Patent Publication Number: US-9834990-B2

Title: Bogey style torque bushing for top drive

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims priority from and the benefit of U.S. Provisional Application Ser. No. 61/746,873, entitled “Bogey Style Torque Bushing for Top Drive,” filed Dec. 28, 2012, which is hereby incorporated by reference in its entirety. 
    
    
     BACKGROUND 
     Embodiments of the present disclosure relate generally to the field of drilling and processing of wells. More particularly, present embodiments relate to a system and method for stabilizing a top drive during a drilling process, a casing process, or another type of well processing operation. 
     Top drives are typically utilized in well drilling and maintenance operations, such as operations related to oil and gas exploration. In conventional oil and gas operations, a well is typically drilled to a desired depth with a drill string, which includes drill pipe and a drilling bottom hole assembly (BHA). During a drilling process, the drill string may be supported and hoisted about a drilling rig by a hoisting system for eventual positioning down hole in a well. As the drill string is lowered into the well, a top drive system may rotate the drill string to facilitate drilling. 
     BRIEF DESCRIPTION 
     In accordance with one aspect of the disclosure, a top drive system includes a top drive, a bogey chassis, wherein the top drive is coupled with the bogey chassis, an upper bushing coupling the bogey chassis to a torque track, and a lower bushing coupling the bogey chassis to the torque track, wherein the upper and lower bushings are configured to translate along the torque track. 
     Another embodiment includes a system having a top drive, a torque bushing system coupled to the top drive comprising a first bushing and a second bushing, and a torque track system, wherein the torque bushing system is configured to absorb an overturning moment acting on the top drive and apply resultant linear forces to the torque track system. 
     In accordance with another aspect of the disclosure, a method includes suspending a top drive system with a hoist and a torque bushing system, applying an overturning moment to the top drive system, and applying resultant linear forces to a torque track system using first and second bushings of the torque bushing system to counterbalance the overturning moment. 
    
    
     
       DRAWINGS 
       These and other features, aspects, and advantages of present embodiments will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein: 
         FIG. 1  is a schematic of a well being drilled, in accordance with present techniques; 
         FIG. 2  is a side view of a top drive having a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 3  is a perspective view of a top drive having a bogey style torque bushing system, in accordance with present technique; 
         FIG. 4  is a side view of a top drive having a bogey style torque bushing system with a lateral extension mechanism in a retracted orientation, in accordance with present techniques; 
         FIG. 5  is a side view of a top drive having a bogey style torque bushing system with a lateral extension mechanism in an extended orientation, in accordance with present techniques; 
         FIG. 6  is a perspective view of a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 7  is a perspective view of a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 8  is a partial perspective view of a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 9  is a partial side view of a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 10  is a top sectional view of a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 11  is a top view of a bogey style torque bushing system, in accordance with present techniques; 
         FIG. 12  is a schematic of a bogey style torque bushing system, illustrating forces acting on the bogey style torque bushing system, in accordance with present techniques; and 
         FIG. 13  is a schematic of a bogey style torque bushing system, illustrating forces acting on the bogey style torque bushing system, in accordance with present techniques. 
     
    
    
