EP2895679A1 - Composants de train de tiges de forage présentant des joints à filetages multiples - Google Patents

Composants de train de tiges de forage présentant des joints à filetages multiples

Info

Publication number
EP2895679A1
EP2895679A1 EP13837637.1A EP13837637A EP2895679A1 EP 2895679 A1 EP2895679 A1 EP 2895679A1 EP 13837637 A EP13837637 A EP 13837637A EP 2895679 A1 EP2895679 A1 EP 2895679A1
Authority
EP
European Patent Office
Prior art keywords
thread
drill string
threads
string component
recited
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13837637.1A
Other languages
German (de)
English (en)
Other versions
EP2895679B1 (fr
EP2895679A4 (fr
Inventor
Christopher L. Drenth
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BLY IP Inc
Original Assignee
Longyear TM Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Longyear TM Inc filed Critical Longyear TM Inc
Priority to EP20180399.6A priority Critical patent/EP3767068A1/fr
Publication of EP2895679A1 publication Critical patent/EP2895679A1/fr
Publication of EP2895679A4 publication Critical patent/EP2895679A4/fr
Application granted granted Critical
Publication of EP2895679B1 publication Critical patent/EP2895679B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • E21B17/0423—Threaded with plural threaded sections, e.g. with two-step threads

Definitions

  • implementations of the present invention relate generally to components and systems for drilling.
  • implementations of the present invention relate to drill components comprising increased strength and resistance to jamming, cross-threading and wedging.
  • Threaded connections have been well known for ages, and threads provide a significant advantage in that a helical structure of the thread can convert a rotational movement and force into a linear movement and force.
  • Threads exist on many types of elements, and can be used in limitless applications and industries. For instance, threads are essential to screws, bolts, and other types of mechanical fasteners that may engage a surface (e.g., in the case of a screw) or be used in connection with a nut (e.g., in the case of a bolt) to hold multiple elements together, apply a force to an element, or for any other suitable purpose. Threading is also common in virtually any industry in which elements are mechanically fastened together.
  • Pipes are used to deliver liquids or gasses under pressure.
  • Pipes may have threaded ends that mate with corresponding threads of an adjoining pipe, plug, adaptor, connector, or other structure. The threads can be used in creating a fluid-tight seal to guard against fluid leakage at the connection site.
  • Oilfield, exploration, and other drilling technologies also make extensive use of threading.
  • casing elements may be placed inside the well.
  • the casings generally have a fixed length and multiple casings are secured to each other in order to produce a casing of the desired height.
  • the casings can be connected together using threading on opposing ends thereof.
  • a drill rod or other similar device may be used as drilling elements are used to create a well or to place objects inside a well.
  • multiple drill rods may be connected together, which can be facilitated using mating threads on opposing ends of the drill rod.
  • the drill rods and casings are ver large and machinery applies large forces in order to thread the rods or casings together.
  • threads may be created using existing cross-sectional shapes— or thread form— and different combinations of thread lead, pitch, and number of starts.
  • lead refers to the linear distance along an axis that is covered in a complete rotation.
  • Pitch refers to the distance from the crest of one thread to the next, and start refers to the number of starts, or ridges, wrapped around the cylinder of the threaded fastener.
  • a single-start connector is the most common, and comprises a single ridge wrapped around the fastener body.
  • a double-start connector comprises two ridges wrapped around the fastener body. Threads-per-inch is also a thread specification element, but is directly related to the thread lead, pitch, and start.
  • existing threads and thread forms are suitable for a number of applications, continued improvement is needed in other areas such as in high torque, high power, and/or high speed applications.
  • existing thread designs are inherently prone to jamming.
  • existing thread designs do not use available material effectively.
  • existing thread designs detract from load capacity of mated components.
  • existing thread designs exhibit excessive wear.
  • Jamming is the abnormal interaction between the start of a thread and a mating thread, such that in the course of a single turn, one thread partially passes under another, thereby becoming wedged therewith. Jamming can be particularly common where threaded connectors are tapered. In another instance, existing drill component designs can have limited drilling load capacity and fatigue load capacity as a result of the material afforded to the male thread or to the underlying material on the male end of a drill component.
  • multiple drill rods, casings, and the like can be made up. As more rods or casings are added, interference due to wedging or cross-threading can become greater. Indeed, with sufficient power (e.g., when made up using hydraulic power of a drill rig) a rod joint can be destroyed.
  • Coring rods in drilling applications also often have threads that are coarse with wide, flat threaded crests parallel to mating crests due to a mating interference fit or slight clearance fit dictated by many drill rod joint designs. The combination of thread tails and flat, parallel thread crests on coarse tapered threads creates an even larger potential for cross-threading interaction, which may not otherwise be present in other applications.
  • the opposing ends of male and female components may be different sizes.
  • a male threaded component may taper and gradually increase in size as distance from the end increases.
  • the female thread may be larger at the end.
  • the difference in size of tapered threads also makes tapered threads particularly prone to jamming, which is also referred to as cross-threading.
  • Cross- threading in tapered or other threads can result in significant damage to the threads and/or the components that include the threads. Damage to the threads may require replacement of the threaded component, result in a weakened connection, reduce the fluid-tight characteristics of a seal between components, or have other effects, or any combination of the foregoing.
  • tail-type thread starts have crests with a joint taper. If the male and female components are moved together without rotation, the tail crests can wedge together. If rotated, the tail crests can also wedge when fed based on relative alignment of the tails.
  • a thread tail is typically about one-half the circumference in length, and since the thread has a joint taper, there is less than half of the circumference of the respective male and female components providing rotational positioning for threading without wedging.
  • Such positional requirements may be particularly difficult to obtain in applications where large feed and rotational forces are used to mate corresponding components. For instance, in the automated making of coring rod connections in the drilling industry, the equipment may operate with sufficient forces such that jamming, wedging, or cross-threading is an all too common occurrence.
  • tail-type connections may also be prone to cross-threading, jamming, and wedging. Accordingly, when the male and female components are fed without rotation, the tail can wedge into a mating thread. Under rotation, the tail may also wedge into a mating thread. Wedging may be reduced, but after a threading opportunity (e.g., mating the tip of the tail in opening adjacent a mating tail), wedging may still occur due to the missed threading opportunity and misalignment.
  • Off-center threads may be configured such that a mid-tail crest on the mail component has equal or corresponding geometry relative to the female thread crest.
  • threaded connectors having tail-type thread starts can be particularly prone to thread jamming, cross-threading, wedging, joint seizure, and the like. Such difficulties may be particularly prevalent in certain industries, such as in connection with the designs of coring drill rods.
  • the thread start provides a leading end, or first end, of a male or female thread and mates with that of a mating thread to make a rod or other connection. If the tail-type thread starts jam, wedge, cross-thread, and the like, the rods may need to be removed from a drill site, and can require correction that requires a stop in drilling production.
  • drill rods and casings commonly make use of tapered threads and tapered joints such that the diameters at the thread starts are smaller than the diameters at the thread ends. Tapered threads and joints reduce the amount of cross-sectional material available to transfer loads. Tapered threads and joints are also prone to cross-threading difficulties. Since a coring rod may have a tapered thread, the tail at the start of the male thread may be smaller in diameter than that of the start of the female thread. As a result, there may be transitional geometry at the start of each thread to transition from a flush to a full thread profile. Because the thread start and transitional geometry may have sizes differing from that of the female thread, the transitional geometry and thread start may mate abnormally and wedge into each other.
  • the start of the male thread may have some clearance to the start of the female thread, such as where the mid-tail geometry corresponds to the geometry of the female thread.
  • the transitional geometry of the start of the thread may nonetheless interact abnormally with turns of the thread beyond the thread start, typically at subsequent turns of mating thread crests, thereby also resulting in jamming, cross-threading, wedging, and the like.
  • the presence of a tail generally acts as a wedge with a mating tail, thereby increasing the opportunity and probability of thread jamming.
  • tail-type thread designs are typically brought about by limitations of existing machining lathes.
