CA2311156A1

CA2311156A1 - Tubular connection torque reaction ring

Info

Publication number: CA2311156A1
Application number: CA002311156A
Authority: CA
Inventors: Trent Michael Victor Kaiser; Maurice William Slack
Original assignee: Tesco Corp Canada
Current assignee: Tesco Corp Canada
Priority date: 2000-06-09
Filing date: 2000-06-09
Publication date: 2001-12-09
Also published as: NO20025862D0; DE60118555D1; WO2001094830A1; NO336198B1; CA2411122C; DE60118555T2; ATE322642T1; US6899356B2; DK1292791T3; US20040046388A1; AU2001267209A1; CA2411122A1; EP1292791B1; EP1292791A1; NO20025862L

Abstract

A shoulder ring ( 10 ) for installing in the J-space between the installed pin ends within a coupling collar is taught having a body with a central opening therethrough, a first end face ( 12 ) on the body, an opposite end face ( 14 ) on the body, an inner surface ( 16 ) adjacent the central opening and extending between the first end face and the opposite end face and an outer surface ( 18 ) extending between the first end face and the opposite end face, the body having a substantially uniform cross sectional shape between the first end face, the opposite end face, the inner surface and the outer surface and the ring shaped such that its radius to the outer surface varies around the outer surface circumference to form a plurality of lobes ( 12 ).

Description

TUBULAR CONNECTION TORQUE REACTION RING
Field of the Invention Tubulars used to drill and complete bore holes in earth materials are typically joined by threaded connections. Numerous threaded connection geometries are employed to provide sealing and load carrying capacities to meet drilling, installation and operating requirements. Of these geometries, tapered pipe threads are among the simplest and most widely used. The present invention provides a means to substantially increase the ability of such connections to transmit torque.
Background of the Invention Within the context of petroleum drilling and well completion, wells are typically constructed by drilling the well bore using one tubular string, largely comprised of drill pipe, then removing the drill pipe string and completing by installing a second tubular string, referred to as casing, which is subsequently permanently cemented in place. The tubular strings are formed by connecting lengths of pipe, referred to as joints, with threaded connections. With this historic method of well construction, both the drill pipe and casing joint designs are separately optimised for the different performance requirements of the drilling and completion operations respectively. More specifically, the drill pipe connections must accommodate torque required to drill which is not required during completion.
Recent advances in drilling technology have enabled wells to be drilled and completed with a single casing string, eliminating the need to 'trip' the drill pipe in and out of the hole to service the bit and make room for the casing upon completion of drilling. This change is motivated by potential cost savings arising from reduced drilling time and the expense of providing and maintaining the drill string, plus various technical advantages, such as reduced risk of well caving before installation of the casing.
But this use of casing to both drill and complete the well changes the performance requirements of the casing string, and more particularly the torque capacity of the casing connections, from those established through use within the historic methods of well construction. The most widely used of these, are the industry standard threaded and coupled buttress (BTC) and 8-round (LTC or STC) connections having tapered pipe thread geometries specified by the American Petroleum Institute (API). These connections have limited torque capacity and are thus not well suited to the casing drilling application, but are readily available and relatively inexpensive. To more fully realize the potential benefit of this emerging casing drilling system (CDS) technology, it is therefore desirable to find means to press these industry standard connections into service by identifying means to inexpensively increase their torque capacity.
Similar motivations to improve the sealing capacity of connections using API
thread forms, have led to the invention of apparatus and methods such as described in US
patents, US4706997, US4878285, US5263748, US5689871 and US4679831. These patents generally describe inventions where a modified coupling having an internal floating sleeve or seal ring is provided to join pipes having standard API
thread forms on their pin ends. The seal ring is positioned in the so called 'J-section' space between the pin ends of a made-up threaded and coupled connection. The seal ring internal diameter is approximately matched to the internal pipe diameter and is coaxially placed inside the coupling at its mid plane so as to engage both the pin ends when the connection is made up. According to the teachings of these inventions, this engagement or shouldering is primarily intended to enhance the seal performance of the connection beyond that provided by the standard API configuration. Several additional benefits are also obtained, such as improved flow performance and a smooth running bore.
The use of resilient materials in conjunction with the rigid seal ring or as separate seals are also taught as means to further promote sealing.
While these descriptions of the prior art do not explicitly address the utility of such a "convertible metal ring" or seal ring as a means to improve the torque capacity, otherwise available from API connections, the increased torque capacity is a well know benefit. In fact, manufacturers of such connections quantify this parameter in published performance data such as provided by Hunting Oilfield Services for a product described as "the KC Convertible coupling system".
These prior art implementations of rigid seal rings recognise that the wide tolerance variation allowed for the pin and box geometries of threaded and coupled connections

