Patent Application
20160230479
This specification generally relates to a tool and method for absorbing axial and torsional shock loads in a drilling string.
In connection with the recovery of hydrocarbons from the earth, wellbores are generally drilled using a variety of different methods and equipment. According to one common method, a roller cone bit or fixed cutter bit is rotated against the subsurface formation to form the wellbore. The drill bit is rotated in the wellbore through the rotation of a drill string attached to the drill bit and/or by the rotary force imparted to the drill bit by a subsurface drilling motor powered by the flow of drilling fluid down through the drill string and through the drilling motor.
Downhole vibrations and shocks (referred to collectively and/or interchangeably herein as “shock loads”) are induced by interactions between the rotating bit and various types of hard rock and/or “sticky” earth formations at or near the floor of the wellbore. Shock loads induced at the drill bit are in turn transmitted to other components of the bottomhole assembly, as well as to the supporting drill string. Shock loads imparted on the drill string can diminish the life of its interconnected members by accelerating the process of fatigue. Additionally, excessive shock loads can cause spontaneous downhole equipment failure, wash-outs and a decrease in penetration rate.
Axial shock loads tend to cause a condition known as “bit bounce,” where the drill bit momentarily lifts up and loses contact with the floor of the wellbore. Bit bounce is known to cause acute damage to bit cutters and supporting bearings. Torsional shock loads are often caused by a phenomenon known as “stick-slip.” Stick-slip occurs when the drill bit stalls (e.g., drags or stops rotating completely) due to friction with the earth formations in the wellbore. When the drill bit stalls, typically, the attached drill string continues to turn, which can result in damage to the drill string and/or other components of the bottomhole assembly. Even if the operating torque applied through the drill string eventually succeeds in breaking the bit free of the formation, (i.e., overcoming the friction torque load on the bit resulting in a stall), the sudden release of the bit can cause it to rotate faster than the drill string. Stick-slip can cause problems in the operation of the drilling assembly and in the formation of the wellbore. In some cases, severe stick-slip can cause strong lateral vibrations in the drill string, which are also damaging.
Downhole shock loads are a major contributor to the failure of various components of the downhole equipment. Downhole shock loads may also cause damage to the wellbore itself (e.g., when lateral vibrations cause the drill string to contact the walls of the wellbore). Thus, mitigation of downhole shock loads is key to avoiding non-productive time and preventing equipment damage
Many of the features are exaggerated to better show the features, process steps, and results. Like reference numbers and designations in the various drawings indicate like elements.
The wellbore 12 can be drilled by rotating the drill string 14, and therefore the drill bit 24, using a rotary table or top drive, and/or by rotating the drill bit with rotary power supplied to the subsurface motor 22 by the circulating drilling fluid. A shock tool assembly 100 in accordance with one or more concepts of the present disclosure is positioned below the subsurface motor 22. As described below, the shock tool assembly 100 absorbs both axial and torsional shock loads generated as the rotating drill bit 24 cuts through earth to create the wellbore 12.
In the foregoing description of the drilling rig 10, various items of equipment, such as pipes, valves, pumps, fasteners, fittings, etc., may have been omitted to simplify the description. However, those skilled in the art will realize that such conventional equipment can be employed as desired. Those skilled in the art will further appreciate that various components described are recited as illustrative for contextual purposes and do not limit the scope of this disclosure. Further, while the drilling rig 10 is shown in an arrangement that facilitates straight downhole drilling, it will be appreciated that directional drilling arrangements are also contemplated and therefore are within the scope of the present disclosure.
In this example, the housing 204 is a multi-component sub-assembly, including a splined housing 204a, a spring housing 204b, and a piston housing 204c. The splined housing 204a, spring housing 204b, and piston housing 204c are coupled to one another in an end-to-end configuration (e.g., by mating threads or by press fitting). The splined housing 204a is positioned above spring housing 204b, which is positioned above the piston housing 204c. In other implementations one or more of the housings 204a, 204b and 204c may be formed as a single integral housing.
Note that use of terminology such as “above” and “below” to describe elements is for describing relative orientations of the various components of the assembly. For example, “above” used in this context means proximal to the beginning of the drill string (i.e., at the point where the drill string is connected to the drilling rig); and “below” means distal to the beginning of the drill string (or proximal to the end of the drill string, toward the floor of the wellbore). Unless otherwise stated explicitly, the use of such terminology does not imply a particular position or orientation of the assembly or any other components relative to the direction of the Earth gravitational force, or the Earth ground surface.
The mandrel 202 engages the splined housing 204a via a mating set of helical splines and grooves. The mating splines and groove facilitate relative telescoping movement between the mandrel 202 and the housing 204. Thus, the mandrel 202 and housing 204 are designed to move in combined rotation and axial motion relative to one another via the matching helical splines and grooves.
Turning now to
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The sealing portion 226 of the mandrel 202 is provided having a substantially smooth outer surface. The diameter of the sealing portion 226 closely mirrors that of the spline housing's central bore 208, so that the dynamic seals located in the sealing trenches 210 bear against the smooth outer surface of the mandrel 202. The spline portion 228 features a pattern of male, multi-spiral splines 232. The male splines 232 are received by the female spline grooves 212 of the spline housing 204a, allowing the mandrel 202 to move telescopically and rotationally through the housing 204.
