Patent Publication Number: US-11655679-B2

Title: Downhole drilling tool with a polycrystalline diamond bearing

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     The present application is a Continuation of U.S. patent application Ser. No. 16/561,335, filed on Sep. 5, 2019 (pending), which is a Continuation-in-Part of U.S. patent application Ser. No. 16/049,608 (now U.S. Pat. No. 10,738,821), entitled “Polycrystalline Diamond Radial Bearing”, filed on Jul. 30, 2018, which are incorporated herein by reference for all purposes and made a part of the present disclosure. 
    
    
     FIELD 
     The present disclosure relates to tools having polycrystalline diamond radial bearings, systems including the same, and methods of making and using the same. 
     BACKGROUND 
     Radial bearings are used in tools, machines, and components to bear load. One application of radial bearings is in motors, including drilling motors. When drilling a wellbore, a drill bit is sometimes rotated via a drilling motor, which may be coupled with the drill bit via a drive shaft extending from the motor, through a bearing housing, and to the drill bit. Such couplings typically include bearings positioned between the bearing housing and the drive shaft to allow rotation of the drive shaft while the bearing housing remains generally stationary within the wellbore or rotates with the drill string. 
     When polycrystalline diamond elements are used as radial bearings in drilling motors, typically the spacing between adjacent polycrystalline diamond elements is minimized in order to avoid edge contact between the engagement surface of the polycrystalline diamond elements and the opposing engagement surface. Minimizing the spacing between adjacent bearing elements reduces the space on the drill string available for sensors, actuators, or other discrete downhole components. 
     Also, when polycrystalline diamond elements are used as radial bearings in drilling tools, typically both the engagement surface and the opposing engagement surface are composed of polycrystalline diamond. This is, at least in part, because thermally stable polycrystalline diamond (TSP), either supported or unsupported by tungsten carbide, and polycrystalline diamond compact (PDC or PCD) have been considered as contraindicated for use in the machining of diamond reactive materials. Diamond reactive materials include ferrous metals, and other metals, metal alloys, composites, hardfacings, coatings, or platings that contain more than trace amounts of diamond catalyst or solvent elements, including cobalt, nickel, ruthenium, rhodium, palladium, chromium, manganese, copper, titanium, or tantalum. Further, this prior contraindication of the use of polycrystalline diamond extends to so called “superalloys”, including iron-based, cobalt-based and nickel-based superalloys containing more than trace amounts of diamond catalyst or solvent elements. The surface speeds typically used in machining of such materials typically ranges from about 0.2 m/s to about 5 m/s. Although these surface speeds are not particularly high, the load and attendant temperature generated, such as at a cutting tip, often exceeds the graphitization temperature of diamond (i.e., about 700° C.), which can, in the presence of diamond catalyst or solvent elements, lead to rapid wear and failure of components. Without being bound by theory, the specific failure mechanism is believed to result from the chemical interaction of the carbon bearing diamond with the carbon attracting material that is being machined. An exemplary reference concerning the contraindication of polycrystalline diamond for diamond catalyst or solvent containing metal or alloy machining is U.S. Pat. No. 3,745,623, which is incorporated herein by reference in its entirety. The contraindication of polycrystalline diamond for machining diamond catalyst or diamond solvent containing materials has long caused the avoidance of the use of polycrystalline diamond in all contacting applications with such materials. 
     Polycrystalline diamond radial bearings have been developed that have polycrystalline diamond bearing surfaces that mate with non-ferrous superhard materials or, much more commonly, with tightly-matched complementary polycrystalline diamond surfaces. As used herein, a “superhard material” is a material that is at least as hard as tungsten carbide (e.g., cemented tungsten carbide or tungsten carbide tiles). An exemplary reference concerning polycrystalline diamond radial bearings, either in contact with superhard materials or with matching polycrystalline diamond, is U.S. Pat. No. 4,764,036, to McPherson and assigned to Smith International Inc., the entirety of which is incorporated herein by reference. As would be understood by one skilled in the art, hardness may be determined using the Vickers hardness test, which may be performed, for example, in accordance with ASTM E92-17. 
     So called high-performance polycrystalline diamond bearings are designed particularly for harsh environments, such as downhole drilling and pumping environments or wind turbine energy units, and utilize sliding, mated, overlapping polycrystalline diamond elements. This requires a large number of polycrystalline diamond elements, each shaped with an exacting outer profile. For example, rotor mounted polycrystalline diamond elements are shaped with a convex outer profile substantially matched to an outer diameter of the rotor. Stator polycrystalline diamond elements are shaped with a concave outer profile substantially matched to an inner diameter of the stator. This shaping of the polycrystalline diamond elements requires exacting precision and is expensive, requiring, for example, cutting with electrical discharge machining (EDM), lasers, or diamond grinding. The polycrystalline diamond elements must then be mounted in precise locations, at precise alignments and at precisely prescribed heights or exposures to ensure mated sliding engagement. The goal in such components is full-face contact of the polycrystalline diamond elements as bearing areas. Thus, the processes used to prepare such polycrystalline diamond elements are expensive and time consuming, with significant opportunities for variance resulting in scrapped parts. Failures in alignment and/or exposure are likely to produce so called “edge clashing” as the polycrystalline diamond elements rotate against each other producing fractured elements and ultimately resulting in bearing failure. 
     Less expensive radial bearings utilizing polycrystalline diamond have been proposed where a nearly full circumferential array of contoured polycrystalline diamond elements are mounted on a rotor with superhard material mounted on the stator. Although this approach requires fewer polycrystalline diamond elements than the previously described approaches, it still requires contouring of the rotor mounted elements. In addition, such so called superhard materials tend to be more brittle and prone to impact damage than the diamond reactive materials disclosed herein. 
     Additional significant references that inform the background of the technology of this application are from the International Journal of Machine Tools &amp; Manufacture 46 and 47 titled “Polishing of polycrystalline diamond by the technique of dynamic friction, part 1: Prediction of the interface temperature rise” and “Part 2, Material removal mechanism” 2005 and 2006. These references report on the dynamic friction polishing of PDC faces utilizing dry sliding contact under load with a carbon attractive steel disk. Key findings in these references indicate that polishing rate is more sensitive to sliding rate than load and that the rate of thermo-chemical reaction between the steel disk and the diamond surface reduces significantly as the surface finish of the diamond surface improves. It is indicated that the thermo-chemical reaction between the steel disk and the PDC face does not occur at sliding speeds below 10.5 m/s at a pressure of 27 MPa. These references are incorporated herein by reference, as if set out in full. Copper and titanium were not typically listed in the early General Electric documentation on diamond synthesis but have been added later. Relevant references include “Diamond Synthesis from Graphite in the Presence of Water and SiO 2 ”; Dobrzhinetskaya and Green, II International Geology Review Vol. 49, 2007 and “Non-metallic catalysts for diamond synthesis under high pressure and high temperature”, Sun et al, Science in China August 1999. 
     BRIEF SUMMARY 
     Some embodiments of the present disclosure include a downhole drilling tool (e.g., motor) for use in a downhole drill string. The downhole drilling motor includes a rotor movably coupled within a stator. A drive shaft is movably coupled within a bearing housing. The drive shaft has a first end coupled with the rotor and a second end coupled with a drill bit. A bearing assembly interfaces engagement between the drive shaft and the bearing housing. The bearing assembly includes a plurality of polycrystalline diamond elements. Each polycrystalline diamond element has an engagement surface. The bearing assembly includes an opposing engagement surface that includes a metal that is softer than tungsten carbide. The opposing engagement surface is movably engaged with each of the engagement surfaces. Either the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing, or the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft. 
     Other embodiments include a bearing assembly for use in a downhole drill string. The bearing assembly includes a drive shaft movably coupled within a bearing housing. The drive shaft has a first end and a second end. A bearing assembly interfaces engagement between the drive shaft and the bearing housing. The bearing assembly includes a plurality of polycrystalline diamond elements, each having an engagement surface, and an opposing engagement surface that includes a metal that is softer than tungsten carbide. The opposing engagement surface is movably engaged with each of the engagement surfaces. Either the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing, or the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft. 
     Other embodiments include a method of bearing radial and thrust load in a drill string bearing assembly. The method includes coupling a drive shaft within a bearing housing. The drive shaft has a first end and a second end. Coupling the drive shaft within the bearing housing includes interfacing engagement between the drive shaft and the bearing housing with a bearing assembly. The bearing assembly includes a plurality of polycrystalline diamond elements, each having an engagement surface, and an opposing engagement surface including a metal that is softer than tungsten carbide. The opposing engagement surface is movably engaged with each of the engagement surfaces. Either the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing, or the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft. The method includes bearing radial and thrust loads on the drive shaft with the bearing assembly. 
     Other embodiments of the present disclosure includes a method of designing a bearing assembly for a drive shaft and bearing housing of a downhole drilling motor. The bearing assembly includes polycrystalline diamond elements, each including an engagement surface in sliding engagement with an opposing engagement surface. The opposing engagement surface includes a metal that is softer than tungsten carbide. The method includes determining if a maximum sliding speed of the drive shaft and the bearing housing is less than a preset limit. If the maximum sliding speed is less than the preset limit, the method includes selecting a configuration of the bearing assembly within the drive shaft and bearing housing. The method includes calculating a maximum contact pressure per polycrystalline diamond element based on a selected number of polycrystalline diamond elements in the selected configuration of the bearing assembly within the drive shaft and bearing housing, and based on anticipated load. The calculated maximum contact pressure is optionally multiplied by a safety factor. The method includes determining if the calculated maximum contact pressure, optionally multiplied by the safety factor, is below a preset maximum allowable pressure. If the calculated maximum contact pressure is determined to be below the preset maximum allowable pressure, the method includes deploying at least a minimum number of the polycrystalline diamond elements on the selected configuration of the bearing assembly within the drive shaft and bearing housing. If the number of the polycrystalline diamond elements fit on the selected configuration of the bearing assembly within the drive shaft and bearing housing, the method includes making the bearing assembly for the drive shaft and bearing housing. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       So that the manner in which the features and advantages of the systems, apparatus, and/or methods of the present disclosure may be understood in more detail, a more particular description briefly summarized above may be had by reference to the embodiments thereof which are illustrated in the appended drawings that form a part of this specification. It is to be noted, however, that the drawings illustrate only various exemplary embodiments and are therefore not to be considered limiting of the disclosed concepts as it may include other effective embodiments as well. 
         FIG.  1    is a flow chart showing generalized evaluation criteria for the use of the technology disclosed herein. 
         FIG.  2 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  2 B  is a cross-sectional view of the rotor and stator radial bearing assembly of  FIG.  2 A  taken along line A-A. 
         FIG.  3 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  3 B  is a cross-sectional view of the assembly of  FIG.  3 A  taken along line B-B. 
         FIG.  4 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  4 B  is a cross-sectional view of the assembly of  FIG.  4 A  taken along line C-C. 
         FIG.  5 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  5 B  is a cross-sectional view of the assembly of  FIG.  5 A  taken along line D-D. 
         FIG.  6 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  6 B  is a cross-sectional view of the assembly of  FIG.  6 A  taken along line E-E. 
         FIG.  7 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  7 B  is a cross sectional view of the assembly of  FIG.  7 A  taken along line F-F. 
         FIG.  8 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  8 B  is a cross-sectional view of the assembly of  FIG.  8 A  taken along line G-G. 
         FIG.  9 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  9 B  is a cross-sectional view of the assembly of  FIG.  9 A  taken along line H-H. 
         FIG.  10 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  10 B  is a top cross-sectional view of the assembly of  FIG.  10 A  taken along line I-I. 
         FIG.  11 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  11 B  is a cross-sectional view of the assembly of  FIG.  11 A  taken along line J-J. 
         FIG.  12 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  12 B  is a cross-sectional view of the assembly of  FIG.  12 A  taken along line K-K. 
         FIG.  13 A  is a partial side view of a rotor and stator radial bearing assembly of an embodiment of the technology of this application. 
         FIG.  13 B  is a cross-sectional view of the assembly of  FIG.  13 A  taken along line L-L. 
         FIG.  14 A  is a portion of a drill string assembly. 
         FIG.  14 B  is a cross-sectional view of a portion of the assembly of  FIG.  14 A . 
         FIG.  14 C  is another cross-sectional view of a portion of the assembly of  FIG.  14 A . 
         FIG.  14 D  is a simplified schematic of a drilling motor coupled with a drill bit. 
         FIG.  15 A  depicts a cup portion and a cone portion of a radiused conical bearing with polycrystalline diamond elements on the cone portion. 
         FIG.  15 B  depicts a cup portion and a cone portion of another radiused conical bearing with polycrystalline diamond elements on the cup portion. 
         FIG.  15 C  is a perspective view of a polycrystalline diamond element showing the engagement surface thereof. 
         FIG.  15 D  is a top view of the polycrystalline diamond element of  FIG.  15 C . 
         FIG.  16 A  is a side view of a portion of a drill string assembly. 
         FIG.  16 B  is a cross-sectional view of the drill string assembly of  FIG.  16 A . 
         FIG.  16 C  is a perspective view of a portion of the drill string assembly of  FIG.  16 A . 
         FIG.  16 D  is another perspective view of a portion of the drill string assembly of  FIG.  16 A . 
         FIG.  16 E  is another side view of a portion of the drill string assembly of  FIG.  16 A . 
         FIG.  16 F  is a detail view of a portion of the drill string assembly of  FIG.  16 E . 
         FIG.  16 G  depicts two, adjacent polycrystalline diamond elements, showing the spacing therebetween. 
         FIG.  17 A  is a side view of a portion of a drill string assembly. 
         FIG.  17 B  is a cross-sectional view of the drill string assembly of  FIG.  17 A . 
         FIG.  17 C  is a perspective view of a portion of the drill string assembly of  FIG.  17 A . 
         FIG.  17 D  is another perspective view of a portion of the drill string assembly of  FIG.  17 A . 
         FIG.  17 E  is another side view of a portion of the drill string assembly of  FIG.  17 A . 
         FIG.  17 F  is a detail view of a portion of the drill string assembly of  FIG.  17 E . 
         FIG.  17 G  depicts two, adjacent polycrystalline diamond elements, showing the spacing therebetween. 
         FIG.  18 A  is a perspective view of a portion of a drill string assembly. 
         FIG.  18 B  is a cross-sectional view of  FIG.  18 A  along line B-B. 
         FIG.  18 C  is a side view of a portion of the drill string assembly of  FIG.  18 A . 
         FIG.  18 D  is a cross-sectional view of  FIG.  18 C  along line D-D. 
         FIG.  18 E  is a perspective view of a drive shaft having a polycrystalline diamond element engaged therewith. 
         FIG.  18 F  is a cross-sectional view of a portion of a drill string assembly substantially identical to that of  FIG.  18 B , with the exception that the drive shaft has a bearing ring positioned thereabout. 
         FIG.  18 G  is a cross-sectional view of a portion of a drill string assembly substantially identical to that of  FIG.  18 F , with the exception that the drive shaft and the bearing housing have bearing rings positioned thereabout. 
         FIG.  19 A  is a perspective view of a portion of a drill string assembly with spaced-apart polycrystalline diamond elements, with additional downhole components positioned within the spaces between adjacent polycrystalline diamond elements. 
         FIG.  19 B  is a side view of a portion of the drill string assembly of  FIG.  19 A . 
         FIG.  19 C  is a cross-sectional view of a portion of the drill string assembly, showing additional available space in a bearing housing. 
         FIG.  19 D  is a cross-sectional view of a portion of the drill string assembly, identical to  FIG.  19 C , with the exception of showing additional downhole components in the available space in the bearing housing. 
     
