Patent Publication Number: US-2016236511-A1

Title: Extended length bearing cone system

Description:
RELATED APPLICATIONS 
     This application claims benefit of U.S. Provisional Application No. 62/116,291, filed Feb. 13, 2015, which is hereby incorporated by reference in its entirety 
    
    
     BACKGROUND 
     Wheel hubs are a vital component of wheeled vehicles as they provide the connection between the vehicle structure and the rotating wheel. The wheel hub typically includes a pair of bearings that allow the free rotation of the wheel hub about a spindle extending from the vehicle structure. The bearings are placed spaced apart within the wheel hub and held in place and proper orientation by the fastening of the hub onto the spindle. 
     When mounting bearings within a wheel hub, the proper amount of tightening is required. Incorrect torque applied to the spindle nut can cause uneven loading of the bearings causing adverse wear or other potentially dangerous situations. If the nut is over torqued, an undue amount of lateral pressure may be exerted on the bearings, constraining them and causing them to overheat during use. Overheated bearings can seize and stop the wheel rotating; a wheel seizing during use can cause dangerous conditions for the user. If the nut is under torqued, the hub and bearings can move laterally along the spindle causing damage to the oil seal which, in turn, could cause loss of lubrication. In either scenario, the final outcome could be potential loss of the wheel and hub assembly due to the lateral force exerted during turning operations. Therefore, proper tightening of the nut is required for safe operation of the attached wheel. 
     To assist a user in properly loading the bearings within the wheel hub, a complicated and detailed procedure for torquing the spindle nut was developed. To further simplify this procedure, a bearing spacer was developed that helped to maintain the bearing spacing and orientation within the wheel hub, ensuring proper loading of the bearings. In order for this system to be effective and efficient, precise tolerancing and machining of portions of the wheel hub and the intervening bearing spacer are required. Such precise tolerancing and machining necessarily increases the cost of the parts as more and precise work must be performed before the system can be delivered and installed. 
     There exists a need for an improved wheel bearing spacing system that is both easy to install and reduces the overall costs and potential for machining error. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1A  is a cross-section in perspective view of a standard straight spindle bearing. 
         FIG. 1B  is a further cross-section in perspective view of the embodiment of  FIG. 1A  including a straight spindle. 
         FIG. 2  is a cross-section in perspective view of a standard straight spindle bearing utilizing a standard spacer system. 
         FIGS. 3A  is a cross-section in perspective view of a pair of bearings within a wheel hub for use with a straight spindle according to an embodiment of the invention. 
         FIG. 3B  is a further cross-section in perspective view of the embodiment of  FIG. 3A  including a straight spindle. 
         FIG. 4A  is a cross-section in perspective view of a pair of bearings within a wheel hub for use with a straight spindle according to a further embodiment of the invention. 
         FIG. 4B  is a further cross-section in perspective view of the embodiment of  FIG. 4A  including a straight spindle. 
         FIG. 5A  is a cross-section in perspective view of a pair of bearings within a wheel hub for use with a tapered spindle according to a further embodiment of the invention. 
         FIG. 5B  is a cross-section view in profile of the embodiment of  FIG. 5A . 
         FIG. 6  is a cross-section view of a pair of bearings within a wheel hub for use with a tapered spindle according to a further embodiment of the invention. 
         FIG. 7  is a cross-section view of a pair of bearings within a wheel hub for use with a tapered spindle according to a further embodiment of the invention. 
         FIG. 8  is a cross-section view of a pair of bearings within a wheel hub for use with a tapered spindle according to a further embodiment of the invention. 
     
    
    
     DETAILED DESCRIPTION 
       FIGS. 1A-1B  are cross-sections in perspective view of a standard straight spindle  101 , such as a P-spindle, wheel hub and bearing assembly. In this design, the bearings  110  and  120  are placed in inner and outer bearing recesses  104  and  106  of the hub  102 . The bearing cup  116  of the inner tapered roller bearing  110  is pressed into the bearing recess  104 . Once the bearing cup  116  is in place, the inner bearing assembly consisting of tapered rollers  114  within an inner cone  112  is inserted to complete the inner bearing  110 . The outer bearing  120  is inserted into the wheel hub  102  in a similar manner. The bearing cup  126  is pressed into the outer bearing recess  106  of the hub  102 . The inner bearing cone  122 , containing tapered rollers  124 , is then inserted in cup  126  to complete the outer bearing  120 . 
     In this system, the bearings,  110  and  120 , and the bearing spacing  108  have standard tolerances, i.e., neither the bearings nor the bearing spacing are precisely machined to tight tolerances. 
