Gearbox assembly for lubricating gears

Abstract

A gearbox assembly includes a planetary gear including an outer surface and an inner surface opposite the outer surface. A pair of circumferential oil conduits is formed in the inner surfaces near opposite ends of the planetary gears. A distributor duct is formed to extend in a longitudinal direction from each of the circumferential oil ducts toward a center of the planetary gear. One or more tooth ducts are formed to extend from each distributor duct to an outer surface of the planetary gear. A journal pin is received within the planetary gear, the journal pin extending along an axis about which the planetary gear rotates. A gap defining a journal bearing is formed between an inner surface of the planetary gear and the journal pin. An oil passage that supplies oil to the gap is provided.

Description

Technical Field

[0001] This specification relates generally to gearbox assemblies for turbine engines, and more specifically to systems and methods for lubricating the gears of gearbox assemblies. Background Technology

[0002] Gearbox assemblies are widely used in various turbine engine applications due to their torque transmission capabilities. The efficient operation of these gearbox assemblies largely depends on effective lubrication to reduce friction, wear, and overheating. Conventional lubrication systems in gearbox assemblies, particularly those used in turbine engines, often face challenges in terms of accessibility, efficiency, and adaptability. For example, conventional lubrication systems are often located in inaccessible locations, making maintenance and installation challenging. Furthermore, these conventional lubrication systems are sensitive to engine deflection and prone to leakage, which can lead to low operating efficiency and increased maintenance requirements. Therefore, systems and methods for lubricating gears in gearbox assemblies are needed to provide enhanced efficiency while ensuring consistent and reliable lubrication. Attached Figure Description

[0003] The embodiments illustrated in the accompanying drawings are illustrative and exemplary in nature and are not intended to limit the subject matter defined by the claims. The following detailed description of the illustrative embodiments will be understood when read in conjunction with the following drawings, wherein the same structures are indicated by the same reference numerals, and wherein:

[0004] Figure 1 A cross-sectional view of a turbine engine taken along the centerline axis of the turbine engine according to one or more embodiments shown and described herein is schematically illustrated.

[0005] Figure 2 The illustration schematically depicts one or more embodiments of a device shown and described herein. Figure 1 A partial cross-sectional side view of the gearbox assembly of a turbine engine;

[0006] Figure 3 A partially enlarged cross-sectional side view of a gearbox assembly according to one or more embodiments shown and described herein is schematically illustrated;

[0007] Figure 4 A side view of a planetary gear of a gearbox assembly according to one or more embodiments shown and described herein is schematically illustrated. The planetary gear includes teeth that mesh with the teeth of an adjacent gear.

[0008] Figure 5 A partially enlarged side view of the teeth of a planetary gear according to one or more embodiments shown and described herein is schematically illustrated.

[0009] Figure 6 A schematic cross-sectional side view of a planetary gear including multiple valves according to one or more embodiments shown and described herein is illustrated; and

[0010] Figure 7 A cross-sectional side view of a valve in each of a first open position, a closed position, and a second open position, according to one or more embodiments shown and described herein, is schematically illustrated. Detailed Implementation

[0011] The embodiments described herein relate to a turbine engine, a gearbox assembly, and a method of providing lubrication to the gears of the gearbox assembly of the turbine engine. The gears of the gearbox assembly to which lubricant is supplied may be planetary gears. Specifically, lubricant is supplied from the gearbox to the teeth of the planetary gears via a lubricant supply line that delivers lubricant to a journal pin about which the planetary gears rotate. The lubricant is guided through the journal pin and into the gap defined between the inner surface of the planetary gear and the journal pin. The centrifugal force generated by the rotation of the planetary gear relative to the journal pin draws the lubricant into channels formed in the planetary gear and into the teeth formed on the outer surface of the planetary gear, thereby increasing lubrication between the teeth of the planetary gear and the teeth of an adjacent gear (e.g., the sun gear) of the gearbox assembly.

[0012] This document describes in more detail various embodiments of a turbine engine, gear assembly, and methods for supplying lubricant to the gears of a gearbox assembly. Wherever possible, the same reference numerals will be used in all the accompanying drawings to denote the same or similar parts.

[0013] This document may express a range as from “about” a particular value, and / or to “about” another particular value. When expressing such a range, another embodiment includes from one particular value and / or to another particular value. Similarly, when a value is expressed as an approximation using the antecedent “about,” it will be understood that the particular value forms another embodiment. It will be further understood that each endpoint of a range is significant relative to the other endpoint and independent of the other endpoint.

[0014] The directional terms used here—such as up, down, right, left, front, back, top, bottom—are for reference only with reference to the accompanying drawings and do not imply absolute orientation.

[0015] Unless otherwise expressly stated, none of the methods described herein should be construed as requiring that the steps be performed in a particular order, nor requiring any particular device orientation. Therefore, in the absence of a method claim actually recounting the order of its steps, or any device claim actually recounting the order or orientation of the various components, or unless the claims or description specifically specify that the steps will be limited to a particular order, or recounts a particular order or orientation of the device components, no inference shall be made in any respect of the order or orientation. This applies to any possible non-explicit basis for interpretation, including: logical questions concerning the arrangement of steps, the flow of operations, the order of components, or the orientation of components; trivial meanings derived from grammatical organization or punctuation; and the number or type of embodiments described in the description.

[0016] As used herein, the singular forms “a,” “an,” and “the” include plural references unless the context clearly indicates otherwise. Thus, for example, unless the context clearly indicates otherwise, reference to “a” component includes aspects having two or more such components.