    
    
     Systems, apparatus, and methods according to present disclosure will now be described more fully with reference to the accompanying drawings, which illustrate various exemplary embodiments. Concepts according to the present disclosure may, however, be embodied in many different forms and should not be construed as being limited by the illustrated embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough as well as complete and will fully convey the scope of the various concepts to those skilled in the art and the best and preferred modes of practice. 
     DETAILED DESCRIPTION 
     Certain embodiments of the present disclosure include tools (e.g., motors) and components thereof having polycrystalline radial bearings, systems including the same, and methods of making and using the same. The motors disclosed herein may be drilling motors for downhole drilling, including directional drilling, such as mud motors. Certain embodiments include drives shafts having polycrystalline diamond radial bearings thereon. For convenience, certain parts of the following descriptions disclose a stator component and a rotor component. However, it would be understood by one skilled in the technology disclosed herein may be applied to parts that are movably engaged other than stators and rotors, such as a drive shaft movably coupled within a housing. Also, for convenience, certain parts of the following descriptions present an outer stator component and an inner rotor component. However, it would be understood by one skilled in the art that the inner component may be held static and the outer component may be rotated. Additionally, it would be understood by one skilled in the art that, although the descriptions of the disclosure are directed to rotor and stator configurations, the technology disclosed herein is not limited to such applications and may be applied in various other applications including discrete bearings with an inner and outer race where the outer and inner races both rotate or where either one or the other of the outer and inner races is held stationary. 
     Definitions, Examples, and Standards 
     Diamond Reactive Materials—As used herein, a “diamond reactive material” is a material that contains more than trace amounts of diamond catalyst or diamond solvent. As used herein, a diamond reactive material that contains more than “trace amounts” of diamond catalyst or diamond solvent, containing at least 2 percent by weight (wt. %) diamond reactive material. In some aspects, the diamond reactive materials disclosed herein contain from 2 to 100 wt. %, or from 5 to 95 wt. %, or from 10 to 90 wt. %, or from 15 to 85 wt. %, or from 20 to 80 wt. %, or from 25 to 75 wt. %, or from 25 to 70 wt. %, or from 30 to 65 wt. %, or from 35 to 60 wt. %, or from 40 to 55 wt. %, or from 45 to 50 wt. % of diamond catalyst or diamond solvent. As used herein, a “diamond catalyst” is a chemical element, compound, or material capable of catalyzing graphitization of polycrystalline diamond, such as under load and at a temperature at or exceeding the graphitization temperature of diamond (i.e., about 700° C.). As used herein, a “diamond solvent” is a chemical element, compound, or material capable of solubilizing polycrystalline diamond, such as under load and at a temperature at or exceeding the graphitization temperature of diamond. Thus, diamond reactive materials include materials that, under load and at a temperature at or exceeding the graphitization temperature of diamond, can lead to wear, sometimes rapid wear, and failure of components formed of or including polycrystalline diamond, such as diamond tipped tools. Diamond reactive materials include, but are not limited to, metals, metal alloys, and composite materials that contain more than trace amounts of diamond catalyst or solvent elements. In some aspects, the diamond reactive materials are in the form of hardfacings, coatings, or platings. For example, and without limitation, the diamond reactive material may be ferrous, cobalt, nickel, ruthenium, rhodium, palladium, chromium, manganese, copper, titanium, tantalum, or alloys thereof. In some aspects, the diamond reactive material is a superalloy including, but not limited to, iron-based, cobalt-based and nickel-based superalloys. In certain aspects, the diamond reactive material is not and/or does not include (i.e., specifically excludes) so called “superhard materials.” As would be understood by one skilled in the art, “superhard materials” are a category of materials defined by the hardness of the material, which may be determined in accordance with the Brinell, Rockwell, Knoop and/or Vickers scales. For example, superhard materials include materials with a hardness value exceeding 40 gigapascals (GPa) when measured by the Vickers hardness test. As used herein, superhard materials include materials that are at least as hard as tungsten carbide tiles and/or cemented tungsten carbide, such as is determined in accordance with one of these hardness scales, such as the Brinell scale. One skilled in the art would understand that a Brinell scale test may be performed, for example, in accordance with ASTM E10-18; the Vickers hardness test may be performed, for example, in accordance with ASTM E92-17; the Rockwell hardness test may be performed, for example, in accordance with ASTM E18; and the Knoop hardness test may be performed, for example, in accordance with ASTM E384-17. The “superhard materials” disclosed herein include, but are not limited to, tungsten carbide (e.g., tile or cemented), infiltrated tungsten carbide matrix, silicon carbide, silicon nitride, cubic boron nitride, and polycrystalline diamond. Thus, in some aspects, the “diamond reactive material” is partially or entirely composed of material(s) (e.g., metal, metal alloy, composite) that is softer (less hard) than superhard materials, such as less hard than tungsten carbide (e.g., tile or cemented), as determined in accordance with one of these hardness tests, such as the Brinell scale. 
     Interfacing Polycrystalline Diamond with Diamond Reactive Materials—In some aspects, the present disclosure provides for interfacing the engagement between a rotor and stator with a polycrystalline diamond element in contact with a diamond reactive material. For example, the polycrystalline diamond element may be positioned and arranged on the stator for sliding contact with the rotor, where the rotor is formed of or includes at least some diamond reactive material. Alternatively, the polycrystalline diamond element may be positioned and arranged on the rotor for sliding contact with the stator, where the stator is formed of or includes at least some diamond reactive material. The polycrystalline diamond element may have an engagement surface for engagement with an opposing engagement surface of the diamond reactive material. As used herein, “engagement surface” refers to the surface of a material (e.g., polycrystalline diamond or diamond reactive materials) that is positioned and arranged within a bearing assembly such that, in operation of the bearing assembly, the engagement surface interfaces the contact between the two components (e.g., between the stator and the rotor). The “engagement surface” may also be referred to herein as the “bearing surface”. In some aspects the opposing engagement surface includes or is composed of at least 2 wt. % of diamond reactive material, or from 2 to 100 wt. %, or from 5 to 95 wt. %, or from 10 to 90 wt. %, or from 15 to 85 wt. %, or from 20 to 80 wt. %, or from 25 to 75 wt. %, or from 25 to 70 wt. %, or from 30 to 65 wt. %, or from 35 to 60 wt. %, or from 40 to 55 wt. %, or from 45 to 50 wt. % of diamond reactive material. 
     Lapped or Polished—In certain applications, the polycrystalline diamond element, or at least the engagement surface thereof, is lapped or polished, optionally highly lapped or highly polished. Although highly polished polycrystalline diamond elements are preferred in at least some applications, the scope of this disclosure is not limited to highly polished polycrystalline diamond elements and includes polycrystalline diamond elements that are highly lapped or polished. As used herein, a surface is defined as “highly lapped” if the surface has a surface finish of 20 μin or about 20 μin, such as a surface finish ranging from about 18 to about 22 μin. As used herein, a surface is defined as “polished” if the surface has a surface finish of less than about 10 μin, or of from about 2 to about 10 μin. As used herein, a surface is defined as “highly polished” if the surface has a surface finish of less than about 2 μin, or from about 0.5 μin to less than about 2 μin. In some aspects, engagement surface  101  has a surface finish ranging from 0.5 μin to 40 μin, or from 2 μin to 30 μin, or from 5 μin to 20 μin, or from 8 μin to 15 μin, or less than 20 μin, or less than 10 μin, or less than 2 μin, or any range therebetween. Polycrystalline diamond that has been polished to a surface finish of 0.5 μin has a coefficient of friction that is about half of standard lapped polycrystalline diamond with a surface finish of 20-40 μin. U.S. Pat. Nos. 5,447,208 and 5,653,300 to Lund et al., the entireties of which are incorporated herein by reference, provide disclosure relevant to polishing of polycrystalline diamond. As would be understood by one skilled in the art, surface finish may be measured with a profilometer or with Atomic Force Microscopy. Table 1, below, sets for a summary of coefficients of friction for various materials, including polished polycrystalline diamond, in both a dry, static state and a lubricated, static state, where the “first material” is the material that is moved relative to the “second material” to determine the CoF of the first material. 
                                 TABLE 1*               First Material   Second Material   Dry Static   Lubricated Static                  Hard Steel   Hard Steel   0.78   0.05-0.11       Tungsten Carbide   Tungsten Carbide   0.2-0.25   0.12       Diamond   Metal   0.1-0.15   0.1        Diamond   Diamond   0.1    0.05-0.1        Polished PDC   Polished PDC   Estimated   Estimated                0.08-1   0.05-0.08       Polished PDC   Hard Steel   Estimated    Estimated                0.08-0.12   0.08-0.1               *References include Machinery&#39;s Handbook; Sexton T N, Cooley C H. Polycrystalline diamond thrust bearings for down-hole oil and gas drilling tools. Wear 2009; 267: 1041-5.            
Evaluation Criteria
 
