RU2723056C2 - Components of drill string, having multi-threaded connections - Google Patents

Abstract

FIELD: components and systems for drilling.SUBSTANCE: threaded component of a drill string comprises a hollow body having a first end, an opposite second end and a central axis, passing through the hollow body and at least two threads located at the first end of the hollow body. Each of said at least two threads comprises a row of helical turns extending along the first end of the hollow body. Each of said at least two threads has thread recess, thread top, thread pitch and thread width. Each of said at least two threads has negative angle of side pressure side inclination. At least one parameter of thread width and thread pitch of said at least two threads increases from first value near front end at least on part of axial length of said row of its helical coils to final value in desired point on said at least one thread.EFFECT: technical result is to provide reduced wear, jamming and spinning screwing, efficient use of available material, increased allowable load during drilling and reliability of connection.33 cl, 6 dwg, 2 tbl

Description

0001] This application claims priority to Provisional Patent Application No. 61/700401, filed September 13, 2012, entitled "DRILL STRING COMPONENTS HAVING MULTIPLE THREAD JOINTS", the entire contents of which are incorporated herein by reference.

State of the art

Technical field

[0002] Embodiments of the present invention relate generally to components and to drilling systems. In particular, embodiments of the present invention relate to drilling components having increased strength as well as resistance to seizing, non-threading and jamming.

Relevant technology

[0003] Threaded connections have been well known since time immemorial, and threads provide a significant advantage in that the screw structure of the thread can convert rotational motion and force into linear motion and force. Threads are present on many types of elements and can be used in unlimited applications and industries. For example, threads are an integral part of screws, bolts and other types of mechanical fasteners that can engage with the surface (for example, in the case of a screw) or used together with a nut (for example, in the case of a bolt) to fasten several elements together, to apply force to an element or for any other suitable purpose. Threading is also common in almost any industry in which the elements are mechanically held together. For example, in the field of pipeline engineering, pipes are used to deliver liquids or gases under pressure. Pipes may have threaded ends that mate with the corresponding threads of an adjacent pipe, plug, adapter, connector, or other structure. Threads can be used to create a tight seal to protect against fluid leakage at the junction.

[0004] Oilfield, exploration and other drilling technologies also make wide use of threads. For example, after a well has been dug, casing elements may be placed inside the well. Casing pipes generally have a fixed length, and several casing pipes are connected to each other in order to obtain a casing of a desired height. Casing pipes can be connected to each other using threads at their opposite ends. Just as drilling elements are used to create a well or to place objects inside a well, a drill rod or other similar device can be used. If the depth of the well is large enough, several drill rods can be connected to each other, which can be facilitated by the use of conjugated threads at opposite ends of the drill rod. Often, drill rods and casing are very large, and the mechanisms make great efforts to bond the rods or casing to each other.

[0005] Significant efforts have been made to standardize equipment in the oilfield, exploration and other drilling industries. In the case of drill rods, standards have been developed for both external and internal diameters and, in the case of threads, standards for multiple threads have been developed to enable different manufacturers to produce interchangeable parts. For example, typical standardization schemes include Unified Thread Standard (UTS), British Whitworth Standard (BSW), British Tapered Pipe Thread Standard (BSPT), National Tapered Pipe Thread Standard (NPT), metric screw threads according to International Standards Organization ( ISO), threads according to American Petroleum Institute (API) standards, as well as numerous other thread standardization schemes.

[0006] Although standardization has provided greater predictability and interchangeability when components from different manufacturers are sized, standardization has also reduced the number of innovations in the design of drilling components. In one example, both the outer and inner diameters of the drill rods were fixed by industry requirements. Accordingly, a portion of the wall thickness designed to mate threads made with the ability to transfer loads during drilling and withstand wear due to repeated screwing and unscrewing of drilling components must be balanced with the remaining material on the threaded parts of the components so that the components can withstand loads drilling and wear due to abrasion in relation to the drilled wall of the well and the resulting drill bit.

[0007] In another example, threads can be created using existing cross-sectional shapes - or thread shapes - and various combinations of stroke, pitch and number of thread starts. In particular, the stroke refers to the linear distance along the axis that is captured at full revolution. The step refers to the distance from the top of one thread to another, and the approach refers to the number of approaches or protrusions wound on the cylinder of a threaded fastener. A one-way connecting element is the most common and contains one protrusion wound on the body of the fastener. The two-way connecting element contains two protrusions wound on the body of the fastener. The number of thread turns per inch is also an element of the thread standard, but is directly related to the stroke, pitch and thread lead.

[0008] Although existing threads and thread shapes are suitable for a number of applications, continuous improvement is needed in other areas, such as applications with high torque, high power and / or high speed. In one case, existing threaded structures are essentially prone to seizing. In another case, existing threaded structures do not use effectively available material. In another embodiment of the invention, existing threaded structures reduce the permissible load of the mating components. In yet another case, existing threaded structures exhibit excessive wear.

[0009] Jamming is an incorrect interaction between a thread and a mating thread in such a way that when one thread is made, one thread partially passes under the other, thereby jamming in it. Jamming can be especially frequent if the threaded connectors are tapered. Alternatively, existing drilling component designs may have a limited allowable drilling load and an allowable fatigue load due to the material provided for the external thread or base material at the male end of the drilling component.

[0010] In some applications, for example, using drilling rigs, several drill rods, casing pipes and the like may be screwed. As more rods or casing pipes are added, the tightness due to jamming or screwing outside the thread may increase. Moreover, sufficient power (for example, when making up using the hydraulic power of a drilling rig) can destroy the connection of the rods. Core drill rods also often have large-pitch threads with wide, flat thread tops parallel to the mating peaks due to a mating fit with a tight fit or small clearance due to many drill rod joint designs. The combination of threaded shoots and flat parallel thread tops on tapered threads with a large pitch creates even greater potential for interaction when screwing non-threading, which otherwise might not be observed in other applications.

[0011] In tapered threads, the opposite ends of the male and female thread components may have different sizes. For example, a threaded component may taper and gradually increase in size as the distance from the end increases. To accommodate the increase in size, the internal thread may be larger at the end. The difference in size of the tapered threads also makes tapered threads particularly prone to seizing, which is also called non-threading. Non-threading in tapered or other threads can result in significant damage to threads and / or components that contain threads. Damage to threads may require replacing the threaded component, weakening the connection, lowering the tightness of the seal between the components, or have another effect, or include any combination of the above.

[0012] For example, thread runs with engagement on a thread run have vertices with a common cone. In the case of interfacing the components with the external and internal threads without rotation, the vertices on the run of the thread can seize together. In the case of rotation of the vertex on the run, the threads can also jam during insertion, based on the relatively coaxial installation of the runoffs. In particular, since the runaway of the thread is typically about half the circumference, and since the thread has a common cone, less than half the circumference of the respective components with external and internal threads provides an angular position for threads without jamming. Such positioning requirements can be particularly difficult to achieve in applications that use high feed and rotational forces to mate the respective components. For example, in the automated establishment of core rod connections in the drilling industry, equipment can operate with sufficient force so that jamming, jamming or screwing without thread occurs too often.

[0013] In addition, when connecting components with external and internal threads that are offset from the center (eccentric), the joints with engagement on the thread run may also be prone to not screwing, seizing and jamming. Accordingly, when components with an external and internal thread are inserted without rotation, the run can jam in the mating thread. During rotation, the run can also jam in the mating thread. Jamming can be reduced, but after the possibility of a threaded connection (for example, mating the end of the run in the hole adjacent to the mating run), jamming can still occur due to the missed possibility of a threaded connection and an axis offset. Displaced relative to the center of the thread can be made so that the middle of the top of the run on the component of the run has equal or corresponding geometry with respect to the top of the internal thread.

[0014] As discussed above, threaded fittings having threaded runs with engagement on the run of the thread may be particularly prone to seizing the thread, screwing off the thread, jamming, jamming of the connecting parts and the like. Such difficulties can be especially common in some industries, for example, in connection with the design of drill rods for core drilling. The thread entry provides the front end, or first end, of the external or internal thread and mates with the front end of the mating thread to make up the rod or other connection. If threads with engagement on the thread run-off stick, jam, screw in unscrewed threads and the like, it may be necessary to remove the rods from the drilling site and may require adjustments that require stopping drilling operations.

[0015] Furthermore, drill rods and casing pipes typically use tapered threads and tapered joints so that the diameters at the thread ends are smaller than the diameters at the ends of the threads. Tapered threads and joints reduce the amount of cross-sectional material available for transferring loads. Tapered threads and connections are also prone to problems with non-threading. Since the core rod may have a tapered thread, the run at the approach of the external thread may be smaller in diameter than the run at the approach of the internal thread. As a result, there may be an intermediate geometry at the approach of each thread for the transition from smooth to full thread profile. Since the thread approach and the intermediate geometry may have dimensions different from the dimensions of the internal thread, the intermediate geometry and the thread approach may mate incorrectly and wedge together.

[0016] If there is a sufficient cone on the run, the external thread approach may have some clearance between the internal thread approach, for example, when the geometry of the middle of the run corresponds to the geometry of the internal thread. However, the intermediate geometry of the thread approach may, nevertheless, incorrectly interact with the thread turns outside the thread lead, as a rule, at subsequent turns of the vertices of the conjugated threads, thereby also leading to jamming, non-threading, jamming and the like. Thus, the presence of runaway, as a rule, performs the function of a wedge mechanism with a conjugate runaway, thereby increasing the possibility and likelihood of jamming of the thread.

[0017] Limitations of threaded structures with engagement on a thread run are typically due to limitations of existing lathes. In particular, the threads are usually cut using machine tools for processing parts such as bodies of revolution, which can only gradually apply changes in the height or depth of the thread with rotation of the part. Accordingly, as a rule, threads are obtained that contain run-offs with geometry and run-offs identical or similar to other parts of the thread run-in. For example, among other things, traditional lathes are not capable of applying a sharp vertical or almost vertical transition from a smooth to full thread profile with rotation of the part during machining. A gradual change is also necessary to remove sharp, individual elements of the edges of the material obtained by the collision of a small angle of thread elevation, or the angle of elevation of the screw thread, with the material being cut.

[0018] Existing threaded structures do not necessarily efficiently use available material. As explained previously, the use of a common cavity and tapered thread leads to a loss in the cross-sectional area of the component, and a loss of cross-sectional material leads to a reduction in the allowable load and fatigue strength for this component. In another case, the use of single-threading provides ease of manufacture and ease of screwing and unscrewing. However, the use of single-threading limits the area of the supporting surface of the side under pressure, and accordingly, the load efficiency of the component. This practice also restricts the material at the junction of the side of the thread profile into the thread depression, the place of maximum stress and cracking causing fatigue failure, as well as the fatigue strength of the component.