[0017] A turbine engine can be configured as a geared engine. A geared engine includes a gearbox assembly for transmitting power from the turbine shaft to the main fan. This gearbox assembly may include a sun gear, multiple planetary gears, and a ring gear. The sun gear meshes with multiple planetary gears, which in turn mesh with the ring gear. In operation, the gearbox assembly transmits torque from the turbine shaft, which operates at a first speed, to the fan shaft, which rotates at a second, lower speed. In a planetary configuration of the gearbox assembly, the sun gear may be coupled to the central shaft of the low-pressure turbine, which rotates at the first speed. The planetary gears meshing with the sun gear then transmit this torque to the fan shaft via a planet carrier. In a star configuration, the ring gear is coupled to the fan shaft. In either configuration, the planetary gears rotate about journal pins, in which journal bearings are formed between the journal pins and the planetary gears. The journal pins are inserted through the planet carrier and are typically fixed to the planet carrier by an interference fit.

[0018] Lubricant is supplied directly to the journal pins of the gearbox assembly. The lubricant is then delivered to other components, such as journal bearings and planetary gears. For example, lubricant can be delivered to the journal bearings and planetary gears via conduits that pass axially through the pins and radially to the journal bearings and planetary gears.

[0019] Now refer to the attached diagram, Figure 1A cross-sectional view of a turbine engine 10 according to an embodiment of the present disclosure, taken along the centerline axis of the turbine engine 10, is shown. The turbine engine 10 defines an axial direction A (extending parallel to a longitudinal centerline 12 for reference) and a radial direction R perpendicular to the axial direction A. Typically, the turbine engine 10 includes a fan section 14 and a core turbine engine 16 disposed downstream of the fan section 14.

[0020] The core turbine engine 16 shown typically includes a casing 18, which is substantially tubular and defines an annular inlet 20. Figure 1 As schematically shown, housing 18 surrounds compressor section 21, combustion section 26, turbine section 27, and injection exhaust nozzle section 32 in a series flow relationship. Compressor section 21 includes a turbocharger or low-pressure (LP) compressor 22, followed by a high-pressure (HP) compressor 24. Turbine section 27 includes a high-pressure (HP) turbine 28, followed by a low-pressure (LP) turbine 30. A high-pressure (HP) shaft 34 or spool drives the HP turbine 28 to the HP compressor 24 to rotate the HP turbine 28 and the HP compressor in unison. A low-pressure (LP) shaft 36 drives the LP turbine 30 to the LP compressor 22 to rotate the LP turbine 30 and the LP compressor 22 in unison. Compressor section 21, combustion section 26, turbine section 27, and injection exhaust nozzle section 32 together define the core airflow path.

[0021] for Figure 1 In the illustrated embodiment, fan section 14 includes a fan 38 (e.g., a variable pitch fan) having a plurality of fan blades 40 spaced apart and coupled to disk 42. Figure 1 As shown, fan blades 40 generally extend outward from disk 42 in a radial direction R. Each fan blade 40 is operatively coupled to an actuation member 44, which is configured to collectively and uniformly change the pitch of the fan blades 40, and each fan blade 40 is rotatable relative to disk 42 about a pitch axis P. The fan blades 40, disk 42, and actuation member 44 are rotatable together about a longitudinal centerline 12 via a fan shaft 45, which is powered by an LP shaft 36 across a gearbox assembly 46. The gearbox assembly 46 includes multiple gears for adjusting the rotational speed of the fan shaft 45 and the rotational speed of the fan 38 relative to the LP shaft 36 to a more efficient fan speed.

[0022] Still referencing Figure 1In an exemplary embodiment, disk 42 is covered by a rotatable fan hub 48, which is aerodynamically shaped to facilitate airflow through a plurality of fan blades 40. Furthermore, fan section 14 includes an annular fan housing or nacelle 50 circumferentially surrounding at least a portion of fan 38 and / or core turbine engine 16. Nacelle 50 is supported relative to the central turbine engine 16 by a plurality of circumferentially spaced outlet guide vanes 52. Additionally, a downstream section 54 of nacelle 50 extends externally over the core turbine engine 16 to define a bypass airflow passage 56 therebetween.

[0023] During the operation of the turbine engine 10, a volume of air 58 enters the turbine engine 10 through the inlet 60 of the nacelle 50 and / or fan section 14. As the volume of air 58 passes through the fan blades 40, a first portion of the air 62 is directed or directed into the bypass airflow passage 56, and a second portion of the air 64 is directed or directed into the upstream section of the core airflow path, or more specifically, into the annular inlet 20 of the LP compressor 22. The ratio between the first portion of air 62 and the second portion of air 64 is commonly referred to as the bypass ratio. Then, as the second portion of air 64 enters the combustion section 26 through the HP compressor 24, the pressure of the second portion of air 64 increases, where the high-pressure air mixes with fuel and burns to provide combustion gases 66.

[0024] Combustion gas 66 is guided into and expanded by the HP turbine 28, where a portion of the thermal and / or kinetic energy from the combustion gas 66 is extracted via a successive stage of HP turbine stator blades 68 connected to housing 18 and HP turbine rotor blades 70 connected to HP shaft 34, causing HP shaft 34 to rotate and thus supporting the operation of HP compressor 24. Combustion gas 66 is then guided into and expanded by the LP turbine 30. Here, a second portion of the thermal and kinetic energy is extracted from the combustion gas 66 via a successive stage of LP turbine stator blades 72 connected to housing 18 and LP turbine rotor blades 74 connected to LP shaft 36, causing LP shaft 36 to rotate. This, in turn, supports the operation of LP compressor 22 and the rotation of fan 38 via gearbox assembly 46.

[0025] Combustion gas 66 is then directed through the injection exhaust nozzle section 32 of the core turbine engine 16 to provide propulsive thrust. Simultaneously, the pressure of the first portion of air 62 increases significantly as it passes through the bypass airflow passage 56 before exiting the fan nozzle exhaust section 76 of the turbine engine 10, also providing propulsive thrust. The HP turbine 28, LP turbine 30, and injection exhaust nozzle section 32 at least partially define the hot gas path 78 for directing combustion gas 66 through the core turbine engine 16.