     DETAILED DESCRIPTION 
     Torque bushings, along with a torque track, may be primarily designed to react to torsional forces along a vertical axis coming from a drilling rotation of a drill string. It is now recognized that top drive systems may have a center of gravity that is offset from a lifting axis or hanging load of the top drive system. Specifically, it is now recognized that the offset center of gravity may cause an overturning moment acting on the top drive system (e.g., around a horizontal axis), which may result in excessive or premature wear on top drive system components or other components coupled to the top drive system. Accordingly, there is a presently recognized need to absorb and/or account for overturning moments acting on a top drive system and related components. 
     Present embodiments provide a bogey style torque bushing system for a top drive system. Specifically, the bogey style torque bushing system is configured to absorb overturning moment reaction forces caused by the offset center of gravity of a top drive with respect to its lifting point and drill string axis. For example, the bogey style torque bushing system may couple the top drive to a torque track system of a derrick or other surface equipment. In certain embodiments, a top drive may be coupled to a bogey chassis of the bogey style torque bushing system, and the bogey chassis may be coupled to a torque track system by two or more bushings. As discussed in detail below, overturning moment reaction forces created by the top drive may act on respective centers of the bushings, which may be configured to transfer distributed direct normal forces (resulting from the overturning moment reaction forces) to the torque track system. In this manner, resultant forces caused by the overturning moment and acting on other components of the top drive system may be absorbed and distributed evenly throughout the torque bushing surface, while reducing premature and excessive wear on torque bushing components. Thus, present embodiments improve top drive performance and prolong the useful life of a top drive. 
     Turning now to the drawings,  FIG. 1  is a schematic of a drilling rig  10  in the process of drilling a well in accordance with present techniques. The drilling rig  10  features an elevated rig floor  12  and a derrick  14  extending above the rig floor  12 . A supply reel  16  supplies drilling line  18  to a crown block  20  and traveling block  22  configured to hoist various types of drilling equipment above the rig floor  12 . The drilling line  18  is secured to a deadline tiedown anchor  24 , and a drawworks  26  regulates the amount of drilling line  18  in use and, consequently, the height of the traveling block  22  at a given moment. Below the rig floor  12 , a drill string  28  extends downward into a wellbore  30  and is held stationary with respect to the rig floor  12  by a rotary table  32  and slips  34 . A portion of the drill string  28  extends above the rig floor  12 , forming a stump  36  to which another length of tubular  38  may be added. A top drive  40 , hoisted by the traveling block  22 , positions the tubular  38  above the wellbore before coupling with the tubular  38 . The top drive  40 , once coupled with the tubular  38 , may then lower the coupled tubular  38  toward the stump  36  and rotate the tubular  38  such that it connects with the stump  36  and becomes part of the drill string  28 . Specifically, the top drive  40  includes a quill  42  used to turn the tubular  38  or other drilling equipment. 
       FIG. 1  further illustrates the top drive  40  coupled to a bogey style torque bushing system  44 . More specifically, the bogey style torque bushing system  44  couples the top drive  40  to a torque track  46 . As discussed below, the center of gravity of the top drive  40  may not be centered above the quill  42  and/or tubular  38  (e.g., a hanging load of the top drive  40 ). Consequently, the top drive  40  may experience a moment or rotating force (e.g., an overturning moment), which is counterbalanced (e.g., counter reacted) by other features. For example, the torque track  46  of the top drive  40  may function to counterbalance (e.g., counter react) the moment. In other words, the torque track  46  (e.g., a torque bushing coupled to the torque track) may experience forces that counteract the overturning moment created by the unbalanced center of gravity of the top drive  40 . As a result, when this occurs on traditional systems, components of the torque track  46  (e.g., a torque bushing) may experience corresponding substantial wear. As discussed in detail below, in accordance with present embodiments, the bogey style torque bushing system  44  of the top drive  40  is configured to counteract the overturning moment created by the unbalanced center of gravity of the top drive  40  and direct distributed normal forces to the torque track  46 . In this manner, wear on the torque track  46  and other components of the top drive  40  caused by the overturning moment may be reduced. 
     It should be noted that the illustration of  FIG. 1  is intentionally simplified to focus on the top drive  40  with the bogey style torque bushing system  44  described in detail below. Many other components and tools may be employed during the various periods of formation and preparation of the well. Similarly, as will be appreciated by those skilled in the art, the orientation and environment of the well may vary widely depending upon the location and situation of the formations of interest. For example, rather than a generally vertical bore, the well, in practice, may include one or more deviations, including angled and horizontal runs. Similarly, while shown as a surface (land-based) operation, the well may be formed in water of various depths, in which case the topside equipment may include an anchored or floating platform. 