     With the bearings  110  and  120  contained in the hub  102 , a spindle (not shown) is then inserted through the hub. The spindle passes through the inner and outer bearings,  110  and  120 , with the inner bearing  110  contacting a flange or surface of the spindle and a threaded portion of the spindle extending past the outer bearing  120 . A spindle nut (not shown) is threaded onto the spindle  101  and tightened against the outer bearing  120 . The tightening of the spindle nut compresses the bearings,  110  and  120 , within the hub  102  and affixes the hub  102  to the spindle  101  for use. 
     Over or under tightening of the spindle nut can cause the bearings to overheat and/or cause the failure of the wheel hub. A precise procedure and a skilled technician are required to ensure that the hub and bearing are attached to the spindle correctly so as not to endanger the user or cause undue wear on the bearings. 
       FIG. 2  is a cross-section in perspective view of a standard P-spindle wheel hub featuring a spacer. In order to overcome the issues associated with the proper tightening of the restraining nut of the standard P-spindle hub, a spacer was developed to span between and assist with proper spacing of the bearings. As with the previous design shown in  FIGS. 1A-1B , the bearings  210  and  220  are inserted into the hub  202 . The inner bearing cup  216  is pressed into the bearing recess  204  and the inner bearing cone  212 , containing the tapered rollers  214 , is inserted within the bearing cup  216 . Before installing the outer bearing  220 , the spacer  230  is inserted into the hub  204 . The outer bearing cup  226  is pressed into the bearing recess  206  until contacting the spacer  230 , and the outer bearing cone  222 , containing the tapered rollers  224 , is inserted to complete the outer bearing  220 . 
     In the design shown in  FIG. 2 , the spacer  230  is required to be precisely sized and machined to properly space the bearings axially apart. The spacer  230  is machined to span the axial distance  208  between the two bearing lands  204  and  206  and to abut the cones  216  and  226  of the inner and outer bearings  210  and  220 . The use of a spacer to assist with maintaining proper bearing spacing and alignment within the hub  202  removes the multi-step process required to properly affix the wheel hub  202  to the spindle. 
     In order to utilize the spacer system, the separate spacer  230 , the bearings  210  and  220  and the hub  202  require precise machining, unlike the system of  FIGS. 1A-1B . The hub  202  is required to have tighter tolerances for the spacing  208  of the bearings so that precise and known dimensions can be used to properly machine the spacer  230 . Additionally, the bearings  210  and  220  also require tighter tolerancing so that they are correctly sized and mate flush with the spacer  230 . The bearings  210  and  220  are typically machined to tolerances much tighter than the tolerances of the bearings of  FIGS. 1A-1B . The same precision is also required of the spacer  230  to ensure the components integrate accurately. 
     The system of  FIG. 2  requires three components, the bearings,  210  and  220 , and the spacer  230  that must be precisely machined and assembled. The stacked nature of the components causes the tolerances to stack which leads to potentially increased error. To counteract this, each of the components individually is required to have a high degree of precision. With three components, this leads to increased costs due to the precision machining processes that are required. 
     Additionally, installing the system of  FIG. 2  requires the alignment of three components, one of which, the spacer  230 , is a free floating component between the other two, the bearings  210  and  220 . This can mean increased time to install and align the system correctly. 
       FIGS. 3A-3B  illustrate a wheel hub and bearing assembly  300  for use with a straight spindle  301 , such as an P-type trailer spindle according to an embodiment of the invention. The wheel hub  302  includes an inner bearing land  304  and an outer bearing land  306 , on which an inner bearing  310  and outer bearing  320  are respectively disposed thereon. Each bearing,  310  and  320 , includes a bearing cup  312 ,  322  which rests on or against the bearing lands  304  and  306  of the wheel hub  302 . Each of the bearings,  310  and  320 , further includes an extended bearing cone  314  and  324  disposed within the bearing cups  312  and  322 . The bearing cones  314  and  324  include inward extensions  317  and  327 , which extend axially through the wheel hub  302  and abut one another along line  309 . 
