Assemblies and methods associated with preload or end play setting for a bearing

Abstract

An example assembly includes a shaft having external threads and a splined portion, a nut having internal threads configured to engage the external threads of the shaft and external splines, wherein the nut is configured to move axially along the shaft when rotated, a tapered bearing mounted to the shaft and having an inner race and an outer race, wherein the nut is configured to apply force against the inner race when moved axially toward the tapered bearing, and a sleeve having internal splines configured to engage both the external splines of the nut and the splined portion of the shaft to prevent relative rotation between the nut and the shaft. The assembly enables precise adjustment of bearing preload through threaded engagement without requiring shims. The sleeve locks the adjustment mechanism after the desired bearing setting is achieved.

Description

Assemblies and Methods Associated with Preload or End Play Setting for a Bearing CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims the benefit of priority under 35 U.S.C. § 119(e) to U.S. Provisional Patent Application No. 63 / 754,754, filed February 6, 2025, the entire contents of which are incorporated herein by reference in its entirety.FIELD OF INVENTION

[0002] The present disclosure relates to bearing assemblies and adjustment mechanisms, and more particularly to assemblies and methods for setting end play or preload of bearings without using shims or trial and error approaches.BACKGROUND

[0003] Tapered bearings are commonly used in mechanical systems, particularly in gearboxes and transmissions, to support both radial and axial loads. These bearings are designed to handle thrust forces and side loading that occur in applications involving helical gears or other components that generate axial forces during operation. The proper functioning of tapered bearings depends on achieving the correct end play or preload setting during assembly.

[0004] End play refers to the axial clearance or distance that a shaft can move between bearings, representing the amount of axial movement allowed by the bearings' design or configuration. Preloading involves applying a controlled axial load to align the bearing raceways, independent of external operational loads. Achieving the proper end play or preload setting is fundamental to maximizing bearing performance and service life in mechanical applications.

[0005] Traditional methods for setting bearing end play or preload typically involve the use of shim washers or gaskets of vary ing thicknesses. Due to manufacturing tolerances in machined components, multiple shim thicknesses are often required to achieve the desiredbearing seting. The assembly process generally follows a trial-and-error approach where technicians fit a shim, measure the resulting end play, and repeat the process with different shim combinations until the proper bearing seting is achieved.

[0006] This conventional shimming approach presents several challenges in manufacturing environments. The process can be time-consuming and labor-intensive, as multiple iterations may be required to achieve the desired bearing seting. Additionally, maintaining inventory of various shim thicknesses adds complexity to parts management and supply chain considerations. The trial-and-error nature of the process can also introduce variability in assembly procedures and may require skilled technicians to achieve consistent results.

[0007] In applications involving multiple tapered bearings on a single shaft, the complexity of the shimming process increases substantially. Each bearing assembly may require individual adjustment, and the cumulative effect of dimensional tolerances across multiple components can create substantial stack-up variations that must be accommodated during assembly.

[0008] There exists a general need for improved methods and assemblies that can provide more efficient and consistent approaches to seting bearing end play or preload while reducing the complexity and variability associated with traditional shimming techniques. It with respect to these and other considerations that the disclosure made herein is presented.SUMMARY

[0009] This summary is provided to introduce a selection of concepts in a simplified form that are further described below in the detailed description. This summary is not intended to identity' key features or essential features of the claimed subject mater, nor is it intended to be used as an aid in determining the scope of the claimed subject mater.

[0010] In a first example implementation, the present disclosure describes an assembly. The assembly includes a shaft having external threads and a splined portion. The assembly comprises a nut having internal threads configured to engage the external threads of the shaftand external splines, wherein the nut is configured to move axially along the shaft when rotated. The assembly comprises a tapered bearing mounted to the shaft and having an inner race and an outer race, wherein the nut is configured to apply force against the inner race when moved axially toward the tapered bearing. The assembly comprises a sleeve having internal splines configured to engage both the external splines of the nut and the splined portion of the shaft to prevent relative rotation between the nut and the shaft.

[0011] In a second example implementation, the present disclosure describes a method for setting bearing preload or end play. The method comprises mounting a nut having internal threads to a shaft having external threads such that the internal threads engage the external threads. The method comprises mounting a sleeve to the nut such that the sleeve is configured to slide axially relative to the nut. The method comprises mounting a tapered bearing to the shaft, wherein the tapered bearing has an inner race and an outer race. The method comprises moving the nut axially toward the inner race of the tapered bearing until the nut applies a force on the inner race, thereby setting a preload against the outer race. The method comprises sliding the sleeve axially relative to the nut until the sleeve engages the shaft while remaining engaged with the nut, thereby preventing relative rotation between the nut and the shaft. The method comprises locking the sleeve in position relative to the shaft.

[0012] The foregoing general description of the illustrative embodiments and the following detailed description thereof are merely exemplary' aspects of the teachings of this disclosure and are not restrictive.BRIEF DESCRIPTION OF FIGURES

[0013] The novel features believed characteristic of the illustrative examples are set forth in the appended claims. The illustrative examples, however, as well as a preferred mode of use, further objectives and descriptions thereof, will best be understood by reference to the following detailed description of an illustrative, non-limiting and non-exhaustive examples of the present disclosure when read in conjunction with the accompanying Figures.

[0014] FIG. 1 illustrates a perspective cross-sectional view of a gearbox with a bearing preload assembly, according to an example implementation.

[0015] FIG. 2 illustrates a cross-sectional view of the gearbox of FIG. 1, according to an example implementation.

[0016] FIG. 3 illustrates a partial exploded perspective view of the bearing preload assembly, according to an example implementation.

[0017] FIG. 4 illustrates a cross-sectional view of the bearing preload assembly in a partially assembled state, according to an example implementation.

[0018] FIG. 5 illustrates a cross-sectional view of the bearing preload assembly with a sleeve engaged, according to an example implementation.

[0019] FIG. 6 illustrates a cross-sectional view of the bearing preload assembly in a fully assembled state, according to an example implementation.

[0020] FIG. 7 illustrates a flowchart of a method for setting bearing preload or end play in a gearbox assembly, according to an example implementation.

[0021] FIG. 8 illustrates a flowchart of a method for simultaneous multi-bearing adjustment in a gearbox assembly, according to an example implementation.DETAILED DESCRIPTION

[0022] The following description sets forth exemplary aspects of the present disclosure. It should be recognized, however, that such description is not intended as a limitation on the scope of the present disclosure. Rather, the description also encompasses combinations and modifications to those exemplary aspects described herein.

