rotary kelly bushing manufacturer

The Kelly Drive Bushing acts as an adapter that serves to connect the rotary table to the Kelly. The Kelly bushing has an inside diameter profile that matches that of the Kelly, usually square or hexagonal. It is connected to the rotary table by four large steel pins that fit into mating holes in the rotary table. The rotary motion from the rotary table is transmitted to the bushing through the pins, and then to the kelly itself through the square or hexagonal flat surfaces between the Kelly and the Kelly drive bushing. The Kelly then turns the entire drillstring because it is screwed into the top of the drillstring itself.

Distributor and manufacturer of new and rebuilt oilfield drilling equipment & supplies including mud pumps and parts. Drilling equipment includes swivels, mud pumps, rotary table & draw works. Drilling supplies include tongs, roller chains, valves, drive bushings & rotary heads. Mud pump supplies include duplex & triplex liners & piston & pony rods. Pump parts include crossheads, slides & cranks. Catheads, washpipes, bearings, union pipes, pump heads, pipe nipples, crankshafts, roller chain sprockets & chain & pump drives are available. Capabilities include contractors" equipment repairing services. Drilling equipment & supplies are used in oilrigs.

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An adapter that serves to connect the rotary table to the kelly. The kelly bushing has an inside diameter profile that matches that of the kelly, usually square or hexagonal. It is connected to the rotary table by four large steel pins that fit into mating holes in the rotary table. The rotary motion from the rotary table is transmitted to the bushing through the pins, and then to the kelly itself through the square or hexagonal flat surfaces between the kelly and the kelly bushing. The kelly then turns the entire drillstring because it is screwed into the top of the drillstring itself. Depth measurements are commonly referenced to the KB, such as 8327 ft KB, meaning 8327 feet below the kelly bushing.

Roller Kelly Bushings are designed and manufactured as per API Spec 7K "Drilling and Well Servicing Equipment" for driving Kelly in the drilling operation.

Roller kelly bushings are constructed in upper body half, low body half, rollers, rollers pin and etc., can be available in square drive or pin drive. Square drive roller kelly bushing designed with taper contact surface in low body half, while pin drive roller kelly bushing designed with pin to be installed in low body half.

According to torque of drilling, roller kelly bushing can be available in heavy duty, medium duty and light duty, heavy duty bushings are for high torque and high speed drilling operations while medium duty and light duty are for medium or shadow depth drilling operations.

Roller kelly bushings can accommodate square Kelly or hex Kelly, for square Kelly, the bushing is designed with four flat rollers, and for hex Kelly, the bushing is designed with two V-shaped rollers and two flat rollers. By changing roller size, roller kelly bushing can accommodate square Kelly from 2½" to 5¼" or hex Kelly from 3" to 6", and can be installed in rotary table range from 17½" to 37½".

The JOTKB MODEL 27 PDHD OR 20 PDHD are developed for pin drive master bushing for rotary table sizes from 27-1/2" to 49-1/2" having 25-3/4" and 23" dia pin center. This unit is used for heavy duty drilling operations and high torque conditions on off shore as well as on shore drilling operations, and handle Kelly sizes from 3" to 6" Square or Hexagonal.

Kelly Bushing, also known as Drive Bushing, is a drilling device that is used to connect a Kelly with a rotary table. This tool is used to fit inside the head where the Kelly fits. The Kelly driver is used to rotate the Kelly. This tool also works along with other drilling tools.

JOT manufacture Pin Drive Kelly Bushing for onshore & offshore Drilling Operations, suitable for a range of 20½” to 49½” Rotary Table, works as connecting equipment between Rotary Table & Kelly.

Kelly Bushing is an essential petroleum drilling tool, and can be equipped with rotary slips, so as to drive Kelly bar. It reduces its friction with kelly bar by the rolling of four rollers in order to prolong its life. Designed to perfection, it is sourced from the trusted vendors who manufacture this by using quality material. Highly acclaimed and demanded by our customers, this Kelly Bushingis offered at very economic price.

