BEARINGS FOR WELL DOWN TOOLS, WELL DOWN TOOLS INCORPORATING THESE BEARINGS AND COOLING METHODS OF TH

专利摘要:
bearings for well tools below, well tools below incorporating these bearings and methods of cooling these bearings for well tools below including a first bearing member and a second bearing member, at least one of the first and second bearing members having a channel formed there. Cooling methods for well tool bearings below comprise the flow of a fluid in a channel formed in at least one bearing member. heat is transferred from at least one bearing member to the fluid. the fluid is allowed to flow from at least one bearing member.
公开号:BR112013007826B1
申请号:R112013007826-0
申请日:2011-09-30
公开日:2020-09-29
发明作者:Alejandro Flores；Aaron J.Dick；Chih Lin；John F. Bradford；Louise F. Van Staden；Gregory B. Swanepoel；Clement D. Van Der Riet；Siu Wah Wai；Dragan Vukovic；Klaus Tank
申请人:Baker Hughes Incorporated；Element Six Limited；
IPC主号:

专利说明:

PRIORITY CLAIM
This order claims the benefit of the filing date of U.S. Provisional Order Serial No. 61 / 388,998, filed on October 1, 2010, for BEARINGS FOR DOWNHOLE TOOLS, DOWNHOLE TOOLS INCORPORATING SUCH BEARINGS, AND METHODS OF COOLING SUCH BEARINGS. TECHNICAL FIELD
The embodiments of the present invention generally relate to bearing systems for ground drilling tools and methods of cooling those bearing systems and, more specifically, to cooling down well tool components using direct contact with a drilling fluid. BACKGROUND
Roller cone drill bits for drilling terrain formations conventionally have roller cones mounted on bearing pins. As the drill rotates, the roller cones rotate on their respective bearing pins. The teeth formed in the roller cones or inserts arranged in recesses in the roller cones impact and crush the underlying ground formation material to form an uncoated well hole. Conventionally, the bearings are arranged between the roller cones and the bearing pins to withstand the forces to which the roller cones are subjected while the drill is rotated under an applied axial force, commonly called weight on the drill, while allowing the cone rollers rotate on the bearing pins. The high forces present during drilling cause friction in the rotating components and generate heat, which can cause the bearing to deteriorate. A deterioration of the bearing can cause failure, resulting in a time-consuming and costly removal and replacement of the uncoated well hole drill.
Friction or sleeve bearings used in roller cone drills can be either sealed or open bearings. Conventionally sealed bearing systems include a lubricant reservoir for supplying lubricant, such as a bearing grease, to the bearing surfaces between the roller cones and the bearing pins. A pressure compensator can be used to equalize the lubricant pressure with the fluid pressure in the well bore. Open bearing systems, in contrast, have no seals or bearing grease. Open bearing systems use a drilling fluid, such as a drilling mud, for cooling and lubricating the bearings. EXPOSURE OF THE INVENTION
In some embodiments, the well tool bearing housings below comprise a first bearing member comprising an outer contact surface defining an outer diameter. A second bearing member comprises an inner contact surface that defines an inner diameter, the inner diameter of the second bearing member being greater than the outer diameter of the first bearing member and the inner contact surface of the second bearing member being in sliding contact with the external contact surface of the first bearing member at an interface. At least one of the first and second bearing members comprises at least one channel formed in a portion of at least one of the first and second bearing members.
In additional embodiments, the well tool bearing housings below comprise a first bearing member comprising a lower contact surface. A second bearing member comprises an upper contact surface, wherein the first bearing member confines against the second bearing member at an interface between the lower contact surface and the upper contact surface, the first and second contact members. bearings are configured to rotate in a sliding way in relation to each other. At least one tooth the first and second bearing members comprises at least one channel extending and is configured to provide a flow path through at least one of the first and second bearing members.
In further embodiments, the well tool bearing housings below comprise a first bearing member comprising a generally cylindrical portion and a generally annular portion connected to the generally cylindrical portion and extending radially outwardly at one end of the cylindrical portion. The generally cylindrical portion comprises an outer contact surface defining an intermediate outer diameter of the first bearing member and the generally annular portion comprises a generally annular lower contact surface, the lower contact surface intercepting the outer contact surface and the contact surfaces lower and outer forming a substantially continuous surface. A second bearing member comprises a generally cylindrical portion and a generally annular portion connected to the generally cylindrical portion and extending radially outwardly at one end of the cylindrical portion. The generally cylindrical portion comprises an inner contact surface defining an inner diameter of the second bearing member and the generally annular portion comprises an upper generally annular contact surface, the upper contact surface intersecting the inner contact surface and the 10 contact surfaces. upper and inner contact forming a substantially continuous surface relying on the substantially continuous surface formed by the lower and external contact surfaces of the first bearing member. At least one channel is formed in the first bearing member or the second bearing member.
In yet other embodiments, the methods of cooling well tool bearings below include the flow of a fluid in a channel formed in at least one bearing member. Heat is transferred from 20 of at least one bearing member to the fluid. The fluid is fluid away from at least one bearing member. BRIEF DESCRIPTION OF THE DRAWINGS
Although the specification is concluded with claims particularly highlighting and distinctly claiming what are considered to be modalities of the present invention, various features and advantages of the modalities exposed can be more readily assessed from the following description, when read in conjunction with the drawings associated, in which: figure 1 is a perspective view of a roller cone drill including a bearing system; figure 2 is a partial perspective sectional view of another roller cone bit similar to the roller cone bit of figure 1, showing an embodiment of a 5-bearing system; figure 3A is an enlarged cross-sectional view of the bearing system of figure 2; Figure 3B is an enlarged cross-sectional view of another embodiment of a bearing system; figures 4A to 4Q are seen in perspective of modalities of gloved bearing members; figures 5A to 51 are seen in perspective of modalities of cone bearing members; figures 6A to 6H are viewed in perspective of modalities of anchor bearing members; Figures 7A and 7B are viewed in perspective of hybrid and radial anchor and radial bearing members; and figure 8 is a cross-sectional view of another embodiment of a bearing system used in a downhole motor; and figures 9A to 9D are seen in cross-section and plane of channels that can be formed in bearing members. MODE (S) FOR CARRYING OUT THE INVENTION
The illustrations presented are not meant to be real views of any particular material or device, but are merely idealized representations that are used to describe the modalities exposed. Thus, the drawings are not necessarily to scale and the relative dimensions may have been exaggerated in the name of clarity. Additionally, common elements between figures may retain the same numerical designation or a similar one.
The modalities of the present exhibition include bearing systems having channels formed there for the provision of pathways for fluids. In some embodiments, a roller cone drill may include bearing systems having channels formed there. In other embodiments, methods of cooling bearing systems include the flow of a fluid through a bearing member using channels of the bearing member.
Although some of the modalities of the present exhibition are described as being used and employed in roller cone drills, people of ordinary skill in the art will understand that the present invention can be used in any terrain drilling tool in which the use of a bearing is desirable. Accordingly, the terms "roller cone drill", "ground drill bit" and "ground drill tool", as used here, mean and include any type of drill or tool employing a rotating component with respect to another component in which the component is assembled and used for drilling during the formation or widening of a well hole in an underground formation and include, for example, roller cone drills, core drills, eccentric drills, drills with two centers, reamers, laminators, hybrid drills using fixed and rotary cutting structures, and other drill bits and tools using rotating components, as known in the art.
Furthermore, the modalities of the present invention can be employed in downhole tools that do not directly fit, shear, cut or crush the underlying ground formation, but still include a rotating component with respect to another component in which the component is mounted. Therefore, the term "downhole tool", as used here, means and includes any type of downhole tool employing a rotary one with respect to another component on which the component is mounted, regardless of whether the downhole tool is used. directly fit, shear, cut or crush the underlying ground formation, such as, for example, Moinean "mud" engines, turbine engines, submersible pumps, roller cone drills, core drills, eccentric drills , two-core drills, reamers, laminators, hybrid drills using fixed and rotary cutting structures, and other drill bits and tools using rotating components, as known in the art.
As used here, the term "drilling fluid" means and includes any type of fluid used to remove cuts from a terrain formation during drilling. For example, a drilling fluid can be a gas, a liquid or a combination of gaseous and liquid phases, such as compressed air, water or a polymer. Drilling fluids specifically include, without limitation, liquids loaded with solids, including a water-based mud, an oil-based mud and a synthetic-based mud. Any combination of the precedent is also encompassed by the term "drilling fluid".
As used here, the term "working fluid" means and includes any fluid residing at an interface between two bearing members, which can serve for lubrication and cooling of the bearing members during a rotation of one or both bearing members with respect to each other. The working fluids include, without limitation, conventional lubricants used in a sealed bearing system, as well as drilling mud and other borehole fluids, which can enter the interface of an open bearing system.
Figure 1 is a perspective view of a rotary field drill bit 100 including a bearing system 128 (see figures 2 and 3) according to an embodiment. Drill bit 100 described as a roller cone drill includes a drill body 102 that has three arms 104 hanging from body 102. A roller cone 106 is rotatably mounted on a bearing pin 116 (see figures 2 and 3) on each of the arms 104. Each roller cone 106 can comprise a plurality of teeth 108, which, as shown, can be formed into roller cones 106 during the manufacture thereof, and are commonly called drills "rolling tooth". Drill bit 100 includes a threaded section 110 at its upper end for connection to a drill string (not shown).
Figure 2 is a partial sectional perspective view of a rotary drill bit for land drilling 100 'similar to drill bit 100 of Figure 1. Drill bit 100' has an inner plenum 112 that extends through the body drill bits 102 and fluid passages 114 extending from plenum 112 to a bearing system 128. The bearing system 128 includes a primary bearing 121 and secondary bearings 127. During drilling, a drilling fluid can be pumped through the center of the drill string, through the plenum 112 and the fluid passages 114 and to the bearing system 128. The drill bit 100 'also includes arms 104 hanging from the body 102. The roller cones 106 are mounted rotating on bearing pins 116, although a bearing pin 116 is described without the roller cone 106, in the name of clarity. The bearing pin 116 includes the bearing system 128, which is described more fully hereinafter. As described in figure 2, the drill bit 100 'employs preformed inserts 108', which are conventionally cemented tungsten carbide and which may have a polycrystalline superabrasive coating (not shown) at the distal ends thereof or may include interdispersed superabrasive particles among the tungsten carbide particles and a metal matrix, known in the art as impregnated inserts.
Figure 3A is an enlarged cross-sectional view of the bearing system 128 of figure 2. The bearing system 128 includes ball bearings 118, a ball plug or retainer 120, a primary bearing 121 comprising a primary cone bearing member 122 and a primary sleeve bearing member 124, and secondary bearings 127 comprising secondary cone bearing members 123 and secondary sleeve bearing members 125. The primary bearing 121 is configured to withstand radial loads, while secondary bearings 127 are configured to withstand radial loads and axial loads, respectively.
During assembly of the bearing system, a roller cone 106 including a primary cone bearing member 122 and secondary cone bearing members 123 is placed in close proximity to and positioned on a bearing pin 116 including a sleeve bearing member primary 124 and secondary sleeve bearing members 125, so that the bearing pin 116 is inserted into the roller cone 106. The primary cone bearing member 122 is positioned on and at least substantially surrounds the primary sleeve bearing member 124, so that an internal contact surface of the primary cone bearing member 122 adjoins an external contact surface of the primary sleeve bearing member 124 at a first interface 126. In other words, the sleeve bearing member primary 124 is housed concentrically in the primary cone bearing member 122, so that the outer contact surface of the primary sleeve bearing member 124 is close to the internal contact surface that of the primary cone bearing member 122. The primary cone bearing member 122 and the primary sleeve bearing member 124 are configured to slide in relation to each other, as the roller cone 106 rotates around the bearing pin 116.
Secondary cone bearing members 123 adjoin secondary sleeve bearing members 125 on second interfaces 129. Like primary bearings 121, one of the secondary cone bearing members 123 is received over one of the secondary sleeve bearing members 125, an external contact surface of the secondary sleeve bearing member 125 abuts an internal contact surface of the secondary cone bearing member. Thus, one of the secondary bearings 127 can be configured to support radial loads in a similar manner to the primary bearing 121. Another of the secondary bearings 127 may include another secondary cone bearing member 123 that has an upper contact surface relying on a lower contact surface of another secondary sleeve bearing member 125. Thus, the other of secondary bearings 127 can be configured to support axial loads. The secondary cone bearing members 123 are configured to rotate slidably against the secondary sleeve bearing members 125, as the roller cone 106 rotates around the bearing pin 116.