[0023] The present disclosure relates to assemblies and methods for setting bearing preload or end play without requiring shims or trial-and-error approaches. The disclosed mechanism may provide a direct adjustment system that eliminates the time-consuming process of selecting and testing vanous shim thicknesses to achieve proper bearing settings.

[0024] The bearing preload or end play setting mechanism may utilize a threaded nut and locking sleeve arrangement to provide precise control over bearing adjustment. In some examples, the mechanism allows for continuous adjustment rather than discrete shim-based increments. The threaded engagement between components may enable fine-tuned positioning to achieve desired bearing settings.

[0025] The precision of the end play mechanism may depend on the number of teeth in the splines and the pitch of the threads. In some examples, increasing the number of spline teeth provides finer resolution for the adjustment mechanism. The thread pitch may also contribute to the overall precision, with finer thread pitches allowing for more precise axial positioning of the adjustment components.

[0026] The disclosed system may provide the capability to simultaneously adjust multiple bearings through a single adjustment mechanism. In examples, adjusting the preload or end play of one tapered bearing simultaneously adjusts the respective preload and end play of other tapered bearings through reaction forces acting on the shaft. This simultaneous adjustment feature may eliminate the need to individually set each bearing in a multi-bearing assembly.

[0027] The system may allow for either setting end play or applying preload to the bearings depending on the application requirements. In an example, the mechanism can be adjusted to provide a near-zero end play condition or to apply a specific preload force to the bearings. The flexibility to achieve either condition may make the system suitable for various gearbox applications with different bearing performance requirements.

[0028] Referring to FIGS. 1 and 2 together, a gearbox 100 may be configured as a standalone gearbox or may be coupled to other transmissions. In some examples, the gearbox 100 may represent a power take-off (PTO) unit that is driven by a transmission of a vehicle. A PTO unit may refer to a mechanical device that transfers power from a primary power source, such as an engine or transmission, to auxiliary equipment or implements. The PTO unit may enable the operation of hydraulic pumps, generators, compressors, or other driven equipment while utilizing the rotational power available from the vehicle's powertrain.

[0029] The gearbox 100 may include a housing 102 that contains the internal components of the gearbox 100. The housing 102 may have a flange 104 that enables mounting the gearbox 100 to other components such as a vehicle frame or transmission.

[0030] The gearbox 100 may include an input gear 106 that may be configured to be driven by an external component such as a gear of a transmission to which the gearbox 100 is mounted. The input gear 106 may be meshed with and configured to drive an output gear 108 disposed within the housing 102. In some examples, the output gear 108 may be a compound gear that includes an outer gear 109 and an inner gear 111 that are coupled to each other via a spline arrangement. The outer gear 109 may engage the input gear 106, while the inner gear 111 may be mounted about a shaft 110.

[0031] The gearbox 100 may include multiple tapered bearings to support the shaft 110 and output gear 108. A first tapered bearing 112 and a second tapered bearing 114 may be mounted adjacent to each other in a back-to-back configuration to support the inner gear 111. The shaft 110 may include a shoulder 115 that interfaces with the first tapered bearing 112. A third tapered bearing 116 may allow the shaft 110 to rotate relative to a first end cap 118 coupled to a first end of the housing 102. A fourth tapered bearing 120 may allow the shaft 110 to rotate relative to a second end cap 122 coupled to a second end of the housing 102.

[0032] The gearbox 100 may include a clutch system for selectively coupling the output gear 108 to the shaft 110. In an example, a vehicle or system that includes the gearbox 100 may include a solenoid valve that operates in response to a command signal via a controller. When such solenoid valve is actuated via the command signal, it sends a fluid signal to a fitting 124 mounted to the first end cap 118 as shown, and such fluid signal actuates the clutch system.

[0033] For example, a central channel 126 may extend longitudinally through the shaft 110, providing a fluid pathway from the fitting 124. Further, a cross-hole 128 (e.g., drilled passage) in the shaft 110 may provide fluid communication between the central channel 126 and a piston 130 to drive the piston 130.

[0034] The piston 130 may be configured to actuate a clutch 132 (e.g., a clutch pack of friction disks) to couple the output gear 108 to the shaft 110. In the example implementation of FIGs. 1-2, the inner gear 111 may have an extension 134. and the clutch 132 may be radially interposed between the extension 134 and a clutch gear 136, which may be engaged with the shaft 110 via splines or other mechanisms.

[0035] When the fluid signal actuates the piston 130, the piston 130 may move axially to compress the clutch plates of the clutch 132 together, thereby coupling the output gear 108 to the shaft 110. The clutch engagement process may transfer rotary7motion from the output gear 108 through the clutch 132 to the clutch gear 136, which in turn rotates the shaft 110.

[0036] The gearbox 100 may include a clutch spring 140 configured to return the piston 130 to disengage the clutch 132 when the fluid signal is removed. Particularly, when the operator deactivates the solenoid valve and the fluid signal no longer pushes the piston 130 to engage the clutch 132. the clutch spring 140 may push the piston 130 back to disengage the clutch 132 and stop spinning the shaft 110. The clutch spring 140 may ensure rapid disengagement of the clutch 132 to prevent unwanted power transmission when the gearbox 100 is deactivated.

[0037] The second end cap 122 may include a cavity 138 that may be configured to accommodate external components driven by the gearbox 100. For example, the shaft 110 may¬ drive a component such as a hydraulic pump mounted to the cavity 138 formed in the second end cap 122.

[0038] The gearbox 100 may further include an assembly 142 that operates as a setting mechanism for end play or preloading the bearings of the gearbox 100. The assembly 142 may provide a direct adjustment system that eliminates the need for shims or trial-and-error approaches in setting bearing preload or end play conditions.

[0039] In an example, the assembly 142 may be configured to provide precise adjustment of bearing preload or end play through a threaded adjustment mechanism that eliminates the need for shims or trial-and-error approaches. The assembly 142 may utilize a combination ofthreaded engagement and splined locking components to achieve and maintain desired bearing settings. In some examples, the assembly 142 may enable continuous adjustment rather than the discrete increments typically associated with shim-based systems.

[0040] The operation of the assembly 142 may involve a sequential process where adjustment components are first positioned to apply the desired force to a bearing and then locked in place to maintain the setting. The adjustment mechanism may provide fine control over the axial positioning of bearing components, allowing for precise preload or end play conditions to be achieved. In examples, the assembly 142 may simultaneously affect multiple bearings through reaction forces, providing system-wide bearing adjustment through a single mechanism.