[0026] Figure 1 The turbine engine 10 shown is merely an example. In other exemplary embodiments, the turbine engine 10 may have any other suitable configuration. For example, in other exemplary embodiments, the fan 38 may be configured in any other suitable manner (e.g., as a fixed-pitch fan) and may also be supported using any other suitable fan frame configuration. Furthermore, it should be understood that in other exemplary embodiments, any other suitable number or configuration of compressors, turbines, shafts, or combinations thereof may be provided. In other exemplary embodiments, aspects of this disclosure may be incorporated into any other suitable gas turbine engine, such as a turbofan engine, a propeller engine, a turbojet engine, and / or a turboshaft engine.

[0027] Now for reference Figure 2 This shows the connection of the LP shaft 36 to the fan 38 ( Figure 1 ) turbo engine 10 ( Figure 1 A cross-sectional side view of gearbox assembly 46. Gearbox assembly 46 includes planetary gearbox assembly 102, which includes a sun gear 104 and a plurality of planet gears 106 (in...). Figure 2 Only one of them is visible in the image (and gear ring 108). For clarity, only a portion of the gear is shown. Although in Figure 2 Not shown, each of the sun gear 104, the plurality of planetary gears 106, and the ring gear 108 includes teeth around its periphery for meshing with other gears. The gearbox assembly 46 is a star-shaped or rotating ring gear gearbox assembly (e.g., the ring gear 108 is rotating, and the planet carrier 110 is stationary). In this arrangement, the fan 38 ( Figure 1 The fan 38 is driven by the ring gear 108. Thus, the ring gear 108 is the output of the gearbox assembly 46. However, other suitable types of gearbox assemblies 46 may also be used. In a non-limiting example, the gearbox assembly 46 may be a planetary arrangement, where the ring gear 108 remains stationary and the planet carrier 110 allows rotation. In this arrangement, the fan 38 ( Figure 1 The planet carrier 110 drives the gearbox assembly 46. Thus, the planet carrier 110 is the output of the gearbox assembly 46. In another non-limiting example, the gearbox assembly 46 may be a differential gearbox, in which both the ring gear 108 and the planet carrier 110 are allowed to rotate.

[0028] A drive shaft (e.g., LP shaft 36) is coupled to the sun gear 104. Thus, the sun gear 104 is the input to the gearbox assembly 46. In some instances, the drive shaft is the HP shaft 34 (…). Figure 1Multiple planetary gears 106 are radially outside and mesh with the sun gear 104. These planetary gears 106 are connected together and supported by a planet carrier 110. The planet carrier 110 supports and constrains the multiple planetary gears 106 so that the multiple planetary gears 106 do not rotate together around the sun gear 104, while allowing each of the multiple planetary gears 106 to rotate about its own axis 13. A ring gear 108 is radially outside and meshes with the multiple planetary gears 106. The ring gear 108 is a ring gear. The ring gear 108 is connected to the fan 38 via a fan shaft 45. Figure 1 ) and rotate to drive fan 38 ( Figure 1 It rotates around the longitudinal centerline 12. Thus, the gear ring 108 is the output of the gearbox assembly 46. In the planetary configuration, the planet carrier 110 is the output of the gearbox assembly 46.

[0029] Each of the plurality of planetary gears 106 includes a journal pin 112 about which the respective planetary gear 106 rotates. For example, a lubricant (e.g., oil) is disposed between the journal pin 112 and the respective planetary gear 106, causing the planetary gear 106 to rotate relative to the journal pin 112. The gearbox assembly 46 includes a gear ratio that defines the ratio of the speed of the input gear (e.g., the sun gear 104) to the speed of the output gear (e.g., the ring gear 108) passing through the gearbox assembly 46. In the planetary configuration, the output is the planet carrier 110.

[0030] Journal pin 112 includes an oil passage 114 extending along axis 13. The oil passage 114 extends from the end of journal pin 112 to the outer surface of journal pin and defines a clearance 132 between journal pin 112 and the associated planetary gear 106. As described in more detail herein, lubrication is supplied to the oil passage 114, such that lubricant is delivered between journal pin 112 and the corresponding planetary gear 106. Journal pin 112 is inserted through a first hole 116 and a second hole 118 of planet carrier 110. Thus, journal pin 112 is secured to planet carrier 110 by an interference fit at the first hole 116 and the second hole 118.

[0031] Still referencing Figure 2Lubricant 119 is stored within a housing 120 and delivered to the journal pin 112 via a lubricant supply line 122 extending from the housing 120 to the journal pin 112. The lubricant supply line 122 is secured to the end of an oil passage 114 in any suitable manner to define a seal between them. The housing 120 may include a pump 124 for directing lubricant 119 from the housing 120 into the oil passage 114 of the journal pin 112. In an embodiment, the lubricant supply line 122 includes a valve 126. The valve 126 may be a one-way check valve, for example, which allows lubricant to flow through the valve 126 in only one direction, such as from the housing 120 into the journal pin 112, rather than from the journal pin 112 into the housing 120.

[0032] Now for reference Figure 3 A more detailed enlarged view of one of the journal pin 112 and the planetary gear 106 is shown. In an embodiment, as shown, the oil passage 114 of the journal pin 112 includes a longitudinal member 128 and a radial member 130 extending from the end of the longitudinal member 128. In an embodiment, the radial member 130 extends perpendicular to the longitudinal member 128. In an embodiment, the oil passage 114 may include a plurality of radial members 130 extending from the longitudinal member 128, one of which is centrally positioned along the + / -X axis of the coordinate axes shown in the figure. In an embodiment, the longitudinal member 128 extends parallel to the axis 13. However, in an embodiment, the oil passage 114 may include a single linear member extending at a constant angle from the end of the journal pin 112, at which the journal pin 112 is sealed to the lubricant supply line 122. Figure 2 When lubricant 119 ( Figure 2 From box 120 ( Figure 2 When the lubricant is pumped to the journal pin 112, the centrifugal force caused by the rotation of the planetary gear 106 creates a pressure difference between the planetary gear 106 and the associated journal pin 112. Therefore, the centrifugal force causes lubricant 119 to flow into the gap 132 defined between the journal pin 112 and the associated planetary gear 106. Thereafter, the lubricant 119 flows outward in the longitudinal direction along the journal pin 112 towards the opposite end of the planetary gear 106 within the gap 132. As used herein, the combination of lubricant 119 within the gap 132 may be referred to as journal bearing 133.