With reference to figure 3B, an enlarged cross-sectional view of another embodiment of a bearing system 128 'is shown. The bearing system 128 'may include a single secondary bearing 127' configured to withstand radial and axial loads, instead of the separate secondary bearings 127 shown in figure 3A. Like this,
Returning to figure 3A, ball bearings 118 are inserted into a ball bearing bearing and ball plug 120 inserted to retain ball bearings 118 in the ball bearing. The ball plug can be held in place using, for example, a solder or a braze. As the drill bit 100 '(see figure 2) rotates, the roller cone 106 rotates around the bearing pin 116, and the inserts 108', described in figure 3A as discrete cutting elements received in recesses on the surface of the roller cone 106, impact and crush the underlying ground formation.
The forces acting on the bearing system 128 as the roller cone 106 collides with the formation of the underlying terrain causes heat generation and accumulation, which can degrade the bearing system 128 and cause the roller cone 106 to grab, eventually causing the 100 'drill bit to fail. As per the 10-bit drill wheel, a drilling fluid is pumped into the center of the drill string through fluid passages 114 to bearing system 128 for lubrication and cooling of bearing system 128 as the drilling fluid passes through of the bearing system. In order to facilitate lubrication at interfaces 126 and 129 between the primary and secondary cone bearing members 122 and 123 and the primary and secondary sleeve bearing members 124 and 125, preferably, and assist in the removal of heat, at least one channel it can be provided in the primary cone bearing member 20, in the secondary cone bearing members 123, in the primary sleeve bearing member 124, in the secondary sleeve bearing members 125 or in any combination thereof.
Figures 4A to 4Q illustrate various embodiments of primary glove bearing members 124. For example, figure 4 describes an embodiment of a primary glove bearing member 124. The primary glove bearing member 124 may include a first side surface. 130 and a second side surface 132 opposite the first side surface 130. Although the first and second opposite side surfaces 130 and 132 are described as being substantially parallel and flat, the opposite side surfaces 130 and 132 can have any shape or configuration, such as not parallel and flat, arched or other configurations. Opposite side surfaces 130 and 132 define at least one substantially annular cross-section of primary sleeve bearing member 124. An outer contact surface 134 defines an outer diameter 138 of primary sleeve bearing member 124, and an inner surface 136 defines an inner diameter 140 of the primary glove bearing member 124. The outer contact surface 134 and the inner surface 136 intersect and are at least substantially perpendicular to the opposite side surfaces 130 and 132, so that the primary glove bearing member 124 has a generally cylindrical shape, as shown.
The channels 142 can be formed on the outer contact surface 134 of the primary sleeve bearing member 124 to provide a fluid path between the opposite side surfaces 130 and 132 of the primary sleeve bearing member 124, in some embodiments. The channels 142 can comprise linear grooves that extend at least substantially parallel to a central geometric axis of the primary sleeve bearing member 124 and can be distributed in a substantially uniform circumferential pattern around the outer contact surface 134. According to a The perforation is pumped through the bearing system 128, channels 142 can allow for improved cooling of the primary sleeve bearing member 124 and other components in the vicinity of them and may provide additional lubrication for the 134 of the primary sleeve bearing member 124 by providing pathways for the drilling fluid to flow from an opposite side surface 130 to the other side surface 132.
As shown in Figure 4B, the channels 142 formed in the primary sleeve bearing member 124 can be distributed around the outer contact surface 134 in a non-uniform circumferential pattern. For example, the angular distance between the two bottom channels 142 in the primary sleeve bearing member 124 shown in Figure 4B is greater than the angular distance between any other two adjacent channels 142. By increasing the angular distance between adjacent channels 142, the contact area between surfaces of the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figures 3A and 3B) is also increased. Furthermore, the total number of channels 142 shown in figure 4B is decreased from the number of channels 142 described in figure 4A, because the angular distance between adjacent channels is increased. Accordingly, persons of ordinary skill in the art will understand that any number of channels 142 may be located on the outer contact surface 134 of the primary sleeve bearing member 124, and that those channels 142 may be spaced in uniform or non-uniform patterns across around the primary glove bearing member 124.
As described in Figure 4C, the channels 142 formed in the primary sleeve bearing member 124 may comprise grooves that extend in a direction that is not parallel to a central geometric axis of the primary sleeve bearing member 124. For example, the channels 142 formed in the primary sleeve bearing member 124 described in figure 4C comprise grooves that extend helically in the outer contact surface 134 of the primary sleeve bearing member 124. The contact area between the primary cone bearing member 122 (see figures 3A and 3B) and the primary sleeve bearing member 124 when the channels 142 comprise helically extending grooves 10 cannot be as large as the contact area between the primary cone bearing member 122 (see figures 3A and 3B) and the primary sleeve bearing member 124, when the channels 142 comprise grooves extending in a direction parallel to a central geometric axis of the luv bearing member 15 a primary 124. As the primary cone bearing member 122 (see figures 3A and 3B) rotates slidingly around the primary sleeve bearing member 124, however, the contact area between the two may remain at least substantially constant or continuous 20, when channels 142 comprise helically extending grooves, due to the circumferential superposition of opposite channels 142 in embodiments in which channels 142 comprising helically extending grooves are formed in each of the member of 25 primary sleeve bearing 124 and primary cone bearing member 122 (see figures 5C and 5D). In contrast, the contact area between the primary cone bearing member 122 (see figures 3A and 3B) and the primary sleeve bearing member 124 as per the primary cone bearing member 30 122 (see figures 3A and 3B ) rotating around the primary sleeve bearing member 124 may vary intermittently, when the channels 142 comprise grooves extending in a direction parallel to a central geometric axis of the primary sleeve bearing member 124, due to an intermittent superposition of opposite channels 142 in embodiments wherein channels 142 comprising helically extending grooves are formed in each of the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figure 5A). In addition, channels 142 comprising helically extending grooves can cause the working fluid to take a longer time to travel between the opposite side surfaces 130 and 132 of the primary sleeve bearing member 124, compared to channels 142 grooves extending in a direction parallel to a central geometric axis, allowing channels 142 comprising helically extending grooves to dissipate heat more effectively.
As shown in figure 4D, the helix angle of channels 142 comprising helically extending grooves in the outer contact surface 134 of the primary sleeve bearing member 124 can be increased relative to the helix angle of channels 142 shown in the figure 4C. In addition, any number of channels 142 can be formed on the outer contact surface 134 of the primary sleeve bearing member 124. As the helix angle of the channels 142 increases, the contact area remains between the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figures 3A and 3B) can increase, and the effectiveness of the working fluid in dissipating heat from primary bearing 121 can also increase. Accordingly, persons of ordinary skill in the art will understand that any number of channels 142 can be formed in the primary sleeve bearing member 124, and that the helix angle of helically extending channels 142 can comprise any helix angle .
Referring to Figure 4E, another embodiment of a primary sleeve bearing member 124 is shown. The channels 142 formed in the primary sleeve bearing member 124 may not provide fluid communication between the opposing side surfaces 130 and 132 of the primary sleeve bearing member 124, in some embodiments. Channels 142 in these embodiments may comprise, for example, grooves that extend circumferentially, which may form a closed flow path on the outer contact surface 134 of the primary sleeve bearing member 12 4. As a specific non-limiting example, the channels 142 may comprise annular grooves defining a circular flow path around the circumference of the primary sleeve bearing member 124 and extending radially inward from the outer contact surface 134 of the primary sleeve bearing member 124, as shown in figure 4E. As another specific non-limiting example, channels 142 may define a closed non-annular flow path (for example, zigzag, sinusoidal or other curvilinear) around the outer circumference of primary sleeve bearing member 124 and extending radially to in from the outer contact surface 134 of the primary sleeve bearing member 124. In some embodiments, a single channel 142 may extend circumferentially around the outer contact surface 134 to define a closed flow path. In other embodiments, a plurality of channels 142 may extend circumferentially around the outer contact surface 134 to define a closed flow path. For example, two channels 142 can extend parallel to each other around the circumference of the outer contact surface 134 of the primary sleeve bearing member 124, as shown in figure 4E. In other embodiments, more than two channels 142 (e.g., three, four, five, etc.) can extend around the circumference of the outer contact surface 134 of the primary sleeve bearing member 124, as shown in figure 4E. In embodiments where at least one channel 142 defines a closed flow path around the outer contact surface 134 of the primary sleeve bearing member 124, the channel or channels 142 may increase lubrication at the first interface 126 of the primary bearing 121 (see figures 3A and 3B) by acting as a local reservoir into which the working fluid can collect and from which the working fluid can flow to the first interface 126 between the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figures 3A and 3B).
In addition, channels 142 defining a closed flow path around the outer contact surface 134 of the primary sleeve bearing member 124 may be particularly creating an opening through the working fluid that can flow between the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figures 3A and 3B), causing the primary cone bearing member 122 (see figures 3A and 3B) to hover or float around the primary sleeve bearing member 124 For example, a distance between the primary sleeve bearing member 124 and the primary cone bearing member 122 may be between about 0.01 mm and about 0.40 mm. More specifically, the distance between the primary sleeve bearing member 124 and the primary cone bearing member 122 10 as the primary cone bearing member 122 rotates about the primary sleeve bearing member 124 may be between about 0.15 mm and 0.25 mm. Of course, the distance between the primary and sleeve bearing members 122 and 124 may not be constant, due to the relative movement between the primary and sleeve bearings 122 and 124, for example, in response to changes in pressure in the working fluid, the presence of abrasive particles to be removed by the working fluid, forces acting on the primary cone and sleeve bearings 122 and 20 124, and other factors that can cause the primary cone and sleeve bearings 122 and 124 elbow or move in another way in relation to each other.
Referring to Figure 4F, another embodiment of a primary sleeve bearing member 124 is shown. The channels 25 142 formed in the primary sleeve bearing member 124 may comprise grooves that extend in different directions that are not parallel to a central geometric axis of the primary sleeve bearing member 124. For example, the channels 142 formed in the primary sleeve member primary sleeve bearing 30 124 described in figure 4F comprise a first plurality of channel 142 'comprising helical grooves extending in a first direction on the outer contact surface 134 of primary sleeve bearing member 124 and a second plurality of channel 142 " helical grooves extending in a second transverse direction on the outer contact surface 134 of the primary sleeve bearing member 124. Thus, the channels 142 can form a cross hatched pattern on the outer contact surface 134 of the primary sleeve bearing member 124 .
As shown in Figure 4G, a channel 142 can be formed on the outer contact surface 134 of the primary sleeve bearing member 124 which comprises a single notch, which can also be characterized as flat. When channel 142 comprises a single notch, depending on the circumferential extent of the notch, the contact area between the primary sleeve bearing member 124 and the primary cone bearing member 122 can be increased with respect to other channel configurations. In addition, the relatively large size of channel 142 comprising a notch may allow solids and residues residing in the drilling fluid to pass more easily through channel 142, which can reduce the potential for fluid flow blockages. Accordingly, those skilled in the art will understand that channels 142 can comprise any number of channels 142 and can comprise larger notches or smaller grooves of any desirable size, depth or cross-sectional shape.
As shown in Figure 4H, channels 142 may not be formed on the outer contact surface 134 of the primary sleeve bearing member 124, but may be positioned on the wall of the primary sleeve bearing member 124 between the outer contact surface 134 and the inner surface 136 and extends between the opposing side surfaces 130 and 132, for openings there. Although the externally extending channels 142 may not provide additional lubrication for the external contact surface 134, they can still provide beneficial cooling for the bearing system 128 (see figures 3A and 3B). Accordingly, persons of ordinary skill in the art will understand that channels 142 may be formed on the outer contact surface 134 of the primary sleeve bearing member 124, or may be formed on the wall of the primary sleeve bearing member 124.
Referring to Figure 41, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. The primary sleeve bearing member 124 may include a channel 142 formed on the outer contact surface 134 of the primary sleeve bearing member 124. The channel 142 may comprise a groove defining a sinusoidal path around the circumference of the outer contact surface 134 of the primary glove bearing member 124. Such a configuration can increase the cooling of the bearing when compared to an annular channel 142 (see figure 4E), because the increased length of the flow path around the glove bearing member primer 124 can provide a larger reservoir of working fluid to cool the bearing.
