumference that defines the slot from the inside, and this first wall can be connected to the front closing wall of the cavity, insofar as it is located on the oil supply side. - The first wall is positioned axially between the frustoconical element and the frustoconical rim. - The first wall is formed by the main body, or by the first portion, or by a second annular portion that is axially attached to and fixed to the main body. - If the first wall is formed by the first portion, the first wall and the first portion are connected to each other by an annular row of connecting fingers that penetrate the cavity and / or slot radially. - The second side wall has its inner circumference connected to the larger diameter longitudinal end of the frustoconical element, and this second wall can be assimilated with the rear inner wall of the cavity, insofar as it is located on the opposite side of the oil supply. - The first portion comprises a cylindrical centering rim having an outer cylindrical surface that can cooperate with the inner cylindrical surface of the main body by centering, - The cylindrical surface is located on the inner circumference of the wheel. - At least one O-ring seal is fitted into one of the annular grooves on the cylindrical surface and cooperates with the other cylindrical surface to seal. -The first part is fixed to the main body by welding or screwing. - The slot has an inner diameter that is longer than the outer diameter of the frustoconical rim. - The inner diameter of the slot is shorter than the outer diameter of the frustoconical element. - At least some of the pipes communicate with axial oil passage channels and are plugged at their radially outer ends by the body or mounting plugs. - The rim widens axially on the opposite side of the cavity. - The rim has a free end with a longer diameter, which is axially positioned on the opposite side of the cavity.

[0029] The present invention also relates to a reduction gear for turbomachinery, the reduction gear comprising a sun gear rotatable about an axis, a ring gear extending about the axis and the sun gear, and a planetary gear located between the sun gear and the ring gear and meshing with the sun gear and the ring gear, the planetary gear being supported by a planetary carrier rotatable about an axis, and a previously described wheel being fixed coaxially with the planetary carrier for lubricating the planetary gear and / or the gear.

[0030] The present invention also relates to a turbomachinery, particularly for aircraft, comprising a reduction gear as described above and at least one oil nozzle configured to inject a jet of oil into the cavity, passing through the slot axially and through the radially outer side of the frustoconical rim.

[0031] Further features and advantages will become apparent from the following description of non-limiting embodiments of the invention with reference to the accompanying drawings. [Brief explanation of the drawing]

[0032] [Figure 1] This is a schematic perspective of a conventional planetary carrier. [Figure 2] This figure schematically shows an axial cross-section of a turbomachinery using the present invention. [Figure 3]This is a detailed cross-sectional view of a planetary gear reducer. [Figure 4] Figure 3 is an exploded perspective view of the gearbox. [Figure 5] Figure 3 is a schematic cross-sectional view of the gearbox wheel. [Figure 6] This is a schematic axial cross-sectional view of a lubricating wheel according to the first embodiment of the present invention. [Figure 7] This is a schematic axial cross-sectional view of a lubrication wheel according to a second embodiment of the present invention. [Figure 8] This is a schematic axial cross-sectional view of a lubricating wheel according to a third embodiment of the present invention. [Figure 9] This is a schematic axial cross-sectional view of a lubrication wheel according to a fourth embodiment of the present invention. [Modes for carrying out the invention]

[0033] Figure 1, described above, represents the prior art of the present invention.

[0034] Figures 2 to 5 show prior art as described in French Patent Application Publication No. 3 041 054A1.

[0035] Figure 1 shows a conventional turbomachinery 100 comprising a fan propeller S, a low-pressure compressor 101a, a high-pressure compressor 101b, a high-pressure turbine 101d, a low-pressure turbine 101e, and an exhaust nozzle 101h. The high-pressure compressor 101b and the high-pressure turbine 101d are connected by a high-pressure shaft 102 and together form the high-pressure (HP) body. The low-pressure compressor 101a and the low-pressure turbine 101e are connected by a low-pressure shaft 103 and together form the low-pressure (BP) body.

[0036] The fan propeller S is driven by a fan shaft 104 coupled to the BP shaft 103 by a planetary gear reducer 110, which is schematically shown here.

[0037] The reduction gear 110 is located in the upstream portion of the turbomachinery. In this application, the terms “upstream” and “downstream” refer to the gas flow through the turbomachinery.

[0038] Hereinafter, the fixed structure, including the upstream section 105a and the downstream section 105b, is arranged to form an enclosure E1 surrounding the reduction gear 110. This enclosure E1 is closed upstream by a level seal of bearing 106a that allows the passage of the fan shaft 104, and closed downstream by a level seal of passage 106b for the BP shaft 103.