[0033] like Figure 3 As shown, the planetary gear 106 includes one or more channels for receiving lubricant 119 from the oil passage 114 of the journal pin 112 and delivering the lubricant 119 to a plurality of teeth 134 of the planetary gear 106, the plurality of teeth 134 being formed at the outer surface 144 of the planetary gear 106 and meshing with the teeth of other gears. It should be noted that the channels are located in... Figure 2 Although not shown in the image, it should be understood that it exists. Figure 3Only the structure of one planetary gear 106 is shown and described herein; however, it should be understood that other planetary gears 106 have similar structures. Similarly, it should be understood that the journal pin 112 associated with each of the other planetary gears 106 is also associated with the housing 120 (…). Figure 2 Fluid connectivity, as described in this article.

[0034] for Figure 3 The planetary gear 106 shown has a passage defined by a pair of circumferential oil channels 136 located near the opposing longitudinal ends of the planetary gear 106. It should be understood that the rotation of the planetary gear 106 relative to the journal pin 112 creates a pressure differential within the clearance 132. Therefore, lubricant 119 is drawn into the clearance 132 from the oil channel 114 via a pump 124 (…). Figure 2 The lubricant 119 is pumped into oil passage 114 and guided into circumferential oil conduit 136. Pump 124 also helps guide lubricant 119 into clearance 132. In a typical journal bearing, oil would leak from the opposing longitudinal open ends. However, in the journal bearing of the present invention, the pressure differential caused by centrifugal force draws lubricant 119 into circumferential oil conduit 136 and prevents lubricant 119 from leaving clearance 132 at the opposing longitudinal open ends. In embodiments, sealing surfaces 135 are provided at one or both of the opposing longitudinal open ends to further prevent lubricant 119 from leaking out of clearance 132. Sealing surfaces 135 reduce the distance between the inner surface 140 of planetary gear 106 and journal pin 112, or completely close the distance between the inner surface 140 of planetary gear 106 and journal pin 112. Sealing surfaces 135 may be defined by thin spaces, polymer lips, springs, mechanical seals, etc.

[0035] The channel is further defined by a pair of distributor conduits 138, each extending inward from a corresponding circumferential oil conduit 136. Each distributor conduit 138 extends toward a longitudinal midpoint of the planetary gear 106 and terminates before intersecting with the other distributor conduit 138. The distributor conduits 138 are oriented at an angle θ relative to the inner surface 140 of the planetary gear 106, which defines a clearance 132 between the planetary gear 106 and the journal pin 112. In one embodiment, the angle θ is greater than 0 degrees and less than 90 degrees. In another embodiment, the angle θ is greater than or equal to 10 degrees and less than or equal to 50 degrees. In another embodiment, the angle θ is greater than or equal to 15 degrees and less than or equal to 45 degrees. In another embodiment, the angle θ is greater than or equal to 20 degrees and less than or equal to 40 degrees. In another embodiment, the angle θ is greater than or equal to 25 degrees and less than or equal to 35 degrees. In another embodiment, the angle θ is 30 degrees + / - 5 degrees. In another embodiment, the angle θ is 30 degrees + / - 10 degrees. In one embodiment, the angle θ is 30 degrees + / - 15 degrees. In another embodiment, the angle θ is 30 degrees + / - 20 degrees. In yet another embodiment, the angle θ is 30 degrees + / - 25 degrees.

[0036] In an embodiment, the first distributor pipe 138 in the distributor pipe 138 in the -X direction of the coordinate axis depicted in the figures may be oriented at an angle θ, while the second distributor pipe 138 in the distributor pipe 138 in the +X direction of the coordinate axis depicted in the figures may be oriented at an angle θ', which is different from the angle θ' of the orientation of the first distributor pipe 138 in the distributor pipe 138. In an embodiment, angle θ' is less than angle θ. In an embodiment, angle θ' is greater than angle θ. In an embodiment, angle θ' is greater than 0 degrees and less than 90 degrees. In an embodiment, angle θ' is greater than or equal to 10 degrees and less than or equal to 50 degrees. In an embodiment, angle θ' is greater than or equal to 15 degrees and less than or equal to 45 degrees. In an embodiment, angle θ' is greater than or equal to 20 degrees and less than or equal to 40 degrees. In an embodiment, angle θ' is greater than or equal to 25 degrees and less than or equal to 35 degrees. In an embodiment, angle θ' is 30 degrees + / - 5 degrees. In an embodiment, angle θ' is 30 degrees + / - 10 degrees. In one embodiment, angle θ' is 30 degrees + / - 15 degrees. In another embodiment, angle θ is 30 degrees + / - 20 degrees. In yet another embodiment, angle θ' is 30 degrees + / - 25 degrees.

[0037] In this embodiment, a plurality of toothed conduits 142 extend from each distributor conduit 138. The toothed conduits 142 terminate at the outer surface 144 of the planetary gear 106 to allow lubricant 119 to coat the meshing teeth of adjacent gears. In this embodiment, the toothed conduits 142 extend from the distributor conduits 138 in a linear direction. However, as described in more detail herein, the toothed conduits 142 can have any suitable shape and extend along any suitable profile. Figure 3 As shown, each distributor conduit 138 includes five toothed conduits 142 spaced equidistantly from each other. However, each distributor conduit 138 may have any number of toothed conduits 142, including a single toothed conduit 142, and multiple toothed conduits 142 may be spaced apart from each other in any arrangement. For example, a distributor conduit 138 may include one or more toothed conduits 142 closer to the circumferential oil conduit 136 and one or more toothed conduits 142 closer to the longitudinal midpoint of the planetary gear 106, such that the toothed conduits 142 are not equidistant from each other.