Referring to Figure 4J, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. The primary sleeve bearing member 124 may include a plurality of channels 142 not substantially aligned with the geometric axis of rotation of the primary cone bearing member 122 (see figures 3A and 3B) and extending between the opposing side surfaces 130 and 132. For example, channels 142 can define curved paths, such as, for example, "S" shaped paths or curved paths at least substantially resembling a cubic function graph. These curved channels 142 can provide increased cooling over axially aligned channels (see figure 4A), due to the longer flow path for the working fluid, which can increase the time during which the bearing heat can be transferred to the working fluid. Adjacent channels 142 can bend in opposite directions, so that at least some of the adjacent channels 142 intersect at least some other adjacent channels 142 at points on the outer contact surface 134 between the opposite side surfaces 130 and 132, such as example, for setting the configuration in "X" format shown in figure 4J.
With reference to figure 4K, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. The primary sleeve bearing member 124 may include a plurality of channels 142 not substantially aligned with the geometric axis of rotation of the primary cone bearing member 122 (see figures 3A and 3B) and extending between the opposing side surfaces 130 and 132. For example, channels 142 can define curved paths, such as, for example, "S" shaped paths or curved paths at least substantially resembling a graph of a cubic function. Adjacent channels 142 can bend in opposite directions and can be spaced so that adjacent channels intersect at points on the outer contact surface 134 between the opposite side surfaces 130 and 132 and the points on the outer contact surface 134 adjacent to the surfaces opposite sides 130 and 132. In other words, channels 142 can define a continuous flow path between the opposite side surfaces 130 and 132 and around the circumference of the outer contact surface 134 of the primary sleeve bearing member 124.
Referring to Figure 4L, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. The primary sleeve bearing member 124 may include a plurality of channels 142 grouped in a region of the outer contact surface 134, rather than uniformly distributed around the entire circumference of the outer contact surface 134. For example, channels 142 may be positioned in a region displaced from a region most likely to support a load. More specifically, channels 142 can be positioned at least 10 ° away from a region of the outer contact surface 134 in which loads are most likely to be applied and supported. Thus, the load-bearing area of the outer contact surface 134 can be increased in relation to some embodiments in which the channels are evenly distributed around the circumference of the primary sleeve bearing member 124 (see, for example, figures 4A to 4D) and the region of the external contact surface 134 most likely to support loads can be free of channels 142 formed on the external contact surface 134. In addition, channels 142 may have non-constant widths. For example, a width of the channels 142 can increase from the first side surface 130 to the second side surface 132. In this way, a pressure gradient can be formed between the opposite side surfaces 130 and 132 of the primary sleeve bearing member 124 .
Referring to Figure 4M, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. The primary sleeve bearing member 124 may include a channel 142 that provides a continuous tortuous flow path between the opposite side surfaces 130 and 132 of the primary sleeve bearing member 124. For example, the channel 142 may extend initial, axially from the first lateral surface 130 towards the second lateral surface 132, it can turn to extend radially around the external contact surface 134 retracted position less than the entire circumference, it can turn again to extend axially in towards the second side surface 132, it can turn again to extend radially around the outer contact surface 134 by less than the entire circumference, and finally it can turn to extend axially to the second side surface 132. The increased length of the flow path between the opposing side surfaces 130 and 132 can increase the cooling that the working fluid can provide for the ma ncai, due to a longer exposure of the working fluid to the bearing.
With reference to figures 4N and 40, the front and rear perspective views of another embodiment of a primary sleeve bearing member 124 are shown. The primary sleeve bearing member 124 may include a channel 142 that provides a continuous tortuous flow path between the opposite side surfaces 130 and 132 of the primary sleeve bearing member 124 and around the circumference of the outer contact surface 134 of the member primary sleeve bearing 124. For example, channel 142 may extend initially axially from the first side surface 130 towards the second side surface 132, as shown in Figure 4N. The channel 142 can turn to extend radially around the outer contact surface 134 over the entire circumference, as shown in figures 4N and 40. The channel 142 can turn again to extend axially towards the second side surface 132, as shown in figure 40. The channel 142 can turn yet again to extend radially around the outer contact surface 134 across the entire circumference, as shown in figures 4N and 40. The channel 142 can finally turn to extend axially to the second lateral surface 132, as shown in figure 4N. The increased length of the flow path between the opposing side surfaces 130 and 132 can increase the cooling that the working fluid can provide to the bearing, due to a longer exposure of the working fluid to the bearing.
Referring to Figure 4P, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. The primary sleeve bearing member 124 may include a plurality of channels extending circumferentially around the outer contact surface 134. Channels 142 can extend in 5 directions so that the central geometrical axes of channels 142 are oblique to an axis central geometry of the primary sleeve bearing member 124. For example, the channels may extend around the circumference of the outer contact surface 134 and may intercept each other on opposite sides of the sleeve bearing member 124, as shown in figure 4P.
Referring to Figure 4Q, a perspective view of another embodiment of a primary sleeve bearing member 124 is shown. In addition to the channels 142 formed on the outer contact surface 134, the channels 142 can be formed on the inner surface 136. For example, channels 142 extending in a direction parallel to a central geometric axis of the primary sleeve bearing member 124 can extends between the opposing side surfaces 130 20 and 132 of the primary sleeve bearing member 124 on the inner surface 136, as shown in figure 4Q. In other embodiments, channels 142 in any of the configurations described previously in relation to figures 4A to 4P can be formed on the inner surface 136. In still other embodiments, channels 142 can be formed on the inner surface 136 of the bearing member. primary sleeve 124, but the outer contact surface 134 may lack channels 142. In still other embodiments, channels 142 may be formed on an axis of the bearing pin 30 116 (see figures 3A and 3B), which the member primary sleeve bearing 124 can be attached. The channels 142 formed on the inner surface 136 of the primary sleeve bearing member 124 or the bearing pin 116 (see figures 3A to 3B) can provide beneficial cooling for the bearing and other drill bit components near the bearing.
Figures 5A and 51 illustrate various modalities of the primary cone bearing members 122. Figure 10 describes a primary cone bearing member 122 having channels 142 comprising linear grooves formed on an internal contact surface 144 of the bearing member. primary cone 122. The primary cone bearing member 122 comprises a generally cylindrical shape defined by the outer surface 150, and includes an inner contact surface 144 defining an internal diameter of the primary cone bearing member 122. The channels 142 extend in a direction at least substantially parallel to a central geometric axis of the primary cone bearing member 122, similarly to the channels 142 shown in figures 4A and 4B. Any number of channels 142 can be located on the inner contact surface 144 of the primary cone bearing member 122, and channels 142 can be spaced in uniform or non-uniform patterns around the inner contact surface 144 of the cone bearing member. primary 122.
As shown in Figure 5B, channels 142 may not be formed on the inner contact surface 144 of the primary cone bearing member 122, but may be positioned on the wall of the primary cone bearing member 122 between the inner contact surface 144 and the outer surface 150 and extend between the openings on opposite side surfaces 146 and 148 of the primary cone bearing member 122, similarly to the channels 142 described in figure 4H.
As shown in figures 5C and 5D, the channels 142 formed on the inner contact surface 144 of the primary cone bearing member 122 can extend in a direction that is not parallel to a central geometric axis of the primary cone bearing member 122, similarly to channels 142 shown in figures 4C and 4D. Any number of channels 142 can be formed on the internal contact surface 144 of the primary cone bearing member 122, and channels 142 can extend helically at any desirable helix angle. Furthermore, channels 142 comprising a propeller shape can be configured to act as a pump to facilitate fluid flow through bearing system 128 (see figures 3A and 3B).
Referring to figure 5E, another embodiment of a primary cone bearing member 122 is shown. The channels 142 formed in the primary cone bearing member 122 may not provide fluid communication between the opposite side surfaces 146 and 148 of the primary cone bearing member 122 in some embodiments. Channels 142 in these embodiments can comprise, for example, circumferentially extending grooves, which can form a closed flow path at the inner contact surface 144 of primary cone bearing member 122, similarly to the channels shown in Figure 4E . As a specific non-limiting example, the channels 142 may comprise annular grooves defining a circular flow path around the circumference of the primary cone bearing member 122 and extending radially outwardly from the inner contact surface 144 of the bearing member primary cone 122, as shown in figure 5E. As another specific non-limiting example, channels 142 may define a closed non-annular flow path (for example, a zigzag, sinusoidal or other curvilinear) around the inner circumference of the primary cone bearing member 122 and extending radially to outside from the inner contact surface 144 of the primary cone bearing member 122. In some embodiments, a single channel 142 may extend circumferentially around the inner contact surface 144 to define a closed flow path. In other embodiments, a plurality of channels 142 may extend circumferentially around the inner contact surface 144 to define a closed flow path. In embodiments in which at least one channel 142 defines a closed flow path around the inner contact surface 144 of the primary cone bearing member 122, the channel or channels 142 may increase lubrication at the first interface 126 of the primary bearing 121 (see figures 3A and 3B) by acting as a local reservoir into which the working fluid can collect and from which the working fluid can flow to the interface 126 between the primary sleeve bearing member 124 (see figures 3A and 3B) and the primary cone bearing member 122.
In addition, channels 142 defining a closed flow path around the inner contact surface 144 of primary cone bearing member 122 may be particularly likely to create a space through which working fluid can flow between the bearing member primary sleeve member 124 (see figures 3A and 3B) and primary cone bearing member 122, causing primary cone bearing member 122 to hover or float around primary sleeve bearing member 124. For example, a distance between the primary sleeve bearing member 124 (see figures 3A and 3B) and the primary cone bearing member 10 may be between about 0.01 mm and about 0.40 mm. More specifically, the distance between the primary sleeve bearing member 124 (see figures 3A and 3B) and the primary cone bearing member 122, as the primary cone bearing member 122 rotates about 15 of the bearing sleeve member. primary glove 124, can be between around 0.15 mm and 0.25 mm. Of course, the distance between primary cone and sleeve bearings 122 and 124 may not be constant, due to a relative movement between primary cone and sleeve bearings 122 and 20 124, for example, in response to changes in frequency of the working fluid, the presence of abrasive particles to be removed by the working fluid, forces acting on the primary cone and sleeve bearings 122 and 124, and other factors that can cause the cone and 25 primary sleeve bearings 122 and 124 elbow or move in another way in relation to each other.
Referring to Figure 5F, another embodiment of a primary cone bearing member 122 is shown. The channels 142 formed in the primary cone bearing member 122 may comprise grooves that extend in different directions that are not parallel to a central geometric axis of the primary cone bearing member 122. For example, the channels 142 formed in the primary cone member primary cone bearing 122 described in figure 5F comprise a first 5 plurality of channels 142 'comprising helical grooves extending in a first direction on the inner contact surface 144 of the primary cone bearing member 122 and a second plurality of channels 142' comprising helical grooves extending in a second transverse direction on the inner contact surface 144 of the primary cone bearing member 122, similarly to the channels described in Figure 4F. Thus, the channels 142 can form a cross hatch pattern on the internal contact surface 144 of the primary cone bearing member 122.
Referring to Figure 5G, another embodiment of a primary cone bearing member 122 is shown. In addition to the channels 142 formed on the inner contact surface 144, the channels 142 can be formed on the outer surface 150. 20 For example, channels 142 extending in a direction parallel to a central geometric axis of the primary cone bearing member 122 can extends between the opposite side surfaces 146 and 148 of the primary cone bearing member 122 on the outer surface 150, as shown in Figure 5G. In other embodiments, channels 142 in any of the configurations previously described in relation to figures 4A to 4Q can be formed on the outer surface 150. In still other embodiments, channels 142 can be formed on the outer surface 150 of the 30-bearing member. primary cone 122, but 144 may lack channels 142. In still other embodiments, channels 142 may be formed in a roller cone body 106 (see figures 3A and 3B) or in a bushing body (not shown) ) to which the primary cone bearing member 122 can be attached. The channels 142 formed on the outer surface 150 of the primary cone bearing member 122, on the roller cone 106 (see figures 3A and 3B) or on the sleeve (not shown) can provide beneficial cooling for the bearing and other drill components drilling holes near the bearing.
