Source: https://patents.justia.com/patent/10557316
Timestamp: 2020-08-07 22:06:28
Document Index: 662164846

Matched Legal Cases: ['Application No. 61', 'Application No. 62', 'Application No. 61', 'art 136', 'art 136', 'Application No. 13837637', 'Application No. 2925166', 'Application No. 2016100686301', 'Application No. 12738877', 'Application No. 2017201366', 'Application No. 201380051222', 'Application No. 13837637', 'Application No. 2012209354', 'Application No. 2012209354', 'Application No. 2012209354', 'Application No. 2013362987', 'Application No. 2016204912', 'Application No. 2013315186', 'Application No. 2', 'Application No. 2', 'Application No. 201380051222', 'Application No. 2015113367']

US Patent for Drill string components having multiple-thread joints Patent (Patent # 10,557,316 issued February 11, 2020) - Justia Patents Search
Justia Patents US Patent for Drill string components having multiple-thread joints Patent (Patent # 10,557,316)
Oct 6, 2015 - BLY IP INC.
Drill string components having a plurality of threads extending around a body. A first end of body can define first and second cylindrical shoulders that are spaced apart relative to a central axis of the body, and at least two threads can extend between the first and second cylindrical shoulders. The first and second cylindrical shoulders have respective cylindrical inner and outer surfaces. Optionally, each thread can have a thread root, a thread crest, and a pressure flank surface extending radially from the thread root to the thread crest and defining a pressure flank angle relative to a plane perpendicular to the central axis. Optionally, the thread crest of at least one thread can circumscribe a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns of the thread.
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This application is a continuation-in-part of U.S. patent application Ser. No. 14/026,611, filed Sep. 13, 2013, entitled “DRILL STRING COMPONENTS HAVING MULTIPLE-THREAD JOINTS,” now U.S. Pat. No. 9,850,723, which is a continuation-in-part of U.S. patent application Ser. No. 13/717,885, filed Dec. 18, 2012, entitled “DRILL STRING COMPONENTS RESISTANT TO JAMMING,” now abandoned, which is a continuation-in-part of U.S. patent application Ser. No. 13/354,189, filed Jan. 19, 2012, “DRILL STRING COMPONENTS RESISTANT TO JAMMING,” now U.S. Pat. No. 9,810,029, which claims the benefit of U.S. Provisional Application No. 61/436,331, filed Jan. 26, 2011, entitled “THREAD START FOR THREADED CONNECTORS.” This application further claims priority to U.S. Provisional Patent Application No. 62/060,238, filed Oct. 6, 2014, entitled “DRILL STRING COMPONENTS HAVING MULTIPLE-THREAD JOINTS.” U.S. patent application Ser. No. 14/026,611 further claims priority to U.S. Provisional Patent Application No. 61/700,401, filed Sep. 13, 2012, entitled “DRILL STRING COMPONENTS HAVING MULTIPLE THREAD JOINTS.” The contents of each of the above-referenced applications are hereby incorporated by reference in their entirety.
Implementations of the present invention relate generally to components and systems for drilling. In particular, implementations of the present invention relate to drill components having increased strength and resistance to jamming, cross-threading and wedging.
Accordingly, a need exists for improved thread designs and drilling components that reduce wear, jamming and cross threading as well as use available material effectively to increase drilling load capacity and joint reliability. Further, the improved thread designs and drilling components provide tubing joints that are usable in the mineral exploratory industry for thin wall tubing used as drill rods and casings, which are stronger and withstand the stresses encountered, particularly during deep hole drilling, and facilitate make-up and break-out and decrease the likelihood of spin-out.
In another aspect, one or more implementations of a threaded drill string component having increased strength and resistance to jamming and cross-threading comprises a hollow body comprising a hollow body having an outer surface, an inner surface, first end, an opposing second end, an intermediate body portion positioned between the first and second ends, and a central axis extending through the hollow body. The threaded drill string component can further comprise a first plurality of threads positioned on the first end of the hollow body. The first end of the hollow body can define first and second cylindrical shoulders that are spaced apart relative to the central axis of the hollow body, and the first and second cylindrical shoulders can have respective cylindrical inner and outer surfaces. Each thread of the first end of the hollow body can comprise a plurality of helical turns extending along the first end of the hollow body between the first and second cylindrical shoulders of the first end of the hollow body.
In a further aspect, one or more implementation of a drill string component having increased strength and resistance to jamming and cross-threading can comprise a hollow body having an outer surface, an inner surface, first end, an opposing second end, an intermediate body portion positioned between the first and second ends, and a central axis extending through the hollow body. The drill string component can further comprise a first plurality of threads positioned on the first end of the hollow body. The first end of the hollow body can define first and second cylindrical shoulders that are spaced apart relative to the central axis of the hollow body, and the first and second cylindrical shoulders can have respective cylindrical inner and outer surfaces. Each thread of the first end of the hollow body can comprise a plurality of helical turns extending along the first end of the hollow body between the first and second cylindrical shoulders of the first end of the hollow body. Each thread of the first plurality of threads can have a thread root, a thread crest, and a pressure flank surface extending radially from the thread root to the thread crest. The pressure flank surface of each thread of the first plurality of threads can define a pressure flank angle relative to a plane perpendicular to the central axis.
In a further aspect, one or more implementation of a drill string component having increased strength and resistance to jamming and cross-threading can comprise a hollow body having an outer surface, an inner surface, first end, an opposing second end, an intermediate body portion positioned between the first and second ends, and a central axis extending through the hollow body. The drill string component can further comprise a plurality of threads positioned on the first end of the hollow body. Each thread of the first end of the hollow body can comprise a plurality of helical turns extending along the first end of the hollow body. Each thread of the plurality of threads can have a thread root, a thread crest, and a pressure flank surface extending radially from the thread root to the thread crest. The pressure flank surface of each thread of the plurality of threads can define a pressure flank angle relative to a plane perpendicular to the central axis. The thread crest of at least one thread of the plurality of threads can circumscribe a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof.
In one aspect, one or more implementations of a drill string component having increased strength and resistance to jamming and cross-threading utilize thin-walled tubing, such as drill rod and casing, for mineral exploratory. The thin-walled tubing has a pin end and a box end and has a plurality of threads defined therein. In this aspect, one thread of the plurality of threads comprises internal circular cylindrical surfaces that extend axially between axially intermediate threaded sections to the respective adjacent nose end shoulders and base shoulders. In this aspect, the shoulders of the thread can be tapered between about 5 degrees to 10 degrees relative to a perpendicular to a joint central axis. In this aspect, the thread can be of a substantially constant depth throughout its circumferential length between the pin and box cylinder sections and the crest and root respectively being of a constant width throughout their circumferential lengths (turns of thread) other than at their juncture to the sections having the cylindrical surfaces. In this aspect, the depth of the thread can be of a relative thickness dimensions such that the pin crest abuts against the box root while leaving a radial gap between the box crest and the pin root. In this aspect, the thread can have pressure flanks of between about negative 7.5 to 25 degrees to provide for lower stress states and clearance flanks of about 45 degrees to 60 degree to facilitate stabbing without damaging the threads.
In addition to the foregoing, an implementation of a method of making a joint in a drill string with increased strength and without jamming or cross-threading involves inserting a pin end of a first drill string component into a box end of a second drill string component. The method also involves rotating the first drill sting component relative to the second drill string component, thereby abutting a planar leading end of a male thread on the pin end of the first drill string component against a planar leading end of a female thread on the box end of the second drill string component. The planar leading end of the male thread is oriented at an acute angle relative to a central axis of the first drill string component. Similarly, the planar leading end of the female thread is oriented at an acute angle relative to a central axis of the second drill string component. Additionally, the method involves sliding the planar leading end of the male thread against and along the planar leading end of the female thread to guide the male thread into a gap between turns of the female thread.
FIG. 3 is a fragmentary side view of a pin end of a drill rod, showing the pin end prior to the turning/formation of threads thereon.
FIG. 4 is a fragmentary side view of a pin end of a drill rod, showing the pin end after the turning/formation of threads thereon.
FIG. 5A is a fragmentary longitudinal sectional view of a pin end of a drill rod, showing the pin end after the threads are formed thereon;
FIG. 5B is an enlarged, fragmentary longitudinal sectional view of a portion of the pin end of the drill rod of FIG. 5A;
FIG. 5C is an enlarged, fragmentary longitudinal sectional view of a cylindrical shoulder and undercut of the pin end of the drill rod of FIG. 5A;
FIG. 6A is a fragmentary longitudinal sectional view of a box end of a drill rod, showing the box end before the threads are formed thereon;
FIG. 6B is a fragmentary longitudinal sectional view of a box end of a drill rod, showing the box end after the threads are formed thereon;
FIG. 6C is an enlarged, fragmentary longitudinal sectional view of a portion of the box end of the drill rod of FIG. 6A;
FIG. 6D is an enlarged, fragmentary longitudinal sectional view of a cylindrical shoulder and undercut of the box end of the drill rod of FIG. 6A;
FIG. 7 is a fragmentary longitudinal view of pin end of a drill rod partially extended into the box end of an adjacent drill rod with the box and one half of the pin being shown in cross section and the joint being shown in a loose condition;
FIG. 8 illustrates a side view of a male end of a drill string component and a cross-sectional view of a female end of another drill string component each having threads as disclosed herein;
FIG. 9 illustrates a side view of an exploded drill string having drill string components having threads as disclosed herein;
FIG. 10A illustrates a side view of a male end of a drill string component having threads as disclosed herein;
FIG. 10B is an enlarged, fragmentary, side view of a leading edge of the thread of the pin end of FIG. 10A;
FIG. 11A illustrates a side view of a female end of a drill string component having threads as disclosed herein;
FIG. 11B is an enlarged, fragmentary, side view of a leading edge of the thread of the box end of FIG. 11A; and
FIG. 12 illustrates a schematic diagram of a drilling system including drill string components having threads as disclosed herein.