[0041] The following detailed description of the assembly 142 components and method of operation demonstrates how the threaded adjustment and splined locking system may function to provide reliable and repeatable bearing settings. The assembly 142 may offer advantages in terms of assembly time, precision, and inventory management compared to traditional shimbased approaches for bearing adjustment in gearbox applications.

[0042] Referring to FIG. 3, the assembly 142 is shown in a partial exploded perspective view that illustrates the individual components for setting end play or preload in the gearbox 100. The shaft 110 may include external threads 144 that may be configured to engage with corresponding internal threads of an adjustment component. The shaft 110 may also include a splined portion 146 that may provide a keyed engagement surface for preventing rotational movement relative to another component that engages the splined portion 146 as described below. An annular groove 148 may be formed in the shaft 110 and may be axially interposed between the external threads 144 and the splined portion 146.

[0043] The assembly 142 may include a nut 150 that may be configured to mount to the shaft 110 and configured to operate as the adjustment component. The nut 150 may have external splines 152 that may provide a keyed engagement surface for interfacing with other components of the assembly 142. The nut 150 may also include internal threads 154 that may be configured to engage with the external threads 144 of the shaft 110. The threadedengagement between the internal threads 154 and the external threads 144 may enable axial movement of the nut 150 along the shaft 110 when the nut 150 is rotated relative to the shaft 110.

[0044] The assembly 142 further includes a sleeve 156 configured as locking mechanism for the nut 150. The sleeve 156 may include internal splines 158 that may be configured to engage with the external splines 152 of the nut 150. The internal splines 158 may also be configured to engage with the splined portion 146 of the shaft 110 when the sleeve 156 is positioned appropriately.

[0045] The sleeve 156 may further include a radial through-hole 160 that may be configured to receive a locking component. Particularly, in an example implementation, a set screw 162 may be configured to be inserted through the radial through-hole 160 for locking the sleeve 156 in position relative to the shaft 110.

[0046] The fourth tapered bearing 120 may be configured as a tapered roller bearing that may support radial and axial loads on the shaft 110. The fourth tapered bearing 120 may include an inner race 164 configured to mount to the shaft 110. The fourth tapered bearing 120 may also include rollers 166 that may be positioned between the inner race 164 and an outer race 168. The outer race 168 may be mounted within the second end cap 122 as shown. The fourth tapered bearing 120 may have a side 170 that faces the nut 150 and may be configured to interface with the nut 150 during the bearing adjustment process.

[0047] The fourth tapered bearing 120 may be mounted to the shaft 110 via a slip fit arrangement, for example. The slip fit mounting may allow the fourth tapered bearing 120 to be positioned on the shaft 110 without requiring press-fit tolerances, which may facilitate assembly and adjustment of the bearing preload or end play. However, in other examples, a transition or press fit may be used for the bearings.

[0048] Referring to FIG. 4. the assembly 142 is illustrated in a partially assembled state that shows the initial configuration for the bearing adjustment process. The nut 150 may be mounted to the shaft 110 such that the internal threads 154 of the nut 150 engage with theexternal threads 144 of the shaft 110. The threaded engagement may enable controlled axial movement of the nut 150 along the shaft 110 when the nut 150 is rotated.

[0049] The sleeve 156 may be positioned over the nut 150 such that the internal splines 158 of the sleeve 156 engage with the external splines 152 of the nut 150. In this example, the sleeve 156 may be configured to slide axially relative to the nut 150 while maintaining the splined engagement. The splined connection between the sleeve 156 and the nut 150 may allow the sleeve 156 to rotate together with the nut 150 while permitting relative axial movement therebetween.

[0050] The fourth tapered bearing 120 may be mounted to the shaft 110 with the side 170 and the inner race 164 positioned adjacent to and interfacing with the nut 150. The outer race 168 may be supported by the second end cap 122, providing a reaction surface for the bearing preload forces that may be applied during the adjustment process.

[0051] The bearing adjustment process may involve applying rotational force via the sleeve 156 to the nut 150 to achieve the desired preload or end play condition. An arrow 200 may indicate the rotational direction for applying torque via the sleeve 156 to the nut 150. When torque is applied to the nut 150 in the direction indicated by the arrow 200, the threaded engagement between the nut 150 and the shaft 110 may cause the nut 150 to move axially along the shaft 110.

[0052] An arrow 202 shown in FIG. 4 indicates a first axial direction of movement of the nut 150 toward the fourth tapered bearing 120 when the sleeve 156 rotates the nut 150 in the direction indicated by the arrow 200. This axial movement of the nut 150 in the direction of the arrow 202 may bring the nut 150 into contact with the inner race 164 of the fourth tapered bearing 120. Continued rotation and axial movement of the nut 150 may cause the nut 150 to apply increasing force against the inner race 164, thereby generating a preload force that acts through the fourth tapered bearing 120 against the outer race 168.

[0053] The force application process may enable precise control over the bearing preload or end play condition. In some examples, the nut 150 may be rotated until a specific force isapplied to the inner race 164. thereby setting a desired preload against the outer race 168 of the fourth tapered bearing 120. The threaded engagement may provide fine control over the axial positioning of the nut 150. allowing for precise adjustment of the bearing forces.

[0054] In an example, the precision of the bearing adjustment mechanism may be determined by the geometric parameters of the threaded and splined components. In some examples, the resolution of the adjustment system may be calculated based on the number of teeth in the splines and the pitch of the threads. For instance, with 16 teeth on the spline and 32 threads per inch on the external threads 144 of the shaft 110, the system may provide a resolution of approximately 2 thousandths of an inch per spline position.

[0055] The resolution calculation may be based on the relationship between thread pitch and spline tooth count. As an example for illustration, with 32 threads per inch, each full rotation of the nut 150 may produce an axial movement of approximately 31 thousandths of an inch (1 inch divided by 32 threads). With 16 spline teeth, each spline position may represent 1 / 16th of a full rotation, resulting in an axial movement of approximately 2 thousandths of an inch per spline position (31 thousandths divided by 1 positions).

[0056] Thus, the resolution of the adjustment mechanism may be related to the number of spline teeth and thread pitch. Increasing the number of spline teeth may provide finer resolution for the bearing adjustment, while decreasing the number of spline teeth may result in coarser adjustment increments. In some examples, using 32 spline teeth instead of 16 may enhance the resolution to approximately 1 thousandth of an inch per spline position, providing even more precise control over the bearing preload or end play setting.

