TORQUE SUB FOR USE WITH TOP DRIVE

Abstract

Embodiments of the present invention generally relate to a torque sub for use with a top drive. In one embodiment a method of connecting threaded tubular members for use in a wellbore is disclosed. The method includes operating a top drive, thereby rotating a first threaded tubular member relative to a second threaded tubular member; measuring a torque exerted on the first tubular member by the top drive, wherein the torque is measured using a torque shaft rotationally coupled to the top drive and the first tubular, the torque shaft having a strain gage disposed thereon; wirelessly transmitting the measured torque from the torque shaft to a stationary interface; measuring rotation of the first tubular member; determining acceptability of the threaded connection; and stopping rotation of the first threaded member when the threaded connection is complete or if the threaded connection is unacceptable.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

So that the manner in which the above recited features of the present invention can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to embodiments, some of which are illustrated in the appended drawings. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments.

FIG. 1A is a side view of a prior art drilling rig having a top drive and an elevator. FIG. 1B is a side view of a prior art drilling rig having a top drive, an elevator, and a spider. FIG. 1C illustrates a side view of a top drive engaged to a tubular, which has been lowered through a spider.

FIG. 2A is a cross-sectional view of a spear, for coupling a top drive and a tubular, in a disengaged position. FIG. 2B is a cross-sectional view of a spear, for coupling a top drive and a tubular, in an engaged position.

FIG. 3 is a cross-sectional view of a prior art torque head. FIGS. 3A-B are isometric views of a prior art jaw for the torque head of FIG. 3.

FIG. 4A is a partial cross section view of a connection between threaded premium grade members. FIG. 4B is a partial cross section view of a connection between threaded premium grade members in which a seal condition is formed by engagement between sealing surfaces. FIG. 4C is a partial cross section view of a connection between threaded premium grade members in which a shoulder condition is formed by engagement between shoulder surfaces.

FIG. 5A is a plot of torque with respect to turns for a premium tubular connection. FIG. 5B is a plot of the rate of change in torque with respect to turns for a premium tubular connection.

FIG. 6 is an isometric view of a torque sub, according to one embodiment of the present invention. FIG. 6A is a side view of a torque shaft of the torque sub. FIG. 6B is an end view of the torque shaft with a partial sectional view cut along line 6B-6B of FIG. 6A. FIG. 6C is a cross section of FIG. 6A. FIG. 6D is an isometric view of the torque shaft. FIG. 6E is a top view of a strain gage. FIG. 6F is a partial section of a reduced diameter portion of the torque shaft showing the strain gage of FIG. 6E mounted thereon. FIG. 6G is a schematic of four strain gages in a Wheatstone bridge configuration. FIG. 6H is a schematic of strain gages mounted on the tapered portion of the torque shaft. FIG. 6I is an electrical diagram showing data and electrical communication between the torque shaft and a housing of the torque sub.

FIG. 7 is a block diagram illustrating a tubular make-up system implementing the torque sub of FIG. 6.

FIG. 8 is a sectional view of a torque sub, according to an alternative embodiment of the present invention.

FIG. 9 is a side view of a top drive system employing a torque meter, according to another alternative embodiment of the present invention. FIG. 9A is an enlargement of a portion of FIG. 9. FIG. 9B is an enlargement of another portion of FIG. 9.

DETAILED DESCRIPTION

FIG. 6 is an isometric view of a torque sub 600, according to one embodiment of the present invention. The torque sub 600 includes a housing 605, a torque shaft 610, an interface 615, and a controller 620. The housing 605 is a tubular member having a bore therethrough. The housing 605 includes a bracket 605a for coupling the housing 605 to the railing system 30, thereby preventing rotation of the housing 605 during rotation of the tubular, but allowing for vertical movement of the housing with the top drive 100 under the traveling block 110. The interface 615 and the controller 620 are both mounted on the housing 605. The housing 605 and the torque shaft 610 are made from metal, preferably stainless steel. The interface 615 is made from a polymer. Preferably, the elevator 35 (only partially shown) is also mounted on the housing 605, although this is not essential to the present invention.

FIG. 6A is a side view of the torque shaft 610 of the torque sub 600. FIG. 6B is an end view of the torque shaft 610 with a partial sectional view cut along line 6B-6B of FIG. 6A. FIG. 6C is a cross section of FIG. 6A. FIG. 6D is an isometric view of the torque shaft 610. The torque shaft 610 is a tubular member having a flow bore therethrough. The torque shaft 610 is disposed through the bore of the housing 605 so that it may rotate relative to the housing 605. The torque shaft 610 includes a threaded box 610a, a groove 610b, one or more longitudinal slots 610c (preferably two), a reduced diameter portion 610d, and a threaded pin 610e, a metal sleeve 610f, and a polymer (preferably rubber, more preferably silicon rubber) shield 610g.