       FIG.  1    depicts flow chart  100  of an emblematic generalized set of evaluation criteria for the use of the technology of this application in a dry, non-lubricated environment. As indicated by box  101 , first it is evaluated if the maximum sliding speed in an application is less than 10.5 m/s. As used herein the “sliding speed”, also referred to as the “sliding interface speed”, is the speed with which two components in contact move relative to one another (e.g., the speed at which a rotor, in contact with a stator, moves relative to the stator). While  FIG.  1    is described with respect to a rotor and stator, the same method may be applied a drive shaft and a bearing housing, or other components that are movably engaged. 
     If it is determined that the maximum sliding speed is not be less than 10.5 m/s, then, as indicated by box  102 , it is determined that the evaluated application is not a candidate for use of a polycrystalline diamond element is sliding engagement with a diamond reactive material because the sliding speed is too high. One skilled in the art would understand that, in a lubricated or wet environment, the sliding interface speed can be significantly higher than in a dry, non-lubricated environment (as is herein evaluated). 
     If it is determined that the maximum sliding speed is less than 10.5 m/s, then, as indicated by box  103 , the configuration (e.g., shape, size, and arrangement) of the polycrystalline diamond element is selected depending on the particular application at hand. Box  103  sets forth various non-limiting polycrystalline diamond element configurations for sliding engagement with diamond reactive materials in various bearing configurations. For example, a planar polycrystalline diamond element may be selected for use on a stator that is engaged with a cylindrical rotor formed of or including at least some diamond reactive material; a convex polycrystalline diamond element may be selected for use on a stator that is engaged with a cylindrical rotor formed of or including at least some diamond reactive material; a polycrystalline diamond element having a concave, or at least slightly concave, surface may be selected for use on a stator that is engaged with a cylindrical rotor formed of or including at least some diamond reactive material; a polycrystalline diamond element having a convex, or at least slightly convex, surface may be selected for use on a rotor that is engaged with a cylindrical stator formed of or including at least some diamond reactive material; a chisel shaped polycrystalline diamond element may be selected for use on a stator that is engaged with a grooved rotor formed of or including at least some diamond reactive material; a dome or hemisphere shaped polycrystalline diamond element may be selected for use on a stator that is engaged with a grooved rotor formed of or including at least some diamond reactive material; a planar polycrystalline diamond element may be selected for use on a conic shaped stator that is engaged with a conic shaped rotor formed of or including at least some diamond reactive material; a polycrystalline diamond element having a convex, or at least slightly convex, surface may be selected for use on a conic shaped stator that is engaged with a conic shaped rotor formed of or including at least some diamond reactive material; a polycrystalline diamond element having a convex, or at least slightly convex, surface may be selected for use on a conic shaped rotor that is engaged with a conic shaped stator formed of or including at least some diamond reactive material; a polycrystalline diamond element having a concave, or at least slightly concave, surface may be selected for use on a conic shaped stator that is engaged with a conic shaped rotor formed of or including at least some a diamond reactive material; a polycrystalline diamond element having a convex, or at least slightly convex, surface may be selected for use on a spherical shaped rotor that is engaged with a spherical shaped stator formed of or including at least some diamond reactive material; or a polycrystalline diamond element having a planar, convex, or at least slightly convex surface may be selected for use on a spherical shaped stator that is engaged with a spherical shaped rotor formed of or including at least some diamond reactive material. One skilled in the art would understand that the present disclosure is not limited to these particular selected shapes and contours, and that the shapes, including surface contouring, of the rotors, stators, polycrystalline diamond elements, and other application specific components may vary depending on the particular application. 
     After selecting the configuration, as set forth in box  103 , the maximum contact pressure per polycrystalline diamond element is calculated. As set forth in box  104 , the maximum contact pressure per polycrystalline diamond element is calculated based on the number of polycrystalline diamond elements and the anticipated load, including radial, axial, bending, or other loads. The maximum contact pressure may be determined by methods known to those skilled in the art. 
     After calculation of the maximum contact pressure per polycrystalline diamond element, the calculated maximum pressure per polycrystalline diamond element is multiplied by a safety factor, as set forth in box  105 . The application of the safety factor, over and above the maximum pressure determined in box  104 , may be set and applied at the discretion of a designer, for example. Thus, the safety factor, if applied, provides for a reduced pressure per polycrystalline diamond element relative to the maximum contact pressure per polycrystalline diamond element. 
     In box  106 , it is determined whether the calculated maximum pressure is below maximum allowable pressure for anticipated cycles of the apparatus. As would be understood by those skilled in the art, the fatigue on the diamond reactive material is the limiting factor. The load is at the diamond/diamond reactive material (e.g., metal) interface. The more the PDC elements in an assembly, the lower the instant load on the metal. S—N curves (contact stress to cycles) can be used to facilitate making the determination in box  106 . 
     If, per box  106 , it is determined that the calculated pressure is not below the maximum allowable pressure, then, as indicated in box  107 , additional polycrystalline diamond elements are deployed to the design configuration that was selected in box  103 . After these additional polycrystalline diamond elements are deployed, the thus modified design configuration is evaluated per boxes  104  and  105  before being, once again, assessed per the criteria of box  106 . 
     If, per box  106 , it is determined that the calculated pressure is below the maximum allowable pressure, then, as indicated in box  108 , the proposed design configuration is then created by deploying at least the minimum number of polycrystalline diamond elements indicated as required by the prior boxes  101 - 106  onto the components of the chosen design configuration of box  103  (e.g., attaching the minimum number of polycrystalline diamond elements onto the stator or rotor). 
     At box  109 , it is determined whether the minimum number of polycrystalline diamond elements, per box  108 , will fit on the chosen configuration of box  103 . If it is determined that, the minimum number of polycrystalline diamond elements will fit on the chosen configuration of box  103 , then the bearing assembly in the rotor and stator is produced, as shown in box  110 . If it determined that the minimum number of polycrystalline diamond elements will not fit on the chosen configuration of box  103 , then the chosen configuration of box  103  is determined to not be a candidate for use of a polycrystalline diamond element in sliding engagement with a diamond reactive material, per box  102 . 
     The designer of the bearing configuration would also have the option (not shown) of choosing an alternative bearing configuration from box  103  if the required minimum number of polycrystalline diamond elements will not fit on the originally chosen design configuration. Alternatively, the safety factor can be lowered to reduce the minimum number of polycrystalline diamond elements required. One skilled in the art would understand that the criteria set forth in  FIG.  1    is exemplary only, that other criteria may be evaluated depending on the particular application, and that, for at least some applications, some of the criteria set forth in  FIG.  1    may be left out without departing from the scope of this disclosure. 
     Various exemplary rotor and stator radial bearing assemblies will now be described with reference to  FIGS.  2 A- 13 B . In  FIGS.  2 A- 13 B , like reference numerals refer to like elements. For example, an exemplary assembly is identified with reference numeral “ 200 ” in  FIGS.  2 A and  2 B  and is identified with reference numeral “ 300 ” in  FIGS.  3 A and  3 B . 
     Stator with Planar Polycrystalline Diamond Element 
       FIG.  2 A  is a partial side view of a rotor and stator radial bearing assembly, and  FIG.  2 B  is a cross-sectional view of the rotor and stator radial bearing assembly of  FIG.  2 A  taken along line A-A. With reference to both  FIGS.  2 A and  2 B , rotor and stator radial bearing assembly  200  will be described. 
     Rotor and stator radial bearing assembly  200  includes stator  202  engaged with rotor  203 . Four planar polycrystalline diamond elements  201  are fitted into stator  202  to provide for sliding engagement between stator  202  and rotor  203 , where rotor  203  is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  201  are deployed (e.g., mechanically fitted) in stator  202  within loading ports  204 , which are ports formed in and/or positioned within stator body  211 . For example, and without limitation, each polycrystalline diamond element  201  may be press fit, glued, brazed, threaded, or otherwise mounted on stator  202  (or rotor in other applications) via methods known to those skilled in the art. One skilled in the art would understand that the present disclosure is not limited to these particular attachment methods or to the use of ports within the stator body, and that the polycrystalline diamond elements may be attached to the stator or rotor by any of a variety of methods. Further, while shown as including equally spaced, planar polycrystalline diamond elements, one skilled in the art would understand that the number, spacing, armament, shape, and size of the polycrystalline diamond elements may vary depending upon any number of various design criteria including, but not limited to, the criteria set forth in  FIG.  1   . In some aspects, polycrystalline diamond elements are composed of thermally stable polycrystalline diamond, either supported or unsupported by tungsten carbide, or polycrystalline diamond compact. 
     Each polycrystalline diamond element  201  includes an engagement surface  213  (here shown as planar surfaces), and rotor  203  includes opposing engagement surface  215 . Polycrystalline diamond elements  201  are positioned on stator  202  in secure contact with rotor  203 , to limit lateral movement of rotor  203  while allowing for free sliding rotation of rotor  203  during operation. Polycrystalline diamond elements  201  are positioned and arranged such that engagement surfaces  213  are in contact (e.g., sliding contact) with opposing engagement surface  215 . Thus, engagement surfaces  213  and opposing engagement surface  215  interface the sliding contact between rotor  203  and stator  202 . In some embodiments, rotor  203  has a rotational velocity, engagement between engagement surface  213  and opposing engagement surface  215  defines a contact area that is independent of the rotational velocity of rotor  203 . In some embodiments, rotor  203  has a variable rotational velocity, and engagement surface  213  follows an engagement path on opposing engagement surface  215  that is constant through the variable rotational velocities. 
       FIGS.  2 A and  2 B  depict a rotor and stator such as would be used in a downhole pump or motor. However, one skilled in the art would understand that radial bearings for other applications, as well as discrete radial bearings, may be designed and manufactured in the same or similar manner in accordance with this disclosure. Non-limiting proximal and distal dimensions for such a discrete bearing are indicated by dashed lines  205  shown in  FIG.  2 A . As shown in  FIG.  2 B , optionally, a through bore  207  is provided in rotor  203 , which could be used in a discrete bearing, for example. As is evident in  FIG.  2 B , polycrystalline diamond elements  201  are deployed in stator  202  to radially support and provide sliding engagement with rotor  203 . 
     Although  FIGS.  2 A and  2 B  depict an assembly that includes four polycrystalline diamond elements  201 , one skilled in the art would understand that less than four polycrystalline diamond elements, such as three polycrystalline diamond elements, or more than four polycrystalline diamond elements may be used depending on the particular application and configuration, such as the space available such polycrystalline diamond elements on the stator or rotor. Further, although  FIGS.  2 A and  2 B  show a single circumferential set of polycrystalline diamond elements  201 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator (or rotor) to increase lateral support and lateral load taking capability of the bearing assembly. 
     Stator with Convex Polycrystalline Diamond Element 
       FIGS.  3 A and  3 B  depict rotor and stator radial bearing assembly  300 , which is substantially similar to that of  FIGS.  2 A and  2 B , with the exception that polycrystalline diamond elements  301  have convex engagement surfaces  313  rather than the flat, planar engagement surfaces of  FIGS.  2 A and  2 B . 
     With reference to  FIGS.  3 A and  3 B , rotor and stator radial bearing  300  includes convex polycrystalline diamond elements  301  fitted into stator body  311  of stator  302  to provide for sliding engagement with rotor  303 , formed of or including at least some diamond reactive material. Polycrystalline diamond elements  301  are deployed in stator  302  through loading ports  304 , and may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. Polycrystalline diamond elements  301  are placed into a secure contacting position with rotor  303  to limit lateral movement of rotor  303  while allowing for free sliding rotation of rotor  303  during operation. As is evident from  FIG.  3 B , polycrystalline diamond elements  301  are deployed in stator  302  to radially support and provide sliding engagement with rotor  303 .  FIG.  3 B  also shows optional through bore  307  such as could be used in a discrete bearing. 
     Although  FIGS.  3 A and  3 B  depict a rotor and stator such as would be used in a downhole pump or motor, other assemblies, including discrete radial bearing assemblies, may be designed and manufactured in the same or substantially the same way. Non-limiting proximal and distal dimensions for such a discrete bearing are indicated by dashed lines  305 . Further, although  FIGS.  3 A and  3 B  show four polycrystalline diamond elements  301 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  302 . Additionally, although  FIGS.  3 A and  3 B  show a single circumferential set of polycrystalline diamond elements  301 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral support and lateral load taking capability of the bearing assembly. 
     As with assembly  200 , in operation engagement surface  313  interfaces with opposing engagement surface  315  to bear load between rotor  303  and stator  302 . 
     Stator with Concave Polycrystalline Diamond Element 
       FIGS.  4 A and  4 B  depict rotor and stator radial bearing assembly  400 , which is substantially similar to that of  FIGS.  2 A- 3 B , with the exception that polycrystalline diamond elements  401  has concave, or at least slightly concave, engagement surfaces  413  rather than the flat, planar engagement surfaces of  FIGS.  2 A and  2 B  or the convex engagement surfaces of  FIGS.  3 A and  3 B . 
     Slightly concave polycrystalline diamond elements  401  are fitted into stator body  411  of stator  402  to provide for sliding engagement with rotor  403 . Polycrystalline diamond elements  401  are deployed in stator  402  through loading ports  404 . Polycrystalline diamond elements  401  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. Polycrystalline diamond elements  401  are placed into secure contacting position with rotor  403  to limit lateral movement of rotor  403  while allowing for free sliding rotation of rotor  403  during operation. 
     As with assembly  300 , in operation engagement surface  413  interfaces with opposing engagement surface  415  to bear load between rotor  403  and stator  402 . The at least slight concavity of each polycrystalline diamond element  401  is oriented with the axis of the concavity, in line with the circumferential rotation of rotor  403 ; thereby ensuring no edge contact between polycrystalline diamond elements  401  and rotor  403  and providing for linear area contact between polycrystalline diamond elements  401  and rotor  403 , generally with the deepest portion of the concavity. That is, engagement between polycrystalline diamond elements  401  and rotor  403  is exclusively interfaced by engagement surface  413  and opposing engagement surface  415 , such that edge or point  417  of polycrystalline diamond elements  401  do not make contact with rotor  403 . As such, only linear area contact, and no edge or point contact, occurs between polycrystalline diamond elements  401  and rotor  403 . As is evident from  FIG.  4 B , polycrystalline diamond elements  401  are deployed in stator  402  to radially support and provide sliding engagement with rotor  403 .  FIG.  4 B  also shows optional through bore  407  such as could be used in a discrete bearing. 
     Although  FIGS.  4 A and  4 B  depict a rotor and stator such as would be used in a downhole pump or motor, assemblies, including a discrete radial bearing assembly, may be designed and manufactured in the same or substantially the same way. Non-limiting proximal and distal dimensions for such a discrete bearing are indicated by dashed lines  405 . Further, although  FIGS.  4 A and  4 B  show four polycrystalline diamond elements  401 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  402 . Additionally, although  FIGS.  4 A and  4 B  show a single circumferential set of polycrystalline diamond elements  401 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral support and lateral load taking capability of the bearing assembly. 
     Rotor with Convex Polycrystalline Diamond Element 
       FIGS.  5 A and  5 B  depict rotor and stator radial bearing assembly  500 , which is substantially similar to that of  FIGS.  3 A and  3 B , with the exception that polycrystalline diamond elements  501 , having the convex, dome shaped engagement surfaces  513 , are installed on rotor  503  rather than on the stator. 
     Convex polycrystalline diamond elements  501  are fitted into rotor body  523  of rotor  503  to provide for sliding engagement with stator  502 , which is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  501  are deployed in rotor  503  in sockets  504  formed into and/or positioned in rotor body  523 . Polycrystalline diamond elements  501  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. Polycrystalline diamond elements  501  are placed into a secure contacting position relative to stator  502  to limit lateral movement of rotor  503  while allowing for free sliding rotation of rotor  503  during operation. As is evident from  FIG.  5 B , polycrystalline diamond elements  501  are deployed in rotor  503  to radially support and provide sliding engagement with stator  502 .  FIG.  5 B  also shows optional through bore  507  such as could be used in a discrete bearing. 
