The present disclosure relates, in some embodiments, to shear couplings in downhole or subsurface oil pumping strings (“sucker rod strings”) to provide a specific, controlled point of failure to protect the other elements of the sucker rod string from damage, including in sucker rod pumping systems.
Upon completion of drilling an oil well, fluids from the oil well may be under sufficient innate or natural pressure to allow the oil well to produce on its own. Therefore, crude oil in such wells can rise to the well surface without any assistance. But, even though an oil well can initially produce on its own, natural pressure generally declines as the well ages. In many oil wells, therefore, fluids are artificially lifted to the surface with downhole or subsurface pumps. Sucker rod pump systems are commonly used systems to transport these fluids from downhole oil-bearing zones to the well surface to be collected, refined, and used for various applications.
Typical sucker rod pump systems have a plunger that reciprocates inside a barrel while attached at the end of a string of sucker rods. A prime mover, such as a gasoline or diesel engine, or an electric motor, or a gas engine, on the surface causes a pump jack to rock back and forth, thereby moving the string of sucker rods up and down inside of the well tubing.
Either because of wear or other environmental factors, when the string sucker rods encounters resistance to movement, one or more elements within the string can become damaged/overstressed. When that happens, it often results in rupture of expensive equipment and downtime, as it may be required to extract the entire rod string out of the ground for repair. And this repair time also causes expensive downtime from production.
It is known to use a shear coupling in sucker rod systems, where the shear coupling provides a controlled and predictable point of failure, including in a rotating sucker rod pump where the rod string is regularly rotated about the axis of the longitudinal pumping motion in order to make the wear more uniform. Without using a shear coupling or shear pin of some type, with all the pieces of a sucker rod string being independently designed to their maximum strength, the point of failure is unpredictable, making recovery from a failure event even more difficult.
Disclosed are embodiments of shear couplings that provide improved performance characteristics over prior art approaches. In particular, it is desired to have a shear coupling that ruptures within its design tolerance. If it fails to rupture when intended, then it risks damage to the other elements of the rod string assembly, longer and costlier workover jobs, and a potential environmental hazard by the spillage of well fluids while pulling tubing out of the well. If it ruptures too easily, it causes needless downtime under a stress condition that would not have been a danger to the remainder of the rod string assembly. It is further desired to have a rod string that has an extended fatigue life provided its working load is not exceeded. It is still further desired that the shear couplings have stable threaded connections so that they remain securely engaged.
Disclosed embodiments of the present application include a shear pin configured to threadably connect within a shear coupling and to provide a point of failure for a sucker rod string, the shear pin including (a) a cylindrical shape positioned along a vertical axis having a first end positioned at a top of the vertical axis and a second end positioned at a bottom of the vertical axis and having a curved portion connecting the first end to the second end. The shear pin may include (b) the first end having a common diameter with the second end and containing: (i) a set of first threads on an outer circumference of the first end, the set of first threads having a first handedness and configured to threadably connect within the shear coupling; and (ii) a first clutch at a point along the vertical axis that is furthest from the second end, the first clutch containing one of a recessing shape and a protruding shape. The shear pin may include (c) the second end that may contain (i) a set of second threads on an outer circumference of the second end, the set of second threads having an opposite handedness from the set of first threads and configured to threadably connect within the shear coupling; and (ii) a second clutch at a point along the vertical axis that is furthest from the first end, the second clutch containing one of a recessing shape and a protruding shape. The shear pin may contain (d) a curved portion including a diameter that is largest where the curved portion connects to each of the first end and the second end and then narrows along the curved portion, forming a curve that culminates at a neck where the diameter is smallest.