[0019] In addition, existing threaded structures using single-threaded threads result in components that are essentially unbalanced when mating components are brought into contact. Not wanting to be bound by theory and / or modeling, when bringing drill string components having a single thread into the butt contact, the external thread is installed in a stretched state, and the internal thread is set in a compressed state. It follows that, since the load in the threaded connection goes to the first point of the mating contact, there is a higher proportion of the load accepted by the part of the mated thread closest to the first contact point on one side of the connection. This asymmetric dynamic load can create a load causing bending in the associated components of the drill string, and can reduce the allowable load.

[0020] Wear is the erosion or shift of the thread material from its original position on the thread surface due to the relative mechanical stresses of the mating threads. Existing threads can also be configured to fit tightly, for example, on the outer diameter of mating components. For example, the top of the external thread may be configured to create a radial interference in the cavity of the internal thread. As the threads are screwed up, an interference fit can serve as a significant source of thread wear, since it can significantly increase the pressure on the contact surface between the threads as they slip relative to each other. Ultimately, interference fit on threaded elements increases thread wear. Wear of the thread worsens the geometry of the thread, and therefore the permissible load or load efficiency of the component of the drill string.

[0021] Thus, the disadvantage of traditional threads can be reinforced by drilling components. In particular, joining drill string components may require joining with a high tensile load due to the length and weight of many drill strings. In addition, the joint will often need to withstand multiple screwing and unscrewing, as the same components of the drill string can be installed and removed from the drill string several times during drilling of the wellbore. Similarly, drill string components can be used several times over their service life. These problems are compounded by the fact that many sectors of the drilling industry, such as exploration drilling, require the use of thin-walled components of the drill string. This thin-walled construction of such drill string components may limit the geometry of the threads.

[0022] Accordingly, there is a need for improved threaded structures and drilling components that reduce abrasion, galling, and non-threaded screwing, as well as efficiently use available material to increase the load bearing capacity and reliability of the joint.

SUMMARY OF THE INVENTION

[0023] It should be understood that this description of the invention does not constitute a broad overview of the present invention. This description of the invention is typical and not limiting, and it is neither intended to identify key or critical elements of the invention, nor to determine its scope. The sole purpose of this description of the invention is to explain and give examples of certain concepts of the present invention as an introduction to the following full and broad detailed description.

[0024] One or more embodiments of the present invention overcome one or more of the above or other problems in the art regarding drilling components, tools, and systems that provide efficient and productive threaded connections. In one aspect, one or more embodiments of the present invention include drill string components having enhanced strength as well as non-threading and jamming resistance. Such drill string components can reduce or eliminate thread damage due to jamming and non-threading. In particular, one or more embodiments of the invention include drill string components having threads with a front end or thread run oriented at an acute angle with respect to the central axis of the drill string component. Additionally or alternatively, the front end of the threads can provide a sharp transition to the full depth and / or width of the thread profile. Additionally or alternatively, threads may have at least one parameter of a variable thread pitch and a variable thread profile width. Additionally or in an alternative embodiment, the threads may have a cylindrical cavity of the thread and the top of the thread, which describe a truncated cone on at least part of the axial length of the threads.

[0025] In one aspect, in one or more embodiments of the invention, a threaded drill string component having increased strength as well as resistance to jamming and non-threaded screwing comprises a hollow body having a first end, an opposite second end and a central axis passing through hollow body. The drill string component also includes at least one thread located at the first end of the hollow body. At least one thread contains a series of screw turns extending along the first end of the hollow body. At least one thread has a thread profile depth, a thread profile width, and a thread pitch. At least one thread comprises a front end near the first end of the hollow body. The front end of said at least one thread is oriented at an acute angle with respect to the central axis of the hollow body. The front end of said at least one thread faces an adjacent thread turn. The step of the specified at least one thread increases from the first value near the front end of at least part of the axial length of the specified row of its helical turns to the final value at the desired point on the specified at least one thread.

[0026] In one aspect, in one or more embodiments of the invention, a drill string component having increased strength as well as resistance to seizing and screwing up to non-threads includes at least one thread having a top and a thread root. The depression of the specified at least one thread describes a cylindrical surface along the axial length of the specified row of its helical turns. The apex of said at least one thread describes a truncated cone-shaped surface extending over at least part of the axial length of the indicated row of its helical turns.

[0027] In one aspect, in one or more embodiments of the invention, a drill string component having increased strength as well as resistance to seizing and screwing not thread, comprises a drill string component having a number of threads.

[0028] In one aspect, in one or more embodiments of the invention, a drill string component having increased strength as well as resistance to seizing and screwing not thread, comprises a drill string component that prevents interference fit on threaded elements. In a further aspect, interference fit is described for components without threaded components, such as, for example, shoulder surfaces.

[0029] In one aspect, in one or more embodiments of the invention, a threaded drill string component having increased strength as well as resistance to seizing and screwing off-thread, comprises a housing, an end with an internal thread, an opposite end with an external thread, and a central axis, passing through the body. The drill string component also comprises an internal thread located at an end with an internal thread of the body. The internal thread has depth and width. In addition, the drill string component also comprises an external thread located at an end with an external thread of the body. The external thread has depth and width. Each of the internal thread and external thread contains a front end. The front end of each of the internal thread and the external thread contains a flat surface extending at right angles to the body. The flat surface of the front end of the internal thread extends across the entire width and throughout the depth of the internal thread. Similarly, the flat surface of the front end of the external thread extends over the entire width and over the entire depth of the external thread.

[0030] In addition to the foregoing, an embodiment of a method for creating a joint in a drill string with increased strength and without jamming or screwing not thread includes putting the end with the external thread of the first component of the drill string into the end with the internal thread of the second component of the drill string. The method also includes rotating the first component of the drill string with respect to the second component of the drill string; thereby connecting end-to-end the flat front end of the external thread at the end with the external thread of the first component of the drill string with the flat front end of the internal thread at the end with the internal thread of the second component of the drill string. The flat front end of the external thread is oriented at an acute angle with respect to the central axis of the first component of the drill string. Similarly, the flat front end of the internal thread is oriented at an acute angle with respect to the central axis of the second component of the drill string. In addition, this method includes sliding the flat front end of the external thread from and along the flat front end of the internal thread to direct the external thread into the gap between the turns of the internal thread.

[0031] Additional features and advantages of exemplary embodiments of the present invention will be set forth in the following description, and they will in part become apparent from this description, or may be learned by practicing such exemplary embodiments. The features and advantages of such embodiments may be realized and obtained by means of the tools and combinations specifically pointed out in the attached claims. These and other features will become more apparent from the following description and appended claims, or may be learned by practicing such exemplary embodiments as set forth below.

Description of drawings

[0032] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and, together with the description, serve to explain the principles of these methods and systems.

[0033] Figure 1 illustrates a partial longitudinal sectional view through a series of connected drill rods in a drill string with the longitudinal middle portion of the drill rods extended to the side;

[0034] Figure 2 is an enlarged longitudinal view in longitudinal section of one of the joints of the drill rod of Figure 1, in which dashed lines indicate the location of the vertices and depressions of the threads diametrically opposed to those shown by solid lines, as well as the connection shown fully twisted. condition;

[0035] Figure 3 is a local longitudinal view of an end with an external thread of a drill rod oriented along the axis with an end with an internal thread of an adjacent drill rod, in which the sleeve and half of the nipple are shown in cross section;

[0036] Figure 4 illustrates a side view of the male end of a drill string component and a cross-sectional view of the female end of another drill string component, each of which has a front end thread in accordance with one or more embodiments of the present invention;

[0037] Figure 5 illustrates an exploded side view of a drill string having front end drill string components in accordance with one or more embodiments of the present invention; and

[0038] Figure 6 illustrates a schematic drawing of a drilling system comprising front end drill string components in accordance with one or more embodiments of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

[0039] Before the disclosure and description of the present methods and systems, it should be understood that these methods and systems are not limited to specific synthetic methods, specific components or specific compositions. It should also be understood that the terminology used in this document is intended to describe only specific embodiments of the invention, and it is not intended to limit.

[0040] When used in this description and the attached claims, the singular includes references to the plural, unless the context clearly dictates otherwise. Ranges can be expressed herein as from “about” one particular value and / or to “about” another specific value. With this range expression, another embodiment of the invention includes a range from one specific value and / or to another specific value. Similarly, if the values are expressed as approximations using the preceding “about”, it should be understood that a particular value forms another implementation option. Additionally, it should be understood that the end values of each range are significant both in relation to another end value, and independently of another end value.

[0041] “Optional” or “optionally” means that the event or circumstance described below may either occur or not occur, and that this description includes instances where the event or circumstance occurs and instances where it does not occur.

[0042] In the description and claims of the present description, the word “comprise” and variations of the word, such as “comprising” and “contains”, mean “including, without limitation to them” and are not intended to exclude, for example, other additives, components, integers or steps. The word “typical” means “an example of something” and is not intended to express an indication of a preferred or optimal implementation. The phrase "such as" is used not in a restrictive sense, but for explanatory purposes.

[0043] Describes components that can be used to perform the described methods and systems. This document describes these and other components, and it should be understood that when describing combinations, subsets, interactions, groups, etc. of these components, although the specific reference to each different individual and group combination and their permutations may not be explicitly described, each of them is specifically implied and described in this document for all methods and systems. This applies to all aspects of a given application, including but not limited to, steps in the disclosed methods. Thus, if there are a number of additional steps that can be performed, it should be understood that each of these additional steps can be performed in any particular embodiment or in a combination of the embodiments of the described methods.

[0044] The present methods and systems can be more easily understood by reference to the following detailed description of the preferred embodiments and examples included herein, as well as to the figures and their previous and subsequent description.

[0045] Embodiments of the present invention are directed to drilling components, tools, and systems that provide efficient threaded components for drilling and productive threaded connections. For example, one or more embodiments of the present invention include drill string components with improved load efficiency and load tolerance, and which may also be resistant to abrasion, sticking, and non-threading. Such drill string components can reduce or eliminate thread damage due to wear, sticking and screwing off-thread, while at the same time increasing load efficiency and load capacity compared to conventional drilling components. In particular, one or more embodiments include drill string components having multiple threads with leading ends or thread runs oriented at an acute angle with respect to the central axis of the drill string component. Additionally or alternatively, the front end of the thread can provide a sharp transition to the full depth and / or width of the thread profile. In addition, one or more embodiments of drill string components that are configured to provide gradual fit and preserve cross-sectional material include at least one of the variable thread widths to provide gradual fit in the axial direction of at least a portion of the thread and taper at least one of the mating vertices of the threads on at least part of the thread, while maintaining a constant inner diameter throughout the thread.