The NOV CUL & CB Casing Bushings are inserted directly into the rotary table and insure that the casing being run is perfectly aligned with the center of the hole. Model CU is a solid bushing and model CB is a split bushing. All of the bushings accept bowls of different sizes to accommodate a wide range of casing. Using CMS-XL or CP-S slips, since these bushings fit into the rotary table, the casing string can be easily rotated during cementing operations.

A kelly drive is a type of well drilling device on an oil or gas drilling rig that employs a section of pipe with a polygonal (three-, four-, six-, or eight-sided) or splined outer surface, which passes through the matching polygonal or splined kelly (mating) bushing and rotary table. This bushing is rotated via the rotary table and thus the pipe and the attached drill string turn while the polygonal pipe is free to slide vertically in the bushing as the bit digs the well deeper. When drilling, the drill bit is attached at the end of the drill string and thus the kelly drive provides the means to turn the bit (assuming that a downhole motor is not being used).

The kelly is the polygonal tubing and the kelly bushing is the mechanical device that turns the kelly when rotated by the rotary table. Together they are referred to as a kelly drive. The upper end of the kelly is screwed into the swivel, using a left-hand thread to preclude loosening from the right-hand torque applied below. The kelly typically is about 10 ft (3 m) longer than the drill pipe segments, thus leaving a portion of newly drilled hole open below the bit after a new length of pipe has been added ("making a connection") and the drill string has been lowered until the kelly bushing engages again in the rotary table.

The kelly hose is the flexible, high-pressure hose connected from the standpipe to a gooseneck pipe on a swivel above the kelly and allows the free vertical movement of the kelly while facilitating the flow of the drilling fluid down the drill string. It generally is of steel-reinforced rubber construction but also assemblies of Chiksan steel pipe and swivels are used.

The kelly is below the swivel. It is a pipe with either four or six flat sides. A rotary bushing fits around the flat sides to provide the torque needed to turn the kelly and the drill string. Rollers in the bushing permit the kelly free movement vertically while rotating. Since kelly threads would be difficult to replace, normally the lower end of the kelly has saver sub — or a short piece of pipe — that can be refurbished more cheaply than the kelly. Usually, a ball valve, called the lower kelly cock, is positioned between the kelly and the kelly saver sub. This valve is used for well control if the surface pressure becomes too high for the rotary hose or surface conditions.

According to the ″Dictionary of Petroleum Exploration, Drilling and Production″, ″[The] kelly was named after Michael J. (King) Kelly, a Chicago baseball player (1880-1887) who was known for his base running and long slides.″

As is well known in oil well drilling, a swivel supported kelly is rotatably driven by a kelly bushing which also permits translational movement of the kelly into a well hole. The driving torque for the kelly is transmitted by a rotary table driven master bushing to the kelly bushing through either a pin or square type drive forming part of the kelly bushing.

Due to the tremendous magnitude of weight and torque imposed on the kelly during the drilling operation, a kelly needs to be strong in tension and in torsion as well as to be equally strong in bending in all directions. As is well known, a slightly bent kelly will produce enough resistance to the longitudinal movement of the kelly through the drive bushing to prohibit its passage therethrough. Furthermore, a slight bend in the kelly causes misalignment of the drill pipe in the bore hole resulting in an uncontrolled wobble that produces deleterious forces that can cause severe damage to the various components of the drilling apparatus.

For most bore hole dimensions, the maximum strength kelly is yielded by a kelly having a circular cross-sectional area such as the one shown in U.S. Pat. No. 2,202,446. Although, the circular kelly is recognized as one of high strength, it suffers from the problem of the absence of practical means for rotating same. Thus, over the years, several other shaped kellys have been developed; such as: a circular kelly provided with longitudinally extending flutes or grooves as illustrated in U.S. Pat. Nos. 2,620,163; 2,338,093 and 2,859,939; a circular kelly provided with longitudinal extending external ribs as exemplified in U.S. Pat. Nos. 1,067,330 and 2,829,866; and polygonal cross-sectional kellys having a square shape as illustrated in U.S. Pat. No. 3,527,064 and those of the hexagonal shape as illustrated in U.S. Pat. No. 2,338,093.