In some embodiments, the present disclosure relates to a shear pin configured to threadably connect within a shear coupling and to provide a point of failure for a sucker rod string. The shear pin may include a cylindrical shape positioned along a vertical axis having a first end positioned at a top of the vertical axis and a second end positioned at a bottom of the vertical axis and having a curved portion connecting the first end to the second end. The shear pin may include the first end having a common diameter with the second end and containing (i) a set of first threads on an outer circumference of the first end, the set of first threads having a first handedness and configured to threadably connect within the shear coupling; and (ii) a first clutch at a point along the vertical axis that is furthest from the second end, the first clutch containing one of a recessing shape and a protruding shape. The second end may include a set of second threads on an outer circumference of the second end, the set of second threads having an opposite handedness from the set of first threads and configured to threadably connect within the shear coupling. The curved portion may include a diameter that is largest where the curved portion connects to each of the first end and the second end and then narrows along the curved portion, forming a curve that culminates at a neck where the diameter is smallest. The ratio of a curvature radius of the curve to the diameter of the neck ranges from about 2 to about 10.
The present disclosure relates to a shear coupling configured to provide a point of failure for a sucker rod string, the shear coupling including a first sleeve containing a substantially cylindrical and hollow body, the first sleeve further containing a first sleeve upper end containing threads around an inner circumference of the first sleeve upper end, the first sleeve configured to internally receive and threadably couple to a sucker rod. The first sleeve may also contain a first sleeve lower end connected to the first sleeve upper end through a first sleeve body, the first sleeve lower end containing threads around an inner circumference of the second sleeve lower end that are separated from the threads of the first sleeve upper end by a gap and configured to internally receive and threadably couple to a shear pin. The shear pin may include a cylindrical shape positioned along a vertical axis having a first end positioned at a top of the vertical axis and a second end positioned at a bottom of the vertical axis and having a curved portion connecting the first end to the second end, the first end having a common diameter with the second end and including a set of first threads on an outer circumference of the first end, the set of first threads having a first handedness and configured to threadably connect within the shear coupling, and a first clutch at a point along the vertical axis that is furthest from the second end, the first clutch containing one of a recessing shape and a protruding shape. The shear pin may include the second end that contains a set of second threads on an outer circumference of the second end, the set of second threads having an opposite handedness from the set of first threads and configured to threadably connect within the shear coupling, and a second clutch at a point along the vertical axis that is furthest from the first end, the second clutch containing one of a recessing shape and a protruding shape. The shear pin may include the curved portion containing a diameter that is largest where the curved portion connects to each of the first end and the second end and then narrows along the curved portion, forming a curve that culminates at a neck where the diameter is smallest.
A shear coupling may include a second sleeve containing a substantially cylindrical and hollow body, the second sleeve further including a second sleeve lower end comprising threads around an inner circumference of the second sleeve lower end, the second sleeve configured to internally receive and threadably couple to a sucker rod, and a second sleeve upper end connected to the second sleeve lower end through a second sleeve body, the second sleeve upper end comprising threads around an inner circumference of the second sleeve upper end that are separated from the threads of the second sleeve lower end by a gap and configured to internally receive and threadably couple to the shear pin. The shear coupling may include a chamber located in between an inner surface of each of the hollow bodies of the first sleeve and the second sleeve and an outer surface of the shear pin, wherein the hollow chamber is filled with one of an epoxy, a corrosive resistant thermoset single polymer, and a corrosive resistant thermoset cross linked polymer.
A shear coupling may include a first sleeve lower end and a first sleeve upper end. The first sleeve lower end may include teeth at a point along a vertical axis that is furthest from the first sleeve upper end and extending away from the first sleeve upper end and the second sleeve upper end further may include teeth at a point along the vertical axis that is furthest from the second sleeve lower end and extending away from the second sleeve lower end. The teeth of the first sleeve lower end are configured to engage the teeth of the second sleeve upper end and the secure the first sleeve and the second sleeve from relative rotational movement, wherein the teeth are further configured to provide for a rupture torque of the shear coupling that ranges from about 500 foot-pounds to about 5000 foot-pounds. The first sleeve lower end may include a protruding hex locking engagement at a point along the vertical axis that is furthest from the first sleeve upper end and extending out of the first sleeve lower end in a direction away from the first sleeve upper end, wherein the second sleeve upper end further comprises a recessing hex locking engagement at a point along the vertical axis that is furthest away from the second sleeve lower end and recessing into the second sleeve upper end in a direction towards the second sleeve lower end, and wherein the protruding hex locking engagement and the recessing hex locking engagement secure the first sleeve and the second sleeve from relative rotational movement. The first sleeve lower end may include a recessing hex locking engagement at a point along the vertical axis that is furthest from the first sleeve upper end and recessing into the first sleeve lower end in a direction towards the first sleeve upper end, where the second sleeve upper end further comprises a protruding hex locking engagement at a point along the vertical axis that is furthest away from the second sleeve lower end and protruding away from the second sleeve lower end in a direction away from the second sleeve lower end. In some embodiments, the recessing hex locking engagement and the protruding hex locking engagement secure the first sleeve and the second sleeve from relative rotational movement.