The threaded box 610a receives the quill of the top drive 100, thereby forming a rotational connection therewith. The pin 610e is received by either a box of the spear body 205 or the top drive connector 310 of the torque head 300, thereby forming a rotational connection therewith. The groove 610b receives a secondary coil 630b (see FIG. 6I) which is wrapped therearound. Disposed on an outer surface of the reduced diameter portion 610d are one or more strain gages 680 (see FIGS. 6E-6H). The strain gages 680 are disposed on the reduced diameter portion 610d at a sufficient distance from either taper so that stress/strain transition effects at the tapers are fully dissipated. The slots 610c provide a path for wiring between the secondary coil 630b and the strain gages 680 and also house an antenna 645a (see FIG. 6I).

The shield 610g is disposed proximate to the outer surface of the reduced diameter portion 610d. The shield 610g may be applied as a coating or thick film over strain gages 680. Disposed between the shield 610g and the sleeve 610f are electronic components 635,640 (see FIG. 6I). The electronic components 635,640 are encased in a polymer mold 630 (see FIG. 6I). The shield 610g absorbs any forces that the mold 630 may otherwise exert on the strain gages 680 due to the hardening of the mold. The shield 610g also protects the delicate strain gages 680 from any chemicals present at the wellsite that may otherwise be inadvertently splattered on the strain gages 680. The sleeve 610f is disposed along the reduced diameter portion 610d. A recess is formed in each of the tapers to seat the shield 610f. The sleeve 610f forms a substantially continuous outside diameter of the torque shaft 610 through the reduced diameter portion 610d. Preferably, the sleeve 610f is made from sheet metal and welded to the shaft 610. The sleeve 610f also has an injection port formed therethrough (not shown) for filling fluid mold material to encase the electronic components 635,640.

FIG. 6E is a top view of the strain gage 680. FIG. 6F is a partial section of the reduced diameter portion 610d of the torque shaft 610 showing the strain gage of FIG. 6E mounted thereon. FIG. 6G is a schematic of four strain gages 680 in a Wheatstone bridge 685 configuration. FIG. 6H is a schematic of strain gages 680t,w mounted on the tapered portion 610d of the torque shaft 610.

Preferably, each strain gage 680 is made of a thin foil grid 682 and bonded to the tapered portion 610d of the shaft 610 by a polymer support 684, such as an epoxy glue. The foil 682 strain gauges 680 are made from metal, such as platinum, tungsten/nickel, or chromium. The sensitive part of each strain gage 680 is along the straight part (parallel to longitudinal axis o-x) of the conducting foil 682. When elongated, this conducting foil 682 increases in resistance. The resistance may be measured by connecting the strain gage 680 to an electrical circuit via terminal wires 683. Two gages 680 are usually configured in a Wheatstone bridge 685 to increase sensitivity. Two more gages 680 not submitted to the strain are added to compensate for temperature variation. The longitudinal load acting on the torque shaft 610 is measured by orientating a strain gage 680w with its longitudinal axis o-x parallel to the longitudinal axis of the torque shaft 610. The torque acting on the torque shaft 610 is measured by orienting a strain gage 680t with its longitudinal axis o-x at a forty-five degree angle relative to the longitudinal axis of the torque shaft 610 and another strain gage 680t at a negative forty-five degree angle relative to the longitudinal axis of the torque shaft 610. Preferably, each of the strain gages 680t,680t,680w is a Wheatstone bridge 685 made up of four strain gages 680. Alternatively, semi-conductor strain gauges (not shown) or piezoelectric (crystal) strain gages may be used in place of the foil strain gauges 680. Alternatively, only a single strain gage 680t may be disposed on the shaft 610.

FIG. 6I is an electrical diagram showing data and electrical communication between the torque shaft 610 and the housing 605 of the torque sub 600. A power source 660 is provided. The power source 660 may be a battery pack disposed in the controller 620, an-onsite generator, or utility lines. The power source 660 is electrically coupled to a sine wave generator 650. Preferably, the sine wave generator 650 will output a sine wave signal having a frequency less than nine kHz to avoid electromagnetic interference. The sine wave generator 650 is in electrical communication with a primary coil 630a of an electrical power coupling 630.

The electrical power coupling 630 is an inductive energy transfer device. Even though the coupling 630 transfers energy between the stationary interface 615 and the rotatable torque shaft 610, the coupling 630 is devoid of any mechanical contact between the interface 615 and the torque shaft 610. In general, the coupling 630 acts similar to a common transformer in that it employs electromagnetic induction to transfer electrical energy from one circuit, via its primary coil 630a, to another, via its secondary coil 630b, and does so without direct connection between circuits. The coupling 630 includes the secondary coil 630b mounted on the rotatable torque shaft 610. The primary 630a and secondary 630b coils are structurally decoupled from each other.