Among the most popular of these kellys are those having the square or hexagonal shape. Both of these shaped kellys are normally driven by a drive bushing having four rollers. In the case of the square kelly, each of the four rollers are essentially cylindrical and equally spaced about the axis of the bushing and so positioned to driveably engage respective sides of the kelly. In the case of the hex kelly, two of the cylindrical rollers are replaced with V-shaped rollers such that the two remaining cylindrical rollers driveably engage two diametrically opposite sides of the kelly whereas the two diametrically opposed V-shaped rollers driveably engage the corresponding adjacent sides of the kelly at the corners formed thereby which theoretically results in roller engagement of all six sides of the hex kelly. In such drive arrangements it has been found that instead of having a line contact between the rollers and sides of the kelly there is actually a point contact. This is largely due to wear of the surfaces of the components after limited use and due to the fact that clearance space is required between the rollers and the kelly to permit longitudinal movement of the latter through the bushing during the drilling operation. Such point contact normally occurs at or very near the corners of the kelly during the driving operation, and thus after continued used, the corners of the kelly wear to a degree which decreases the frictional drive engagement by the rollers to a point where slippage occurs resulting in damage to the rollers and replacement of the kelly.

Thus, it is desirable to have a kelly for a given bore hole having a cross-sectional area that approaches that of a circular kelly and which is greater than the cross-sectional area of a standard square or hexagonal kelly so as to maximize the strength of the kelly. Further, it is desirable that the kelly has flat drive surfaces similar to the square and hex kelly to facilitate the driving of same which is one of the shortcomings of the circular kelly. Furthermore, it is desirable that the kelly has a sufficient cross-sectional area that the corners thereof are of sufficient strength so as to prevent excessive wear thereto due to the point drive contact of the rollers to thereby prolong the useful life of the kelly. Still further it is desirable to have a kelly drive bushing that driveably cooperates with the kelly such that the bushing rollers are in drive engagement with the flat drive surfaces of the kelly simultaneously.

Accordingly, it is one of the principal objects of the present invention to provide an improved kelly which is stronger in tension and in torsion compared to a square or hex kelly adapted to be received within a given bore hole.

Another object of the present invention is to provide an improved kelly having a cross-sectional area which approximates that of a circular kelly but which is provided with flat drive surfaces to facilitate driving of same.

Still another object is to provide an improved kelly having flat drive surfaces wherein the corners thereof are stronger than comparable square and hex kellys so as to reduce the wear thereof and prolong the useful life of the kelly.

A still further object of the present invention is to provide an improved kelly drive bushing for driveable cooperation with the improved kelly of the present invention such that the bushing rollers simultaneously driveably engage the respective flat drive surfaces of the kelly.

Yet another object is to provide an improved kelly drive bushing which driveably cooperates with the shape of the improved kelly as well as with a standard hex kelly.

In furtherance of these and other objects, the present invention sets forth an improved kelly having an elongated six sided drive section with a longitudinally extending central axis of rotation. Preferably, the drive section has a substantially uniform cross-section with three arcuately spaced flat drive sides alternating with three arcuate sides. The arcuate sides are spaced an equal radii from the central axis of the kelly. Each of the three flat sides has a midpoint spaced the same radial distance from the central axis with the radial distance being less than the radius of the arcuate sides.

More particularily, the three flat drive sides of the kelly lie in planes that form an equilateral triangle therebetween. Still further, the three flat drive sides are preferably equal in length and the arcuate extent of the three arcuate sides are preferably equal.

The present invention further includes an improved kelly drive bushing which is adapted to driveably cooperate with the improved kelly as well as with a standard hex kelly. More specifically, the improved bushing includes three rotatably mounted rollers with cylindrical outer surfaces having lines of engagement with the drive sides of the kelly lying essentially in the planes defined by the drive sides for simultaneous drive engagement of the drive sides. The respective axis of the rollers are positioned radially outwardly of the central axis of the drive bushing and are parallel to respective ones of the drive sides.