Turning now to FIGS. 1-11B, implementations of exemplary threaded drill string components are illustrated. The threaded drill string components having increased load capacity and load efficiency that can also be joined while avoiding or reducing the risk of wear, cross-threading and jamming are described in particular detail below. As shown in the Figures, a first drill string component 102 can comprise a body 103 and a male connector or pin end 104. A second drill string component 106 can comprise a body 107 and a female connector or box end 108. The pin end 104 of the first drill string component 106 can be configured to connect to the box end 108 of the second drill string component 106.
In one or more implementations, each drill string component 102, 106 can comprise a hollow body having a central axis 126 extending there through as shown in FIGS. 1-11B. In alternative implementations, one or more of the drill string components 102, 106 can comprise a solid body (such as a percussive drill rod or drill bit) or a partially hollow body. More particularly, in the case of a hollow body, the hollow body can comprise an inner diameter, an outer diameter and a wall thickness.
In one exemplary aspect, the drill string component can have the following typical dimensions:
Exemplary Drill String Component Dimensions
OD (in) 2.20 2.75 3.50 4.50 ID (in) 1.91 2.38 3.06 4.0 Wall Thickness (in) 0.15 0.19 0.22 0.25 Major Diameter (in) 2.09 2.61 3.34 4.35
TABLE 2 Exemplary Drill String Component Characteristics
Wall thickness to outer diameter 7% 6% 6% 7% (%) Thread depth to wall thickness 19% 16% 21% 16% (%) Range of joint taper (deg) 0.8 1.0 1.0 0.5 Range of flank angle (deg) −10 15 2 −20 Threaded length to diameter (%) 55% 39% 44% 43% Range of thread pitch (tpi) 3.50 3.00 2.50 1.75 Major diameter less inner 62% 62% 70% 63% diameter, to wall thickness Shoulder thickness to wall 38% 38% 30% 37% thickness (%)
In one or more implementations, the male and female threads 110, 112 can comprise characteristics the same as or similar to those described in U.S. Pat. No. 5,788,401, the entire contents of which are incorporated by reference herein. For example, in one or more implementations, the male and female threads 110, 112 have a crest, a root, a pressure flank and a clearance flank. According to one aspect, threads 110, 112 can have a pressure flank angle (or thread load flank angle) that can be from about −30 to about 15 degrees; more particularly, from about −20 to about −10 degrees; and, most particularly, about −20 to about −15 degrees, all measured relative to a plane perpendicular to the drill string central axis. As one skilled in the art will appreciate in light of the present disclosure, such negative pressure flank angles can aid in maintaining the joint in a coupled condition, even under overload and also reduce overall stress as compared to positive flank angles. In exemplary aspects, the male and female threads can be spaced from the respective end faces 114, 120 of the pin and box ends 104, 108 of the drill string component to respectively define a pin end shoulder face and a box end shoulder face. Optionally, in these aspects, the pin and box end shoulders can have a substantially cylindrical shape and profile, with the pin end shoulder defining a cylindrical outer surface and the box end shoulder defining a cylindrical inner surface. It is further contemplated that the pin end shoulder can define a cylindrical inner surface and that the box end shoulder can define a cylindrical outer surface. Thus, the male and female threads as disclosed herein can extend between the cylindrical pin and box end shoulders.
By not tapering the cylindrical end shoulders, the wall thickness is not decreased such as would otherwise occur with the accompanying reduced compressive strength, and the wall thickness thereof is not decreased such as would otherwise occur with the accompanying reduction in tensile strength. However, the wall thickness of the cylindrical end shoulders does limit the joint taper for a given thread length.
Optionally, the thickness of the box end shoulder can be greater than that of the pin end shoulder to allow for greater wear to the joint outer diameter resulting from in the hole abrasion. This can result in the joint having an increased life.
In one exemplary aspect, and with reference to FIGS. 5A-6D, the male and female threads 110, 112 can be generally classified as a tapered, modified buttress thread form wherein the angles 30 and 31 of the pressure flanks 138 and 142 respectively are small and the angles 40 and 41 of the clearance flanks 144 and 140 are comparatively large. Further, the male and female threads can have crests 32 and 33 and roots 34 and 35 respectively. In one aspect, the crest of the female thread can have a frustoconical surface extending the helical length thereof, the generatrix of which is a straight line that is tapered relative to threaded drilling component central axis 126 while the root of the female thread likewise has a frustoconical surface that is similarly tapered relative to the threaded drilling component central axis. Similarly, the crest of the male thread can have a frustoconical surface extending the helical length thereof, the generatrix of which is a straight line that is tapered relative to the threaded drilling component central axis while the root of the male thread has a frustoconical surface, the generatrix of which is a straight line that is tapered relative to the threaded drilling component central axis.
In a further aspect, the respective depth 130 and 132 of the male and female threads can be proportional to the threaded drilling component wall thickness. In one exemplary aspect, for thin wall drill rods, the depth of each of the male and female threads is in the range of about 10-15% of the drill rod main wall body thickness when the drill rod is not of an upset type. In another exemplary aspect, each of the male and female thread depths can be substantially constant along their entire helical lengths in contrast to vanishing type threads.
In a further aspect, and referring to the attached figures, the pressure flank angles are negative. In this aspect, and since the pressure flank surfaces are connected to the root surfaces in tension, it is contemplated that the root-flank intersections can be filleted about 0.0035″ to 0.009″. As one skilled in the art will appreciate, due to the pressure flank angle on any thread form, radial loads are induced as a component of the normal force acting between mated pressure flanks. By incorporating a negative flank angle in the joint as shown herein, the induced radial loads “compress” the box and pin together, whereas radial loads induced from a positive flank angle “push” the box and pin ends of the threaded drilling components apart and results in increased wear and thread jumping. The magnitude of the radial load component is equal to the tangent of the pressure flank angle (measured from the perpendicular to the threaded drilling component central axis) times the axial joint load. Thus, the smaller the pressure flank angle, the smaller the induced radial component. With the negative pressure flank angles, the greater the tension load transferred through the joint, the more the pin and box are pulled together, the greater the torque resistance is to spin-out, the greater the resistance is to joint parts belling (buckling) or splitting and thread turns jumping over one another.
In one aspect, it is preferred that the pressure flank angle be between about 5 degrees to about a −25 degrees, more preferred from between about 0 degrees to about −25 degrees, between about a −7.5 degrees to about a −23 degrees, or between about a −10 degrees to about a −20 degrees. By using a negative flank angle, the increased wear and the thread jumping associated with boxes pushed out by positive flank angles is eliminated. Also, with the negative flank angles, the threads will remain engaged under significant overloading which is required to retrieve stuck drill strings or valuable in-the-hole tools from deep holes.
In a further exemplary aspect, the clearance flank angle 40 of the box end and the clearance angle 41 of the pin end is of a minimum of about 45 degrees to facilitate the ease of making up a joint. Further, when the joint is made up, the pin and box ends can be configured such that there is about a 0.010″ axial clearance between the pin and box clearance flanks to allow for a relief passage for pressurized lubricant or debris. In one aspect, by having the clearance flank angle 45 degrees or greater (for example about 45 to 85 degrees, including for example about 45 degrees, about 60 degrees, and about 75 degrees) and providing a clearance between the clearance flanks, the radial impact component is greater which deflects the pin end into alignment and thereby during make-up when the pin is mis-aligned allows axial motion into the box end to continue.
In another aspect, as described in U.S. Pat. No. 5,788,401, each of the male and female thread turns can be of the same axial dimension while the axial dimension of a thread root (distance from the intersection of straight line extensions of a pressure flank with the frustoconical surface of the thread root to the intersection of straight line extensions of the frustoconical surface of the clearance flank with the frustoconical surface of the thread root) is less than one half than the axial dimension of the thread turns. Further, the axial dimension of a thread clearance flank of the threads from the intersection of crest frustoconical surface with chamfer to the intersection of the frustoconical surface of the thread root with a straight line intersection of the frustoconical surface of the clearance flank is advantageously about 20 to 25 percent of the dimension of the thread root. These dimensions in conjunction with the profile of the thread clearance flanks provide an axial gap between the clearance flanks. However, it is contemplated in this embodiment that the axial dimensions of the male and female crests and roots for each of the thread turns can be configured to remain substantially constant axially intermediate of the respective set of the cylinder sections.
The depth of each male crest relative to that of the female crest is sufficiently greater such that when the joint is made up, the male thread crests have an interference fit with the female thread root along the length of the thread. In this aspect, the relative depths of the male and female crests is such that the female thread crests are radially spaced from the male thread roots. This interference fit induces an interference contact pressure, commonly referred to as a “press-shrink fit,” which forms a rigid joint that maximizes fatigue strength and galling resistance by resisting relative movement between the box and pin end that results from alternating stresses caused by drilling in deviated or bent holes. Further, the frictional force offered by the contact pressure between the male and female threads provides an additional torsion transfer path to prevent over-torquing or over make-up of the joint and a resistant torque against “spin-out” of the joint under rotational deceleration resulting from discontinuing the rotary drive to the drill string at the drill drive surface.
In one aspect, and as further described in U.S. Pat. No. 5,788,401, each male pressure flank can be joined to the adjacent male crest by a chamfer and each male clearance flank can be joined to the adjacent male crest by a chamfer. Each of the chamfers can be at angles of about 30 degrees relative to the pin crest while the radial component of each of the chamfers can be about one-tenth of the pin thread depth 130. Further, each male clearance flank can be joined to the adjacent male root by a radius that can be about 0.025″−0.040″. In another aspect, each female pressure flank can be joined to the adjacent female crest by a chamfer at an angle that can be about degrees, and can be joined to the adjacent clearance flank by a radius that can be about 0.025″ 0.040″. In this aspect, the female clearance flank can be joined to the adjacent root by a radius and can be joined to the adjacent pressure flank by another radius.