The primary coil 630a may be encased in a polymer 627a, such as epoxy. A coil housing 627b may be disposed in the groove 610b. The coil housing 627b is made from a polymer and may be assembled from two halves to facilitate insertion around the groove 610b. The secondary coil 630b may then be wrapped around the coil housing 627b in the groove 610b. Optionally, the secondary coil 630b is then molded in the coil housing 627b with a polymer. The primary 630a and secondary coils 630b are made from an electrically conductive material, such as copper, copper alloy, aluminum, or aluminum alloy. The primary 630a and/or secondary 630b coils may be jacketed with an insulating polymer. In operation, the alternating current (AC) signal generated by sine wave generator 650 is applied to the primary coil 630a. When the AC flows through the primary coil 630a, the resulting magnetic flux induces an AC signal across the secondary coil 630b. The induced voltage causes a current to flow to rectifier and direct current (DC) voltage regulator (DCRR) 635. A constant power is transmitted to the DCRR 635, even when torque shaft 610 is rotated by the top drive 100. The primary coil 630a and the secondary coil 630b have their parameters (i.e., number of wrapped wires) selected so that an appropriate voltage may be generated by the sine wave generator 650 and applied to the primary coil 630a to develop an output signal across the secondary coil 630b. Alternatively, conventional slip rings, roll rings, or transmitters using fluid metal may be used instead of the electrical coupling 630 or a battery pack may be disposed in the torque shaft 610, thereby eliminating the need for the electrical coupling 630 or alternatives.

The DCRR 635 converts the induced AC signal from the secondary coil 630b into a suitable DC signal for use by the other electrical components of the torque shaft 610. The DCRR outputs a first signal to the strain gages 680 and a second signal to an amplifier and microprocessor controller (AMC) 640. The first signal is split into sub-signals which flow across the strain gages 680, are then amplified by the amplifier 640, and are fed to the controller 640. The controller 640 converts the analog signals from the strain gages 680 into digital signals, multiplexes them into a data stream, and outputs the data stream to a modem 640 (preferably a radio frequency modem). The modem 640 modulates the data stream for transmission from antenna 645a. The antenna 645a transmits the encoded data stream to an antenna 645b disposed in the interface 615. Alternatively, the analog signals from the strain gages may be multiplexed and modulated without conversion to digital format. Alternatively, conventional slip rings, an electric swivel coupling, roll rings, or transmitters using fluid metal may be used to transfer data from the torque shaft 610 to the interface 615.

Rotationally coupled to the torque shaft 610 is a turns gear 665. Disposed in the interface 615 is a proximity sensor 670. The gear/sensor 665,670 arrangement is optional. Various types of gear/sensor 665,670 arrangements are known in the art and would be suitable. The proximity sensor 665 senses movement of the gear 670. Preferably, a sensitivity of the gear/sensor 665,670 arrangement is one-tenth of a turn, more preferably one-hundredth of a turn, and most preferably one-thousandth of a turn. Alternatively a friction wheel/encoder device (see FIG. 9) or a gear and pinion arrangement may be used instead of a gear/sensor arrangement. A microprocessor controller 655 may provide power to the proximity sensor 670 and receives an analog signal indicative of movement of the gear 665 therefrom. The controller 655 may convert the analog signal from the proximity sensor 670 and convert it to a digital format.

The antenna 645b sends the received data stream to a modem 655. The modem 655 demodulates the data signal and outputs it to the controller 655. The controller 655 de-codes the data stream, combines the data stream with the turns data, and re-formats the data stream into a usable input (i.e., analog, field bus, or Ethernet) for a make-up computer system 706 (see FIG. 7). The controller 655 is also powered by the power source 660. The controller 655 may also process the data from strain gages 680 and proximity sensor 665 to calculate respective torque, longitudinal load, and turns values therefrom. The controller 655 may also be connected to a wide area network (WAN) (preferably, the Internet) so that office engineers/technicians may remotely communicate with the controller 655. Further, a personal digital assistant (PDA) may also be connected to the WAN so that engineers/technicians may communicate with the controller 655 from any worldwide location.

The interface controller 655 may also send data to the torque shaft controller 640 via the antennas 645a, b. A separate channel may be used for communication from the interface controller 655 to the torque shaft controller 640. The interface controller 655 may send commands to vary operating parameters of the torque shaft 610 and/or to calibrate the torque shaft 610 (i.e., strain gages 680t, w) before operation. In addition, the interface controller 655 may also control operation of the top drive 100 and/or the torque head 300 or the spear 200.

FIG. 7 is a block diagram illustrating a tubular make-up system implementing the torque sub of FIG. 6. Generally, the tubular make-up system 700 includes the top drive 100, torque sub 600, and the computer system 706. A computer 716 of the computer system 706 monitors the turns count signals and torque signals 714 from torque sub 600 and compares the measured values of these signals with predetermined values. In one embodiment, the predetermined values are input by an operator for a particular tubing connection. The predetermined values may be input to the computer 716 via an input device, such as a keypad, which can be included as one of a plurality of input devices 718.