2 meeting API specifications permits a correspondingly wide range of axial position after make up, if a satisfactory level of interference or "dimensional control" is to be achieved (see US patent 5,263,748). Consequently, to obtain satisfactory "dimensional control"
this prior art teaches that additional measures must be taken to reduce the tolerance range of pins and/or boxes provided for use with seal rings and to control the make up position. Such steps include specifically manufacturing "modified boxes" to tighter tolerances than required by API specifications and pre-screening of product manufactured to API tolerances to similarly obtain pins and boxes having more precisely controlled geometry. To ensure controlled placement and retention of the seal ring, it is taught that additional machining of the coupling central thread region is required to form a seat for the seal ring. To obtain dimensional control of the so called mill end make up position, additional fixtures or measurements are required.
However, these measures substantially reduce the benefits of low cost and simplicity originally sought from using existing industry standard couplings and pins.
They are in large part motivated by the desire to upgrade the pressure containment capacity of API
connections and as such are not optimised to obtain upgraded torque capacity desired for casing drilling applications.
Summary of the Invention The present invention was therefore conceived specifically as a means to upgrade the torque capacity of tapered couplings such as, for example, unmodified API
buttress and round threaded and coupled connections, manufactured to industry standard tolerances, to meet the requirements of casing drilling applications.
To be most generally useful for these applications, the torque enhancement device must be amenable to rapid field installation on joints with couplings already bucked on without damaging the connection threads. It must be anchored or securely enough fixed to prevent being dislodged or knocked out from loads arising due to handling and installation operations such as, make up, break out or equipment movement in and out of the open ended casing in the rig floor. Use of the device must not substantially reduce the minimum diameter (drift diameter) through the connection but must be able to carry the maximum axial and torsional loads that can be carried by the pin tips to

3 mobilize the full shouldering potential of the pin ends. To meet these objectives, the method of the present invention provides a multi-lobe torque ring device coaxially placed in the centre of a coupling having internally taper threaded box ends, for example, meeting API specifications. The multi-lobe ring shape is arranged to have alternating radial peaks and valleys around its circumference, so that when placed in a coupling, the peaks interfere with and engage the internal surface of the coupling with sufficient radial force to securely retain the ring in place and coincidentally to largely elastically deform the ring to displace the valleys radially outward. Said multi-lobe ring having upper and lower ends forming torque shoulders against which the pin ends of pipe lengths, made up into the boxes, may bear upon application of sufficient torque across the connection. Thus induced, the bearing forces cause a frictional response on the ring faces and in the threads so as to react additional torque and prevent excess penetration of either pin into the coupling.
The primary purpose of the present invention is to provide a method employing a multi-lobe ring to increase the torque capacity of tubular strings joined by tapered coupling connections, when the ring is placed coaxially in the coupling of the connection, between the pin ends of the joined tubulars. The multi-lobe ring:
~ Preferably made of material similar to the pin ends of the tubulars being joined, ~ Being of generally uniform crossectional shape around its circumference, ~ Having an external circumference substantially similar to the internal circumference of the coupling as defined by the coupling inner diameter, ~ Preferably having an internal circumference slightly less than the internal circumference of the pins and somewhat greater than the specified or otherwise required drift, ~ Having a length sufficient to prevent excess penetration of the pins into their respective boxes preferably by maintaining the made up pin position within the allowable power tight position range such as that specified by API, ~ Being shaped to have its radius vary, preferably in a generally sinusoidal manner, around its circumference to form at least two but preferably three or more lobes thus