[0046] Reference will now be made to graphic materials for describing various aspects of one or more embodiments of the present invention. It should be understood that the graphic materials are graphic and schematic images of one or more embodiments and do not limit the present invention. In addition, although various graphic materials are presented on a scale that is considered functional for one or more embodiments, the graphic materials are not necessarily drawn to scale for all considered embodiments. Thus, graphic materials represent a typical scale, but one should not draw a conclusion from graphic materials regarding any necessary scale.

[0047] In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. However, those skilled in the art should understand that the present invention can be practiced without these specific details. In other cases, the well-known aspects of thread standards, thread manufacturing, in-field equipment for connecting threaded components and the like have not been described in particularly detail to avoid unnecessarily obscure aspects of the described embodiments.

[0048] Turning now to FIG. 1, an embodiment of a typical threaded drill string component is illustrated. Threaded drill string components having increased load capacity and load efficiency, which can also be connected to avoid or reduce the risk of wear, non-threading and jamming, are described in detail below. As shown in figures 1-4, the first component 102 of the drill string may include a housing 103 and a male connector or end 104 with an external thread. The second drill string component 106 may comprise a housing 107 and a female thread connecting end or end 108. The end 104 with the external thread of the first component 106 of the drill string may be configured to connect with the end 108 with the internal thread of the second component 106 of the drill string.

In one or more embodiments of the invention, each drill string component 102, 106 may comprise a hollow body having a central axis 126 extending through it, as shown in Figures 1-4. In alternative embodiments of the invention, one or more drill string components 102, 106 may comprise a continuous body (such as an impact drill rod or drill bit) or a partially hollow body. More specifically, in the case of a hollow body, the hollow body may comprise an inner diameter (ID), an outer diameter (OD), and a wall thickness. In one exemplary aspect, a drill string component may have the following characteristic dimensions:

Example 1 Example 2 Example 3 Example 4 OD (inches) 2.20 2.75 3,50 4,50 ID (inches) 1.91 2,38 3.06 4.0 Wall thickness (inch) 0.15 0.19 0.22 0.25 Outside Diameter (Inch) 2.09 2.61 3.34 4.35

[0049] The male end 104 may include at least one external thread 110 (that is, a thread that projects radially outward from the outer surface of the external thread end 104). Alternatively, the female thread end 108 may comprise at least one internal thread 112 (i.e., a thread that projects radially inward from the inner surface of the female thread end 108). At least one external thread 110 and at least one internal thread 112 may generally have corresponding characteristics (e.g., width, height or depth, length of a threaded part, taper, stroke, pitch, number of threads per inch, number thread runs, average diameter, threads of mating thread, etc.) or they may differ in one or more of the listed characteristics.

[0050] In another aspect of the present invention, when characterizing the components of a drill string of the present invention, the following ranges and ratios are considered:

Ranges / Ratios Example 1 Example 2 Example 3 Example 4 Wall Thickness to Outside Diameter (%) 7% 6% 6% 7% Depth of thread to wall thickness (%) nineteen% sixteen% 21% sixteen% Common cone range (degrees) 0.8 1,0 1,0 0.5 Side angle range (degrees) -10 fifteen 2 -twenty The length of the threaded part to the diameter (%) 55% 39% 44% 43% Thread Pitch Range (turns per inch) 3,50 3.00 2,50 1.75 Outer diameter less than inner diameter, to wall thickness 62% 62% 70% 63% Shoulder thickness to wall thickness (%) 38% 38% thirty% 37%

[0051] In one or more embodiments of the invention, at least one external thread 110 and at least one internal thread 112 may include straight peaks and troughs. In a further embodiment of the invention, at least one of the vertices of said at least one external thread and said at least one internal thread 110, 112 are conical in shape, while the troughs of the thread 110, 112 remain constant. In another aspect, there is no need for threads 110, 112 to be constant over their entire length. Moreover, at least one external thread 110 may have characteristics corresponding to the characteristics of said at least one internal thread 112, despite a change in characteristics along the respective lengths of the male end 104 and the female end 108. In one or more embodiments, the at least one outer and at least one inner threads 110, 112 may have a variable thread pitch on at least a portion of the threads 110, 112. In other further or alternative embodiments, the at least one outer thread and at least one internal thread 110, 112 may have a constant pitch when measuring between the thread of at least one threaded parameter, and a variable thread width on at least a portion of the threads 110, 112. In additional or alternative embodiments of the invention, at least one of the peaks of the at least one external thread and the at least one internal thread 110, 112 are tapered on a desired portion of the length of the threads 110, 112, while the troughs of the threads 110, 112 remain constant.

[0052] In one or more embodiments, the external and internal threads 110, 112 may have characteristics identical or similar to those described in US Pat. No. 5,788,401, the entire contents of which are incorporated herein by reference. For example, in one or more embodiments of the invention, the external and internal threads 110, 112 have an apex, recess, pressure lateral, and clearance lateral. In accordance with one aspect of the thread 110, 112 may have an angle of inclination of the lateral side under pressure (or an angle of inclination of the support side), which may be from about -30 to about 15 degrees; more specifically, from about -20 to about -10 degrees; and, even more specifically, from about -20 to about -15 degrees when measured with respect to a surface perpendicular to the central axis of the drill string. As will be appreciated by one of ordinary skill in the art in light of the present description, such negative angles of inclination of the lateral side under pressure can help to keep the joint in a conjugated state, even during overload, and also reduce the overall load compared to positive angles of inclination of the lateral side of the thread.

[0053] In another aspect, the end with a female thread and the end with an external thread of a drill string component can have shoulders with a taper of about 0 to about 15 degrees. In another aspect, the shoulders may have an outer diameter thickness of about 0.055 to about 0.080 inches; and, more specifically, about 0.055 inches, about 0.083 inches, about 0.070 inches, or about 0.075 inches.

[0054] In other aspects, the critical thickness of the part of the nipple, or the specified thickness of the material under the external thread, can be used as an indicator of the ultimate tensile strength and stress enhancement resulting from thread cutting. In one aspect, the critical thickness of the nipple portion may be from about 40% to about 50% of the wall thickness; and more specifically, about 44%, about 45%, about 46%, or about 47% of the wall thickness.

[0055] In other aspects, the critical stiffness of the sleeve of the sleeve, or the cross-sectional moment of moment, or the "inertia modulus" of the sleeve of the sleeve, may contribute to torsion resistance and may be exponentially sensitive to the thickness of the shoulder. In one aspect, the critical stiffness of the coupling shoulder can be from about 34% to about 48% of the stiffness of the pipes; more preferably about 40%, about 41%, or about 43% of the pipe stiffness.

[0056] In light of the description herein, it should be understood that the above description is only one configuration of the external and external threads 110, 112. In alternative embodiments of the invention, the configuration of the external and external threads 110, 112 may differ from the description above . In some alternative embodiments of the invention, threads 110, 112 may also have negative angles of inclination of the side under pressure of about 5 to 30 degrees with respect to a plane perpendicular to the center axis of the drill string, and sides with a clearance of at least an angle at least 45 degrees to help keep the joint in conjugate condition, even during overload, and to help make up the joint. In addition, the end with an internal thread and the end with an external thread can have shoulders with a taper of about 5 to 20 degrees.

[0057] In another aspect, the angle of inclination of the side of the thread can be characterized by a decomposition of the radial load of the angle of inclination of the side of the thread, which describes the radial load created by the angle of inclination of the support side that must be absorbed in the joint. As will be appreciated by one of ordinary skill in the art in light of the present disclosure, the radial load decomposition values of the tilt angle of the side can be limited by the tilt angles of the side of the thread that cause excessive thread tension. Radial loads can be defined as the percentage of axial load applied to the side of the thread or to a joint defined by the angle of inclination of the side of the thread. In particular, the created radial load is equal to the axial load multiplied by the tangent of the angle of inclination of the side of the thread. As will also be clear to a person skilled in the art in light of the present description, positive values of the radial load can cause undesirable decomposition, while negative values can provide positive compression. Compression is positive because it can reduce overall stress or von Mises stresses, and it can increase pressure on the contact surface between mating threads, which increases the friction and torsional load transmitted to the joint. However, positive compression due to negative radial load values may become undesirable after crossing a certain threshold value. In this description, the decomposition of the radial load of the angle of inclination of the side of the thread may be from about -18% to about -36%; more specifically, from about -18% to about -36%; and even more specifically, about -27%.

[0058] The external thread 110 may begin near the leading edge 140 of the end 104 with the external thread. For example, Figures 1-3 illustrate that the external thread 110 can be deflected a distance (shown has a linear distance 116) from the leading edge 140 of the male end 104. The deflection distance may allow the non-mating portion of the shoulder of the threaded element to elastically compress under the torque applied during make-up of the joint. As one skilled in the art will understand, the resultant joint can maintain a preload condition under the application of make-up torque, and a sufficient deflection distance may be required to allow threading, and may provide the possibility of creating a “preload” since the shoulder subjected to elastic compression. This “preload” may be required to keep the connection closed, while at high tensile loads during drilling or deflection of the loads causing bending, which could otherwise lead to the opening of the contact surface of the shoulder, thereby increasing the bending load on the nipple and creating the potential that a male end is subjected to fatigue failure. Accordingly, in various aspects, the deviation distance 116 may vary as desired and, in particular, may vary depending on the size of the drill string component 102, the configuration of the thread 110, or depend on other factors. In at least one embodiment, the deflection distance 116 is in the range of about half to about twice the width 118 of the outer thread 110. Alternatively, the deflection distance 116 may be larger or smaller. For example, in one or more embodiments of the invention, the deviation distance 116 is zero, so that the external thread 110 starts at the leading edge 140 of the male end 104.

[0059] Similarly, the internal thread 112 may begin near the leading edge 120 of the end 108 with the internal thread. For example, Figures 1-4 illustrate that the internal thread 112 may be deflected a distance (shown has a linear distance 122) from the leading edge 120 of the female end 108. Deviation distance 122 may vary as desired and, in particular, may vary depending on the size of the drill string component 106, the configuration of the internal thread 110, or depend on other factors. In at least one embodiment, the deviation distance 122 is in the range of about half to about twice the width 124 of the internal thread 112. Alternatively, the deviation distance 122 may be larger or smaller. For example, in one or more embodiments of the invention, the deviation distance 122 is zero, so that the internal thread 112 starts at the leading edge 120 of the end 108 with the internal thread.

[0060] Furthermore, the deviation distance 116 may be equal to the deviation distance 122, as shown in figures 1-4. In alternative embodiments, the deviation distance 122 may be larger or smaller than the deviation distance 116. In any case, as the leading edge 140 of the end 104 with the external thread is inserted into the end 108 with the internal thread and rotates, the external thread 110 may engage with the internal thread 112, and the end 104 with the external thread may linearly advance along the central axis 126 of the end 108 with internal thread.

