Classifications

• • E—FIXED CONSTRUCTIONS
  • E21—EARTH OR ROCK DRILLING; MINING
  • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
  • E21B3/00—Rotary drilling
  • E21B3/02—Surface drives for rotary drilling
  • E21B3/022—Top drives
• • E—FIXED CONSTRUCTIONS
  • E21—EARTH OR ROCK DRILLING; MINING
  • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
  • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
  • E21B19/16—Connecting or disconnecting pipe couplings or joints
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
  • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
  • F16C23/06—Ball or roller bearings
  • F16C23/08—Ball or roller bearings self-adjusting
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
  • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
  • F16C27/066—Ball or roller bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C3/00—Shafts; Axles; Cranks; Eccentrics
  • F16C3/02—Shafts; Axles
  • F16C3/023—Shafts; Axles made of several parts, e.g. by welding
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2352/00—Apparatus for drilling
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
  • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
  • F16C35/07—Fixing them on the shaft or housing with interposition of an element
  • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring

Definitions

• the disclosure is directed to an apparatus including a bearing housing fixed in one direction and moveable in a second, perpendicular direction, along with methods of using such bearing housings and apparatuses.
• the present disclosure encompasses an apparatus, which has a first housing defining an opening; and a bearing housing disposed in the opening so that movement of at least a portion of the bearing housing within the first housing and along a first axis is permitted, the bearing housing defining first and second bearing surfaces, the first and second bearing surfaces being spaced apart along a second axis to prevent movement of the bearing housing within the first housing and along the second axis, the second axis being perpendicular to the first axis.
• the bearing housing is at least substantially annular in shape and defines an outside diameter; wherein the opening is at least substantially cylindrical in shape, and defines a center and an inside diameter of the first housing that passes through the center, the inside diameter of the first housing being greater than the outside diameter of the bearing housing; wherein the first axis extends radially through the center; and wherein the second axis extends longitudinally through the center.
• the present disclosure also encompasses a method including: disposing a bearing housing in an opening defined by a first housing; permitting movement of the bearing housing within the first housing and along a first axis; and preventing movement of the bearing housing within the first housing and along a second axis, the second axis being perpendicular to the first axis.
• Top drive systems are used to rotate a drill string made up of tubulars within a wellbore.
• Some top drives include a quill that provides vertical float between the top drive and the drill string, where the quill is usually threadedly connected to an upper end of a tubular of the drill string to transmit torque and rotary movement to the drill string.
• the quill may be indirectly linked to the drill string through a clamp, for example.
• drilling, drilling fluids or drilling mud are delivered to the drill string through a washpipe system connected to the quill. From the top drive and associated wash pipe, the fluids are transported and supplied to the drill string through the quill. Sometimes additional drilling fluids such as cement, chemicals, epoxy resins, etc. are also delivered downhole via the same system.
• the washpipe system often has multiple components. Due to imperfections that come with the machining process, as well as wear on components once in use, there can be a difference between two diameters on a single component. Effectively, the center lines of two diameters of one component are not shared perfectly. Instead, there is a distance between the two center lines. Stacking multiple components introduces additional center lines that may not be shared, and the distance between center lines can increase. If the objective is to guide this stacked set of components on a common center, the distance between center lines will be forced to zero, introducing forces into the components.
• the present disclosure is directed to apparatuses and methods to address this problem of undesired forces in the components.
• the present disclosure provides a unique structural arrangement that supports a bearing and/or bearing housing such that it absorbs the differences between components' center lines, or radial runout, by allowing motion of the bearing and/or bearing housing in the radial direction while preventing movement in a longitudinal direction. Absorbing radial runout reduces the forces introduced into the components.
• FIG. 1 is a schematic of an apparatus according to one or more aspects of the present disclosure.
• FIG. 2A is a sectional view of an apparatus according to one or more aspects of the present disclosure.
• FIG. 2B is an enlarged sectional view of a portion of the apparatus shown in FIG 2A.