  • threads are typically cut by rotational machining lathes which can only gradually apply changes in thread height or depth with rotation of the part.
  • threads are generally formed to include tails having geometry and tails identical or similar to other portions of the thread start.
  • traditional lathes are not capable of applying an abrupt vertical or near vertical transition from a flush to full thread profile to rotation of the part during machining. The gradual change is also required to remove sharp, partial feature edges of material created where the slight lead, or helix angle, of the thread meets the material being cut.
  • Wear is the erosion or displacement of thread material from its original position on the thread surface due to the relative mechanical actions of mating threads.
  • Existing thread designs can also be configured to create an interference fit on, for example, the major diameter of the mating components.
  • the male thread crest can be configured to create a radial interference with the female thread root.
  • the interference fit may be a significant source of thread wear as it can add greatly to the contact pressure between the threads as they slide relative to one another.
  • interference fits on thread features increase thread wear. Thread wear degrades the thread geometry thus the load capacity or load efficiency of the drill string component.
  • one or more implementations of the present invention overcome one or more of the foregoing or other problems in the art with drilling components, tools, and systems that provide for effective and efficient making of threaded joints.
  • one or more implementations of the present invention comprise drill string components comprising increased strength and resistance to jamming and cross-threading. Such drill string components can reduce or eliminate damage to threads due to jamming and cross-threading.
  • one or more implementations comprise drill string components having threads with a leading end or thread start oriented at an acute angle relative to the central axis of the drill string component. Additionally or alternatively, the leading end of the threads can provide an abrupt transition to full thread depth and/or width. Additionally or alternatively, the threads can have at least one of a variable thread pitch and a variable thread width.
  • the threads can have a cylindrical thread root and a thread crest that circumscribes a frusta-cone over at least a portion of the axial length of the threads.
  • one or more implementation of a threaded drill string component having increased strength and resistance to jamming and cross-threading comprises a hollow body having a first end, an opposing second end, and a central axis extending through the hollow body.
  • the drill string component also comprises at least one thread positioned on the first end of the hollow body.
  • the at least one thread comprises a plurality of helical turns extending along the first end of the hollow body.
  • the at least one thread has a thread depth, a thread width and a thread pitch.
  • the at least one thread comprises a leading end proximate the first end of the hollow body. The leading end of the at least one thread is orientated at an acute angle relative to the central axis of the hollow body.
  • the leading end of the at least one thread faces toward an adjacent turn of the thread.
  • the thread pitch of the at least one thread 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 at least one thread.
  • one or more implementation of a drill string component having increased strength and resistance to jamming and cross-threading comprises at least one thread having a thread crest and a thread root.
  • the thread root of the at least one thread circumscribes a cylindrical surface over the axial length of the plurality of helical turns thereof.
  • the thread 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.
  • one or more implementations of a drill string component having increased strength and resistance to jamming and cross-threading comprises a drill string component having a plurality of threads.
  • one or more implementations of a drill string component having increased strength and resistance to jamming and cross-threading comprises a drill string component that eliminates interference fits on thread features.
  • interference fits are provided at non-thread component features such as such as shoulder surfaces.
  • a threaded drill string component having increased strength and resistance to jamming and cross-threading comprises a body, a box end, an opposing pin end, and a central axis extending through the body.
  • the drill string component also comprises a female thread positioned on the box end of the body.
  • the female thread has a depth and a width.
  • the drill string component also comprises a male thread positioned on the pin end of the body.
  • the male thread has a depth and a width.
  • Each of the female thread and the male thread comprises a leading end.
  • the leading end of each of the female thread and the male thread comprises a planar surface extending normal to the body.
  • the planar surface of the leading end of the female thread extends along the entire width and the entire depth of the female thread.
  • planar surface of the leading end of the male thread extends along the entire width and the entire depth of the male thread.
  • 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.
  • 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.
  • Figure 1 illustrates fragmentary longitudinal sectional view through a plurality of connected drill rods in a drill string with a longitudinal intermediate portion of the drill rods being broken away;
  • Figure 2 is an enlarged fragmentary longitudinal sectional view of one of the drill rod joints of Figure 1, the dotted lines indicating the location of the crests and roots of threads diametrically opposite those shown in solid lines and the joint being shown in a hand tight condition;
  • Figure 3 is a fragmentary longitudinal view of a pin end of a drill rod oriented axially with the box end of an adjacent drill rod with the box and one half of the pin being shown in cross-section;
  • Figure 4 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 a thread with a leading end in accordance with one or more implementations of the present invention
  • Figure 5 illustrates a side view of an exploded drill string having drill string components having leading ends in accordance with one or more implementations of the present invention.
  • Figure 6 illustrates a schematic diagram of a drilling system including drill string components having leading ends in accordance with one or more implementations of the present invention
  • Implementations of the present invention are directed toward drilling components, tools, and systems that provide for effective drill thread components and efficient making of threaded joints.
  • one or more implementations of the present invention comprise drill string components with increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading.
  • Such drill string components can reduce or eliminate damage to threads due to wear, jamming and cross-threading while also increasing the load efficiency and load capacity over conventional drilling components.
  • one or more implementations comprise drill string components having multiple threads with leading ends or thread starts oriented at an acute angle relative to the central axis of the drill string component. Additionally or alternatively, the leading end of the thread can provide an abrupt transition to full thread depth and/or width. Furthermore, one or more
  • drill string components operable to provide a progressive fit and that conserve cross-sectional material comprise at least one of varying thread width to provide a progressive fit in an axial direction over at least a portion of the thread and tapering at least one of the mating thread crests over at least a portion of the thread while maintaining a constant root diameter over the entire thread.
  • a first drill siring 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.
  • each drill string component 102, 106 can comprise a hollow body having a central axis 126 extending there through as shown in Figures 1-4.
  • 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.
  • the drill string component can have the following typical dimensions:
  • the pin end 104 can comprise at least one male thread 110 (i.e., a thread that projects radially outward from outer surface of the pin end 104).
  • the box end 108 can comprise at least one female thread 112 (i.e., a thread that projects radially inward from an inner surface of the box end 108).
  • the at least one male thread 110 and the at least one female thread 112 can have generally corresponding characteristics (e.g., width, height or depth, threaded length, taper, lead, pitch, threads per inch, number of thread starts, pitch diameter, mating thread turns, etc.) or they can vary in one or more of the enumerated characteristics.
  • the at least one male thread 110 and at least one female thread 112 can comprise straight thread crests and roots.
  • at least one of the crests of the at least one male thread and at least one female thread 110, 1 12 are tapered while the thread roots of the threads 110, 112 remain constant.
  • the at least one male thread 110 may have characteristics corresponding to those of the at least one female thread 112 despite the characteristics changing along the respective lengths of pin end 104 or box end 108.
  • the at least one male and at least one female threads 110 are examples of the at least one male thread 110.
  • the at least one male and the at least one female threads 110, 112 can have a constant pitch as measured between thread at least one thread feature and a variable thread width over at least a portion of the threads 110, 112.
  • at least one of the crests of the at least one male thread and at least one female thread 110, 112 are tapered over a desired portion of the length of the threads 110, 112 while the thread roots of the threads 110, 112 remain constant.