[0038] It should be understood that during the rotation of the planetary gear 106, due to centrifugal force, the distributor conduit 138, oriented at angle θ, facilitates the flow of lubricant along the distributor conduit 138 to each tooth conduit 142. The orientation of the distributor conduit 138 also regulates the relative flow of lubricant 119 between the tooth conduits 142 by changing the net distance and resistance of each tooth conduit 142. Therefore, in use, lubricant 119 flows from the tank 120 ( Figure 2 The oil is pumped into the journal pin 112 through the oil passage 114 and into the gap 132 that forms the journal bearing 133. As the planetary gear 106 rotates relative to the journal pin 112, centrifugal force draws the lubricant 119 in the gap 132 into the circumferential oil passage 136 along the distributor passage 138 and into each of the plurality of tooth passages 142.

[0039] The planetary gear 106 can be formed in any suitable manner to include a distributor conduit 138 and a toothed conduit 142. For example, the planetary gear 106 can initially be formed by casting, molding, etc., and the distributor conduit 138 and the toothed conduit 142 are respectively formed within the planetary gear 106 by drilling into it. For example, the distributor conduit 138 can be formed by drilling into the planetary gear 106 at an angle and then drilling radially inward from the outer surface 144 of the planetary gear 106 to contact the distributor conduit 138 to form the toothed conduit 142. Alternatively, the planetary gear 106 can be formed by milling the conduits defining the distributor conduit 138 and the toothed conduit 142 into plates and then laminating these plates together to form a stack.

[0040] Although planetary gear 106 is described in this article as being located between LP turbine 30 and fan 38 ( Figure 1 The planetary gear 106 is part of the gearbox assembly 46 between the gearboxes, but it should be understood that the planetary gear 106 can be any gear with journal bearings mounted on it. For example, the planetary gear 106 can be associated with any of the following without departing from the scope of this disclosure: an accessory gearbox, an accessory drive system mounted on an aircraft, a power gearbox mounted on an aircraft, a tiltrotor gearbox, a turboprop reduction gearbox, etc.

[0041] Now for reference Figure 4An embodiment of a planetary gear 106 is shown, comprising a plurality of teeth 134 arranged along the periphery of the planetary gear 106, the plurality of teeth 134 meshing with teeth 200 of a pair of adjacent gears 202. Multiple arrows are shown, indicating tooth channels 142 for lubricant to flow from the journal pin 112 to each of the plurality of teeth 134. Thus, as indicated by the arrows, lubricant is delivered to each tooth 134 of the planetary gear 106. However, in an embodiment, each tooth 134 of the planetary gear 106 may not include an associated channel. Although only a single arrow is shown, it indicates the channel for lubricant 119 (…). Figure 2 Individual tooth channels 142 flow within each tooth 134 of the planetary gear 106, but it should be understood that, as Figure 3 As shown, multiple toothed channels 142 are arranged overlapping each other within each tooth 134 along the + / -X axis of the coordinate axis shown in the figure. In embodiments where multiple toothed channels 142 are arranged within each tooth 134, the toothed channels 142 can be oriented at different angular positions, such that the multiple toothed channels 142 can... Figure 4 As seen in the view shown. For example, in an embodiment, the ends of the toothed conduit 142 terminating at the corresponding teeth 134 will be oriented at different positions relative to the front and rear ends of the teeth 134, so as to be closer to or further away from the adjacent teeth 134, such that the toothed conduits 142 do not completely overlap each other along the + / X axes of the coordinate axes shown in the figures.

[0042] Journal pin 112 ( Figure 3 ) including parallel planetary gear 106 ( Figure 2 The central longitudinal axis 15 extends from axis 13. (e.g.) Figure 3 As shown, the axis 15 of the journal pin 112 is coaxial with the axis 13 of the planetary gear 106. However, in an embodiment, the axis 15 of the journal pin 112 is offset from the axis 13 of the planetary gear 106. Therefore, in the gap 132 ( Figure 3 Lubricant 119 (inside) Figure 2 The thickness of the lubricant 119 can vary circumferentially around the journal pin 112. This results in variations in the pressure and / or temperature of the lubricant 119. It may be desirable to supply the lubricant to the corresponding teeth 134 of the planetary gear 106 “phase-wise.” For example, due to specific temperature and / or pressure limitations, it may be desirable to extract the lubricant 119 from a specific location off-center from the journal bearing 133 from the teeth 134 where the lubricant 119 is delivered. Specifically, it is preferred to extract the lubricant 119 at a temperature and / or pressure different from that directly acting on the teeth 134 that will mesh with the adjacent gear 202. Therefore, in an embodiment, the location where the lubricant 119 leaves the journal bearing 133 is off-center from the teeth 134 to which the lubricant 119 is delivered, rather than as... Figure 3The toothed conduit 142 extends linearly. For example, the tooth 134 closest to the location where the lubricant 119 leaves the journal bearing 133 may be one tooth 134 away from the tooth 134 to which the lubricant 119 is delivered. In other embodiments, the tooth 134 closest to the location where the lubricant 119 leaves the journal bearing 133 may be two teeth 134 away from the tooth 134 to which the lubricant 119 is delivered. In other embodiments, the tooth 134 closest to the location where the lubricant 119 leaves the journal bearing 133 may be three teeth 134 away from the tooth 134 to which the lubricant 119 is delivered. In other embodiments, the tooth 134 closest to the location where the lubricant 119 leaves the journal bearing 133 may be more than three teeth 134 away from the tooth 134 to which the lubricant 119 is delivered. Figure 4 As shown, the teeth 134 closest to the location where the lubricant 119 leaves the journal bearing 133 are the four teeth 134 furthest from the teeth to which the lubricant 119 is delivered. Therefore, in Figure 4 In the illustrated embodiment, the toothed conduit 142 extending between the journal bearing 133 and the teeth 134 of the planetary gear 106 has a serpentine path. In this embodiment, the planetary gear 106 can more likely be formed by milling the conduits defining the distributor conduit 138 and the toothed conduit 142 into plates and then laminating these plates together to form a stack, rather than drilling the serpentine channel into the previously formed planetary gear 106.