[0039] Referring to Figures 2 and 3, the reduction gear is surrounded by a ring gear 114 fixed to the fixed structures 105a, 105b by a support casing 120, using flexible means configured to allow, for example, in certain degraded operating cases, to follow the possible movement of the fan shaft 104. These mounting means are known to those skilled in the art and will not be described in detail here. A brief description can be found, for example, in French Patent Application Publication No. 2 987 416A1.

[0040] In this example, the reducer 110 engages with the BP shaft 103 on one side via a spline 107 that drives a planetary gear pinion known as the sun gear 111, and on the other side with the fan shaft 104 fixed to the planetary carrier 113. Typically, the sun gear 111, whose axis of rotation A coincides with that of the turbomachine, drives a series of pinions of planetary gears 112 that are evenly distributed around the reducer 110. The number of planetary gears 112 is generally specified between three and six. The pinions of the planetary gears 112 also rotate about the axis A of the turbomachine and mesh with the internal teeth of a ring gear 114 that is stationary to the turbomachine by a support casing 120. Each of the planetary gears 112 rotates freely around a planetary gear shaft 116 connected to the planetary carrier 113, using plain bearings or rolling element bearings (ball or roller bearings) as shown in Figure 3.

[0041] The rotation of the planetary gear 112 around the planetary gear shaft 116, due to the cooperation of its pinion and the teeth of the ring gear 114, causes the rotation of the planetary carrier 113 around axis A, and consequently the rotation of the fan shaft 104 connected to it, at a rotational speed lower than the rotational speed of the BP shaft 103.

[0042] The fan shaft 104, passing through the planetary carrier 113, is driven by a series of centering fingers 117 that extend axially from the downstream end of the fan shaft 104 and into a bore provided in the planetary carrier 113, and are distributed at equal intervals around the reduction gear 110. The planetary carrier 113 extends symmetrically on both sides of the planetary gear shaft 116 and forms an enclosure that can implement the function of lubricating the gear. A closing socket 119 at the end of the planetary gear shaft 116 allows this enclosure to be closed at the level of the bearings of the planetary gear 112.

[0043] Figure 3, along with Figure 4, shows the transport of oil toward the reduction gear 110 and its internal path. The arrows in Figure 3 indicate the path of oil from the buffer reservoir 131 connected to the fixed structure, pinion, and bearings to be lubricated in this example of the turbomachinery. The lubrication system comprises three schematic parts, which will be described sequentially below: a first part connected to the fixed structure and delivering oil toward the rotating part of the reduction gear 110; a wheel that rotates with the planetary carrier 113 that receives this oil; and an oil distribution circuit that carries the oil supplied by the wheel toward the place to be lubricated.

[0044] The first part comprises at least one injector 132, whose calibrated end is constricted to form a nozzle 133. Oil is supplied from a reservoir of the engine (not shown) through a transport pipe 129 to the injector. A buffer reservoir 131 may be inserted next to the gearbox 110 on the pipe, preferably above, so that the oil can flow toward the center of the gearbox by gravity. The nozzle 133 discharges oil in the form of a jet 134, which is formed under pressure generated together by the weight of a supply pump (not shown) and an oil column located above it. The nozzle 133 is here positioned radially inward of the planetary carrier 113 with respect to axis A, and the jet 134 is oriented to have a radial component directed outward from the gearbox 110.

[0045] Referring to Figures 4 and 5, the oil receiving wheel 130 connected to the planetary carrier 113 essentially comprises a cylindrical cup 135 having a radially U-shaped cross-section, with the U-shaped opening oriented in the direction of the axis of rotation A. The wheel 130 is positioned on the planetary carrier 113 such that the bottom 136 of the U of the cup 135 collects the oil jet 134 ejected by the nozzle 133.

[0046] The cup 135 of the wheel 130 is divided into circumferentially continuous troughs 137a, 137b, separated by a radially oriented wall 138 that extends axially between the two side walls 139a, 139b of the U formed by the cup 135. In the illustrated example, the circumferential partition wall 138 defines two alternating sequences of four troughs 137a, 137b, where one sequence has the same circumferentially extending portion but is different from one sequence to the next.