Illustrative predetermined values which may be input, by an operator or otherwise, include a delta torque value 724, a delta turns value 726, minimum and maximum turns values 728 and minimum and maximum torque values 730. During makeup of a tubing assembly, various output may be observed by an operator on output device, such as a display screen, which may be one of a plurality of output devices 720. The format and content of the displayed output may vary in different embodiments. By way of example, an operator may observe the various predefined values which have been input for a particular tubing connection. Further, the operator may observe graphical information such as a representation of the torque rate curve 500 and the torque rate differential curve 500a. The plurality of output devices 720 may also include a printer such as a strip chart recorder or a digital printer, or a plotter, such as an x-y plotter, to provide a hard copy output. The plurality of output devices 720 may further include a horn or other audio equipment to alert the operator of significant events occurring during make-up, such as the shoulder condition, the terminal connection position and/or a bad connection.

Upon the occurrence of a predefined event(s), the computer system 706 may output a dump signal 722 to automatically shut down the top drive unit 100. For example, dump signal 722 may be issued upon detecting the terminal connection position and/or a bad connection.

The comparison of measured turn count values and torque values with respect to predetermined values is performed by one or more functional units of the computer 716. The functional units may generally be implemented as hardware, software or a combination thereof. By way of illustration of a particular embodiment, the functional units are described as software. In one embodiment, the functional units include a torque-turns plotter algorithm 732, a process monitor 734, a torque rate differential calculator 736, a smoothing algorithm 738, a sampler 740, a comparator 742, and a deflection compensator 752. The process monitor 734 includes a thread engagement detection algorithm 744, a seal detection algorithm 746 and a shoulder detection algorithm 748. It should be understood, however, that although described separately, the functions of one or more functional units may in fact be performed by a single unit, and that separate units are shown and described herein for purposes of clarity and illustration. As such, the functional units 732-742,752 may be considered logical representations, rather than well-defined and individually distinguishable components of software or hardware.

The deflection compensator 752 includes a database of predefined values or a formula derived therefrom for various torque and system deflections resulting from application of various torque on the top drive unit 100. These values (or formula) may be calculated theoretically or measured empirically. Since the top drive unit 100 is a relatively complex machine, it may be preferable to measure deflections at various torque since a theoretical calculation may require extensive computer modeling, i.e. finite element analysis. Empirical measurement may be accomplished by substituting a rigid member, i.e. a blank tubular, for the premium grade assembly 400 and causing the top drive 100 to exert a range of torques corresponding to a range that would be exerted on the tubular grade assembly to properly make-up a connection. In the case of the top drive unit 100, the blank may be only a few feet long so as not to compromise rigidity. The torque and rotation values provided by torque sub 600, respectively, would then be monitored and recorded in a database. The test may then be repeated to provide statistical samples. Statistical analysis may then be performed to exclude anomalies and/or derive a formula. The test may also be repeated for different size tubulars to account for any change in the stiffness of the top drive 100 due to adjustment of the units for different size tubulars. Alternatively, only deflections for higher values (i.e. at a range from the shoulder condition to the terminal condition) need be measured.

Deflection of tubular member 402, preferably, will also be added into the system deflection. Theoretical formulas for this deflection may readily be available. Alternatively, instead of using a blank for testing the top drive, the end of member 402 distal from the top drive may simply be locked into a spider. The top drive 100 may then be operated across the desired torque range while measuring and recording the torque and rotation values from the torque sub 600. The measured rotation value will then be the rotational deflection of both the top drive 100 and the tubular member 402. Alternatively, the deflection compensator may only include a formula or database of torques and deflections for just the tubular member 402.

In operation, two threaded members 402,404 are brought together. The box 406 is usually made-up on tubular 404 off-site before the tubulars 402,404 are transported to the rig. One of the threaded members (i.e., tubular 402) is rotated by the top drive 100 while the other tubular 404 is held by the spider 60. The applied torque and rotation are measured at regular intervals throughout a pipe connection makeup. In one embodiment, the box 406 may be secured against rotation so that the turns count signals accurately reflect the rotation of the tubular 402. Alternatively or additionally, a second turns counter may be provided to sense the rotation of the box 406. The turns count signal issued by the second turns counter may then be used to correct (for any rotation of the box 406) the turns count signals.

At each interval, the rotation value may be compensated for system deflection. The term system deflection encompasses deflection of the top drive 100 and/or the tubular 402. To compensate for system deflection, the deflection compensator 752 utilizes the measured torque value to reference the predefined values (or formula) to find/calculate the system deflection for the measured torque value. The deflection compensator 752 then subtracts the system deflection value from the measured rotation value to calculate a corrected rotation value. Alternatively, a theoretical formula for deflection of the tubular member 402 may be pre-programmed into the deflection compensator 752 for a separate calculation of deflection and then the deflection may be added to the top drive deflection to calculate the system deflection during each interval. Alternatively, the deflection compensator 752 may only compensate for the deflection of the tubular member 402.