4 creating radial peaks and valleys contained within two circles having diameters referred to as the outer peak diameter and inner valley diameter, ~ Preferably having a rough or circumferentially grooved external surface finish, and ~ Having largely flat end faces largely flat to act as torque shoulders.
Thus configured, the multi-lobe ring has reduced effective hoop stiffness and increased elastic range compared to constant radius rings under 'shrink fit' radial loading conditions. In this context, effective hoop stiffness is defined as: change in average radial stress developed on the exterior of a multi-lobe ring caused by a change in radius of a largely cylindrical confining surface (surface having a diameter less than the initial outer peak diameter) divided by said change in radius, i.e., average contact stress increase between a multi-lobe ring and a confining surface per unit decrease in the confining surface radius. Elastic range refers to the range of confining diameters over which the hoop stiffness of a multi-lobe ring is largely constant. It will be apparent to one skilled in the art, that by adjusting the number of lobes, initial outer peak and inner valley diameters, a large range of effective hoop stiffnesses and elastic range can be obtained.
An additional purpose of the present invention is to provide a multi-lobe ring capable of developing sufficient radial gripping force, when installed in a tapered coupling, to substantially resist being dislodged regardless of tolerancing variations in the coupling internal diameter but without requiring the large axial installation loads developed under plastic shrink fit conditions as generally known in spring design. This purpose is realized by exploiting the ability to control the effective hoop stiffness and elastic range of multi-lobe rings by selecting the number of lobes, initial outer peak and inner valley diameters, thickness and material mechanical properties to:
~ Ensure the installed inner diameter cannot fall below the minimum drift diameter required by the application for multi-lobe rings installed in maximum internal diameter couplings, ~ Obtain the maximum gripping force possible for maximum internal diameter couplings without incurring excess installation force for multi-lobe rings installed in minimum diameter couplings, and ~ Preferably without substantially engaging the inelastic hoop response of the ring.
A further purpose of the present invention is to provide a multi-lobe ring capable of providing shoulder seals on its end faces when brought to bear on the pin ends. In a preferred embodiment, this purpose is realized by providing smooth axisymmetric end faces on the ring to facilitate conformable engagement with the pin ends and by application of sufficient torque to cause such conformable engagement to occur.
The multi-lobe ring of the present invention can have any number of lobes, provided that the outer peak diameter is greater than or equal to the diameter of a circle having the same circumference of the multi-lobe ring.
Description of the Preferred Embodiment According to the present invention, a multi-lobe ring is provided for placement in a standard API connection joining two lengths or joints of tubulars. As shown in Figure 1 the multi-lobe ring, 1, is positioned in the centre of, for example, an API
buttress coupling, 2, having internal tapered threads on both ends, which female tapered thread is referred to as a box. As typically employed by industry, one of the coupling boxes is arbitrarily selected for first make up, the so called mill end make up, to an externally end-threaded tubular joint, which male end thread is then referred to as the mill end pin, 3. Correspondingly, the box joined to the mill end pin is referred to as the mill end box and the join itself referred to as the mill end connection. As the name suggests, the mill end make up is commonly conducted at the pipe mill, and the tubulars thus prepared are shipped for eventual field assembly into a string in the well. The second make up required for field assembly, the so called field make up, joins the mill end pin, 3, to the second coupling box, referred to as the field end box, which connection forms the field end connection.
When placed in the centre of a made up coupling, the multi-lobe ring provides shoulders or abutment surfaces on each of its ends, against which the ends of the mill end pin, 3, and field end pin, 4, may bear upon application of sufficient torque applied to complete the field end make up or subsequently during operations employing the string in the well bore to further drill or complete the well or perform other operations. The multi-lobe ring thus transmits load between the pin ends and the bearing load thus created on the pin ends, and reacted in the threads, results in an increased frictional capacity capable of resisting rotation and increasing the torque capacity of the connection.