• FIG. 3 is a flow chart illustration of a method of operating the apparatus of FIG. 2A, according to one or more aspects of the present disclosure.
• first and second features are formed in direct contact
• additional features may be formed interposing the first and second features, such that the first and second features may not be in direct contact.
• the present disclosure is directed to apparatuses and methods having a unique structural arrangement that support a bearing and/or bearing housing such that it absorbs radial runout by allowing motion of said bearing and/or bearing housing in one direction, e.g., the radial direction, while maintaining rigidity in a second, perpendicular direction, e.g., axial rigidity (face parallelism).
• FIG. 1 illustrated is a schematic view of an apparatus 100 demonstrating one or more aspects of the present disclosure.
• the apparatus 100 is or includes a land-based drilling rig.
• a land-based drilling rig such as jack-up rigs, semisubmersibles, drill ships, coil tubing rigs, well service rigs adapted for drilling and/or re-entry operations, and casing drilling rigs, among others within the scope of the present disclosure.
• the apparatus 100 includes a mast 105 supporting lifting gear above a rig floor 110.
• the lifting gear includes a crown block 115 and a traveling block 120.
• the crown block 1 15 is coupled at or near the top of the mast 105, and the traveling block 120 hangs from the crown block 115 by a drilling line 125.
• One end of the drilling line 125 extends from the lifting gear to drawworks 130, which is configured to reel out and reel in the drilling line 125 to cause the traveling block 120 to be lowered and raised relative to the rig floor 1 10.
• the other end of the drilling line 125 known as a dead line anchor, is anchored to a fixed position, possibly near the drawworks 130 or elsewhere on the rig.
• a hook 135 is attached to the bottom of the traveling block 120.
• a top drive 140 is suspended from the hook 135.
• a quill 145 extending from the top drive 140 is attached to a saver sub 150, which is attached to a drill string 155 suspended within a wellbore 160.
• the quill 145 may be attached to the drill string 155 directly. It should be understood that other conventional techniques for arranging a rig do not require a drilling line, and these are included in the scope of this disclosure.
• the drill string 155 includes interconnected sections of drill pipe 165, a bottom hole assembly (BHA) 170, and a drill bit 175.
• the bottom hole assembly 170 may include stabilizers, drill collars, and/or measurement- while-drilling (MWD) or wireline conveyed instruments, among other components.
• the drill bit 175, which may also be referred to herein as a tool, is connected to the bottom of the BHA 170 or is otherwise attached to the drill string 155.
• One or more pumps 180 may deliver drilling fluid to the drill string 155 through a hose or other conduit 185, which may be fluidically and/or actually connected to the top drive 140.
• This embodiment includes an apparatus 200 that may be referred to as a floating bearing apparatus disposed between the top drive 140 and the quill 145. The apparatus 200 is described more fully further below.
• the top drive 140 is used to impart rotary motion to the drill string 155.
• aspects of the present disclosure are also applicable or readily adaptable to implementations utilizing other drive systems, such as a power swivel, a rotary table, a coiled tubing unit, a downhole motor, and/or a conventional rotary rig, among others.
• the apparatus 100 also includes a control system 190 configured to control or assist in the control of one or more components of the apparatus 100.
• the control system 190 may be configured to transmit operational control signals to the drawworks 130, the top drive 140, the BHA 170 and/or the pump 180.
• the control system 190 may be a stand-alone component installed near the mast 105 and/or other components of the apparatus 100. In some embodiments, the control system 190 is physically displaced at a location separate and apart from the drilling rig.
• the washpipe system depicted often has multiple components. Due to imperfections that come with the machining process, there can be a difference between two diameters on a single component, or runout between two diameters on a single component. Effectively, the center lines of two diameters of one component are not shared perfectly. Instead, there is a distance between the two center lines, which is often referred to as the total indicated runout (TIR). The runout between two diameters is twice the TIR. Stacking multiple components introduces additional center lines that may not be shared, and the distance between center lines can increase. This can lead to an increase in the TIR. If the objective is to guide this stacked set of components on a common center, the distance between center lines will be forced to zero, introducing forces into the components. Such forces can, for example, cause premature wear or even component failure.