[0057] In FIG. 4, an arrow 204 may indicate a second axial direction that is opposite to the first axial direction indicated by the arrow 202. The arrow 204 may represent the subsequent direction for movement of the sleeve 156 during the locking phase of the adjustment process. After the desired preload or end play condition has been achieved through rotation and axial movement of the nut 150, the sleeve 156 may be moved in the direction indicated by the arrow 204 to engage with the splined portion 146 of the shaft 110, thereby locking the nut 150 in position and maintaining the established bearing setting.

[0058] Referring to FIG. 5, the assembly 142 is illustrated in a partially assembled state showing the sleeve 156 engaged with the splined portion 146 of the shaft 110. The sleeve 156 may be positioned such that the sleeve 156 has been moved axially in the direction indicated by the arrow 204 from the configuration show n in FIG. 4. This axial movement of the sleeve 156 may result in a dual engagement configuration that provides locking functionality for the bearing adjustment mechanism.

[0059] Particularly, in the configuration shown in FIG. 5. a first portion of the internal splines 158 of the sleeve 156 may engage with the splined portion 146 of the shaft 110. Simultaneously, a second portion of the internal splines 158 may remain engaged with the external splines 152 of the nut 150. This dual engagement configuration may create a mechanical connect on that spans between the shaft 110 and the nut 150 through the sleeve 156.

[0060] The dual engagement of the sleeve 156 may prevent relative rotation between the nut 150 and the shaft 110. In some examples, the splined engagement between the first portion of the internal splines 158 and the splined portion 146 may rotationally lock the sleeve 156 to the shaft 110. The continued engagement between the second portion of the internal splines 158 and the external splines 152 may rotationally lock the sleeve 156 to the nut 150. The combination of these two splined connections may effectively prevent the nut 150 from rotating relative to the shaft 110.

[0061] The prevention of relative rotation between the nut 150 and the shaft 110 may maintain the axial position of the nut 150 that has been established during the bearing adjustment process. The threaded engagement between the internal threads 154 of the nut 150 and the external threads 144 of the shaft 110 may be prevented from changing due to the rotational locking provided by the sleeve 156. This rotational locking may preserve the force applied by the nut 150 against the inner race 164 of the fourth tapered bearing 120.

[0062] Thus, maintaining the position of the nut 150 may preserve the preload or end play condition that has been set during the adjustment process described with reference to FIG. 4. As such, the force applied by the nut 150 against the inner race 164 may continue to generatethe desired preload against the outer race 168 of the fourth tapered bearing 120. The dual engagement configuration of the sleeve 156 may provide a reliable locking mechanism that maintains the bearing setting without requiring additional adjustment or monitoring.

[0063] The sleeve 156 configuration shown in FIG. 5 may represent an intermediate stage in the assembly process where the bearing adjustment has been completed and the locking mechanism has been engaged. Subsequently, the position of the sleeve 156 is secured relative to the shaft 110.

[0064] Referring to FIG. 6, the assembly 142 is illustrated in a fully assembled and locked state that represents the final configuration of the bearing preload adjustment mechanism. After the sleeve 156 is positioned to engage both the nut 150 and the splined portion 146 of the shaft 110, maintaining the dual engagement configuration described with reference to FIG. 5, the set screw 162 may then be inserted through the radial through-hole 160 of the sleeve 156 to engage wi th the annular groove 148 formed in the shaft 110.

[0065] The engagement of the set screw 162 with the annular groove 148 may provide a positive locking mechanism that secures the sleeve 156 in position relative to the shaft 110. The set screw 162 may be threaded into the radial through-hole 160 until the set screw 162 extends into the annular groove 148, creating a mechanical interference that prevents axial movement of the sleeve 156 along the shaft 110. This locking arrangement may ensure that the sleeve 156 cannot shift from the position established during the bearing adjustment process.

[0066] The locked configuration shown in FIG. 6 may prevent any alteration of the preload or end play setting that has been established for the fourth tapered bearing 120. Particularly, the combination of the dual splined engagement of the sleeve 156 and the positive locking provided by the set screw 162 may create a secure mechanism that maintains the bearing adjustment under operating conditions. The set screw 162 may prevent the sleeve 156 from moving axially, which in turn may maintain the rotational locking between the nut 150 and the shaft 110.

[0067] In some examples, alternative locking mechanisms may be employed to secure the sleeve 156 in position relative to the shaft 110. For example, a snap ring or retaining ring may be positioned in the annular groove 148 to provide axial retention of the sleeve 156. The snap ring may be compressed and inserted into the annular groove 148 after the sleeve 156 has been positioned, thereby creating a mechanical stop that prevents axial movement of the sleeve 156.

[0068] In other examples, a lock washer and bolt arrangement may be used to secure the sleeve 156. The bolt may extend through a hole in the sleeve 156 and thread into a corresponding threaded hole in the shaft 110, with the lock washer positioned between the bolt head and the sleeve 156 to prevent loosening under vibration or operational loads.

[0069] In another example, a pin or dowel may be inserted through aligned holes in both the sleeve 156 and the shaft 110 to provide positive positioning. The pin may be press-fit or may include a head that prevents the pin from passing completely through the aligned holes, thereby maintaining the axial position of the sleeve 156 relative to the shaft 110.

[0070] In further examples, a clamp mechanism may be integrated into the sleeve 156. The sleeve 156 may include a split configuration with a clamping feature that allows the sleeve 156 to be tightened around the shaft 110. A bolt or fastener may be used to close the split and generate clamping force that creates friction between the sleeve 156 and the shaft 110, thereby preventing relative movement.

[0071] In some implementations, an adhesive or thread-locking compound may be applied to the interface between the sleeve 156 and the shaft 110. The adhesive may cure to create a bond that resists relative movement between the components while still allowing for disassembly if adjustment or maintenance is required.

[0072] In other examples, a wedge or tapered locking element may be positioned between the sleeve 156 and the shaft 110. The wedge may be driven into position to create an interference fit that prevents axial movement of the sleeve 156. The wedge may be removable to allow for future adjustment of the bearing preload or end play setting.

[0073] In another example, a spring-loaded detent mechanism may be incorporated into the sleeve 156. The detent may engage with features on the shaft 110, such as grooves or dimples, to provide positive positioning of the sleeve 156. The spring force may maintain engagement of the detent while allowing for intentional repositioning when sufficient force is applied.

[0074] Regardless of the type of locking mechanisms, the prevention of sleeve movement may ensure that the nut 150 remains in the axial position where the desired force is applied against the inner race 164 of the fourth tapered bearing 120. Any change in the position of the nut 150 could alter the preload or end play condition, but the locked configuration may prevent such changes from occurring during operation of the gearbox 100. The locking mechanism may provide long-term stability for the bearing adjustment without requiring periodic readjustment or maintenance.

