EP1226330B1 - Rangement horizontal de tiges de forage et systeme de distribution - Google Patents

Rangement horizontal de tiges de forage et systeme de distribution Download PDF

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Publication number
EP1226330B1
EP1226330B1 EP00970530A EP00970530A EP1226330B1 EP 1226330 B1 EP1226330 B1 EP 1226330B1 EP 00970530 A EP00970530 A EP 00970530A EP 00970530 A EP00970530 A EP 00970530A EP 1226330 B1 EP1226330 B1 EP 1226330B1
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EP
European Patent Office
Prior art keywords
pipe
array
stand
cart
drill
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00970530A
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German (de)
English (en)
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EP1226330A1 (fr
EP1226330A4 (fr
Inventor
Vance E. Bolding
Andrew J. Brooks, Iii
Michael D. Keen
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Global Marine Inc
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Global Marine Inc
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Publication date
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Publication of EP1226330A4 publication Critical patent/EP1226330A4/fr
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
    • E21B19/09—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods specially adapted for drilling underwater formations from a floating support using heave compensators supporting the drill string
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/002—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables specially adapted for underwater drilling
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
    • E21B19/14—Racks, ramps, troughs or bins, for holding the lengths of rod singly or connected; Handling between storage place and borehole
    • E21B19/15—Racking of rods in horizontal position; Handling between horizontal and vertical position

Definitions

  • This invention pertains to structures and procedures for horizontally storing drill pipe adjacent to and preferably below the level of the drill floor of a well drilling installation. It also pertains to structures and procedures for moving stands of drill pipe between their storage locations and the drill floor.
  • Drill pipe is one of the items affected by the increase in water depth.
  • drilling operations were performed in water depths of a few hundred meters using 5 inch (12.7 cm.) drill pipe weighing 21.5 pounds per linear foot (30.6 Kg./m) including the connecting tool joints.
  • triples for deep water drilling operations are made up of 5 inch (12.7 cm.) drill pipe weighing about 31 pounds per linear foot (46.3 Kg./m.), 5.5 inch (14.0 cm.) drill pipe weighing about 34 pounds per linear foot (50.8 Kg./m.), and 6.625 inch (16.8 cm.) drill pipe weighing up to 46 pounds per foot (68.7 Kg./m.).
  • the weight of drill pipe triples made up of these heavier pipes is about 2880 pounds (1309 Kg.) for the 5 inch drill pipe, about 3160 pounds (1436 Kg.) for the 5.5 inch drill pipe, and about 4300 pounds (1955 Kg.) for the 6.625 inch drill pipe.
  • the drill pipe used for deep water drilling is made from low alloy steel which has been heat-treated to high strengths.
  • the material is stressed to high levels in use and, therefore, must be maintained free from significant scratches, gouges and other imperfections which can act as stress risers.
  • To get the maximum life out of drill pipe it must be protected from being scratched and gouged while it is being handled between a pipe storage location and the drill string where it is used. Drill pipe which is damaged beyond rigorous low damage limits must be discarded.
  • Horizontal pipe rackers commonly are used in floating offshore drilling rigs, especially those of ship-form configuration, because they contribute to the floating stability of the rig; they lower the position in the rig of the stored drill pipe.
  • Horizontal pipe rackers store drill pipe triples in a horizontal position and include devices and mechanisms which transport the pipe, in either direction, between the pipe racker and the drill floor. At the drill floor, drill pipe from the racker is moved into a vertical position and is inserted into (connected to) the drill string.
  • Horizontal pipe rackers currently in use typically store several stands of drill pipe triples in a single bin. When the pipe is put into and removed from the bin, it is rolled down an incline to an indexing device that allows only one stand of pipe to be placed on a transporting device. The rolling produces sliding and impact loading between adjacent drill pipe triples and between drill pipe and the stationary pipe stops. While the pipe is stored in the bins, it can roll back and forth in response to the vessel's own motions thus causing wear and damage between adjacent drill pipe triples.
  • Some pipe rackers prevent the drill pipe movement by storing each stand of pipe in a separate locking mechanism, a tactic that generally limits the drill pipe to only one size.
  • the current method of transporting the drill pipe stands between the drill floor and the drill pipe racker involves sliding the pipe along a long trough causing further wear and scratching along the pipe where it contacts the trough.
  • US Patent 4,129,221 describes equipment for shipboard storage and handling of tubular elements of different types in the course of drilling subsea oil and gas wells.
  • the different types of tubular elements are: drillpipe which is handled as individual lengths and as double and triple stands; individual lengths of casing pipe for lining a well bore as it is drilled and through which drilling operations are performed; and individual lengths of large buoyant riser pipe which, when installed, effectively extend the well casing from a subsea wellhead to a surface drilling facility.