  • the male and female threads 110, 112 can comprise characteristics the same as or similar to those described in U.S. Patent No. 5,788,401, the entire contents of which are incorporated by reference herein.
  • the male and female threads 110, 1 12 have a crest, a root, a pressure flank and a clearance flank.
  • threads 1 10, 1 12 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.
  • 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.
  • the box end and pin end of the drill sting component can have shoulders tapered at about 0 to about 15 degrees.
  • 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.
  • the critical pin section thickness, or the target material thickness under the pin thread can be used as an indicator of ultimate tensile strength and the stress amplification resulting from cutting the thread.
  • the critical pin section thickness can be from about 40% to about 50% of wall thickness; and more particularly about 44%, about 45%, about 46% or about 47% ofthe wall thickness.
  • the critical box shoulder stiffness can contribute torsion strength and can be exponentially sensitive to shoulder thickness.
  • 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% ofthe tubing stiffness.
  • the configuration of the male and female threads 110, 112 can differ from the forgoing description.
  • 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.
  • the box end and pin end can have shoulders tapered at about 5 to 20 degrees.
  • the flank angle can be characterized by a flank angle radial load expansion which describes the radial load created by the load flank angle that must be absorbed in the joint.
  • values of flank angle radial load expansion can be bounded by flank angles that cause excessive thread stress.
  • Radial loads can be defined as the percentage of axial load applied to the thread flank or to the joint determined by the flank angle. Specifically, the radial load created is equal to the axial load multiplied by the tangent of the flank angle.
  • positive values of radial load can cause unwanted expansion while negative values can provide beneficial contraction. Contraction is beneficial because it can reduce overall or Von Mises total stress levels, and it can increase the contract pressure between mating threads which increases friction and the torsion load transferred to the joint.
  • flank angle radial load expansion can be from about -18% to about -36%; more particularly, from about -18% to about -36%; and even more particularly, about -27%.
  • the male thread 110 can begin proximate a leading edge 140 of the pin end 104.
  • Figure 1 -3 illustrate that the male thread 110 can be offset a distance (shown has a linear distance 116) from the leading edge 140 of the pin end 104.
  • 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.
  • 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.
  • the offset distance 1 16 may vary as desired, and can particularly be different based on the size of the drill string component 102, configuration of the thread 1 10, or based on other factors. In at least one implementation, the offset distance 1 16 is between about one-half and about twice the width 1 18 of the male thread 110. Alternatively, the offset distance 1 16 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 leading edge 140 of the pin end 104.
  • female thread 112 can begin proximate a leading edge 120 of the box end 108.
  • Figures 1-4 illustrate that the female thread 112 can be offset a distance (shown has a linear distance 122) from the leading edge 120 of the box end 108.
  • 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.
  • the offset distance 122 is between about one- half and about twice the width 124 of the female thread 112.
  • the offset distance 122 may be greater or lesser.
  • the offset distance 122 is zero such that the female thread 112 begins at the leading edge 120 of the box end 108.
  • the offset distance 116 can be equal to the offset distance 122 as shown in Figures 1-4. In alternative implementations, the offset distance 122 may be greater or smaller than the offset distance 116. In any event, as the leading edge 140 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.
  • the male and female threads 110, 112 can be helically disposed relative to the respective pin and box ends 104, 108.
  • 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.
  • the threads may therefore rotate relative to each other and fit within gaps between corresponding threads.
  • the male thread 110 generally winds around pin end 104 at an angle 128, which can also be measured relative to the leading edge 140 of the pin end 104.
  • One or more implementations of the present invention comprise drill string components having a plurality of threads.
  • the drill string component comprises at least two threads having respective thread starts that are, optionally, evenly spaced about the leading end of the drill string component.
  • use of multiple threads can increase the thread load flank bearing surface area and can result in a greater overall load efficiency when pin and box components are joined together.
  • use of two threads doubles the thread bearing area as compared to a single thread when all other thread characteristics are held constant.
  • use of multiple threads can also increase the thread flank-to- thread root interface material and, correspondingly, the fatigue strength of the drill component.
  • the thread flank-to- thread root interface is the location of maximum stress and for fatigue failure crack initiation in drill string component j oints. It follows that, all other things held constant, use of multiple threads can increase the fatigue strength of the drill component since the available material fatigue strength is reduced by the mean load as illustrated by a standard Modified Goodman Fatigue Diagram.
  • use of multiple threads spaced equally about the respective leading ends of drill string components can increase the load capacity of drill string components placed in mating contact by creating a symmetrical load response about the central axis of the component.
  • the thread lead angle can increase as the thread pitch decreases and the number of threads is increased. Increasing the thread lead angle past an optimal angle can decrease the break-out torque requirement such that mating drill string components could disassemble in use.
  • individual thread width and, correspondingly, load shear area can decrease as the number of threads on a given drill component increase, ultimately leading to thread shear overload failure.
  • a number of threads that increases the load efficiency, load capacity and fatigue strength of the drill string component while maintaining acceptable thread lead angles and shear area for a drill string component of given dimensions can be determined to be the maximum number of threads possible where the thread width is not less than the thread height.
  • this disclosure provides for drill string components having at least two threads, and, preferably from about two to about four threads, operable to increase the load efficiency, load capacity and fatigue strength of the drill string components while maintaining acceptable thread lead angles and shear area over
  • At least two male threads 1 10 can begin proximate to a leading edge 140 of pin end 104.
  • the at least two male threads can be spaced equally about a leading edge 140 of pin end 104.
  • a pin end has two male threads having thread starts spaced about 180 degrees apart and proximate to a leading edge 140 of pin end 104.
  • a pin end has two male threads having thread starts spaced about 180 degrees apart and proximate to a leading edge 140 of pin end 104.
  • At least two female threads 112 can begin proximate to a leading edge 120 of box end 108.
  • the at least two female threads can be spaced equally about a leading edge 120 of box end 108.
  • a box end 108 has two female threads 112 having thread starts spaced about 180 degrees apart and proximate to a leading edge 120 of box end 108.
  • 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 edge 120 of box end 108.
  • At least two male threads 110 and at least two female threads 112 can be helically disposed relative to the respective pin and box ends 104, 108.
  • each of the male threads 110 and each of the female threads 112 can comprise a plurality of helical turns extending along the respective drill string component 102, 106.
  • Each of the male threads 110 and each of the female threads 112 can each comprise leading ends oriented at an acute angle relative to and equally spaced about the central axis of the respective drill string component 102, 106.
  • the threads may therefore rotate relative to each other and fit within gaps between corresponding threads and eventually form a drill string joint.
  • a drill string joint is formed having increased load efficiency, load capacity, and fatigue strength while maintaining acceptable thread lead angles and shear area for a given diameter drill string component.
  • One or more implementations of the present invention comprise drill string components that substantially 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.
  • 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.
  • material typically lost to overall joint and thread taper is conserved by providing drill string components having at least one thread comprising a thread pitch that varies 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 thereby selectively enabling an axial progressive fit.
  • the thread pitch can increase uniformly from the first value over at least the first turn to a final value over at least the final turn of the plurality of helical turns.
  • the thread pitch can increase non-uniformly from the first value to a final value over the full axial length of the plurality of helical turns.
  • the thread pitch can increase from the first value to a final value across a portion of the axial length of the plurality of helical turns and can remain constant thereafter.
  • the at least one thread can have a pitch that varies from about 2.0 to 5.0 threads/inch, preferably from about 3 to about 4 threads/inch and, most preferably, from about 3 to about 3.5 threads/inch.
  • the thread can have a varying pitch over at least one turn and, preferably, two turns of the thread.