In another aspect, the box end and pin end of the drill sting component can have shoulders tapered at about 0 to about 15 degrees. Alternatively, the box end and pin end of the drill string component can have substantially cylindrical (un-tapered) shoulders as further disclosed herein. In another aspect, the shoulders can have an outer diameter thickness of about 0.055 to about 0.080 inches; and more particularly, about 0.055 inches, about 0.083 inches, about 0.070 inches or about 0.075 inches.
In other aspects, the critical box shoulder stiffness, or the section modulus or ‘modulus of inertia’ of the box shoulder, can contribute torsion strength and can be exponentially sensitive to shoulder thickness. In one aspect, the critical box shoulder stiffness can be from about 34% to about 48% of the tubing stiffness; more preferably, about 40%, about 41%, or about 43% of the tubing stiffness.
In another optional aspect, the thread crest can be configured to be radiused or curved in longitudinal cross-section, in contrast to using a series of adjoining multiple tapered surfaces. In this aspect, it is contemplated that the crest of the thread can circumscribe a frustra-conical surface with a curvature that extends over at least a portion of the axial length of the plurality of helical turns of the tread. In this exemplary aspect, it is contemplated that the generatrix of the frustra-conical surface can be a slightly curved line that initialed at an angle with respect to the threaded drilling component central axis.
One will appreciate in light of the disclosure herein, the foregoing description provides exemplary configurations for the male and female threads 110, 112. In alternative implementations, the configuration of the male and female threads 110, 112 can differ from the foregoing description. In certain alternative implementations, the threads 110, 112 can also have negative pressure flank angles of about 5 to 30 degrees relative to a plane perpendicular to the drill string central axis and clearance flanks of an angle of at least 45 degrees to aid in maintaining the joint in a coupled condition, even under overload, and facilitate joint make up. Also, the box end and pin end can have shoulders tapered at about 5 to 20 degrees.
The male thread 110 can begin proximate a leading edge 140 of the pin end 104. For example, FIG. 1-3 illustrate that the male thread 110 can be offset a distance (shown has a linear distance 116) from a shoulder face 114 of the pin end 104. The offset distance 116 can optionally define a pin end shoulder, which can optionally have a substantially cylindrical shape as further described herein. The offset distance can allow for an un-mated shoulder portion of a threaded member to be elastically compressed under torque applied during joint make-up. As one skilled in the art will appreciate, a resulting joint can maintain a pre-loaded condition given an applied make-up torque wherein a sufficient amount of offset distance can be required to allow thread travel and can allow a “pre-load” to build as the shoulder undergoes elastic compression. This “pre-load” can be required to maintain the joint in a closed condition while under large drilling tension loads or deviation bending loads that could otherwise cause the shoulder interface to open, thus increasing the bending load on the pin and creating the potential for the pin end to undergo fatigue failure. Accordingly, in various aspects, the offset distance 116 may vary as desired, and can particularly be different based on the size of the drill string component 102, configuration of the thread 110, or based on other factors. In at least one implementation, the offset distance 116 is between about one-half and about twice the width 118 of the male thread 110. Alternatively, the offset distance 116 may be greater or lesser. For example, in one or more implementations the offset distance 116 is zero such that the male thread 110 begins at the shoulder face 114 of the pin end 104.
Similarly, female thread 112 can begin proximate a leading end 120 of the box end 108. For example, it is contemplated that the female thread 112 can be offset a distance (shown has a linear distance 122) from the leading end 120 of the box end 108. The offset distance 122 can optionally define a box end shoulder, which can optionally have a substantially cylindrical shape as further described herein. The offset distance 122 may vary as desired, and can particularly be different based on the size of the drill string component 106, configuration of the female thread 112, or based on other factors. In at least one implementation, the offset distance 122 is between about one-half and about twice the width 124 of the female thread 112. Alternatively, the offset distance 122 may be greater or lesser. For example, in one or more implementations the offset distance 122 is zero such that the female thread 112 begins at the leading end 120 of the box end 108.
Furthermore, the offset distance 116 can be equal to the offset distance 122. In alternative implementations, the offset distance 122 may be greater or smaller than the offset distance 116. In any event, as the shoulder face 114 of the pin end 104 is inserted into the box end 108 and rotated, the male thread 110 may engage the female thread 112, and the pin end 104 may advance linearly along a central axis 126 of the box end 108.
More particularly, the male and female threads 110, 112 can be helically disposed relative to the respective pin and box ends 104, 108. In other words, each of the male thread 110 and the female thread 112 can comprise a plurality of helical turns extending along the respective drill string component 102, 106. As the male and female threads 110, 112 mate, the threads may therefore rotate relative to each other and fit within gaps between corresponding threads. In one aspect, the male thread 110 generally winds around pin end 104 at an angle 128, which can also be measured relative to the shoulder face 114 of the pin end 104.
In an alternative aspect, it is contemplated that for a drill string component having a plurality of threads providing a substantially constant difference in pitch values of the respective male and female threads can provide a desired interference fit. In exemplary aspects, at least one of a constant width of the thread, a constant pitch, and/or the like can differ or otherwise be inconsistent between the mating male and female threads throughout a portion or the entirety of the longitudinal length of the helical turns of the male and female threads.
It is also contemplated that, in an exemplary aspect, that the thread width and the thread pitch of the at least two threads remains substantially constant from proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof. In a further aspect, it is contemplated that at least one of the thread width and/or the thread pitch of the at least two threads can be different. Optionally, both the thread width and the thread pitch of the at least two threads can be different.
In one example, at least two male threads 110 can begin proximate to a shoulder face 114 of pin end 104. In a further aspect, the at least two male threads can be spaced equally about a shoulder face 114 of pin end 104. For example, it is contemplated that a pin end has two male threads having thread starts spaced about 180 degrees apart and proximate to a shoulder face 114 of pin end 104. In another example, it is contemplated that a pin end has three male threads, having thread starts that can be spaced about 120 degrees apart and proximate to a shoulder face 114 of pin end 104.
Similarly, at least two female threads 112 can begin proximate to a leading end 120 of box end 108. In a further aspect, the at least two female threads can be spaced equally about a leading end 120 of box end 108. For example, it is contemplated that a box end 108 has two female threads 112 having thread starts spaced about 180 degrees apart and proximate to a leading end 120 of box end 108. In another example, it is contemplated that a box end 108 has three female threads 112 having thread starts that can be spaced about 120 degrees apart and proximate to a leading end 120 of box end 108.
One or more implementations of the present invention comprise drill string components that substantially minimize overall root and thread taper in favor of at least one of varying thread pitch, varying thread width, and tapering at least a portion of the thread crest while providing a uniform thread root. Another aspect of the present invention comprises drill string components that eliminate overall root and thread taper in favor of at least one of varying thread pitch, varying thread width and tapering at least a portion of the thread crest while providing a uniform thread root.
In yet another aspect, the at least one thread can have a width that varies from about 50% of full thread width proximate the leading end and increases to full thread width proximate the trailing end of the thread. In a further aspect, the at least one thread can have a width that varies from about 75% of full thread width proximate the leading end and increases to full thread width proximate the trailing end of the thread. In other aspects, the thread can have a varying width over at least one turn and, preferably, two turns of the thread. In alternative aspect, the thread can have a width that varies from the leading end to the trailing end of the thread. In one exemplary embodiment, a 2 tpi (turns per inch) thread having a full width of ¼″ proximate the trailing end can have a reduced width of about ⅛″ at the leading end. As one skilled in the art will appreciate, the spacing between the adjacent turns of the at least one thread is largest at the leading end and provides additional axial clearance when starting threads.
In one example, at least one male thread 110 can begin proximate to a shoulder face 114 of pin end 104. The at least one male thread 110 can comprise a plurality of helical turns extending along the respective length of pin end 104. In a further aspect, the at least one male thread can have a pitch that increases from a first value proximate the leading end 134 over at least a portion of the axial length of the plurality of helical turns thereof to a final value at a desired point on the at least one male thread 110 and be held constant thereafter. In another aspect, the at least one male thread can have a pitch that increases from a first value proximate the leading end over the entire portion of the axial length of the plurality of helical turns thereof to a final value. In alternative aspects, the pitch can increase uniformly or non-uniformly across the axial length of the at least one male thread 110. For example, it is contemplated that a pin end has two male threads having a pitch that increases from the leading end 134 of pin end 104 to a final value at a desired point along the axial length of the thread, such point being measured from shoulder face 114 of the pin end 104.
Similarly, at least one female thread 112 can begin proximate to a shoulder face 120 of box end 108. The at least one female thread 112 can comprise a plurality of helical turns extending along the respective length of box end 108. In a further aspect, the at least one female thread can have a pitch that increases from a first value proximate the leading end 136 over at least a portion of the axial length of the plurality of helical turns thereof to a final value at a desired point on the at least one female thread 112 and be held constant thereafter. In another aspect, the at least one female thread can have a pitch that increases from a first value proximate the leading end 136 over the entire portion of the axial length of the plurality of helical turns thereof to a final value. In alternative aspects, the pitch can increase uniformly or non-uniformly across the axial length of the at least one female thread 112. For example, it is contemplated that a pin end has two female threads having a pitch that increases from the leading end 136 of box end 108 to a final value at a desired point along the axial length of the thread, such point being measured from the shoulder face 120 of the box end 108.