• TIR total indicated runout
• FIGS. 2A and 2B show an exemplary embodiment of the apparatus 200 referenced in FIG. 1 that allows for TIR, and therefore, reduces the creation of forces, such as a bending moment, within components of the apparatus 200.
• the apparatus 200 connects to, or is driven by, the top drive 140 (FIG. 1).
• the apparatus 200 is divided into sections. Accordingly, as referenced in FIG. 2A, the apparatus 200 includes a first stationary section 202 and a second rotating and reciprocating section 204.
• the stationary section 202 connects with a non-rotating portion of the top drive 140, for example, and the rotating and reciprocating section 204 connects to a tubular of the drill string 155 (FIG. 1) to make a part of a well casing.
• a fluid flow passage 206 having a longitudinal axis 208 extends through both the stationary section 202 and the rotating and reciprocating section 204.
• An inlet 210 to the flow passage 206 is formed at the stationary section 202, and provides fluid to the quill 145 connected to the rotating and reciprocating section 204.
• a bonnet or housing 216 is disposed over both the stationary section 202 and the rotating and reciprocating section 204.
• the housing 216 is rigidly connected to the stationary section 202 and includes an intermediate support section 217 extending radially inwardly.
• the intermediate support section 217 supports at least a portion of the stationary section 202 and the rotating and reciprocating section 204.
• an opening exists in the intermediate support section 217, the opening having a longitudinal axis arranged in parallel or "at least substantially” (e.g., within 10 degrees) parallel to a longitudinal axis of the stationary section 202 and/or the rotating and reciprocating section 204.
• the opening is at least substantially cylindrical in shape and defines a center and an inside diameter of the housing 216 that passes through the center.
• the axis 208 extends longitudinally through the center of the opening of the intermediate support section 217.
• the stationary section 202 includes an upper connection 218, a housing fixture 220 coupling the upper connection 218 to the housing 216, and a first portion 224a of a rotational seal 224.
• the upper connection 218 is a rigid element forming a portion of the fluid flow passage 206.
• the housing fixture 220 also forms a portion of the fluid flow passage 206 and is coupled to a flange 226 securing the housing 216 in place.
• the rotating and reciprocating section 204 includes a second portion 224b of the rotational seal 224, a first rotating component 228, a turn lock adapter 230, a washpipe referred to herein as a conduit 232, and a reciprocating assembly 234.
• the second portion 224b of the rotational seal 224 abuts the first portion 224a of the rotational seal 224, coupling the stationary section 202 and the rotating and reciprocating section 204 in a sealed and rotatable matter. Accordingly, the first and second portions 224a, 224b of the rotational seal 224 accommodate rotation while preventing fluid ingress and egress between the fluid flow passage 206 and the outer environment.
• the first rotating component 228 is fixedly connected to, and may carry the second portion 224b of the rotational seal 224. It attaches to an extending flange portion 236 that extends over the intermediate support section 217 of the housing 216, preventing the first rotating component 228 from passing through the housing 216.
• the first rotating component 228 is coupled to the turn lock adapter 230.
• the turn lock adapter 230 forms a portion of the fluid flow passage 206.
• the turn lock adapter 230 extends through the opening in the intermediate support section 217.
• the apparatus 200 includes a plurality of bearing assemblies or bearings 238 and 240.
• the plurality of bearings 238 and 240 are disposed between a bearing housing 242 and the turn lock adapter 230.
• the bearings 238 and 240 are radial bearings.
• the bearings 238 and 240 are continuous rings.
• the bearings 238 and 240 are independently selected, e.g., such that one is a set of radial bearings and the other is a continuous ring.
• the bearings 238 and 240 have an outer surface corresponding to an outer diameter and have an inner surface corresponding to an inner diameter.