Referring to Figure 5H, another embodiment of a primary cone bearing member 122 is shown. The primary cone bearing members 122 can be configured to create a pressure resisting a flow of working fluid through the channels 142 formed on the inner contact surface 144 of the primary cone bearing members 122. For example, a bearing member primary cone 122 can be configured to rotate in a counterclockwise direction around a primary sleeve bearing member 124 (see figures 4A to 4Q), as indicated by the arrow surrounding the primary cone bearing member 122. In this orientation, the spacer ring 146 can face the drill body 102 (see figures 1 and 2) and the second side surface 148 can face an underlying terrain formation (not shown). The counterclockwise rotation of the primary cone bearing member 122 can suck the working fluid into the channels extending helically 142 from the second side surface 148, due to the inclined orientation of the channels 142. As additional fluid is sucked in channels 142 from the second side surface 148, the working fluid can create a pressure directed through channels 142 to the first side surface 146, as indicated by the arrow extending along channels 142 in figure 5H. This action can resist the natural flow of the working fluid, which can be directed downward from the first side surface 146 to the second side surface 148. Thus, the direction of rotation of the primary cone bearing member 122 and the orientation helical channels 142 can withstand the flow of working fluid through channels 142.
Referring to Figure 51, another embodiment of a primary cone bearing member 122 is shown. The primary cone bearing members 122 can be configured to create a pressure contributing to a flow of working fluid through the channels 142 formed on the inner contact surface 144 of the primary cone bearing members 122. For example, a member primary cone bearing 122 can be configured to rotate in a clockwise direction around a primary sleeve bearing member 124 (see figures 3A and 3B), as indicated by the arrow surrounding the primary cone bearing member 122. In this orientation, the first side surface 146 can face the drill body 102 (see figures 1 and 2) and the second side surface 148 can face an underlying terrain formation (not shown). The counterclockwise rotation of the primary cone bearing member 122 can suck working fluid into the helically extending channels 142 from the first lateral surface 146, due to the inclined orientation of the channels 142. An additional fluid is sucked in channels 142 from the first side surface 146, the working fluid can create a pressure directed through the channels 142 to the second side surface 5 148, as indicated by the arrow extending along one of the channels 142 in figure 51. This This action can cause the primary cone bearing member 122 to act as a pump in the direction of the natural flow of the working fluid, which can be directed downward from the first side surface 146 to the second side surface 148. Thus , the direction of rotation of the primary cone bearing member 122 and the helical orientation of the channels 142 can contribute to the flow of working fluid through the channels 142.
In other embodiments, the primary cone bearing members 122 can include channels 142 in any of the configurations described previously in relation to the primary sleeve bearing members 124 shown in figures 41 to 4Q. In other words, the channel configurations 142 described in figures 41 to 4Q can be projected from the outer contact surface 134 of the primary sleeve bearing members 124 onto the inner contact surface 144 of the primary cone bearing members 122. Although primary cone bearing members 122 may include channels 142 in these configurations, it is not required that those primary cone bearing members 122 be used with primary sleeve bearing members 124 having a similar channel configuration 142.
When incorporated into the bearing system, the primary sleeve bearing member 124, the primary cone bearing member 122 or both may comprise at least one channel 142. In addition, any combination of channel configurations 142 may be employed. For example, the primary sleeve bearing member 124 may comprise a channel 142 formed as a single notch on the outer contact surface 134 of the primary sleeve bearing member 124, and the primary cone bearing member 122 may comprise a plurality of channels 142 formed within the primary taper bearing member 122 and extending between openings on opposite side surfaces 146 and 148 of the primary taper bearing member 122 and extending in a direction substantially parallel to the central geometric axis of the taper bearing member. primary cone 122. Any combination of channel configurations 142 can be employed, so that at least one primary cone bearing member 122, 124 or 122 and 124 comprises at least one channel 142. Furthermore, channels 142 can be configured for minimizing stresses on the primary sleeve bearing member 124 and the primary cone bearing member 122, while maximizing heat removal efficiency.
A pressurized working fluid flowing through the bearing system 128 (see figures 3A and 3B) can form and fill an at least substantially uniform space between the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figures 3A and 3B), causing the primary cone bearing member 122 (see figures 3A and 3B) to hover or float around the primary sleeve bearing member 124. For example, a distance between the bearing member of primary sleeve 124 and the primary cone bearing member 122 may be between about 0.01 mm and about 0.40 mm. More specifically, the distance between the primary sleeve bearing member 124 and the primary cone bearing member 122 as the primary cone bearing member 122 rotates about the primary sleeve bearing member 124 may be between about 0 , 15 mm and 0.25 mm. As the working fluid flows between the opposing side surfaces 130 and 132, the working fluid can remove abrasive particles that might otherwise remain between the primary sleeve bearing member 124 and the primary cone bearing member 122 (see figures 3A and 3B), which can erode, damage or even cause failure of the primary sleeve bearing member 124, of the primary cone bearing member 122 (see figures 3A and 3B), or both of the bearing member primary sleeve 124 and primary cone bearing member 122 (see figures 3A and 3B). Thus, channels 142 can reduce the wear rate of primary bearing 121, compared to primary bearings lacking channels.
As the primary sleeve bearing members 124 and the primary cone bearing members 122 described with reference to figures 4A to 5E, the secondary sleeve bearing members 125 and the secondary cone bearing members 123 can comprise annular members having surfaces external and internal contact points, respectively, and can be configured to withstand radial loads acting on the mounted bearing system 128 (see figures 3A and 3B). The secondary sleeve bearing member 125, the secondary cone bearing member 123 or both the secondary sleeve bearing member 125 and the secondary cone bearing member 123 may comprise at least one channel 142 formed there, such as, for example, example, any of the channel configurations 142 described with reference to figures 4A to 5E. Thus, secondary bearings 127 that are configured to support radial loads can be configured in a similar manner to primary bearings 121, which are configured to support radial loads. When a bearing system 128 includes at least one primary bearing 121 and at least one secondary bearing 127 configured to withstand radial loads, the primary bearings 121 may have the same channel configuration 142 as the secondary bearings 127, in some embodiments. In other embodiments, primary bearings 121 may have a different channel configuration 142 than secondary bearings 127.
Since primary bearings 121 and secondary bearings 127 configured to support radial loads, secondary bearings 127 configured to support axial loads, sometimes referred to as thrust bearings, can include at least one channel 142. For example, at least one of a secondary cone bearing member 123 and a secondary sleeve bearing member 125 may comprise at least one channel 142 formed there. For example, figure 6A depicts a secondary cone bearing member 123 configured for use in a thrust bearing. The secondary cone bearing member 123 can comprise a generally annular member having an annular top surface 152, a generally annular lower contact surface 154 parallel to the annular top surface 152, a lateral surface 156 transverse to and intersecting the top surface 152 and the lower contact surface 154 defining an external diameter of the secondary cone bearing member 123, and an internal surface 157 transversal to and intersecting the top surface 152 and the lower contact surface 154 defining an internal diameter of the bearing member of secondary cone 123, in some modalities. In other embodiments, the secondary cone bearing member 123 may comprise a generally disk-shaped member having a circular top surface 152 and a generally circular bottom contact surface 154 parallel to the top surface 152. Channels 142 can be formed on the lower contact surface 154 of the secondary cone bearing member 123 and have openings on the side surface 156 and on the inner surface 157 of the secondary cone bearing member 123. Although the channels 142 shown in figure 6A comprise four straight linear channels, channels 142 can comprise any number of channels 142 extending in any direction and having any cross-sectional shape. For example, channels 142 may comprise two arcuate channels 142, a plurality of channels 142 extending radially from a central geometric axis of the secondary cone bearing member 123 or a single linear channel 142. Channels 142 allow the fluid workflow flows through the lower contact surface 154 of the secondary cone bearing member 123 for the lubrication provision at the second interface 129 between the secondary cone bearing member 123 and the secondary sleeve bearing member 125, for cooling the bearing axial 127 and other components in the vicinity of it, and for removing abrasive particles that can shorten the life of the secondary bearing 127.
As shown in figure 6B, channels 142 cannot be formed on the lower contact surface 154 of the secondary cone bearing member 123, but can be formed internally to the secondary cone bearing member 123 and have exits on the side surface 156 and on the inner surface 157 of the secondary cone bearing member 123. Channels 142 allow a working fluid to flow through the secondary cone bearing member 123 and cool axial bearing 127 and other components in the vicinity of it, but generally do not provide additional lubrication at the second interface 129 between the secondary cone bearing member 123 and the axial sleeve bearing member 125 or remove abrasive particles from the second interface 129 between the secondary cone bearing member 123 and the sleeve bearing member secondary 125.
As shown in figures 6C and 6D, a secondary sleeve bearing member 125 may have a generally annular shape including an upper contact surface 158 having a generally annular shape, a bottom surface 160 parallel to the upper contact surface 158 and having a annular shape, a lateral surface 162 transversal to and intersecting the upper contact surface 158 and the bottom surface 160 defining an outer diameter of the secondary sleeve bearing member 125, and an internal surface 163 transversal to and intercepting the upper contact surface 158 and the bottom surface 160 defining an internal diameter of the secondary sleeve bearing member 125, in some embodiments. In other embodiments, the secondary cone bearing member 123 may comprise a generally disk-shaped member having a generally circular upper contact surface 158 and a circular bottom surface 160 parallel to the upper contact surface 158. Channels 142 are formed on the upper contact surface 158 of the secondary cone bearing member 123 and have openings on the side surface 156 and on the inner surface 163 of the secondary cone bearing member 123. Channels 142 allow the working fluid to flow through the contact surface upper 158 of the secondary sleeve bearing member 125 for the provision of lubrication at the second interface 129 between the secondary cone bearing member 123 and the secondary sleeve bearing member 125, for cooling the secondary bearing 127 and other components in proximity to it, and for removing abrasive particles that can shorten the life of secondary bearing 127. Channels 142 can comprise any number of channels 142 extending in any direction and having any cross-sectional shape. As shown in figure 6D, channels 142 can also be formed internally in the secondary sleeve bearing member 125 and have outlets on the side surface 162 and on the inner surface 157 thereof.
Referring to figure 6E, another embodiment of a secondary cone bearing member 123 configured to support axial loads is shown. The secondary cone bearing member 123 may include a plurality of channels 142 extending radially outward like forks on the lower contact surface 154 of the secondary cone bearing member 123. For example, the secondary cone bearing member 123 may include four channels 142 spaced circumferentially uniformly (i.e., 90 °) from one another and extending radially between the inner surface 157 and the side surface 156 of the secondary cone bearing member 123.
Referring to figure 6F, another embodiment of a secondary cone bearing member 123 configured to support axial loads is shown. The secondary cone bearing member 123 may include a plurality of channels 142 extending radially outward like forks on the lower contact surface 154 of the secondary cone bearing member 123. For example, the secondary cone bearing member 123 may include eight channels 142 spaced circumferentially uniformly (i.e., 45 °) from one another and extending radially between the inner surface 157 and the side surface 156 of the secondary cone bearing member 123.
Referring to figure 6G, another embodiment of a secondary cone bearing member 123 configured to support axial loads is shown. The secondary cone bearing member 123 may comprise a plurality of linear channels 142 extending from one side of the side surface 156 to an opposite side of the side surface 156 and intercepting the inner surface 157 between the opposite sides of the side surface 156. Instead of the semicircular cross-sectional shape of channels 142 shown in the other embodiments (see, for example, figures 6E and 6F), channels 142 may have a rectangular cross-sectional shape.
Referring to Figure 6H, another embodiment of a secondary cone bearing member 123 configured to support axial loads is shown. Secondary cone bearing member 123 may include a set of channels 142 extending radially outward like forks on the lower contact surface 154 of secondary cone bearing member 123. For example, secondary cone bearing member 123 may include four sets of four channels 142 extending between the inner surface 157 and the side surface 156 of the secondary cone bearing member 123 through the lower contact surface 154. At least one of the channels 142 from one of the sets of four channels 142 can intercept at least one other channel 142 from another set of four channels 142, which can increase fluid flow and particle removal, due to the increased number of channels 142 and due to the larger spaces created by channels 142 being intercepted .