[0075] Notably, the force applied by the nut 150 to the fourth tapered bearing 120 against the second end cap 122 may generate reaction forces that propagate through the shaft 110 to affect other bearings in the gearbox 100. Particularly, when the nut 150 applies an axial force against the fourth tapered bearing 120, the shaft 110 may experience an equal and opposite reaction force that acts in the direction away from the fourth tapered bearing 120. This reaction force may be transmitted through the shaft 110 to the shoulder 115 (see FIGs. 1-2).

[0076] Referring back to FIGs. 1-2, the shoulder 115 of the shaft 110 may apply a force against the first tapered bearing 112 in response to the reaction force generated by the adjustment of the fourth tapered bearing 120. It should be understood that a shoulder is used herein as an example. In some examples, instead of a shoulder, other features or components such as snap rings or spacers mounted to the shaft 110 to interface with the bearings can be used. The force applied by the shoulder 115 may act on the inner race of the first tapered bearing 112, which in turn may transmit the force to the outer race of the first tapered bearing 112. The first tapered bearing 112 may be positioned in a back-to-back configuration with the second tapered bearing 114, and the force transmitted through the first tapered bearing 112 may affect the loading condition of the second tapered bearing 114. The force propagation throughthe bearing assembly may continue from the second tapered bearing 114 to the third tapered bearing 116.

[0077] Such simultaneous adjustment of multiple bearings may occur because the axial force applied by the nut 150 creates a force chain through the shaft 110 and the bearing assemblies. In some examples, tightening the nut 150 to increase the preload on the fourth tapered bearing 120 may simultaneously increase the preload on the first tapered bearing 112, the second tapered bearing 114, and the third tapered bearing 116 through the reaction forces acting on the shaft 110. The force distribution may depend on the stiffness characteristics of the shaft 110, the bearing configurations, and the housing components.

[0078] The ability to simultaneously adjust multiple bearings through a single adjustment mechanism may provide advantages in assembly efficiency and bearing performance. In some examples, the system may eliminate the need to individually set each bearing in the gearbox 100, as the adjustment of the nut 150 may establish appropriate preload or end play conditions for all bearings through the force transmission path. The simultaneous adjustment may also help ensure that the bearings operate in a coordinated manner, with consistent loading conditions that may contribute to balanced performance across the bearing system.

[0079] Referring to FIG. 7. a method 700 for setting bearing preload or end play in a gearbox assembly is illustrated. The method 700 may provide a systematic approach for adjusting bearing settings without requiring shims or trial-and-error techniques. The method 700 may be performed during assembly of the gearbox 100 or during maintenance procedures where bearing adjustment is required.

[0080] At block 702, the method 700 may include threading the nut 150 onto the shaft 110 such that internal threads 154 of the nut 150 engage with external threads 144 of the shaft 110. The threaded engagement may enable controlled axial movement of the nut 150 along the shaft 110 when the nut 150 is rotated.

[0081] At block 704, the method 700 may include positioning the sleeve 156 over the nut 150 such that internal splines 158 of the sleeve 156 engage with external splines 152 of the nut150. The splined engagement may allow the sleeve 156 to rotate together with the nut 150 while permitting relative axial movement between the sleeve 156 and the nut 150.

[0082] At block 706, the method 700 may include mounting the fourth tapered bearing 120 to the shaft 110. In some examples, the fourth tapered bearing 120 may be mounted to the shaft 110 via a slip fit arrangement. The inner race 164 of the fourth tapered bearing 120 may be positioned on the shaft 110 adjacent to the nut 150, while the outer race 168 may be supported by a housing component such as the second end cap 122. The slip fit mounting may allow the bearing to be positioned without requiring press-fit tolerances. However, in other examples, a transition or press fit.

[0083] At block 708, the method 700 may include rotating the nut 150 via the sleeve 156 to move the nut 150 axially toward the fourth tapered bearing 120 and apply force thereto. Rotational force may be applied to the sleeve 156, which in turn rotates the nut 150 due to the splined engagement therebetween. The rotation of the nut 150 may cause the nut 150 to move axially along the shaft 110 due to the threaded engagement. The axial movement may bring the nut 150 into contact with the inner race 1 4 of the fourth tapered bearing 120, and continued rotation may cause the nut 150 to apply increasing force against the inner race 164 to achieve a desired preload or end play condition.

[0084] At block 710, the method 700 may include sliding the sleeve 156 axially to engage the splined portion 146 of the shaft 110. After the desired preload or end play condition has been achieved, the sleeve 156 may be moved axially along the shaft 110 while maintaining the splined engagement with the nut 150. The axial movement of the sleeve 156 may bring a portion of the internal splines 158 into engagement with the splined portion 146 of the shaft 110, creating a dual engagement configuration where the sleeve 156 simultaneously engages both the nut 150 and the shaft 110.

[0085] At block 712, the method 700 may include locking the sleeve 156 in position relative to the shaft 110 to prevent axial movement of the sleeve 156 and maintain the bearing adjustment under operating conditions. In some examples, this may be accomplished by inserting the set screw 162 through the radial through-hole 160 of the sleeve 156 and threadingthe set screw 162 until it extends into the annular groove 148 formed in the shaft 110. The engagement of the set screw 162 with the annular groove 148 in the shaft 110 may provide a positive locking mechanism that secures the sleeve 156 in its adjusted position.

[0086] The method 700 may provide several advantages over traditional shimming approaches. In some cases, the method 700 may reduce assembly time by eliminating the need to select and test various shim thicknesses. The continuous adjustment capability provided by the threaded engagement may allow for more precise bearing settings compared to discrete shim-based increments. The method 700 may also reduce inventory requirements by eliminating the need to stock multiple shim thicknesses for different tolerance combinations.

[0087] In some examples, the method 700 may be applied to adjust multiple bearings simultaneously. The force applied to the fourth tapered bearing 120 through the nut 150 may generate reaction forces that act on the shaft 110, thereby affecting the preload or end play conditions of other bearings mounted on the shaft 110, such as the first tapered bearing 112, the second tapered bearing 114, and the third tapered bearing 116. This simultaneous adjustment capability may further reduce assembly time and complexity in multi-bearing assemblies.

[0088] Referring to FIG. 8, a method 800 for simultaneous multi-bearing adjustment in a gearbox assembly is illustrated. The method 800 may provide a systematic approach for adjusting multiple bearings through a single adjustment mechanism by utilizing force transmission through a shaft. The method 800 may be particularly applicable to gearbox assemblies where multiple tapered bearings support a common shaft and where coordinated bearing adjustment is desired.