  • the thread can have a pitch that varies from the leading end to the trailing end of the thread.
  • material typically lost to overall joint and thread taper is conserved by providing drill string components having at least one thread comprising a thread pitch that is constant when measured from at least one given thread feature but whose width can vary 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 thereby selectively enabling an axial progressive fit.
  • the thread width can increase uniformly from the first value over at least the first turn to a final value over at least the final turn of the plurality of helical turns.
  • the thread width can increase non-uniformly from the first value to a final value over the full axial length of the plurality of helical turns.
  • the thread pitch can increase from the first value to a final value across a portion of the axial length of the plurality of helical turns and can remain constant thereafter.
  • the thread load flank can be held at a constant pitch while the lead flank increases.
  • the thread lead flank can be held at a constant pitch while the pitch of the load flank increases.
  • the mid-point of the thread can have a constant pitch while both flanks have a varying pitch.
  • the varying pitch of the load flank can be different from the varying pitch of the lead flank.
  • 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.
  • a 2 tpi thread having a full width of 1/4" proximate the trailing end can have a reduced width of about 1/8" at the leading end.
  • 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.
  • material typically lost to overall joint and thread taper is conserved by providing drill string components having at least one thread comprising a root that circumscribes a cylindrical surface extending over the full axial length of the plurality of helical turns of the thread and a crest that circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof, thereby selectively enabling a radial progressive fit.
  • the generatrix of the frusta-conical surface is a straight line having an angle relative to the central axis of the hollow body.
  • the crest circumscribes a frusta-conical surface over the full axial length of the plurality of helical turns.
  • the at least one thread can have a frusta-conical crest over at least a portion of the axial length of the at least one thread with the generatrix of the frusta-cone having an angle of about 0.75 to 1.6 degrees while the at least one thread can have cylindrical roots.
  • the crest circumscribes a frusta-conical surface extending the axial length of at least one turn of the thread and, preferably at least two turns of the thread.
  • the axial length can be substantially the full axial length of the thread.
  • material typically lost to overall joint and thread taper is conserved by providing drill string components having both at least one thread comprising a thread pitch that varies 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, and further comprising a thread root that circumscribes a cylindrical surface extending over the full axial length of the plurality of helical turns and a thread crest that circumscribes a frusta-conical surface extending over at least a portion of the axial length of the plurality of helical turns thereof thereby selectively enabling both an axial progressive fit and a radial progressive fit.
  • At least one male thread 110 can begin proximate to a leading edge 140 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.
  • the at least one male thread can have a pitch that increases from a first value proximate the leading edge 140 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.
  • the at least one male thread can have a pitch that increases from a first value proximate the leading edge over the entire portion of the axial length of the plurality of helical turns thereof to a final value.
  • the pitch can increase uniformly or non-uniformly across the axial length of the at least one male thread 1 10.
  • a pin end has two male threads having a pitch that increases from the leading edge of pin end 104 to a final value at a desired point along the axial length of the thread, such point being measured from the pin end 104.
  • At least one female thread 112 can begin proximate to a leading edge 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.
  • the at least one female thread can have a pitch that increases from a first value proximate the leading edge 120 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.
  • the at least one female thread can have a pitch that increases from a first value proximate the leading edge 120 over the entire portion of the axial length of the plurality of helical turns thereof to a final value.
  • the pitch can increase uniformly or non-uniformly across the axial length of the at least one female thread 112.
  • a pin end has two female threads having a pitch that increases from the leading edge 120 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 box end 108.
  • 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.
  • 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 1 10 and the at least one female thread 112 can each comprise leading ends oriented at an acute angle relative to and spaced about the central axis of the respective drill string component 102, 106.
  • 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 axial direction is selectively created between the respective pin and box ends 104, 108 as the pitch 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.
  • At least one male thread 110 can begin proximate to a leading edge 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.
  • the at least one male thread can have a thread width that increases from a percentage of the full thread width proximate the leading edge 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.
  • the at least one male thread can have a thread width that increases from a percentage of the full thread width proximate the leading edge over the entire portion of the axial length of the plurality of helical turns thereof to the full thread width.
  • the thread width can increase uniformly or non-uniformly across the axial length of the at least one male thread 1 10.
  • 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 edge of pin end 104 to the full thread width at a desired point along the axial length of the thread.
  • At least one female thread 112 can begin proximate to a leading edge 142 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 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.
  • the at least one female thread can have a thread width that increases from a percentage of the full thread width proximate the leading edge 142 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 female thread 112 and be held constant thereafter.
  • the at least one female thread can have a thread width that increases from a percentage of the full thread width proximate the leading edge 142 over the entire portion of the axial length of the plurality of helical turns thereof to the full thread width.
  • the thread width can increase uniformly or non-uniformly across the ax ial length of the at least one female thread 112.
  • a box end has two female threads where at least one female 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 edge 142 of box end 108 to the full thread width at a desired point along the axial length of the thread.
  • 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.
  • 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 and spaced about the central axis of the respective drill string component 102, 106.
  • 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 axial direction is selectively created between the respective pin and box ends 104, 108 as the width of at least one of the at least one male thread 110 and the at least one female thread 112 increases while at least one feature of both the at least one male thread 110 and the at least one female thread 112 has a constant pitch across the axial length of the respective thread. Accordingly, in one or more embodiments, a drill string joint is formed having optimal material cross sections for maximum load capacity.
  • At least one male thread 1 10 can begin proximate to a leading edge 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.
  • the at least one male thread 110 can have a thread root that circumscribes a cylindrical surface over the entire axial length of the plurality of helical turns.
  • the at least one male thread 110 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 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 at least one male thread 110 and be held constant thereafter.
  • the generatrix of the frusta-conical surface is a straight line passing through the thread crests that lies at an angle relative to the central axis extending through the hollow body.
  • the at least one male thread 110 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge extending over the full axial length of the plurality of helical turns thereof to a final diameter.
  • a pin end has at least one male thread having a thread crest that circumscribes a cylinder and a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge extending over at desired portion of the axial length of the plurality of helical turns thereof to a final diameter at a desired point on the at least one male thread 110 and held constant thereafter.
  • At least one female thread 112 can begin proximate to a leading edge 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.
  • 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.
  • the at least one female thread 112 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 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 at least one female thread 112 and be held constant thereafter.
  • the generatrix of the frusta-conical surface is a straight line passing through the thread crests that lies at an angle relative to the central axis extending through the hollow body.
  • the at least one female thread 112 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 120 extending over the full axial length of the plurality of helical turns thereof to a final diameter.