In other embodiments, the secondary sleeve bearing members 125 may include channels 142 in any of the configurations described previously in relation to the secondary cone bearing members 123 shown in figures 6E to 6H. In other words, the channel configurations 142 described in figures 6E to 6H can be projected from the lower contact surface 154 of the secondary cone bearing members 123 on the upper contact surface 158 of the secondary sleeve bearing members 125. Although the secondary sleeve bearing members 125 may include channels 142 in these configurations, it is not required that those secondary sleeve bearing members 125 be used with secondary cone bearing members 123 having a similar channel configuration 142.
With reference to figure 7A, a 5-sleeve secondary bearing member 123 'that can be used on a secondary bearing 127' (see figure 3B) is shown. A secondary sleeve bearing member 123 'like this can be employed on a secondary bearing 127' configured to support axial and radial loads. The secondary sleeve bearing member 10 '123' can generally be configured as a combination of the secondary sleeve bearing members 123 generally configured as the primary sleeve bearing members shown in Figures 4A to 4H and as the sleeve bearing members secondary 123 shown in figures 6A 15 and 6B. Thus, the secondary sleeve bearing member 123 'may comprise a generally cylindrical portion 161 that has a side surface 130' that defines at least a substantially annular cross section, an outer contact surface 134 'that defines an intermediate outer diameter 20 'of the secondary sleeve bearing member 123', an inner surface 136 'defining an inner diameter 140' of the secondary sleeve bearing member 123 '. The secondary sleeve bearing member 123 'may further comprise a generally annular portion 165 connected to the generally cylindrical portion 161 and extending radially outwardly at a top of the cylindrical portion 161. The generally annular portion 165 may have an annular top surface 152 ', a lower annular contact surface 154' parallel to the annular surface 152 ', 30 a lateral surface 156' transverse to and intersecting the top surface 152 'and the lower contact surface 154' defining an outer diameter 141, greater than that the intermediate outer diameter 138 ', of the secondary sleeve bearing member 123', the inner surface 136 'being transverse to and intersecting the top surface 152', in some embodiments. Thus, the bottom contact surface 154 'can intersect the outer contact surface 134', and the bottom and outer contact surfaces 154 'and 134' can form a substantially continuous surface configured to abut a secondary cone bearing member. 125 'at the second interface 129 (see figure 3B). A chamfer or smooth curve can provide a transition between the lower contact surface 154 'and the external contact surface 134'.
At least one channel 142 can be formed in the secondary sleeve bearing member 123 '. For example, a plurality of channels 142 can form linear grooves extending axially on the outer contact surface 134 'in the generally cylindrical portion 161 and extending radially outwardly on the lower contact surface 154' in the generally annular portion 165. Thus, the channels 142 can form a continuous flow path between the side surfaces 130 'and 156' of the secondary sleeve bearing member 123 ', as shown in figure 7A. In addition, when it is said that the lower contact surface 154 'and the outer contact surface 134' can form a substantially continuous surface, this means that the otherwise continuous surface can be interrupted by channels 142 extending to the surfaces bottom and outer contact 154 'and 134'. In other embodiments, channels 142 may be formed in the body of the secondary sleeve bearing member 123 'and have openings in the side surfaces 130' and 156 'of the secondary sleeve bearing member 123', may comprise non-linear grooves, may comprise any number of slots, can have any cross-sectional shape, can be of any depth, and can otherwise include channel configurations 142 previously discussed in connection with subscriber figures 4A to 6D.
With reference to figure 7B, a secondary cone bearing member 125 'that can be used on a secondary bearing 127' (see figure 3B) is shown. A secondary cone bearing member 125 'like this can be employed on a secondary bearing 127' configured to support axial and radial loads. The secondary cone bearing member 125 'can generally be configured as a combination of the secondary cone bearing members 125 generally configured as the primary cone bearing members shown in Figures 5A to 5F and the secondary cone bearing members 125 shown in figures 6C and 6D. Thus, the secondary cone bearing member 125 'may comprise a generally cylindrical portion 161' having a side surface 146 'defining at least a substantially annular cross section and an inner contact surface 144' defining an inner diameter of the bearing member secondary cone 125 '. The secondary cone bearing member 125 'may further comprise a generally annular portion 165' connected to the generally cylindrical portion 161 'and extending radially outwardly at a top of the cylindrical portion 161'. The generally annular portion 165 'may have a generally annular upper contact surface 158', an annular bottom surface 160 'parallel to the upper contact surface 158', a lateral surface 162 'transverse to and intersecting the upper contact surface 158' and defining an outer diameter, greater than the intermediate outer diameter, of the secondary cone bearing member 125 ', the inner contact surface 144' being transverse to and intersecting the upper contact surface 158 ', in some embodiments. Thus, the upper contact surface 158 'can intersect the inner contact surface 144' and the upper and inner contact surfaces 158 'and 144' can form a substantially continuous surface configured to abut a secondary sleeve bearing member 123 'at the second interface 129 (see figure 3B). A chamfer or smooth curve can provide a transition between the upper contact surface 158 'and the inner contact surface 144'.
At least one channel 142 can be formed in the secondary cone bearing member 125 '. For example, a plurality of channels 142 can form linear grooves extending axially on the inner contact surface 144 'in the generally cylindrical portion 161' and extending radially outwardly on the upper contact surface 158 'in the generally annular portion 165'. Thus, the channels 142 can form a continuous flow path between the side surfaces 160 'and 146' of the secondary sleeve bearing member 123 ', as shown in figure 7A. In addition, when it is said that the upper contact surface 158 'and the inner contact surface 144' can form a substantially continuous surface, it is meant that the otherwise continuous surface can be interrupted by channels 142 extending to the surfaces bottom and external contact 158 'and 144'. In other embodiments, channels 142 may be formed in the body of the secondary sleeve bearing member 123 'and have openings in the side surfaces 140' and 146 'of the secondary sleeve bearing member 123', may comprise non-linear grooves, may comprise any number of slots, can have any cross-sectional shape, can be of any depth, and otherwise can include channel configurations 142 previously discussed with reference to figures 4A to 6D.
Primary bearings 121 and secondary bearings 127 can comprise any suitable material. For example, sleeve and cone bearing members 122 to 125 may comprise ceramic materials, such as carbides, nitrides, oxides and borides, metal materials, such as cobalt, aluminum, copper, magnesium, titanium, iron, steel and nickel and alloys thereof, super hard materials, such as synthetic diamond scream, natural diamond scream, diamond film or cubic boron nitride, or any combination of the preceding materials. As a specific non-limiting example, primary bearings 121 and secondary bearings 127 may comprise a ceramic-metallic composite material (i.e., a cermet) comprising a plurality of tungsten carbide particles in a metal matrix.
Although the preceding bearing members 123 to 125 have been described as being used in a rotary field drill bit, persons of ordinary skill in the art will understand that bearings according to the modalities of the invention can be used in other tools well below. For example, a bearing system 128 'according to an embodiment of the present invention can be employed on a downhole engine 164, as shown in figure 8. The downhole engine 164 may comprise, for example, a " mud "of the Moinean type or a turbine engine. The components above and below the 128A real bearing system are not illustrated. The downhole motor 164 includes a central tubular downhole motor drive shaft 166 rotatably located in a tubular bearing housing 167, with the downhole motor bearing system 128 'located and providing relative rotation between the drive shaft 166 and the housing 167. Those skilled in the art will recognize that the drive shaft 166 is rotated by the action of the downhole motor 164 and supplies a rotary drive for a ground drilling tool, such as drill bits drilling holes 100 and 100 'shown in figures 1 and 2. Housing 167 remains rotationally stationary during engine operation.
The bearing system 128 'includes at least one thrust bearing 169. The thrust bearings 169 may comprise a plurality of axially stacked annular members 168 having upper and lower confining contact surfaces 170 and 172, respectively. For example, axial bearings 169 may comprise opposing PCD bearings, such as, for example, those set forth in U.S. Patent No. 4,764,036, issued August 16, 1988 to McPherson. The channels 142 can be formed on the upper and lower contact surfaces 170 and 172 in a manner similar to the bearing members 123 and 125 previously described with reference to figures 6A to 6H.
The bearing system 128 'also includes at least one radial bearing 171. In the embodiment shown in figure 8, the bearing system 128' includes two radial bearings 171, an upper radial bearing 171A and a lower radial bearing 171B. Each radial bearing 171 includes an inner bearing member 178 that is in sliding contact on a bearing interface 180 with an outer bearing member 177. The inner bearing member 178 is housed concentric in the outer bearing member 177. In others In other words, a radially outer surface of the inner bearing member 178 is in sliding contact with a radially inner surface of the outer bearing member 177.
As the sleeve and cone bearing members 122 and 124 previously described in relation to figures 4A to 5F, the inner and outer radial bearing members 178 and 177 can include channels 142 formed in the inner and outer radial bearing members 178 and 177 for the provision of a fluid path between the axially opposite ends 188 and 190 of the radial bearing member 178 or for the provision of a local reservoir of working fluid at an interface between the inner and outer radial bearing members 178 and 177 Like the channels 142 previously described in relation to figures 4A to 5F, the channels can facilitate a flow of working fluid through each radial bearing 171, which can allow an increased cooling of each radial bearing 171 and the components in proximity to it, can provide additional lubrication for the interface between the inner and outer radial bearing members 178 and 177, and can remove abrasive particles that may otherwise shorten life radial bearing housing 127.
Referring to Figure 9A, a cross-sectional view of a channel 142 is shown. Channel 142 may have a semicircular cross-sectional shape. In other embodiments, the channel 142 may have a curved shape that defines more than half a circle, less than half a circle, a partial oval, a partial ellipse or another curved shape. With reference to figure 9B, a cross-sectional view of another embodiment of a channel 142 is shown. The channel can have a "V" shaped cross section. For example, channel 142 may comprise a groove defined by two planes oriented around 90 ° to each other and around 225 ° from the outer contact surface 134, 134 ', 144, 144', 154, 154 ', 158, or 158' in which it is formed. With reference to figure 9C, a cross-sectional view of another embodiment of a channel 142 is shown. Channel 142 may have a rectangular cross-sectional shape. In some embodiments, the corners of rectangular channels 142 can be chamfered or rounded to provide a transition between surfaces of channels 142 and between channels 142 and contact surfaces 134, 134 ', 144, 144', 154, 154 ' , 158, or 158 'in which they are formed. A width w of any of the preceding channel configurations in a wider portion of channels 142 may have between about 0.5 mm and about 6.0 mm. More specifically, the width w of the channels 142 can be between about 2.0 mm and about 5.0 mm. Likewise, the depth d of any of the preceding channel configurations can be between about 0.5 mm and about 4 mm. More specifically, the depth d of the channels 142 can be between about 1.0 mm and about 3.0 mm. Referring to figure 9D, a plan view of a channel 142 is shown. The channel 142 can have a non-uniform cross-sectional shape, a cross-sectional area or both a non-uniform shape and area. For example, channel 142 may exhibit a taper between the opening ends of channel 142. In these embodiments, the non-uniform cross section of channel 142 15 and the resulting change in the cross section area can create a pressure gradient across channel 142 , which can cause the working fluid to be pumped in a desired direction, increasing fluid flow and removing particles. Any of the preceding configurations 20 of channel 142 can be used in combination with any of the bearing systems 128 and 128 'and their corresponding components described previously.
In practice, a working fluid, such as a drilling mud, for example, can be pumped into a bearing system 128 or 128 'and can flow in channels 142 formed on one or all bearings 121, 127, 127 ', 169, and 171. As the working fluid flows through the bearing system 128 or 128', and specifically in the channels 142, heat can be transferred from the relatively hotter bearings 30, 127, 127, 127 ' , 169, and 171 for the relatively cooler working fluid. By the flow of the heated working fluid away from the bearing system 128 or 128 ', and therefore away from one or all bearings 121, 127, 127', 169, and 171, the bearing system 128 or 128 ' it can be cooled.
In any of the foregoing embodiments, the contact surfaces 134, 134 ', 144, 144' 154, 154 ', 158, and 158' can comprise a super hard material, such as, for example, a polycrystalline diamond material, a film diamond or a cubic boron nitride material. This super hard material can be attached to a substrate of a cermet material, such as, for example, cemented tungsten carbide.
Although the present exhibition has been described here with respect to certain modalities, those of ordinary skill in the art will recognize and appreciate that it is not so limited. Instead, many additions, deletions and modifications to the modalities described here can be made, without departing from the scope of the invention, as claimed hereinafter, including legal equivalents. In addition, resources from one modality can be combined with resources from another modality, while still being included in the scope of the invention, as contemplated by the inventor.