[0047] Due to centrifugal force, as the wheel 130 rotates with the planetary carrier 113, the oil received in the bottom 136 of the cup 135 is rotationally driven and pressurized between the bottom 136 and the side walls 139a, 139b of the cup 135. Each cup 135a, 135b, passing continuously in front of the nozzle 133 during rotation, collects an amount of oil proportional to its circumferentially extended length. In practice, the radially inner edges of the walls 139a-139b-138 of the troughs 137a, 137b define the inlet surfaces to the troughs along the radial direction. This oil remains trapped between the walls 138, 139a, 139b of the troughs 137a, 137b as long as the oil level relative to the bottom 136 remains below the minimum height h of its wall 138 relative to the bottom 136.

[0048] The inner radial edges 140a, 140b of the side walls 139a, 139b are substantially circular. Their radius R1 defines the overall depth H of the cup 135 relative to the bottom 136. Preferably, the circumferential partition wall 138 has an inner radial edge 141 located at a distance R2 from axis A that is slightly larger than the radius R1 of the inner edges 140a, 140b of the side walls 139a, 139b. Thus, the height h of the circumferential partition wall 138 relative to the bottom 136 of the troughs 137a, 137b is slightly smaller than the height H of the side walls 139a, 139b relative to this same bottom 136.

[0049] Furthermore, the bottom 136 of each trough 137a, 137b is provided with openings 142a, 142b that communicate with the pipe lines 143, 145 of the oil distribution circuit installed on the planetary carrier 113.

[0050] Referring to Figures 4 and 5, there are two types of oil distribution circuits here. The first series of oil distribution circuits corresponds to the first tube 143, which distributes oil at equal intervals around the reduction gear 110 in a number equal to the number of planetary gears 112. These tubes 143 extend radially from the opening 142a at the bottom of the first series of troughs 137a and penetrate into the internal enclosure of each planetary gear shaft 116, which is closed by the planetary carrier 113. The oil flowing through the first tube 143 penetrates the internal cavity of each planetary gear shaft 116 and then, by centrifugal force, enters guide channels 144 that pass radially through these planetary gear shafts 116. These channels 144 open around the planetary gear shafts 116 at the level of the bearings supporting the pinions of the planetary gears 112, thus ensuring lubrication of these bearings (Figure 3).

[0051] The second series of oil distribution circuits comprises a second tube 145 that delivers oil between the planetary gears 112 from an opening 142b at the bottom of trough 137b of the second series of troughs and divides into several channels 145a, 145b. Channels 145a, 145b deliver oil to the gears formed on the one hand by the planetary gears 112 and the pinions of the sun gear 111, and on the other hand by the planetary gears 112 and the pinions of the outer ring gear 114. Each channel 145a extends axially along the planetary gear pinions between the planetary gears 112 and the sun gear 111, forming a lubrication ramp across the entire width of the pinions. Channel 145b, which supplies oil to the gears between the ring gear 114 and the pinions of the planetary gears 112, sprays its oil into the center of the cylinders formed by each planetary gear 112. As shown in the figure, each planetary gear 112 is made up of two parallel pinions. These teeth are oriented obliquely to the rotation axis of the planetary gear 112, thereby giving them the function of grooves that drive oil from the center of the cylinder outwards to lubricate the gear across its entire width.

[0052] The first oil distribution circuits 143 to 144, which lubricate the bearings supporting the planetary gears, need to carry a much larger flow rate of oil than the second circuits 145-145a-145b. Therefore, the circumferential extension of the first series of troughs 137a corresponding to these is longer than the circumferential extension of the second series of troughs 137b. Here, the nominal oil flow rate during operation requires a ratio of two-thirds to one-third. The circumferential extensions of the two series of troughs 137a and 137b effectively double this ratio.

[0053] The assembly is presented here with reference to a gearbox architecture 110 having four planetary gears 112, each having two sets of oil distribution circuits 143 to 144, 145-145a-145b of different types. For other gearbox architectures, the number of troughs per series may differ. Also, the number of similar circumferentially extending sets of troughs may differ depending on the type of oil distribution circuit. For example, the second oil distribution circuit can be subdivided into two: one dedicated to the pinion gear of the planetary gear 112 that meshes with the sun gear 111, and the other dedicated to the gear having the ring gear 114. In this case, variations of the oil recovery wheel can be realized by three sets of troughs extending in different circumferential directions.

[0054] Figures 6 to 9 show several embodiments of the wheel 230 according to the present invention.

[0055] Wheel 230 possesses the characteristics described above, which are indicated by the same reference numerals in Figures 3 to 5. It comprises, in particular, tubes 143 and 145.

[0056] Wheel 230 has a roughly annular shape centered on the aforementioned axis A, which is not visible in Figures 6 to 9.

