Gearbox assembly for turbine engine

Abstract

A gearbox assembly for a turbine engine includes a plurality of planetary gears. Each of a plurality of planetary gears is associated with a planetary pin. A plurality of planetary bearing rollers are disposed between the planetary pin and each of the plurality of planetary gears. The plurality of planetary bearing rollers are configured to transmit rotation of each of the plurality of planetary gears to the planetary pin. The rolling bearing cage is configured to guide and position the plurality of planetary bearing rollers such that the plurality of planetary bearing rollers are equidistantly distributed, the rolling bearing cage having an inner diameter surface facing the planetary pin and an outer diameter surface facing away from the planetary pin. The outer diameter guide ring is disposed radially outward of the outer diameter surface for holding the rolling bearing cage.

Description

Technical Field

[0001] This disclosure generally relates to gearbox assemblies for engines, such as turbine engines. Background Technology

[0002] A turbine engine typically includes a fan and a turbine arranged in mutual flow communication. A turbine engine may include one or more gearbox assemblies, and a lubrication system for supplying lubricant to one or more components of the gearbox assemblies. Attached Figure Description

[0003] Features and advantages will become apparent from the following more detailed description of various exemplary embodiments, as illustrated in the accompanying drawings, wherein the same reference numerals generally denote the same, functionally similar and / or structurally similar elements.

[0004] Figure 1 This is a schematic cross-sectional view of a turbine engine according to an embodiment of the present disclosure, taken along the longitudinal centerline axis of the turbine engine.

[0005] Figure 2 According to embodiments of this disclosure Figure 1 A schematic cross-sectional detail of the gearbox assembly shown.

[0006] Figure 3 This is a schematic cross-sectional side view of the gearbox assembly according to the present disclosure, along... Figure 1 The longitudinal centerline axis of the turbine engine shown is cut off.

[0007] Figure 4 This is a schematic cross-sectional view of a gearbox assembly according to an embodiment of the present disclosure, along... Figure 3 The line 4-4 shown is cut perpendicular to the longitudinal centerline axis.

[0008] Figure 5 This is a schematic cross-sectional view of a gearbox assembly according to an embodiment of the present disclosure.

[0009] Figure 6A According to embodiments of this disclosure Figure 5 A perspective view of the rolling element bearing (REB) cage of the gearbox assembly shown.

[0010] Figure 6B According to embodiments of this disclosure Figure 6A The partial cross-sectional view of the REB cage shown illustrates the internal structure of the REB cage's circumferential side rails.

[0011] Figure 6C According to embodiments of this disclosure Figure 6AAnother partial sectional view of the REB cage shown illustrates the internal structure of the REB cage's cross rails.

[0012] Figure 7 This is a partial cross-sectional view of the REB cage according to an embodiment of the present disclosure.

[0013] Figure 8 This is a partially cross-sectional and partially transparent view of a REB cage including optional reinforcement structures according to another embodiment of this disclosure.

[0014] Figure 9 This is a partial cross-sectional view of the REB cage according to another alternative embodiment of the present disclosure. Detailed Implementation

[0015] The features, advantages, and embodiments of this disclosure will be set forth or become apparent from the following detailed description, drawings, and claims. Furthermore, the foregoing summary and the following detailed description are exemplary and intended to provide further explanation, not to limit the scope of the claims made herein.

[0016] Various embodiments of this disclosure will be discussed in detail below. While specific embodiments are discussed, they are for illustrative purposes only. Those skilled in the art will understand that other components and configurations can be used without departing from the scope of this disclosure.

[0017] As used herein, the terms “first” and “second” are used interchangeably to distinguish one component from another and are not intended to indicate the location or importance of a single component.

[0018] The terms "upstream" and "downstream" refer to the relative directions of fluid flow within a fluid flow path. For example, "upstream" refers to the direction from which the fluid flows, and "downstream" refers to the direction from which the fluid flows.

[0019] When the terms “low” and “high”, or their respective comparatives (e.g., lower, higher, where applicable), are used with compressors, turbines, shafts, or spool components, they refer to relative pressure and / or relative speed within the engine, unless otherwise specified. For example, a “low-speed” component is defined as a component configured to operate at a rotational speed (such as the maximum permissible rotational speed) lower than the rotational speed of “high-speed” components of the engine. Alternatively, unless otherwise specified, the above terms may be understood as their superlatives. For example, “low-pressure turbine” may refer to the lowest maximum pressure within the turbine section, and “high-pressure turbine” may refer to the highest maximum pressure within the turbine section. The terms “low” or “high” above may additionally or optionally be understood as the minimum permissible rotational speed and / or pressure, or the minimum or maximum permissible rotational speed and / or pressure, relative to the engine’s normal, desired, steady-state, etc., operation.

[0020] The terms “connection,” “fixation,” “attachment,” “linkage,” etc., refer to direct connection, fixation, attachment, or linking, as well as indirect connection, fixation, attachment, or linking through one or more intermediate parts or features, unless otherwise specified herein.

[0021] The singular forms “a,” “one,” and “the” include plural references unless the context clearly indicates otherwise.

[0022] As used herein, the term "axial" refers to a direction and orientation that extends substantially parallel to the longitudinal centerline of the turbine engine. Furthermore, the terms "radial" and "radially" refer to a direction and orientation that extends substantially perpendicular to the longitudinal centerline of the turbine engine. Additionally, as used herein, the term "circumferentially" refers to a direction and orientation that extends in an arc around the longitudinal centerline of the turbine engine.

[0023] This disclosure provides a planetary gear rolling bearing (REB) cage designed within a planetary gearbox to withstand high G-loads. Conventional gearbox designs employing a planetary configuration (rotating carrier) typically utilize journal bearings due to the limitations of the REB cage. In a planetary configuration, the planetary gears and planetary bearing subassemblies are subjected to centrifugal loads by the rotating carrier. The rotating carrier forces the planetary gear bearing subassemblies to revolve around the engine centerline. In this situation, the REB cage is radially outwardly compressed, forming a single load-bearing interface between the REB cage inner diameter (ID) bore and the pin shoulder. For high G-loads, this interface is insufficient to withstand centrifugal high G-loads. "High G-load" as used herein refers to planetary applications in a revolve bearing system, ranging from 400G to 5000G, depending on transmission parameters such as input speed, gear ratio, and torque density. The symbol "G" represents the Earth's gravitational constant.