     Although  FIGS.  5 A and  5 B  depict a rotor and stator such as would be used in a downhole pump or motor, other assemblies, including a discrete radial bearing assembly, may be designed and manufactured in the same or similar way. Non-limiting proximal and distal dimensions for such a discrete bearing are indicated by dashed lines  505 . Further, although  FIGS.  5 A and  5 B  show four polycrystalline diamond elements  501 , one skilled in the art would understand that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in rotor  503 . Additionally, although  FIGS.  5 A and  5 B  show a single circumferential set of polycrystalline diamond elements  501 , it would be understood by one skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the rotor to increase lateral support and lateral load taking capability of the bearing assembly. 
     Thus, contrary to the embodiments shown in  FIGS.  2 A- 4 B , in the embodiment shown in  FIGS.  5 A and  5 B , the engagement surfaces  513  are on the rotor  503 , and the opposing engagement surface  515  is on the stator  502 . 
     Stator with Chisel Shaped Polycrystalline Diamond Element 
       FIGS.  6 A and  6 B  depict rotor and stator radial bearing assembly  600  with chisel shaped polycrystalline diamond elements  601  fitted into stator body  611  of stator  602  to provide for sliding engagement with rotor  603 , which is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  601  are deployed in stator  602  through loading ports  604 , which are formed in and/or positioned in stator body  611 . Polycrystalline diamond elements  601  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Polycrystalline diamond elements  601  are placed into a secure contacting position within radial/thrust surface groove  606  of rotor  603  to limit lateral and axial movement of rotor  603  while allowing for free sliding rotation of rotor  603  during operation. Chisel shaped polycrystalline diamond elements  601  are positioned, arranged, shaped, sized, and oriented to slidingly engage into the mating radial/thrust surface groove  606  of rotor  603 . Chisel shaped polycrystalline diamond elements  601  include engagement surface (defined by the chisel shaped polycrystalline diamond elements  601 ), which interfaces in contact with opposing engagement surface, here the surface of radial/thrust surface groove  606 . It is evident from  FIG.  6 B  that chisel shape polycrystalline diamond elements  601  are deployed in stator  602  to radially and axially support and provide sliding engagement with rotor  603 .  FIG.  6 B  also depicts optional through bore  607  such as could be used in a discrete bearing. The embodiment shown in  FIGS.  6 A and  6 B  may further act as a rotor catch. 
     Although  FIGS.  6 A and  6 B  depict a rotor and stator such as would be used in a downhole pump or motor, other assemblies, including a discrete radial bearing assembly, may be designed and manufactured in the same or similar way. Non-limiting proximal and distal dimensions for such a discrete bearing are indicated by dashed lines  605 . Further, although  FIGS.  6 A and  6 B  depicts four polycrystalline diamond elements  601 , it would be understood by one skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements  601  may be deployed in stator  602 . Additionally, although  FIGS.  6 A and  6 B  depict a single circumferential set of polycrystalline diamond elements  601 , it would be understood by one skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     Stator with Dome or Hemisphere Shaped Polycrystalline Diamond Element 
       FIGS.  7 A and  7 B  depict rotor and stator radial bearing assembly  700 , which is substantially similar to that of  FIGS.  6 A and  6 B , with the exception that polycrystalline diamond elements  701  have dome or hemisphere shaped engagement surfaces  713  rather chisel shaped polycrystalline diamond elements. 
     Dome or hemisphere shaped polycrystalline diamond elements  701  are fitted into stator housing  711  of stator  702  to provide for sliding engagement with rotor  703 . Polycrystalline diamond elements  701  are deployed in stator  702  through loading ports  704  formed in and/or positioned in stator body  711 . Polycrystalline diamond elements  701  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. Polycrystalline diamond elements  701  are placed into a secure contacting position relative to radial/thrust surface groove  706  of rotor  703  to limit lateral and axial movement of rotor  703  while allowing for free sliding rotation of rotor  703  during operation. Dome or hemisphere polycrystalline diamond elements  701  slidingly engage the mating radial/thrust surface groove  706  of rotor  703 . Dome or hemisphere polycrystalline diamond elements  701  define engagement surface, which interfaces in contact with opposing engagement surface, here the surface of radial/thrust surface groove  706 . As is evident from  FIG.  7 B , dome or hemisphere polycrystalline diamond elements  701  are deployed in stator  702  to radially and axially support and provide sliding engagement with rotor  703 .  FIG.  7 B  also shows optional through bore  707  such as could be used in a discrete bearing. The embodiment shown in  FIGS.  7 A and  7 B  may further act as a rotor catch. 
     Although  FIGS.  7 A and  7 B  depict a rotor and stator such as would be used in a downhole pump or motor, other assemblies, including a discrete radial bearing assembly, may be designed and manufactured in the same or similar way. Non-limiting proximal and distal dimensions for such a discrete bearing are indicated by dashed lines  705 . Further, although  FIGS.  7 A and  7 B  depict four polycrystalline diamond elements  701 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  702 . Additionally, although  FIGS.  7 A and  7 B  depict a single circumferential set of polycrystalline diamond elements, it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     Stator with Planar Polycrystalline Diamond Element 
       FIGS.  8 A and  8 B  depict rotor and stator radial bearing assembly  800  including planar polycrystalline diamond elements  801  fitted into stator body  811  of stator  802  to provide for sliding engagement with rotor  803 , which is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  801  are deployed in stator  802  through loading ports  804  formed in and/or positioned in stator body  811 . Polycrystalline diamond elements  801  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Polycrystalline diamond elements  801  are placed into a secure contacting position relative to radial/thrust conical surface  806  of rotor  803  to limit lateral and upward axial movement of rotor  803  while allowing for free sliding rotation of rotor  803  during operation. 
     The planar polycrystalline diamond elements  801  slidingly engage the mating radial/thrust conical surface of rotor  803 , such that engagement surfaces  813  contact and interface with opposing engagement surface  806 . As is evident from  FIG.  8 B , polycrystalline diamond elements  801  are deployed in stator  802  to radially and axially support and provide sliding engagement with rotor  803 . 
     Although  FIGS.  8 A and  8 B  depict four polycrystalline diamond elements  801 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  802 . Further, although  FIGS.  8 A and  8 B  depict a single circumferential set of polycrystalline diamond elements  801 , it would be understood that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     While  FIGS.  8 A and  8 B  are described as a bearing arrangement between a rotor  803  and stator  802 , one skilled in the art would understand that the rotor may, instead, be a drive shaft, and the stator may, instead, be a bearing housing. 
     Stator with Convex Polycrystalline Diamond Element 
       FIGS.  9 A and  9 B  depict rotor and stator radial bearing assembly  900 , which is substantially similar to that of  FIGS.  8 A and  8 B , with the exception that polycrystalline diamond elements  901  have convex engagement surfaces  913  rather than planar engagement surfaces. 
     Convex polycrystalline diamond elements  901  are fitted into stator body  911  of stator  902  to provide for sliding engagement with rotor  903 . Polycrystalline diamond elements  901  are deployed in stator  902  through loading ports  904  formed in and/or positioned in stator body  911 . Polycrystalline diamond elements  901  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Convex polycrystalline diamond elements  901  are placed into secure contacting position with radial/thrust conical surface  906  of rotor  903  to limit lateral and upward axial movement of rotor  903  while allowing for free sliding rotation of rotor  903  during operation. Polycrystalline diamond elements  901  slidingly engage the mating radial/thrust conical surface of rotor  903 , such that engagement surfaces  913  contact and interface with opposing engagement surface  906 . 
     As is evident from  FIG.  9 B , convex polycrystalline diamond elements  901  are deployed in stator  902  to radially and axially support and provide sliding engagement with rotor  903 . 
     Although  FIGS.  9 A and  9 B  depict four polycrystalline diamond elements  901 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  902 . Further, although  FIGS.  9 A and  9 B  depict a single circumferential set of polycrystalline diamond elements  901 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     While  FIGS.  9 A and  9 B  are described as a bearing arrangement between a rotor  903  and stator  902 , one skilled in the art would understand that the rotor may, instead, be a drive shaft, and the stator may, instead, be a bearing housing. 
     Rotor with Convex Polycrystalline Diamond Element 
       FIGS.  10 A and  10 B  depict a rotor and stator radial and thrust bearing assembly  1000  including convex polycrystalline diamond elements  1001  fitted into rotor body  1023  of rotor  1003  to provide for sliding engagement with stator  1002 , which is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  1001  are deployed in rotor  1003  in sockets  1004  formed in and/or positioned in rotor body  1023 . Polycrystalline diamond elements  1001  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Convex polycrystalline diamond elements  1001  are placed into a secure contacting position within radial/thrust conical surface  1006  of stator  1002  to limit lateral and upward axial movement of rotor  1003  while allowing for free sliding rotation of rotor  1003  during operation. The convex polycrystalline diamond elements  1001  slidingly engage the mating radial/thrust conical surface of stator  1002 , such that engagement surfaces  1013  contact and interface with opposing engagement surface  1006 . As is evident from  FIG.  10 B , convex polycrystalline diamond elements  1001  are deployed in rotor  1003  to radially and axially support and provide sliding engagement with subject material stator  1002 . 
     Although  FIGS.  10 A and  10 B  depict four polycrystalline diamond elements  1001 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in rotor  1003 . Further, although  FIGS.  10 A and  10 B  depict a single circumferential set of polycrystalline diamond elements  1001 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the rotor to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     While  FIGS.  10 A and  10 B  are described as a bearing arrangement between a rotor  1003  and stator  1002 , one skilled in the art would understand that the rotor may, instead, be a drive shaft, and the stator may, instead, be a bearing housing. 
     Stator with Planar Polycrystalline Diamond Element 
       FIGS.  11 A and  11 B  depict rotor and stator radial and thrust bearing assembly  1100  including concave, or at least slightly concave, polycrystalline diamond elements  1101  fitted into stator body  1111  of stator  1102  to provide for sliding engagement with rotor  1103 , which is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  1101  are deployed in stator  1102  through loading ports  1104  formed and/or positioned therethrough. Polycrystalline diamond elements  1101  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Polycrystalline diamond elements  1101  are placed into a secure contacting position within radial/thrust conical surface  1106  of rotor  1103  to limit lateral and upward axial movement of rotor  1103  while allowing for free sliding rotation of rotor  1103  during operation. Polycrystalline diamond elements  1101  are oriented with the axis of the concavity in line with the circumferential rotation of the rotor  1103  to ensure no edge or point contact, and thus ensure only linear area contact generally with the deepest portion of the concavity. The slightly concave polycrystalline diamond elements  1101  slidingly engage the radial/thrust conical surface of rotor  1103 , such that engagement surfaces  1113  contact and interface with opposing engagement surface  1106 . 
     As is evident from  FIG.  11 B , slightly concave polycrystalline diamond elements  1101  are deployed in stator  1102  to radially and axially support and provide sliding engagement with rotor  1103 . 
     Although  FIGS.  11 A and  11 B  depict four polycrystalline diamond elements  1101 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  1102 . Further, although  FIGS.  11 A and  11 B  show a single circumferential set of polycrystalline diamond elements  1101 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     While  FIGS.  11 A and  11 B  are described as a bearing arrangement between a rotor  1103  and stator  1102 , one skilled in the art would understand that the rotor may, instead, be a drive shaft, and the stator may, instead, be a bearing housing. 
     Rotor with Convex Polycrystalline Diamond Elements 
       FIGS.  12 A and  12 B  depict rotor and stator radial and thrust bearing assembly  1200 , including convex polycrystalline diamond elements  1201  are fitted into rotor body  1223  of rotor  1203  to provide for sliding engagement with stator  1202 . Polycrystalline diamond elements  1201  are deployed in rotor  1203  in sockets  1204  formed in and/or positioned in rotor body  1223 . Polycrystalline diamond elements  1201  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Convex polycrystalline diamond elements  1201  are placed into a secure contacting position within radial/thrust concave curved surface  1206  of stator  1202  to limit lateral and upward axial movement of rotor  1203  while allowing for free sliding rotation of rotor  1203  during operation. Convex polycrystalline diamond elements  1201  slidingly engage the mating radial/thrust concave curved surface of stator  1202 , such that engagement surfaces  1213  engage with radial/thrust concave curved surface  1206 . In the embodiment of  FIGS.  12 A and  121 B , the radial/thrust concave curved surface  1206  is or forms the opposing engagement surface. In the assembly  1200 , the contact areas on the convex polycrystalline diamond elements  1201  are generally circular. However, one skilled in the art would understand that the polycrystalline diamond elements are not limited to having such a contact area. 
     As is evident from  FIG.  12 B , convex polycrystalline diamond elements  1201  are deployed in rotor  1203  to radially and axially support and provide sliding engagement with stator  1202 . 
     Although  FIGS.  12 A and  12 B  depict four polycrystalline diamond elements  1201 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in rotor  1203 . Further, although  FIGS.  12 A and  12 B  depict a single circumferential set of polycrystalline diamond elements  1201 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the rotor to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     While  FIGS.  12 A and  12 B  are described as a bearing arrangement between a rotor  1203  and stator  1202 , one skilled in the art would understand that the rotor may, instead, be a drive shaft, and the stator may, instead, be a bearing housing. 
     Stator with Planar Polycrystalline Diamond Elements 
       FIGS.  13 A and  13 B  depict a partial side view of a rotor and stator radial and thrust bearing assembly  1300  including planar (or domed, not shown) polycrystalline diamond elements  1301  fitted into stator body  1311  of stator  1302  to provide for sliding engagement with rotor  1303 , which is formed of or includes at least some diamond reactive material. Polycrystalline diamond elements  1301  are deployed in stator  1302  through loading ports  1304  formed in and/or positioned in stator body  1311 . Polycrystalline diamond elements  1301  may be press fit, glued, brazed, threaded, or otherwise mounted using methods known to those skilled in the art. 
     Polycrystalline diamond elements  1301  are placed into a secure contacting position with radial/thrust convex curved surface  1306  of rotor  1303  to limit lateral and upward axial movement of rotor  1303  while allowing for free sliding rotation of rotor  1303  during operation. Radial/thrust convex curved surface  1306  is or forms the opposing engagement surface. Polycrystalline diamond elements  1301  slidingly engage the radial/thrust convex curved surface  1306  of rotor  1403 , such that engagement surface  1313  is engaged with the opposing engagement surface (i.e., radial/thrust convex curved surface  1306 ). In the assembly  1300 , the contact areas on the planar or domed polycrystalline diamond elements are typically circular. However, one skilled in the art would understand that the polycrystalline diamond elements may have different contact areas. 
     As is evident from  FIG.  13 B , planar polycrystalline diamond elements  1301  are deployed in stator  1302  to radially and axially support and provide sliding engagement with rotor  1303 . 
     Although  FIGS.  13 A and  13 B  show four polycrystalline diamond elements  1301 , it would be understood by those skilled in the art that fewer (e.g., three) or more polycrystalline diamond elements may be deployed in stator  1302 . Further, although  FIGS.  13 A and  13 B  depict a single circumferential set of polycrystalline diamond elements  1301 , it would be understood by those skilled in the art that one or more additional circumferential sets of polycrystalline diamond elements may be deployed in the stator to increase lateral and axial support and lateral and axial load taking capability of the bearing assembly. 
     While  FIGS.  13 A and  13 B  are described as a bearing arrangement between a rotor  1303  and stator  1302 , one skilled in the art would understand that the rotor may, instead, be a drive shaft, and the stator may, instead, be a bearing housing. 
     As is evident in view of  FIGS.  2 A- 13 B , some aspects of the present disclosure include high-performance radial bearings incorporating polycrystalline diamond elements in sliding engagement with curved or cylindrical surfaces formed of or including at least some diamond reactive material. Some such aspects include high-performance radial bearings where a diamond reactive material containing rotor is put into sliding contact with preferably three or more polycrystalline diamond elements mounted on a stator. The polycrystalline diamond elements of the stator are preferably planar faced, but may also be slightly concave, convex, or any combination of the three. The facial contours of the polycrystalline diamond elements of the stator need not, and preferably do not, match the curve of the circumference of the stator. Although three or more polycrystalline diamond elements are preferred, the technology of the application may be practiced with as few as one or two polycrystalline diamond elements, such as where the polycrystalline diamond elements are used to reduce wear and friction on the gravitational low side of a stator in a horizontally oriented positive displacement pump or opposite the scribe side of a directional drilling assembly. 