     Each bearing  310 ,  320  includes a plurality of bearing elements  316 ,  326  that are constrained to the bearing cone  314 ,  324  by a bearing cage. The bearing elements  316 ,  326  are constrained by and allowed to rotate within the bearing cage between a first bearing surface  313 ,  323  of a bearing cup  314 ,  324  and a second bearing surface  315 ,  325  of an extended bearing cone  314 ,  324 . The bearing elements  316 ,  326  reduce friction between the bearing cup  312 ,  322  and the bearing cone  314 ,  324 , allowing the bearing cups  312  and  322  and hub  302  to freely rotate about the bearing cones  314  and  324  during vehicle movement. The first bearing surface  313 ,  323  and the second bearing surface  315 ,  325  can include profiles to restrain the bearing elements  316 ,  326  in a desired location(s) between the bearing cup  312 ,  322  and the bearing cone  314 ,  324 . 
     In the embodiment of  FIGS. 3A-3B , the wheel hub  302  and bearings  310  and  320  are for use with a straight spindle  301 , such as a standard P-spindle found on a trailer. A straight spindle  301  has a constant diameter along its axial length. For use with such a spindle  301 , the bearing cones  314 ,  324  of the bearings  310  and  320  have similar or identical inner diameters and do not require a reduction or enlargement of the diameter across their axial length. 
     The bearings  310  and  320  of the embodiment shown in  FIGS. 3A-3B  are tapered roller type bearings. The bearing elements  316 ,  326  are cylindrical roller elements constrained within a radially angled groove  315 ,  325  about an outer circumference of the bearing cone  314 ,  324  by a bearing cage (not shown). The bearing cage constrains the cylindrical roller elements  316 ,  326  to the radially angled groove  315 ,  325 , allowing the cylindrical roller elements a single degree of freedom, that is rotation of each element  316 ,  326  about their own axis. The outer bearing cup  312 ,  322  include a radially angled surface  313 ,  323  paralleling the radially angled surface of the radially angled groove  315 ,  325 . 
     Tapered roller bearings are used as they can take high radial and axial loads, typical of those experienced by a wheel hub and spindle assembly. Depending on the projected levels of loading the bearing can be expected to endure, alternative bearing designs can be used. Alternative bearing designs can include ball or roller bearings, featuring an extended bearing cone. 
     The new, self-spacing bearing design can be used with a standard wheel hub and spindle assembly, such as those used with traditional wheel bearings and bearing and spacer systems. The extended bearing cones remove the requirement for a spacer, while maintaining the ease of installation. Further, the removal of the spacer element reduces the number of components that require precise machining and tolerancing required for optimal bearing installation. 
     The bearings  310  and  320  are installed in the traditional manner, with the bearing cups  316  and  326  inserted and press-fitted into the machined bearing lands  304  and  306 , respectively. The inner bearing cones  314  and  324 , containing the roller elements  316  and  326 , are inserted to complete the inner  310  and outer bearing  320 . In the embodiment of  FIGS. 3A-3B , the extended bearing cones  314  and  324  have the same length and meet at line  309  axially midway between the two bearing lands  304  and  306 . Alternatively, the pair of extended bearing cones  314  and  324  can abut at any point axially between the two bearing lands  304  and  306 . That is the length of the bearing cones  314  and  324  can be unequal, thus shifting the line  309  along which the bearing cones  314  and  324  abut to a position nearer the inner bearing  310  or outer bearing  320  (see line  409  of  FIG. 4A ). 
     The bearings  310  and  320 , and the hub  302  require precise machining for proper bearing installation and running efficiency. A critical dimension is the bearing spacing, or the axial distance  308  between the bearing lands  304  and  306 . To achieve a high degree of tolerance for the distance  308 , the bearing lands  304  and  306  themselves and the bearing cups  312  and  322  require precision machining to establish the endpoints of the axial distance  308  within a high tolerance level. Further, the extended bearing cones  314  and  324  require precision machining on their abutting surfaces such that they adjoin in a plane orthogonal to and at a desired point along the axial distance  308 . 
     Such precision machining is also inherently required within a spacer system such as that of  FIG. 2 . The spacing between the bearings requires a high degree of precision in order to properly size the intervening spacer of the system of  FIG. 2 . Additionally, the intervening spacer between the bearing pair requires precision machining to properly interface with the bearings and space them the required distance apart. As such, the system of  FIG. 2  requires an additional element and further machining which is rendered unnecessary by the new bearing spacing system, such as that of  FIGS. 3A-3B , disclosed herein. 