A shear pin may include a ratio of a curvature radius of the curve to the diameter of the neck ranges from about 2 to about 10. The shear pin may have a diameter of the neck ranging from about 0.25 inches to about 1.25 inches. The shear pin may have a stress safety factor of lower than 1.10. A shear pin may have a rupture load ranging from about 5,000 pounds to about 70,000 pounds. The shear pin may have a first clutch or a second clutch, where each of the first clutch and second clutch may have a recessing shape or a protruding shape. The recessing shape of the first clutch contains one of a triangular-shaped cross-section, a cross-shaped cross-section, a three-arm-shaped cross-section, a hex-shaped cross-section, a star-shaped cross-section, a square-shaped cross-section, and a polygon-shaped cross-section. The protruding shape of the first clutch contains one of a triangular-shaped cross-section, a cross-shaped cross-section, a three-arm-shaped cross-section, a hex-shaped cross-section, a star-shaped cross-section, a square-shaped cross-section, and a polygon-shaped cross-section. The recessing shape of the second clutch contains one of a triangular-shaped cross-section, a cross-shaped cross-section, a three-arm-shaped cross-section, a hex-shaped cross-section, a star-shaped cross-section, a square-shaped cross-section, and a polygon shaped-cross-section. The protruding shape of the second clutch contains one of a triangular-shaped cross-section, a cross-shaped cross-section, a three-arm-shaped cross-section, a hex-shaped cross-section, a star-shaped cross-section, a square-shaped cross-section, and a polygon-shaped cross-section. A first clutch may have a protruding shape while a second clutch may have a protruding shape. The first clutch may have a recessing shape while the second clutch may have a protruding shape. The first clutch may have a protruding shape while the second clutch may have a recessing shape. The first clutch may have a recessing shape while the second clutch may have a recessing shape.
In some embodiments, the present disclosure relates to a method for assembling a shear coupling configured to provide a point of failure for a sucker rod string, the method including securing a first sleeve to a first non-rotating shaft by passing the first non-rotating shaft through a hollow body of the first sleeve until a first mechanical coupler of the first non-rotating shaft is exposed through an end of the first sleeve. The method may also include securing a second sleeve to a second non-rotating shaft by passing the second non-rotating shaft through a hollow body of the second sleeve until a second mechanical coupler of the second non-rotating shaft is exposed through an end of the second sleeve, wherein the first sleeve, the first non-rotating shaft, the second sleeve, and the second rotating shaft are all aligned along a horizontal axis. The method may include coupling a first end of a shear pin to the first mechanical coupler of the first non-rotating shaft, wherein the first end of the shear pin comprises a set of first threads on an outer circumference of the first end, and wherein the first threads have a first handedness configured to threadably connect within the shear coupling. The method may include coupling a second end of the shear pin to the second mechanical coupler of the second non-rotating shaft, wherein the second end of the shear pin comprises a set of second threads on an outer circumference of the second end having an opposite handedness from the set of first threads and configured to threadably connect within the shear coupling. The method may include applying a thread locker on a surface of each of the set of first threads and set of second threads and rotating the first sleeve about the horizontal axis so that the first set of threads is threaded inside the first sleeve while rotating the second sleeve about the horizontal axis so that the second set of threads is threaded inside the second sleeve until the first sleeve and the second sleeve meet at a center point along a horizontal axis of the shear pin, thereby forming an assembled shear coupling. The method may include engaging teeth of the first sleeve with teeth of the second sleeve, thereby securing the first sleeve and the second sleeve from relative rotational movement, wherein the teeth on each of the first sleeve and the second sleeve are oriented toward each other.