[0043] Now for reference Figure 5 This shows a partially enlarged schematic diagram of one tooth 134 of the planetary gear 106. In the lubricant ( Figure 2 In embodiments where the tooth channels 142 are fed to each tooth 134 of the planetary gear 106 and have the serpentine geometry disclosed above, parameters are satisfied to ensure that one or more tooth channels 142 of the associated tooth 134 do not interfere with one or more tooth channels 142 of the adjacent tooth 134. Therefore, the following expression (1) must be satisfied:

[0044] (1)

[0045] In the above expression (1), t represents the distance between two adjacent toothed pipes 142. This indicates the diameter of the toothed tube 142. The circumferential distance traveled along the planetary gear 106 between the end of the toothed conduit 142 extending from the distributor conduit 138 and the opposite end of the toothed conduit 142 within the associated tooth 134, N represents the total number of teeth 134 on the planetary gear 106, and w represents the thickness of the planetary gear 106 extending between the inner surface 140 and the outer surface 144 of the planetary gear 106, with the teeth 134 extending from the outer surface 144 of the planetary gear 106.

[0046] If the above expression (1) is not satisfied after inputting known variables, the variables should be adjusted. For example, the distance t between two adjacent toothed pipes 142 may need to be reduced, and the diameter of the toothed pipe 142 may also need to be adjusted. It may be necessary to reduce the circumferential distance traveled. The number of teeth 134, N, may need to be reduced, and / or the thickness w of the planetary gear 106 may need to be increased. As mentioned above, it should be noted that the above expression (1) only applies when forming the toothed duct 142. Therefore, an alternative solution would not form the toothed duct 142 for each associated tooth 134, for example, alternating teeth 134.

[0047] Now refer to Figure 6 A partial view of planetary gear 106 is shown, which includes a plurality of valves 146 for controlling lubricant 119. Figure 2 ) flows through a specific toothed conduit 142. Although only three valves 146 are shown, it should be understood that the planetary gear 106 may include a valve 146 associated with each tooth 134. In the gearbox assembly 46 ( Figure 2 During operation, planetary gear 106 is subjected to two different centrifugal forces. Specifically, planetary gear 106 is subjected to a first centrifugal force (as indicated by arrow A1) around its center of rotation, and a second centrifugal force generated by planet carrier 110 (…). Figure 2 The rotation of the first centrifugal force A1 causes a second centrifugal force (as indicated by arrow A2). The cyclic rotational relationship between the first centrifugal force A1 and the second centrifugal force A2 generates radial and circumferential excitation forces. These excitation forces cause the operation of valve 146 based on its rotational position, as described in more detail herein. In embodiments, valve 146 is a shuttle valve, a baffle valve, etc.

[0048] Specifically, such as Figure 7 The diagram shows an enlarged view of one of the valves 146. Valve 146 includes a valve body 148 having an outer end surface 150, an inner end surface 152 opposite to the outer end surface 150, a first sidewall 154, and a second sidewall 156 opposite to the first sidewall 154. The first sidewall 154 and the second sidewall 156 extend between the outer end surface 150 and the inner end surface 152. As used herein, the outer end surface 150 refers to the surface of valve body 148 facing the outer end surface 144 of the planetary gear 106. Figure 3 ), while the inner end surface 152 refers to the surface of the valve body 148 facing the inner surface 140 of the planetary gear 106 ( Figure 3The valve body 148 defines an open interior 158. A first sidewall 154 has an inlet 160 formed between an outer end surface 150 and an inner end surface 152, and a second sidewall 156 has an outlet 162 formed between the outer end surface 150 and the inner end surface 152. The inlet 160 and outlet 162 are aligned with each other. As described above, each valve 146 is located within a corresponding toothed conduit 142. Therefore, as... Figure 7 As shown, valve 146 is located within toothed conduit 142 such that an upstream portion 164 of toothed conduit 142 extends from inlet 160 to allow lubricant 119 to flow into valve 146, as indicated by arrow B1, and a downstream portion 166 of toothed conduit 142 extends from outlet 162 to allow lubricant 119 to exit valve 146, as indicated by arrow B2.

[0049] like Figure 7 As shown, valve 146 includes a mass body 168 and is shown in each of the following positions: a first open position C1 (shown in dashed lines), a closed position C2 (shown in dashed lines), and a second open position C3 (shown in solid lines). The mass body 168 is movable within an opening 158 of valve body 148 in a longitudinal direction extending between an outer end surface 150 and an inner end surface 152. When the mass body 168 is in the first open position C1 or the second open position C3, lubricant 119 is allowed to flow from inlet 160 to outlet 162 of valve 146. Alternatively, when the mass body 168 is in the closed position C2, lubricant 119 is prevented from flowing from inlet 160 to outlet 162 of valve 146.

[0050] In an embodiment, based on the direction of the excitation force applied to the mass 168, the mass 168 can move freely within the opening 158 of the valve body 148. For example, in the planetary gear 106 and planet carrier 110 ( Figure 2 During the full rotation of the valve 146, the mass body 168 can move from the first open position C1 to the closed position C2, from the closed position C2 to the second open position C3, from the second open position C3 back to the closed position C2, and from the closed position C2 back to the first open position C1. It should be understood that the valve 146 can be positioned at any part along the toothed conduit 142 such that when the tooth 134 associated with the valve 146 engages with the adjacent gear 202 (… Figure 5 When the tooth 200 of the valve 146 engages with the tooth 200 of the adjacent gear 202, the excitation force causes the mass 168 to move from the closed position C2 to the first open position C1 or the second open position C3. Alternatively, when the tooth 134 associated with the valve 146 does not engage with the tooth 200 of the adjacent gear 202 ( Figure 5 The excitation force causes the mass 168 to move from the first open position C1 or the second open position C3 to the closed position C2. In an embodiment, the mass 168 itself can be adjusted to take into account the desired position of the mass 168 between different positions.