权利要求:
Claims (13)
[0001]
1. Bearing (121, 169 and 171) for a downhole tool (100, 100 '), characterized by the fact that it comprises: a first bearing member (124) comprising an external contact surface (134) defining an external diameter (138); and a second bearing member (122) comprising an inner contact surface (144) that defines an inner diameter, the inner diameter of the second bearing member (122) being greater than the outer diameter (138) of the first bearing member (124) and the internal contact surface (144) of the second bearing member (122) being in sliding contact with the external contact surface (134) of the first bearing member (124) at an interface (126); wherein the first bearing member (124) comprises a channel (142) formed on the outer contact surface (134) of the first bearing member (124), the channel (142) comprising a notch defining a flat surface interrupting a shape circular cross-section of the external contact surface (134); and wherein the second bearing member (122) comprises at least one other channel (142, 142 ') formed on the internal contact surface (144) of the second bearing member (122).
[0002]
2. Bearing (121, 169 and 171) for a downhole tool (100, 100 '), according to claim 1, characterized in that the at least one other channel (142, 142') comprises a first plurality of channels (142) extending helically in a first direction and a second plurality of channels (142 ') extending helically in a second transverse direction to define a cross hatch pattern.
[0003]
3. Bearing (121, 169 and 171) for a downhole tool (100, 100 '), according to claim 1, characterized by the fact that the first bearing member (124) and the second bearing member (122) be of cylindrical configuration, each having a central geometric axis transversal to the respective surfaces on the opposite side (130, 146, 148), and at least one channel (142, 142 ') comprising at least one axially oriented groove at least linear extending into the internal contact surface (144) of the second bearing member (122).
[0004]
4. Bearing (121, 169 and 171) for a downhole tool (100, 100 ') according to claim 1, characterized in that at least one channel (142, 142') comprises at least one helical groove on the internal contact surface (144) of the second bearing member (122).
[0005]
5. Bearing (121, 169 and 171) for a downhole tool (100, 100 '), according to claim 3, characterized in that at least one channel (142, 142') is positioned on an internal wall of the second bearing member (122) and open on the opposite side surfaces (146, 148) of them.
[0006]
6. Bearing (121, 169 and 171) for a downhole tool (100, 100 '), according to claim 1, characterized in that at least one channel (142, 142') comprises a groove that defines a closed flow path extending around the inner contact surface (144) of the second bearing member (122).
[0007]
7. Bearing (127, 127 ') for a downhole tool (100, 100'), characterized by the fact that it comprises: a first bearing member (123 ') comprising a cylindrical portion (161) and an annular portion ( 165) connected to the cylindrical portion (161) and extending radially outwardly at one end of the cylindrical portion (161), wherein the cylindrical portion (161) comprises an outer contact surface (134 ') defining an intermediate outer diameter (138 ') of the first bearing member (123), and wherein the annular portion (165) comprises an annular lower contact surface (154'), the lower contact surface (154 ') intercepting the outer contact surface (134' ) and the lower and outer contact surfaces (134 ', 154') forming a continuous surface; a second bearing member (125 ') comprising a cylindrical portion (161') and an annular portion (165 ') connected to the cylindrical portion (161') and extending radially outwardly at one end of the cylindrical portion (161 ') , wherein the cylindrical portion (161 ') comprises an internal contact surface (144') defining an internal diameter (140 ') of the second bearing member (125'), the internal diameter (140 ') being greater than the intermediate outer diameter (138 '), and where the annular portion (165') comprises an upper annular contact surface (158 '), the upper contact surface (158') intercepting the inner contact surface (144 ') and the upper and inner contact surfaces (144 ', 158') forming a continuous surface adjoining the continuous surface formed by the lower and outer contact surfaces (134 ', 154') of the first bearing member (123 ') in an interface (129); a channel (142) formed on at least one external contact surface (134 ') of the first bearing member (123'), the channel (142) comprising a notch defining a flat surface interrupting a circular cross-sectional shape of the surface of external contact (134 '); and at least one other channel (142) formed on at least one internal contact surface (144 ') of the second bearing member (125').
[0008]
8. Bearing (127, 127 ') for a downhole tool (100, 100'), according to claim 7, characterized in that the lower contact surface is transversal to the external contact surface and the contact surface upper section is transversal to the internal contact surface.
[0009]
9. Bearing (127, 127 ') for a downhole tool (100, 100'), according to claim 8, characterized in that a chamfer or smooth curve provides a transition between the lower contact surface (154 ') and the external contact surface (134') and between the upper contact surface (158 ') and the internal contact surface (144').
[0010]
10. Bearing (127, 127 ') for a downhole tool (100, 100'), according to claim 7, characterized in that at least one other channel (142) is still formed on the upper contact surface ( 158 ') of the second bearing member (125').
[0011]
11. Method for cooling a bearing of a well tool below, characterized by the fact that it comprises: the flow of a fluid in a channel (142, 142 ') formed in a first bearing member comprising an external contact surface (134 , 134 ') defining an outer diameter, the first bearing member being located within a second bearing member comprising an inner contact surface defining an inner diameter, the inner diameter of the second bearing member being greater than the outer diameter of the first bearing member and the internal contact surface of the second bearing member being in sliding contact with the external contact surface of the first bearing member at an interface, the channel comprising a notch defining a flat surface interrupting a cross-sectional shape circular from the external contact surface; flow is fluid within at least one other channel (142, 142 ') formed on the internal contact surface (144, 144') of the second bearing member (122, 125 '); transferring heat from the first bearing member and the second bearing member to the fluid; and the fluid flow away from the first bearing member and the second bearing member.
[0012]
12. Method according to claim 11, characterized in that it further comprises the removal of at least one abrasive particle from the interface (126) between the first bearing member (123 ', 124) and the second bearing member (122 , 125 ').
[0013]
13. Method according to claim 11, characterized in that the fluid flow in at least one other channel comprises the fluid flow in a groove defining a closed flow path in an internal contact surface of the second bearing member .