  • the drillpipe is stored in a racker which is arranged to roll pipe along tiltable support arms to and from elevators for the pipe, and to roll drillpipe between the elevators and an elongate transfer cart which functions to move drillpipe stands from the racker to the floor of a drilling rig.
  • the individual lengths of casing and riser pipe are stacked in vertical open-top bins.
  • An overhead bridge crane is provided to move casing and riser pipe lengths between the bins and the transfer cart.
  • US Patent 3,979,994 describes a movable pipe racker for drillpipe stands.
  • the pipe stands When stored, the pipe stands are in an array of plural vertically spaced layers in which there are plural stands in each layer. In each layer, the stands are supported in upwardly open notches formed in pipe support arms.
  • the arms which support the bottom layer cannot move from a horizontal position; each arm above those bottom arms rests on pipe stands carried in the arms below it, and those arms are hingeable when empty to vertical positions adjacent one end of the array.
  • All pipe stand support arms are mounted on a carriage which is movable laterally of the stand lengths to move the array toward and away from a mechanism which lifts individual stands from the support arms and moves lifted stands between the movable racker and a drilling rig floor.
  • This arrangement is for use in land-based operations; the use of laterally movable pipe rackers in shipboard contexts, where the vessel can roll from side to side, is seen to be very dangerous.
  • This invention meaningfully addresses the needs noted above. It does so by providing structural and procedural aspects of a horizontal drill pipe racking and handling system.
  • the system avoids the disadvantages and limitations of former horizontal pipe rackers and pipe delivery arrangements.
  • the system possesses the above-mentioned desirable attributes and characteristics, as well as others.
  • drill pipe storage apparatus having
  • a method of storing oil and gas well drill pipe in which a selected number of pipe lengths are disposed, as a first bottom layer, individually in upwardly open notches of a set of stationary pipe supports disposed transversely of the pipe lengths at stations spaced along the lengths, and further numbers of pipe lengths are disposed in further similarly notched pipe support sets placed at each station atop the supports therebelow in a stationary array of plural layers of plural pipe lengths, and characterized by selectively moving the pipe supports between deployed positions in the array and horizontal retracted positions in which the pipe supports are received from the array.
  • the improved horizontal drill pipe racker provides positive control of the drill pipe stands at all phases of handling.
  • the drill pipe is safely secured while stored in a bin area.
  • Positive control of the drill pipe allows higher operating speeds to be achieved and reduces the time required to transfer drill pipe between the horizontal pipe racker and the drill floor.
  • the time required to transfer drill pipe from the pipe racker to the drill floor is sufficiently low to keep pace with the drill floor operations.
  • the invention provides a drill pipe storage and handling apparatus for a well drilling rig.
  • a track extends from one end adjacent the drilling rig to an opposite end remote from the rig.
  • An elongate carriage is adapted to travel along the track and to receive a length of drill pipe disposed longitudinally with respect to the track.
  • a received pipe length is supported on the carriage at spaced locations along the length of the pipe.
  • a pipe storage bin is disposed laterally of the remote end of the track.
  • the bin includes horizontal pipe support members which are cooperatively configured for individually supporting plural lengths of drill pipe in an array of plural vertically spaced layers of pipe and plural lengths of pipe in each layer.
  • the pipe support members above the bottom layer are indexable between deployed positions in and transversely of the array and retracted positions outside the array.
  • the method includes the step of horizontally disposing a selected number of pipe lengths, as a first bottom layer thereof, individually in upwardly open notches in the upper extent of a set of pipe supports disposed transversely of the pipe lengths at stations spaced along the lengths.
  • Another method step is horizontally disposing further numbers of pipe lengths in further similarly notched pipe support sets at each station atop the supports therebelow to create an array of plural layers of plural lengths of pipe.
  • a further step of the method is raising and lowering individual pipe lengths directly from and to receiving notches in the pipe supports.
  • a method for storing, handling and moving drill pipe in association with a well drilling rig having a drilling operations floor includes lifting a stand of drill pipe directly from an individual storage position in an array of stand storage positions. Another step is placing the lifted stand on a carriage adapted to support the stand at spaced locations along its length. The carriage is moved towards the floor to place one end of the carriage at the floor. Another step is elevating the one end of the placed stand above its placed positions on the carriage as the carriage nears the floor. The stand is hoisted via its one end to a vertical position above the floor while the other end of the stand is movably supported on the carriage.
  • a pipe racker system includes a main foundation and support structure, multiple levels of indexable sleepers which define racks on which pipe is stored horizontally, a mechanism, such as a bridge crane, to transfer drill pipe stands between the sleepers and a drill pipe transporter, a drill pipe transporter to transport the pipe between the pipe racker and the drill floor, and a control system to provide the man-machine interface and to perform automatic control functions and to enable manual control operations to be performed.