In another example, at least one male thread 110 can begin proximate to a leading end of pin end 104. The at least one male thread 110 can comprise a plurality of helical turns extending along the respective length of pin end 104 and can also have at least one thread feature with a constant pitch across the axial length of the thread. Exemplary thread features whose pitch can be held constant can include the load flank, the leading flank, the thread midpoint, and the like. In a further aspect, the at least one male thread can have a thread width that increases from a percentage of the full thread width proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof to the full thread width at a desired point on the at least one male thread 110 and be held constant thereafter. In another aspect, the at least one male thread can have a thread width that increases from a percentage of the full thread width proximate the leading end over the entire portion of the axial length of the plurality of helical turns thereof to the full thread width. In alternative aspects, the thread width can increase uniformly or non-uniformly across the axial length of the at least one male thread 110. For example, it is contemplated that a pin end has two male threads where at least one male thread has at least one feature having a constant pitch across the entire axial length of that thread and a width that increases from a percentage of full thread width at the leading end of pin end 104 to the full thread width at a desired point along the axial length of the thread.
More particularly, at least one male thread 110 and at least one female thread 112 can be helically disposed relative to the respective pin and box ends 104, 108. In other words, the at least one male thread 110 and the at least one female thread 112 can comprise a plurality of helical turns extending along the respective drill string component 102, 106. The at least one male thread 110 and the at least one female thread 112 can each comprise leading ends oriented at an acute angle relative to the central axis of the respective drill string component 102, 106. In one aspect, both the at least one male thread 110 and the at least one female thread 112 can have a thread root that circumscribes a cylindrical surface over the entire axial length of the plurality of helical turns. In a further aspect, at least one of the at least one male thread 110 and the at least one female thread 112 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the respective shoulder faces 114, 120 extending over at least a portion of the axial length of the plurality of helical turns thereof to a final diameter at a desired point on the respective at least one thread and be held constant thereafter. As the at least one male thread 110 and the at least one female thread 112 mate, the threads may therefore rotate relative to each other and fit within gaps between corresponding threads and eventually form a drill string joint. A progressive fit in the radial direction is selectively created between the respective pin and box ends 104, 108 as the crest diameter of at least one of the at least one male thread 110 and the at least one female thread 112 increases. Also, a progressive fit in the axial direction is selectively created between the respective pin and box ends 104, 108. As at least one of the pitch and the width of at least one of the at least one male thread 110 and the at least one female thread 112 increases. Accordingly, in one or more embodiments, a drill string joint is formed having optimal material cross sections for maximum load capacity.
With reference to FIGS. 8 and 10A-11B, one or more implementations of the present invention comprise drill string components having threads whose respective leading ends are oriented at an acute angle relative to the central axis of the drill string component and, additionally or alternatively, the leading end of the thread can provide an abrupt transition to the full thread depth and/or width.
As alluded to above, both the male and female threads 110, 112 can comprise a leading end or thread start. For example, the attached figures illustrate that the male thread 110 can comprise a thread start or leading end 134. Similarly, the female thread 112 can comprise a thread start or leading end 136.
In one or more implementations, the leading end 134 of the male thread 110 can comprise a planar surface that extends from the outer surface of the pin end 104. For example, the leading end 134 of the male thread 110 can comprise a planar surface that extends radially outward from the outer surface of the pin end 104, thereby forming a face surface. In one or more implementations the leading end 134 extends in a direction normal to the outer surface of the pin end 104. In alternative implementations, the leading end 134 extends in a direction substantially normal to the outer surface of the pin end 104 (i.e., in a direction oriented at an angle less than about 15 degrees to a direction normal to the outer surface of the pin end 104). In still further implementations, the leading end 134 can comprise a surface that curves along one or more of its height or width.
Furthermore, in one or more implementations the leading end 134 of the male thread 110 can extend the full thread width 118 of the male thread 110. In other words, the leading end 134 of the male thread 110 can extend from a clearance flank 140 to a pressure flank 138 of the male thread 110. Thus, the planar surface forming the leading end 134 can span the entire thread width 118 of the male thread 110.
Additionally, in one or more implementations the leading end 134 of the male thread 110 can extend the full thread depth 130 of the male thread 110. In other words, a height of the leading end 134 of the male thread 110 can be equal to the thread depth 130. Thus, the planar surface forming the leading end 134 can span the entire thread depth 130 of the male thread 110. As such, the leading end 134 or thread start can comprise an abrupt transition to the full depth and/or width of the male thread 110. In other words, in one or more implementations, the male thread 110 does not comprise a tail end that tapers gradually to the full depth of the male thread 110.
Along similar lines, the leading end 136 of the female thread 112 can comprise a planar surface that extends from the inner surface of the box end 108. For example, the leading end 136 of the female thread 112 can comprise a planar surface that extends radially inward from the inner surface of the box end 108, thereby forming a face surface. In one or more implementations the leading end 136 extends in a direction normal to the inner and/or outer surface of the box end 108. In alternative implementations, the leading end 136 extends in a direction substantially normal to the inner or outer surface of the box end 108 (i.e., in a direction oriented at an angle less than about 15 degrees to a direction normal to the inner and/or outer surface of the box end 108). In still further implementations, the leading end 136 can comprise a surface that curves along one or more of its height or width. For example, the leading end 134 and the leading end 136 can comprise cooperating curved surfaces.
Furthermore, in one or more implementations the leading end 136 of the female thread 112 can extend the full thread width 124 of the female thread 112. In other words, the leading end 136 of the female thread 112 can extend from a pressure flank 142 to a clearance flank 144 of the female thread 112. Thus, the planar surface forming the leading end 136 can span the entire thread width 124 of the female thread 112.
Additionally, in one or more implementations the leading end 136 of the female thread 112 can extend the full thread depth 132 of the female thread 112. In other words, a height of the leading end 136 of the female thread 112 can be equal to the thread depth 132. Thus, the planar surface forming the leading end 136 can span the entire thread depth 132 of the female thread 112. As such, the leading end 136 or thread start can comprise an abrupt transition to the full depth and/or width of the female thread 112. In other words, in one or more implementations, the female thread 112 does not comprise a tail end that tapers gradually to the full depth of the female thread 112. In the illustrated implementation, the leading end or thread start 136 of the female thread 112 is illustrated as being formed by material that remains after machining or another process used to form the threads. Thus, the leading end or thread start 136 may be, relative to the interior surface of the box end 108, embossed rather than recessed.
In one or more implementations, the leading end 134 of the male thread 110 can have a size and/or shape equal to the leading end 136 of the female thread 112. In alternative implementations, the size and/or shape of the leading end 134 of the male thread 110 can differ from the size and/or shape of the leading end 136 of the female thread 112. For example, in one or more implementations the leading end 134 of the male thread 110 can be larger than the leading end 136 of the female thread 112.
In one or more implementations, the leading ends 134, 136 of the male and female threads 110, 112 can each have an off-axis orientation. In other words, the planar surfaces of the leading ends 134, 136 of the male and female threads 110, 112 can each extend in a direction offset or non-parallel to a central axis 126 of the drill string components 102, 106. For example, the planar surface of the leading end 134 of the male thread 110 can face an adjacent turn of the male thread 110. Similarly, planar surface of the leading end 136 of the female thread 112 can face an adjacent turn of the female thread 112.
More particularly, the planar surface of the leading end 134 of the male thread 110 can extend at an angle relative to the shoulder face 114 or the central axis 126 of the pin end 104. For instance, the planar surface of the leading end 134 of the male thread 110 is oriented at an angle 146 relative to the central axis 126 of the drill string component 102, although the angle may also be measured relative to the shoulder face 114. The illustrated orientation and existence of a planar surface of the leading end 134 is particularly noticeable when compared to traditional threads, which taper to a point such that there is virtually no distance between the leading and trailing edges of a thread, thereby providing no face surface.
Similar to the leading end 134, the leading end 136 of the female thread 112 can extend at an angle relative to the shoulder face 120 or the central axis 126 of the pin end 104. For instance, the planar surface of the leading end 136 of the female thread 112 is oriented at an angle 148 relative to the central axis 126 of the drill string component 106, although the angle may also be measured relative to the shoulder face 120.
In one or more implementations the angles 146, 148 are each acute angles. For example, each of the angles 146, 148 can comprise an angle between about 10 degrees and 80 degrees, about 15 degrees and about 75 degrees, about 20 degrees and about 70 degrees, about 30 degrees and about 60 degrees, about 40 degrees and about 50 degrees. In further implementations, the angles 146, 148 can comprise about 45 degrees. One will appreciate in light of the disclosure herein that upon impact between two mating leading ends 134, 136 or start faces with increasing angles 146, 148, there is decreasing loss of momentum and decreasing frictional resistance to drawing the threads 110, 112 into a fully mating condition. In any event, a leading end 134 of the male thread 110 can mate with the leading end 136 of the female thread 112 to aid in making a joint between the first drill string component 102 and the second drill string component 106.
By eliminating the long tail of a thread start and replacing the tail with a more abrupt transition to the full height of the thread 110, 112, a leading ends 134, 136 or thread start face can thus be provided. Moreover, while the leading ends 134, 136 may be angled or otherwise oriented with respect to an axis 126, the thread start face may also be normal to the major and/or minor diameters of cylindrical surfaces of the corresponding pin and box ends 104, 108. Such geometry eliminates a tail-type thread start that can act as a wedge, thereby eliminating geometry that leads to wedging upon mating of the pin and box ends 104, 108.
Moreover, as the pin and box ends 104, 108 are drawn together, the leading ends 134, 136 or thread starts may have corresponding surfaces that, when mated together, create a sliding interface in a near thread-coupled condition. For instance, where the leading ends 134, 136 are each oriented at acute angles, the leading ends 134, 136 or thread start faces may engage each other and cooperatively draw threads into a fully thread-coupled condition. By way of example during make up of a drill rod assembly, as the pin end 104 is fed into the box end 108, the leading ends 134, 136 can engage and direct each other into corresponding recesses between threads. Such may occur during rotation and feed of one or both of the drill string components 102, 106. Furthermore, since thread start tails are eliminated, there are few-if any-limits on rotational positions for mating. Thus, the pin and box ends 104, 108 can have the full circumference available for mating, with no jamming prone positions.