Similar to the sealing portion 226, the spring portion 230 exhibits a substantially uniform or smooth outer surface (i.e., a surface without splines). The diameter of the spring portion 230 is significantly less than that of the spline portion 228, so as to form an annulus between the outer surface of the mandrel and the inner surface of the spring housing's central bore. The annulus is designed to accommodate a resilient member 234 (see
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In this example, the resilient member 234 includes an arrangement of disc springs, e.g., Bellville discs. The resilient member 234 is designed to preload under WOB (Weight on Bit) and torque-transfer loads. Additional deflection beyond this initial preloading accommodates one or both of axial and torsional shock loads. The preload creates a biasing force in the resilient member 234 urging the mandrel 202 outwardly through the upper end of the spline housing 204a. The number of disc springs, the characteristics of the individual disc springs (e.g., spring force, static loading limit, dynamic loading limit, etc.), and the configuration of the arrangement (e.g., series or parallel) can be selected so as to provide the resilient member with appropriate performance properties. In some examples, the resilient member is designed to preload up to about 8% under WOB. In some examples, the resilient member is designed to preload up to about 15% under torque transfer conditions.
The piston housing 204c is positioned below the spring housing 204b. As noted above, the piston housing's rim 238 supports the lower end of the resilient member 234. The wash pipe 224 is coupled to the end of the mandrel 202 and projects downward into the central bore of the piston housing 204c. The bore 240 of the wash pipe 224 is aligned with the bore 218 of the mandrel 202, allowing drilling fluid to pass from the mandrel to the wash pipe. A balance piston 242 is located in an annulus between the outer surface of the wash pipe 224 and the inner surface of the central bore of the piston housing 204c. The balance piston 242 is designed to balance the pressure the lubricant oil with the pressure of the drilling fluid. The piston housing 204c, at its lower end, provides a coupling 244 for attaching directly or via other downhole equipment to the drill bit 24.
As noted above, the mandrel 202 is coupled to the housing 204 such that torque imparted on the rotationally driven mandrel is transferred to the housing, causing the housing to rotate together with the mandrel. This arrangement is permitted by cooperation between the mating splines 232 and grooves 212 together with the resilient member 234. The spiral nature of the splines 232 and grooves 212 tends to urge the mandrel 202 to rotationally and telescopically move through the housing 204 as the mandrel is rotated. However, the resilient member 234 is located between the housing 204 and the mandrel 202 and therefore resists the relative telescopic movement. When further movement of the mandrel 202 is prevented by spring force of the resilient member 234, the mandrel's splines 232 bear against the spline housing's grooves 212, resulting in a transfer of torque from the rotationally driven mandrel to the housing. The resilient member 234 is designed to preload under the force of the mandrel 202 bearing downward as it is rotated and urged through the housing 204.
Axial and torsional shock loads encountered by the drill bit 24 are imparted on the housing 204, urging the housing to move rotationally and telescopically relative to the rotating mandrel 202. This movement of the housing 204 relative to the mandrel 202, causing the housing to “ride up” the splines 232 of the mandrel, compressing the resilient member 234, which is positioned to resist the relative movement. Thus, the shock loads are absorbed by compression of the resilient member 234. Small axial and torsional vibrations and nominal shocks are also damped out by the resilient action of the resilient member 234. Larger excitements are damped out by the lubricant oil acting on the balance piston 242. For example, when the resilient member 234 compresses due to shock, the volume holding the lubricant oil is reduced, which in turn increases the oil pressure. The oil pressure increase causes the balance piston 242 to move downward to restore a pressure balance.
Characteristics of the helical splines 232 and grooves 212 are selected so as to balance the need to manage both torsional and axial shock loads encountered by the drill bit 24 with a single shock tool. This goal is accomplished, for example, in the illustrated embodiment where the geometry of the splines and grooves is a mult-start helical pattern having a pitch angle of about nine degrees measured from a longitudinal axis of the tool, with the splines and grooves exhibiting a rectangular cross-section. In some examples, the pitch angle is between about five and sixty degrees. As the pitch angle increases in severity, the shock tool is able to accommodate more torsional shock and less axial shock. Conversely, as the pitch angle decreases, the shock tool is able to accommodate more axial shock and less torsional shock. Creating a pitch angle of about twenty-two degrees provides substantial equal response to either axial or torsional shock loads. Thus, the pitch angle can be optimized for the expected drilling conditions. If more axial shock is expected verses torsional shock, then the pitch angle used can be less than twenty-two degrees, and vice versa.
In some implementations, the multi-spline arrangement described in the shock tool assembly 200 provides superior strength and wear resistance compared to a single spline. For example, the shear stress acting on the splines during operation of the shock tool is distributed evenly over the multiple splines, thereby reducing the stress in each individual spline.
A number of embodiments of the invention have been described. Nevertheless, it will be understood that various modifications may be made without departing from the spirit and scope of the inventions.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/US2013/071461 | 11/22/2013 | WO | 00 |