• the outer diameter of the bearing 238 is equal to or "at least substantially similar” (e.g., difference between diameters within +/- 10% of smaller diameter) to the outer diameter of the bearing 240.
• the inner diameter of the bearing 238 is equal to or at least substantially similar to the inner diameter of the bearing 240.
• the bearing 238 has an upper bearing surface and a lower bearing surface, and a bearing height between its upper bearing surface and its lower bearing surface measured in a direction along the axis 208.
• the bearing 240 has an upper bearing surface and a lower bearing surface, and a bearing height between its upper bearing surface and its lower bearing surface measured in a direction along the axis 208.
• the apparatus 200 may have any number of bearings or bearing assemblies.
• the bearing housing 242 is contained within the opening in the intermediate support section 217.
• the bearing housing 242 includes an annular sealing element, such as an O-ring 244, disposed between the outside surface of the bearing housing 242 and an inside surface of the opening of the intermediate section 217.
• the O-ring 244 typically extends circumferentially around the bearing housing 242.
• an annular groove is formed in the outside surface of the bearing housing 242, and the O-ring 244 extends within the annular groove.
• respective annular grooves are formed in the outside surface of the bearing housing 242 and the inside surface of the opening, and the O-ring 244 and an annular sealing element, such an as an O-ring 246 extend within the respective annular grooves.
• an inside diameter of the O-ring 244 is less than an outside diameter of the bearing housing 242.
• the outside diameter of the bearing housing 242 is less than a diameter of the inside surface of the opening of the intermediate support section 217, creating a housing clearance. That is, the difference between the diameter of the inside surface of the opening of the intermediate support section 217 and the outside diameter of the bearing housing 242 is equal to the housing clearance in this embodiment.
• the housing clearance is equal to the runout associated with components of the apparatus 200. In one embodiment, the housing clearance is equal to the runout that is associated with components of the apparatus 200 and that is to be allowed within the floating bearing system. In one embodiment, the housing clearance equals to the runout associated with components of the apparatus 200 so that radial translation of the bearing housing 242 absorbs the runout associated with components of the apparatus 200.
• the housing clearance is equal to the TIR associated with components of the apparatus 200. In one embodiment, the housing clearance is equal to the TIR that is associated with components of the apparatus 200 and that is to be allowed within the apparatus 200. In one embodiment, the housing clearance equals to the TIR associated with components of the apparatus 200 so that the radial translation of the bearing housing 242 absorbs the TIR associated with components of the apparatus 200. In one embodiment, the outside diameter of the bearing housing 242 correlates to the expected runout or TIR within the components. In one embodiment, the radial translation of the bearing housing 242 is along a transverse axis 247 of the bearing housing 242. In one embodiment, the transverse axis 247 of the bearing housing 242 is perpendicular to the axis 208. In one embodiment, the transverse axis 247 extends radially through the center of the opening of the intermediate support structure 217.
• the bearing housing 242 has an upper surface spaced along the axis 208 and a lower surface spaced along the axis 208.
• a bearing housing height is the distance between the upper surface of the bearing housing 242 and the lower surface of the bearing housing 242 measured along the axis 208.
• the bearing housing height is greater than the bearing height of the bearing 238 or the bearing height of the bearing 240 or both.
• the upper surface of the bearing housing 242 extends above the upper bearing surface of the bearing 238.
• the lower surface of the bearing housing 242 extends below the lower bearing surface of the bearing 240.
• an annular groove is formed in an inside surface of the bearing housing 242, and the bearings 238 and 240 extend within the annular groove.
• the bearings 238, 240 may be arranged so as to not contact the upper or lower surface of the bearing housing 242.
• the bearing housing 242 has a flat bearing 248 located above the upper surface of the bearing housing 242 to maintain axial alignment of the bearing housing 242 with the axis 247. In one embodiment, the bearing housing 242 has a flat bearing 250 located below the lower surface of the bearing housing 242 to maintain axial alignment of the bearing housing 242 with the axis 247. In one embodiment, a loading nut applies pressure to the flat bearings 248 and 250 so that the bearing housing 242 does not rotate about the axis 208 while translating in the radial direction along the transverse axis 247. In one embodiment, any type of fastener may be used to apply pressure to the flat bearings 248 and 250.