[0051] In an embodiment, valve 146 may include a damper 170 fixed to an inner end surface 152 of valve body 148 and an end of mass 168 opposite to the outer end surface 150 of valve body 148. Therefore, damper 170 provides a biasing force to mass 168 to push mass 168 toward the outer end surface 150 and into a first open position C1. In gearbox assembly 46 ( Figure 2 During operation, once the excitation force exceeds the bias force of the damper 170, the mass 168 is allowed to move from the first open position C1 to the closed position C2, and subsequently to the second open position C3. Thereafter, once the excitation force drops below the bias force of the damper 170, the mass 168 is allowed to move back to the first open position C1. In embodiments, the damper 170 can be any suitable device, such as a spring, a compressible elastomer, etc.

[0052] As can be understood from the above, the turbine engine defined herein includes a gearbox assembly designed to distribute lubricant to the teeth of the gears of the gearbox assembly during meshing with adjacent gears, thereby increasing the efficiency and lubrication of the gearbox assembly. Specifically, the gearbox assembly includes planetary gears having an outer surface and an inner surface opposite to the outer surface. A pair of circumferential oil channels are formed in the inner surface near the opposite ends of the planetary gears, a distributor channel is formed extending longitudinally from each circumferential oil channel toward the center of the planetary gear, and one or more tooth channels are formed extending from each distributor channel to the outer surface of the planetary gear. A journal pin is received within the planetary gear, extending along the axis of rotation of the planetary gear about which it rotates. A clearance defining a journal bearing is formed between the inner surface of the planetary gear and the journal pin. Oil passages are provided to supply oil to the clearance. Therefore, lubricant can be delivered to the teeth.

[0053] Other aspects of the embodiments described herein are provided by the subject matter of the following items:

[0054] A gearbox assembly includes: a planetary gear, the planetary gear including: an outer surface; and an inner surface opposite the outer surface, wherein a pair of circumferential oil conduits are formed in the inner surface near opposite ends of the planetary gear, a distributor conduit is formed extending longitudinally from each circumferential oil conduit toward the center of the planetary gear, and one or more tooth conduits are formed extending from each distributor conduit to the outer surface of the planetary gear; and a journal pin received within the planetary gear, the journal pin extending along an axis of rotation of the planetary gear thereabouts, defining a clearance of a journal bearing formed between the inner surface of the planetary gear and the journal pin, and an oil passage configured to supply oil to the clearance.

[0055] The gearbox assembly according to any one of the preceding clauses, wherein the distributor conduit is oriented at an angle θ relative to the inner surface of the planetary gear, the angle θ being greater than 0 degrees and less than 90 degrees.

[0056] The gearbox assembly according to any one of the preceding clauses, wherein a plurality of toothed conduits extend from each distributor conduit to the outer surface of the planetary gear.

[0057] The gearbox assembly according to any one of the preceding clauses, wherein the plurality of toothed pipes extending from each distributor pipe are spaced apart from each other at equal distances.

[0058] The gearbox assembly according to any one of the preceding clauses, wherein the oil passage of the journal pin comprises: a longitudinal member extending from an end of the journal pin parallel to the axis; and a radial member extending from the end of the longitudinal member to the clearance.

[0059] The gearbox assembly according to any one of the preceding clauses, wherein the radial component extends perpendicular to the longitudinal component.

[0060] The gearbox assembly according to any one of the preceding clauses, wherein: the planetary gear includes a plurality of teeth formed on the outer surface of the planetary gear; the one or more tooth channels include a plurality of tooth channels, each of the plurality of tooth channels extending to a corresponding tooth of the plurality of teeth.

[0061] The gearbox assembly according to any one of the preceding clauses, wherein: the planetary gear includes a plurality of teeth formed on the outer surface of the planetary gear; the one or more tooth conduits include a plurality of tooth conduits, each of the plurality of tooth conduits defining a serpentine path extending from the distributor conduit to a corresponding tooth among the plurality of teeth.

[0062] The gearbox assembly according to any one of the preceding clauses further includes a valve located within the one or more toothed conduits.

[0063] The gearbox assembly according to any one of the preceding clauses, wherein the valve comprises: a valve body; and a mass body capable of being positioned within the valve body, between a first open position, a closed position, and a second open position.

[0064] The gearbox assembly according to any one of the preceding clauses, wherein: the valve body includes an inlet formed in a first sidewall and an outlet formed in a second sidewall, the one or more toothed conduits extending from the inlet and the outlet of the valve; when the mass body is in the first open position or the second open position, lubricant is allowed to flow into the valve through the inlet and out of the valve through the outlet; when the mass body is in the closed position, lubricant is prohibited from flowing into the valve through the inlet and out of the valve through the outlet.

[0065] The gearbox assembly according to any one of the preceding clauses, wherein the valve includes a damper that biases the mass toward the first open position.

[0066] A turbine engine includes: a fan section including a fan; a fan shaft coupled to the fan, the fan shaft configured to rotate the fan; a turbine section including an input shaft; and a gearbox assembly coupled to the input shaft and the fan shaft such that the gearbox assembly transmits rotational motion from the input shaft to the fan shaft, the gearbox assembly including planetary gears, the planetary gears including: an outer surface; an inner surface opposite the outer surface, a pair of circumferential oil passages formed in the inner surface near opposite ends of the planetary gears, distributor passages formed to extend longitudinally from each circumferential oil passage toward the center of the planetary gears, and a plurality of toothed passages formed to extend from each distributor passage to the outer surface of the planetary gears; and a journal pin received within the planetary gears, the journal pin extending along an axis of rotation of the planetary gears thereabouts, and an oil passage formed within the journal pin extending from an end of the journal pin to the outer surface of the journal pin.