  • the drill pipe transporter preferably includes a carriage system which is comprised of a skate cart movable between the vicinity of the sleepers and the drill floor at the level of the floor, a further cart on the skate cart for receiving and supporting the pin end of a pipe stand being moved to or from the sleeper array.
  • the drill pipe transporter also comprises low and high lift mechanisms for elevating and lowering the box end of a pipe stand from and to the skate cart at the drill floor, and a pipe stabber at the drill floor for guiding the lower end of a pipe stand between the carriage system and the vertical axis at the drill floor at which drilling operations are performed.
  • a pipe storage and handling system includes a track which extends from one end adjacent the drilling rig to an opposite end remote from rig floor.
  • the skate cart travels along the track and protectively supports a length of drill pipe disposed longitudinally with respect to the track.
  • a pipe storage bin is disposed laterally of the track.
  • the bin includes the horizontal pipe support sleepers which are cooperatively configured for individually supporting plural drill pipe lengths in an array of plural vertically spaced layers of pipe lengths with plural lengths in each layer.
  • the array of sleepers is effective to support the pipe without subjecting any pipe length in the array to loads due to pipes and sleepers above or adjacent to it in the array.
  • the storage bin also includes drive mechanisms connected to the pipe support sleepers. The drive mechanisms are selectively operable to move the individual sleepers between positions in which the sleepers are in the array and positions in which the sleepers are removed from the array when not supporting a drill pipe length.
  • the system also includes a pipe lifter.
  • the pipe lifter is disposable above the sleeper array and is operable to move individual pipe lengths between the array and the carriage. More particularly, the pipe lifter can include several controllable magnetic pipe lifting heads which are spaced from each other along the length of the sleeper array. The several lifting heads are effective to lift and to hold a pipe length.
  • the lifter preferably also includes indexable mechanical safety supports which are movable into and out of supportive relation to a pipe length which has been lifted by the lifting heads.
  • the pipe lifter preferably includes a bridge crane above and movable between the skate cart track and the pipe storage bin. The crane includes mechanisms for raising and lowering the several lifting heads and the safety supports if present in association with the lifting heads.
  • the control subsystem preferably monitors the position of the lifting heads and permits effective demagnetization of the lifting heads only when the load of a pipe length held by the heads has been accepted by the carriage or by pipe support sleepers in the bin.
  • the control subsystem can be defined to operate at desired times and in desired sequences in a semiautomatic manner.
  • the system preferably includes a second pipe storage bin disposed on the other side of the skate cart track from the first bin.
  • a second pipe lifter preferably is provided for the second bin.
  • the two pipe lifters preferably are arranged to service either bin providing redundancy of pipe lifters.
  • the pipe storage and handling system also has procedural aspects which are described or made apparent from the following descriptions of presently preferred and other embodiments of the system.
  • FIGs. 1A and 1B and FIGs. 2A and 28, respectively, are side elevation and top plan views of a pipe storage and handling system 10 according to this invention.
  • the system includes a horizontal pipe racker subsystem 11 which is supported on the main deck 12 of a deepwater drillship by a substructure 13; it is within the scope of this invention to locate racker 11 directly on deck 12 or upon such other foundation as may be appropriate to the nature and location of the operations supported by the racker and other associated structures described below.
  • the racker substructure has a height on the order of 20 feet (6.1 meters).
  • Racker 11 is shown to be located in the drillship forward of a drilling rig 15 which is supported on the vessel main deck by its own substructure 16 which locates a floor 17 of a drilling platform a desired distance above the main deck.
  • Drilling rig 15 is located over a vertical passage 14 through the drillship hull.
  • the racker substructure serves, among other things, to elevate racker 11 above main deck 12 adequately that the path of fore-and-aft movement of a drill pipe skate cart assembly 18 is horizontal and is substantially at the same height as the drill floor above the main deck.
  • the skate cart assembly provides a carriage which transports drill pipe stands in a fore-and-oft direction within system 10.
  • a portion 21 of the skate truss 19 just forward of the drill rig can be removable to enable a transversely movable bridge crane 22 to be used to move a blowout preventer, or other equipment as needed, into position on the vessel centerline before being moved rearward into alignment with a vertical well centerline 23, i.e., the drilling axis as defined in the drilling rig.
  • the removable portion of the skate truss when in its installed position shown in FIG. 1A, preferably is supported at its opposite ends on the elevated athwartships rails and rail supports 16 provided for crane 22.
  • the drilling rig 15 is located at about amidships of the vessel hull over the vertical passage 14 (known as a "moonpool") through the hull.
  • the rig includes a derrick (not shown) equipped with a crown block atop the derrick, a traveling block in the derrick, and a drawworks operable for raising and lowering the traveling block along well centerline 23 above the rig floor.
  • the drawworks also can be operated to raise and lower other blocks or lifting hooks in the derrick, and to perform other functions as known in the oil and gas drilling industry.