[0061] In particular, the external and internal threads 110, 112 may be arranged along a helical line with respect to the respective male and female ends 104, 108. In other words, each of the external 110 and internal thread 112 may comprise a series of helical turns extending along the corresponding drill string component 102, 106. As the external and external threads 110, 112 are mated, the threads can thus rotate with respect to each other and sit within the gaps between the respective threads. In figures 1-4, the external thread 110, as a rule, is wound on the end 104 with an external thread at an angle of 128, which can also be measured with respect to the leading edge 140 of the end 104 with an external thread.

Multiple Thread Approaches

[0062] One or more embodiments of the present invention include drill string components having a number of threads. For example, in one or more embodiments of the invention, the drill string component comprises at least two threads having corresponding thread starts, which are optionally located at equal distances from the front end of the drill string component.

[0063] In one aspect, the use of multiple threads can increase the area of the supporting surface of the supporting side of the thread and can lead to greater overall load efficiency when connecting components to the external and internal threads. In one example, the use of two threads doubles the area of the thread support compared to a single thread, while keeping all other thread characteristics constant.

[0064] In another aspect, the use of multiple threads can also increase the amount of material at the junction of the side of the thread profile into the thread depression and, accordingly, the fatigue strength of the drilling component. Not wanting to be bound by theory and / or modeling, the place of transition of the side of the thread profile into the thread depression is the place of maximum stress and causing fatigue fracture in the joints of the components of the drill string. It follows that, while maintaining all other factors constant, the use of multiple threads can increase the fatigue strength of the drilling component, since the fatigue strength of the available material is reduced due to the average load, as illustrated by the standard modified Goodman fatigue diagram.

[0065] In a further aspect, the use of multi-threaded threads spaced equidistant from the respective front ends of the drill string components can increase the load bearing capacity of drill string components placed in the butt contact by creating a symmetrical dynamic load near the center axis of the component.

[0066] On the other hand, the angle of the thread may increase as the pitch of the thread decreases and the number of threads increases. An increase in the angle of thread elevation after reaching the optimum angle can reduce the requirement for the torque of the thread to be unfastened, as a result of which the interface of the drill string components can be disassembled during operation. In another aspect, the individual thread width and, accordingly, the shear area of the load may decrease as the number of threads on a given drilling component increases, ultimately leading to damage due to overload of the thread shear.

[0067] In one embodiment, the number of threads that increases the load efficiency, allowable load and fatigue strength of the drill string component while maintaining acceptable thread angles and shear area for the drill string component of the given size can be determined as the maximum possible number of threads, when this thread width is not less than the thread height. In another embodiment of the invention, this description provides drill string components having at least two threads, and preferably from about two to about four threads, configured to increase the load efficiency, allowable load and fatigue strength of the drill string while maintaining acceptable angles thread elevation and shear area compared to conventional one-way drill string components.

[0068] In one example, at least two external threads 110 may begin near the leading edge 140 of the external thread end 104. In an additional aspect, at least two external threads can be placed at an equal distance near the leading edge 140 of the male end 104. For example, it is assumed that the end with an external thread has two external threads with thread runs located at a distance of about 180 degrees from each other and near the leading edge 140 of the end 104 with an external thread. In another example, it is assumed that the end with an external thread has three external threads with thread starts, which can be located at a distance of about 120 degrees from each other and near the leading edge 140 of the end 104 with an external thread.

[0069] Similarly, at least two internal threads 112 may begin near the leading edge 120 of the end 108 with internal thread. In an additional aspect, at least two internal threads can be placed at an equal distance near the leading edge 120 of the end 108 with internal thread. For example, it is assumed that the end 108 with an internal thread has two internal threads 112 with approaches located at a distance of about 180 degrees from each other and near the leading edge 120 of the end 108 with an internal thread. In another example, it is assumed that the end 108 with an internal thread has three internal threads 112 with approaches that can be located at a distance of about 120 degrees from each other and near the leading edge 120 of the end 108 with an internal thread.

[0070] In particular, at least two external threads 110 and at least two internal threads 112 may be disposed along a helical line with respect to respective male and female ends 104, 108. In other words, each of the external threads 110 and each of the internal threads 112 may comprise a series of helical turns extending along the corresponding drill string component 102, 106. Each of the external threads 110 and each of the internal threads 112 may include front ends oriented at an acute angle with respect to the central axis of the corresponding drill string component 102, 106 and placed at an equal distance about it. As at least two external threads 110 and at least two internal threads 112 are mated, they can thus rotate with respect to each other and sit within the gaps between the respective threads and, ultimately, form a drill string connection. Accordingly, in one or more embodiments of the invention, a drill string joint is obtained having enhanced load efficiency, load tolerance and fatigue strength while maintaining acceptable thread angles and shear area for a given diameter of the drill string component.

Optimum material cross sections for maximum load capacity

[0071] One or more embodiments of the present invention include drill string components that substantially eliminate the overall taper of the trough and thread in favor of at least one of a variable thread pitch, variable thread width, and taper of at least a portion of the thread apex, while providing uniform thread depression. Another aspect of the present invention includes drill string components that eliminate the overall taper of the trough and thread in favor of at least one of a variable thread pitch, a variable thread width, and a taper of at least a portion of the thread tip, while providing a uniform thread trough.

[0072] In one aspect, material that is typically lost on the overall taper of the joint and thread is retained by providing drill string components having at least one thread containing a thread pitch that changes from a first value near the front end to at least at least part of the axial length of the indicated row of its helical turns to the final value at the desired point on the specified at least one thread, thereby selectively providing an axial gradual fit. In one aspect, the thread pitch may increase uniformly from the first value at least at the first turn to the final value at least at the last turn of the indicated series of screw turns. In an alternative aspect, the thread pitch may increase unevenly from the first value to the final value along the entire axial length of the indicated series of helical turns. In an additional aspect, the thread pitch may increase from the first value to the final value on a part of the axial length of the specified series of screw turns and after that it can remain constant. In another aspect, the at least one thread may have a height that varies from about 2.0 to 5.0 turns / inch, preferably from about 3 to about 4 turns / inch, and most preferably from about 3 to about 3.5 turns / inch In other aspects, the thread may have a variable pitch on at least one thread and, preferably, two threads. In an alternative aspect, the thread may have a pitch that varies from the front end to the rear end of the thread.

[0073] In another aspect, a material that is typically lost on the overall taper of the joint and thread is maintained by providing drill string components having at least one thread containing a thread pitch that is constant when measuring at least one predetermined thread parameter, but the width of which can vary from the first value near the front end of at least part of the axial length of the indicated row of its helical turns to the final value at the desired point on the specified at least one thread, thereby selectively providing an axial gradual fit. In one aspect, the thread width may uniformly increase from the first value at least at the first turn to the final value at least at the last turn of the indicated series of screw turns. In an alternative aspect, the thread width may increase unevenly from the first value to the final value along the entire axial length of the indicated series of screw turns. In an additional aspect, the thread pitch may increase from the first value to the final value on a part of the axial length of the specified series of screw turns and after that it can remain constant. In other aspects, the pitch on the support side of the thread may be kept constant, while on the front side it increases. In alternative aspects, the pitch on the front side of the thread can be kept constant, while on the support side it increases. In other aspects, the middle of the thread may have a constant pitch, while both sides have a variable pitch. In other further aspects, the variable pitch of the support side may be different from the variable pitch of the front side.

[0074] In yet another aspect, the at least one thread may have a width that varies from about 50% of the total width of the thread near the front end and increases to the full width of the thread near the rear end. In a further aspect, the at least one thread may have a width that varies from about 75% of the total width of the thread near the front end and increases to the full width of the thread near the rear end. In other aspects, the thread may have a variable width on at least one thread and, preferably, two threads. In an alternative aspect, the thread may have a width that varies from the front end to the rear end of the thread. In one exemplary embodiment, a thread with 2 turns per inch having a full width of 1/4 "near the rear end may have a reduced width of about 1/8" at the front end. As will be understood by a person skilled in the art, the largest distance between adjacent turns of the at least one thread is at the front end and provides additional axial clearance when baiting the threads.

[0075] In yet another aspect, a material that is typically lost on the overall taper of the joint and thread is retained by providing drill string components having at least one thread containing a cavity that describes a cylindrical surface extending along its entire axial length the specified number of screw threads, and a vertex that describes a surface in the form of a truncated cone, extending at least part of the axial length of the specified series of its screw turns, thereby selectively providing a radial gradual fit. A truncated cone-shaped surface is a straight line having an angle with respect to the central axis of the hollow body. In one aspect, the apex describes a surface in the form of a truncated cone along the entire axial length of the indicated series of helical turns. In another aspect, the at least one thread may have a truncated cone apex on at least a portion of the axial length of said at least one thread with a truncated cone generatrix with an angle of about 0.75 to 1.6 degrees, while at least one thread may have cylindrical cavities. In another aspect, the apex describes a truncated cone surface extending along the axial length of at least one thread and, preferably, at least two threads. In alternative aspects, the axial length may be essentially the total axial length of the thread.

[0076] In yet another aspect, material that is typically lost on the overall taper of the joint and thread is retained by providing drill string components having at least one thread including a thread pitch that changes from a first value near the front end at least a part of the axial length of the indicated series of its helical turns to the final value at the desired point on the specified at least one thread, and further comprising a thread depression that describes a cylindrical surface extending along the entire axial length of the specified series of helical turns, and the apex , which describes a surface in the form of a truncated cone, extending at least part of the axial length of the indicated row of its helical turns, thereby selectively providing both axial gradual fit and radial gradual fit.

[0077] In one example, at least one external thread 110 may begin near the leading edge 140 of the external thread end 104. At least one external thread 110 may comprise a series of helical turns extending along the corresponding length of the external thread end 104. In a further aspect, the at least one external thread may have a pitch that increases from a first value near the leading edge 140 of at least a portion of the axial length of said row of its helical turns to a final value at a desired point on said at least one external thread 110, and after that is kept constant. In another aspect, the at least one external thread may have a pitch that increases from a first value near the leading edge along the entire axial length of the indicated row of its helical turns to the final value. In alternative aspects, the pitch may increase uniformly or unevenly along the axial length of the at least one external thread 110. For example, it is contemplated that the male end has two external threads having a pitch that increases from the leading edge of the male thread end 104 to the final values at the desired point along the axial length of the thread when measuring this point from the end 104 with an external thread.