     In certain applications, the bearing assemblies disclosed herein are configured to resist thrust load. At least some embodiments of the bearing assemblies disclosed herein are capable of simultaneously handling components of both radial and thrust loads. 
     At least some embodiments of the bearing assemblies disclosed are economically viable and of a relatively large diameter. 
     Edge Radius Treatment 
     In some aspects, the polycrystalline diamond elements are subjected to edge radius treatment. Edge radius treatment of polycrystalline diamond elements are well known in the art. In some embodiments of the technology of this application that employ planar or concave polycrystalline diamond elements, it is preferred to employ edge radius treatment of such polycrystalline diamond elements. One purpose of employing an edge radius treatment is to reduce or avoid potential for outer edge cutting or scribing at the outer limits of the linear engagement area of a given polycrystalline diamond elements with the opposing engagement surface (e.g., a curved surface. 
     Polycrystalline Diamond Element 
     In certain applications, the polycrystalline diamond elements disclosed herein have increased cobalt content transitions layers between the outer polycrystalline diamond surface and a supporting tungsten carbide slug, as is known in the art. 
     The polycrystalline diamond elements may be supported by tungsten carbide, or may be unsupported, “standalone” polycrystalline diamond elements that are mounted directly to the bearing component. 
     The polycrystalline diamond elements may by non-leached, leached, leached and backfilled, thermally stable, coated via chemical vapor deposition (CVD), or processed in various ways as known in the art. 
     Polycrystalline Diamond Element—Shapes, Sizes, and Arrangements 
     The polycrystalline diamond elements may have diameters as small as 3 mm (about ⅛″) or as large as 75 mm (about 3″), depending on the application and the configuration and diameter of the bearing. Typically, the polycrystalline diamond elements have diameters between 8 mm (about 5/16″) and 25 mm (about 1″). 
     Although the polycrystalline diamond elements are most commonly available in cylindrical shapes, it is understood that the technology of the application may be practiced with polycrystalline diamond elements that are square, rectangular, oval, any of the shapes described herein with reference to the Figures, or any other appropriate shape known in the art. In some applications, the radial bearings have one or more convex, contoured polycrystalline diamond elements mounted on a rotor (or stator) in sliding contact with a stator (or rotor). 
     In some applications, the polycrystalline diamond elements are deployed in rings along the bearing component. A non-limiting example is a ring of five planar face polycrystalline diamond elements deployed on a distal portion of a stator and another ring of five planar face polycrystalline diamond elements deployed on a proximal portion of the stator. Thus, the high-performance polycrystalline diamond elements bearing assemblies can be deployed to ensure stable operation along the length of the stator/rotor interface, while requiring less total polycrystalline diamond elements than are used in prior, existing assemblies. 
     The polycrystalline diamond elements may be arranged in any pattern, layout, spacing or staggering within the bearing assembly to provide the desired support, without concern for the need for overlapping contact with polycrystalline diamond elements engagement surfaces on the opposing bearing component. 
     Polycrystalline Diamond Element—Contact Area of Engagement Surface 
     The polycrystalline diamond elements disclosed herein are, in some embodiments, not shaped to conform precisely to the opposing engagement surface. In certain embodiments, the sliding interface contact area of the engagement surface of the polycrystalline diamond element is less than 80%, or less than 75%, or less than 70%, or less than 60% of the total surface area of the polycrystalline diamond element. As used herein, the “contact area” of the engagement surface refers to the surface area of the engagement surface that is in contact with the opposing engagement surface. In some embodiments, the engagement surface is in sliding engagement with the opposing engagement surface along a contact area, the opposing engagement surface rotates about an axis of rotation, and any imaginary line extending from and normal to the contact area surface is at an angle relative to the axis of rotation. In some embodiments, the engagement surface is in sliding contact with the opposing engagement surface through a substantial portion of its use profile. 
     A key performance criterion is that the polycrystalline diamond element is configured and positioned in such a way as to preclude any edge or point contact with the opposing engagement surface or component. For a planar faced polycrystalline diamond element placed on the stator, such polycrystalline diamond elements typically experience less than full face contact with the rotor. That is, as the rotor rotates against the polycrystalline diamond elements, the engagement surface contact area is less than full face. For polycrystalline diamond elements, mounted on either the rotor or stator, that are at least slightly domed or convex, such polycrystalline diamond elements exhibit a small, generally circular engagement surface contact area. If the convex polycrystalline diamond elements, mounted on either the rotor or stator, are saddle shaped, then the polycrystalline diamond elements exhibit a small linear area engagement surface contact area. For slightly concave polycrystalline diamond elements that are deployed on the stator, a somewhat narrow linear engagement surface contact area is exhibited on each polycrystalline diamond element. 
     Polycrystalline Diamond Element—Mounting 
     As previously described, the polycrystalline diamond elements may be mounted directly to the bearing element (e.g., stator or rotor) via methods known in the art including, but not limited to, brazing, gluing, press fitting, shrink fitting, or threading. Additionally, the polycrystalline diamond elements may be mounted in a separate ring or rings. The ring or rings may then be deployed on the bearing element (rotor or stator) via methods known in the art including, but not limited to, gluing, press fitting, thread locking, or brazing. 
     Planar face or domed polycrystalline diamond elements may be mounted in a manner to allow them to rotate about their own axis. Reference is made to U.S. Pat. No. 8,881,849, to Shen et. al., as a non-limiting example of a method to allow the polycrystalline diamond element to spin about its own axis while in facial contact with subject material. 
     Treatment of Opposing Engagement Surface 
     In some aspects, the opposing engaging surface of the diamond reactive material is pre-saturated with carbon (e.g., prior to engagement with the engagement surface). Such pre-saturation reduces the ability of the diamond reactive material to attract carbon through graphitization of the surface of the polycrystalline diamond. The pre-saturation of the diamond reactive material surface contact area may be accomplished via any method known in the art. 
     Solid Lubricant Source 
     In certain applications, a solid lubricant source, for example, a graphite or hexagonal boron nitride stick or inclusion, either energized or not energized, is in contact with the opposing engagement surface formed of or including at least some the diamond reactive material. In some embodiments, the sliding engagement between engagement surface and opposing engagement surface is non-lubricated. 
     Drive Shaft with Polycrystalline Diamond Elements 
     Certain embodiments of the present disclosure include drilling tools (e.g., motors) and components thereof, such as drive shafts and bearing housings, that include polycrystalline radial bearing assemblies thereon. As used herein, downhole tools and downhole drilling tools may be or include, but are not limited to, rotary steerable tools, turbines, jars, reamers, agitators, MWD tools, LWD tools, and drilling motors. Drill strings may include a number of segments, including drill piping or tubulars extending from the surface, a mud motor (i.e., a positive displacement progressive cavity mud powered motor) and a drill bit. The mud motor may include a rotor catch assembly, a power section, a transmission, a bearing package (bearing assembly), and a bit drive shaft with a bit box. The power section generally includes a stator housing connected to and part of the drill string, and a rotor. The radial bearings shown and described with reference to  FIGS.  1 - 13 B  may be incorporated into a such drilling motors (e.g., at the drive shaft and bearing housing). With reference to  FIGS.  14 A and  14 B , some embodiments include a bottom hole assembly (BHA) or a portion thereof, including assembly  1430 . Assembly  1430  includes rotor  1440  movably coupled within a bore of stator  1442 . Rotor  1440  is coupled with transmission  1438 , which is positioned and movably coupled within a bore of transmission housing  1432 . Transmission  1438  is coupled with drive shaft  1436 , which is positioned and movably coupled within a bore of bearing housing  1444 . Drive shaft  1436  is coupled with bit shaft  1434 , and bit shaft  1434  is coupled with or integral with drill bit  1431 . Stator  1442  is coupled with transmission housing  1432 , which is coupled with bearing housing  1444 , which is coupled with shaft housing  1446 . In operation, the mud motor (rotor  1440  and stator  1442 ) is powered by energy harvested from drilling mud as the mud passes through the power section. The drilling mud is pumped at high pressures and volumes from the surface down the internal cavities of a drill string and through the power section. Mud passing through the power section rotates rotor  1440  with respect to stator  1442 . Rotor  1440 , in-turn, drives rotation, through a transmission driveline (transmission  1438 ), drive shaft  1436 , and bit shaft  1434 , to drill bit  1431 . Assembly  1430  may be generally tubular, and may include one or more tubular subunits or subs to, for example and without limitation, facilitate assembly thereof. One having ordinary skill in the art with the benefit of this disclosure would understand that the specific sub arrangement of assembly  1430  depicted and described herein is merely exemplary and is not intended to limit the scope of this disclosure. In some embodiments, assembly  1430  includes one or more external stabilizers  1448  to, for example and without limitation, position assembly  1430  within a wellbore. External stabilizers  1448  may be, for example and without limitation, one or more radial protrusions. External stabilizers  1448  may be positioned and sized depending on the wellbore in which assembly  1430  is to be used. While drive shaft  1436  is shown as coupled with rotor  1440  via transmission  1438 , in some embodiments, drive shaft  1436  is coupled directly to rotor  1440 . Also, while drive shaft  1436  is shown as coupled with drill bit  1431  via bit shaft  1434 , in some embodiments drive shaft  1436  is coupled directly to drill bit  1431 .  FIG.  14 D  is a simplified schematic showing the basic arrangement and coupling between rotor  1440 , drive shaft  1436 , and drill bit  1431 , such that rotor  1440  drives shaft  1436 , which in-turn drives bit  1431 . 
     Drive shaft  1436  is coupled with bearing housing  1444  via one or more bearings  1452 , which are or include polycrystalline diamond elements. In some embodiments, bearings  1452  are radiused conical bearings, also referred to in the art as angle, taper, or cup/cone bearings, including cup portion  1450  coupled with cone portion  1454 .  FIGS.  15 A and  15 B  depict more detailed views of radiused conical bearings. With reference to  FIG.  15 A , radiused conical bearing  1552   a  includes cup portion  1550  and cone portion  1554 . As shown in  FIG.  15 A , cone portion  1554  includes bearing surface  1554 . Bearing surface  1556  has a plurality of polycrystalline diamond elements  1501  thereon, and extending therefrom. Each polycrystalline diamond element  1501  has an engagement surface  1513 , and cup portion  1550  has opposing engagement surface  1515 . Cup portion  1550  and cone portion  1554  may be generally annular and configured to contact at engagement surfaces  1513  and opposing engagement surface  1515 . Bearing surface  1556  and opposing engaging surface  1515  may be generally frustoconical in shape, such that bearing  1552   a  resists longitudinal or thrust loading as well as resisting radial loading between cup portion  1550  and cone portion  1554 , while allowing relative rotation between cup portion  1550  and cone portion  1554 . As such, bearing  1552   a  may act as both a radial and thrust bearing. Opposing engagement surface  1515  is or includes a diamond reactive material, such as steel.  FIG.  15 B  depicts bearing  1552   b , which is identical to bearing  1552   a , with the exception that polycrystalline diamond elements  1501  are positioned and extend from surface  1515 , as opposed to surface  1556 . In some embodiments, when engagement surfaces  1513  are engaged with opposing engagement surface ( 1515  or  1556 ), less than an entirety of each engagement surface  1513  is engaged with the opposing engagement surface. In some embodiments, less than 90%, less than 80%, less than 70%, less than 60%, less than 50%, less than 40%, or less than 30% of a surface area of each engagement surface  1513  is engaged with the opposing engagement surface. With reference to  FIGS.  15 C and  15 D , engagement surface  1513  of polycrystalline diamond element  1501  is shown, with contact area  1573   a  indicating the portion of the surface area of engagement surface  1513  that would be in contact with the opposing engagement surface in a bearing assembly, with the remainder of contact area  1573   b  of engagement surface  1513  not in contact with the opposing engagement surface. That is, contact area  1573   a  defines the area of contact of engagement surface  1513  after a bearing load is applied thereto. The contact area  1573   a  is, of course, for exemplary purposes only and is only intended to illustrate that the contact area  1573   a  is less than an entirety of available surface area on engagement surface  1513 . As shown, contact area  1573   a  may be or define a line contact or linear contact  1575 , such that when engagement surface  1513  is in sliding engagement with an opposing engagement surface, the sliding contact occurs along line contact  1575 . In some embodiments, engagement surface  1513  is in sliding engagement with an opposing engagement surface along contact area  1573   a , the opposing engagement surface rotates about an axis of rotation, and any imaginary line extending from and normal to contact area  1573  surface is at an angle relative to said axis of rotation. In some embodiments, engagement surface  1513  is in sliding contact with an opposing engagement surface through a substantial portion of its use profile. 
     In some embodiments, the opposing engagement surface does not have any polycrystalline diamond elements or any other bearing elements, and is a single, continuous surface. In some such embodiments, the engagement surfaces are multiple, discrete, spaced-apart surfaces that are each positioned to engage with the same opposing engagement surface. When engaged, in operation, the multiple, discrete, spaced-apart engagement surfaces may maintain constant contact with the single continuous, opposing engagement surface. In some embodiments, the sliding engagement between the engagement surfaces and the opposing engagement surface is non-lubricated. In some embodiments, the drive shaft has a rotational velocity, the engagement between the engagement surface and opposing engagement surface defines a contact area, and the contact area is independent of the rotational velocity of the drive shaft. In some such embodiments, the drive shaft has a variable rotational velocity, and the engagement surfaces follow an engagement path on the opposing engagement surface that is constant through the variable rotational velocities. 
     With reference to  FIGS.  14 A and  14 B , the cup portion shown and described in  FIGS.  15 A and  15 B  may be a portion of bearing housing  1444 , and the cone portion may be a portion of drive shaft  1436 . 
     With reference to  FIG.  14 C , bearings  1452   a  and  1452   b  may be positioned such that bearings  1452   a  and  1452   b  retain drive shaft  1436  both longitudinally and radially. In some embodiments, bearings  1452   a  and  1452   b  may be oriented in opposing directions, as shown by mounting orientations  1463   a  and  1463   b . Although described herein as utilizing two bearings  1452   a  and  1452   b , one having ordinary skill in the art with the benefit of this disclosure would understand that any number of bearings may be utilized without deviating from the scope of this disclosure.  FIG.  14 C  also depicts the effective bearing spread  1461 . 
       FIGS.  16 A- 16 G  depict portions of a drill string assembly without the outer housing thereon, including transmission  1638 , drive shaft  1636 , bit shaft  1634 , and drill bit  1631 . Drive shaft  1636  includes cone portions  1654 , each engaged with a plurality of polycrystalline diamond elements  1601 . While not shown, the polycrystalline diamond elements  1601  are coupled on a cup portion of a bearing housing (not shown) surrounding drive shaft  1636 , which may be the same as that shown in  FIGS.  14 A- 14 C , and are positioned on the bearing housing such that the polycrystalline diamond elements  1601  engaged with drive shaft  1636 . Each polycrystalline diamond element  1601  includes an engagement surface  1613 , for engagement with an opposing engagement surface of cone portions  1654 . As shown in  FIGS.  16 F and  16 G , the bearing element spacing  1663  between adjacent polycrystalline diamond elements  1601  is relatively narrow. As used herein, “bearing element spacing” refers to the distance between adjacent polycrystalline diamond elements. In some embodiments, the bearing element spacing  1663  is sufficiently narrow, such that bearing element spacing  1663  is less than a width  1665  of each adjacent polycrystalline diamond element  1601 . 
       FIGS.  17 A- 17 G  depict portions of a drill string assembly without the outer housing thereon. The portion of the drill string assembly shown in  FIGS.  17 A- 17 G  is identical to that of  FIGS.  16 A- 16 G , with the exception that the bearing element spacing in  FIGS.  17 A- 17 G  is greater than the bearing element spacing in  FIGS.  16 A- 16 G . The drill string assembly shown in  FIGS.  17 A- 17 G  includes transmission  1738 , drive shaft  1736 , bit shaft  1734 , and drill bit  1731 . Drive shaft  1736  includes cone portions  1754  engaged with a plurality of polycrystalline diamond elements  1701 , which are coupled on cup portion of a bearing housing (not shown), which may be the same as the bearing housing ( 1444 ) shown in  FIGS.  14 A- 14 C . Each polycrystalline diamond element  1701  includes an engagement surface  1713 , for engagement with an opposing engagement surface of cone portions  1754 . As shown in  FIGS.  17 F and  17 G , the bearing element spacing  1763  between adjacent polycrystalline diamond elements  1701  is wide relative to that of  FIGS.  16 F and  16 G . In some embodiments, the bearing element spacing  1763  is sufficiently wide, such that bearing element spacing  1763  is greater than a width  1765  of each adjacent polycrystalline diamond element  1701 . In some embodiments, bearing element spacing  1763  is at least 50%, at least 75%, at least 100%, at least 150%, at least 200%, or at least 300% greater than width  1765 . 