[0024] One aspect of this disclosure is to provide high G-load REBs in a planetary configuration by implementing two elements. First, the planetary bearing design incorporates a support pin shoulder and a guide ring, thereby creating an additional load-bearing surface on the outer diameter (OD) surface of the REB cage, in addition to the inner diameter (ID) bore. This doubles the G-load capacity. Second, a lightweight lattice structure can be created in the REB cage using additive manufacturing methods, further reducing the G-load and increasing the orbital speed capability of the bearing system.

[0025] Please refer to the attached diagram. Figure 1 This is a schematic cross-sectional view of the turbine engine 10 according to an embodiment of the present disclosure, taken along the longitudinal centerline axis 12 of the turbine engine 10. Figure 1As shown, the turbine engine 10 defines an axial direction A (extending parallel to the longitudinal centerline axis 12 for reference) and a radial direction R perpendicular to the axial direction A. Generally, the turbine engine 10 includes a fan section 14 and a turbocharger engine 16 disposed downstream of the fan section 14.

[0026] like Figure 1 As shown, the turbocharged engine 16 typically includes a generally tubular housing 18 defining an annular inlet 20. Figure 1 Schematic illustration: A housing 18 encloses a compressor section 21, a combustion section 26, a turbine section 27, and an exhaust nozzle section 32 in a series flow relationship. The compressor section includes a turbocharger or low-pressure (LP) compressor 22, downstream of which is a high-pressure (HP) compressor 24. The turbine section includes a high-pressure (HP) turbine 28, downstream of which is a low-pressure (LP) turbine 30. A high-pressure (HP) shaft 34 or spool drives the HP turbine 28 to the HP compressor 24, causing the HP turbine 28 and HP compressor 24 to rotate synchronously. A low-pressure (LP) shaft 36 or spool drives the LP turbine 30 to the LP compressor 22, causing the LP turbine 30 and LP compressor 22 to rotate synchronously. The compressor section 21, combustion section 26, turbine section 27, and exhaust nozzle section 32 together define the core airflow path.

[0027] Figure 1 In the illustrated embodiment, fan section 14 includes a fan 38 (e.g., a variable pitch fan or a fixed pitch fan) having a plurality of fan blades 40 spaced apart and coupled to disk 42. Figure 1 As shown, fan blades 40 extend outward from disk 42 generally in the radial direction R. Each fan blade 40 is rotatable relative to disk 42 about pitch axis P because the fan blades 40 are operably coupled to actuating member 44, which is configured to collectively change the pitch of the fan blades 40. The fan blades 40, disk 42, and actuating member 44 are rotatable together about longitudinal centerline axis 12 via fan shaft 45, which is driven by LP shaft 36 through a power gearbox (also called gearbox assembly 46). Gearbox assembly 46 in Figure 1 The diagram is schematically shown. The gearbox assembly 46 includes a plurality of gears for adjusting the rotational speed of the fan shaft 45, thereby adjusting the rotational speed of the fan 38 relative to the LP shaft 36.

[0028] Still referencing Figure 1In one embodiment, the disk 42 is covered by a rotatable fan hub 48, which has an aerodynamic profile to facilitate airflow through a plurality of fan blades 40. Furthermore, the fan section 14 includes an annular fan housing or nacelle 50 circumferentially surrounding at least a portion of the fan 38 and / or the turbocharged engine 16. The nacelle 50 is supported relative to the turbocharged engine 16 by a plurality of circumferentially spaced outlet guide vanes 52. Additionally, a downstream section 54 of the nacelle 50 extends beyond the exterior of the turbocharged engine 16 to define a bypass airflow passage 56 between them.

[0029] During operation of the turbine engine 10, a certain amount of air 58 enters the turbine engine 10 through the inlet 60 of the nacelle 50 and / or fan section 14. As the certain amount 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. The pressure of the second portion of air 64 is then increased to form compressed air 65, which is directed through the HP compressor 24 and into the combustion section 26, where the compressed air 65 is mixed with fuel and burned to provide combustion gases 66.

[0030] Combustion gas 66 is guided into and expanded by the HP turbine 28, where a portion of the thermal and / or kinetic energy of the combustion gas 66 is extracted via a successive stage of HP turbine stator blades 68 connected to the housing 18 and HP turbine rotor blades 70 connected to the HP shaft 34, thereby rotating the HP shaft 34 and supporting the operation of the 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 the housing 18 and LP turbine rotor blades 74 connected to the LP shaft 36, thereby rotating the LP shaft 36 and supporting the operation of the LP compressor 22 and the rotation of the fan 38 via the gearbox assembly 46.

[0031] Combustion gas 66 is then directed through the injection exhaust nozzle section 32 of the turbocharged engine 16, providing propulsive thrust. Simultaneously, as a first portion of air 62 is directed through the bypass airflow passage 56 and then exits from the fan nozzle exhaust section 76 of the turbocharged engine 10, the pressure of the first portion of air 62 increases significantly, 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 turbocharged engine 16.

[0032] 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 further be supported using any other suitable fan frame configuration. Furthermore, in other embodiments, any other suitable number or configuration of compressors, turbines, shafts, or combinations thereof may be provided. In other embodiments, aspects of this disclosure may be incorporated into any other suitable turbine engine, such as a turbofan engine, propeller fan engine, turbojet engine, turboprop engine, and / or turboshaft engine.

[0033] Figure 2 According to embodiments of this disclosure Figure 1 A schematic cross-sectional detail view of the gearbox assembly 46 shown. (See attached image.) Figure 2 As shown, the gearbox assembly 46 includes a plurality of gears 200 for adjusting the rotational speed of the fan shaft 45, thereby adjusting the fan 38 relative to the LP shaft 36 (e.g., Figure 1 The rotational speed (shown). The multiple gears 200 include a sun gear 202, multiple planetary gears 204, and a ring gear 206. In Figure 2 In the configuration shown, the gear ring 206 is fixed and connected to the turbine engine 10 via the mounting structure 208 (e.g., Figure 1 The static structure 210 (as shown) is as follows. The input shaft 212 is connected to the sun gear 202. The input shaft 212 can be, for example, an LP shaft 36 (such as...). Figure 1 (As shown). Output shaft 214 is connected to planetary gear 204 via planetary pin 203. Output shaft 214, for example, may be connected to fan 38 (e.g. Figure 1 The fan shaft 45 (as shown). Lubricant 216 is delivered to the gearbox assembly 46 via an oil delivery device 218.