[0078] Similarly, at least one internal thread 112 may begin near the leading edge 120 of the female end 108. At least one internal thread 112 may comprise a series of helical turns extending along the corresponding length of the female end 108. In an additional aspect, the at least one internal thread may have a step that increases from a first value near the leading edge 120 at least a portion of the axial length of the indicated row of its helical turns to the final value at the desired point on the specified at least one internal thread 112, and after that is kept constant. In another aspect, the at least one internal thread may have a pitch that increases from a first value near the leading edge 120 over the entire part of the axial length of the indicated row of its helical turns to the final value. In alternative aspects, the pitch may uniformly or unevenly increase along the axial length of the at least one internal thread 112. For example, it is contemplated that an end with an external thread has two internal threads having a step that increases from the leading edge 120 of the end 108 with the internal thread to the final value at the desired point along the axial length of the thread, when measuring this point from the end 108 with internal thread.

[0079] In particular, at least one external thread 110 and at least one internal thread 112 may be arranged along a helical line with respect to respective male and female ends 104, 108. In other words, at least one outer 110 and at least one inner thread 112 may comprise a series of helical turns extending along the corresponding drill string component 102, 106. At least one external 110 and at least one internal thread 112 - each may include front ends oriented at an acute angle with respect to the central axis of the corresponding component 102, 106 of the drill string and placed near it. As the at least one external thread 110 and the at least one internal thread 112 are mated, the threads can thus rotate with respect to each other and sit within the gaps between the respective threads and, ultimately, form a drill string connection. A gradual axial fit is selectively created between the respective male and female ends 104, 108 as the pitch of at least one of said at least one external thread 110 and said at least one internal thread 112 increases. Accordingly, in one or more embodiments of the invention provide a drill string joint having optimal cross sections of the material for the maximum allowable load.

[0080] In another example, at least one external thread 110 may begin near the leading edge of the external thread end 104. At least one external thread 110 may comprise a series of helical turns extending along the corresponding length of the male end 104, and may also have at least one thread parameter with a constant pitch along the entire axial length of the thread. Typical thread parameters, the height of which may be kept constant, may include a support side, a front side, a middle thread, and the like. In an additional aspect, at least one external thread may have a width that increases from a percentage of the total width of the thread near the leading edge of at least a portion of the axial length of the indicated row of its helical turns to the full width of the thread at the desired point on the specified at least one external thread 110, and thereafter maintained constant. In another aspect, at least one external thread may have a width that increases from a percentage of the total width of the thread near the leading edge along the entire axial length of the indicated row of its helical turns to the full width of the thread. In alternative aspects, the thread width may increase uniformly or unevenly along the axial length of the at least one external thread 110. For example, it is assumed that the male end has two external threads, with at least one external thread having at least one parameter having a constant pitch along the entire axial length of this thread and a width that increases from a percentage of the total width of the thread on the leading edge of the male end 104 to the full width of the thread at a desired point along the axial length of the thread.

[0081] Similarly, at least one internal thread 112 may begin near the leading edge 142 of the female end 108. At least one internal thread 112 may comprise a series of helical turns extending along the corresponding length of the female end 108, and may also have at least one thread parameter with a constant pitch along the entire axial length of the thread. Typical thread parameters, the height of which may be kept constant, may include a support side, a front side, a middle thread, and the like. In an additional aspect, at least one internal thread may have a width that increases from a percentage of the total width of the thread near the leading edge 142 at least part of the axial length of the indicated row of its helical turns to the full width of the thread at the desired point on the specified at least one internal thread 112, and thereafter maintained constant. In another aspect, the at least one internal thread may have a thread width that increases from a percentage of the total thread width near the leading edge 142 along the entire axial length of the indicated row of its helical turns to the full thread width. In alternative aspects, the width of the thread may uniformly or unevenly increase along the axial length of the at least one internal thread 112. For example, it is assumed that the end with an internal thread has two internal threads, with at least one internal thread having at least one parameter having a constant pitch along the entire axial length of this thread and a width that increases from a percentage of the total width of the thread on the leading edge 142 of the end 108 with the internal thread to the full width of the thread at a desired point along the axial length of the thread.

[0082] In particular, at least one external thread 110 and at least one internal thread 112 may be arranged along a helical line with respect to respective male and female ends 104, 108. In other words, at least one external thread 110 and at least one internal thread 112 may comprise a series of helical turns extending along the corresponding drill string component 102, 106. At least one external thread 110 and at least one internal thread 112 can each contain front ends oriented at an acute angle with respect to the central axis 102 and 106 of the drill string. As at least one external thread 110 and at least one internal thread 112 are mated, they can thus rotate with respect to each other and sit within the gaps between the respective threads and, ultimately, form a drill string connection. A gradual fit in the axial direction is selectively created between the respective male and female ends 104, 108 as the width of the at least one of the at least one external thread 110 and the at least one internal thread 112 increases, while at least one parameter of at least one external thread 110 and at least one internal thread 112 has a constant pitch along the entire axial length of the corresponding thread. Accordingly, in one or more embodiments of the invention, a drill string connection is obtained having optimal cross sections of the material for maximum allowable load.

[0083] In another example, at least one external thread 110 may begin near the leading edge of the external thread end 104. At least one external thread 110 may comprise a series of helical turns extending along the corresponding length of the external thread end 104. In one aspect, the at least one external thread 110 may have a thread depression that describes a cylindrical surface along the entire axial length of said series of helical turns. In a further aspect, at least one external thread 110 may have a thread apex that describes a truncated cone surface from a first diameter near a leading edge extending at least a portion of the axial length of a specified row of its helical turns to a final diameter at a desired point on the specified at least one external thread 110 and then maintained constant. The specified generatrix of the surface in the form of a truncated cone is a straight line passing through the tops of the thread, which lies at an angle with respect to the central axis passing through the hollow body. In another aspect, at least one external thread 110 may have a thread apex that describes a truncated cone surface from a first diameter near a leading edge extending along the entire axial length of a specified series of its helical turns to a final diameter. For example, it is assumed that the end with an external thread has at least one external thread having a top of a thread that describes a cylinder and a top of a thread that describes a surface in the form of a truncated cone from a first diameter near a leading edge extending over a desired portion of an axial length of said a number of its helical turns, to a final diameter at a desired point on said at least one external thread 110 and thereafter maintained constant.

[0084] Similarly, at least one internal thread 112 may begin near the leading edge 120 of the female end 108. At least one internal thread 112 may comprise a series of helical turns extending along the corresponding length of the female end 108. In one aspect, the at least one internal thread 112 may have a thread depression that describes a cylindrical surface along the entire axial length of said series of helical turns. In a further aspect, at least one internal thread 112 may have a thread apex that describes a truncated cone surface from a first diameter near a leading edge 120 extending at least a portion of the axial length of a specified row of its helical turns to a final diameter at a desired point on said at least one internal thread 112 and thereafter is kept constant. The specified generatrix of the surface in the form of a truncated cone is a straight line passing through the tops of the thread, which lies at an angle with respect to the central axis passing through the hollow body. In another aspect, at least one internal thread 112 may have a thread apex that describes a truncated cone surface from a first diameter near the leading edge 120 extending along the entire axial length of the indicated row of its helical turns to the final diameter. For example, it is assumed that the female end 108 has at least one internal thread 112 having a peak that describes a cylinder and a peak that describes a surface in the form of a truncated cone from a first diameter near the leading edge 120 extending on the desired axial length the specified number of its helical turns to the final diameter at the desired point on the specified at least one internal thread 112, and after that is kept constant.

[0085] In particular, at least one external thread 110 and at least one internal thread 112 may be disposed along a helical line with respect to respective male and female ends 104, 108. In other words, at least one outer 110 and at least one inner thread 112 may comprise a series of helical turns extending along the corresponding drill string component 102, 106. At least one external 110 and at least one internal thread 112 may each comprise front ends oriented at an acute angle with respect to the central axis of the corresponding drill string component 102, 106. In one aspect, at least one outer 110 and at least one inner thread 112 may have a depression that describes a cylindrical surface along the entire axial length of the indicated series of helical turns. In a further aspect, said at least one outer 110 and said at least one inner thread 112 may have a vertex that describes a surface in the shape of a truncated cone from a first diameter near a leading edge extending at least part of the axial length of said row of its helical turns to the final diameter at the desired point on the at least one internal thread 112 and thereafter is kept constant. As the at least one external 110 and at least one internal thread 112 are mated, they can thus rotate with respect to each other and sit within the gaps between the corresponding threads and, ultimately, form a drill string connection. A gradual fit in the radial direction is selectively created between the respective male and female ends 104, 108 as the diameter of the apex of at least one of said at least one external 110 and said at least one internal thread 112 increases. Accordingly, in one or more embodiments of the invention provide a drill string joint having optimal cross sections of the material for maximum allowable load.

[0086] In another example, at least one external thread 110 may begin near the leading edge of the external thread end 104. At least one external thread 110 may comprise a series of helical turns extending along the corresponding length of the external thread end 104. In one aspect, the at least one external thread may have at least one parameter of pitch and width that increases from a first value near the leading edge of at least a portion of the axial length of the indicated row of its helical turns to a final value at a desired point on said at least one external thread 110 and thereafter is kept constant. In an additional aspect, at least one external thread 110 may have a depression that describes a cylindrical surface along the entire axial length of the specified series of helical turns. In yet a further aspect, at least one external thread 110 may have a vertex that describes a truncated cone surface from a first diameter near a leading edge extending at least a portion of the axial length of said row of its helical turns to a final diameter at a desired point on said at least one external thread 110 and thereafter is kept constant. The specified generatrix of the surface in the form of a truncated cone is a straight line passing through the tops of the thread, which lies at an angle with respect to the central axis passing through the hollow body. In another aspect, at least one external thread 110 may have a vertex that describes a surface in the form of a truncated cone from a first diameter near the leading edge extending along the entire axial length of the indicated row of its helical turns to the final diameter. For example, it is assumed that an end with an external thread has at least one external thread having an apex that describes a cylinder and a apex of a thread that describes a surface in the form of a truncated cone from a first diameter near a leading edge extending on a desired portion of the axial length of the row its helical turns, to a final diameter at a desired point on said at least one external thread 110 and thereafter maintained constant. At least one external thread 110 also has at least one parameter of a step and a width that increases from the leading edge of the external thread end 104 to the final value at a desired point along the axial length of the thread when measuring this point from the external thread end 104 .