• the flat bearings 248 and 250 engage the bearing housing 242 to prevent movement of the bearing housing 242 along the axis 208.
• the flat bearings 248 and 250 are radial and have an inner diameter and an outer diameter.
• the inner diameter of the flat bearings 248 and 250 is equal to or greater than the outer diameter of the bearings 238 and 240.
• the flat bearings 248 and 250 do not contact the bearings 238 and 240 so that at least a portion of the bearings 238 and 240 are free to rotate about the axis 208.
• the outer diameter of the flat bearings 248 and 250 are equal to or substantially similar to the outer diameter of the bearing housing 242.
• the flat bearings 248 and 250 are Garlock DU bearings.
• the bearing housing 242 is manufactured from a commercially available bearing material, such as SAE 630.
• the turn lock adapter 230 is fixedly engaged with the washpipe or conduit 232.
• the conduit 232 is a piston of a top drive 140. Accordingly, the conduit 232 rotates with the turn lock adapter 230.
• the conduit 232 is configured to form a portion of the fluid flow passage 206.
• the conduit 232 includes a body 252 that extends through the opening of the intermediate section 217 toward the quill 145.
• a lower end 254 of the conduit 232 has an outer diameter matching that of the body 252 of the conduit.
• a sleeve 256 is configured to receive the lower end 254 of the conduit 232.
• a diameter of an opening of the sleeve 256 is greater than the outer diameter of the lower end 254.
• the quill 145 includes an inner fluid flow passage and is configured to receive a lower end of the sleeve 256. Accordingly, the diameter of the inner fluid flow passage of the quill 145 is greater than an outer diameter of the lower end of the sleeve 256.
• the summation of runout associated with the quill 145, the sleeve 256, the conduit 232, or any combination thereof results in a longitudinal axis of the turn lock adapter 230 being offset from the axis 208 by a cumulative TIR. Instead of forcing a longitudinal axis of the turn lock adapter 230 to rotate about the axis 208, the turn lock adapter 230 may rotate about its longitudinal axis because of the housing clearance.
• a method of reducing bending moment within stacked components, by operating the apparatus 200 is generally referred to by the reference numeral 300.
• the bearing housing 242 is disposed in the opening of the intermediate support structure 217.
• movement of the bearing housing 242 along the axis 247 is permitted in a first direction. Movement is permitted along the axis 247 due to the difference between the diameter of the inside surface of the opening of the intermediate support section 217 and the outside diameter of the bearing housing 242. In an exemplary embodiment, this difference, or the housing clearance, correlates to the amount of TIR or runout that will be absorbed by the apparatus 200. Thus, movement in the first direction is permitted to absorb the runout.
• the outside diameter of the bearing housing 242 is based on the expected runout of the components. That is, as the expected runout increases, the outside diameter of the bearing housing 242 decreases. In one embodiment, the movement in the first direction is equal to or lesser than the runout.
• step 315 movement of the bearing housing 242 along the axis 208 is prevented.
• movement is prevented along the axis 208 due to the flat bearing 248 engaging the upper surface of the bearing housing 242 and the flat bearing 250 engaging the lower surface of the bearing housing 242.
• Pressure can be applied, using the flat bearings 248 and 250, in a direction along the axis 208 to secure the bearing housing 242 at a location along the axis 208.
• the bearing housing 242 is urged to move in a second direction along the axis 247, where the second direction is opposite the first direction.
• the annular sealing element such as the O-ring 244 urges the bearing housing 242 to move in the second direction along the axis 247.
• compression characteristics of the O-ring 244 correlate to the urging of the bearing housing 242 along the axis 247.
• a thickness of the O-ring 244 correlates to the urging of the bearing housing 242 along the axis 247.