[0034] Figure 3 It is based on the publicly disclosed turbocharged engine 10 (such as...) Figure 1 A schematic cross-sectional side view of the gearbox assembly 300 (shown), taken along the longitudinal centerline axis 12 of the turbine engine 10. Figure 4 This is a schematic cross-sectional view of a gearbox assembly 300 according to an embodiment of the present disclosure, along... Figure 3 The line 4-4 shown is cut perpendicular to the longitudinal centerline axis 12. This gearbox assembly 300 can be used as... Figure 1 Gearbox assembly 46 in the middle.

[0035] The gearbox assembly 300 includes a planetary gear assembly 302, which is enclosed by a gearbox housing 304. The planetary gear assembly 302 includes a sun gear 306 and a plurality of planetary gears 308. Figure 3 Only two of them are shown in the figure, along with the gear ring 310. For clarity, only a portion of the gears is shown in the figure. Multiple planetary gears 308 are supported by planet carriers 312 (…). Figure 3 (Illustrated in the middle) containment and support.

[0036] refer to Figure 3 and Figure 4 In this embodiment, the gearbox assembly 300 is a planetary configuration. In this planetary configuration, the ring gear 310 remains fixed, while the planet carrier 312 allows rotation about the sun gear 306, for example... Figure 4 As shown. For example, the gear ring 310 is connected to the static structure 316 of the turbine engine 10 ( Figure 2 (Seen as static structure 210). In this configuration, fan 38 (as shown in the diagram) Figure 1 (As shown) via planetary carrier 312 through fan shaft 45 (as shown) Figure 1 (As shown) Driven. In this way, multiple planetary gears 308 provide the output of the gearbox assembly 300. Figure 4 It also shows a planetary gear 308 and a bearing system (such as...) Figure 5 The centrifugal force generated by the revolution around the longitudinal centerline axis 12 (as shown) is 350.

[0037] The gearbox assembly 300 includes an input shaft 314. Figure 3 In this configuration, the input shaft 314 is connected to the sun gear 306, or the input shaft 314 and the sun gear 306 are a single integral component. In some embodiments, the sun gear 306 and the input shaft 314 are separate components, with the input shaft 314 connected to the sun gear 306. The input shaft 314 is connected to the turbine section 27 (e.g., Figure 1 (As shown). For example, input axis 314 can be connected to LP axis 36 (as shown). Figure 1 (As shown), or can be specifically represented as LP shaft 36. Multiple planetary gears 308 are located radially outside and mesh with the sun gear 306. The multiple planetary gears 308 are interconnected and supported by a planet carrier 312. The planet carrier 312 supports the multiple planetary gears 308 such that the multiple planetary gears 308 rotate about the sun gear 306, while also allowing each of the multiple planetary gears 308 to rotate about the longitudinal centerline axis 313 of each planetary gear 308 (e.g., ...). Figure 3 (As shown). The gear ring 310 is coupled to the output shaft 318, which is connected to the fan 38 (as shown). Figure 1 (As shown). The gear ring 310 rotates, thereby driving the fan 38 (as shown). Figure 1 (As shown) rotates about the longitudinal centerline axis 12. For example, the output shaft 318 is connected to the fan shaft 45 (as shown). Figure 1 (As shown). In some embodiments, the output shaft 318 and the fan shaft 45 (as shown) Figure 1 (As shown) is formed as a single integral component. The gear ring 310 is an annular gear ring located radially outside and meshing with the plurality of planetary gears 308. The gear ring 310 is operatively connected to the plurality of planetary gears 308.

[0038] Each planetary gear 308 includes a planetary pin 320 (corresponding to...). Figure 2 The planetary pin 320 (203) is used to rotate the corresponding planetary gear 308 about the planetary pin 320. For example, the planetary pin 320 is disposed within the corresponding planetary gear 308. A lubricant 335 (e.g., oil) is provided between the planetary pin 320 and the corresponding planetary gear 308, causing the planetary gear 308 to rotate relative to the planetary pin 320. In addition, a lubricant 335 is also provided between the plurality of planetary gears 308 and the gear ring 310.

[0039] Gearbox assembly 300 includes a lubrication system 330 for supplying lubricant 335 (e.g., oil) to each planetary gear 308 and other components of gearbox assembly 300 (e.g., sun gear 306, ring gear 310, etc.). Lubrication system 330 includes a primary lubrication system 332. Primary lubrication system 332 includes a main lubricant tank 334 for storing lubricant 335. For example, the main lubricant tank 334 may store oil therein. Primary lubrication system 332 includes multiple components, including a lubricant pump 336 and primary lubricant lines 338. Lubricant pump 336 is coupled to, for example, an HP shaft 34 (e.g.,...). Figure 1 (As shown) and powered by it. For example, rotation of the HP shaft 34 causes the lubricant pump 336 to pump lubricant 335 from the main lubricant tank 334. The lubricant pump 336 can include any type of pump for pumping lubricant 335 from the main lubricant tank 334. The primary lubricant line 338 is coupled to the lubricant delivery device 340, which is used to deliver lubricant 335 from the primary lubricant line 338 to the planetary gears 308. In this way, each of the plurality of planetary gears 308 rotates about the planetary pin shaft 320 about the longitudinal centerline axis 313 of the planetary gear. The rotation of the plurality of planetary gears 308 is converted into the revolution of the planet carrier 312 about the sun gear 306. This causes the plurality of planetary gears 308 and bearings to revolve about the longitudinal centerline axis 12. The lubricant delivery device 340 allows lubricant 335 to be delivered from stationary components (e.g., primary lubricant line 338) to rotating components (e.g., sun gear 306, planetary gear 308, and planet carrier 312).

[0040] The gearbox assembly 300 also includes a reservoir 342 and an oil return line 344. The reservoir 342, as... Figure 3As shown, the lubricant 335 delivered to the gearbox assembly 300 is located at the bottom of the gearbox assembly 300. The lubricant 335 is discharged into the reservoir 342. In this way, the reservoir 342 serves as a storage container for collecting and storing lubricant 335 discharged from the rotating gear ring 310 or other parts of the gearbox assembly 300. For example, during operation of the gearbox assembly 300, gravity causes the lubricant 335 to flow between the gear ring 310 and the gearbox housing 304, and towards the reservoir 342.

[0041] The return line 344 provides fluid communication from the reservoir 342 to the return pump 370 to the deaerator (not shown), and then to the main lubricant tank 334. In this way, the lubricant 335 in the reservoir 342 is provided from the reservoir 342 back to the main lubricant tank 334 through the return line 344, so that the lubricant 335 circulates through the primary lubrication system 332.