FIG. 1 is a fragmentary front elevational view, partly in section, of a drilling apparatus incorporating the principles of the present invention with the improved kelly extending within and in drive engagement with the improved kelly bushing.

FIG. 3b is an illustrative view showing in cross-section the improved kelly (represented by solid lines a), the cross-section of a comparable square kelly (represented in dotted lines c), and a comparable hexagonal kelly (represented in dashed lines b).

Referring now to the drawings, and particularly FIG. 1, there is shown a fragmentary view of a drilling apparatus of well known construction, being indicated generally by the numeral 10, which incorporates a preferred embodiment of the invention. The drilling apparatus 10 basically includes a swivel (not shown) supported elongated kelly 12 supported within a kelly drive bushing 14 which rotatably drives the kelly 12 about a vertical axis while at the same time permitting relative vertical movement of the kelly 12 to advance a connected drill string (not shown) downwardly within a well hole.

The kelly bushing 14 is of the pin type drive and is supported on a master bushing assembly that includes a master bushing 16 and insert bowl 18. The master bushing assembly is arranged to be rotatably driven in a well known manner in a suitably rotatably driven rotary table 20 which rotary table is suitably supported by a rotary table frame 22 on bearings 24. For a more thorough and complete understanding of the operation and interrelationship of the rotary table, master bushing assembly and kelly bushing, reference is made to U.S. Pat. No. 3,527,064 which is also assigned to the present assignee. Furthermore, it should be pointed out here that even though the kelly bushing shown is of the pin type drive, the principles of the present invention are equally applicable to the square type drive bushings.

Turning to FIGS. 2 and 3, the improved kelly 12 will now be discussed in detail. The kelly 12, being elongated, basically includes an upper conventional female end portion 26, a lower conventional male end portion 28, and an improved drive section 30 extending longitudinally between the end portions 26, 28. The upper female end portion 26 contains internal threads for receiving a swivel mechanism (not shown) whereas the lower male end portion 28 contains external threads for connection to a drill string (not shown).

As best seen in FIG. 3, the drive section 30 of the kelly 12 has a uniform cross-section defined by three substantially flat drive sides 32 alternating with three substantially arcuate sides 34. The three flat drive sides 32 lie in planes that form an equilateral triangle therebetween with the center of the equilateral triangle being concentric with the central axis of the kelly such that the perpendicular radial distances from the midpoint of each of the drive sides 32 to the central axis are equal.

The arcuate sides 34 extend arcuately between adjacent pairs of the respective drive surfaces 32 with the radially inward ends thereof terminating at the respective ends of the drive sides 32. In other words, the three arcuate sides 34 are spaced an equal radii from the central axis of the kelly 12 which radii is greater than the radial distance from the central axis to the midpoint on each of the drive sides 32.

In FIG. 3b which is an illustrative cross-sectional view of the improved kelly 12 represented in solid lines a, a hexagonal kelly represented in dashed lines b, and a square kelly represented in dotted lines c, the cross-sectional areas of comparable square, hexagonal, and the improved kelly are shown. As discussed herein, comparable size kellys are those kellys which can be received by a standard size casing.

As can be easily seen and readily calculated from FIG. 3a, the cross-sectional area of the square kelly "c" is less than the cross-sectional area of the hex kelly "b" which is less than the cross-sectional area of the improved kelly "a". For comparable kellys, the cross-sectional area of the improved kelly "a" is approximately 10% more than a hex kelly and approximately 36% more than a square kelly. This results in the improved kelly being approximately 29% stronger in bending, 12% stronger in tension, and 32% stronger in torsion when compared to the drive section of a hex kelly.

Furthermore, it can be appreciated from FIG. 3a that the drive section of the improved kelly has corner supports which decrease the tendency of the corners to roll over as experienced with the corners of the hexagonal and square kelly.