[0087] Similarly, at least one internal thread 112 may begin near the leading edge 120 of the female end 108. At least one internal thread 112 may comprise a series of helical turns extending along the corresponding length of the female end 108. In one aspect, the at least one external thread may have at least one parameter of pitch and width that increases from a first value near the leading edge 120 at least a portion of the axial length of a specified row of its helical turns to a final value at a desired point on said at least one internal thread 112 and thereafter is kept constant. In a further aspect, the at least one internal thread 112 may have a thread depression that describes a cylindrical surface along the entire axial length of said series of helical turns. In yet another aspect, the at least one internal thread 112 may have a vertex that describes a truncated cone surface from a first diameter near the leading edge 120 extending at least a portion of the axial length of the indicated row of its helical turns to a final diameter in the desired a point on said at least one internal thread 112 and thereafter is kept constant. The specified generatrix of the surface in the form of a truncated cone is a straight line passing through the tops of the thread, which lies at an angle with respect to the central axis passing through the hollow body. In another aspect, at least one internal thread 112 may have a vertex that describes a truncated cone-shaped surface from a first diameter near a leading edge 120 extending over the entire axial length of a specified series of its helical turns to a final diameter. For example, it is assumed that the female end 108 has at least one internal thread 112 having a top that describes a cylinder and a thread top that describes a truncated cone surface from a first diameter near the leading edge 120 extending on the desired axial portion the length of the indicated row of its helical turns, to the final diameter at the desired point on the at least one internal thread 112, and then maintained constant. At least one internal thread 112 also has at least one parameter of a step and a width that increases from the leading edge 120 of the end 108 with the internal thread to the final value at a desired point along the axial length of the thread when measuring this point from the end 108 with the inner carving.

[0088] In particular, at least one external 110 and at least one internal thread 112 may be arranged along a helical line with respect to respective male and female ends 104, 108. In other words, at least one outer 110 and at least one inner thread 112 may comprise a series of helical turns extending along the corresponding drill string component 102, 106. At least one external 110 and at least one internal thread 112 may each comprise front ends oriented at an acute angle with respect to the central axis of the corresponding drill string component 102, 106. In one aspect, at least one outer 110 and at least one inner thread 112 may have a thread depression that describes a cylindrical surface along the entire axial length of said series of helical turns. In an additional aspect, said at least one outer 110 and said at least one inner thread 112 may have a vertex that describes a surface in the form of a truncated cone from the first diameter near the corresponding edge 114, 120 extending at least part of the axial length of the specified row its helical turns, to a final diameter at the desired point on the corresponding at least one thread, and after that is kept constant. As the at least one external 110 and at least one internal thread 112 are mated, they can thus rotate with respect to each other and sit within the gaps between the corresponding threads and, ultimately, form a drill string connection. A gradual fit in the radial direction is selectively created between the respective male and female ends 104, 108 as the diameter of the apex of at least one of the at least one external 110 and the at least one internal thread 112 increases. Also, a gradual axial fit a direction is selectively created between respective male and female ends 104, 108. At least one parameter of the pitch and width of at least one of said at least one external 110 and said at least one internal thread 112 is increased. Accordingly, in one or more embodiments of the invention, a drill string connection is obtained having optimal cross sections of the material for maximum allowable load.

Thread seals with anti-seizing

[0089] One or more embodiments of the present invention include drill string components having threads, the corresponding front ends of which are oriented at an acute angle with respect to the central axis of the drill string component, and, additionally or alternatively, the front end of the thread can provide a sharp transition to full depth and / or width of the thread profile.

[0090] The external thread 110 may include a thread profile width 118 and the internal thread 112 may include a thread profile width 124, as previously mentioned. When used in the text of this document, the term "thread profile width" may include the linear distance between the edges of the threads at the measurement along a line perpendicular to the edges of the threads. It should be understood that the widths 118, 124 of the thread profile may vary depending on the configuration of the threads 110, 112. In one or more embodiments of the invention, the width 118 of the profile of the external thread 110 is equal to the width 124 of the profile of the inner 112. In alternative embodiments, the width 118 of the profile of the outer thread 110 is larger or smaller than the width 124 of the profile of the inner 112.

[0091] The outer thread 110 may include a thread depth 130 and the inner 112 may include a thread depth 132. As used herein, the term "thread depth" may include a linear distance from the surface from which the thread extends (for example, the outer surface of the end 104 with the external thread or the inner surface of the end 108 with the internal thread) to the radially farthest point the top of the thread when measured along a line perpendicular to the surface from which the thread passes. It should be understood that the depths 130, 132 of the threads may vary depending on the configuration of the threads 110, 112 and / or the size of the components 102, 106 of the drill string. In one or more embodiments, the depth 130 of the external thread 110 is equal to the depth 132 of the internal thread 112. In alternative embodiments, the depth 130 of the external thread 110 is greater or less than the depth 132 of the internal thread 112.

[0092] In one or more embodiments of the invention, the width 118, 124 of each thread 110, 112 is greater than the depth 130, 132 of each thread 110, 112. For example, in one or more embodiments of the invention, the width 118, 124 of each thread 110, 112 at least two times greater than the depth 130, 132 of each thread 110, 112. In alternative embodiments, the width 118, 124 of each thread 110, 112 is approximately equal to or less than the depth 130, 132 of each thread 110, 112.

[0093] As mentioned above, both the male and female threads 110, 112 may include a front end or thread lead. For example, Figures 1-4 illustrate that the outer thread 110 may comprise a thread lead or front end 114. Similarly, the inner thread 112 may comprise a thread lead or front end 120.

[0094] In one or more embodiments, the front end 114 of the external thread 110 may comprise a flat surface that extends from the external surface of the external thread end 104. For example, the front end 114 of the external thread 110 may comprise a flat surface that extends radially outward from the surface of the external thread end 104, thereby forming an end surface. In one or more embodiments, the front end 114 extends in a direction perpendicular to the outer surface of the external thread end 104. In alternative embodiments, the front end 114 extends in a direction substantially perpendicular to the outer surface of the male thread end 104 (i.e., in a direction oriented at an angle of less than about 15 degrees to the direction perpendicular to the external surface of the male thread end 104). In other further embodiments, the front end 114 may comprise a surface that bends along one or more of its heights and widths.

[0095] Furthermore, in one or more embodiments of the invention, the front end 114 of the outer thread 110 may extend over the entire width 118 of the outer thread 110. In other words, the front end 114 of the outer thread 110 may extend from the front to the trailing edge 138 of the outer thread 110. Thus, the flat surface forming the front end 114 may span the entire width 118 of the external thread 110.

[0096] Furthermore, in one or more embodiments of the invention, the front end 114 of the external thread 110 may extend along the entire depth 130 of the external thread 110. In other words, the height of the front end 114 of the external thread 110 may be equal to the depth of the thread 130. Thus, flat the surface forming the front end 114 may span the entire depth 130 of the external thread 110. Thus, the front end 114 or the thread entry may comprise a sharp transition to the full depth and / or profile width of the external thread 110. In other words, in one or more embodiments of the invention, the external thread 110 does not contain a thread run-off end that gradually tapers to the full depth of the external thread 110.

[0097] Similarly, the front end 120 of the internal thread 112 may include a flat surface that extends from the internal surface of the end 108 with the internal thread. For example, the front end 120 of the internal thread 112 may comprise a flat surface that extends radially inward from the internal surface of the female end 108, thereby forming an end surface. In one or more embodiments of the invention, the front end 120 extends in a direction perpendicular to the internal and / or external surface of the female thread end 108. In alternative embodiments, the front end 120 extends in a direction substantially perpendicular to the inner or outer surface of the end 108 with internal thread (i.e., in a direction oriented at an angle of less than about 15 degrees to the direction perpendicular to the inner and / or outer surface of the end 108 with internal thread). In other further embodiments, the front end 120 may comprise a surface that bends along one or more of its heights and widths. For example, the front end 114 and the front end 120 may contain common curved surfaces.

[0098] Furthermore, in one or more embodiments, the front end 120 of the internal thread 112 may extend over the entire width 124 of the internal thread 112. In other words, the front end 120 of the internal thread 112 may extend from the leading edge 144 to the trailing edge 144 of the internal thread 112. Thus, the flat surface forming the front end 120 may span the entire width 124 of the internal thread 112.

[0099] Furthermore, in one or more embodiments of the invention, the front end 120 of the internal thread 112 may extend along the entire depth 132 of the internal thread 112. In other words, the height of the front end 120 of the internal thread 112 may be equal to the depth of the thread 132. Thus, flat the surface forming the front end 120 may span the entire depth 132 of the internal thread 112. Thus, the front end 120 or the thread entry may comprise a sharp transition to the full depth and / or profile width of the internal thread 112. In other words, in one or more embodiments of the invention, the internal thread 112 does not contain a thread run-off end that gradually tapers to the full depth of the internal thread 112. In the illustrated embodiment, it is shown that the front end or inlet 120 of the internal thread 112 is formed by material that remains after machining or another method, used to make threads. Thus, the front end or thread start 120 can be made with respect to the inner surface of the end 108 with an internal thread, extrusion by a press, and not machining.

[00100] In one or more embodiments, the front end 114 of the external thread 110 may have a size and / or shape equal to the front end 120 of the internal thread 112. In alternative embodiments, the size and / or shape of the front end 114 of the external thread 110 may differ on the size and / or shape of the front end 120 of the internal thread 112. For example, in one or more embodiments of the invention, the front end 114 of the external thread 110 may be larger than the front end 120 of the internal 112.

[00101] In one or more embodiments, the front ends 114, 120 of each of the external and internal threads 110, 112 may have a non-axial orientation. In other words, the flat surfaces of the front ends 114, 120 of each of the external and internal threads 110, 112 may extend in a direction spaced apart or not parallel to the central axis 126 of the drill string components 102, 106. For example, as shown in Figures 1-4, the flat surface of the front end 114 of the external thread 110 may face an adjacent turn of the external thread 110. Similarly, the flat surface of the front end 120 of the internal thread 112 may face an adjacent turn of the internal thread 112.

[00102] In particular, the flat surface of the front end 114 of the external thread 110 may extend at an angle with respect to the front edge 140 or the central axis 126 of the external thread end 104. For example, Figures 1-4 illustrate that the flat surface of the front end 114 of the external thread 110 is oriented at an angle 146 with respect to the central axis 126 of the drill string component 102, although the angle can also be measured with respect to the leading edge 114. The orientation shown and the presence of a flat the surfaces of the front end 114 are particularly noticeable when compared with traditional threads that are tapered to a point such that there is virtually no distance between the front and rear edges of the thread, thereby ensuring that there is no end surface.

[00103] Similarly to the front end 114, the front end 120 of the internal thread 112 may extend at an angle with respect to the front edge 120 or the central axis 126 of the male end 104. For example, Figures 1-4 illustrate that the flat surface of the front end 120 of the internal thread 112 is oriented at an angle of 148 with respect to the central axis 126 of the drill string component 106, although the angle can also be measured with respect to the leading edge 120.

[00104] Angles 146, 148 may be modified in accordance with the present invention and comprise any number of different angles. The angles 146, 148 can be changed based on other characteristics of the threads 110, 112, or based on a value that is independent of the characteristics of the threads. In one or more embodiments of the invention, angle 146 is equal to angle 148. In alternative embodiments, angle 146 may be different from angle 148.