[0057] The wheel 230 includes means for supporting the rotating shafts 116 of the planetary gears of the reduction gear, and these support means are formed by cylindrical end caps 260 that engage with the internal cavities of these axles 116. The wheel 230 also includes means for lubricating the teeth of the planetary gears, particularly those comprising the aforementioned tubes 143, 145, and the bearings of the axles 116.

[0058] The lubrication means also comprises an annular cavity 238 located on the inner circumference of the wheel 230 and connected to tubes 143, 145. Tube 143 extends substantially radially between the cavity 238 and the axle 116 for their oil supply. Tube 145 may extend substantially radially between the cavity 238 and nozzle mounting holes or channels 145a, 145b, as described above in relation to Figures 3 to 5.

[0059] The annular cavity 238 is axially separated by two annular side walls 240 and 242, which are respectively called the first wall 240 and the second wall 242.

[0060] The annular cavity 238 is also radially defined by the internal circumferential wall 246 and the external circumferential wall 244.

[0061] Wall 240 extends radially between walls 244 and 246. The radially inner ends of pipes 143 and 145 open onto wall 244.

[0062] Unlike conventional techniques where the supply to the wheel 130 is radial for centrifugal force accumulation, the cavity 238 of the wheel 230 is closed radially inward by a wall 246. Wall 246 is connected to wall 240 and extends radially inward from wall 242, and radially away from there. Thus, the inner circumference of wall 242 and wall 246 define the annular lubricant supply slot 248 of the cavity 238 between them.

[0063] Wall 240 can be considered a front wall insofar as it is located on the oil supply side of the cavity 238. Wall 242 can be considered a rear wall insofar as it is located on the opposite side from the oil supply to the cavity 238.

[0064] The cavity 238 may include an internal frustoconical element 254 facing the slot 248.

[0065] The frustum element 254 may be a surface or may be formed by a surface. In this case, the frustum element 254 is a frustum surface.

[0066] Alternatively, the frustoconical element 254 may be formed by the inclined edge of the fin 254a.

[0067] Each of the fins 254a has a substantially triangular shape and comprises a first side connected to wall 242, a second side connected to wall 246, and a free, inclined third side extending from wall 242 to wall 246.

[0068] If the cavity 238 does not contain the frustoconical element 254, it is understood that the inner circumference of wall 242 is directly connected to wall 246.

[0069] Element 254 may have an axial dimension L1 that represents at least 25%, and even 50%, of the axial dimension of wall 246, and may even represent more than 100% of the axial dimension of wall 246, insofar as element 254 can extend through slot 248 to the outside of cavity 238.

[0070] The double lines in Figures 6 to 9 indicate the jets of oil 258 emitted by nozzles fixed to the stator of the turbomachine.

[0071] The nozzle is slightly inclined with respect to axis A and can emit a jet of oil 258 into the cavity 238, passing through the slot 248 and around the frustoconical rim 300 on the inner circumference of the wheel 230. This oil jet 258 collides with element 254 and / or wall 246. When element 254 is formed by fin 254a, the oil jet 258 collides with wall 246, and the oil is then driven to rotate by the fin 254a for centrifugal separation.

[0072] The rim 300 collects oil at the level of the slot 248 and forms an annular trough 302 having a U-shaped or V-shaped cross-section.

[0073] The rim 300 may be formed by a first annular portion 304 that extends around axis A and is fitted into and fixed axially to an annular body 306 that defines at least a portion of the cavity 238 and the tubes 143, 145.

[0074] In the drawing, it can be seen that the frustoconical element 254 has a small-diameter longitudinal end connected to the small-diameter longitudinal end of the frustoconical rim 300. The large-diameter longitudinal end of the rim 300 is free and located on the opposite side of the cavity 238.

[0075] The wall 242 is preferably positioned axially between the frustoconical element 254 and the frustoconical rim 300. Thus, the connection between the aforementioned end of the frustoconical element 254 and the rim 300 is preferably enclosed by the wall 242, and the inner circumference of this wall 242 defines the aforementioned slot 248.

[0076] The slot 248 preferably has an inner diameter D1 that is longer than the outer diameter D2 of the frustoconical rim 300.

[0077] The frustoconical rim 300 may have an axial dimension L2 that represents 10 to 50%, for example 20 to 30%, of the axial dimension L1 of element 254.

[0078] The inner diameter D1 of slot 248 is preferably shorter than the outer diameter D3 of the frustoconical element 254, as shown in Figures 7 and 8. Alternatively, the inner diameter D1 of slot 248 may be greater than or equal to the outer diameter D3 of the frustoconical element 254, as shown in Figure 6.