[0089] At block 802, the method 800 may include mounting multiple tapered bearings on a shaft. The bearings may be positioned at various locations along the shaft to support radial and axial loads. In some examples, the bearings may include a first tapered bearing and a second tapered bearing in a back-to-back configuration, a third tapered bearing at one end of the shaft, and a fourth tapered bearing at an opposite end of the shaft.

[0090] At block 804, the method 800 may include threading an adjustment nut onto the shaft. The nut may have internal threads that engage with external threads formed on the shaft, enabling controlled axial movement of the nut when rotated. The nut may be positioned adjacent to one of the tapered bearings, which may serve as the primary' bearing for the adjustment mechanism.

[0091] At block 806, the method 800 may include applying force to a primary bearing through the adjustment mechanism. The nut may be rotated to move axially along the shaft until the nut contacts the inner race of the primary bearing. Continued rotation may cause the nut to apply increasing force against the inner race, thereby generating a preload force that acts through the primary' bearing against its outer race.

[0092] At block 808, the method 800 may include generating reaction forces through the shaft as a result of the force applied to the primary' bearing. When the nut applies an axial force against the primary bearing, the shaft may experience an equal and opposite reaction force that acts in the direction away from the primary' bearing. This reaction force may be transmitted through the shaft to other bearing locations.

[0093] At block 810, the method 800 may include simultaneously adjusting the remaining bearings through the transmitted reaction forces. The reaction force propagating through the shaft may act on features such as shoulders or steps that interface with other bearings in the assembly. In some examples, a shoulder on the shaft may apply force against a first tapered bearing, which in turn may affect the loading condition of a second tapered bearing in a back-to-back configuration, and the force propagation may continue to additional bearings along the shaft. In some examples, instead of a shoulder, other features or components such as snap rings or spacers mounted to the shaft to interface with the bearings can be used.

[0094] At block 812, the method 800 may include locking the adjustment mechanism in position to maintain the established bearing settings. A sleeve may be positioned to engage both the nut and a splined portion of the shaft, creating a rotational lock that prevents the nut from changing position. A locking element such as a set screw may be inserted to secure the sleeve in position relative to the shaft.

[0095] The method 800 may provide advantages in assembly efficiency by eliminating the need to individually adjust each bearing in a multi-bearing assembly. In some cases, the simultaneous adjustment capability may reduce assembly time and may help ensure consistent loading conditions across all bearings in the system. The force transmission approach may also contribute to balanced bearing performance during operation of the gearbox.

[0096] The disclosed bearing preload adjustment assembly and method may provide numerous benefits and advantages over conventional shim-based approaches for setting bearing preload or end play in gearbox applications. The elimination of shim-based trial-and-error approaches may significantly reduce assembly time and complexity. Traditional methods may require multiple iterations of shim selection, installation, measurement, and replacement to achieve proper bearing settings. The disclosed threaded adjustment mechanism may enable direct setting of bearing preload or end play without the need for discrete shim components, thereby streamlining the assembly process and reducing the potential for assembly errors.

[0097] The simultaneous adjustment capability of multiple bearings through a single adjustment mechanism may provide substantial efficiency gains in multi-bearing assemblies. Rather than requiring individual adjustment of each bearing, the disclosed system may utilize reaction forces transmitted through the shaft to establish appropriate preload or end play conditions across multiple bearings simultaneously. This coordinated adjustment approach may ensure consistent loading conditions throughout the bearing system while reducing the number of adjustment operations required during assembly.

[0098] The adjustable precision of the bearing adjustment mechanism may be tailored to specific application requirements through selection of spline and thread parameters. The resolution of the adjustment system may be determined by the relationship between the number of spline teeth and the thread pitch, allowing for customization of the adjustment increment based on the precision requirements of the particular gearbox application. Applications requiring finer adjustment resolution may utilize configurations with increased spline tooth counts or finer thread pitches, while applications with less stringent precision requirements may utilize coarser configurations that may provide faster adjustment capability.

[0099] The flexibility to set either end play or preload conditions may make the disclosed system suitable for a wide range of gearbox applications with varying bearing performance requirements. Some applications may benefit from a near-zero end play condition that minimizes axial movement while avoiding excessive bearing loading, while other applications may require specific preload forces to optimize bearing stiffness and performance under high-load conditions. The continuous adjustment capability of the threaded mechanism may enable precise achievement of either condition without the discrete limitations inherent in shim-based systems.

[0100] Manufacturing efficiency and consistency may be enhanced through the elimination of shim inventory requirements and the reduction of assembly variability'. Traditional shim-based approaches may require stocking multiple shim thicknesses to accommodate various tolerance combinations, creating inventory management challenges and potential supply chain disruptions. The disclosed adjustment mechanism may eliminate these inventory requirements while providing more consistent bearing settings across production units. The direct adjustment capability' may also reduce the skill level required for assembly operations, as the adjustment process may be more straightforward and less dependent on technician experience compared to shim selection and measurement procedures.

[0101] The locking mechanism may provide long-term stability of the bearing adjustment under operating conditions. Once the desired preload or end play condition has been established and the locking mechanism engaged, the bearing setting may be maintained without requiring periodic readjustment or monitoring. This stability may contribute to consistent gearbox performance throughout the operational life of the equipment and may reduce maintenance requirements compared to systems where bearing settings may drift over time.

[0102] Quality control and repeatability may be improved through the use of standardized adjustment procedures that do not depend on the availability' of specific shim combinations. The threaded adjustment mechanism may enable consistent bearing settings across production units regardless of individual component tolerance variations. This consistency may contributeto more predictable gearbox performance characteristics and may reduce the potential for field failures related to improper bearing adjustment.

[0103] The disclosed system may also provide advantages in terms of serviceability and maintenance. In applications where bearing adjustment may be required during the operational life of the gearbox, the threaded adjustment mechanism may enable field adjustment without requiring disassembly of the entire gearbox or the procurement of specific shim combinations. This serviceability may reduce maintenance costs and equipment downtime compared to traditional approaches that may require more extensive disassembly and parts replacement procedures.

[0104] The detailed description above describes various features and operations of the disclosed systems with reference to the accompanying figures. The illustrative implementations described herein are not meant to be limiting. Certain aspects of the disclosed systems can be arranged and combined in a wide variety of different configurations, all of which are contemplated herein.