  • a box end 108 has at least one female thread 112 having a thread crest that circumscribes a cylinder and a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 120 extending over at desired portion of the axial length of the plural ity of helical turns thereof to a final diameter at a desired point on the at least one female thread 112 and held constant thereafter.
  • 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.
  • 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 1 10 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.
  • both the at least one male thread 110 and the at least one female thread 1 12 can have a thread root that circumscribes a cylindrical surface over the entire axial length of the plurality of helical turns.
  • 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 leading edge 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 at least one female thread 1 12 and be held constant thereafter.
  • 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 1 10 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.
  • At least one male thread 110 can begin proximate to a leading edge 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.
  • the at least one male thread can have at least one of a pitch and a width that increases from a first value proximate the leading edge 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.
  • the at least one male thread 1 10 can have a thread root that circumscribes a cylindrical surface over the entire axial length of the plurality of helical turns.
  • the at least one male thread 1 10 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 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 at least one male thread 1 10 and be held constant thereafter.
  • the generatrix of the frusta-conical surface is a straight line passing through the thread crests that lies at an angle relative to the central axis extending through the hollow body.
  • the at least one male thread 1 10 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge extending over the full axial length of the plurality of helical turns thereof to a final diameter.
  • a pin end has at least one male thread having a thread crest that circumscribes a cylinder and a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge extending over at desired portion of the axial length of the plurality of helical turns thereof to a final diameter at a desired point on the at least one male thread 1 10 and held constant thereafter.
  • the at least one male thread 110 also has at least one of a pitch and a width that increases from the leading edge of pin end 104 to a final value at a desired point along the axial length of the thread, such point being measured from the pin end 104.
  • At least one female thread 1 2 can begin proximate to a leading edge 120 of box end 108.
  • the at least one female thread 1 12 can comprise a plurality of helical turns extending along the respective length of box end 108.
  • the at least one male thread can have at least one of a pitch and a width that increases from a first value proximate the leading edge 120 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.
  • 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.
  • the at least one female thread 1 12 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 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 at least one female thread 112 and be held constant thereafter.
  • the generatrix of the frusta-conical surface is a straight line passing through the thread crests that lies at an angle relative to the central axis extending through the hollow body.
  • the at least one female thread 112 can have a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 120 extending over the full axial length of the plurality of helical turns thereof to a final diameter.
  • a box end 108 has at least one female thread 1 12 having a thread crest that circumscribes a cylinder and a thread crest that circumscribes a frusta-conical surface from a first diameter proximate the leading edge 120 extending over at desired portion of the axial length of the plurality of helical turns thereof to a final diameter at a desired point on the at least one female thread 1 12 and held constant thereafter.
  • the at least one female thread 112 also has at least one of a pitch and a width that increases from the leading edge 120 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 box end 108.
  • 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.
  • the at least one male thread 1 10 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.
  • both the at least one male thread 1 10 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.
  • At least one of the at least one male thread 1 10 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 edge 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.
  • 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 1 12 increases.
  • a drill string joint is formed having optimal material cross sections for maximum load capacity.
  • 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 ful l thread depth and/or width.
  • the male thread 110 can comprise a thread width 118 and the female thread 112 can comprise a thread width 124 as previously mentioned.
  • thread width can comprise the linear distance between edges of a thread crest as measured along a line normal to the edges of the thread crest.
  • the thread widths 118, 124 can vary depending upon the configuration of the threads 110, 112. In one or more implementations, the thread width 1 18 of the male thread 110 is equal to the thread width 124 of the female thread 112. In alternative implementations, the thread width 118 of the male thread 110 is larger or smaller than the thread width 124 of the female thread 112.
  • the male thread 1 10 can comprise a thread depth 130 and the female thread 112 can comprise a thread depth 132.
  • thread depth can comprise the linear distance from the surface from which the thread extends (i.e., the outer surface of the pin end 104 or inner surface of the box end 108) to most radially distal point on the thread crest as measured along a line normal to the surface from which the thread extends.
  • the thread depths 130, 132 can vary depending upon the configuration of the threads 1 10, 1 12 and/or the size of the drill string components 102, 106.
  • the thread depth 130 of the male thread 110 is equal to the thread depth 132 of the female thread 112.
  • the thread depth 130 of the male thread 110 is larger or smaller than the thread depth 132 of the female thread 112.
  • the thread width 118, 124 of each thread 110, 112 is greater than the thread depth 130, 132 of each thread 110, 112.
  • the thread width 118, 124 of each thread 110, 112 is at least two times the thread depth 130, 132 of each thread 110, 112.
  • the thread width 118, 124 of each thread 110, 112 is approximately equal to or less than the thread depth 130, 132 of each thread 110, 1 12.
  • both the male and female threads 110, 112 can comprise a leading end or thread start.
  • Figures 1-4 illustrate that the male thread 110 can comprise a thread start or leading end 114.
  • the female thread 112 can comprise a thread start or leading end 120.
  • the leading end 114 of the male thread 110 can comprise a planar surface that extends from the outer surface of the pin end 104.
  • the leading end 1 14 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.
  • the leading end 114 extends in a direction normal to the outer surface of the pin end 104.
  • the leading end 114 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).
  • the leading end 114 can comprise a surface that curves along one or more of its height or width.
  • leading end 1 14 of the male thread 110 can extend the full thread width 118 of the male thread 110.
  • leading end 1 14 of the male thread 1 10 can extend from a leading edge to a trailing edge 138 of the male thread 1 10.
  • planar surface forming the leading end 114 can span the entire thread width 1 18 of the male thread 110.
  • the leading end 114 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 114 of the male thread 110 can be equal to the thread depth 130.
  • the planar surface forming the leading end 1 14 can span the entire thread depth 130 of the male thread 110.
  • the leading end 114 or thread start can comprise an abrupt transition to the full depth and/or width of the male thread 1 10.
  • the male thread 110 does not comprise a tail end that tapers gradually to the full depth of the male thread 1 10.
  • the leading end 120 of the female thread 1 12 can comprise a planar surface that extends from the inner surface of the box end 108.
  • the leading end 120 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.
  • the leading end 120 extends in a direction normal to the inner and/or outer surface of the box end 108.
  • the leading end 120 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).
  • the leading end 120 can comprise a surface that curves along one or more of its height or width.
  • the leading end 114 and the leading end 120 can comprise cooperating curved surfaces.
  • leading end 120 of the female thread 1 12 can extend the full thread width 124 of the female thread 1 12.
  • leading end 120 of the female thread 112 can extend from a leading edge 144 to a trailing edge 144 of the female thread 1 12.
  • planar surface forming the leading end 120 can span the entire thread width 124 of the female thread 112.
  • the leading end 120 of the female thread 1 12 can extend the full thread depth 132 of the female thread 112. In other words, a height of the leading end 120 of the female thread 112 can be equal to the thread depth 132.
  • the planar surface forming the leading end 120 can span the entire thread depth 132 of the female thread 112.
  • the leading end 120 or thread start can comprise an abrupt transition to the full depth and/or width of the female thread 1 12.
  • the female thread 1 12 does not comprise a tail end that tapers gradually to the full depth of the female thread 112.
  • leading end or thread start 120 of the female thread 112 is illustrated as being formed by material that remains after machining or another process used to form the threads.
  • the leading end or thread start 120 may be, relative to the interior surface of the box end 108, embossed rather than recessed.