       FIG. 2  is a side view of an embodiment of the top drive  40  coupled to the torque track  46  with the bogey style torque bushing system  44 . As mentioned above, the top drive  40  may experience an overturning moment  50 , such as when the quill  42  and/or tubular  38  supported by the top drive  40  is not in line with the center of gravity of the top drive  40 . That is, the overturning moment  50  is caused by the top drive  40  center of gravity being offset from the lifting or hanging load axis. In order to absorb and counteract the overturning moment  50  experienced by the top drive  40 , the illustrated embodiment includes the bogey style torque bushing system  44 . 
     Specifically, the bogey style torque bushing system  44  includes a bogey chassis  52 , which is coupled to the top drive  40  and to the torque track  46  with bushings  54  (e.g., upper bushing  60  and lower bushing  62 ). In particular, the illustrated embodiment includes two bushings  54 . However, in other embodiments, additional bushings  54  may be used. As described in detail below, the use of two or more bushings  54  enables the absorption of the moments acting on the torque track  46 , as well as the distribution of resultant linear forces acting on the torque track  46  that are created by the overturning moment  50 . As shown, pinned connections  56  are used to couple the top drive  40  to the bogey chassis  52 . The pinned connections  56  secure the top drive  40  such that the top drive  40  does not move or translate along the bogey chassis  52 . In other words, the top drive  40  is fixed to the bogey chassis  52 . However, in other embodiments, the pinned (e.g., fixed) location of the top drive  40  along the length of the bogey chassis  52  may vary relative to the fixed position of the top drive  40  in the illustrated embodiment. As discussed below, the location of the top drive  40  along the bogey chassis  52  may partially determine the magnitude of the various forces acting on the bushings  54  of the bogey style torque bushing system  44 . 
     Furthermore, pinned connections  58  are used to couple the top drive  40  to the bushings  54 . In this manner, the bogey chassis  52  may absorb bending moments (e.g., moments with a horizontal axis) from the top drive  40 . However, bending moments may not be transferred through the bushings  54  individually due to the pinned connections  58  coupling the bogey chassis  52  to the bushings  54 . Instead, the overturning moment  50  will produce substantially evenly distributed resultant linear forces on each of the bushings  54 . For example, the overturning moment  50  in the illustrated embodiment will produce a liner force  64  in the upper bushing  60  and a linear force  66  in the lower bushing  62 . 
     As mentioned above, the pinned location of the top drive  40  along the bogey chassis  52  may affect the magnitude of various forces acting on the bushings  54 . For example, a torsion  68  acting on the top drive  40  (e.g., a drilling torque) may be transferred to the bushings  54 . That is, while the pinned connections  58  coupling the bogey chassis  52  to the bushings  54  may block transfer a moment with a horizontal axis (e.g., overturning moment  50 ), the pinned connections  58  may still transfer a moment with a vertical axis (e.g., torsion  68 ) to the bushings  54 . However, the location of the top drive  40  along the bogey chassis  52  may be selected to selectively distribute the forces caused by the torsion  68 . For example, in the illustrated embodiment, the top drive  40  is positioned along the bogey chassis  52  closer to the bottom bushing  62  than the top bushing  60 . As such, the bottom bushing  62  may experience greater forces (e.g., bending moments) resulting from the torsion  68  than the top bushing  60 . 
     The bushings  54  may have a variety of configurations. While each bushing  54  is configured to couple the bogey chassis  52  to the torque track  46 , each bushing  54  may also be configured to translate along the torque track  46 . For example, each bushing  54  may include low friction mechanisms, such as rollers or wheels, to enable the bushing  54  to slide or translate along the torque track  46 . As a result, the top drive  40  may be moved vertically to enable the positioning or landing of the tubular  38  or other equipment. Additionally, as described in detail below, the bogey style torque bushing system  44  may include features to enable to horizontal displacement of the top drive  40 . 
       FIG. 3  is a perspective view of an embodiment of the top drive  40  having the bogey style torque bushing system  44 . The illustrated embodiment includes similar elements and element numbers as the embodiment shown in  FIG. 3 . Additionally, the illustrated embodiment of the bogey style torque bushing system  44  includes a leveling system  100 . 
     As described above, the top drive  40  is coupled to the bogey chassis  52  by pinned connections  56 , and the bogey chassis  52  is coupled to the bushings  54  by pinned connections  58 . In the illustrated embodiment, the top drive  40 , the bogey chassis  52 , and the lower bushing  62  are all coupled by a single pinned connection  102 . That is, the lower pinned connection  56  and pinned connection  58  for the lower bushing  62  are the same single pinned connection  102 . As a result, the top drive  40  is positioned much closer to the lower bushing  62  than the upper bushing  60 . As such, a drilling torque or other torsion (e.g., torsion  68  of  FIG. 2 ) acting on the top drive  40  may produce resultant forces (e.g., moments) acting on the lower bushing  62  that are greater than resultant forces (e.g., moments) acting on the upper bushing  60  that are produced by a drilling torque or torsion. 