     The spacer system of  FIG. 2  requires more components and thus has an increased number of surface interfaces. With the high degree of precision and the tight tolerances, the number of interfaces between the elements of the system of  FIG. 2  increases the “stack-up” effect of tolerances. That is, with each interface between elements, there is a dimensional tolerance for the length of the element along the axial distance between the bearings and a further surface tolerance for flatness of the surface for proper interfacing. In the spacer system, you have the interface between each of the two bearings  210  and  220  and the intervening spacer  230 , and between each bearing  210  and  220  and the bearing lands  204  and  206 . The new system, as shown in  FIGS. 3A-3B , has fewer components and mating surfaces which creates a smaller stack up of tolerances than the system of  FIG. 2 . In the new system, you have a singular interface between the bearings and the interface between each bearing  310  and  320  and each bearing land  304  and  306 . The reduced number of elements of the new system subsequently reduces the number of critical dimensions and tolerances, thereby minimizing the stack up of tolerances and simplifying the system and the manufacturing required. 
       FIGS. 4A-4B  illustrate a wheel hub and bearing assembly  400  for use with a straight spindle  401 , such as an P-type trailer spindle according to a further embodiment of the invention. In this embodiment of the wheel hub and bearing assembly  400 , only one of the two bearings  410  and  420  includes an extended bearing cone  424 . In the example of  FIGS. 4A-4B , the extended bearing cone  424  of the outer bearing  420  extends the full axial distance  408  to abut the standard bearing cone  414  of the inner bearing  410  at line  409 . With this system of bearings, only one of the bearings  420  includes the extended bearing cone  424 , while the other bearing  410  includes a standard length bearing cone  414 . Such a bearing can include a high precision bearing like that of the system of  FIG. 2   
     The bearings  410  and  420  shown in the embodiment of  FIGS. 4A-4B  are tapered roller type bearings. The bearings  410  and  420  include bearing cups  412  and  422  configured to rest on the bearing lands  404  and  406  of the wheel hub  402 . Bearing cones  414  and  424  are disposed within the bearing cups  412  and  422  of each of the bearings  410  and  420 . Bearing elements  416  and  426  are disposed between the first bearing surfaces  413  and  423  of the bearing cups  412  and  422  and the second bearing surfaces  415  and  425  of the bearing cones  414  and  424  of the bearings  410  and  420 . 
     The first bearing surfaces  413  and  423  and second bearing surfaces  415  and  425  are radially profiled to orient the cylindrical bearing elements  416  and  426  in the tapered bearing profile. Orientation of the bearing elements  416  and  426  in this manner allows the bearings  410  and  420  to sustain large radial and axial loads. Alternative bearing elements  416  and  426  and orientations can be selected based on the expected loading the bearing will experience during use. 
     As with the previous embodiment of  FIGS. 3A-3B , a certain amount of precision machining is required in the full-length extended bearing cone system  400  of  FIGS. 4A-4B . As with the system of  FIGS. 3A-3B , the system  400  requires precise machining of the bearings  410  and  420  and the wheel hub  402 . The bearing lands  404  and  406  are precisely machined to accept and orient the inserted, precision machined bearing cups  412  and  422  and to set a defined distance for the axial spacing  408 . The extended bearing cone  424  and the standard length bearing cone  414  are machined to properly abut, or interface, one another at line  409 , with the extended bearing cone  424  also precisely machined to extend across the entire axial distance  408 . 
     Like the embodiment of  FIGS. 3A-3B , the full-length extended bearing cone system  400  of  FIGS. 4A-4B , the new system eliminates the requirement of an intervening spacer between the two bearings, simplifying the overall system and reducing costs. The full-length extended cone  424  of the bearing  420  functions as a spacer, ensuring that the bearings  410  and  420  maintain proper alignment and spacing while maintaining the simplified method and procedure for fastening the wheel hub  402  to a standard straight spindle  401 , such as a P-type trailer spindle. 
     The assembly  300  of  FIGS. 3A-3B  and assembly  400  of  FIGS. 4A-4B  are configured to be used with standard straight, parallel, or P-, spindles  301  and  401 . A parallel spindle  301 ,  401  has a constant diameter across the axial distance  308  and  408 . The example assemblies  300  and  400  can be modified and sized to fit various and different standard P-spindle designs, such as those standard designs defined by the Society of Automotive Engineers (SAE). 
       FIGS. 5A and 5B  illustrate a further embodiment of a wheel hub and bearing assembly  500  for use with a tapered spindle, such as an R-series drive spindle. In the system  500 , the larger diameter, inner bearing  510  includes a full-length extended bearing cone  514  which abuts the bearing cone  524  of the smaller diameter, outer bearing  520 , similar to the system  400  of  FIG. 4 . However, in the assembly  500 , the extended bearing cone  514  is necked  517  to decrease the diameter of extended bearing cone  514  to match the diameter of the smaller diameter, bearing cone  524  of the bearing  520 . 