The frequency with which torque and rotation are measured may be specified by the sampler 740. The sampler 740 may be configurable, so that an operator may input a desired sampling frequency. The measured torque and corrected rotation values may be stored as a paired set in a buffer area of computer memory. Further, the rate of change of torque with corrected rotation (i.e., a derivative) is calculated for each paired set of measurements by the torque rate differential calculator 736. At least two measurements are needed before a rate of change calculation can be made. In one embodiment, the smoothing algorithm 738 operates to smooth the derivative curve (e.g., by way of a running average). These three values (torque, corrected rotation and rate of change of torque) may then be plotted by the plotter 732 for display on the output device 720.

These three values (torque, corrected rotation and rate of change of torque) are then compared by the comparator 742, either continuously or at selected rotational positions, with predetermined values. For example, the predetermined values may be minimum and maximum torque values and minimum and maximum turn values.

Based on the comparison of measured/calculated/corrected values with predefined values, the process monitor 734 determines the occurrence of various events and whether to continue rotation or abort the makeup. In one embodiment, the thread engagement detection algorithm 744 monitors for thread engagement of the two threaded members. Upon detection of thread engagement a first marker is stored. The marker may be quantified, for example, by time, rotation, torque, a derivative of torque or time, or a combination of any such quantifications. During continued rotation, the seal detection algorithm 746 monitors for the seal condition. This may be accomplished by comparing the calculated derivative (rate of change of torque) with a predetermined threshold seal condition value. A second marker indicating the seal condition is stored when the seal condition is detected. At this point, the turns value and torque value at the seal condition may be evaluated by the connection evaluator 750.

For example, a determination may be made as to whether the corrected turns value and/or torque value are within specified limits. The specified limits may be predetermined, or based off of a value measured during makeup. If the connection evaluator 750 determines a bad connection, rotation may be terminated. Otherwise rotation continues and the shoulder detection algorithm 748 monitors for shoulder condition. This may be accomplished by comparing the calculated derivative (rate of change of torque) with a predetermined threshold shoulder condition value. When the shoulder condition is detected, a third marker indicating the shoulder condition is stored. The connection evaluator 750 may then determine whether the turns value and torque value at the shoulder condition are acceptable.

In one embodiment the connection evaluator 750 determines whether the change in torque and rotation between these second and third markers are within a predetermined acceptable range. If the values, or the change in values, are not acceptable, the connection evaluator 750 indicates a bad connection. If, however, the values/change are/is acceptable, the target calculator 752 calculates a target torque value and/or target turns value. The target value is calculated by adding a predetermined delta value (torque or turns) to a measured reference value(s). The measured reference value may be the measured torque value or turns value corresponding to the detected shoulder condition. In one embodiment, a target torque value and a target turns value are calculated based off of the measured torque value and turns value, respectively, corresponding to the detected shoulder condition.

Upon continuing rotation, the target detector 754 monitors for the calculated target value(s). Once the target value is reached, rotation is terminated. In the event both a target torque value and a target turns value are used for a given makeup, rotation may continue upon reaching the first target or until reaching the second target, so long as both values (torque and turns) stay within an acceptable range. Alternatively, the deflection compensator 752 may not be activated until after the shoulder condition has been detected.

In one embodiment, system inertia is taken into account and compensated for to prevent overshooting the target value. System inertia includes mechanical and/or electrical inertia and refers to the system's lag in coming to a complete stop after the dump signal is issued. As a result of such lag, the top drive unit 100 continues rotating the tubing member even after the dump signal is issued. As such, if the dump signal is issued contemporaneously with the detection of the target value, the tubing may be rotated beyond the target value, resulting in an unacceptable connection. To ensure that rotation is terminated at the target value (after dissipation of any inherent system lag) a preemptive or predicative dump approach is employed. That is, the dump signal is issued prior to reaching the target value. The dump signal may be issued by calculating a lag contribution to rotation which occurs after the dump signal is issued. In one embodiment, the lag contribution may be calculated based on time, rotation, a combination of time and rotation, or other values. The lag contribution may be calculated dynamically based on current operating conditions such as RPMs, torque, coefficient of thread lubricant, etc. In addition, historical information may be taken into account. That is, the performance of a previous makeup(s) for a similar connection may be relied on to determine how the system will behave after issuing the dump signal. Persons skilled in the art will recognize other methods and techniques for predicting when the dump signal should be issued.

In one embodiment, the sampler 740 continues to sample at least rotation to measure counter rotation which may occur as a connection relaxes. When the connection is fully relaxed, the connection evaluator 750 determines whether the relaxation rotation is within acceptable predetermined limits. If so, makeup is terminated. Otherwise, a bad connection is indicated.

In the previous embodiments turns and torque are monitored during makeup. However, it is contemplated that a connection during makeup may be characterized by either or both of theses values. In particular, one embodiment provides for detecting a shoulder condition, noting a measured turns value associated with the shoulder condition, and then adding a predefined turns value to the measured turns value to arrive at a target turns value. Alternatively or additionally, a measured torque value may be noted upon detecting a shoulder condition and then added to a predefined torque value to arrive at a target torque value. Accordingly, it should be emphasized that either or both a target torque value and target turns value may be calculated and used as the termination value at which makeup is terminated. Preferably, the target value is based on a delta turns value. A delta turns value can be used to calculate a target turns value without regard for a maximum torque value. Such an approach is made possible by the greater degree of confidence achieved by relying on rotation rather than torque.