[0042] In operation, lubricant pump 336 pumps lubricant 335 from main lubricant tank 334 into primary lubricant line 338. Primary lubricant line 338 operably guides lubricant 335 to lubricant delivery device 340. Lubricant delivery device 340 operably guides lubricant 335 to rotary bearing. In this way, lubricant 335 is supplied to planetary gear 308 to allow planetary gear 308 to rotate about planetary pin shaft 320 (e.g., about the longitudinal centerline axis 313 of planetary gear 308), thereby reducing friction. After lubrication, lubricant 335 flows from planetary gear 308 to reservoir 342, and flows between gear ring 310 and gearbox housing 304, and then back to reservoir 342. Lubricant 335 then flows back to main lubricant tank 334 through return line 344.

[0043] Figure 5 This is a schematic cross-sectional view of a gearbox assembly 300 according to an embodiment of the present disclosure. Figure 5 More details of the gearbox assembly 300 are shown, particularly the planetary pins 320. The planetary pins 320 revolve around the longitudinal centerline axis 12, while the planetary gears 308 and the REB cage 512 (described in further detail below) rotate around the longitudinal centerline axis 313 of the planetary gears. Figure 5 As shown, each planetary gear 308 includes a planetary pin 320 (corresponding to...) Figure 2Planetary pin 320 (203) and corresponding planetary gear 308 rotate around it. Planetary pin 320 is connected to output shaft 318 via bracket adapter plate 500. Wrench lock nut 502 is used to secure bracket adapter plate 500 to planetary pin 320. Multiple planetary bearing rollers 504 are disposed between planetary pin 320 and each of multiple planetary gears 308. Multiple planetary bearing rollers 504 are configured to transmit rotation of planetary gear 308 to planetary pin 320 while supporting gear load between the two components. An oil supply sleeve 508 is provided between inner ring 506 and planetary pin 320. Inner ring 506 is connected to bracket adapter plate 500. Bracket adapter plate 500 is connected to planetary pin 320 via inner ring 506. Lubricant delivery system 510 is used to supply lubricant to multiple planetary bearing rollers 504. Lubricant delivery system 510 is connected to primary lubricant line 338, which is connected to lubricant delivery device 340 for delivering lubricant 335 from primary lubricant line 338 to multiple planetary gears 308 (e.g., Figure 3 (As shown).

[0044] In a planetary configuration, the planetary gear 308 is subjected to a centrifugal load because the rotating planetary carrier 312 is connected to the rotating planetary pin 320. The rotating planetary carrier 312 forces the planetary gear 308 to revolve about the longitudinal centerline axis 12. The rotation of the planetary carrier 312 and the rotation of the planetary pin 320 apply a centrifugal force that can radially push the planetary gear 308 away from the planetary pin 320. This generates a radial G-load on the planetary gear 308. The radial G-load on the planetary gear 308 is supported by the planetary bearing roller 504, which transmits this load to the planetary pin 320. The carrier adapter plate 500 is used for assembly. If the diameter on the left side of the planetary carrier 312 is smaller, the planetary bearing assembly (including the planetary bearing roller 504 and the REB cage 512) may not be able to rotate from left to right (e.g., Figure 5 (As shown) Install and slide it onto the planetary carrier 312. Therefore, a larger hole needs to be drilled on the left side of the planetary carrier 312 to slide the planetary bearing assembly into the planetary carrier 312, and then the planetary pin 320 is connected to the planetary carrier 312 only on the left side using the carrier adapter plate 500 (as shown). Figure 5 (As shown).

[0045] For relatively high centrifugal forces (relatively high G-loads), multiple planetary bearing rollers 504 are used between the planetary gear 308 and the planetary pin shaft 320 to keep the planetary gear 308 relatively centered around the longitudinal centerline axis 313 of the planetary gear. Using multiple planetary bearing rollers 504 (i.e., solid bearings) instead of traditional journal bearings that rely solely on fluid pressure provided by lubricant is beneficial, even in cases of lubricant deficiency or deterioration in the journal bearings (e.g., due to…). Figure 3In the event of a malfunction of the lubricant pump 336 (as shown) or if the planetary gear 308 stops rotating, the use of multiple planetary bearing rollers 504 also allows the planetary gear 308 to continue rotating by being supported by the multiple planetary bearing rollers 504.

[0046] However, the multiple planetary bearing rollers 504 may also move radially away from the planetary pin shaft 320 and toward the planetary gear 308. Therefore, the REB cage 512 is used to guide and position the multiple planetary bearing rollers 504 in an equidistant configuration (i.e., substantially equidistant). The REB cage 512 is configured to align the rotation axes 504A of each of the multiple planetary bearing rollers 504 with each other. Without the REB cage 512, the multiple planetary bearing rollers 504 would be tilted and misaligned, causing them to collide with each other. The REB cage 512 has an outer diameter (OD) guide ring 514 to keep the rotation axes 504A of the multiple planetary bearing rollers 504 substantially parallel to the longitudinal centerline axis 313 of the planetary gear 308. The REB cage 512 is configured to keep the multiple planetary bearing rollers 504 longitudinally spaced along the longitudinal centerline axis 313 of the planetary gear 308. REB cage 512 is an integral component with windows cut out from the integral component to provide spacing for the multiple planetary bearing rollers 504 around their circumference. REB cage 512 is also subject to centrifugal force Fc and is therefore radially pushed away from planetary pins 320.

[0047] REB cage 512 has an inner diameter (ID) surface 512A and an outer diameter (OD) surface 512B. The inner diameter (ID) surface 512A of REB cage 512 generally faces the planetary pin 320. The outer diameter (OD) surface 512B of REB cage 512 faces away from the planetary pin 320. Generally, there are no rolling elements or other support elements between REB cage 512 and planetary pin 320 to support REB cage 512. Since multiple planetary bearing rollers 504 rotate with REB cage 512, and REB cage 512 may come into contact with planetary pin 320, a lubricating film is provided between the inner diameter (ID) surface 512A of REB cage 512 and planetary pin 320 to form a journal bearing for REB cage 512, thereby allowing REB cage 512 to rotate with less friction.

[0048] Furthermore, the outer diameter (OD) guide ring 514 is located radially outside the outer diameter (OD) surface 512B of the REB cage 512 to hold the REB cage 512 in place relative to the longitudinal centerline axis 313 of the planetary gear. The outer diameter (OD) guide ring 514 is located at each end of the gearbox assembly 300 (near the carrier adapter plate 500 and near the planetary carrier 312). Therefore, in addition to providing a lubricating film between the inner diameter surface 512A of the REB cage 512 and the planetary pin 320, another lubricating film (e.g., a supporting hydrodynamic lubricating film) is provided between the outer diameter surface 512B of the REB cage 512 and the outer diameter (OD) guide ring 514. The outer diameter (OD) guide ring 514 is connected to the carrier adapter plate 500, in... Figure 5 On the upper left side, and connected to the planetary bracket 31, in Figure 5 On the upper right side.