[0067] The turbine engine according to any one of the preceding clauses, wherein each distributor pipe is oriented at an angle θ relative to the inner surface of the planetary gear, the angle θ being greater than 0 degrees and less than 90 degrees.

[0068] The turbine engine according to any one of the preceding clauses, wherein: the planetary gear includes a plurality of teeth formed on the outer surface of the planetary gear; and each of the plurality of tooth paths extends to a corresponding tooth of the plurality of teeth.

[0069] The turbine engine according to any one of the preceding clauses, wherein: the planetary gear includes a plurality of teeth formed on the outer surface of the planetary gear; and each of the plurality of tooth channels defines a serpentine path extending from the distributor channel to a corresponding tooth among the plurality of teeth.

[0070] A method includes: guiding lubricant from an oil passage of a journal pin into a gap defined between an inner surface of a planetary gear and the journal pin about which the planetary gear rotates, the lubricant within the gap defining a journal bearing; and rotating the planetary gear to generate a centrifugal force that causes the lubricant to flow from the gap into a pair of circumferential oil channels, a pair of distributor channels extending from the pair of circumferential oil channels, and a plurality of tooth channels extending from each of the pair of distributor channels to a plurality of teeth formed on the outer surface of the planetary gear.

[0071] According to any one of the preceding clauses, the plurality of toothed conduits define a serpentine path extending from the dispenser conduit to a corresponding tooth among the plurality of teeth.

[0072] The method according to any one of the preceding clauses further includes operating the valve between a first open position, a closed position, and a second open position based on the centrifugal force applied to a valve located in a respective toothed channel of the plurality of toothed channels.

[0073] The method according to any one of the preceding clauses, wherein: when the valve is in the first open position or the second open position, the lubricant is allowed to flow through the valve; and when the valve is in the closed position, the lubricant is prevented from flowing through the valve.

[0074] The gearbox assembly according to any one of the preceding clauses, wherein each distributor conduit is oriented at an angle θ relative to the inner surface of the planetary gear, the angle θ being 30 degrees + / - 10 degrees.

[0075] The gearbox assembly according to any one of the preceding clauses, wherein each distributor conduit is oriented at an angle θ relative to the inner surface of the planetary gear, the angle θ being 30 degrees + / - 20 degrees.

[0076] The gearbox assembly according to any one of the preceding clauses, wherein the distributor pipes are oriented at different angles.

[0077] The gearbox assembly according to any one of the preceding clauses further includes a sealing surface disposed at one or both of the opposing longitudinal ends of the opening defining the clearance of the journal bearing.

[0078] The gearbox assembly according to any one of the preceding clauses, wherein the following expression (1) is satisfied:

[0079]

[0080] Where t represents the distance between two adjacent toothed tubes. Indicates the diameter of the toothed tube. The circumferential distance traveled along the planetary gear between the end of the toothed tube extending from the distributor tube and the opposite end of the toothed tube within the associated tooth, where N represents the total number of teeth on the planetary gear, and w represents the thickness of the planetary gear extending between the inner and outer surfaces of the planetary gear, with teeth extending from the planetary gear.

[0081] It will be apparent to those skilled in the art that various modifications and variations can be made to the embodiments described herein without departing from the scope of the claimed subject matter. Therefore, this specification is intended to cover modifications and variations of the various embodiments described herein, provided that such modifications and variations are within the scope of the appended claims and their equivalents.

Claims

1. A gearbox assembly, characterized in that, include: Planetary gears, the planetary gears comprising: outer surface; and An inner surface, opposite to the outer surface, wherein a pair of circumferential oil conduits are formed in the inner surface near the opposite ends of the planetary gear, a distributor conduit is formed extending longitudinally from each circumferential oil conduit toward the center of the planetary gear, and one or more tooth conduits are formed extending from each distributor conduit to the outer surface of the planetary gear; and A journal pin, which is received within the planetary gear, extends along the axis of rotation of the planetary gear about it, a clearance defining a journal bearing, the clearance being formed between the inner surface of the planetary gear and the journal pin, and an oil passage configured to supply oil to the clearance.

2. The gearbox assembly according to claim 1, characterized in that, in, Each of the distributor pipes is oriented at an angle θ relative to the inner surface of the planetary gear, the angle θ being greater than 0 degrees and less than 90 degrees.

3. The gearbox assembly according to claim 1, characterized in that, in, Multiple toothed channels extend from each distributor channel to the outer surface of the planetary gear.

4. The gearbox assembly according to claim 3, characterized in that, in, The plurality of toothed pipes extending from each distributor pipe are spaced equidistantly from each other.

5. The gearbox assembly according to claim 1, characterized in that, in, The oil passage of the journal pin includes: A longitudinal member extending from the end of the journal pin parallel to the axis; and A radial component that extends from the end of the longitudinal component into the gap.

6. The gearbox assembly according to claim 5, characterized in that, in, The radial component extends perpendicular to the longitudinal component.

7. The gearbox assembly according to claim 1, characterized in that, in: The planetary gear includes a plurality of teeth formed on the outer surface of the planetary gear; and The one or more toothed conduits include a plurality of toothed conduits, each of the plurality of toothed conduits extending to a corresponding tooth in the plurality of teeth.

8. The gearbox assembly according to claim 1, characterized in that, in: The planetary gear includes a plurality of teeth formed on the outer surface of the planetary gear; and The one or more toothed conduits include a plurality of toothed conduits, each of the plurality of toothed conduits defining a serpentine path extending from the dispenser conduit to a corresponding tooth among the plurality of teeth.

9. The gearbox assembly according to claim 1, characterized in that, It further includes a valve located within the one or more toothed conduits.

10. The gearbox assembly according to claim 9, characterized in that, in, The valve includes: Valve body; and A mass body that can be positioned within the valve body, between a first open position, a closed position, and a second open position.

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