Simultaneously, if the bearing load is sufficient to cause the pin ends to come into conformable contact with the end faces of the multi-lobe ring, shoulder seals are formed.
While the multi-lobe ring may be installed prior to conducting the mill end make up and anytime immediately prior to stabbing the field end on the rig floor, according to the preferred embodiment of the present invention, the multi-lobe ring, 1, is installed in the coupling after the mill end connection is formed, and prior to assembly on the rig floor.
This method is least intrusive to the existing operational practice, and allows the ring length to be adjusted to accommodate for variations in the mill end make up position from the specified API power tight position. In certain applications, this adjustment may be desirable to control the variation in field end make up shoulder position allowed by the combination of mill end make position and ring length to provide a more satisfactory interference state or "dimensional control" and may be accomplished according to the following teachings.
Variation in power tight position, is referred to as power tight stand off, and is the axial distance from the made up end of the mill end pin, 3, to its power tight plane in the coupling as specified by API. The mill end power tight stand off may be determined in various ways, but is preferably obtained by measuring the distance from the end 30 of the mill end pin, 3, to the face 31 of the coupling field end box, with a suitable instrument such as a caliper, and subtracting one half the coupling length and the specified distance between the centre of coupling and nominal end of pipe power tight planes. (See API Standard 5B, "Specification for Threading, Gauging and Thread Inspection of Casing, Tubing and Line Pipe Threads".) The mill end power tight stand off, thus determined, may be used to adjust the length of the multi-lobe ring prior to installation, to compensate for this stand off and locate the face of the installed multi-lobe ring field end, 12, at or near the power tight plane of the field end box. This adjustment is most easily accomplished by providing a selection of manufactured ring lengths from which to choose during installation.
In its preferred embodiment, the multi-lobe ring of the present invention is formed to have three or more, symmetrically distributed lobes, depending on the effective hoop stiffness required by the application. An end view of a three lobe ring configuration is shown in Figure 2 as it would appear prior to installation in a coupling showing the outer peak diameter (Douter peak). the inner valley diameter (Dinner peak) and the diameter (Dcirc) of a circle whose circumference equals that of the ring external circumference.
The diameter Dcirc is chosen to be nearly the same as the minimum coupling diameter in with the rings are to be installed. Installation is accomplished by placing the ring in the open box end of a coupling and pushing it toward the coupling centre as the external lobe peaks come into contact with the box threads and develop radial bearing forces as the outer peak diameter of the ring is reduced as confined by the decreasing diameter of the tapered box.
Various means may be employed to position the ring in the coupling centre including simply pushing the ring into an open box by hand and allowing the pin end to displace it toward centre during make up. However in its preferred embodiment, a hydraulic installation device is provided as shown in Figure 3, comprised of a single acting hydraulic actuator, 5, which may be pressured by suitable means through its pressure port, 6. The piston, 7, of the hydraulic actuator, 5, is attached to a load plate, 8, configured to engage and apply a force to the end face of the multi-lobe ring, 1, located in an open box end of coupling, 2, pushing it toward the coupling centre. The frictional forces developed between the ring and box are reacted through the coupling body to the threaded plate, 9, threaded into the end of the coupling box on its exterior and coaxially attached to the ram at its centre bore, which completes the load reaction into the ram body. (This device may also be used to remove installed rings in couplings with both pins removed, should this be required for repair or other purposes.) The installation means provided by this device is readily deployed in settings such as pipe yards and rig sites where the tubulars are stored on pipe racks. The threaded plate, 9, is readily threaded into the exposed box end on the pipe rack and centrally positions the device to ensure accurate and controlled installation.