In one or more implementations, a thread 110 may be formed with a tail using conventional machining processes. The tail may be least partially removed to form the leading end 134. In such implementations, a tail may extend around approximately half the circumference of a given pin end 104. Consequently, if the entire tail of the thread 110 is removed, the thread 110 may have a leading end 134 aligned with the axis 126. If, however, more of the thread 110 beyond just the tail is removed, leading end 134 may be offset relative to the axis 126. The tail may be removed by a separate machining process. Although this example illustrates the removal of a tail for formation of a thread start, in other embodiments a thread start face may be formed in the absence of creation and/or subsequent removal of a tail-type thread start. For example, instead of using conventional machining processes, the thread is formed using electrical discharge machining. Electrical discharge machining can allow for the formation of the leading end 114 since metal can be consumed during the process. Alternatively, electrochemical machining or other processes that consume material may also be used to form the leading ends 134, 136 of the threads 110, 112.
As previously mentioned, in one or more implementations and with reference to FIGS. 1 and 8, the drill string components 102, 106 can comprise hollow bodies. More specifically, in one or more implementations the drill string components can be thin-walled. In particular, the drill string component 106 can comprise an outer diameter 150, an inner diameter 152, and a wall thickness 154. The wall thickness 154 can equal one half of the outer diameter 150 minus the inner diameter 152. In one or more implementations, the drill string component 106 has a wall thickness 154 between about approximately 5 percent and 15 percent of the outer diameter 150. In further implementations, the drill string component 106 has a wall thickness 154 between about approximately 6 percent and 8 percent of the outer diameter 150. One will appreciate that such thin-walled drill string components can limit the geometry of the threads 112. However, a thin-walled drill string component can nonetheless comprise any combination of features discussed hereinabove despite such limitations.
In one aspect, the drill string components 102, 106 can comprise any number of different types of tools. In other words, virtually any threaded member used on a drill string can comprise one or more of a box end 108 and a pin end 104 having leading ends or thread starts as described. For example, and with reference to FIG. 9, the drill string components can comprise a locking coupling 201, an adaptor coupling 202, a drill rod 204, and a reamer 206 can each comprise both a pin end 104 and a box end 108 with leading ends 134, 136 having increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading as described above. FIG. 9 further illustrates that drill string components can comprise a stabilizer 203, a landing ring 205 and a drill bit 207 including a box end 108 with a leading end 136 having increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading as described above. In yet further implementations, the drill string components 102, 106 can comprise casings, reamers, core lifters, or other drill string components.
As shown in FIG. 12, a drilling system 300 may be used to drill into a formation 304. The drilling system 300 may comprise a drill string 302 formed from a plurality of drill rods 204 or other drill string components 201-207. The drill rods 204 may be rigid and/or metallic, or alternatively may be constructed from other suitable materials. The drill string 302 may comprise a series of connected drill rods that may be assembled section-by-section as the drill string 302 advances into the formation 304. A drill bit 207 (for example, an open-faced drill bit or other type of drill bit) may be secured to the distal end of the drill string 302. As used herein the terms “down,” “lower,” “leading,” and “distal end” refer to the end of the drill string 302 including the drill bit 207. While the terms “up,” “upper,” “trailing,” or “proximal” refer to the end of the drill string 302 opposite the drill bit 207.
The drilling system 300 can further comprise a drill rod clamping device 312. In further detail, the driving mechanism may advance the drill string 302 and particularly a first drill rod 204 until a trailing portion of the first drill rod 204 is proximate an opening of a borehole formed by the drill string 302. Once the first drill rod 204 is at a desired depth, the drill rod clamping device 312 may grasp the first drill rod 204, which may help prevent inadvertent loss of the first drill rod 204 and the drill string 302 down the borehole. With the drill rod clamping device 312 grasping the first drill rod 204, the driving mechanism may be disconnected from the first drill rod 204.
An additional or second drill rod 204 may then be connected to the driving mechanism manually or automatically using a drill rod handling device, such as that described in U.S. Pat. No. 8,186,925, issued on May 29, 2012, the entire contents of which are hereby incorporated by reference herein. Next driving mechanism can automatically advance the pin end 104 of the second drill rod 204 into the box end 108 of the first drill rod 204. A joint between the first drill rod 204 and the second drill rod 204 may be made by threading the second drill rod 204 into the first drill rod 204. One will appreciate in light of the disclosure herein that the leading ends 134, 136 of the male and female threads 110, 112 of the drill rods 204 can prevent or reduce jamming and cross-threading even when the joint between the drill rods 204 is made automatically by the drill rig 301.
Accordingly, the figures and the corresponding text, provide a number of different components and mechanisms for making joints between drill string components with increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading. In addition to the foregoing, implementations of the present invention can also be described in terms acts and steps in a method for accomplishing a particular result. For example, a method of a method of making a joint in a drill string with increased load efficiency and load capacity and with resistance to wear, jamming and cross-threading is described below with reference to the components and diagrams of FIGS. 1 through 12.
The method can involve inserting a pin end 104 of a first drill string component 102 into a box end 108 of a second drill string component 106. The method can also involve rotating the first drill sting component 102 relative to the second drill string component 108. The method can further involve abutting a planar leading end 134 of a male thread 110 on the pin end 104 of the first drill string component 102 against a planar leading end 136 of a female thread 112 on the box end 108 of the second drill string component 106.
The planar leading end 134 of the male thread 110 can be oriented at an acute angle 146 relative to a central axis 26 of the first drill string component 102. Similarly, the planar leading end 136 of the female thread 112 can be oriented at an acute angle 148 relative to a central axis 126 of the second drill string component 106.
The method can further involve sliding the planar leading end 114 of the male thread 110 against and along the planar leading end 120 of the female thread 112 to guide the male thread 110 into a gap between turns of the female thread 112. Sliding the planar leading end 134 of the male thread 110 against and along the planar leading end 136 of the female thread 112 can cause the first drill string component 102 to rotate relative to the second drill string component 106 due to the acute angles 146, 148 of the planar leading ends 134, 136 of the male and female threads 110, 112. The method can involve automatically rotating and advancing the first drill sting component 102 relative to the second drill string component 106 using a drill rig 301 without manually handling the drill string components 106, 108.
The planar leading end 120 of the female thread 112 can extend along an entire depth 132 of the female thread 110. The planar leading end 114 of the male thread 110 can extend along an entire depth 130 of the male thread 110. When rotating the first drill sting component 102 relative to the second drill string component 108, the depths of the planar leading ends 134, 136 of the female thread 112 and the male thread 110 can prevent jamming or wedging of the male and female threads 110, 112.
Thus, implementations of the foregoing provide various desirable features. For instance, by including leading ends or start faces which are optionally the full width of the thread, the tail-type thread start can be eliminated, thereby allowing: (a) substantially full circumference rotational positioning for threading; and (b) a guiding surface for placing mating threads into a threading position. For instance, the angled start face can engage a corresponding thread or thread start face and direct the corresponding thread into a threading position between helical threads. Moreover, at any position of the corresponding threads, the tail has been eliminated to virtually eliminate wedging geometry.
Similar benefits may be obtained regardless of whether threading is concentric or off-center in nature. For instance, in an off-center arrangement, a line intersecting a thread crest and a thread start face may comprise a joint taper. Under feed, the thread start face can mate with the mating thread crest in a manner that reduces or eliminates wedging as the intersection and subsequent thread resist wedging, jamming, and cross-threading. In such an embodiment, a joint taper as further disclosed herein may be sufficient to reduce the major diameter at a smaller end of a male thread to be less than a minor diameter at a large end of a female thread. Thus, off-center threading may be used for tapered threads.
Threads of the present disclosure may be formed in any number of suitable manners. For instance, as described previously, turning devices such as lathes may have difficulty creating an abrupt thread start face such as those disclosed herein. Accordingly, in some embodiments, a thread may be formed to comprise a tail. A subsequent grinding, milling, or other process may then be employed to remove a portion of the tail and create a thread start such as those described herein, or may be learned from a review of the disclosure herein. In other embodiments, other equipment may be utilized, including a combination of turning and other machining equipment. For instance, a lathe may produce a portion of the thread while other machinery can further process a male or female component to add a thread start face. In still other embodiments, molding, casting, single point cutting, taps and dies, die heads, milling, grinding, rolling, lapping, or other processes, or any combination of the foregoing, may be used to create a thread in accordance with the disclosure herein.
In one exemplary embodiment, a threaded drill string component for a drill rod, a casing, an adaptor coupling, a reamer, a drill bit, a locking coupling, and the like, is provided that comprises a hollow body, at least two male helical threads, and at least two corresponding female helical threads. In this aspect, the hollow body has a first end, an opposing second end, and a central axis that extends through the hollow body. The hollow body can be a thin-walled body that has a wall thickness between approximately 5 percent and 15 percent of an outer diameter of the hollow body. It is contemplated that the at least two male helical threads are positioned on the first end of the hollow body and the at least two corresponding female helical threads can be defined in the second end of the hollow body. In this aspect, the first end can be a pin end and the second end can be a box end.
In this aspect, each thread can comprise a plurality of helical turns that extend along the respective first and second ends of the hollow body. Further, each thread comprises a thread root, a thread crest, a thread pitch, a thread width, and a pressure flank angle between about degrees to about −25 degrees (optionally, a negative pressure flank angle between about −7.5 degrees to about −23 degrees). It is contemplated that at least one of the thread width and the thread pitch of the at least two threads of the respective male and female helical threads can increase from a first value proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof to a final value at a desired point on the respective thread.