     The smaller diameter, outer bearing  520  includes a bearing cup  522  which rests and is supported by the outer bearing land  506  and a standard length bearing cone  524  and bearing elements  526 . The outer bearing  520  can be a standard high-precision bearing having a smaller diameter to match the tapered profile of the spindle  501 . 
     The larger diameter, inner bearing  510  includes a bearing cup  512  disposed on the inner bearing land  508  and the full-length bearing cone  514  and bearing elements  516 . The full-length bearing cone  514  includes a neck portion  517  which reduces the diameter of the bearing cone  514  to match the diameter of the bearing cone  524  of the outer bearing  520 . The reduction in diameter at the neck portion  517  allows the extended length bearing cone  514  of the assembly  500  to be used with alternative spindle designs, such as the standard R-series drive tapered spindle  501  of  FIGS. 5A and 5B . 
     As with the previous systems, various elements of the assembly  500  require precision machining for optimal bearing performance and efficiency. That is, the bearing lands  504  and  506  require machining to align and properly space the bearing  510  and  520  an axial distance  508  apart. The inner bearing cones  514  and  524  require machining for proper abutment with the full-length inner bearing cone  514  of the bearing  510  requiring further machining to properly size the cone  514  to span the axial distance  508 . 
     The wheel hub and bearing assembly  500  of  FIGS. 5A and 5B  are configured to be used with standard, tapered drive spindles  501 , such as  200  and  200 R drive spindles, and wheel hubs  502 . The various components of the system  500  can be modified and sized to fit a variety of different standard tapered spindles as necessary or desired. 
       FIG. 6  illustrates a further embodiment of the wheel hub and bearing assembly  600  for use with a tapered spindle, such as an R-series drive spindle  601 . In the example embodiment shown, both the inner bearing  610  and outer bearing  620  include an extended bearing cone  614  and  624 , respectively. The two extended bearing cones  614  and  624  extend inward along axial distance  608  and abut along line  609 . 
     The inner bearing  610  is a tapered roller bearing that includes a bearing cup  612  that rests on an inner bearing land  604  of a wheel hub  602  and an extended length cone  614  that includes bearing elements  616 . The extended length cone  614  extends along the axially inward of the wheel hub  602  to abut an extended length bearing cone  624  of the outer bearing  620  along line  609  at a point along the axial distance  608 . A necked portion  617 , reduces a diameter of the extended length inner bearing cone  614  to match a diameter of an extended length outer bearing cone  624 . 
     The outer bearing  620  is a tapered roller bearing that includes a bearing cup  622  that rests on an outer bearing land  606  of the wheel hub  602  and an extended length cone  624  that includes bearing elements  626 . The extended length outer bearing cone  624  extends axially inward of the wheel hub  602  to abut the extended length inner bearing cone  614  of the inner bearing  610  along line  609 . 
     The diameter of the outer bearing cone  624  is smaller than the diameter of the inner bearing cone  614  to account for the tapered nature of the spindle  601 . In alternative embodiments, the extended cones  614  and  624  of the bearings  610  ad  620 , respectively, can meet at any point along axial distance  608 . As such, one or both extended length bearing cones  614  or  624  can include a necked portion  617  to alter the diameter of the bearing cone, or cones, to account for the tapered nature of the spindle  601 . 
     As with the previously discussed embodiments of  FIGS. 3-5 , the wheel hub  602  and bearings  610  and  620  of the system  600  require precision machining. Namely, the precise machining of the axial distance, or bearing land distance,  608  of the wheel hub  602  and the precision machining of the bearing cones  614 ,  624  and cups  612 ,  622 . 
       FIG. 7  illustrates a further embodiment of the wheel hub and bearing assembly  700  for use with a tapered spindle, such as an FF-series front-steer spindle  701 . In the embodiment shown, an inner bearing  710  includes an extended bearing cone  714  that extends across an axial distance  708  to abut an outer bearing cone  724  of an outer bearing  720 . The abutment of extended inner bearing cone  714  and outer bearing cone  724  maintains proper spacing between and the orientation of the inner  710  and outer bearing  720 . 
     A wheel hub  702  is configured to receive the tapered spindle  701  and includes an inner bearing land  704  and outer bearing land  706 , which are separated by the axial distance  708 . 