[0105] Further, unless context suggests otherwise, the features illustrated in each of the figures may be used in combination with one another. Thus, the figures should be generally viewed as component aspects of one or more overall implementations, with the understanding that not all illustrated features are necessary for each implementation.

[0106] Additionally, any enumeration of elements, blocks, or steps in this specification or the claims is for purposes of clarity. Thus, such enumeration should not be interpreted to require or imply that these elements, blocks, or steps adhere to a particular arrangement or are carried out in a particular order.

[0107] Further, devices or systems may be used or configured to perform functions presented in the figures. In some instances, components of the devices and / or systems may be configured to perform the functions such that the components are actually configured and structured (with hardware and / or software) to enable such performance. In other examples,components of the devices and / or systems may be arranged to be adapted to. capable of, or suited for performing the functions, such as when operated in a specific manner.

[0108] By the term “substantially” or “about” it is meant that the recited characteristic, parameter, or value need not be achieved exactly, but that deviations or variations, including for example, tolerances, measurement error, measurement accuracy limitations and other factors known to those with skill in the art, may occur in amounts that do not preclude the effect the characteristic was intended to provide.

[0109] The arrangements described herein are for purposes of example only. As such, those skilled in the art will appreciate that other arrangements and other elements (e.g., machines, interfaces, operations, orders, and groupings of operations, etc.) can be used instead, and some elements may be omitted altogether according to the desired results. Further, many of the elements that are described are functional entities that may be implemented as discrete or distributed components or in conjunction with other components, in any suitable combination and location.

[0110] While various aspects and implementations have been disclosed herein, other aspects and implementations will be apparent to those skilled in the art. The various aspects and implementations disclosed herein are for purposes of illustration and are not intended to be limiting, with the true scope being indicated by the following claims, along with the full scope of equivalents to which such claims are entitled. Also, the terminology used herein is for the purpose of describing particular implementations only, and is not intended to be limiting.

[0111] Embodiments of the present disclosure can thus relate to one of the enumerated example embodiments (EEEs) listed below.

[0112] EEE 1. An assembly, comprising: a shaft having external threads and a splined portion; a nut having internal threads configured to engage the external threads of the shaft and external splines, wherein the nut is configured to move axially along the shaft when rotated; atapered bearing mounted to the shaft and having an inner race and an outer race, wherein the nut is configured to apply force against the inner race when moved axially toward the tapered bearing; and a sleeve having internal splines configured to engage both the external splines of the nut and the splined portion of the shaft to prevent relative rotation between the nut and the shaft.

[0113] EEE 2. The assembly of EEE 1, wherein the shaft further comprises an annular groove positioned between the external threads and the splined portion.

[0114] EEE 3. The assembly of EEE 1 or EEE 2, wherein the sleeve further comprises a radial through-hole configured to receive a locking element.

[0115] EEE 4. The assembly of EEE 3, wherein the locking element comprises a set screw configured to be inserted through the radial through-hole and engage the annular groove to lock the sleeve in position relative to the shaft.

[0116] EEE 5. The assembly of any one of EEEs 1-4, wherein the tapered bearing is mounted to the shaft via a slip fit arrangement that facilitates assembly and adjustment of bearing preload or end play.

[0117] EEE 6. The assembly of any one of EEEs 1-5, wherein the sleeve is configured to slide axially relative to the nut while maintaining engagement with the external splines of the nut.

[0118] EEE 7. The assembly of EEE 6, wherein a first portion of the internal splines of the sleeve is configured to engage the splined portion of the shaft and a second portion of the internal splines of the sleeve is configured to remain engaged with the external splines of the nut.

[0119] EEE 8. The assembly of any one of EEEs 1-7, wherein the nut is configured to apply a preload force against the inner race of the tapered bearing when moved axially toward the tapered bearing.

[0120] EEE 9. The assembly of any one of EEEs 1 -8, wherein the shaft supports a plurality of tapered bearings, and wherein axial movement of the nut generates a reaction force through the shaft that simultaneously adjusts preload conditions of the plurality of tapered bearings.

[0121] EEE 10. The assembly of EEE 9, wherein the shaft comprises a shoulder configured to interface with at least one of the plurality of tapered bearings to transmit the reaction force.

[0122] EEE 11. A method for operating the assembly of any one of EEEs 1-10 for setting bearing preload. For example, the method comprises: mounting a nut having internal threads to a shaft having external threads such that the internal threads engage the external threads; mounting a sleeve to the nut such that the sleeve is configured to slide axially relative to the nut; mounting a tapered bearing to the shaft, wherein the tapered bearing has an inner race and an outer race; moving the nut axially toward the inner race of the tapered bearing until the nut applies a force on the inner race, thereby setting a preload against the outer race; sliding the sleeve axially relative to the nut until the sleeve engages the shaft while remaining engaged with the nut, thereby preventing relative rotation between the nut and the shaft; and locking the sleeve in position relative to the shaft.

[0123] EEE 12. The method of EEE 11, wherein moving the nut axially toward the inner race comprises rotating the nut about the shaft, causing the nut to move axially due to engagement of the internal threads with the external threads.

[0124] EEE 13. The method of EEE 11 or EEE 12, wherein the nut has external splines and the sleeve has internal splines, and wherein mounting the sleeve to the nut comprises engaging the internal splines of the sleeve with the external splines of the nut.

[0125] EEE 14. The method of EEE 13, wherein the shaft has a splined portion, and wherein sliding the sleeve axially relative to the nut comprises sliding the sleeve until a first portion of the internal splines of the sleeve engages the splined portion of the shaft while a second portion of the internal splines of the sleeve remains engaged with the external splines of the nut.

[0126] EEE 15. The method of any one of EEEs 11-14, wherein moving the nut axially toward the inner race comprises moving the nut in a first axial direction, and wherein sliding the sleeve axially relative to the nut comprises sliding the sleeve in a second axial direction opposite the first axial direction.

[0127] EEE 16. The method of any one of EEEs 11-15, wherein the shaft has an annular groove and the sleeve has a radial through-hole, and wherein locking the sleeve in positioncomprises inserting a set screw through the radial through-hole until the set screw engages the annular groove.

[0128] EEE 17. The method of EEE 16. wherein the annular groove is positioned between the external threads and a splined portion of the shaft.

[0129] EEE 18. The method of any one of EEEs 11-17, wherein the shaft supports a plurality of tapered bearings, and wherein moving the nut axially generates a reaction force through the shaft that simultaneously adjusts preload conditions of the plurality of tapered bearings.

[0130] EEE 19. The method of EEE 18, wherein the reaction force is transmitted through a shoulder of the shaft that interfaces with at least one of the plurality of tapered bearings.