[0049] Furthermore, the integral outer guide ring 505 is integrally formed with the planetary pin 320. The integral outer guide ring 505 is configured to support the inner diameter surface 512A of the REB cage 512. By adding the outer diameter (OD) guide ring 514, two bearing surfaces can be used, namely the inner diameter surface 512A and the outer diameter surface 512B of the REB cage 512. During the rotation of the plurality of planetary gears 308, the load on the REB cage 512 is distributed between the inner diameter surface 512A and the outer diameter surface 512B of the REB cage 512. The REB cage 512 is mounted within the REB cage cavity 512C defined by the outer diameter (OD) guide ring 514, the planetary bearing roller 504, and the planetary pin 320.

[0050] In addition, an integral inner guide ring 516 is provided, which is located between two adjacent REB cages 512. The integral inner guide ring 516 is configured to support the inner diameter surface 512A and outer diameter surface 512B of the two adjacent REB cages 512. The integral inner guide ring 516 is integrally formed with the lubricated inner ring 506 near the planetary pin 320. The integral inner guide ring 516 has a T-shaped cross-section to retain the adjacent REB cages 512. Using an integral inner guide ring 516 integrally formed with the inner ring 506 instead of providing a separate mounting piece allows for a reduction in the number of parts in the gearbox assembly 300. The two adjacent REB cages 512 are spaced apart by the integral inner guide ring 516.

[0051] Lubricant from a lubricant delivery bearing (e.g., an oil delivery bearing OTB) is supplied via a lubricant delivery system 510, which is connected to a primary lubricant line 338, which in turn is connected to a lubricant delivery device 340 for delivering lubricant 335 from the primary lubricant line 338 to the planetary gear 308 (e.g., ...). Figure 3(As shown). Lubricant from the lubricant delivery system 510 is also distributed to multiple planetary bearing rollers 504 via multiple lubricant conduits 510A within the inner ring 506 (also referred to as "under-ring lubrication"). Lubricant from the lubricant delivery system 510 is also guided through lubricant conduits 514A within the outer diameter (OD) guide ring 514 to provide a lubricating film between the inner diameter surface 512A of the REB cage 512 and the inner ring 506, and between the outer diameter surface 512B of the REB cage 512 and the outer diameter (OD) guide ring 514.

[0052] Furthermore, lubricant from the lubricant delivery system 510 is guided through a first lubricant conduit 516A and a second lubricant conduit 516B within an integral inner guide ring 516 to provide a lubricating film between the inner diameter surface 512A of the REB retainer 512 and the inner ring 506, and between the outer diameter surface 512B of the REB retainer 512 and the integral inner guide ring 516. The first lubricant conduit 516A and the second lubricant conduit 516B form a T-shape to allow lubricant to be guided through the first lubricant conduit 516A and split into two lubricant streams through the second lubricant conduit 516B, thereby delivering lubricant to each of the two adjacent REB retainers 512.

[0053] In operation, lubricant is delivered via lubricant delivery system 510 and distributed through multiple lubricant conduits 510A, lubricant conduit 514A within outer diameter (OD) guide ring 514, a first lubricant conduit 516A within integral inner diameter guide ring 516, and a second lubricant conduit 516B within integral inner guide ring 516. The lubricant is delivered to lubricate planetary bearing rollers 504 and REB cage 512. The lubricant used for lubrication is then discharged or removed through end holes and channels. For example, an inclined end hole 514B is provided within outer diameter (OD) guide ring 514 for discharging or clearing lubricant from the REB cage cavity 512C. Furthermore, lubricant is also discharged through integral inner guide ring channel 516C defined between integral inner guide ring 516 and the tapered surface 516D of planetary gear 308. The lubricant in integral inner guide ring channel 516C is then discharged through planetary gear conduit 518 to the planetary gear 308. Figure 5 The black arrow in the image shows an example of lubricant flow during operation of the gearbox assembly 300.

[0054] Figure 6AThis is a perspective view of a REB retainer 600 according to an embodiment of the present disclosure. The REB retainer 600 can be used as the aforementioned REB retainer 512. As shown in FIG. 6, the REB retainer 600 includes a cylindrical body 602. The cylindrical body 602 includes a plurality of pocket-shaped openings 604 defined within and circumferentially positioned about the cylindrical body 602. Specifically, the plurality of pocket-shaped openings 604 are circumferentially positioned relative to a centerline 606 of the cylindrical body 602. The REB retainer 600 further includes a pair of circumferential side rails 608 and a plurality of transverse rails 610 extending between the pair of circumferential side rails 608, such that the plurality of pocket-shaped openings 604 are defined therebetween. Furthermore, the plurality of pocket-shaped openings 604 are formed within the cylindrical body 602 such that the outer diameter portion 612 of the plurality of transverse rails 610 is thicker than the inner diameter portion 614 of the plurality of transverse rails 610. For example, the outer diameter portions 612 of the plurality of transverse rails 610 of the REB cage 600 correspond to Figure 5 The outer diameter surface 512B of the REB cage 512. For example, the inner diameter portions 614 of the plurality of cross rails 610 of the REB cage 600 correspond to... Figure 5 The inner diameter surface 512A of the REB cage 512.

[0055] As described above, a plurality of planetary bearing rollers 504 are respectively housed within corresponding bag-shaped openings 604. More specifically, the plurality of planetary bearing rollers 504 are radially inserted into each of the plurality of bag-shaped openings 604. The size of the plurality of bag-shaped openings 604 is excessively large relative to the planetary bearing rollers 504, allowing the plurality of planetary bearing rollers 504 to move freely within the plurality of bag-shaped openings 604, and within the gearbox assembly 300 (e.g., Figure 5 When centrifugal loads are generated during operation (as shown), the planetary bearing rollers 504 are forced to abut against the circumferential side rails 608 and / or the transverse rails 610. Therefore, the REB cage 600 guides the plurality of planetary bearing rollers 504 to move circumferentially and axially within a plurality of pouch-like openings 604. In an embodiment, the plurality of pouch-like openings 604 have a rectangular cross-section for accommodating the plurality of cylindrical planetary bearing rollers 504.