In this aspect, optionally, at least one of the thread width and the thread pitch of the at least two threads of the respective male and female helical threads can remains substantially constant from proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof. In another option, at least one of the width and the pitch can increase uniformly from the first value to a final value across the full axial length of the plurality of helical turns. It is also contemplated that at least one of the width and the pitch can increase non-uniformly from the first value to a final value across the full axial length of the plurality of helical turns. In yet another optional aspect, at least one of the width and the pitch of the respective threads can increase from the first value to a final value across a portion of the axial length of the plurality of helical turns and remains constant thereafter.
In another aspect, it is contemplated that at least one of the thread width and the thread pitch of the at least two male helical threads is different from the at least two corresponding female helical threads. It is also contemplated that both the thread width and the thread pitch of the at least two male helical threads can be different from the at least two corresponding female helical threads.
In a further aspect, the crest of the at least one thread circumscribes a frusta-conical surface can extend over at least a portion of the axial length of the plurality of helical turns thereof. In this aspect, the generatrix of the frusta-conical surface forms a substantially straight line that lies at an angle relative to the central axis extending through the hollow body. Optionally, the generatrix of the frusta-conical surface can form a curved line that begins at an angle relative to the central axis extending through the hollow body.
In another exemplary embodiment, the threaded drill string component can be a drill rod, a casing, an adaptor coupling, a reamer, a drill bit, a locking coupling, and the like and can comprise a hollow body having a first end, an opposing second end, and a central axis extending through the hollow body; at least two male helical threads positioned on the first end of the hollow body; and at least two corresponding female helical threads defined in the second end of the hollow body. Optionally, the respective leading ends of the at least two threads can be evenly spaced about the first end of the hollow body. In this aspect, it is contemplated that the first end comprises a pin end and the second end comprises a box end.
In this aspect, each thread can comprise a plurality of helical turns that extend along the respective first and second ends of the hollow body, a thread root, a thread crest, a thread pitch, a thread width, and a pressure flank angle (optionally, a negative pressure flank angle). In one aspect, the pressure flank angle can be between about 5 degrees to about −25 degrees (optionally, between about −7.5 degrees to about −23 degrees). In this aspect, it is contemplated that the thread width and the thread pitch of the respective male and female helical threads can remain substantially constant from proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof. Further, at least one of the thread width and the thread pitch of the at least two male helical threads can be different from the at least two corresponding female helical threads. Optionally, it is contemplated that both the thread width and the thread pitch of the at least two male helical threads differs from the at least two corresponding female helical threads.
In this aspect, the crest of the at least one thread can circumscribe a frusta-conical surface that extends over at least a portion of the axial length of the plurality of helical turns thereof. Optionally, the generatrix of the frusta-conical surface can form a substantially straight line that lies at an angle relative to the central axis extending through the hollow body or a curved line that begins at an angle relative to the central axis extending through the hollow body. It is also contemplated that the respective leading ends of the at least two threads are evenly spaced about the first end of the hollow body.
In a further exemplary aspect, the threaded drill string component can comprise a hollow body having a pin end, an opposing box end, and a central axis extending through the hollow body. In this aspect, the pin end can have a predominantly radially extending terminal shoulder and a substantially circular cylinder external surface that extends axially from the pin thread to closely adjacent to the pin shoulder. Further, the box end can have a predominantly radially extending terminal shoulder and a substantially circular cylinder internal surface that extends axially from the box thread to closely adjacent to the box shoulder.
In an additional aspect, at least two male helical threads are positioned on the pin end of the hollow body and at least two corresponding female helical threads defined in the box end of the hollow body. In this aspect, each thread can comprise a plurality of helical turns that extend along the respective pin and box ends of the hollow body a thread root, a thread crest, a thread pitch, a thread width; and pressure flank. Each pressure flank can have a helical tapered surface abuttable against the helical tapered surface of the other flank that is positioned at a pressure flank angle (optionally, a negative pressure flank angle) between about 5 degrees to about −25 degrees (optionally, between about −7.5 degrees to about −23 degrees) relative to a plane perpendicular to the central axis. In this particular aspect, the crest of the at least one thread circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof and a generatrix of the frusta-conical surface forms a substantially straight line that lies at an angle relative to the central axis extending through the hollow body. Optionally, the angle of taper of the threads can be between about 0.5 degrees to about 1.6 degrees relative to the central axis.
Optionally, at least one of the thread width and the thread pitch of the at least one thread can increase from a first value proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof to a final value at a desired point on the at least one thread. In another aspect, at least one of the width and the pitch can increase uniformly from the first value to a final value across the full axial length of the plurality of helical turns. It is also contemplated that at least one of the width and the pitch can increase non-uniformly from the first value to a final value across the full axial length or a portion of the axial length of the plurality of helical turns.
Optionally, at least one of the thread width and the thread pitch of the respective male and female helical threads can remain substantially constant from proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof. In an optional aspect, it is contemplated that at least one of the thread width and the thread pitch of the at least two male helical threads can differ from the at least two corresponding female helical threads. In another option, it is also contemplated that both the thread width and the thread pitch of the at least two male helical threads can be different from the at least two corresponding female helical threads.
In another aspect, each of the respective at least two threads can have a substantially constant taper and of the same taper between a first annular section having a terminal annular end shoulder and a second annular section having an annular base shoulder axially opposite the terminal end shoulder. In this aspect, the threads can be formed to have substantially constant depths between the respective first and second annular section.
In a further exemplary embodiment, the threaded drill string component can comprise: a hollow body having a pin end, an opposing box end, and a central axis extending through the hollow body; at least two male helical threads positioned on the pin end of the hollow body; and at least two corresponding female helical threads defined in the box end of the hollow body. In this aspect, each of the at least two threads on the respective box and pin ends can comprise a plurality of helical turns extending along the respective pin and box ends of the hollow body; a thread root, a thread crest, a thread pitch, a thread width, and a pressure flank. In this aspect, the pressure flank can have a helical tapered surface abuttable against the helical tapered surface of the other flank that is positioned at a pressure flank angle (optionally, a negative pressure flank angle). Optionally, the pressure flank angle can be between about 5 degrees to about −25 degrees (or, more preferably, between about −7.5 degrees to about −23 degrees) relative to a plane perpendicular to the central axis. In a further aspect, it is contemplated that the crest of the at least one thread can circumscribe a frusta-conical surface that extends over at least a portion of the axial length of the plurality of helical turns thereof. In this aspect, the generatrix of the frusta-conical surface forms a curved line that begins at an angle relative to the central axis extending through the hollow body.
In this aspect, the pin end can have a predominantly radially extending terminal shoulder and a substantially circular cylinder external surface that extends axially from the pin thread to closely adjacent to the pin shoulder. In a similar aspect, the box end can have a predominantly radially extending terminal shoulder and a substantially circular cylinder internal surface extending axially from the box thread to closely adjacent to the box shoulder. In is contemplated that at least one of the thread width and the thread pitch of the at least two threads on the respective box and pin ends can remain substantially constant from proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof. Optionally, it is also contemplated that both the thread width and the thread pitch of the at least two male helical threads can differ from the at least two corresponding female helical threads. In exemplary aspects, a threaded drill string component as disclosed herein can comprise: a hollow body having a first end, an opposing second end, and a central axis extending through the hollow body; at least two male helical threads positioned on the first end of the hollow body; and at least two corresponding female helical threads defined in the second end of the hollow body, wherein each thread comprises: a plurality of helical turns extending along the respective first and second ends of the hollow body; a thread root, a thread crest, a thread pitch, and a thread width; and a negative pressure flank angle, wherein at least one of the thread width and the thread pitch of the at least two threads of the respective male and female helical threads increases from a first value proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof to a final value at a desired point on the respective thread.
In other exemplary aspects, a threaded drill string component as disclosed herein can comprise: a hollow body having a first end, an opposing second end, and a central axis extending through the hollow body; at least two male helical threads positioned on the first end of the hollow body; and at least two corresponding female helical threads defined in the second end of the hollow body, wherein each thread comprises: a plurality of helical turns extending along the respective first and second ends of the hollow body, a thread root, a thread crest, a thread pitch, and a thread width, and a negative pressure flank angle, wherein the thread width and the thread pitch of the respective male and female helical threads remains substantially constant from proximate the leading end over at least a portion of the axial length of the plurality of helical turns thereof, and wherein at least one of the thread width and the thread pitch of the at least two male helical threads is different from the at least two corresponding female helical threads.
In other exemplary aspects, a threaded drill string component as disclosed herein can comprise a hollow body having a pin end, an opposing box end, and a central axis extending through the hollow body, wherein the pin end has a predominantly radially extending terminal shoulder and a substantially circular cylinder, axially extending external surface extending from the pin thread to closely adjacent to the pin shoulder, and wherein the box end has a predominantly radially extending terminal shoulder and a substantially circular cylinder, axial internal surface extending axially from the box thread to closely adjacent to the box shoulder, at least two male helical threads positioned on the pin end of the hollow body; and at least two corresponding female helical threads defined in the box end of the hollow body, wherein each thread comprises: a plurality of helical turns extending along the respective pin and box ends of the hollow body; a thread root, a thread crest, a thread pitch, and a thread width; and a negative pressure flank angle, wherein the crest of the at least one thread circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and wherein a generatrix of the frusta-conical surface is a straight line that lies at an angle relative to the central axis extending through the hollow body, wherein the angle of taper of the threads being 0.5° to 1.6° relative to the central axis.