A method for assembling a shear coupling may include positioning a wrench on a flat on each of the first sleeve and a second sleeve; adjusting an orientation of a head on the wrench until a bar of the wrench is aligned with the horizontal axis; and applying a first low preload torque of about 10% to about 20% of a shear pin yield stress strength on the bar of the wrench until the wrench makes a clicking sound. The method for assembling the shear coupling may include releasing the first torque on the bar without removing the wrench; applying a second preload torque of about 70% of the shear pin yield stress strength on the bar of the wrench; and removing the shear coupling from each of the first non-rotating shaft and the second non-rotating shaft. In some embodiments, the first sleeve and the second sleeve each comprise a perforation on each of their respective ends that are oriented toward each other. The shear coupling may include a hollow chamber located in between an inner surface of each of the hollow bodies of the first sleeve and the second sleeve and an outer surface of the shear pin. The method for assembling the shear coupling may include applying a polymer to at least one perforation of the first sleeve and the second sleeve, thereby filling the hollow chamber to form a polymer filled chamber comprising the applied polymer, wherein the polymer comprises an epoxy, a corrosive resistant thermoset single polymer, and a corrosive resistant thermoset cross linked polymer.
A subsurface pump 21 is located in the tubing 19 at or near the formation 15. A string 23 of sucker rods extends from the pump 21 up inside of the tubing 19 to a polished rod and a stuffing box 25 on the surface 13. The sucker rod string 23 is connected to a pump jack unit, or beam pump unit 24, which reciprocates up and down due to a prime mover 26, such as an electric motor or gasoline or diesel engine, or gas engine. The sucker rod string 23 typically consists of a series of fixed-length straight rods joined together by couplings 35. The sucker rod string may as well comprise a continuous metal or fiber-glass string running uninterrupted from the surface 13 down to a depth near that of the pump, and including other elements such as guides, sinker-bars, or pony-rods, among others.
The rod string may include one or multiple shear-couplings 45 to provide a known point of failure to protect surface and downhole assets in the event of overstresses during the operation or handling of the sucker rod string 23/pump 21 assembly. The shear coupling is typically installed at the bottom of the sucker rod string (nearest to the pump 21); additionally, there may sometimes be a shear coupling placed at the top of the sucker rod string (farthest from the pump) or at another locations dependent upon design needs.
Shear couplings may be utilized in other forms of artificial lift (not shown in
The nature and magnitude of the stresses overseen by the rod string in a progressive cavity application, however, differs from those in a rod pumping application; while axial stresses induced by the weight of the hydrostatic column of fluid above the pump may be similar in magnitude in both, shear stress from torque transmission exclusively impacts progressive cavity applications.
Hereafter, the term rod string alludes to both types of artificial lift systems; reciprocating rod-pumping systems as well as rotational progressive cavity applications. Furthermore, the rod string, including shear couplings or any other subcomponent, are presumed to be simultaneously under axial and torsional load.
When a pump becomes stuck downhole, the actuation of the shear coupling allows the workover crew to pull the rods and the tubing separately in a considerably faster and safer manner, reducing the cost and the risk to the operators intrinsically associated with the pulling job. Furthermore, given the tubing may be abnormally charged with well fluids, the actuation of the shear coupling facilitates the containment of the said fluids in the surface preventing a potential spillage at the wellhead. The actuation of the shear-coupling is a last resource action aimed at protecting company assets, minimizing downtime, and preventing a potential oil spillage at the well.