       FIGS.  18 A- 18 D  depict portions of the drive shaft and bearing elements thereof. Drive shaft  1836  is engaged with, at cup portion  1854 , a plurality of polycrystalline diamond elements  1801 . Each polycrystalline diamond element  1801  has an engagement surface  1813 , is supported via supports  1871  (e.g., tungsten carbide), and is coupled on a cone portion of a bearing housing,  1844 , which may be the same as the bearing housing ( 1444 ) shown in  FIGS.  14 A- 14 C . As shown, each engagement surface  1813  is planar. As shown in  FIG.  18 B , edge contact between the polycrystalline diamond and drive shaft  1836  is avoided. 
       FIG.  18 F  is a cross-sectional view of a portion of a drill string assembly substantially identical to that of  FIG.  18 B , with the exception that the drive shaft has a bearing ring positioned thereabout. 
     Bearing ring  1899  is coupled about the outer circumference of drive shaft  1836 , at cup portion  1854  of drive shaft  1836 . Bearing ring  1899  may be composed of the same material as drive shaft  1836 , or may be composed of a different material than drive shaft  1836 . In some embodiments bearing ring  1899  is composed of a material that has higher wear-resistance than the material that drive shaft  1836  is composed of. Bearing ring  1899  includes or defines opposing engagement surface  1815  for engagement with diamond engagement surface  1813 . In some embodiments, bearing ring  1899  is replaceable, such that after a certain degree of wear to bearing ring  1899 , bearing ring  1899  may be removed from drive shaft  1836  and a new and/or replacement bearing ring  1899  may then be coupled onto drive shaft  1836 . Thus, the use of bearing ring  1899  may increase the usable lifetime of drive shaft  1836  because the wear only or mostly occurs on the replaceable bearing ring  1899  and not on drive shaft  1836 . Bearing ring  1899  may encircle drive shaft  1836 . Bearing ring  1899  is not limited to the shape shown in  FIG.  18 F . While the bearing ring is shown and described as being coupled about the drive shaft and positioned for engagement with the polycrystalline diamond elements that are on the bearing housing, the bearing assembly disclosed herein is not limited to this particular arrangement. For example, the bearing ring may be coupled about an inner surface of the bearing housing and positioned for engagement with the polycrystalline diamond elements that are on the outer surface of the drive shaft. 
     As shown in  FIG.  18 F , the cone component, or a portion thereof, of the conical bearing assemblies can be discrete. That is, in some embodiments the cone component, or a portion thereof, is not integral with the mandrel or drive shaft, but is a discrete component that is coupled therewith. Such an arrangement provides for the opposing engagement surface to have selected or engineered properties that are different from that of the mandrel or drive shaft (e.g., being composed of a different material composition). Such selected or engineered properties may include superior performance properties, such as higher wear-resistance properties in comparison to the mandrel or drive shaft surface. Also, such an arrangement, in some embodiments, provides for ease of repair and replacement, as well as a lower cost for repair and replacement. 
       FIG.  18 G  is a cross-sectional view of a portion of a drill string assembly substantially identical to that of  FIG.  18 F , with the exception that the drive shaft and bearing housing each have a bearing ring positioned thereabout. As shown in  FIG.  18 G , both the cup and cone components of the conical bearing assemblies disclosed herein can be discrete components. That is, drive shaft  1836  includes bearing ring  1899   a  coupled thereabout (i.e., not integral with the drive shaft). Also, bearing housing  1844  includes bearing ring  1899   b  coupled therewith, and not integral therewith. Polycrystalline diamond element  1801  is coupled with bearing ring  1899   b , and includes diamond engagement surface  1813  engaged with opposing engagement surface  1815  of bearing ring  1899   a.    
     While the polycrystalline diamond element is shown and described as coupled with bearing ring  1899   b  on bearing housing  1844  in  FIG.  18 G , in other embodiments the polycrystalline diamond elements are coupled with bearing ring  1899   a  on drive shaft  1836 , such that the diamond engagement surface of the polycrystalline diamond elements engage with an opposing engagement surface of bearing ring  1899   b  (or of bearing housing  1844 , in embodiments where bearing ring  1899   b  is not used). In some embodiments, the polycrystalline diamond elements are coupled with the drive shaft  1836  (when bearing ring  1899   a  is not used), and the polycrystalline diamond elements are engage with an opposing engagement surface of bearing ring  1899   b  (or of bearing housing  1844 , in embodiments where bearing ring  1899   b  is not used). 
     In some embodiments, the bearing ring, the bearing housing, the drive shaft, or combinations thereof are composed, at least partially, of a “hardened material” as defined in U.S. patent Ser. No. 16/425,758, the entirety of which is incorporated herein by reference. 
     The bearing rings disclosed herein, including the embodiments shown in  FIGS.  18 F and  18 G , can be used as sacrificial surfaces and/or components. That is, the bearing rings can be used to bear loads such that the surfaces of the bearing rings are worn. Worn bearing rings can be then be replaced without having to replace an entirety of the bearing assembly. Thus, in some embodiments, the bearing rings can provide for easier and more cost-effective repair and/or replacement of the bearing assemblies disclosed herein. 
     Deployment of Additional Components 
     In some embodiments, the additional space on the drive shaft and/or in the bearing housing that is available due to increased spatial distance between adjacent polycrystalline diamond elements is utilized to deploy one or more additional downhole components on the drill string assembly. For example, in a drive shaft in accordance with  FIGS.  17 A- 17 G , space  1763  between adjacent polycrystalline diamond elements may be used to deploy additional downhole components on or within the associated bearing housing. 
     With reference to  FIGS.  19 A and  19 B , drive shaft  1936  is depicted engaged with a plurality of polycrystalline diamond elements  1901 , which are coupled with a bearing housing (not shown) that is the same or similar to the bearing housing ( 1444 ) shown in  FIGS.  14 A- 14 C . Spaces  1963 , positioned between adjacent polycrystalline diamond elements  1901 , may accommodate downhole components  2000 . While downhole components  2000  are shown positioned between each set of adjacent polycrystalline diamond elements  1901 , the drive shafts disclosed herein are not limited to including a downhole component between each set of adjacent polycrystalline diamond elements. In some embodiments, at least one space between adjacent polycrystalline diamond elements lacks a downhole component. In some embodiments, at least one space between adjacent polycrystalline diamond elements includes multiple downhole components. The downhole components may be embedded in, attached to, or otherwise coupled with the bearing housing. By incorporating downhole components where there would otherwise be bearing elements (e.g., polycrystalline diamond elements) or empty space, the available space on the bearing housing is more efficiently utilized. As such, the bearing housing may be incorporated with additional functionalities and capabilities that would otherwise not be available, or at least would otherwise occupy additional surface area on the bearing housing or other part of the drill string assembly. That is, spacing the polycrystalline diamond elements apart provides additional surface area on the drill string assembly that would otherwise not be available for use; thereby, increasing the potential functionality of the bearing housing and utilization of the space thereon. Each of the plurality of downhole components  2000  may be the same, or the plurality of downhole components  2000  may include multiple different downhole components. Each downhole component  2000  may be or include a mechanical downhole component, an electromechanical downhole component, a sensor, communication components, or recording components. For example, and without limitation, each downhole component  2000  may be or include a mechanical or electromechanical downhole component, such as a dynamic lateral pad (DLP), a dynamic lateral cutter (DLC), a mandrel driven generator, one or more batteries, an actuator, an extendable sensor (e.g., a sensor in face of a DLP), an extendable reamer blade, a caliper, or a rotary electrical connection, such as a slip ring, a rotary union, or a fiber optic rotary joint. Each downhole component  2000  may be or include a sensor, such as an azimuth sensor (gyroscope), an inclination sensor (inclinometer, gyroscope, magnometer), an accelerometer (to measure vibrations), an acoustic sensor, a gamma ray sensor (e.g., a scintillation crystal), a density sensor (deinsimeter), a resistivity sensor (electrodes, current generator), a temperature sensor (thermocouple), a pressure sensor (pressure transducers), a magnetic field sensor, a torque sensor, a weight on bit (WOB) sensor, a bending moments sensor (strain gage), an RPM sensor (e.g., accelerometers, tachometers), a linear displacement sensor (e.g., for use with calipers, pads), such as a linear variable differential transformer (LVDT) sensor, a porosity, lithology, permeability or rock strength sensor (e.g., piezoelectric transducers and receivers, such as for sonic and ultrasonic components, or a nuclear magnetic resonance sensor. Each downhole component  2000  may be or include a communication and/or recording component, such as a pulser, a data storage, a transmitter, or a microprocessor. As used herein DLPs and DLCs are those shown and described in U.S. Patent Publication No. 2017/70234071, the entirety of which is incorporated herein by reference and made a part of the present disclosure. 
     In some embodiments, the spacing between adjacent polycrystalline diamond elements can be selected and/or determined such that a desired downhole component can be positioned therein. For example, if it is know that a temperature sensor of a particular size is needed, the bearing assembly can be designed such that at least one spacing between two adjacent polycrystalline diamond elements is of sufficient size that the temperature sensor can be positioned therein, while still attaining sufficient bearing capacity for the particular drilling operation. Thus, in some embodiments the number of polycrystalline diamond elements in the bearing assembly is not maximized but is, instead, designed to be sufficient to bear expected load while also being spaced apart enough to provide space for additional downhole components. In some embodiments, adjacent polycrystalline diamond elements are spaced apart on the conical radial bearing to provide axial space on the drill string that would otherwise not be available for downhole components. In some embodiments, additional space for placement of downhole components on the drill string is formed by maintaining a standard bit-to-bend length while also using the bearing technology disclosed herein (e.g., having spaced apart adjacent polycrystalline diamond elements in accordance with  FIGS.  17 A- 17 G ) that only requires a portion of the standard bit-to-bend length. That is, the additional unneeded bit-to-bend length may be utilized for incorporation of additional downhole components onto the drill string. 
       FIG.  19 C  depicts additional space  1933  on bearing housing  1944  that may be available when using the conical bearing assemblies disclosed herein, with polycrystalline diamond elements  1901  arranged in a spaced-apart configuration, such as is shown in  FIGS.  17 A- 17 G .  FIG.  19 D  is identical to  FIG.  19 C , with the exception that additional downhole components  2000   a  and  2000   b  are positioned in additional spaces  1933 . 
     In some embodiments, the bearings disclosed herein may be sealed bearing packages. In other embodiments, the bearings disclosed herein may be unsealed bearing package. 
     One skilled in the art would understand that the drill string assembly and drilling motor disclosed herein is not limited to the particular arrangement of parts shown and described with reference to  FIGS.  14 A- 19 D . For example, while the drive shaft is described as being connected with the rotor, the drive shaft may be integral with and an extension of the rotor. Also, the drill bit is described as being connected with the drive shaft, the drill bit or a portion thereof may be integral with and an extension of the drive shaft. 
     One skilled in the art would understand that the features shown and described with respect to  FIGS.  1 - 13 B  with respect to rotors and stators can be combined with and/or applied to the drive shaft and bearing housing assembly described with reference to  FIGS.  14 A- 19 D . For example, the same or similar polycrystalline diamond elements may be used, and may be mounted in the same or similar way. Also, a drive shaft and bearing housing in accordance with  FIGS.  14 A- 19 D  may be coupled with a rotor and stator in accordance with  FIGS.  1 - 13 B . 
     Bearing Housing Antenna 
     In some embodiments, the bearing housing functions as an antenna for communication between the downhole components incorporated into or on the bearing housing and other components, such as other downhole components or surface components at the surface (i.e., not downhole). For example, the bearing housing, or a portion thereof, may be composed of an electrically conductive material that is capable of transmitting data signals to and/or from downhole components, such as a copper alloy. For example, the downhole components incorporated into or on the bearing housing may include a sensor that is coupled with the bearing housing such that sensor measurement data from sensor may be transmitted along bearing housing, or a portion thereof, when bearing housing is configured to function as an antenna. 
     Applications 
     The bearing assemblies disclosed herein may form a portion of a machine or other apparatus or system. In some such aspects, the proximal end of the stator may be connected to another component, such as a drill string or motor housing by threaded connection, welding, or other connection means as known in the art. In some aspects, if the bearing assembly is used in a downhole application, the distal end of the rotor may be augmented by a thrust bearing and may carry a threaded connection for the attachment of a drill bit, or the distal end of the rotor may be a drill bit directly formed on and/or positioned on the end of the mandrel of the rotor. The component connections are not limited to downhole applications, and can be applied to other applications, for example wind turbine energy generators, or marine applications. 
     Furthermore, discrete versions of the bearing assemblies described herein may be used in a broad array of other applications including, but not limited to, heavy equipment, automotive, turbines, transmissions, rail cars, computer hard drives, centrifuges, medical equipment, pumps, and motors. 
     In certain aspects, the bearing assemblies disclosed herein are suitable for deployment and use in harsh environments (e.g., downhole). In some such aspects, the bearing assemblies are less susceptible to fracture than bearing assemblies where a polycrystalline diamond engagement surface engages with another polycrystalline diamond engagement surface. In certain aspects, such harsh environment suitable radial bearings provide enhanced service value in comparison with bearing assemblies that include a polycrystalline diamond engagement surface engaged with another polycrystalline diamond engagement surface. Furthermore, the bearing assemblies disclosed herein may be capable of being spaced apart at greater distances that the spacings required when using bearing assemblies that include a polycrystalline diamond engagement surface engaged with another polycrystalline diamond engagement surface. 
     In certain applications, the bearing assemblies disclosed herein can act as a rotor catch, such as in downhole applications. 
     In lubricated environments, the bearing assemblies may benefit from the hydrodynamic effect of the lubricant creating a clearance between the moving and stationary elements of the bearing assembly. 
     Exemplary Testing 
     In an effort to develop a robust cam follower interface for use in Applicants&#39; previously referenced “Drilling Machine” of U.S. patent application Ser. No. 15/430,254 (the &#39;254 Application), Applicants designed and constructed an advanced test bench. The test bench employed a 200 RPM electric gearmotor driving a hard-faced ferrous rotor mandrel inside a hard-faced ferrous stator housing. The mandrel incorporated a non-hard faced offset camming cylinder midway along its length. The rotor/stator assembly was fed a circulating fluid through the use of a positive displacement pump. Candidate cam follower interface mechanisms were placed in contact and under load with the camming cylinder of the rotor mandrel. Employing the test bench, candidate interface mechanisms were tested for survivability and wear under loads ranging from 500 to 3000 lbf either in clear water or in sand laden drilling fluid. 
     The Applicants conducted testing of the ferrous camming cylinder in sliding contact with polished polycrystalline diamond surfaces without deleterious effects or apparent chemical interaction. Ferrous materials are attractive for bearing applications due to their ready availability, ease of forming and machining, higher elasticity, and lower cost than so called superhard materials. 
     The testing program conducted by the Applicants has established that, even at relatively high loads and high RPM speeds, a successful load interface between polycrystalline diamond and diamond reactive materials can be employed in bearing applications. 
     A key finding has been that, as long as polycrystalline diamond elements are not put into edge or point contact with diamond reactive materials, which, it is believed, could lead to machining and chemical interaction, the polycrystalline diamond can experience sliding contact with diamond reactive materials at the typical bearing loads and speeds called for in many applications. This unexpected and surprising success of the Applicants&#39; testing has led to the development of new high performance radial bearings. 
     The testing program included tests of a curved ferrous surface in high load facial linear area contact with planar polycrystalline diamond under rotation. This testing produced a slightly discolored Hertzian contact area on the face of the PDC about 0.250″ in width along the entire ½″ wide face of the polycrystalline diamond. The width of the contact area can be explained by the cam offset, vibration in the system and by slight deformation of the ferrous metal under load. It is estimated that the total contact area on the ½″ polycrystalline diamond element face, at any given point in time, is about 7%, or less, of the total area of the polycrystalline diamond element face. The configuration employed in the testing demonstrates that even a small surface area on the face of a polycrystalline diamond element can take significant load. 
     Additional testing of a spherical ferrous ball under load and rotation against a planar polycrystalline diamond face produced a small, approximately 0.030 diameter, discolored Hertzian contact area in the center of the polycrystalline diamond element. As in the contact explanation above, it is believed, without being bound by theory, that the diameter of the discoloration is a result of slight vibration in the test apparatus and by slight deformation of the ferrous metal under load. 
     Table 2, below, sets forth data summarizing the testing performed by the Applicants of various configurations of sliding interface. 
     