[00105] In one or more embodiments of the invention, each of the angles 146, 148 represents an acute angle. For example, each of the angles 146, 148 may include an angle from about 10 degrees to 80 degrees, from about 15 degrees to about 75 degrees, from about 20 degrees to about 70 degrees, from about 30 degrees to about 60 degrees, from about 40 degrees to about 50 degrees. In further embodiments, angles 146, 148 may be about 45 degrees. In light of the descriptions in this document, it should be understood that with a dynamic load between two adjacent front ends 114, 120 or lead-in chamfers with an increase in angles 146, 148, a decrease in impulse loss and a decrease in friction resistance are observed to bring the threads 110, 112 to full mate. In any case, the front end 114 of the external thread 110 may mate with the front end 120 of the internal thread 112 to facilitate the connection between the first 102 and the second component 106 of the drill string.

[00106] Thus, the front ends 114, 120 or the lead-in bevel of the thread can be achieved by eliminating the long run of the run of the thread and replacing the run by a sharper transition to the full height of the thread 110, 112. In addition, although the front ends 114, 120 can be located oriented at an angle or otherwise with respect to axis 126, the lead-in chamfer of the thread can also be perpendicular to the outer and / or inner diameters of the cylindrical surfaces of the respective ends 104, 108 with external and internal threads. Such a geometry excludes the run-in of threads with engagement on the run, which can act as a wedge mechanism, thereby eliminating geometry that leads to jamming when the ends 104, 108 are coupled to the external and internal threads.

[00107] In addition, as the ends 104, 108 are pulled together with the external and internal threads, the front ends 114, 120 or the threads can have corresponding surfaces that, when mated, create a border of the slip strip in a state close to the mating of the thread. For example, when each of the front ends 114, 120 is oriented at an acute angle, the front ends 114, 120 or the entry chamfers of the threads can mesh with each other and together tighten the threads into a fully mated state. As an example, during screwing up of the drill rod assembly as the end 104 with the external thread is inserted into the end 108 with the internal thread, the front ends 114, 120 may mesh and guide each other into respective recesses between the threads. This may occur during rotation and insertion of one or both of the drill string components 102, 106. In addition, since runaway runaways are excluded, there are several - if any - restrictions regarding the angular position for mating. Thus, the ends 104, 108 with external and internal thread can have the entire circumference available for pairing, without prone to sticking conditions.

[00108] In one or more embodiments of the invention, thread 110 may be abraded using conventional machining methods. The escape may be at least partially removed to form a front end 114. In such embodiments, the escape may extend approximately half the circumference of a predetermined male end 104. Therefore, if the entire run of thread 110 is removed, thread 110 may have a front end 114 matching the axis 126. However, if more thread 110 is removed after the run, front end 114 can be offset relative to axis 126. The run can be removed by means of a separate processing method. Although this example illustrates the removal of a runoff to obtain a thread start, in other embodiments of the invention, a lead-in chamfer of a thread may be formed in the absence of the creation and / or subsequent removal of a run of thread with engagement on the thread run. For example, instead of using conventional machining methods, threads are obtained by electrospark processing. Electrospark processing may provide the possibility of obtaining a front end 114, since metal can be used during this process. Alternatively, electrochemical processing or other methods that use the material can also be used to produce front ends 114, 120 of threads 110, 112.

Optimum interference fit

[00109] One or more embodiments of the present invention include excluding interference fit on thread elements and optionally transferring an interference fit to other connection elements, such as radially mating shoulder surfaces. In one aspect, the external and internal threads 110, 112 may have relative depths such that the top of the external thread maintains a certain radial distance from the trough of the mating internal thread and the top of the internal thread corresponds to the trough of the external thread. In another aspect, the external and internal threads 110, 112 may have relative depths such that the top of the internal thread maintains a certain radial distance from the trough of the mating external thread and the top of the internal thread corresponds to the trough of the external thread. In another aspect, the external and internal threads 110, 112 may have relative depths such that the top of the external thread maintains a certain radial distance with the trough of the mating internal thread and the top of the internal thread maintains a certain radial distance with the trough of the mating external thread. In one aspect, the radial distance between the peaks and troughs of the mating threads may be from about 0.001 to about 0.010 inches, more specifically from about 0.003 to about 0.007 inches, and most preferably about 0.005 inches. In an alternative aspect, the radial distance between the vertices of the mating threads may be from about 1% to about 5%, more specifically from about 1.5% to about 3%, and most specifically from about 2% to about 2.5% of the wall thickness hollow body.

[00110] As previously mentioned, in one or more embodiments of the invention, the drill string components 102, 106 may comprise hollow bodies. In particular, in one or more embodiments of the invention, the components of the drill string may be thin-walled. In particular, as shown in figures 1-4, the component 106 of the drill string may contain an outer diameter 150, an inner diameter 152 and a wall thickness 154. The wall thickness 154 may be equal to half the outer diameter 150 minus the inner diameter 152. In one or more embodiments of the invention, the drill string component 106 has a wall thickness 154 in the range of about 5 to 15 percent of the outer diameter 150. In further embodiments, the component 106 the drill string has a wall thickness of 154 in the range of about 6 to 8 percent of the outer diameter 150. It should be understood that such thin-walled components of the drill string may limit the geometry of the threads 112. However, the thin-walled component of the drill string may nevertheless contain any combination of the elements described higher despite such limitations.

[00111] Turning now to FIG. 5, it is illustrated that drill string components 102, 106 may comprise any number of different types of tools. In other words, almost any threaded element used in the drill string may contain one or more ends 108 with internal thread and ends 104 with external thread having front ends or thread starts, as described in relation to figures 1-4. For example, FIG. 5 illustrates that drill string components may include a relief adapter 201, a coupler 202, a drill stem 204, and an expander 206, each of which may include both an end 104 with an external thread and an end 108 with an internal thread with front ends 114 , 120, having increased load efficiency and allowable load, and which can also be resistant to wear, jamming and screwing not thread, as described above in relation to figures 1-4. Figure 5 further illustrates that the components of the drill string may include a stabilizer 203, a seat ring 205 and a drill bit 207, containing a female end 108 with a front end 120, which have improved load efficiency and allowable load, and which can also be resistant to wear, jamming and screwing not thread, as described above in relation to figures 1-4. In other further embodiments, the drill string components 102, 106 may include casing, reamers, core drills, or other drill string components.

[00112] Referring now to FIG. 6, it is illustrated that the drilling system 300 can be used to drill into the formation 304. The drilling system 300 may include a drill string 302 formed from a series of drill rods 204 or other drill string components 201-207. Drill rods 204 may be rigid and / or metallic, or alternatively may be made of other suitable materials. Drill string 302 may comprise a series of connected drill rods that can be assembled sectionally as drill string 302 moves into formation 304. Drill bit 207 (e.g., an open drill bit or other type of drill bit) may be attached to the distal end of drill string 302. When used in the text of this document, the terms “down”, “lower”, “front” and “far end” refer to the end of drill string 302, including drill bit 207. The terms “up”, “upper”, “ the back "or" near "refers to the end of the drill string 302, opposite the drill bit 207.

[00113] The drilling system 300 may include a drilling rig 301 that can rotate and / or advance the drill bit 207, drill rods 204 and / or other parts of the drill string 302 into the formation 304. The drilling rig 301 may include a drive mechanism, for example, a drill head 306 rotary action, the slide assembly 308 and the mast 310. The drill head 306 can be connected to the drill string 302 and can rotate the drill bit 207, drill rods 204 and / or other parts of the drill string 302. If necessary, the rotary drill head 306 can be configured to change the speed and / or direction in which these components rotate. The slide assembly 308 can move with respect to the mast 310. As the slide assembly 308 moves with respect to the mast 310, the slide assembly 308 can provide a force to the rotary drill head 306, which can advance the drill bit 207, drill rods 204 and / or other parts of the drill string 302 further into the formation 304, for example, during their rotation.

[00114] However, it should be appreciated that the drilling rig 301 does not require a rotary drill head, slide assembly, sliding frame, or drive assembly, and that the drilling rig 301 may contain other suitable components. It should also be appreciated that the drilling system 300 does not require a drilling rig, and that the drilling system 300 may contain other suitable components that can rotate and / or advance the drill bit 207, drill rods 204, and / or other parts of the drill string 302 into the formation 304. For example, sonic, shock, or submersible motors may be used.

[00115] As shown in FIG. 6, the drilling system 300 may further comprise a drill rod retainer 312. In more detail, the drive mechanism can advance the drill string 302 and, in particular, the first drill rod 204 until the liner of the first drill rod 204 approaches the wellhead formed by the drill string 302. After the first drill rod 204 reaches the desired of depth, the drill rod retainer 312 can clamp the first drill rod 204, which can help prevent the inadvertent loss of the first drill rod 204 and drill string 302 below the borehole. By clamping the first drill rod 204 with its latch 312, the drive mechanism may be disconnected from the first drill rod 204.

[00116] Then, an additional or second drill rod 204 can be connected to the drive mechanism manually or automatically using a drill rod control device, such as described in US Patent No. 8186925, issued May 29, 2012, the entire contents of which are incorporated herein by links. Then, the drive mechanism may automatically advance the end 104 of the external thread of the second drill rod 204 to the end 108 with the internal thread of the first drill rod 204. The connection between the first 204 and the second drill rod 204 may be threadedly connected to the second 204 with the first drill rod 204. B In light of the description herein, it should be understood that the front ends 114, 120 of the external and internal threads 110, 112 of the drill rods 204 can prevent or reduce non-thread jamming and screwing, even if the connection between the drill rods 204 is made automatically by the drilling rig 301.

[00117] After connecting the second drill rod 204 to the drive mechanism and to the first drill rod 204, the drill rod retainer 312 can release the drill 302. The drive mechanism can push the drill string 302 further into the formation to a greater desired depth. This process of clamping the drill string 302, disconnecting the drive mechanism, connecting the additional drill rod 204, opening the clamp, and moving the drill string 302 to a greater depth can be repeated to go deeper and deeper into the formation.

[00118] Accordingly, Figures 1-Y, the corresponding text, provide a number of different components and mechanisms for creating connections between drill string components with increased load efficiency and load tolerance, and which can also be resistant to abrasion, jamming and screwing not thread. In addition to the foregoing, embodiments of the present invention may also be described in terms of actions and steps in a method for achieving a specific result. For example, a method of creating a connection in a drill string with increased load efficiency and allowable load, as well as resistance to wear, jam and screwing not thread is described below with reference to the components and diagrams of figures 1 to Y inclusive.

[00119] This method may include placing the end 104 with the external thread of the first drill string component 102 at the end 108 with the internal thread of the second drill string component 106. The method may also include rotating the first drill string component 102 with respect to the second drill string component 108. This method may further include end-to-end connection of the flat front end 114 of the external thread 110 at the end 104 with the external thread of the first drill string component 102 with the flat front end 120 of the internal thread 112 at the end 108 with the internal thread of the second drill string component 106.