A shear pin may have a ratio of a curvature radius of the curve to the diameter of the neck that ranges from about 2 to about 10. A ratio of a curvature of radius of the curve to the diameter of the neck may be about 2, or about 3, or about 4, or about 5, or about 6, or about 7, or about 8, or about 9, or about 10, where about includes plus or minus 0.5. A shear pin may have a diameter of a neck that ranges from about 0.25 inches to about 1.25 inches. A shear pin may have a diameter of a neck of about 0.25 inches, or about 0.50 inches, or about 0.75 inches, or about 1.00 inch, or about 1.25 inches, where about includes plus or minus 0.125 inches. A shear pin may have a stress safety factor of lower than about 1.50. A shear pin may have a stress safety factor of lower than about 1.10. A shear pin may have a stress safety factor ranging from about 0.10 to about 1.50. A shear pin may have a stress safety factor of about 0.10, or about 0.20, or about 0.30, or about 0.40, or about 0.50, or about 0.60, or about 0.70, or about 0.80, or about 0.90, or about 1.00, or about 1.10, or about 1.20, or about 1.30, or about 1.40, or about 1.50, where about includes plus or minus 0.05. A shear pin may have a rupture load ranging from about 5,000 pounds to about 70,000 pounds. A shear pin may have a rupture load of about 5,000 pounds, or about 10,000 pounds, or about 15,000 pounds, or about 20,000 pounds, or about 25,000 pounds, or about 30,000 pounds, or about 35,000 pounds, or about 40,000 pounds, or about 45,000 pounds, or about 50,000 pounds, or about 55,000 pounds, or about 60,000 pounds, or about 65,000 pounds, or about 70,000 pounds, or about 75,000 pounds, where about includes plus or minus 2,500 pounds.
As illustrated in the embodiment of
The profiled neck of the curved portion 410 in embodiments disclosed herein is a smooth curve, either analytic or discrete, or a combination of both in a piecewise defined function. For analytic curves, the neck, or sections of it, may follow a polynomial curve of order 2 or higher, as well as other standard curves such as power, exponential, logarithmic, or trigonometric functions such as sine, cosine, or tangent. Likewise, linear or non-linear, implicit or explicit combinations of the aforementioned functions may be included, including hyperboles, ellipses, parabolas, or circles in which the ratio of the local radius of curvature R in the stress-focus region 440,550 to the neck diameter D is >=4.
As the two sleeves 502,504 are brought into engagement, the teeth 520 of one sleeve are aligned with the corresponding mounts 530 in the other sleeve 504 preventing any relative rotational movement between the two sleeves 502, 504 around the coaxial axis between them, this allows a fully seated engagement between sleeves 502,504. At this time, the torque (τ1 and τ2) continues to be applied substantially equally to the clutches 480 at each end of the shear pin 500 to “pre-load” a tension on the engagement between the shear pin 500 and the sleeves 502,504. That pre-load amounts to a purely axial tensile stress that is applied and held between the sleeves 502,504 and the shear pin 500, and this pre-loaded tensile stress is distributed nearly evenly across the stress-focus region 550.
In some embodiments, a shear coupling 510 may be configured to provide a point of failure for a sucker rod string and may include a first sleeve 502 containing a substantially cylindrical and hollow body. A first sleeve 502 may include a first sleeve upper end and containing threads around an inner circumference of the first sleeve upper end, the first sleeve configured to internally receive and threadably couple to a sucker rod. A first sleeve 502 may include a first sleeve lower end connected to the first sleeve upper end through a first sleeve body, the first sleeve lower end containing threads around an inner circumference of the second sleeve lower end that are separated from the threads of the first sleeve upper end by a gap and configured to internally receive and threadably couple to the shear pin. A shear coupling may include a second sleeve containing a substantially cylindrical and hollow body, the second sleeve including a second sleeve lower end having threads around an inner circumference of the second sleeve lower and, the second sleeve configured to internally receive and threadably couple to a sucker rod. The second sleeve may include a second sleeve upper end connected to the second sleeve lower end through a second sleeve body, the second sleeve upper end may include threads around an inner circumference of the second sleeve upper end that are separated from the threads of the second sleeve lower end by a gap and configured to internally receive and threadably couple to the shear pin. A shear coupling may include a chamber located in between an inner surface of each of the hollow bodies of the first sleeve and the second sleeve and an outer surface of the shear pin, wherein the hollow chamber is filled with one of an epoxy, a corrosive resistant thermoset single polymer, and a corrosive resistant thermoset cross linked polymer.
In prior art implementations of shear pins where the “one-sided” assembly and pre-loading is performed by a clutch at a single side, those pre-load stresses are applied asymmetrically, which results in torque failures during the pre-loading assembly process. Further in the prior art, the asymmetry of pre-load stress can cause fatigue failures during operation outside of the originally intended shear pin rupturing parameters.