[0056] Figure 6B According to embodiments of this disclosure Figure 6A The partial cross-sectional view of the REB retainer 600 shown illustrates the internal structure of the circumferential side rail 608. In an embodiment, at least a portion of the cylindrical body 602 is hollow to reduce the weight of the REB retainer 600. For example, the circumferential side rail 608 may have a hollow cavity 618. The hollow cavity 618 of the circumferential side rail 608 of the cylindrical body 602 of the REB retainer 600 may be provided with a reinforcing structure 620. The reinforcing structure 620 within the hollow cavity 618 may include a porous material, such as polyetheretherketone (PEEK) material, or a foam material, such as metal foam, or a wire mesh.

[0057] Figure 6C According to embodiments of this disclosure Figure 6A Another partial cross-sectional view of the REB retainer 600 shown illustrates the internal structure of the cross rail 610. In this embodiment, at least a portion of the cylindrical body 602 is hollow to reduce the weight of the REB retainer 600. For example, in addition to the circumferential side rails 608 having hollow cavities 618, the cross rails 610 may also have hollow cavities 622. The hollow cavities 622 of the cross rails 610 of the cylindrical body 602 of the REB retainer 600 may also be provided with reinforcing structures 624. The reinforcing structures 624 within the hollow cavities 622 may include porous materials, such as polyetheretherketone (PEEK) materials, or foam materials, such as metal foam, or wire mesh.

[0058] Figure 7 This is a partial cross-sectional view of a REB retainer 700 according to an embodiment of the present disclosure. The REB retainer 700 further includes a reinforcing structure 701 extending within a hollow portion of the cylindrical body 602. Therefore, the reinforcing structure 701 provides stiffness or reinforcement to the cylindrical body 602 and reinforcing the structural integrity of the pocket-shaped opening 604 in the cylindrical body 602. In an alternative embodiment, the reinforcing structure 701 may be omitted from the cylindrical body 602, and the cylindrical body 602 may be completely hollow to reduce the mass of the REB retainer 700.

[0059] As described above, the REB retainer 700 includes a pair of circumferential side rails 608 and a plurality of transverse rails 610 extending between the pair of circumferential side rails 608. In an embodiment, at least one of the pair of circumferential side rails 608 and the plurality of transverse rails 610 is hollow for accommodating a reinforcing structure 701 therein. More specifically, the hollow portion of the cylindrical body 602 includes opposing sidewalls 702 defining a hollow cavity 704. The reinforcing structure 701 interconnects the opposing sidewalls 702. The reinforcing structure 701 can be any suitable structural support capable of enabling the REB retainer 600 to perform the functions described herein. Furthermore, in some embodiments, the reinforcing structure 701 can be based on the gearbox assembly 300 (such as...). Figure 5 During operation (as shown), the predetermined direction of the maximum directional load borne by different parts of the cylindrical body 602 is oriented within the hollow cavity 704.

[0060] For example, during operation of the gearbox assembly 300, the maximum load acting on a pair of circumferential side rails 608 is radial due to centrifugal force, while the maximum load acting on the plurality of transverse rails 610 is circumferential due to engagement with a plurality of rotating planetary bearing rollers 504 (as shown in FIG. 5). In some embodiments, the reinforcing structure 701 provides directional stiffness force, i.e., the stiffness force provided by the reinforcing structure 701 in one direction is greater than the stiffness force in another direction. Therefore, the reinforcing structure 701 is positioned such that the directional stiffness force it provides is directed to counteract directional loads acting on different portions of the cylindrical body 602.

[0061] For example, refer to Figure 7 The reinforcement structure 701 includes a first rib 706 extending between opposing sidewalls 702 of a pair of circumferential side rails 608, and a second rib 708 extending between opposing sidewalls 702 of a plurality of transverse rails 610. The first rib 706 and the second rib 708 contribute to increasing the shear and bending load-bearing stiffness of the REB cage 600. As described above, the reinforcement structure 701 is oriented based on directional loads received at different portions of the cylindrical body 602. In this embodiment, the first rib 706 extending within the pair of circumferential side rails 608 is radially oriented relative to the centerline 606 of the cylindrical body 602 (as shown in FIG. 6). Furthermore, the second rib 708 extending within the plurality of transverse rails 610 is circumferentially oriented relative to the centerline 606 of the cylindrical body 602. In this way, the directional stiffness force provided by the first rib 706 is radially oriented relative to the centerline 606 (as shown in FIG. 6). Figure 6A As shown), the directional stiffness force provided by the second rib member 708 is circumferentially oriented relative to the centerline 606 in order to counteract directional loads acting on different parts of the cylindrical body 602.

[0062] Figure 8 This is a partially cross-sectional and partially transparent view of a REB retainer 800 including an optional reinforcement structure according to another embodiment of this disclosure. The reinforcement structure 701 includes a honeycomb structure 801 (e.g., a porous structure) extending within a hollow portion of a cylindrical body 602. The honeycomb structure 801 includes a plurality of sidewalls 802 oriented to define a plurality of hollow channels 804. As described above, the reinforcement structure 701 is oriented within the hollow cavity 704 based on a predetermined direction of the maximum directional load received by different portions of the cylindrical body 602. In an exemplary embodiment, the honeycomb structure 801, positioned within a pair of circumferential side rails 608, is oriented such that the sidewalls 802 are relative to the centerline 606 of the cylindrical body 602 (e.g., ...). Figure 6A(As shown) Extending radially. Furthermore, the honeycomb structure 801, positioned within a plurality of transverse rails 610, is oriented such that the sidewalls 802 extend circumferentially relative to the centerline 606 of the cylindrical body 602. Therefore, the directional stiffness force provided by the honeycomb structure 801 positioned within a pair of circumferential side rails 608 is radially oriented relative to the centerline 606, and the directional stiffness force provided by the honeycomb structure 801 positioned within the plurality of transverse rails 610 is circumferentially oriented relative to the centerline 606, to help counteract directional loads acting on different portions of the cylindrical body 602.

[0063] Figure 9 This is a partial cross-sectional view of a REB retainer 900 according to another alternative embodiment of this disclosure. See also Figure 9 The reinforcing structure 701 includes a predetermined amount of filler material 901 that fills the hollow cavity 704. The filler material 901 can be made of any material capable of enabling the reinforcing structure 701 to perform the functions described herein. In an embodiment, the filler material 901 differs from the material used to manufacture the cylindrical body 602. In an embodiment, the cylindrical body 602 is made of a metallic material. Furthermore, the density of the filler material 901 is lower than that of the material used to manufacture the cylindrical body 602, so that even though the hollow cavity 704 is filled with filler material 901, the mass of the REB retainer 600 is reduced. Examples of the filler material 901 include, but are not limited to, polyetheretherketone (PEEK) materials and foam materials, such as metal foam or wire mesh.