The unique shape of the improved kelly incorporates more steel for higher strength and longer life. For comparison of the improved kelly to square and hexagonal kellys, the following table is provided. It should be noted here that all values have no safety factor and are based on 110,000 psi minimum tensile yield strength and a shear strength of 57.7% of the minimum tensile yield strength. Furthermore, the values for the improved "a" kelly appear in the second column of the first three headings and in the second and fourth columns of the fourth heading.TABLE I

STRENGTH OF KELLY DRIVE SECTIONS Tensile Torsional Minimum Yield of Yield of Yield in Bending Kelly Recommended Drive Drive ft.-lbs. Kelly Size Bore Casing O. D. Section Section Through On Through On and Type In. In. lbs. ft.-lbs. Corners Radius Faces Flat

The unique shape of the drive section 30 of the improved kelly 12 insures that the kelly 12 is always centered in the drive bushing 14 and thus wear and vibration are reduced. Another advantage of this improved kelly is that it has higher tensile, bending, and torsional strengths than comparable hexagon or square kellys. Furthermore, the improved kelly 12 has a more uniform bending strength which means it is more resistant to bending in all directions than hex or square kellys of comparable size and thus decreases the tendency of the kelly to bend which is commonly due to dropping, side pull during make-up, and improper tie-down, loading or unloading procedures. Further, the improved kelly 12 is less susceptible to fatigue due to the fact that the larger cross-sectional area lowers the stress level in the drive section 30 and increases the fatique limits thereby enabling the kelly 12 to be better able to tolerate derrick misalignment and drill ship motion. The improved kelly 12 does not have corners susceptible to being rounded off due to wear as on hex and square kellys, thus, prolonging the useful life of the kelly.

As mentioned earlier, the kelly 12 is rotatably driven by an improved kelly drive bushing 14 which will now be discussed in further detail with specific reference to FIGS. 4 and 5.

The drive bushing 14 is similar in construction to known four roller drive bushings, such as the one shown and described in the above-referenced U.S. Pat. No. 3,513,665, but has been modified in structure to include three rollers 36, 38 and 40 that evenly transmit torque to the three flat drive surfaces 32 of the kelly drive section 30 simultaneously. The bushing 14 is of integral construction, preferably a casting, including a rigid tubular main body portion 42 having a longitudinally extending central opening for receiving the kelly 12 therethrough, an upper generally circular cap portion 44, and a lower end portion with an outwardly extending generally square flange 46. Mounted on and extending downwardly from the respective corners of the flange 46 are four short pins 48 that form the pin drive means of the kelly. The pins 48 are received in mating apertures provided in the upper surface of the master bushing 16 (FIG. 1). The bushing 14 is additionally provided with a generally cylindrical tubular downwardly longitudinally extending centering skirt 50 rigidly fixed to the undersurface of flange 46 and coaxial with the central opening.

Each of the rollers 36, 38 and 40 are rotatably mounted between pairs of integral rib members 52 that extend generally vertically between the respective upper and lower end portions 44, 46 of the bushing 14. Only one pair of rib members 52 are shown in FIG. 4. The three pairs of rib members 52 are positioned approximately 120° apart about the central axis of the bushing 14 such that the rollers 36, 38 and 40 are disposed approximately 120° from one another. The axis of the rollers 36, 38 and 40 lie in a generally horizontal plane which plane is generally parallel to flange 46. Additionally, the axes of the rollers 34, 36 and 38 are positioned such that extension thereof would form an equilateral triangle.

With particular reference to FIG. 5, each rotatably mounted roller 36, 38 and 40 has a cylindrical outer surface that forms a line of engagement with the respective flat drive sides 32 of the kelly drive section 30 which line of engagement lies essentially in the respective planes defined by the respective drive sides 32 for simultaneous drive engagement of the drive sides of kelly 12. As can be seen in this three roller design no roller is directly opposite another, instead, each is offset 120° from the other two. Thus, the rollers 36, 38 and 40 transmit rotary torque equally and smoothly, keeping the kelly 12 centered and fully supported at all times. This reduces impact loading on the drive system caused by bending loads, kelly to drive roller clearances, and derrick misalignment.