     The inner bearing  710  includes a bearing cup  712  that rests on the inner bearing land  704 , the extended inner bearing cone  714  and bearing elements  716  disposed therebetween. The extended inner bearing cone  714  has a first diameter that is maintained axially until a first transition  717 . At the first transition  717 , the extended inner bearing cone  714  begins to taper to a second, smaller diameter that is equal to the diameter of the outer bearing cone  724 . At a second transition  718 , the extended inner bearing cone  714  has tapered to the smaller, second diameter and abuts the outer bearing cone  724  squarely. 
     The outer bearing  710  includes a bearing cup  722  that rests on an outer bearing land  706 , the outer bearing cone  724  and bearing elements  726  disposed therebetween. Due to the tapered nature of the FF-series spindle  701 , the outer bearing  720  has a smaller diameter than that of the inner bearing  710 . As such, the outer bearing cone  724  has a second, smaller, diameter than the first diameter of the extended inner bearing cone  714 . The outer bearing cone  724  is of a standard length and does not feature an extended portion. 
     In the embodiment shown in  FIG. 7 , only the inner bearing  710  includes an extended bearing cone  714 , with the other bearing cone,  724 , being of standard length. Alternatively, both bearing cones,  714  and  724 , can be extended and abut at any point along the axial distance  708 , as desired. Further, either bearing cone  714 ,  724  can include the requisite transitions to reduce or enlarge the diameter of the bearing cone  714 ,  724  to accommodate the tapered nature of the spindle  701 . 
     As with the previously discussed embodiments of  FIGS. 3-6 , the wheel hub  702  and bearings  710  and  720  of the system  700  require precision machining. Namely, the precise machining of the axial distance, or bearing land distance,  708  of the wheel hub  702  and the precision machining of the bearing cones  714 ,  724  and cups  712 ,  722 . 
       FIG. 8  illustrates a further embodiment of the wheel hub and bearing assembly  800  for use with a tapered spindle, such as an N-type trailer spindle  801 . In the embodiment shown, the assembly  800  includes a wheel hub  802 , inner bearing  810  and outer bearing  820 . 
     The wheel hub  802  includes an inner bearing land  804  and an outer bearing land  806  that are separated an axial distance  808  apart. Due to the tapered nature of the spindle  801 , the inner bearing land  804  has a larger, first diameter than the smaller, second diameter of the outer bearing land  806 . 
     The inner bearing  810  has a first diameter and includes an inner bearing cup  812  that rests on the inner bearing land  804 , an extended inner bearing cone  814  and bearing elements  816  disposed therebetween. The extended inner bearing cone  814  has a first diameter that begins to reduce at a first transition point  817  along the axial distance  808 . At the first transition point  817 , the extended inner bearing cone  814  begins to taper to the smaller, second diameter of the outer bearing cone  824 . Once reduced to the second diameter at a second transition point  818 , the extended inner bearing cone  814  abuts, or can further extend until abutting, the outer bearing cone  824 . The abutment of the inner bearing cones  814  and  824  assists in maintaining proper bearing  810 ,  820  spacing and orientation while allowing for the use of the simplified tightening process. 
     The outer bearing  820  has a second diameter, smaller than the first diameter, and includes an outer bearing cup  822  that rests on the outer bearing land  806 , the outer bearing cone  824  and bearing elements  826  disposed therebetween. In alternative embodiments, the outer bearing  820  can include an extended outer bearing cone  824  that extends to a point, or fully, along the axial distance  808  to abut the inner bearing cone  812 . 
     As with the previously discussed embodiments of  FIGS. 3-7 , the wheel hub  802  and bearings  810  and  820  of the system  800  require precision machining. Namely, the precise machining of the axial distance, or bearing land distance,  808  of the wheel hub  802  and the precision machining of the bearing cones  814 ,  824  and cups  812 ,  822 . 
     A further benefit of the systems shown in  FIGS. 3-8 , and described herein, is that they can be used with standard spindle designs, such as the P- and N-type spindles for trailers and the R-series driven spindles and the FF-series front-steer spindles used in trucks. As such, the system of an extended bearing cone or cones can be retrofitted into existing wheel hub and spindle systems without modification of the existing components. As a further benefit, bearing life and performance is not reduced as the extended length coned bearings will be subjected to identical or near identical mechanical and thermal loading as existing bearing designs due to their use in conjunction the existing standard spindles and wheel hubs, and thereby maintaining the standard bearing land distances and bearing dimensions. 
     It will be appreciated that variants of the above-disclosed and other features and functions, or alternatives thereof, may be combined into many other different systems or applications. Various presently unforeseen or unanticipated alternatives, modifications, variations, or improvements therein may be subsequently made by those skilled in the art which are also intended to be encompassed by the following claims.