Sufficient hydraulic power may be easily obtained with electric or pneumatically powered pumps enabling rapid installation of the multi-lobe rings.
An end cross sectional view of a multi-lobe ring, with initial shape shown in Figure 2, is shown in Figure 4 as it would appear installed in the coupling centre. (For illustration purposes, the initial amplitude of the lobes and the final gap between the lobe exterior valleys and the coupling inside surface have been exaggerated in these two figures.) By comparison between these two figures, it will be evident that while the circumference of the ring is largely unchanged, the radial forces developed by installation cause the outer peak diameter (Douter peak) to decrease and the inner valley diameter (Dinner peak) to increase.
The largely flexural stresses arising from this deformation mode give rise to the reduced effective hoop stiffness sought by the multi-lobe ring design with consequent increase in radial elastic range compared to a constant radius ring shape. The effective hoop stiffness and elastic range may be adjusted by selecting the number of lobes, initial outer peak and inner valley diameters, thickness and material mechanical properties.
The response obtained for a given ring design may be obtained by various stress analysis techniques such as the finite element method (FEM) or by experiment.
The range of diameters allowed at the centre of couplings manufactured to API
specifications is large compared to the available elastic range of constant radius steel rings, but is readily accommodated by multi-lobe rings having three or more lobes while simultaneously controlling the average radial stress to balance installation load against gripping force.
Lobe shapes may created using numerous manufacturing methods. It was found that forming by application of external radial displacement, sufficient to permanently deform the rings, provided satisfactory control.
In the preferred embodiment, the effective frictional capacity or gripping force obtained for a given average radial stress is increased by providing the rings with a roughened or serrated external surface 10, as shown in Figure 5, created by placing circumferential machining grooves in the ring exterior surface, prior to forming the lobes.
Various surface finish profiles may be used however the simple V-shape shown proved to provide substantially increased effective friction coefficients from that obtained with smooth surfaces and is economic to manufacture.
With reference to Figure 5. as a further means to improve the gripping force of the multi-lobe ring, in its preferred embodiment the ring is formed to follow the coupling taper on the outer surface of its field end 12. In particular, to facilitate installation into a coupling the mill end 11 of the multi-lobe ring is formed generally of uniform thickness. At about half the length of the ring, the ring thickness is gradually increased with the field end of the ring generally having a frusto-conical outer surface substantially matching the taper of the coupling. Thus, when the ring is properly installed in a tapered coupling, the field end of the ring is in contact with the threads of the coupling. The inner surface remains generally linear along the entire ring. This refinement accommodates installation of the muli-lobe ring mill end past the minimum coupling centre diameter but provides more conformable contact between the multi-lobe ring field end, 12 and the coupling field end box.
Alternate Embodiments In another aspect of the preferred embodiment, we believe an increase in torque capacity may be gained, particularly for API connections of thinner wall tubulars, by providing conically convex profiled faces on the ends of the multi-lobe rings which conical profile may be uniform may be increasingly conical toward the inner edge of the ring face. By thus providing a reverse angled shoulder on which the pin end bears when reacting torque, the pin end will tend to be prevented from sliding inward under application of high load thus further increasing the torque capacity of the connection.
In another aspect of the preferred embodiment, we believe providing multi-lobe rings with roughened end surfaces will increase the effective friction coefficient of the shoulders and thus increase the connection torque capacity possibly at the expense of shoulder seal capacity. The roughening may be provided in various ways such as knurling or machining of directional teeth and may be provided in combination with hardening.

As an alternative embodiment, the multi-lobe rings may be formed to have lobes of non-symmetric shape. We believe such variations in shape may be exploited as a another means to control the effective hoop stiffness and elastic range to further optimize the gripping capacity of the ring.