       
         
           
               
               
               
               
               
               
             
               
                   
               
               
                   
                   
                 RPM  
                 Surface Speed 
                 Loading 
                 Result 
               
               
                   
               
             
            
               
                   
               
            
           
           
               
               
               
               
               
               
               
            
               
                   
                 Tested Mechanism - Bearing Steel 
                   
                   
                   
                   
                   
               
               
                   
                 Ball in Alloy Steel Cup Against 
                   
                   
                   
                   
                   
               
               
                   
                 Rotating Steel Cam Surface 
                   
                   
                   
                   
                   
               
               
                 Test 1 
                 1.50 Ball Socket 
                 200 
                 1.13 m/s 
                 1200  
                 lb 
                 Abort after 3 minutes, ball is not rolling, heavy 
               
               
                   
                   
                   
                   
                   
                   
                 galling on ball and cup 
               
               
                 Test 2 
                 1.25 Ball Socket 
                 200 
                 1.13 m/s 
                 500 
                 lb 
                 Abort after 3 minutes, ball is not rolling, heavy 
               
               
                   
                   
                   
                   
                   
                   
                 galling on ball and cup 
               
               
                 Test 3 
                 Single Polished PDC 1.50 Ball 
                 200 
                 1.13 m/s 
                 700  
                 lb 
                 Ball is rolling, wear of steel on side wall of cup 
               
               
                   
                   
                   
                   
                   
                   
                 after 45 minutes 
               
               
                 Test 4 
                 Tripod Polished PDC 1.50 Ball 
                 200 
                 1.13 m/s 
                 700  
                 lb 
                 20 hr. test, little wear on Ball slight Hertzian 
               
               
                   
                   
                   
                   
                   
                   
                 trace on PDCs 
               
               
                   
                 Tested Mechanism - Planar PDC 
                   
                   
                   
                   
                   
               
               
                   
                 Rotating Steel Cam Surface 
                   
                   
                   
                   
                   
               
               
                 Test 5 
                 Single Polished PDC Slider 
                 200 
                 1.13 m/s 
                 900  
                 lb 
                 Ran 20 hours, PDC direct on steel cam in water.  
               
               
                   
                   
                   
                   
                   
                   
                 Slight, small Hertzian trace on PDC 
               
               
                 Test 6 
                 Single Polished PDC Slider 
                 200 
                 1.13 m/s 
                 900  
                 lb 
                 Varied load from zero, 4 hrs, good results in water. 
               
               
                   
                   
                   
                   
                   
                   
                 Slight, small Hertzian trace on PDC 
               
               
                 Test 7 
                 Single Polished PDC Slider 
                 200 
                 1.13 m/s 
                 2000  
                 lb 
                 Varied load from zero, 20 hrs, good results in water. 
               
               
                   
                   
                   
                   
                   
                   
                 Slight, small Hertzian trace on PDC 
               
               
                 Test 8 
                 Single Polished PDC Slider 
                 200 
                 1.13 m/s 
                 2000  
                 lb 
                 Drilling Fluid &amp; Sand test, 32+ hrs, good results. 
               
               
                   
                   
                   
                   
                   
                   
                 Slight, small Hertzian trace on PDC 
               
               
                 Test 9 
                 Single Polished PDC Slider 
                 200 
                 1.13 m/s 
                 3000  
                 lb 
                 Mud test at 3000 lbf, 10 hrs, good results. 
               