  • the leading end 114 of the male thread 110 can have a size and/or shape equal to the leading end 120 of the female thread 112.
  • the size and/or shape of the leading end 114 of the male thread 110 can differ from the size and/or shape of the leading end 120 of the female thread 112.
  • the leading end 114 of the male thread 110 can be larger than the leading end 120 of the female thread 112.
  • the leading ends 114, 120 of the male and female threads 1 10, 112 can each have an off-axis orientation.
  • the planar surfaces of the leading ends 114, 120 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.
  • the planar surface of the leading end 114 of the male thread 110 can face an adjacent turn of the male thread 110.
  • planar surface of the leading end 120 of the female thread 112 can face an adjacent turn of the female thread 1 12.
  • the planar surface of the leading end 114 of the male thread 110 can extend at an angle relative to the leading edge 140 or the central axis 126 of the pin end 104.
  • the planar surface of the leading end 114 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 leading edge 114.
  • the illustrated orientation and existence of a planar surface of the leading end 114 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.
  • the leading end 120 of the female thread 112 can extend at an angle relative to the leading edge 120 or the central axis 126 of the pin end 104.
  • the planar surface of the leading end 120 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 leading edge 120.
  • the angles 146, 148 can be varied in accordance with the present disclosure and comprise any number of different angles. The angles 146, 148 may be varied based on other characteristics of the threads 110, 112, or based on a value that is independent of thread characteristics. In one or more implementations, angle 146 is equal to angle 148. In alternative implementations, the angle 146 can differ from angle 148.
  • angles 146, 148 are each acute angles.
  • 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.
  • the angles 146, 148 can comprise about 45 degrees.
  • a leading end 1 14 of the male thread 110 can mate with the leading end 120 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.
  • a leading ends 114, 120 or thread start face can thus be provided.
  • the leading ends 114, 120 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.
  • the leading ends 114, 120 or thread starts may have corresponding surfaces that, when mated together, create a sliding interface in a near thread-coupled condition.
  • the leading ends 114, 120 are each oriented at acute angles, the leading ends 114, 120 or thread start faces may engage each other and cooperatively draw threads into a fully thread-coupled condition.
  • the leading ends 1 14, 120 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.
  • thread start tails are eliminated, there are few— if any— limits on rotational positions for mating.
  • the pin and box ends 104, 108 can have the full circumference available for mating, with no jamming prone positions.
  • a thread 1 10 may be formed with a tail using conventional machining processes.
  • the tail may be least partially removed to form the leading end 114.
  • 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 1 10 may have a leading end 114 aligned with the axis 126. If, however, more of the thread 1 10 beyond just the tail is removed, leading end 114 may be offset relative to the axis 126.
  • the tail may be removed by a separate machining process.
  • a thread start face may be formed in the absence of creation and/or subsequent removal of a tail-type thread start.
  • the thread is formed using electrical discharge machining. Electrical discharge machining can allow for the formation of the leading end 1 14 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 1 14, 120 of the threads 110, 112.
  • male and female threads 110, 112 can have relative depths such that the male thread crest maintains a radially spaced relationship with the mating female root while the female thread crest meets the male thread root.
  • the male and female threads 1 10, 112 can have relative depths such that the female thread crest maintains a radially spaced relationship with the mating male thread root while the female thread crest meets the male thread root.
  • male and female threads 110, 1 12 can have relative depths such that the male thread crest maintains a radially spaced relationship with the mating female root and the female thread crest maintains a radially spaced relationship with the mating male thread root.
  • the radial spacing between mating thread crests and roots can be from about .001 to about .010 inches, more particularly from about .003 to about .007 inches and, most preferably about .005 inches.
  • the radial spacing between mating thread crests can be from about 1% to about 5%, more particularly from about 1.5% to about 3%, and most particularly from about 2% to about 2.5% of the wall thickness of a hollow body.
  • 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, as shown by Figures 1-4, 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 ofthe outer diameter 150.
  • 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.
  • the drill string components 102, 106 can comprise any number of different types of tools.
  • 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 in relation to Figures 1-4.
  • 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 114, 120 having increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading as described above in relation to Figures 1- 4.
  • Figure 5 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 120 having increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading as described above in relation to Figures 1-4.
  • 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 120 having increased load efficiency and load capacity, and that can also be resistant to wear, jamming and cross-threading as described above in relation to Figures 1-4.
  • the drill string components 102, 106 can comprise casings, reamers, core lifters, or other drill string components.
  • 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.
  • 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
  • the drilling system 300 may comprise a drill rig 301 that may rotate and/or push the drill bit 207, the drill rods 204 and/or other portions of the drill string 302 into the formation 304.
  • the drill rig 301 may comprise a driving mechanism, for example, a rotary drill head 306, a sled assembly 308, and a mast 310.
  • the drill head 306 may be coupled to the drill string 302, and can rotate the drill bit 207, the drill rods 204 and/or other portions of the drill string 302. If desired, the rotary drill head 306 may be configured to vary the speed and/or direction that it rotates these components.
  • the sled assembly 308 can move relative to the mast 310.
  • the sled assembly 308 may provide a force against the rotary drill head 306, which may push the drill bit 207, the drill rods 204 and/or other portions of the drill string 302 further into the formation 304, for example, while they are being rotated.
  • the drill rig 301 does not require a rotary drill head, a sled assembly, a slide frame or a drive assembly and that the drill rig 301 may comprise other suitable components. It will also be appreciated that the drilling system 300 does not require a drill rig and that the drilling system 300 may comprise other suitable components that may rotate and/or push the drill bit 207, the drill rods 204 and/or other portions of the drill string 302 into the formation 304. For example, sonic, percussive, or down hole motors may be used.
  • the drilling system 300 can further comprise a drill rod drill rod clamping device 312.
  • 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.
  • 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. Patent 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.
  • leading ends 114, 120 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.
  • the drill rod clamping device 312 may release the drill 302.
  • the driving mechanism may advance the drill string 302 further into the formation to a greater desired depth. This process of grasping the drill string 302, disconnecting the driving mechanism, connecting an additional drill rod 204, releasing the grasp, and advancing the drill string 302 to a greater depth may be repeatedly performed to drill deeper and deeper into the formation.
  • Figures 1-Y 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.
  • 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 Figures 1 through Y.
  • 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 114 of a male thread 1 10 on the pin end 104 of the first drill string component 102 against a planar leading end 120 of a female thread 112 on the box end 108 of the second drill string component 106.
  • the planar leading end 114 of the male thread 1 10 can be oriented at an acute angle 146 relative to a central axis 26 of the first drill string component 102.
  • the planar leading end 120 of the female thread 1 12 can be oriented at an acute angle 148 relative to a central axis 26 of the second drill string component 106.
  • the method can further involve sliding the planar leading end 114 of the male thread 1 10 against and along the planar leading end 120 of the female thread 1 12 to guide the male thread 1 10 into a gap between turns of the female thread 112.
  • Sliding the planar leading end 1 14 of the male thread 110 against and along the planar leading end 120 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 1 14, 120 of the male and female threads 1 10, 1 12.
  • 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.
  • 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.
  • 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.
  • the tail has been eliminated to virtually eliminate wedging prone geometry.
  • 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.
  • a joint taper 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.
  • 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 difficultly 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Drilling Tools (AREA)