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公开号 | 公开日

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CN103221628A|2013-07-24|

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BR112013007826A2|2016-06-21|

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WO2012044973A2|2012-04-05|

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EP2622167A2|2013-08-07|

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CN103221628B|2016-03-16|

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CA2813446C|2016-08-16|

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WO2012044973A3|2012-07-19|

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EP2622167A4|2017-03-22|

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RU2580540C2|2016-04-10|

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ZA201302613B|2014-10-29|

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RU2013120095A|2014-11-20|

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MX2013003700A|2014-04-14|

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CA2813446A1|2012-04-05|

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US20140301679A1|2014-10-09|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US1890887A|1929-06-26|1932-12-13|Chicago Pneumatic Tool Co|Earth boring apparatus|

---

US2272128A|1940-11-28|1942-02-03|Osbourne Alan|Marine propeller|

---

US3476446A|1967-06-08|1969-11-04|Smith International|Rock bit and bearing|

---

US4141605A|1976-07-02|1979-02-27|Eastman Whipstock, Inc.|Bearing|

---

US4151686A|1978-01-09|1979-05-01|General Electric Company|Silicon carbide and silicon bonded polycrystalline diamond body and method of making it|

---

US4232912A|1978-12-11|1980-11-11|Dresser Industries, Inc.|Earth boring bit with gridded ferrous bearing surface|

---

US4386663A|1981-02-25|1983-06-07|Hughes Tool Company|Cooled journal bearing|

---

DE3150496C2|1981-12-19|1993-06-09|Mannesmann Ag, 4000 Duesseldorf, De|

---

US4569601A|1982-09-01|1986-02-11|Dresser Industries, Inc.|Wound wire bearing|

---

US4511307A|1983-09-02|1985-04-16|Dresser Industries, Inc.|Centrifugal pump|

---

SU1194990A1|1983-11-23|1985-11-30|Государственный Научно-Исследовательский И Проектный Институт Нефтяной Промышленности "Укргипрониинефть"|Section of roller bit and method of mounting same|

---

US4555186A|1984-02-10|1985-11-26|Dresser Industries, Inc.|Amorphous alloy plain bearings|

---

US4593776A|1984-03-28|1986-06-10|Smith International, Inc.|Rock bits having metallurgically bonded cutter inserts|

---

US4802539A|1984-12-21|1989-02-07|Smith International, Inc.|Polycrystalline diamond bearing system for a roller cone rock bit|

---

US4738322A|1984-12-21|1988-04-19|Smith International Inc.|Polycrystalline diamond bearing system for a roller cone rock bit|