The pre-load in assembled shear couplings is defined as a percentage of the design rupture load, and it can be up to 70% of the specific rupture load of a specific configuration. Since shear couplings are manufactured to different rupture loads, the assembly pre-load will vary accordingly following proprietary correlations, not to exceed 70% of the rupture load. For example, a shear coupling made to rupture at 21,000 lbs, may be pre-loaded up to 14,700 lbs during assembly, and a shear coupling made to rupture at 50,000 lbs may be pre-loaded up to 35,000 lbs. The target pre-load is calculated based on the rupture load. The rupture load as referred to in the context of shear-couplings corresponds to the maximum pure axial load the shear-pin may withstand under static conditions.
Note that the target pre-load needed to reach 70% of the rupture load of the shear-pin is not attainable unless the torque is applied symmetrically from both ends of the shear-pin, thereby exhibiting the synergy between the applied pre-load and the torque-balanced assembly method subject of the present disclosure. A one-sided or a highly asymmetrical application of the pre-load on the shear-pin will result in an unbalanced torque at the rupture neck of the pin, leading to a shear-pin failure should the shear-stress at the neck exceeds the maximum shear strength of the section. Even if the application of an asymmetrical torque does not yield to the immediate rupture of the shear-pin during assembly, it may still irreversibly damage the part by inducing micro-cracks in the neck of the shear pin, which will act as initiation points for fatigue cracks to propagate reducing the fatigue life of the assembly. As a reference, when torqued unilaterally, shear-pins as disclosed in the present disclosure rupture due to shear-stress upon reaching 60% of the axial design rupture load.
Thus, using the described embodiments and assembly techniques, an improved shear coupling is provided that can provide for increased pre-load, reducing alternating stress (Sa) during pump operation, and thereby increasing fatigue life of the shear coupling. Increasing the pre-load further strengthens the threaded connection of the shear pin into the first and second sleeves, making the threaded engagement between the shear pin and first and second sleeves less susceptible to backing off. Further, again because of the greater stress pre-load, the integrity of the assembly becomes less reliant on using a thread locker to keep the shear pin engaged in the sleeves. This is further advantageous because thread locker compounds can be prone to failure at high temperature operating conditions.
As further described, the improved stress-focus zone design provides a reduction in stress concentration and thereby reduces fatigue load and accordingly lessens stress fatigue, reducing fatigue-related failure. The stress concentration, and accordingly the safety factor, is increased by up to 24% relative to prior known designs not using the described RID ratio and constant curve approaches described herein.
As still further described above, the two-sided shear coupling and shear pin designs allow for a greatly reduced (to less than 1% or less) residual shear-stress after assembly and provides for a reduced or eliminated risk of induced cracks during assembly pre-loading of the shear coupling. Following are a number of additional embodiments, but the foregoing design advantages are applicable to all of these additional embodiments.
In this embodiment, there are provided two teeth 720 and the first sleeve 702 that engage with two mounts 730. The embodiment also illustrates a triangular female clutch 780, which while illustrated on one side of the shear pin 700 in
A shear pin 1600 may include a first clutch and a second clutch that may each contain one of a triangular-shaped cross-section, a cross-shaped cross-section, a three-arm-shaped cross-section, a hex-shaped cross-section, a star-shaped cross-section, a square-shaped cross-section, and a polygon-shaped cross-section. In some embodiments, a shear pin 1600 may include a first clutch and a second clutch that may each include one of a protruding shape and a recessing shape.
Disclosed shear pins may incorporate anyone of the clutching features exemplified in
As shown in
In some embodiments, assembling a shear coupling may include engaging teeth of a first sleeve with teeth of a second sleeve, thereby securing the first sleeve and the second sleeve from relative rotational movement. Teeth on each of the first sleeve and the second sleeve may be oriented toward each other. Assembling a shear coupling may include positioning a wrench on a flat on each of the first sleeve and a second sleeve, adjusting an orientation of a head on the wrench until a bar of the wrench is aligned with the horizontal axis, and applying a first low preload torque of about 10% to about 20% of a shear pin yield stress strength on the bar of the wrench until the wrench makes a clicking sound.