Whether a target value is based on torque, turns or a combination, the target values are not predefined, i.e., known in advance of determining that the shoulder condition has been reached. In contrast, the delta torque and delta turns values, which are added to the corresponding torque/turn value as measured when the shoulder condition is reached, are predetermined. In one embodiment, these predetermined values are empirically derived based on the geometry and characteristics of material (e.g., strength) of two threaded members being threaded together.

In addition to geometry of the threaded members, various other variables and factors may be considered in deriving the predetermined values of torque and/or turns. For example, the lubricant and environmental conditions may influence the predetermined values. In one aspect, the present invention compensates for variables influenced by the manufacturing process of tubing and lubricant. Oilfield tubes are made in batches, heat treated to obtain the desired strength properties and then threaded. While any particular batch will have very similar properties, there is significant variation from batch to batch made to the same specification. The properties of thread lubricant similarly vary between batches. In one embodiment, this variation is compensated for by starting the makeup of a string using a starter set of determined parameters (either theoretical or derived from statistical analysis of previous batches) that is dynamically adapted using the information derived from each previous makeup in the string. Such an approach also fits well with the use of oilfield tubulars where the first connections made in a string usually have a less demanding environment than those made up at the end of the string, after the parameters have been ‘tuned’.

According to embodiments of the present invention, there is provided a method and apparatus of characterizing a connection. Such characterization occurs at various stages during makeup to determine whether makeup should continue or be aborted. In one aspect, an advantage is achieved by utilizing the predefined delta values, which allow a consistent tightness to be achieved with confidence. This is so because, while the behavior of the torque-turns curve 500 (FIG. 5) prior to reaching the shoulder condition varies greatly between makeups, the behavior after reaching the shoulder condition exhibits little variation. As such, the shoulder condition provides a good reference point on which each torque-turns curve may be normalized. In particular, a slope of a reference curve portion may be derived and assigned a degree of tolerance/variance. During makeup of a particular connection, the behavior of the torque-turns curve for the particular connection may be evaluated with respect to the reference curve. Specifically, the behavior of that portion of the curve following detection of the shoulder condition can be evaluated to determine whether the slope of the curve portion is within the allowed tolerance/variance. If not, the connection is rejected and makeup is terminated.

In addition, connection characterizations can be made following makeup. For example, in one embodiment the rotation differential between the second and third markers (seal condition and shoulder condition) is used to determine the bearing pressure on the connection seal, and therefore its leak resistance. Such determinations are facilitated by having measured or calculated variables following a connection makeup. Specifically, following a connection makeup actual torque and turns data is available. In addition, the actual geometry of the tubing and coefficient of friction of the lubricant are substantially known. As such, leak resistance, for example, can be readily determined according to methods known to those skilled in the art.

FIG. 8 is a sectional view of a torque sub 800, according to an alternative embodiment of the present invention. The torque sub 800 includes two boxes 806a, b; links 803 (preferably four); splined adapters 802; and a torque shaft 810. Box 806a and/or box 806b may be replaced by a pin as necessary to connect the torque shaft 810 to the top drive 100 and the spear 200 or the torque head 300. At least one torsional strain gage 680t (preferably two Wheatstone bridges) is disposed on the torque shaft 810. One or more longitudinal strain gages 680w may also be disposed on one or more of the links 803. The torque shaft 810 has two straight-splined ends. Each splined end mates with one of the splined adapters 802, thereby only torque is transmitted through torque shaft 810. The links 803 are coupled to the boxes with pins 804 and lugs, thereby transmitting only longitudinal loads through the links 803. The turns may be measured with a lower turns counter 905b (see FIG. 9), thereby eliminating the need for the deflection compensator 752. Power and data communication may be provided similarly as for torque sub 600. The interface 615 may instead be located in a housing of the top drive.

FIG. 9 is a side view of a top drive system employing a torque meter 900, according to another alternative embodiment of the present invention. FIG. 9A is an enlargement of a portion of FIG. 9. FIG. 9B is an enlargement of another portion of FIG. 9. The torque meter 900 includes upper 905a and lower 905b turns counters. The upper turns counter 905a is located between the top drive 100 and the torque head 300. The lower turns counter is located along the first tubular 402 proximate to the box 406. Each turns counter includes a friction wheel 920, an encoder 915, and a bracket 925a, b. The friction wheel 920 of the upper turns counter 905a is held into contact with a drive shaft 910 of the top drive 100. The friction wheel 920 of the lower turns counter 905b is held into contact with the first tubular 402. Each friction wheel is coated with a material, such as a polymer, exhibiting a high coefficient of friction with metal. The frictional contact couples each friction wheel with the rotational movement of outer surfaces of the drive shaft 910 and first tubular 402, respectively. Each encoder 915 measures the rotation of the respective friction wheel 920 and translates the rotation to an analog signal indicative thereof. Alternatively, a gear and proximity sensor arrangement or a gear and pinion arrangement may be used instead of a friction wheel for the upper 905a and/or lower 905b turns counters. In this alternate, for the lower turns counter 905b, the gear would be split to facilitate mounting on the first tubular 402.