               
                   
                   
                   
                   
                   
                   
                 Slight, small Hertzian trace on PDC 
               
               
                 Test 10 
                 Single Polished vs Single 
                 200 
                 1.13 m/s 
                 1100 
                 lb 
                 Mud test, 2 hours each, Unpolished coefficient of  
               
               
                   
                 Unpolished 
                   
                   
                   
                   
                 friction at least 50% higher by ampere measurement 
               
               
                   
               
            
           
         
       
     
     Tests 1 and 2 summarize failed tests of individual steel balls rolling in a steel cup under load. Test 3 summarizes the results of a more successful test of a steel ball supported by a single polished PDC element in a steel cup. Test 4 summarizes a very successful test of a single steel ball supported by an array of three polished polycrystalline diamond elements in a steel cup. Tests 5 through 9 summarize increasingly rigorous tests each of a single polished polycrystalline diamond element in sliding contact with a rotating ferrous cam surface. Test 10 summarizes a comparative test of a single polished polycrystalline diamond element versus a single unpolished polycrystalline diamond element, each in sliding contact with a rotating ferrous cam surface. The final test shows a significant increase in coefficient of friction when the unpolished polycrystalline diamond element was used. The conditions and results presented in Table 2 are emblematic of the potential use of polycrystalline diamond on diamond reactive material and are not to be considered limiting or fully encompassing of the technology of the application. 
     Testing Conclusions 
     It was found that applications of polycrystalline diamond elements in a radial bearing can employ far less than the full face of the elements and still take significant load. This finding means effective polycrystalline diamond element containing radial bearings can be designed and manufactured without the need for full face contact of the polycrystalline diamond elements with the opposing surface. Employing this finding in the technology of the present application means it is possible to manufacture radial bearings with far less processing of the polycrystalline diamond elements used and substantially reducing the risk of edge clashing, or of the instigation of machining of a diamond reactive material opposing surface. 
     Without being bound by theory, in operation, running a cam and cam follower in a liquid cooled, lubricated environment, allows for higher speeds and loads to be attained without commencing a thermo-chemical reaction. Further, a polycrystalline diamond face that has been polished, notably, provides a lower thermo-chemical response. 
     From the descriptions and figures provided above it can readily be understood that the bearing assembly technology of the present application may be employed in a broad spectrum of applications, including those in downhole environments. The technology provided herein additionally has broad application to other industrial applications. 
     Furthermore, while shown and described in relation to engagement between surfaces in a radial bearing assembly, one skilled in the art would understand that the present disclosure is not limited to this particular application and that the concepts disclosed herein may be applied to the engagement between any diamond reactive material surface that is engaged with the surface of a diamond material. 
     EMBODIMENTS 
     Certain embodiments will now be described. 
     Embodiment 1. A downhole drilling tool for use in a downhole drill string, the downhole drilling tool comprising: a rotor movably coupled within a stator; a drive shaft movably coupled within a bearing housing, the drive shaft having a first end coupled with the rotor and a second end coupled with a drill bit; a bearing assembly interfacing engagement between the drive shaft and the bearing housing, the bearing assembly comprising: a plurality of spaced-apart polycrystalline diamond elements, wherein each polycrystalline diamond elements has an engagement surface; and an opposing engagement surface comprising a metal that is softer than tungsten carbide, wherein the opposing engagement surface is movably engaged with each of the engagement surfaces; wherein the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing, or wherein the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft. 
     Embodiment 2. The downhole drilling tool of embodiment 1, wherein the bearing assembly comprises a first bearing assembly interfacing engagement between the drive shaft and the bearing housing at the first end of the drive shaft, and a second bearing assembly interfacing engagement between the drive shaft and the bearing housing at the second end of the drive shaft. 
     Embodiment 3. The downhole drilling tool of embodiment 1 or 2, wherein the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing. 
     Embodiment 4. The downhole drilling tool of embodiment 1 or 2, wherein the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft. 
     Embodiment 5. The downhole drilling tool of embodiment 2, wherein the first and second bearing assemblies are radiused conical bearings, each including a cup portion that is coupled with a cone portion. 
     Embodiment 6. The downhole drilling tool of embodiment 5, wherein the cup portion is a portion of the bearing housing and the cone portion is a portion of the drive shaft. 
     Embodiment 7. The downhole drilling tool of embodiment 6, wherein opposing engagement surface is a surface on the cup portion, and wherein the plurality of polycrystalline diamond elements are on a surface of the cone portion. 
     Embodiment 8. The downhole drilling tool of embodiment 6, wherein opposing engagement surface is a surface on the cone portion, and wherein the plurality of polycrystalline diamond elements are on a surface of the cup portion. 
     Embodiment 9. The downhole drilling tool of any of embodiments 1 to 8, wherein the opposing engagement surface is a single, continuous surface, and wherein the engagement surfaces are multiple, discrete, spaced-apart surfaces that are positioned to engage with the opposing engagement surface. 
     Embodiment 10. The downhole drilling tool of embodiment 2, wherein the first and second bearing assemblies bear both radial and thrust loads. 
     Embodiment 11. The downhole drilling tool of embodiment 2, wherein the first and second bearing assemblies are oriented in opposing directions. 
     Embodiment 12. The downhole drilling tool of any of embodiments 1 to 11, wherein a bearing element spacing between adjacent polycrystalline diamond elements is greater than a width of each of the adjacent polycrystalline diamond elements. 
     Embodiment 13. The downhole drilling tool of any of embodiments 1 to 12, wherein the engagement surface of each polycrystalline diamond element is a planar surface. 
     Embodiment 14. The downhole drilling tool of any of embodiments 1 to 13, wherein the engagement surface of each polycrystalline diamond element has a surface finish that is equal to or less than 10 μin. 
     Embodiment 15. The downhole drilling tool of any of embodiments 1 to 14, wherein a contact area between each engagement surface and the opposing engagement surface is less than 75% of a total surface area of that engagement surface. 
     Embodiment 16. The downhole drilling tool of any of embodiments 1 to 15, wherein the metal of the opposing engagement surface is a diamond reactive metal. 
     Embodiment 17. The downhole drilling tool of any of embodiments 1 to 16, wherein the metal of the opposing engagement surface comprises iron or an alloy thereof, cobalt or an alloy thereof, nickel or an alloy thereof, ruthenium or an alloy thereof, rhodium or an alloy thereof, palladium or an alloy thereof, chromium or an alloy thereof, manganese or an alloy thereof, copper or an alloy thereof; titanium or an alloy thereof; or tantalum or an alloy thereof. 
     Embodiment 18. The downhole drilling tool of any of embodiments 1 to 17, further comprising one or more downhole components positioned in a space between two adjacent polycrystalline diamond elements, positioned in on or within the bearing housing, or combinations thereof. 
     Embodiment 19. The downhole drilling tool of embodiment 18, wherein the downhole components comprise a mechanical or an electromechanical downhole component. 
     Embodiment 20. The downhole drilling tool of embodiment 19, wherein the downhole components comprise a dynamic lateral pad (DLP), a dynamic lateral cutter (DLC), a mandrel driven generator, one or more batteries, an actuator, a sensor, a reamer blade, a caliper, a rotary electrical connection, or combinations thereof. 
     Embodiment 21. The downhole drilling tool of embodiment 20, wherein the downhole components comprise a slip ring, a rotary union, a fiber optic rotary joint, or combinations thereof. 
     Embodiment 22. The downhole drilling tool of embodiment 18, wherein the downhole components comprise a sensor. 
     Embodiment 23. The downhole drilling tool of embodiment 22, wherein the downhole components comprise an azimuth sensor, an inclination sensor, an accelerometer, an acoustic sensor, a gamma ray sensor, a density sensor, a resistivity sensor, a temperature sensor, a pressure sensor, a magnetic field sensor, a torque sensor, a weight on bit (WOB) sensor, a bending moments sensor, an RPM sensor, a linear displacement sensor, one or more sensors for detecting porosity sensor, one or more sensors for detecting permeability, a piezoelectric transducer and receiver, a nuclear magnetic resonance sensor, or combinations thereof. 
     Embodiment 24. The downhole drilling tool of embodiment 18, wherein the downhole components comprise a communication or recording component. 
     Embodiment 25. The downhole drilling tool of embodiment 24, wherein the downhole components comprises a pulser, a data storage, a transmitter, a microprocessor, or combinations thereof. 
     Embodiment 26. A bearing assembly for use in a downhole drill string, the bearing assembly comprising: a drive shaft movably coupled within a bearing housing, the drive shaft having a first end and a second end; a bearing assembly interfacing engagement between the drive shaft and the bearing housing the bearing assembly comprising: a plurality of polycrystalline diamond elements, wherein each polycrystalline diamond element has an engagement surface; and an opposing engagement surface comprising a metal that is softer than tungsten carbide, wherein the opposing engagement surface is movably engaged with each of the engagement surfaces; wherein the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing, or wherein the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft. 
     Embodiment 27. A method of bearing radial and thrust load in a drill string bearing assembly, the method comprising: coupling a drive shaft within a bearing housing, the drive shaft having a first end and a second end, wherein coupling the drive shaft within the bearing housing includes interfacing engagement between the drive shaft and the bearing housing with a bearing assembly, the bearing assembly comprising: a plurality of polycrystalline diamond elements, wherein each polycrystalline diamond elements has an engagement surface; and an opposing engagement surface comprising a metal that is softer than tungsten carbide, wherein the opposing engagement surface is movably engaged with each of the engagement surfaces; wherein the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing housing, or wherein the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the drive shaft; and bearing radial and thrust loads on the drive shaft with the bearing assembly. 
     Embodiment 28. The method of embodiment 27, wherein interfacing engagement between the drive shaft and the bearing housing with the bearing assembly includes continuously engaging the opposing engagement surface with each of the engagement surfaces, wherein the opposing engagement surface is a single, continuous surface, and wherein the engagement surfaces are multiple, discrete, spaced-apart surfaces that are positioned to engage with the opposing engagement surface. 
     Embodiment 29. The method of embodiment 27 or 28, further comprising positioning the plurality of polycrystalline diamond elements such that a bearing element spacing between adjacent polycrystalline diamond elements is greater than a width of each of the adjacent polycrystalline diamond elements. 
     Embodiment 30. The method of any of embodiments 27 to 29, wherein interfacing engagement between the drive shaft and the bearing housing with the bearing assembly includes engaging a contact area of each engagement surface with the opposing engagement surface, wherein the contact area of each engagement surface is less than 75% of a total surface area of that engagement surface. 
     Embodiment 31. The method of any of embodiments 27 to 30, wherein the metal of the opposing engagement surface is a diamond reactive metal, and wherein the method includes polishing the engagement surfaces to have a surface finish that is equal to or less than 10 pin. 
     Embodiment 32. The method of any of embodiments 27 to 31, further comprising positioning a downhole component in a space between two adjacent polycrystalline diamond elements. 
     Embodiment 33. A method of designing a bearing assembly for a drive shaft and bearing housing of a downhole drilling tool, wherein the bearing assembly includes polycrystalline diamond elements, each polycrystalline diamond element including an engagement surface in sliding engagement with an opposing engagement surface, the opposing engagement surface includes a metal that is softer than tungsten carbide, the method comprising: determining if a maximum sliding speed of the drive shaft and the bearing housing is less than a preset limit; if the maximum sliding speed is less than the preset limit, selecting a configuration of the bearing assembly within the drive shaft and bearing housing; calculating a maximum contact pressure per polycrystalline diamond element based on a selected number of polycrystalline diamond elements in the selected configuration of the bearing assembly within the drive shaft and bearing housing, and based on anticipated load, wherein the calculated maximum contact pressure is optionally multiplied by a safety factor; determining if the calculated maximum contact pressure, optionally multiplied by the safety factor, is below a preset maximum allowable pressure; wherein, if the calculated maximum contact pressure is determined to be below the preset maximum allowable pressure, deploying at least a minimum number of the polycrystalline diamond elements on the selected configuration of the bearing assembly within the drive shaft and bearing housing, and, if the number of the polycrystalline diamond elements fit on the selected configuration of the bearing assembly within the drive shaft and bearing housing, making the bearing assembly for the drive shaft and bearing housing. 
     Embodiment 34. The method of embodiment 33, wherein selecting the configuration of the bearing assembly within the drive shaft and bearing housing includes selecting a configuration that has at least one space between adjacent polycrystalline diamond elements that is of a sufficient size such that a downhole component is positionable in the space between the adjacent polycrystalline diamond elements or is positionable on or in the bearing housing. 
     Embodiment 35. The method of embodiment 32, further comprising transmitting data to or from the downhole component via at least a portion of the bearing housing that is an antenna. 
     Embodiment 36. The method of embodiment 27, further comprising: positioning a bearing ring about the bearing housing, wherein the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the bearing ring; or positioning a bearing ring about the drive shaft, wherein the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the bearing ring. 
     Embodiment 37. The downhole tool of embodiment 1, further comprising a bearing ring; and wherein: the plurality of polycrystalline diamond elements are coupled with the drive shaft, the bearing ring is coupled with the bearing housing, and the opposing engagement surface is a surface on the bearing ring; or the plurality of polycrystalline diamond elements are coupled with the bearing housing, the bearing ring is coupled with the drive shaft, and the opposing engagement surface is a surface on the bearing ring. 
     Embodiment 38. The downhole tool of embodiment 1, wherein the downhole tool is a downhole drilling motor. 
     Embodiment 39. The method of embodiment 37, further comprising, after the surface on the bearing ring is worn, replacing the bearing ring with a replacement bearing ring, including: positioning the replacement bearing ring about the bearing housing, wherein the plurality of polycrystalline diamond elements are coupled with the drive shaft and the opposing engagement surface is a surface on the replacement bearing ring; or positioning the replacement bearing ring about the drive shaft, wherein the plurality of polycrystalline diamond elements are coupled with the bearing housing and the opposing engagement surface is a surface on the replacement bearing ring. 
     Although the present embodiments and advantages have been described in detail, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the disclosure. Moreover, the scope of the present application is not intended to be limited to the particular embodiments of the process, machine, manufacture, composition of matter, means, methods and steps described in the specification. As one of ordinary skill in the art will readily appreciate from the disclosure, processes, machines, manufacture, compositions of matter, means, methods, or steps, presently existing or later to be developed that perform substantially the same function or achieve substantially the same result as the corresponding embodiments described herein may be utilized according to the present disclosure. Accordingly, the appended claims are intended to include within their scope such processes, machines, manufacture, compositions of matter, means, methods, or steps.