In some embodiments, a method for assembling a shear coupling may include releasing a first torque on the bar without removing the wrench; applying a second preload torque of about 70% of the shear pin yield stress strength on the bar of the wrench and removing the shear coupling from each of the first non-rotating shaft and the second non-rotating shaft.
The above embodiments are described as specific embodiments and should not be used to limit the scope of the claims, although it should be appreciated that there are synergies in providing a combination of claimed features as disclosed in the embodiments of this specification. For example, use of the disclosed and/or claimed stress-zone designs can be synergistically combined with two-sided assembly structures and techniques disclosed herein to minimize or eliminate torque assembly damages, voids, and/or discontinuities in metallurgical properties. The synergistic combination of these elements further provides for a finally assembled shear coupling that has a higher pre-load applied and that provides for better thread engaging of the shear coupling with the other elements of a rod string and provides for an improved shear coupling that is less susceptible to operational fatigue.
Where the verb “may” appears, it is intended to convey an optional and/or permissive condition, but its use is not intended to suggest any lack of operability unless otherwise indicated. Where open terms such as “having” or “comprising” are used, one of ordinary skill in the art having the benefit of the instant disclosure will appreciate that the disclosed features or steps optionally may be combined with additional features or steps. Such option may not be exercised and, indeed, in some embodiments, disclosed systems, compositions, apparatuses, and/or methods may exclude any other features or steps beyond those disclosed herein. Persons skilled in the art may make various changes in the systems of the disclosure.
Also, where ranges have been provided, the disclosed endpoints may be treated as exact and/or approximations as desired or demanded by the particular embodiment. Where the endpoints are approximate, the degree of flexibility may vary in proportion to the order of magnitude of the range. For example, on one hand, a range endpoint of about 50 in the context of a range of about 5 to about 50 may include 50.5, but not 52.5 or 55 and, on the other hand, a range endpoint of about 50 in the context of a range of about 0.5 to about 50 may include 55, but not 60 or 75. In addition, it may be desirable, in some embodiments, to mix and match range endpoints. Also, in some embodiments, each figure disclosed (e.g., in one or more of the examples, tables, and/or drawings) may form the basis of a range (e.g., depicted value +/− about 10%, depicted value +/− about 50%, depicted value +/− about 100%) and/or a range endpoint. With respect to the former, a value of 50 depicted in an example, table, and/or drawing may form the basis of a range of, for example, about 45 to about 55, about 25 to about 100, and/or about 0 to about 100. Disclosed percentages are weight percentages except where indicated otherwise.
All or a portion of a device and/or system for rod string shear couplings may be configured and arranged to be disposable, serviceable, interchangeable, and/or replaceable. These equivalents and alternatives along with obvious changes and modifications are intended to be included within the scope of the present disclosure. Accordingly, the foregoing disclosure is intended to be illustrative, but not limiting, of the scope of the disclosure.
This application claims priority to U.S. Provisional Application No. 63/156,835, filed on Mar. 4, 2021, which is incorporated by reference herein in its entirety for all purposes.
Number | Name | Date | Kind |
---|---|---|---|
3329450 | Current | Jul 1967 | A |
4411546 | Fischer | Oct 1983 | A |
4459060 | Patterson | Jul 1984 | A |
20090271966 | Fotty | Nov 2009 | A1 |
20110150596 | Wolodko et al. | Jun 2011 | A1 |
20150030374 | Lea-Wilson et al. | Jan 2015 | A1 |
20150368989 | Lauder et al. | Dec 2015 | A1 |
20170356252 | Wollmann et al. | Dec 2017 | A1 |
Number | Date | Country |
---|---|---|
1020100059330 | Jun 2010 | KR |
Entry |
---|
International Written Opinion for PCT/US2021/063349, dated Apr. 11, 2022, 6 pages. |
International Search Report for PCT/US2021/063349, dated Apr. 11, 2022, 4 pages. |
Number | Date | Country | |
---|---|---|---|
20220282579 A1 | Sep 2022 | US |
Number | Date | Country | |
---|---|---|---|
63156835 | Mar 2021 | US |