---

US4620803A|1985-07-26|1986-11-04|Edward Vezirian|Friction bearing couple|

---

JPH0647991B2|1986-05-15|1994-06-22|三菱電機株式会社|Scroll compressor|

---

AT85841T|1986-05-19|1993-03-15|Smith International|COOLING NETWORKS FOR BEARING AREAS MADE OF POLYCRYSTALLINE DIAMOND.|

---

DE3619828A1|1986-06-12|1987-12-17|Rothemuehle Brandt Kritzler|AXIAL PRESSURE OR - BEARING BEARINGS, ESPECIALLY FOR SLOWLY TURNING MACHINES|

---

US4732491A|1986-08-27|1988-03-22|Smith International, Inc.|Downhole motor bearing assembly|

---

SU1539305A1|1987-02-19|1990-01-30|Научно-производственное объединение "Техника и технология добычи нефти"|Roller-type drill bit|

---

US4764036A|1987-05-14|1988-08-16|Smith International, Inc.|PCD enhanced radial bearing|

---

US4756631A|1987-07-24|1988-07-12|Smith International, Inc.|Diamond bearing for high-speed drag bits|

---

US4875532A|1988-09-19|1989-10-24|Dresser Industries, Inc.|Roller drill bit having radial-thrust pilot bushing incorporating anti-galling material|

---

US5112188A|1991-01-25|1992-05-12|Barnetche Gonzalez Eduardo|Multiple stage drag and dynamic turbine downhole motor|

---

US5133639A|1991-03-19|1992-07-28|Sta-Rite Industries, Inc.|Bearing arrangement for centrifugal pump|

---

RU2068069C1|1991-05-15|1996-10-20|Восточно-Сибирский научно-исследовательский институт геологии, геофизики и минерального сырья|Bearing assembly of roller-cutter drilling bit|

---

US5092687A|1991-06-04|1992-03-03|Anadrill, Inc.|Diamond thrust bearing and method for manufacturing same|

---

ZA942003B|1993-03-26|1994-10-20|De Beers Ind Diamond|Bearing assembly.|

---

US5679894A|1993-05-12|1997-10-21|Baker Hughes Incorporated|Apparatus and method for drilling boreholes|

---

CN1110764A|1994-11-19|1995-10-25|韩玉亮|Multi-stage pump axial force balance device|

---

US5593231A|1995-01-17|1997-01-14|Dresser Industries, Inc.|Hydrodynamic bearing|

---

US5655611A|1995-08-04|1997-08-12|Baker Hughes Inc.|Earth-boring bit with improved bearing seal|

---

US6068070A|1997-09-03|2000-05-30|Baker Hughes Incorporated|Diamond enhanced bearing for earth-boring bit|

---

WO1999031389A2|1997-12-18|1999-06-24|Baker Hughes Incorporated|Method of making stators for moineau pumps|

---

US6260635B1|1998-01-26|2001-07-17|Dresser Industries, Inc.|Rotary cone drill bit with enhanced journal bushing|

---

US6190050B1|1999-06-22|2001-02-20|Camco International, Inc.|System and method for preparing wear-resistant bearing surfaces|

---

KR100310444B1|1999-06-25|2001-09-29|이충전|An apparatus for lubricating a main shaft in a sealing type reciprocating compressor|

---

US6280089B1|1999-07-15|2001-08-28|Sunonwealth Electric Machine Industry Co., Ltd.|Rotational shaft for a non-ball type bearing|

---

US6460635B1|1999-10-25|2002-10-08|Kalsi Engineering, Inc.|Load responsive hydrodynamic bearing|

---

RU14621U1|2000-02-01|2000-08-10|Открытое акционерное общество "ГАЗ"|SLIDING BEARING|

---

US6454027B1|2000-03-09|2002-09-24|Smith International, Inc.|Polycrystalline diamond carbide composites|

---

JP2001295576A|2000-04-12|2001-10-26|Japan National Oil Corp|Bit device|

---

US7492069B2|2001-04-19|2009-02-17|Baker Hughes Incorporated|Pressurized bearing system for submersible motor|

---

US20030035603A1|2001-08-15|2003-02-20|V.W. Kaiser Engineering, Inc.|Thrust bushing for steering kingpin assembly|

---

US6684966B2|2001-10-18|2004-02-03|Baker Hughes Incorporated|PCD face seal for earth-boring bit|

---

US6652147B2|2001-12-20|2003-11-25|Sunonwealth Electric Machine Industry Co., Ltd.|Bearing structure|

---

UA80420C2|2002-01-30|2007-09-25|Composite material with compact abrasive layer|

---

US20040190804A1|2003-03-26|2004-09-30|Baker Hughes Incorporated|Diamond bearing with cooling/lubrication channels|

---

CN2670577Y|2003-12-24|2005-01-12|江西省宜春飞龙钻头制造有限公司|Roller cone bit with steel ball locking bearing structure|

---

SE530135C2|2004-09-21|2008-03-11|Sandvik Intellectual Property|Rock drill bit adapted for striking drilling|

---

US20070151769A1|2005-11-23|2007-07-05|Smith International, Inc.|Microwave sintering|

---

CN101025076A|2006-02-21|2007-08-29|霍利贝顿能源服务公司|Roller cone drill bit with enhanced debris diverter grooves|

---

US7703559B2|2006-05-30|2010-04-27|Smith International, Inc.|Rolling cutter|

---

EP2038507B1|2006-06-09|2010-05-12|Baker Hughes Incorporated|Surface textures for earth boring bits|

---

US20080056879A1|2006-08-30|2008-03-06|Schlumberger Technology Corporation|System and Method for Reducing Thrust Acting On Submersible Pumping Components|

---

TWI345355B|2007-06-11|2011-07-11|Sunonwealth Electr Mach Ind Co|Bearing structure|

---

US7896551B2|2007-10-15|2011-03-01|Us Synthetic Corporation|Hydrodynamic bearing assemblies, and hydrodynamic bearing apparatuses and motor assemblies using same|

---

US20090205873A1|2008-02-19|2009-08-20|Baker Hughes Incorporated|Downhole tool bearing system containing diamond enhanced materials|

---

US20110024198A1|2008-02-19|2011-02-03|Baker Hughes Incorporated|Bearing systems containing diamond enhanced materials and downhole applications for same|

---

US8277124B2|2009-02-27|2012-10-02|Us Synthetic Corporation|Bearing apparatuses, systems including same, and related methods|

---

MX342232B|2010-10-01|2016-09-21|Element Six Ltd|Bearings for downhole tools, downhole tools incorporating such bearings, and methods of cooling such bearings.|US9574405B2|2005-09-21|2017-02-21|Smith International, Inc.|Hybrid disc bit with optimized PDC cutter placement|

---

US8672060B2|2009-07-31|2014-03-18|Smith International, Inc.|High shear roller cone drill bits|

---

MX342232B|2010-10-01|2016-09-21|Element Six Ltd|Bearings for downhole tools, downhole tools incorporating such bearings, and methods of cooling such bearings.|

---

US9909365B2|2011-04-29|2018-03-06|Baker Hughes Incorporated|Downhole tools having mechanical joints with enhanced surfaces|

---

US8672550B1|2011-08-19|2014-03-18|Us Synthetic Corporation|Cooling-enhanced bearing assemblies, apparatuses, and motor assemblies using the same|

---

US10260560B2|2013-12-04|2019-04-16|Us Synthetic Corporation|Compact bearing assemblies including superhard bearing surfaces, bearing apparatuses, and methods of use|

---

US9657528B2|2014-10-28|2017-05-23|PDB Tools, Inc.|Flow bypass compensator for sealed bearing drill bits|

---

WO2017106708A1|2015-12-18|2017-06-22|National Oilwell Varco, L.P.|Microfluidic-assisted hydrodynamic lubrication system and method|

---

US10538967B2|2015-12-30|2020-01-21|Halliburton Energy Services, Inc.|Bearing assembly for drilling a subterranean formation|

---

WO2018044599A1|2016-08-29|2018-03-08|Halliburton Energy Services, Inc.|Stabilizers and bearings for extreme wear applications|

---

RU2634676C1|2016-10-19|2017-11-02|Андрей Георгиевич Ищук|Support of rolling cutter drilling bit|

---

RU2655065C1|2016-12-07|2018-05-23|Производственно-торговое общество с ограниченной ответственностью "АГРОСТРОЙ"|Drilling bit roller cutter bearing support|

---

RU2654902C1|2017-02-02|2018-05-23|Производственно-торговое общество с ограниченной ответственностью "АГРОСТРОЙ"|Drilling bit roller cutter support|

---

US10941779B2|2017-04-07|2021-03-09|Baker Hughes, A Ge Company, Llc|Abrasion resistant inserts in centrifugal well pump stages|

---

RU2670456C1|2017-11-21|2018-10-23|Дмитрий Юрьевич Сериков|Drilling bit support|

---

US11098541B2|2018-03-16|2021-08-24|Ulterra Drilling Technologies, L.P.|Polycrystalline-diamond compact air bit|

---

US10363786B1|2018-03-23|2019-07-30|Federal-Mogul Motorparts Llc|Ball socket assembly with a low friction bearing|

---

US11268570B2|2018-06-19|2022-03-08|Us Synthetic Corporation|Bearing assemblies, related bearing apparatuses and related methods|

---

CN110984921B|2019-12-26|2021-10-29|东北石油大学|Artificial lifting device and artificial lifting method applied to low-yield well|

---

US11111958B1|2020-03-03|2021-09-07|Schaeffler Technologies AG & Co. KG|Hydrodynamic bearing|

法律状态:
2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

---

2019-08-06| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

---

2020-02-27| B06A| Patent application procedure suspended [chapter 6.1 patent gazette]|

---

2020-06-09| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2020-09-29| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 30/09/2011, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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US38899810P| true| 2010-10-01|2010-10-01|

---

US61/388,998|2010-10-01|

---

PCT/US2011/054293|WO2012044973A2|2010-10-01|2011-09-30|Bearings for downhole tools, downhole tools incorporating such bearings, and methods of cooling such bearings|

---