Abstract

Selon certains modes de réalisation, cette invention concerne des composants de train de tiges de forage présentant au moins un filetage s'étendant autour d'un corps. Une extrémité de tête du filetage peut présenter une configuration telle que sa rigidité et sa résistance à la déformation du filetage sont accrues. En particulier, l'extrémité de tête du filetage peut présenter une transition abrupte vers une profondeur de passe maximale qui aide à réduire ou à éliminer la déformation du filetage et permet une orientation en angle par rapport à l'axe du composant de train de tiges de forage. De plus, le filetage peut présenter au moins une caractéristique parmi une largeur de filet variable et un pas de vis variable destinées assurer un ajustement axial progressif. Le filetage peut en outre présenter un fond de filet cylindrique et un sommet de filet qui circonscrit un tronc de cône au-dessus d'au moins une partie de la longueur axiale des filets, afin d'assurer un ajustement radial progressif.
EP13837637.1A 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples Active EP2895679B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20180399.6A EP3767068A1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201261700401P 2012-09-13 2012-09-13
PCT/US2013/059716 WO2014043505A1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP20180399.6A Division EP3767068A1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples
EP20180399.6A Division-Into EP3767068A1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples

Publications (3)

Publication Number Publication Date
EP2895679A1 true EP2895679A1 (fr) 2015-07-22
EP2895679A4 EP2895679A4 (fr) 2016-06-01
EP2895679B1 EP2895679B1 (fr) 2020-08-05

Family

ID=50278717

Family Applications (2)

Application Number Title Priority Date Filing Date
EP13837637.1A Active EP2895679B1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples
EP20180399.6A Pending EP3767068A1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP20180399.6A Pending EP3767068A1 (fr) 2012-09-13 2013-09-13 Composants de train de tiges de forage présentant des joints à filetages multiples

Country Status (11)