Due to the arrangement of the upper 905a and lower 905b turns counters, a torsional deflection of the first tubular 402 may be measured. This is found by subtracting the turns measured by the lower turns counter 905b from the turns measured by the upper turns counter 905a. By turns measurement, it is meant that the rotational value from each turns counter 905a, b has been converted to a rotational value of the first tubular 402. Once the torsional deflection is known a controller or computer 706 may calculate the torque exerted on the first tubular by the top drive 100 from geometry and material properties of the first tubular. If a length of the tubular 402 varies, the length may be measured and input manually (i.e. using a rope scale) or electronically using a position signal from the draw works 105. The turns signal used for monitoring the make-up process would be that from the lower turns counter 905b, since the measurement would not be skewed by torsional deflection of the first tubular 402.

If an outside diameter of the first tubular 402 is not known, the tubular 402 may be rotated by a full turn without torque (not engaged with the box 406). The rotational measurement from the encoder of the lower turns counter 905b may be multiplied by a diameter of the drive shaft 910 and divided by an rotational measurement from the encoder of the upper turns counter 905a. This calculation assumes that diameters of the friction wheels are equal. Alternatively, the operation may be performed using a defined time instead of a full turn.

The torque meter 900 may be calibrated by inserting a torque sub, i.e. torque sub 600 or a conventional torque sub, between the first tubular 402 and the box 406 and exerting a range of torques on the first tubular 402. The lower turns counter 905b would be adjusted so that it contacted the first tubular in the same position as without the torque sub.

The lower turns counter 905b may also be used to control the rotational speed of the top drive 100. Once a seal or shoulder condition is reached, the rotational velocity of the first tubular 402 will noticeably decrease. This rotational velocity signal could be input to the top drive controller or the computer 716 to reduce the speed of the drive shaft 910.

In addition, the torque meter 900 may be used with buttress casing connections. The make-up length of the thread may be measured by a longitudinal measuring attachment disposed located at the top drive 100 or at the casing, i.e. in combination with the encoder 915 of the lower turns counter 905b.

It will be appreciated that although use of the torque sub 600, the torque sub 800, and the torque meter 900 have been described with respect to a tapered premium grade connection, the embodiments are not so limited. Accordingly, the torque sub 600, the torque sub 800, and the torque meter 900 may be used for making-up parallel premium grade connections. Further, some connections do not utilize a box or coupling (such as box 406). Rather, two tubing lengths (one having external threads at one end, and the other having cooperating internals threads) are threadedly engaged directly with one another. The torque sub 600, the torque sub 800, and the torque meter 900 are equally applicable to such connections. In general, any pipe forming a metal-to-metal seal which can be detected during make up can be utilized. Further, use of the term “shoulder” or “shoulder condition” is not limited to a well-defined shoulder as illustrated in FIG. 4. It may include a connection having a plurality of metal-to-metal contact surfaces which cooperate together to serve as a “shoulder.” It may also include a connection in which an insert is placed between two non-shouldered threaded ends to reinforce the connection, such as may be done in drilling with casing. In this regard, torque sub 600, the torque sub 800, and the torque meter 900 have application to any variety of tubulars characterized by function including: drill pipe, tubing/casing, risers, and tension members. The connections used on each of these tubulars must be made up to a minimum preload on a torque shoulder if they are to function within their design parameters and, as such, may be used to advantage with the present invention. The torque sub 600, the torque sub 800, and the torque meter 900 may also be used in the make-up of any oil country tubular good.

While the foregoing is directed to embodiments of the present invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow.

Claims

1. A method of connecting threaded tubular members for use in a wellbore, comprising: operating a top drive, thereby rotating a first threaded tubular member relative to a second threaded tubular member;measuring a torque exerted on the first tubular member by the top drive, wherein the torque is measured using a torque shaft rotationally coupled to the top drive and the first tubular, the torque shaft having a strain gage disposed thereon;wirelessly transmitting the measured torque from the torque shaft to a stationary interface;measuring rotation of the first tubular member;determining acceptability of the threaded connection; andstopping rotation of the first threaded member when the threaded connection is complete or if the threaded connection is unacceptable.

2. The method of claim 1, further comprising wirelessly transmitting electrical energy from a stationary interface to the torque shaft.

3. The method of claim 1, wherein: the two threaded members define a shoulder,the method further comprises detecting a shoulder condition during rotation of the first tubular member; andthe threaded connection is complete when reaching a predefined rotation value from the shoulder condition.

4. The method of claim 3 wherein detecting the shoulder condition comprises calculating and monitoring a rate of change of torque with respect to rotation.