     Furthermore, the pinned connection  58  coupling the upper bushing  60  to the bogey chassis  52  includes the leveling system  100 . More specifically, the leveling system  100  includes an adjustable pin  104  that axially abuts a pin  106  of the pinned connection  58  coupling the upper bushing  50  and the bogey chassis  52 . In operation, the adjustable pin  104  may be adjusted to alter the orientation of central member  108  of the bogey chassis  52 . For example, the top drive  40  may be fixed (e.g., via pinned connections  56 ) to the central member  108  and outer members  110  of the bogey chassis  52 . As such, the outer members  110  are also fixed to the central member  108  of the bogey chassis  52 . Additionally, the central member  108  is coupled to the pinned connection  58  by pivoting members  112 . As the adjustable pin  104  is adjusted (e.g., via a threaded connection), the central member  108  of the bogey chassis  52  may pivot about the single pinned connection  102 , and the pivoting members  112  may accommodate the adjustment in the orientation of the central member  108 . In this manner, the levelness of the top drive  40  may be adjusted. 
       FIGS. 4 and 5  are side views of an embodiment of the top drive  40  having the bogey style torque bushing system  44 . The illustrated embodiments include similar elements and element numbers as the embodiment illustrated in  FIG. 2 . Additionally, the bogey style torque bushing system  44  of  FIGS. 4 and 5  includes a lateral extension mechanism  120 .  FIG. 4  shows the lateral extension mechanism  120  in a retracted position, and  FIG. 5  shows the lateral extension mechanism  120  in an extended position. 
     As shown, the lateral extension mechanism  120  extends from the bogey chassis  52 . Specifically, the lateral extension mechanism  120  includes pivoting arms  122 , which extend from the bogey chassis  52  and couple to the top drive  40 . For example, the lateral extension mechanism  120 , may include 2, 4, 6, 8, or more pivoting arms  122  that couple the top drive  40  to the bogey chassis  52 . As similarly described above, pinned connections  124  are used to couple the pivoting arms  122  to the top drive  40  and the bogey chassis  52 . 
     In the retracted position shown in  FIG. 4 , the pivoting arms  122  are substantially parallel with the torque track  46 , thereby positioning the top drive  40  adjacent to the torque track  46 . In the extended position shown in  FIG. 5 , the pivoting arms  122  of the lateral extension mechanism  120  swing out from the torque track  46 , thereby increasing the lateral distance between the top drive  40  and the torque track  46 . For example, the pivoting arms  122  may be pivoted outwardly using one or more hydraulic cylinders  126  or other actuation mechanisms. 
       FIGS. 6-11  illustrate various views of embodiments of the bogey style torque bushing system  44 . For example,  FIG. 6  is a perspective view of an embodiment of the bogey style torque bushing system  44 , illustrating the bushings  54  configured to couple to the torque track  46 .  FIG. 7  is another perspective view of an embodiment of the bogey style torque bushing system.  FIG. 8  is a partial perspective view of an embodiment of the bogey style torque bushing system  44 , illustrating a portion of the bushings  54 .  FIG. 9  is a partial side view of an embodiment of the bogey style torque bushing system  44 , partially illustrating the bushings  54  configured to couple to the torque track  46 .  FIG. 10  is a top sectional view of an embodiment of the bogey style torque bushing system  44 , and  FIG. 11  is a top view of an embodiment of the bogey style torque bushing system  44 . 
       FIGS. 12 and 13  are schematics of embodiments of the bogey style torque bushing system  44 , illustrating forces acting on the bogey style torque bushing system  44 . As shown in  FIG. 12 , the bogey style torque bushing system  44  has one bushing  54 . On the one bushing  54 , the overturning moment acting on the top drive  40  causes a reactionary coupling primarily near ends of the bushing  54 . These high forces on small areas of the bushing  54  cause high pressure. The wear on the wear or liner material of the bushing  54  is proportional to pressure times velocity. In  FIG. 13 , the bogey style torque bushing system  44  includes two bushings  54 . As such, the coupling force acting on the pinned connections  58  at the middle of each bushing  54  causes the reaction forces to be distributed evenly along the surface of the wear or liner material of the bushings  54 , thereby resulting in a lower pressure acting on the various points of the bushings  54 . 
     As discussed in detail above, embodiments of the present disclosure are directed towards the bogey style torque bushing system  44 . In the manner described above, the bogey style torque bushing system  44  is configured to absorb reaction forces caused by the overturning moment  50  acting on the top drive  40 . In certain embodiments, the overturning moment  50  is created when the center of gravity of the top drive  40  is not aligned with the hanging load of the top drive  40 . The bogey style torque bushing system  44  may couple the top drive  40  to the torque track  46  of the derrick  14  or to other surface equipment. In certain embodiments, the bogey style torque bushing system  44  includes the bogey chassis  52  which couples to the top drive  40 . The bogey chassis  52  further couples to two or more bushings  54 , which are connected to the torque track  46 . As discussed in detail above, overturning moment  50  reaction forces created by the top drive  40  may be applied at respective centers (e.g., axial midpoints) of the bushings  54 . Specifically, the bushings  54  may be configured to transfer a distributed direct normal force to the torque track  46 . In this manner, forces caused by the overturning moment  50  and acting on other components of the top drive  40  may be absorbed, while reducing premature and excessive wear on torque bushing components. 
     While the present disclosure may be susceptible to various modifications and alternative forms, specific embodiments have been shown by way of example in the drawings and tables and have been described in detail herein. However, it should be understood that the embodiments are not intended to be limited to the particular forms disclosed. Rather, the disclosure is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the disclosure as defined by the following appended claims. Further, although individual embodiments are discussed herein, the disclosure is intended to cover all combinations of these embodiments.