[0064] REB cages 600, 700, 800, and 900 can be formed using any manufacturing technique that enables gearbox assembly 300 to achieve the functions described herein. For example, to achieve a structure that is at least partially hollow, REB cages 600, 700, 800, and 900 can be formed using additive manufacturing techniques. Alternatively, REB cages 600, 700, 800, and 900 can also be formed using casting or brazing techniques.

[0065] As described above, embodiments of REB cages 600, 700, 800, and 900 can be used in high-speed, low-reduction-ratio planetary integral drive systems. More specifically, the bearings in planetary integral drive systems experience high centrifugal loads due to the rotation of the planetary carrier. The mass of the rolling bearing cage can be reduced to help reduce the stress caused by high centrifugal loads. Furthermore, the rolling bearing cage includes a reinforcing structure that reinforcing the structural integrity of the rolling bearing cage while still reducing its mass. Therefore, the strain on the rolling bearing cage is reduced, enabling the rolling bearing cage to withstand the greater centrifugal loads caused by the rotation of the planetary carrier.

[0066] Further aspects of this disclosure are provided by the subject matter of the following clauses.

[0067] A gearbox assembly for a turbine engine includes: a plurality of planetary gears, each of which is associated with a planetary pin; a plurality of planetary bearing rollers disposed between the planetary pin and each of the planetary gears, the planetary bearing rollers being configured to transmit rotation of each of the planetary gears to the planetary pin; a REB cage configured to guide and position the plurality of planetary bearing rollers such that the plurality of planetary bearing rollers are equidistantly spaced, the REB cage having an inner diameter surface facing the planetary pin and an outer diameter surface facing away from the planetary pin; and an outer diameter guide ring disposed radially outside the outer diameter surface for holding the REB cage in place relative to the longitudinal centerline axis of the planetary gears. During rotation of the plurality of planetary gears, the load on the REB cage is distributed between the inner diameter surface and the outer diameter surface of the REB cage.

[0068] According to the gearbox assembly described in the foregoing clause, the plurality of planetary bearing rollers are configured to support the rotation of each of the plurality of planetary gears.

[0069] According to any of the preceding items, the gearbox assembly wherein the REB cage is configured to align the rotation axes of the plurality of planetary bearing rollers relative to each other.

[0070] According to any of the preceding items, the gearbox assembly wherein the REB cage is an integral component having a plurality of pouch-like openings configured to receive the plurality of planetary bearing rollers, thereby providing spacing for the plurality of planetary bearing rollers around their circumference.

[0071] According to any of the preceding items, a lubricating film is provided between the inner diameter surface of the REB cage and the planetary pin to form a journal bearing for the REB cage, thereby allowing the REB cage to rotate with less friction.

[0072] According to any of the preceding items, a lubricating film is provided between the outer diameter surface of the REB cage and the outer diameter guide ring to form a journal bearing for the REB cage, thereby allowing the REB cage to rotate with less friction.

[0073] According to any of the preceding claims, the outer diameter guide ring includes a lubricant conduit configured to guide lubricant between the outer diameter surface of the REB cage and the outer diameter guide ring.

[0074] The gearbox assembly according to any of the preceding items further includes an integral inner guide ring disposed between two adjacent REB cages, the integral inner guide ring being configured to support the inner diameter surface and the outer diameter surface of the two adjacent REB cages.

[0075] According to any of the preceding items, the REB cage includes a cylindrical body and a reinforcing structure extending within a portion of the cylindrical body.

[0076] According to any of the preceding items, the reinforcing structure includes one or more ribs, a honeycomb structure extending within the hollow portion of the cylindrical body, or a filling material configured to fill the hollow cavity of the cylindrical body, or any combination thereof.

[0077] The gearbox assembly according to any of the preceding items further includes a bracket adapter plate, through which the planetary pins are connected to the output shaft.

[0078] According to any of the preceding items, the gearbox assembly has the bracket adapter plate connected to the planetary pin via an inner ring, such that the inner ring is connected to the bracket adapter plate.

[0079] The gearbox assembly according to any of the preceding items further includes a lubricant delivery system configured to provide lubricant to the plurality of planetary bearing rollers.

[0080] According to any of the preceding items, in the gearbox assembly, the lubricant delivery system is connected to a primary lubricant line, which is connected to a lubricant delivery device configured to deliver lubricant from the primary lubricant line to the plurality of planetary gears.

[0081] According to any of the preceding items, the REB cage includes an outer diameter (OD) guide ring to keep the rotational axes of the plurality of planetary bearing rollers substantially parallel to the longitudinal centerline axis of the planetary gear.

[0082] According to any of the preceding items, the REB cage is configured to keep the plurality of planetary bearing rollers spaced apart in the longitudinal direction along the longitudinal centerline axis of the planetary gear.

[0083] According to any of the preceding items, the gearbox assembly, the REB cage includes a cylindrical body having a plurality of pouch-like openings defined within the cylindrical body and circumferentially positioned about the cylindrical body.

[0084] According to any of the preceding items, the plurality of bag-shaped openings are circumferentially positioned relative to the centerline of the cylindrical body.

[0085] According to any of the preceding items, the gearbox assembly, the REB cage further includes a pair of circumferential side rails and a plurality of transverse rails extending between the pair of circumferential side rails, such that the plurality of pocket-shaped openings are defined therebetween.

[0086] According to any of the preceding items, at least a portion of the cylindrical body is hollow to reduce the mass of the REB cage.

[0087] A turbine engine includes an input shaft and an output shaft, and a gearbox assembly comprising: a ring gear coupled to a static structure of the turbine engine; a sun gear coupled to the input shaft; a plurality of planetary gears operatively connected to the sun gear, each of the plurality of planetary gears associated with a planetary pin connected to the output shaft; a plurality of planetary bearing rollers disposed between the planetary pin and each of the plurality of planetary gears, the plurality of planetary bearing rollers configured to transmit rotation of each of the plurality of planetary gears to the planetary pin; a REB cage configured to guide and position the plurality of planetary bearing rollers such that the plurality of planetary bearing rollers are equidistantly spaced, the REB cage having an inner diameter surface facing the planetary pin and an outer diameter surface facing away from the planetary pin; and an outer diameter guide ring disposed radially outside the outer diameter surface to hold the REB cage in place relative to the longitudinal centerline axis of the plurality of planetary gears. During the rotation of the plurality of planetary gears, the load on the REB cage is distributed between the inner diameter surface and the outer diameter surface of the REB cage.