[00120] The flat front end 114 of the male thread 110 may be oriented at an acute angle 146 with respect to the central axis 26 of the first drill string component 102. Similarly, the flat front end 120 of the internal thread 112 may be oriented at an acute angle 148 with respect to the central axis 26 of the second drill string component 106.

[00121] This method may further include sliding the flat front end 114 of the external thread 110 from and along the flat front end 120 of the internal thread 112 to direct the external thread 110 into the gap between the turns of the internal thread 112. Sliding the flat front end 114 of the external thread 110 from and along the flat front end 120 of the internal thread 112 may cause the first drill string component 102 to rotate with respect to the second 106 due to the sharp angles 146, 148 of the flat front ends 114, 120 of the external and internal threads 110, 112. This method may include automatic rotation and advancing the first drill string component 102 with respect to the second drill string component 106 using the drill rig 301 without manually controlling the drill string components 106, 108.

[00122] The flat front end 120 of the internal thread 112 may extend over the entire depth 132 of the internal thread 110. The flat front end 114 of the external thread 110 may extend over the entire depth 130 of the external thread 110. When the first drill string component 102 rotates with respect to the second component 108 the depth of the drill string of the flat front ends 114, 120 of the inner 112 and the outer thread 110 can prevent jamming or jamming of the outer and inner threads 110, 112.

[00123] Thus, embodiments of the foregoing provide various required parameters. For example, by including front ends or lead-in chamfers, which optionally make up the full width of the thread, thread entry with engagement on the thread run can be eliminated, thereby making it possible to: (a) essentially set the rotation to 360 degrees for the thread; and (b) surface directions to accommodate mating threads in the thread position. For example, an angled chamfer may engage with a corresponding thread or a chamfer of the thread and direct the corresponding thread to the thread position between the screw threads. In addition, in any position of the corresponding threads, the run-out was excluded in order to practically exclude jamming geometry.

[00124] Similar advantages can be obtained regardless of whether the nature of the thread is concentric or eccentric. For example, in an eccentric arrangement, a line intersecting the top of the thread and the entry chamfer of the thread may contain a common cone. When applying, the lead-in chamfer of the thread can mate with the mating thread tip in such a way as to reduce or eliminate jamming at the intersection, and the subsequent thread prevents jamming, jamming and screwing not on the thread. In such an embodiment, a common cone may be sufficient to reduce the outer diameter at the smaller end of the external thread to a diameter that would be smaller than the inner diameter at the large end of the internal thread. Thus, eccentric threads can be used for tapered threads.

[00125] The threads of the present invention can be obtained by any number of suitable methods. For example, as described above, overturning devices, such as lathes, may have problems creating a sharp lead-in chamfer, such as described herein. Accordingly, in some embodiments of the invention, a thread comprising a run can be obtained. Subsequent grinding, milling, or another method can then be used to remove part of the runoff and create a thread run, such as described in this document, or which can be found in the overview description in this document. In other embodiments, other equipment may be used, including combinations of turning and other machining equipment. For example, a lathe can produce part of a thread, while other mechanical equipment can further process a component with an external or internal thread to add a chamfer. In other embodiments of the invention, casting, casting, cutting with a single-blade tool, machining with taps and dies, screw heads, milling, grinding, rolling, lapping or other methods, or any combination of the above, can be used to create threads as described in this document.

[00126] Thus, the present invention can be embodied in other specific forms without departing from its essence or essential characteristics. The described embodiments of the invention should be considered in all respects only as illustrative and non-limiting. Therefore, the scope of this invention is determined by the attached claims, and not by the above description. All changes that fall within the meaning and range of equivalence of the claims should be included in its scope.

Claims (57)

1. A threaded component of the drill string containing: a hollow body having a first end, an opposite second end and a central axis passing through the hollow body; and at least two threads located at the first end of the hollow body; wherein: each of the at least two threads contains a series of screw turns extending along the first end of the hollow body, each of said at least two threads has a thread depression, a thread apex, a thread pitch and a thread width, each of the at least two threads has a negative angle of inclination of the side under pressure, and at least one parameter of the width of the thread and the thread pitch of the specified at least two threads increases from the first value near the front end of at least part of the axial length of the specified row of its helical turns to the final value at the desired point on the specified at least one thread. 2. The component of the drill string according to claim 1, characterized in that at least one parameter of the width and pitch evenly increases from the first value to the final value along the entire axial length of the specified series of helical turns. 3. The component of the drill string according to claim 1, characterized in that at least one parameter from the width and the pitch unevenly increases from the first value to the final value along the entire axial length of the specified series of helical turns. 4. The component of the drill string according to claim 1, characterized in that at least one parameter from the width and the pitch increases from the first value to the final value on the part of the axial length of a series of helical turns and after that remains constant. 5. The component of the drill string according to claim 1, characterized in that the depression of the specified at least one thread describes a cylindrical surface extending along the axial length of the indicated row of its helical turns. 6. The drill string component according to claim 5, characterized in that the apex of said at least one thread describes a truncated cone-shaped surface extending at least on a part of the axial length of the indicated row of its helical turns, and wherein said surface forming in the form The truncated cone is a straight line that lies at an angle with respect to the central axis passing through the hollow body. 7. The drill string component according to claim 1, characterized in that each of said at least two threads further comprises a front end near the first end of the hollow body. 8. The drill string component according to claim 7, characterized in that the front end of each of the at least two threads is oriented at an acute angle with respect to the central axis of the hollow body and faces the first end of the hollow body. 9. The drill string component of claim 8, wherein the front end of said at least one thread comprises a flat surface extending perpendicular to the hollow body. 10. The drill string component according to claim 9, characterized in that the flat surface of the front end of the thread extends over the entire width of the thread. 11. The component of the drill string according to claim 1, characterized in that the corresponding front ends of the specified at least two threads are located at equal distances from the first end of the hollow body. 12. The drill string component according to claim 1, characterized in that the hollow body is a thin-walled body having a wall thickness in the range from about 5 to 15 percent of the outer diameter of the hollow body. 13. The component of the drill string according to claim 1, characterized in that the first end includes an end with an internal thread, while the thread includes an internal thread. 14. The component of the drill string according to claim 1, characterized in that the component of the drill string includes one element of a drill rod, casing, coupler, reamer, drill bit or relief adapter. 15. The drill string component according to claim 1, characterized in that the front end of the thread deviates from the first end of the hollow body by a distance equal to or less than approximately the width of the thread. 16. A threaded component of the drill string containing: at least two threads located at the first end of the hollow body; wherein: each of the at least two threads contains a series of screw turns extending along the first end of the hollow body, each of said at least two threads has a thread depression, a thread apex, a thread pitch and a thread width, each of the at least two threads has a negative angle of inclination of the side under pressure, and the thread depression of said at least one thread describes a cylindrical surface extending along the axial length of said row of its helical turns, and the apex of said at least one thread describes a truncated cone-shaped surface extending at least on a part of the axial length of the indicated row of its helical turns, wherein said truncated-cone shaped surface is a straight line that lies at an angle with respect to the central axis passing through the hollow body. 17. The component of the drill string according to clause 16, characterized in that at least one parameter of the width and thread pitch of the specified at least one thread increases from the first value near the front end at least part of the axial length of the specified row of its helical turns to the final value at the desired point on the specified at least one thread. 18. The component of the drill string according to claim 17, characterized in that at least one parameter from the width and the pitch evenly increases from the first value to the final value along the entire axial length of the specified series of helical turns. 19. The component of the drill string according to claim 17, characterized in that at least one parameter from the width and the pitch unevenly increases from the first value to the final value along the entire axial length of the specified series of helical turns. 20. The component of the drill string according to claim 17, characterized in that at least one parameter from the width and the pitch unevenly increases from the first value to the final value on the part of the axial length of the specified series of helical turns and after that remains constant. 21. The drill string component of claim 16, wherein the front end of said at least one thread comprises a flat surface extending perpendicular to the hollow body. 22. The component of the drill string according to item 21, characterized in that the flat surface of the front end of the thread extends over the entire width of the thread. 23. The drill string component of claim 16, wherein said at least one thread comprises a series of threads. 24. The drill string component according to claim 23, wherein said series of threads includes two threads. 25. The drill string component according to claim 23, wherein the corresponding front ends of said at least two threads are located at equal distances from the first end of the hollow body. 26. The drill string component according to clause 16, wherein the hollow body is a thin-walled body having a wall thickness in the range from about 5 to 10 percent of the outer diameter of the hollow body. 27. The drill string component of claim 16, wherein the first end includes an end with an internal thread, and the thread includes an internal thread. 28. The drill string component according to clause 16, wherein the drill string component includes one element from a drill rod, casing, coupler, reamer, drill bit or relit adapter. 29. The drill string component according to claim 16, characterized in that the front end of the thread deviates from the first end of the hollow body by a distance equal to or less than approximately the width of the thread. 30. A threaded component of the drill string containing: at least two threads located at the first end of the hollow body; wherein: each of the at least two threads contains a series of screw turns extending along the first end of the hollow body, each of said at least two threads has a thread depression, a thread apex, a thread pitch and a thread width, each of these at least two threads has a negative angle of inclination of the side under pressure, comprising from about 20 to about 10 degrees. 31. A threaded component of the drill string, containing: a housing, an end with an internal thread, an opposite end with an external thread, and a central axis passing through the housing; a series of internal threads located at an end with an internal thread of the housing, wherein each of the specified series of internal threads has a hollow of a thread, an apex of a thread, a pitch of a thread, and a width of a thread; a series of external threads located at an end with an external thread of the housing, wherein each of the specified series of external threads has a hollow of a thread, an apex of a thread, a pitch of a thread, and a width of a thread; wherein: each of the specified series of internal and each of the specified series of external threads has a negative angle of inclination of the side under pressure; the depression of each of the specified series of internal and specified series of external threads describes a cylindrical surface extending along the axial length of the specified series of its helical turns, the apex of each of the specified series of internal and specified series of external threads describes a truncated cone-shaped surface extending at least on a part of the axial length of the indicated row of its helical turns, and wherein said truncated-cone shaped surface is a straight line that lies beneath an angle with respect to a central axis passing through the hollow body, and at least one parameter from the width of the thread and the thread pitch of each of the specified series of internal and specified series of external threads increases from the first value near the front end at least part of the axial length of the specified row of its screw turns to the final value at the desired point on each thread from the specified number of threads. 32. The component of the drill string according to p, characterized in that the component of the drill string includes a drill rod. 33. The drill string component of claim 32, wherein the drill rod is hollow and thin-walled.

Images