• the O-ring 244 can be compressed by the TIR.
• a hardness of the annular sealing elements correlates to the urging of the bearing housing 242 along the axis 247 and/or to vibration dampening within the apparatus 200.
• the material of the annular sealing elements correlates to the urging of the bearing housing 242 along the axis 247 and/or to vibration dampening within the apparatus 200.
• a cross- sectional shape of the annular sealing element correlates to the urging of the bearing housing 242 along the axis 247 and/or the vibration dampening within the apparatus 200.
• a Quad-Seal, H-Seal, or any other variety of seal can correlate to vibration dampening characteristics within the apparatus 200.
• the annular sealing element may be a spring-energized lip seal or O-ring loaded lip seal, such as a Parker PolyPak® Seal.
• one or more annular grooves in the outside surface of the bearing housing 242 is not associated with an annular sealing element.
• four annular grooves may be located on the outside surface of the bearing housing 242, but only two of the four annular grooves may have an annular sealing element located therein.
• the apparatus 200 includes any number of annular grooves and any number of annular sealing elements. In one embodiment, the number of annular sealing elements correlates to the urging of the bearing housing 242 along the axis 247 and/or to vibration dampening within the apparatus 200.
• the number of annular sealing elements may be altered to reduce or alter vibrations within the apparatus 200 while the apparatus is in operation. Additionally, before or after operation of the apparatus 200, an annular sealing element may be exchanged for an annular sealing element having a different hardness, thickness, shape, etc., or a combination thereof, to reduce or alter vibrations within the apparatus 200 while the apparatus is in operation.
• the annular sealing element characteristics, in combination with the number and placement of such annular sealing elements, can be adjusted to minimize or prevent undesirable levels of vibration during operation of the apparatus 200. In one embodiment, reducing or altering vibrations within the apparatus 200 while the apparatus 200 is in operation inhibits or prevents the apparatus 200 from resonating, or vibrating, at a frequency at which resonance of the apparatus 200, or a portion of the apparatus 200, occurs.
• the bearing housing 242 rotatably supports a first tubular member.
• the first tubular member is the turn lock adapter 230.
• a second tubular member is spaced from the first tubular member along the axis 208.
• the second tubular member is the quill 145.
• a third tubular member is coupled to at least one of the first and second tubular members so that the third tubular member extends between the first and the second tubular member.
• the third tubular member is the sleeve 256.
• the movement of the bearing housing 242 and/or bearings 238 and 240 reduces any bending movement experienced by the third tubular member or the sleeve 256.
• a fourth tubular member is coupled to at least one of the first and third tubular members so that the fourth tubular member extends between the first and the third tubular member.
• the fourth tubular member is the conduit 232.
• the movement of the bearing housing 242 and/or bearings 238 and 240 reduces any bending movement experienced by the fourth tubular member or the conduit 232.
• the radial translation or movement of the bearings 238 and 240 and/or bearing housing 242 of the apparatus 200 in the method 300 reduces a bending moment occurring within the conduit 232 or the sleeve 256 or both.
• the disclosure encompasses an apparatus, which has a first housing defining an opening; and a bearing housing disposed in the opening so that movement of at least a portion of the bearing housing within the first housing and along a first axis is permitted, the bearing housing defining first and second bearing surfaces, the first and second bearing surfaces being spaced apart along a second axis to prevent movement of the bearing housing within the first housing and along the second axis, the second axis being perpendicular to the first axis.
• the bearing housing is at least substantially annular in shape and defines an outside diameter; wherein the opening is at least substantially cylindrical in shape, and defines a center and an inside diameter of the first housing that passes through the center, the inside diameter of the first housing being greater than the outside diameter of the bearing housing; wherein the first axis extends radially through the center; and wherein the second axis extends longitudinally through the center.
• the difference between the outside diameter and the inside diameter limits the range of movement of the bearing housing within the first housing and along the first axis.