[0088] According to the turbine engine described in the foregoing clause, the plurality of planetary bearing rollers are configured to support the rotation of each of the plurality of planetary gears.

[0089] According to any of the preceding items, the REB cage is configured to align the rotation axes of the plurality of planetary bearing rollers relative to each other.

[0090] According to any of the preceding items, the turbine engine wherein the REB cage is an integral component having a plurality of pouch-like openings configured to receive the plurality of planetary bearing rollers, thereby providing spacing for the plurality of planetary bearing rollers around their circumference.

[0091] According to any of the preceding items, a lubricating film is provided between the inner diameter surface of the REB cage and the planetary pin to form a journal bearing for the REB cage, thereby allowing the REB cage to rotate with less friction.

[0092] According to any of the preceding items, a lubricating film is provided between the outer diameter surface of the REB cage and the outer diameter guide ring to form a journal bearing for the REB cage, thereby allowing the REB cage to rotate with less friction.

[0093] According to any of the preceding items, the outer diameter guide ring includes a lubricant conduit configured to guide lubricant between the outer diameter surface of the REB cage and the outer diameter guide ring.

[0094] According to any of the preceding items, the turbine engine, wherein the gearbox assembly further includes an integral inner guide ring disposed between two adjacent REB cages, the integral inner guide ring being configured to support the inner diameter surface and the outer diameter surface of the two adjacent REB cages.

[0095] According to any of the preceding items, the REB cage includes a cylindrical body and a reinforcing structure extending within a portion of the cylindrical body.

[0096] According to any of the preceding items, the reinforcing structure includes one or more ribs, a honeycomb structure extending within the hollow portion of the cylindrical body, or a filling material configured to fill the hollow cavity of the cylindrical body, or any combination thereof.

[0097] The turbine engine according to any of the preceding items further includes a bracket adapter plate, through which the planetary pin is connected to the output shaft.

[0098] According to any of the preceding items, in the turbine engine, the bracket adapter plate is connected to the planetary pin via an inner ring, such that the inner ring is connected to the bracket adapter plate.

[0099] The turbine engine according to any of the preceding items further includes a lubricant delivery system configured to provide lubricant to the plurality of planetary bearing rollers.

[0100] According to any of the preceding items, in the turbine engine, the lubricant delivery system is connected to a primary lubricant line, which is connected to a lubricant delivery device configured to deliver lubricant from the primary lubricant line to the plurality of planetary gears.

[0101] According to any of the preceding items, the REB cage includes an outer diameter (OD) guide ring to keep the rotational axes of the plurality of planetary bearing rollers substantially parallel to the longitudinal centerline axis of the planetary gear.

[0102] According to any of the preceding items, the REB cage is configured to keep the plurality of planetary bearing rollers spaced apart in the longitudinal direction along the longitudinal centerline axis of the planetary gear.

[0103] According to any of the preceding items, the REB cage includes a cylindrical body having a plurality of pouch-like openings defined within the cylindrical body and circumferentially positioned about the cylindrical body.

[0104] According to any of the preceding items, the plurality of bag-shaped openings are circumferentially positioned relative to the center of the cylindrical body of the turbine engine.

[0105] According to any of the preceding items, the REB cage further includes a pair of circumferential side rails and a plurality of transverse rails extending between the pair of circumferential side rails, such that the plurality of bag-shaped openings are defined therebetween.

[0106] According to any of the preceding items, at least a portion of the cylindrical body is hollow to reduce the mass of the REB cage.

[0107] While the above description pertains to preferred embodiments of this disclosure, those skilled in the art will understand that other changes and modifications can be made without departing from the scope of this disclosure. Furthermore, even if not explicitly stated above, features described in connection with one embodiment of this disclosure can be used in conjunction with other embodiments.

Claims

1. A gearbox assembly for a turbine engine, characterized in that, The gearbox assembly includes: A plurality of planetary gears, each of which is associated with a planetary pin; A plurality of planetary bearing rollers are disposed between each of the planetary pins and each of the plurality of planetary gears, the plurality of planetary bearing rollers being configured to transmit rotation of each of the plurality of planetary gears to the planetary pins; A rolling bearing (REB) cage configured to guide and position the plurality of planetary bearing rollers such that the plurality of planetary bearing rollers are equidistantly spaced, the REB cage having an inner diameter surface facing the planetary pins and an outer diameter surface facing away from the planetary pins; and An outer diameter guide ring, disposed radially outside the outer diameter surface, is used to hold the REB cage in place relative to the longitudinal centerline axis of the planetary gears of the plurality of planetary gears. During the rotation of the plurality of planetary gears, the load on the REB cage is distributed between the inner diameter surface and the outer diameter surface of the REB cage.

2. The gearbox assembly according to claim 1, characterized in that, The plurality of planetary bearing rollers are configured to support the rotation of each of the plurality of planetary gears.

3. The gearbox assembly according to claim 1, characterized in that, The REB cage is configured to align the rotation axes of the plurality of planetary bearing rollers relative to each other.

4. The gearbox assembly according to claim 1, characterized in that, The REB cage is an integral component with multiple pouch-like openings configured to receive the multiple planetary bearing rollers, thereby providing spacing for the multiple planetary bearing rollers around their circumference.

5. The gearbox assembly according to claim 1, characterized in that, A lubricating film is provided between the inner diameter surface of the REB cage and the planetary pin to form a journal bearing for the REB cage, thereby allowing the REB cage to rotate with less friction.

6. The gearbox assembly according to claim 1, characterized in that, A lubricating film is provided between the outer diameter surface of the REB cage and the outer diameter guide ring to form a journal bearing for the REB cage, thereby enabling the REB cage to rotate with less friction.

7. The gearbox assembly according to claim 1, characterized in that, The outer diameter guide ring includes a lubricant conduit configured to guide lubricant between the outer diameter surface of the REB cage and the outer diameter guide ring.

8. The gearbox assembly according to claim 1, characterized in that, It further includes an integral inner guide ring disposed between two adjacent REB cages, the integral inner guide ring being configured to support the inner diameter surface and the outer diameter surface of the two adjacent REB cages.

9. The gearbox assembly according to claim 1, characterized in that, The REB cage comprises a cylindrical body and a reinforcing structure extending within a portion of the cylindrical body.

10. The gearbox assembly according to claim 9, characterized in that, The reinforcing structure includes one or more ribs, a honeycomb structure extending within the hollow portion of the cylindrical body, or a filling material configured to fill the hollow cavity of the cylindrical body, or any combination thereof.

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