Country Link
EP (2) EP2895679B1 (fr)
CN (1) CN104769210B (fr)
AU (3) AU2013315186B2 (fr)
BR (1) BR112015005576B1 (fr)
CA (2) CA2973262C (fr)
CL (1) CL2015000632A1 (fr)
IN (1) IN2015DN02778A (fr)
PE (2) PE20200332A1 (fr)
RU (3) RU2607560C2 (fr)
WO (1) WO2014043505A1 (fr)
ZA (2) ZA201502415B (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9850723B2 (en) 2011-01-26 2017-12-26 Bly Ip Inc. Drill string components having multiple-thread joints
US9810029B2 (en) 2011-01-26 2017-11-07 Bly Ip Inc. Drill string components resistant to jamming
US10557316B2 (en) 2011-01-26 2020-02-11 Bly Ip Inc. Drill string components having multiple-thread joints
ES2959488T3 (es) * 2014-07-18 2024-02-26 Longyear Tm Inc Varilla de perforación que tiene partes que sobresalen internamente
CN106168121B (zh) * 2016-07-28 2018-06-29 天津钢管集团股份有限公司 应用于油套管的管端镦粗的整体式螺纹接头结构
WO2021035301A1 (fr) * 2019-08-30 2021-03-04 Reflex Instruments Asia Pacific Pty Ltd Formation de filet pour l'accouplement d'outils de fond de trou
WO2021255494A1 (fr) * 2020-06-15 2021-12-23 Epiroc Canada Inc. Tige de forage de ligne terrestre

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3989284A (en) * 1975-04-23 1976-11-02 Hydril Company Tubular connection
US4688832A (en) * 1984-08-13 1987-08-25 Hydril Company Well pipe joint
US4956888A (en) * 1985-05-28 1990-09-18 Green William P Formation of fasteners and connections with variable pitch threads
US4842464A (en) * 1985-05-28 1989-06-27 Mark Hattan Equalization of load in threaded connections
US4707001A (en) * 1986-06-20 1987-11-17 Seal-Tech, Inc. Liner connection
US5190426A (en) * 1992-03-02 1993-03-02 Illinois Tool Works Inc. Concrete fastener
US6485061B1 (en) * 1996-05-07 2002-11-26 Frank's Casing Crew And Rental Tools, Inc. Threaded tool joint for connecting large diameter tubulars
US5788401A (en) 1996-12-24 1998-08-04 Boart Longyear International Holdings, Inc. Rod joint
US6158785A (en) * 1998-08-06 2000-12-12 Hydril Company Multi-start wedge thread for tubular connection
FR2821916B1 (fr) * 2001-03-09 2003-05-16 Vallourec Mannesmann Oil & Gas Element filete pour joint filete tubulaire resistant a la fatigue
US6682101B2 (en) 2002-03-06 2004-01-27 Beverly Watts Ramos Wedgethread pipe connection
GB0215668D0 (en) * 2002-07-06 2002-08-14 Weatherford Lamb Coupling tubulars
US8186925B2 (en) 2006-04-11 2012-05-29 Longyear Tm, Inc. Drill rod handler
JP5100755B2 (ja) * 2007-10-03 2012-12-19 住友金属工業株式会社 鋼管用ねじ継手
US8136846B2 (en) * 2008-11-17 2012-03-20 Gandy Technologies Corporation Cylindrical tapered thread form for tubular connections
CN201358732Y (zh) * 2008-11-26 2009-12-09 上海海隆石油管材研究所 一种低应力高抗扭矩双头螺纹钻杆接头
FR2952993B1 (fr) * 2009-11-20 2011-12-16 Vallourec Mannesmann Oil & Gas Joint filete
FR2953272B1 (fr) * 2009-11-30 2011-12-16 Vallourec Mannesmann Oil & Gas Joint filete
US8882157B2 (en) * 2010-09-27 2014-11-11 United States Steel Corporation Connecting oil country tubular goods
US9810029B2 (en) * 2011-01-26 2017-11-07 Bly Ip Inc. Drill string components resistant to jamming

Also Published As

Publication number Publication date
AU2013315186A1 (en) 2015-04-09
AU2017201366B2 (en) 2018-12-06
AU2019201562A1 (en) 2019-03-28
RU2015113367A (ru) 2016-11-10
ZA201502415B (en) 2019-07-31
PE20150586A1 (es) 2015-05-06
AU2013315186B2 (en) 2016-12-01
BR112015005576B1 (pt) 2021-03-02
AU2017201366A1 (en) 2017-03-16
WO2014043505A1 (fr) 2014-03-20
CA2973262C (fr) 2020-06-30
AU2017201366C1 (en) 2019-07-25
PE20200332A1 (es) 2020-02-13
IN2015DN02778A (fr) 2015-09-04
EP3767068A1 (fr) 2021-01-20
RU2723056C2 (ru) 2020-06-08
EP2895679B1 (fr) 2020-08-05
CA2973262A1 (fr) 2014-03-20
AU2019201562B2 (en) 2020-10-01
EP2895679A4 (fr) 2016-06-01
RU2020117937A (ru) 2021-12-01
BR112015005576A2 (pt) 2017-08-08
RU2016149672A3 (fr) 2020-04-02
CN104769210A (zh) 2015-07-08
RU2607560C2 (ru) 2017-01-10
CA2884798A1 (fr) 2014-03-20
ZA201806700B (en) 2020-01-29
CA2884798C (fr) 2017-08-15
CN104769210B (zh) 2018-09-21
RU2016149672A (ru) 2018-11-02
CL2015000632A1 (es) 2015-07-03

Similar Documents

Publication Publication Date Title
US10934786B2 (en) Drill string components resistant to jamming
AU2019201562B2 (en) Drill string components having multiple-thread joints
US11898404B2 (en) Drill string components having multiple-thread joints
US20130220636A1 (en) Drill string components resistant to jamming
WO2014099902A1 (fr) Composants de train de tiges de forage résistants au calage
US10557316B2 (en) Drill string components having multiple-thread joints
NZ614134B2 (en) Drill string components resistant to jamming

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150406

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
RA4 Supplementary search report drawn up and despatched (corrected)

Effective date: 20160503

RIC1 Information provided on ipc code assigned before grant

Ipc: E21B 17/042 20060101AFI20160427BHEP

Ipc: E21B 19/16 20060101ALI20160427BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20170912

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BLY IP INC.

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20200406

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1298931

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602013071408

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: FI

Ref legal event code: FGE

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200805

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1298931

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200805

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201105

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201106

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201105

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201207

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201205

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602013071408

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200913

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

26N No opposition filed

Effective date: 20210507

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20201105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210401

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200930

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200913

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201205

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200805

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230523

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20230912

Year of fee payment: 11

Ref country code: FI

Payment date: 20230830

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20230908

Year of fee payment: 11

Ref country code: FR

Payment date: 20230807

Year of fee payment: 11