• the apparatus further has a compressible element disposed in the opening and between an outside surface of the bearing housing and an inside surface of the first housing that is defined by the opening.
• the compressible element is coupled to the bearing housing and compresses in response to movement of the bearing housing within the first housing and along the first axis.
• the apparatus further has a first flat bearing and a second flat bearing defining a third bearing surface and a fourth bearing surface, respectively; wherein the first and the second flat bearings are spaced along the second axis; and wherein the third and the fourth bearing surfaces engage the first and the second bearing surfaces, respectively, to prevent movement of the bearing housing within the first housing and along the second axis.
• the apparatus further has: a first tubular member around which the bearing housing circumferentially extends; a second tubular member spaced from the first tubular member along the second axis; and a third tubular member coupled to at least one of the first and the second tubular members and extending between the first and the second tubular members; wherein movement of the bearing housing within the first housing and along the first axis reduces any bending moment experienced by the third tubular member.
• the third tubular member is coupled to the second tubular member; wherein the apparatus further includes a fourth tubular member coupled to the first tubular member and extending between the first and the third tubular member, the fourth tubular member including an opposing first and a second end portion; and wherein movement of the bearing housing within the first housing and along the first axis reduces any bending moment experienced by the fourth tubular member.
• the first, second, and third tubular members define a first, a second, and a third internal passage, respectively; wherein the first end portion of the fourth tubular member extends within the first internal passage and at least the second end portion of the fourth tubular member extends within the third internal passage; and wherein at least a portion of the third tubular member extends within the second internal passage.
• the apparatus further has: a top drive; and a quill operably coupled to the top drive; wherein the second tubular member is part of the quill, the third tubular member is a sleeve of the top drive, and the fourth tubular member is a piston of the top drive.
• the apparatus further has a radial bearing disposed in the bearing housing, the radial bearing including; a first ring to engage a tubular member; and a second ring engaged with the bearing housing, the second ring extending circumferentially about, and spaced along the first axis from, the first ring.
• the apparatus further has a radial bearing disposed in the bearing housing, the radial bearing including: a first ring to engage a tubular member; and a second ring engaged with the bearing housing, the second ring extending circumferentially about, and spaced along the first axis from, the first ring; wherein the first flat bearing and the second flat bearing are generally annular in shape and define an inside diameter; and wherein the inside diameter of the first flat bearing and the second flat bearing is greater than or equals to a diameter of the second ring.
• the radial bearing is disposed in the bearing housing between the first bearing surface and the second bearing surface.
• the apparatus further includes: (a) a compressible element disposed in the opening and between an outside surface of the bearing housing and an inside surface of the first housing that is defined by the opening; (b) a radial bearing disposed in the bearing housing, the radial bearing comprising: (i) a first ring to engage a tubular member; and (ii) a second ring engaged with the bearing housing, the second ring extending circumferentially about, and spaced along the first axis from, the first ring; (c) a first flat bearing and a second flat bearing defining a third bearing surface and a fourth bearing surface, respectively; (i) wherein the first and the second flat bearings are spaced along the second axis; and (ii) wherein the third and the fourth bearing surfaces engage the first and the second bearing surfaces, respectively, to prevent movement of the bearing housing within the first housing and along the second axis; or (d) any combination of (a), (b), and (c).
• the present disclosure also introduces a method of using the apparatus that includes: spacing apart first and second tubular members; coupling a third tubular member to each of the first and second tubular members so that the third tubular member extends therebetween; rotatably supporting each of the first and second tubular members; and reducing any bending moment experienced by the third tubular member while rotatably supporting each of the first and second tubular members.
• first, second, and third tubular members extend longitudinally along the second axis; wherein rotatably supporting each of the first and second tubular members includes extending the first tubular member within the opening so that the bearing housing circumferentially extends around the first tubular member; and wherein reducing any bending moment experienced by the third tubular member during rotatably supporting each of the first and second tubular members includes: permitting movement of the bearing housing within the first housing and along the first axis; and preventing movement of the bearing housing within the first housing and along the second axis.