[0079] In the embodiments shown in Figures 6 and 7, the frustoconical element 254 is formed by the first part 304. In the embodiment shown in Figure 8, the frustoconical element 254 is formed by the body 306.

[0080] The wall 242 may be formed by the main body 306 as in Figure 6, or by the first part 304 as in Figure 9, or by a second annular part 308 that is axially attached and fixed to the main body 306 as in Figures 6 and 8. In the latter case, the wheel 230 is formed by an assembly of three annular elements: the main body 306 and the two parts 304 and 308.

[0081] Part 304 or parts 304, 308 may be fixed to the body 306 by welding or screwing.

[0082] In the figure, it can be seen that pipe 143 is in communication with the axial oil channel 314. In Figures 6, 7, and 9, pipe 143 is plugged at its radially outer end by the body 306 itself. In Figure 8, pipe 143 is blocked at its radially outer end by a plug 316 inserted radially. This last variation allows pipe 143 to be fabricated by drilling radially through the body 306 from the outside.

[0083] In Figure 9, where the first wall 242 is formed by the main body 304, the first wall 242 is also axially covered by a seal shell 318 associated with the main body 304. A connecting finger 309 connects this shell 318 to the frustoconical element 254, in particular to the free edge of the fin 254a described above.

[0084] The number of fingers 309 is equal to the number of fins 254a, and each finger 309 is connected to a fin 254a. The fins 254a and fingers 309 may extend in a radial plane passing through axis X.

[0085] The fingers 309 form an annular array around axis X and pass radially through the cavity 238 and / or slot 248.

[0086] To facilitate assembly, the first portion 304 advantageously includes a cylindrical centering rim 310 having an outer cylindrical surface 310a that can cooperate with the inner cylindrical surface 306a of the main body by centering.

[0087] The cylindrical surfaces 310a and 306a are located on the inner circumference of the wheel 230 in the illustrated example.

[0088] At least one O-ring seal 312 is fitted into an annular groove in one of the cylindrical surfaces, such as surface 310a, so that it can cooperate in sealing with the other cylindrical surface, such as surface 306a.

[0089] As shown in Figure 9, at least one O-ring seal 314 may be installed between the shell 318 and the wall 242.

[0090] The advantages of the lubricating wheel according to the present invention include the following:

[0091] - Reduction of the overall radial dimensions of this technology, - Increase in wheel hydraulic pressure, - More efficient oil collection, -Simplified manufacturing while maintaining the same performance and overall dimensions. [Explanation of symbols]

[0092] 10 Planetary Carriers 12 Cylindrical body 14 Ring Wall 16 axles 18 Planetary Gear 20 Lubrication Wheels 22 Sun Gear 24 groove 100 Turbo Machinery 101a Low-pressure compressor 101b High-pressure compressor 101d High-pressure turbine 101e Low-Pressure Turbine 101h Exhaust Nozzle 102 High-pressure shaft 103 Low-pressure shaft, BP shaft 104 Fan Shaft 105a Upstream part of the solid structure 105b Downstream part of a solid structure 106a Bearing 106b aisle 107 Splines 110 Gearbox Architecture, Gearbox 111 Sangear 112 Planetary Gear 113 Planetary Carrier 114 Ring Gear 116 Planetary gear shaft, axle, planetary gear shaft, rotating shaft 117 Centering Finger 119 Closed Socket 120 Support casing 129 Conveyor pipe 130 wheels 131 Buffer Reservoir 132 Injectors 133 Nozzles 134 Jet 135 cups 135a cup 135b cup 136 Bottom 137a Trough 137b trough 138 Wall 139a Wall 139b Wall 140a Inner edge, inner radial edge 140b Inner edge, inner radial edge 141 Inner radial edge 142a aperture 142b aperture 143 Pipes, pipe oil distribution circuits, oil passage pipes 144 channels 145 Tubes, circuits 145a channel 145b channel 230 wheels 238 Annular oil passage cavity 240 Side wall 242 Wall 244 External peripheral wall 246 Internal peripheral wall 248 annular oil supply slot, annular lubricating oil supply slot, annular slot 254 elements, frustum of a cone element 258 Jet, Oil Jet 260 Cylindrical End Caps 300 frustum cone rim, rim 302 Annular Trough 304 Ring section 306 Ring-shaped body 306a Cylindrical surface 308 Ring section 309 Connecting Finger 310 Cylindrical Centering Rim 310a Cylindrical surface 312 O-ring seal 314 Axial oil channel 316 Plug 318 Seal Shell 318 shells