5. The method of claim 3 wherein acceptability is determined using a value measured at or after the shoulder condition.

6. The method of claim 5 wherein the measured value is a torque value.

7. The method of claim 5 wherein the measured value is a rotation value.

8. The method of claim 4, wherein acceptability is determined using the rate of change of torque with respect to rotation after detecting the shoulder condition.

9. The method of claim 3 wherein acceptability is determined using a relaxation rotation of the first threaded tubular member.

10. The method of claim 1, further comprising compensating the rotation measurement by subtracting a deflection of at least one of: the top drive, andthe first tubular member.

11. The method of claim 10, wherein compensating the rotation measurement comprises subtracting the deflection of the top drive.

12. The method of claim 11, further comprising calculating the deflection of the top drive using the measured torque.

13. The method of claim 10, wherein compensating the rotation measurement comprises subtracting the deflection of the first tubular member.

14. The method of claim 1, further comprising measuring a longitudinal load exerted on the top drive using the torque shaft, the torque shaft having a second strain gage disposed thereon.

15. The method of claim 11, further comprising wirelessly transmitting a calibration signal and/or control signals from the stationary interface to the torque shaft.

16. A system for connecting threaded tubular members for use in a wellbore, comprising: a top drive operable to rotate a first threaded tubular member relative to a second threaded tubular member;a torque sub comprising: a torque shaft rotationally coupled to the top drive;a strain gage disposed on the torque shaft for measuring a torque exerted on the torque shaft by the top drive; andan antenna in communication with the strain gage;a turns counter for measuring rotation of the first tubular; andan antenna in electromagnetic communication with the torque sub antenna and located at a stationary position relative to the top drive;a computer: located at a stationary position relative to the top drive;in communication with the turns counter and the stationary antenna; andconfigured to perform an operation, comprising: monitoring the torque and rotation measurements during rotation of the first tubular member relative to the second tubular member;determining acceptability of the threaded connection; andstopping rotation of the first threaded member when the threaded connection is complete or if the computer determines that the threaded connection is unacceptable.

17. The system of claim 16, wherein the torque sub further comprises: an interface, wherein the torque shaft is disposed in the interface so that the torque shaft may rotate relative to the interface;an electrical coupling, comprising: a primary coil disposed in the interface; anda secondary coil wrapped around the torque shaft and in communication with the strain gage, wherein a current is generated in the secondary coil when a current is passed through the primary coil.

18. The system of claim 17, wherein the torque sub further comprises: a rectifier disposed on the torque shaft and in electrical communication with the secondary coil; anda modulator in communication with the strain gage.

19. The system of claim 18, wherein the torque sub further comprises an amplifier in communication with the strain gage and the modulator.

20. The system of claim 16, wherein the torque sub further comprises: a second strain gage disposed on the torque shaft for measuring a longitudinal load exerted on the torque shaft.

21. The system of claim 16, wherein the torque sub further comprises: first and second connectors, each connector rotationally coupled to a respective end of the torque shaft; andfirst and second links longitudinally coupling the connectors together so that only torque is exerted on the torque shaft.

22. The system of claim 16, wherein the turns counter comprises: a gear rotationally coupled to the torque shaft; anda proximity sensor disposed in the interface and configured to sense movement of the gear.

23. The system of claim 16, wherein: the two threaded members define a shoulder,the operation further comprises detecting a shoulder condition during rotation of the first tubular member; andthe threaded connection is complete when reaching a predefined rotation value from the shoulder condition.

24. The system of claim 23, wherein detecting the shoulder condition comprises calculating and monitoring a rate of change of torque with respect to rotation.

25. The system of claim 16, wherein the operation further comprises wirelessly transmitting a calibration signal and/or control signals from the computer to the torque shaft.

26. A system for connecting threaded tubular members for use in a wellbore, comprising: a top drive operable to rotate a first threaded tubular member relative to a second threaded tubular member;a torque sub comprising: a torque shaft rotationally coupled to the top drive; anda strain gage disposed on the torque shaft for measuring a torque exerted on the torque shaft by the top drive;first and second connectors, each connector rotationally coupled to a respective end of the torque shaft; andfirst and second links longitudinally coupling the connectors together so that only torque is exerted on the torque shaft; anda turns counter for measuring rotation of the first tubular.

27. A method of connecting threaded tubular members for use in a wellbore, comprising: operating a top drive, thereby rotating a first threaded tubular member relative to a second threaded tubular member;measuring a torque exerted on the first tubular member by the top drive, wherein the torque is measured using upper and lower turns counters, each turns counter disposed proximate to a respective longitudinal end of the first tubular; andmeasuring rotation of the first tubular member, wherein the rotation is measured using the lower turns counter.

28. A system for connecting threaded tubular members for use in a wellbore, comprising: a top drive operable to rotate a first threaded tubular member relative to a second threaded tubular member;an upper turns counter for measuring rotation of an upper longitudinal end of the first tubular; anda lower turns counter for measuring rotation of a lower longitudinal end of the first tubular.