• the bearing housing moves in a first direction along the first axis; and wherein the method further includes urging the bearing housing to move in a second direction along the first axis in response to the movement of the bearing housing in the first direction along the first axis, the second direction being opposite to the first direction.
• the second tubular member is part of a quill operably coupled to a top drive
• the third tubular member is one of a sleeve and a piston associated with the top drive.
• the present disclosure also introduces a method including: disposing a bearing housing in an opening defined by a first housing; permitting movement of the bearing housing within the first housing and along a first axis; and preventing movement of the bearing housing within the first housing and along a second axis, the second axis being perpendicular to the first axis.
• the bearing housing is generally annular in shape and defines an outside diameter; wherein the opening is generally cylindrical in shape, and defines a center and an inside diameter of the first housing that passes through the center, the inside diameter of the first housing being greater than the outside diameter of the bearing housing; wherein the first axis extends radially through the center; and wherein the second axis extends longitudinally through the center.
• the difference between the outside diameter and the inside diameter limits the range of movement of the bearing housing within the first housing and along the first axis.
• the bearing housing moves in a first direction along the first axis; and wherein the method further includes urging the bearing housing to move in a second opposite direction along the first axis in response to the movement of the bearing housing in the first direction along the first axis.
• preventing movement of the bearing housing within the first housing and along the second axis includes engaging a first flat bearing and a second flat bearing against the bearing housing, the first flat bearing and the second flat bearing being spaced along the second axis.
• the method further includes: employing the bearing housing to rotatably support the first tubular member; spacing a second tubular member from the first tubular member along the second axis; and coupling a third tubular member to at least one of the first and second tubular members so that the third tubular member extends between the first and second tubular members; wherein movement of the bearing housing within the first housing and along the first axis reduces any bending moment experienced by the third tubular member.
• the method further includes coupling a fourth tubular member to at least one of the first and third tubular members so that the fourth tubular member extends between the first and third tubular members; wherein movement of the bearing housing within the first housing and along the first axis reduces any bending moment experienced by the fourth tubular member.
• the first, second, and third tubular members define first, second and third internal passages, respectively; wherein the first end portion of the fourth tubular member extends within the first internal passage and at least the second end portion of the fourth tubular member extends within the third internal passage; and wherein at least a portion of the third tubular member extends within the second internal passage.
• the second tubular member is part of a quill operably coupled to a top drive
• the third tubular member is a sleeve of the top drive
• the fourth tubular member is a piston of the top drive.
• employing the bearing housing to rotatably support the first tubular member includes disposing a radial bearing coupled to the first tubular member in the bearing housing, the radial bearing including: a first ring to engage the first tubular member; and a second ring engaged with the bearing housing, the second ring extending circumferentially about, and spaced along the first axis from, the first ring; wherein the first flat bearing and the second flat bearing are generally annular in shape and define an inside diameter; and wherein the inside diameter of the first flat bearing and the second flat bearing is greater than or equals to a diameter of the second ring.
• the bearing housing (a) is generally annular in shape and defines an outside diameter; (i) wherein the opening is generally cylindrical in shape, and defines a center and an inside diameter of the first housing that passes through the center, the inside diameter of the first housing being greater than the outside diameter of the bearing housing; (ii) wherein the first axis extends radially through the center; and (iii) wherein the second axis extends longitudinally through the center; (b) moves in a first direction along the first axis; and (i) wherein the method further includes urging the bearing housing to move in a second opposite direction along the first axis in response to the movement of the bearing housing in the first direction along the first axis; or (c) both (a) and (b).

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• Environmental & Geological Engineering (AREA)
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• 2013
  • 2013-04-26 US US13/871,679 patent/US20130284459A1/en not_active Abandoned
  • 2013-04-26 CA CA2869668A patent/CA2869668A1/fr active Pending
  • 2013-04-26 WO PCT/US2013/038499 patent/WO2013163603A1/fr not_active Ceased

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