[0131] EEE 20. The method of any one of EEEs 11-19, wherein mounting the tapered bearing to the shaft comprises mounting the tapered bearing via a slip fit, a transition fit, or a press fit arrangement.

[0132] EEE 21. An assembly, comprising: a shaft having external threads; a nut having internal threads configured to engage the external threads of the shaft, wherein the nut is configured to move axially along the shaft when rotated; a tapered bearing mounted to the shaft and having an inner race and an outer race, wherein the nut is configured to apply force against the inner race when moved axially toward the tapered bearing; and a sleeve configured to lock the nut in position relative to the shaft to prevent relative rotation between the nut and the shaft.

[0133] EEE 22. The assembly of EEE 21, wherein the sleeve is configured to engage the nut and subsequently engage the shaft to prevent relative rotation between the nut and the shaft.

[0134] EEE 23. The assembly of EEE 21 or EEE 22, wherein the sleeve comprises internal splines and the nut comprises external splines, and wherein the internal splines of the sleeve are configured to engage the external splines of the nut.

[0135] EEE 24. The assembly of any one of EEEs 21-23, wherein the shaft comprises a splined portion, and wherein the sleeve is configured to engage the splined portion of the shaft.

[0136] EEE 25. The assembly of any one of EEEs 21-24, wherein the sleeve is configured to slide axially relative to the nut.

[0137] EEE 26. The assembly of any one of EEEs 21-25, wherein the shaft further comprises an annular groove, and wherein the sleeve comprises a radial through-hole configured to receive a locking element that engages the annular groove.

[0138] EEE 27. The assembly of EEE 26, wherein the locking element comprises a set screw, a snap ring, a pin, or a bolt.

[0139] EEE 28. The assembly of any one of EEEs 21-27, wherein the tapered bearing is mounted to the shaft via a slip fit, a transition fit, or press fit arrangement.

[0140] EEE 29. The assembly of any one of EEEs 21-28, wherein the shaft supports a plurality of tapered bearings, and wherein axial movement of the nut generates a reaction force through the shaft that simultaneously adjusts preload conditions of the plurality of tapered bearings.

[0141] EEE 30. The assembly of EEE 29, wherein the shaft comprises a shoulder configured to interface with at least one of the plurality of tapered bearings to transmit the reaction force.

Claims

CLAIMS1. An assembly, comprising:a shaft having external threads and a splined portion;a nut having internal threads configured to engage the external threads of the shaft and external splines, wherein the nut is configured to move axially along the shaft when rotated;a tapered bearing mounted to the shaft and having an inner race and an outer race, wherein the nut is configured to apply force against the inner race when moved axially toward the tapered bearing; anda sleeve having internal splines configured to engage both the external splines of the nut and the splined portion of the shaft to prevent relative rotation between the nut and the shaft.

2. The assembly of claim 1 , wherein the shaft further comprises an annular groove positioned between the external threads and the splined portion.

3. The assembly of claim 2, wherein the sleeve further comprises a radial through-hole configured to receive a locking element.

4. The assembly of claim 3, wherein the locking element comprises a set screw configured to be inserted through the radial through-hole and engage the annular groove to lock the sleeve in position relative to the shaft.

5. The assembly of claim 1, wherein the tapered bearing is mounted to the shaft via a slip fit arrangement that facilitates assembly and adjustment of bearing preload or end Play.

6. The assembly of claim 1. wherein the sleeve is configured to slide axially relative to the nut while maintaining engagement with the external splines of the nut.

7. The assembly of claim 6, wherein a first portion of the internal splines of the sleeve is configured to engage the splined portion of the shaft and a second portion of the internal splines of the sleeve is configured to remain engaged with the external splines of the nut.

8. The assembly of claim 1, wherein the nut is configured to apply a preload force against the inner race of the tapered bearing when moved axially toward the tapered bearing.

9. The assembly of claim 1, wherein the shaft supports a plurality of tapered bearings, and wherein axial movement of the nut generates a reaction force through the shaft that simultaneously adjusts preload conditions of the plurality of tapered bearings.

10. The assembly of claim 9. wherein the shaft comprises a shoulder configured to interface with at least one of the plurality of tapered bearings to transmit the reaction force.

11. A method for setting bearing preload, the method comprising: mounting a nut having internal threads to a shaft having external threads such that the internal threads engage the external threads;mounting a sleeve to the nut such that the sleeve is configured to slide axially relative to the nut;mounting a tapered bearing to the shaft, wherein the tapered bearing has an inner race and an outer race;moving the nut axially toward the inner race of the tapered bearing until the nut applies a force on the inner race, thereby setting a preload against the outer race;sliding the sleeve axially relative to the nut until the sleeve engages the shaft while remaining engaged with the nut. thereby preventing relative rotation between the nut and the shaft; andlocking the sleeve in position relative to the shaft.

12. The method of claim 11, wherein moving the nut axially toward the inner race comprises rotating the nut about the shaft, causing the nut to move axially due to engagement of the internal threads with the external threads.

13. The method of claim 11 , wherein the nut has external splines and the sleeve has internal splines, and wherein mounting the sleeve to the nut comprises engaging the internal splines of the sleeve with the external splines of the nut.

14. The method of claim 13, wherein the shaft has a splined portion, and wherein sliding the sleeve axially relative to the nut comprises sliding the sleeve until a first portion of the internal splines of the sleeve engages the splined portion of the shaft while a second portion of the internal splines of the sleeve remains engaged with the external splines of the nut.

15. The method of claim 11, wherein moving the nut axially toward the inner race comprises moving the nut in a first axial direction, and wherein sliding the sleeve axially relative to the nut comprises sliding the sleeve in a second axial direction opposite the first axial direction.

16. The method of claim 11 , wherein the shaft has an annular groove and the sleeve has a radial through-hole, and wherein locking the sleeve in position comprises inserting a set screw through the radial through-hole until the set screw engages the annular groove.

17. The method of claim 16, wherein the annular groove is positioned between the external threads and a splined portion of the shaft.

18. The method of claim 11, wherein the shaft supports a plurality of tapered bearings, and wherein moving the nut axially generates a reaction force through the shaft that simultaneously adjusts preload conditions of the plurality of tapered bearings.

19. The method of claim 18, wherein the reaction force is transmitted through a shoulder of the shaft that interfaces with at least one of the plurality of tapered bearings.

20. The method of claim 11, wherein mounting the tapered bearing to the shaft comprises mounting the tapered bearing via a slip fit, a transition fit, or a press fit arrangement.

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