Claims

1. A lubrication wheel (230) for turbomachinery, particularly for an aircraft reduction gear (110), wherein the wheel (230) is configured to rotate about an axis (A), and has a substantially annular shape about the axis (A), and the wheel is On its inner circumference is an annular oil passage cavity (238) extending around the axis (A), On its inner circumference is an annular oil supply slot (248) that extends around the axis (A) and opens axially into the cavity (238) for the purpose of supplying oil, The system includes oil passage pipes (143, 145) that extend radially with respect to the axis (A), and whose radially inner ends are connected to the cavity (238) so that oil can pass through the cavity (238) due to centrifugal force from the cavity (238) into the pipes (143, 145), The wheel (230) is characterized in that the inner circumference of the wheel (230) comprises a frustoconical rim (300) for collecting oil at the height of the slot (248), wherein the frustoconical rim (300) is formed by a first annular portion (304) that extends around the axis (A) and is axially mounted and fixed in an annular body (306) defining at least a portion of the cavity (242) and the tubes (143, 145).

2. The wheel (230) according to claim 1, wherein the cavity (238) comprises a frustoconical element (254) on its inner circumference, extending around the axis (A), with one longitudinal end of its small diameter connected to the longitudinal end of the small diameter of the frustoconical rim (300).

3. The wheel (230) according to claim 2, wherein the frustoconical element (254) is formed by the body (306) or the first portion (304).

4. The wheel (230) according to any one of claims 1 to 3, wherein the cavity (238) is defined axially by two annular side walls (240, 242), the first of these walls having an inner circumference that defines the slot (248) from the inside.

5. The wheel (230) according to claim 4, dependent on claim 2 or claim 3, wherein the first wall (242) is axially positioned between the frustoconical element (254) and the frustoconical rim (300).

6. The wheel (230) according to claim 4 or 5, wherein the first wall (242) is formed by the body (306), or by the first portion (304), or by a second annular portion (308) that is axially attached and fixed to the body (306).

7. The wheel (230) according to claim 6, wherein when the first wall (242) is formed by the first portion (304), the first wall (242) and the first portion (304) are connected to each other by an annular row of connecting fingers (309) that penetrate radially through the cavity (238) and / or slot (248).

8. A wheel (230) according to any one of claims 4 to 7, dependent on claim 2 or 3, wherein the second side wall (240) has an inner circumference connected to the larger diameter longitudinal end of the frustoconical element (254).

9. The wheel (230) according to any one of claims 1 to 8, wherein the first portion (304) comprises a cylindrical centering rim (310) having an outer cylindrical surface (310a) that can cooperate with the inner cylindrical surface (306a) of the main body by centering.

10. The wheel (230) according to claim 9, wherein the cylindrical surfaces (310a, 306a) are located on the inner circumference of the wheel (230).

11. The wheel (230) according to claim 9, wherein at least one O-ring seal (312) is attached to one of the annular grooves of the cylindrical surface (310a) and cooperates with the other of the cylindrical surface (306a) to seal.

12. The wheel (230) according to any one of claims 1 to 11, wherein the first portion (304) is fixed to the main body (306) by welding or screw fastening.

13. The wheel (230) according to any one of claims 1 to 12, wherein the slot (248) has an inner diameter (D1) that is larger than the outer diameter (D2) of the frustoconical rim (300).

14. A wheel (230) according to claim 13, dependent on claim 2 or claim 3, wherein the inner diameter (D1) of the slot (248) is shorter than the outer diameter (D3) of the frustoconical element (254).

15. A reduction gear (110) for a turbomachinery (100), comprising a sun gear (111) rotatable about an axis (A), a ring gear (114) extending about the axis (A) and the sun gear (111), and a planetary gear (112) located between the sun gear (111) and the ring gear (114) and meshing with the sun gear (111) and the ring gear (114), wherein the planetary gear (112) is supported by a planetary carrier (113) rotatable about the axis (A), and the wheel (230) according to any one of claims 1 to 14 is fixed coaxially with the planetary carrier (113) for lubricating the planetary gear (112) and / or the gear.

16. A turbomachinery (100) particularly for aircraft, comprising a reduction gear (110) as described in claim 15, and at least one oil nozzle configured to inject an oil jet (258) into the cavity (238), passing through the slot (248) in the axial direction and passing radially outside the frustoconical rim (300).

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