In other exemplary aspects, a threaded drill string component as disclosed herein can comprise a hollow body having a pin end, an opposing box end, and a central axis extending through the hollow body; at least two male helical threads positioned on the pin end of the hollow body; and at least two corresponding female helical threads defined in the box end of the hollow body, wherein each of the at least two threads on the respective box and pin ends comprise: a plurality of helical turns extending along the respective pin and box ends of the hollow body; a thread root, a thread crest, a thread pitch, and a thread width; and a negative pressure flank angle, wherein the crest of the at least one thread circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, wherein the crest of the at least one thread circumscribes a curved frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and wherein the generatrix of the frusta-conical surface is a curved line that begins at an angle relative to the central axis extending through the hollow body.
Exemplary Drill String Components Having Cylindrical Shoulders
In various exemplary aspects, and with reference to FIGS. 1-11B, a threaded drill string component 102, 106 as disclosed herein can comprise a hollow body 103 or 107 having an outer surface, an inner surface, first end, an opposing second end, an intermediate body portion 105 or 109 positioned between the first and second ends, and a central axis 126 extending through the hollow body. In these aspects, the drill string component 102 or 106 can comprise a first plurality of threads 110 or 112 positioned on the first end 104 or 108 of the hollow body. In one aspect, the first end of the hollow body can define first and second cylindrical shoulders 160, 162 or 170, 172 that are spaced apart relative to the central axis 126 of the hollow body. In this aspect, the first and second cylindrical shoulders can have respective cylindrical inner and outer surfaces. In another aspect, each thread 110 or 112 of the first end 104 or 108 of the hollow body 103 or 107 can comprise a plurality of helical turns extending along the first end of the hollow body between the first and second cylindrical shoulders 160, 162 or 170, 172 of the first end of the hollow body.
In some exemplary aspects, the first plurality of threads 110 can be positioned on the outer surface of the pin end 104 of the hollow body 103, 107 between the cylindrical outer surfaces 161b, 163b of the first and second cylindrical shoulders 160, 162. In these aspects, the first and second cylindrical shoulders 160, 162 can also have cylindrical inner surfaces 161a, 163a. Optionally, in these aspects, the threaded drill string component 102, 106 can further comprise a second plurality of threads 112 positioned on the inner surface of the box end 108 of the hollow body 103. In one aspect, the inner surface of the box end of the hollow body 103 can define third and fourth cylindrical shoulders 170, 172 that are spaced apart relative to the central axis 126 of the hollow body 103, 107. In this aspect, the third and fourth cylindrical shoulders 170, 172 can have respective cylindrical inner and outer surfaces 171a, 173a and 171b, 173b. In a further aspect, each thread 112 of the second plurality of threads can comprise a plurality of helical turns extending along the box end 108 of the hollow body 103 between the third and fourth cylindrical shoulders 170, 172.
In additional aspects, each thread of the first plurality of threads 110, 112 can have a thread root 34, 35, a thread crest 32, 33, and a pressure flank surface 138, 142 extending radially from the thread root to the thread crest. In these aspects, and with reference to FIGS. 5A-6D, the pressure flank surface 138, 142 of each thread of the first plurality of threads 110, 112 can define a pressure flank angle 30, 31 relative to a plane perpendicular to the central axis. Optionally, in some aspects, the pressure flank angle 30, 31 of each thread can range from about 5 degrees to about −30 degrees. In other optional aspects, the pressure flank angle of each thread can range from about −7.5 degrees to about −23 degrees.
In further aspects, each thread of the first plurality of threads 110, 112 can have a clearance flank surface 140, 144 that is opposed from the pressure flank surface 138, 142 relative to the central axis 126 and that extends radially from the thread root 34, 35 to the thread crest 32, 33. In these aspects, the pressure flank surface 138, 142 of each thread 110, 112 can be positioned between the clearance flank surface 140, 144 of the thread and the intermediate body portion 105, 109 relative to the central axis 126. In another aspect, the clearance flank surface 140, 144 of each thread 110, 112 of the first plurality of threads can define a clearance flank angle 41, 40 relative to the central axis. In exemplary aspects, the clearance flank angle can be at least 45 degrees and can optionally be about 45 degrees, about 50 degrees, about 55 degrees, about 60 degrees, about 65 degrees, about 70 degrees, about 75 degrees, about 80 degrees, or about 85 degrees.
Optionally, in some aspects, the thread crest 32, 33 of at least one thread 110, 112 of the first plurality of threads can circumscribe a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and the generatrix 64, 66 of the frusta-conical surface can be a straight line that lies at a joint taper angle 60, 62 relative to the central axis 126 extending through the hollow body. Optionally, in these aspects, the joint taper angle 60, 62 can range from about 0.5 degrees to about 1.5 degrees relative to the central axis 126.
Optionally, in further aspects, the thread crest 32, 33 of at least one thread 110, 112 of the first plurality of threads can circumscribe a curved frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and the generatrix 64, 66 of the frusta-conical surface can be a curved line that begins at a joint taper angle 60, 62 relative to the central axis 126 extending through the hollow body 103, 107. Optionally, in these aspects, the joint taper angle 60, 62 can range from about 0.5 degrees to about 1.5 degrees relative to the central axis 126.
In additional exemplary aspects, the first plurality of threads 112 can be positioned on the inner surface of the box end 108 of the hollow body 103 or 107 between the cylindrical inner surfaces 171a, 173a of the first and second cylindrical shoulders 170, 172. In these aspects, the first and second cylindrical shoulders 170, 172 can also have cylindrical outer surfaces 171b, 173b. In these aspects, the threaded drill string component 102, 106 can further comprise a second plurality of threads 110 positioned on the outer surface of the pin end 104 of the hollow body. In one aspect, the outer surface of the pin end 104 of the hollow body 103 or 107 can define third and fourth cylindrical shoulders 160, 162 that are spaced apart relative to the central axis 126 of the hollow body. In this aspect, the third and fourth cylindrical shoulders 160, 162 can have respective cylindrical inner and outer surfaces 161a, 163a and 161b, 163b. In a further aspect, each thread 110 of the second plurality of threads can comprise a plurality of helical turns extending along the pin end 104 of the hollow body between the third and fourth cylindrical shoulders 160, 162.
In further exemplary aspects, each thread 112 of the first plurality of threads can a thread root 35, a thread crest 33, and a pressure flank surface 142 extending radially from the thread root to the thread crest. In these aspects, the pressure flank surface 142 of each thread 112 of the first plurality of threads can define a pressure flank angle 31 relative to a plane perpendicular to the drill string central axis 126. It is further contemplated that each thread 110 of the second plurality of threads can have a thread root 34, a thread crest 32, and a pressure flank surface 138 extending radially from the thread root to the thread crest. It is still further contemplated that the pressure flank surface 138 of each thread 110 of the second plurality of threads can define a pressure flank angle 30 relative to a plane perpendicular to the central axis 126. In exemplary aspects, the pressure flank angle 30, 31 of each thread 110, 112 can range from about 5 degrees to about −30 degrees. Optionally, in other exemplary aspects, the pressure flank angle 30, 31 of each thread 110, 112 can range from about −7.5 degrees to about −23 degrees.
Optionally, and with reference to FIGS. 5C and 6D, it is contemplated that undercut portions 164, 174 can be provided at the junction between shoulders 162, 172 and their adjacent intermediate body portions 105, 109. These undercut portions 164, 174 can be cut into the surfaces of the drill string components 102, 106 to extend the face and surface area of the surfaces at the junction with the intermediate body portions 105, 109. As one will appreciate, lathe machine tool inserts typically have a rounded tip, and the presence of the undercut portions 164 eliminates the need for reducing the depth of the shoulder face. If the undercut portions 164, 174 are not provided, then it is necessary to reduce the depth of the shoulder face by the radius of the rounded tip of the lathe tool insert.
Exemplary Drill String Components Having Pressure Flanks and a Joint Taper
In still further exemplary aspects, and with reference to FIGS. 1-11B, a threaded drill string component 102, 106 as disclosed herein can comprise a hollow body 103, 107 having an outer surface, an inner surface, a first end, an opposing second end, an intermediate body portion 105, 109 positioned between the first and second ends, and a central axis 126 extending through the hollow body. In these aspects, the drill string component 102, 106 can further comprise a plurality of threads 110, 112 positioned on the first end of the hollow body. It is contemplated that the first end of the hollow body can be a pin end 104 or a box end 108 as further disclosed herein. In one aspect, each thread 110, 112 of the first end of the hollow body can comprise a plurality of helical turns extending along the first end of the hollow body. In another aspect, each thread of the plurality of threads 110, 112 has a thread root 34, 35, a thread crest 32, 33, and a pressure flank surface 138, 142 extending radially from the thread root to the thread crest. In this aspect, the pressure flank surface 138, 142 of each thread 110, 112 of the plurality of threads can define a pressure flank angle 30, 31 relative to a plane perpendicular to the central axis 126. In a further aspect, the thread crest 32, 33 of at least one thread 110, 112 of the plurality of threads can circumscribe a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof. Optionally, in exemplary aspects, the pressure flank angle 30, 31 of each thread 110, 112 can range from about 5 degrees to about −30 degrees. Optionally, in other aspects, the pressure flank angle 30, 31 of each thread 110, 112 can range from about −7.5 degrees to about −23 degrees.
Optionally, in some aspects, the generatrix 64, 66 of the frusta-conical surface circumscribed by the thread crest 32, 33 of at least one thread 110, 112 of the plurality of threads can be a straight line that lies at a joint taper angle 60, 62 relative to the central axis 126 extending through the hollow body. In these aspects, it is contemplated that the joint taper angle 60, 62 can range from about 0.5 degrees to about 1.5 degrees.
Optionally, in still other aspects, the generatrix 64, 66 of the frusta-conical surface circumscribed by the thread crest 32, 33 of at least one thread 110, 112 of the plurality of threads can be a curved line that begins at a joint taper angle 60, 62 relative to the central axis 126 extending through the hollow body. In these aspects, it is contemplated that the joint taper angle 60, 62 can range from about 0.5 degrees to about 1.5 degrees.
Optionally, in exemplary aspects, the drill string component 102, 106 can have first and second ends (pin and box ends 104, 108) having threads with pressure flank angles 30, 31 and joint taper angles 60, 62 as disclosed herein.
a hollow body having an outer surface, an inner surface, first end, an opposing second end, an intermediate body portion positioned between the first and second ends, and a central axis extending through the hollow body; and
a first plurality of threads positioned on the first end of the hollow body,
wherein the first end of the hollow body defines first and second cylindrical shoulders that are spaced apart relative to the central axis of the hollow body, wherein the first and second cylindrical shoulders have respective cylindrical inner and outer surfaces,
wherein each thread of the first end of the hollow body comprises a thread crest, a thread root, and a plurality of helical turns extending along the first end of the hollow body between the first and second cylindrical shoulders of the first end of the hollow body, and
wherein the thread root of each thread of the first plurality of threads has a frustoconical surface that is tapered relative to the central axis between the first and second shoulders.
2. The threaded drill string component of claim 1, wherein the first plurality of threads are positioned on the outer surface of the first end of the hollow body between the cylindrical outer surfaces of the first and second cylindrical shoulders.
3. The threaded drill string component of claim 2, wherein the threaded drill string component further comprises a second plurality of threads positioned on the inner surface of the second end of the hollow body, wherein the inner surface of the second end of the hollow body defines third and fourth cylindrical shoulders that are spaced apart relative to the central axis of the hollow body, wherein the third and fourth cylindrical shoulders have respective cylindrical inner and outer surfaces, and wherein each thread of the second plurality of threads comprises a plurality of helical turns extending along the second end of the hollow body between the third and fourth cylindrical shoulders.
4. The threaded drill string component of claim 3, wherein each thread of the first plurality of threads has a pressure flank surface extending radially from the thread root to the thread crest, wherein the pressure flank surface of each thread of the first plurality of threads defines a pressure flank angle relative to a plane perpendicular to the drill string central axis, wherein each thread of the second plurality of threads has a thread root, a thread crest, and a pressure flank surface extending radially from the thread root to the thread crest, wherein the pressure flank surface of each thread of the second plurality of threads defines a pressure flank angle relative to a plane perpendicular to the central axis.
5. The threaded drill string component of claim 4, wherein the pressure flank angle of each thread ranges from about 5 degrees to about −30 degrees.
6. The threaded drill string component of claim 4, wherein the pressure flank angle of each thread ranges from about −7.5 degrees to about −23 degrees.
7. The threaded drill string component of claim 3, wherein the second cylindrical shoulder is spaced toward the second end of the hollow body with respect to the first cylindrical shoulder, wherein the fourth cylindrical shoulder is spaced toward the first end of the hollow body with respect to the third cylindrical shoulder, wherein the outer surface of the hollow body defines a first undercut portion at a junction between the second cylindrical shoulder and the intermediate body portion, and wherein the inner surface of the hollow body defines a second undercut portion at a junction between the fourth cylindrical shoulder and the intermediate body portion.
8. The threaded drill string component of claim 3, wherein the first cylindrical surface extends to the first end of the drill string component, wherein the third cylindrical surface extends to the second end of the drill string component, wherein a spacing between the inner surface and the outer surface of the first cylindrical surface defines a first wall thickness, wherein a spacing between the inner surface and the outer surface of the third cylindrical surface defines a second wall thickness, and wherein the second wall thickness is greater than the first wall thickness.
9. The threaded drill string component of claim 1, wherein the first plurality of threads are positioned on the inner surface of the first end of the hollow body between the cylindrical inner surfaces of the first and second cylindrical shoulders.
10. The threaded drill string component of claim 9, wherein the threaded drill string component further comprises a second plurality of threads positioned on the outer surface of the second end of the hollow body, wherein the outer surface of the second end of the hollow body defines third and fourth cylindrical shoulders that are spaced apart relative to the central axis of the hollow body, wherein the third and fourth cylindrical shoulders have respective cylindrical inner and outer surfaces, and wherein each thread of the second plurality of threads comprises a plurality of helical turns extending along the second end of the hollow body between the third and fourth cylindrical shoulders.
11. The threaded drill string component of claim 1, wherein each thread of the first plurality of threads has a pressure flank surface extending radially from the thread root to the thread crest, wherein the pressure flank surface of each thread of the first plurality of threads defines a pressure flank angle relative to a plane perpendicular to the central axis.
12. The threaded drill string component of claim 11, wherein the pressure flank angle of each thread ranges from about 5 degrees to about −30 degrees.
13. The threaded drill string component of claim 11, wherein the pressure flank angle of each thread ranges from about −7.5 degrees to about −23 degrees.
14. The threaded drill string component of claim 12, wherein each thread of the first plurality of threads has a clearance flank surface that is opposed from the pressure flank surface relative to the central axis and that extends radially from the thread root to the thread crest, wherein the pressure flank surface of each thread is positioned between the clearance flank surface of the thread and the intermediate body portion relative to the central axis, wherein the clearance flank surface of each thread of the first plurality of threads defines a clearance flank angle relative to the central axis, and wherein the clearance flank angle is at least 45 degrees.
15. The threaded drill string component of claim 11, wherein the thread crest of at least one thread of the first plurality of threads circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and wherein the generatrix of the frusta-conical surface is a straight line that lies at a joint taper angle relative to the central axis extending through the hollow body.
16. The threaded drill string component of claim 15, wherein the joint taper angle ranges from about 0.5 degrees to about 1.5 degrees relative to the central axis.
17. The threaded drill string component of claim 11, wherein the thread crest of at least one thread of the first plurality of threads circumscribes a curved frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and wherein the generatrix of the frusta-conical surface is a curved line that begins at a joint taper angle relative to the central axis extending through the hollow body.
18. The threaded drill string component of claim 17, wherein the joint taper angle ranges from about 0.5 degrees to about 1.5 degrees relative to the central axis.
19. The threaded drill string component of claim 1, wherein the second cylindrical shoulder is spaced toward the second end of the hollow body with respect to the first cylindrical shoulder, and wherein the outer surface of the hollow body defines a first undercut portion at a junction between the second cylindrical shoulder and the intermediate body portion.
20. A threaded drill string component, comprising:
wherein each thread of the first end of the hollow body comprises a plurality of helical turns extending along the first end of the hollow body between the first and second cylindrical shoulders of the first end of the hollow body,
wherein each thread of the first plurality of threads has a thread root, a thread crest, and a pressure flank surface extending radially from the thread root to the thread crest, wherein the pressure flank surface of each thread of the first plurality of threads defines a pressure flank angle relative to a plane perpendicular to the central axis, and
21. The threaded drill string component of claim 20, wherein the pressure flank angle of each thread ranges from about 5 degrees to about −30 degrees.
22. The threaded drill string component of claim 20, wherein the pressure flank angle of each thread ranges from about −7.5 degrees to about −23 degrees.
23. A threaded drill string component, comprising:
a plurality of threads positioned on the first end of the hollow body,
wherein each thread of the first end of the hollow body comprises a plurality of helical turns extending along the first end of the hollow body,
wherein each thread of the plurality of threads has a thread root, a thread crest, and a pressure flank surface extending radially from the thread root to the thread crest, wherein the pressure flank surface of each thread of the plurality of threads defines a pressure flank angle relative to a plane perpendicular to the central axis,
wherein the thread crest of at least one thread of the plurality of threads circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, and
wherein the thread root of each thread of the plurality of threads has a frustoconical surface that is tapered relative to the central axis between the first and second shoulders.
24. The threaded drill string component of claim 23, wherein the pressure flank angle of each thread ranges from about 5 degrees to about −30 degrees.
25. The threaded drill string component of claim 23, wherein the pressure flank angle of each thread ranges from about −7.5 degrees to about −23 degrees.
26. The threaded drill string component of claim 23, wherein the generatrix of the frusta-conical surface circumscribed by the thread crest of at least one thread of the plurality of threads is a straight line that lies at a joint taper angle relative to the central axis extending through the hollow body, wherein the joint taper angle ranges from about 0.5 degrees to about 1.5 degrees.
27. The threaded drill string component of claim 23, wherein the generatrix of the frusta-conical surface circumscribed by the thread crest of at least one thread of the plurality of threads is a curved line that begins at a joint taper angle relative to the central axis extending through the hollow body, wherein the joint taper angle ranges from about 0.5 degrees to about 1.5 degrees.
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Response to Non-Final Office Action filed on Nov. 16, 2016 with the U.S. Patent and Trademark Office for U.S. Appl. No. 14/026,611, filed Sep. 13, 2013 and published as US 2014/0102808 dated Apr. 17, 2014 (Inventor—Drenth et al.; Applicant—Longyear TM, Inc.) (19 pages).
Final Office Action dated Feb. 23, 2017 by the U.S. Patent and Trademark Office for U.S. Appl. No. 14/026,611, filed Sep. 13, 2013 and published as US 2014/0102808 on Apr. 17, 2014 (Inventor—Drenth et al.; Applicant—Longyear TM, Inc.) (14 pages).
Non-Final Office Action issued by the U.S. Patent & Trademark Office dated Aug. 1, 2016 for U.S. Appl. No. 14/026,611, filed Sep. 13, 2013 and published as US-2014-012808-A1 on Apr. 17, 2014 (Applicant—Boart Longyear, Inc. // Inventor—Drenth, et al.) (16 pages).
Patent number: 10557316
Patent Publication Number: 20160024856
Assignee: BLY IP INC. (Salt Lake City, UT)
Inventor: Christopher L. Drenth (Burlington)
Application Number: 14/876,501
International Classification: E21B 17/042 (20060101);