  • Skate cart 18 and skate truss 19 are components of a pipe handling subsystem in the overall pipe storage and handling system 10.
  • the structure of racker 11 includes an assembly 26 composed of a relatively massive base 24 and of columns 25.
  • Assembly 26 preferably is constructed to be stiff and rigid in its own right.
  • the substructure 13 which supports that assembly on the vessel main deck both supports and secures the assembly in place as a part of the ship structure and substantially isolates that assembly from bending deflections in the ship hull.
  • Positions A, B and C, positions D, E, and F, and positions G, H and J are each arrayed along lines transverse to the vessel centerline respectively at the rear, center and forward positions of the racker. Those columns at positions A, D, and G are located on a line to port of and parallel to the centerline, those at positions B, E, and H are on the centerline, and those at positions C, F and J are on a line to starboard of and parallel to the centerline.
  • the columns at the corner positions A, G, C and J are of the same height which is greater than the height of the centerline columns and the outboard center columns D and F.
  • the upper ends of the outboard column pairs at the forward and aft portions of the racker are interconnected by transverse beams 27 which have outboard extensions from those columns, as shown in FIGs. 5 and 6.
  • the space below the upper ends of the centerline columns and between those columns and the port outboard columns comprises a port pipe storage bay or bin 28.
  • a starboard pipe storage bay or bin 29 is formed below the tops of the centerline columns and between those columns and the starboard outboard columns.
  • the centerline columns support corresponding portions of skate truss 19.
  • Columns 25 are interconnected at their bases by longitudinal and transverse girders which are components of base 24.
  • transversely aligned outboard corner columns and their interconnecting beams 27 support transversely oriented forward and aft guide and support rails 31 for a pair of longitudinally extending port and starboard bridge cranes 32 and 33, respectively.
  • Additional vertical members are located in the racker along the outboard sides of storage bins 28 and 29, as at 34 in FIG. 1B.
  • a transverse vertical plate 35 attached to structural members, is located at each of the ends of the bins and supports wooden buckboards 36 which face toward the respective bins.
  • the buckboards limit fore and aft sliding motion of pipe stands which are individually supported in the racker without damaging the threaded connection features at the ends of the stands.
  • the cross-hatched area in FIG. 7 represents the vertical and forward limits of the volume in the racker in which a triple stand of drill pipe can be found either when stored in the racker or when being moved in a horizontal attitude within, to or from the racker.
  • the racker structure includes means for individually supporting each triple stand of drill pipe which is to be stored at any time in the racker.
  • Those means include a plurality of horizontal sleepers 38 and 39 which cooperate with each other and with the stands in the manner shown in FIG. 13.
  • Sleepers 38 are movable, whereas bottom sleepers 39 are fixed and are carried by the transverse portions of the racker base 24 as shown in FIG. 6.
  • the movable sleepers are sufficiently long that, when in their deployed positions, they extend across the entire width of the respective pipe storage bin between transversely aligned ones of columns 25.
  • the pipe stands are stored in an array of layers in each of bins 28 and 29. there being plural stands in each layer. Except for the stands in the topmost layer, each stand is disposed between two vertically adjacent sleepers.
  • the vertically adjacent sleepers are configured to keep adjacent stands in a layer in spaced relation to each other, and to carry the vertical loads of sleepers and of stands supported by the sleepers to the racker base 24 within the sleepers themselves and not through any stands in the storage array.
  • the arrows in FIG. 13 represent the way in which vertical forces are carried in the deployed sleepers around the pipe stands received in the sleepers.
  • the only forces applied to a stand when stored in the racker are the forces attributable to that stand itself due to its own weight and due to motions of the drillship.
  • a given stand, when stored in the racker does not have applied to it any portion of such forces associated with any other stand.
  • sleepers 38 and 39 are provided at each of three stations spaced along the length of each pipe storage bin.
  • the fixed sleepers 39 are notched at intervals along their top surfaces.
  • the movable sleepers 38 are similarly notched at the same intervals along the top and bottom surfaces.
  • the upwardly opening 41 notches have sloping sides; the downwardly opening notches 42 can be accurately shaped.
  • the cooperating notches in vertically adjacent sleepers are sized so that a pipe stand 43 disposed in the space formed by a notch 41 and a notch 42 contacts only the upwardly opening notch 41. Therefore, the stand is not subjected to any forces attributable to sleepers or stands above it in the bin in which the stand is stored.
  • the sloped surface of upwardly opening notches 41 can be defined by wood or by pieces of other materials which are softer than the metal of a pipe stand and which preferably cannot participate in electrolytic corrosion processes with the pipe.
  • Each cooperating pair of notches 41, 42 has sufficient open area that the sleeper array can accept pipe of either a specified diameter or with a defined range of diameters with variations from truly straight to in excess of 0.2 percent of pipe length deviation from truly straight.
  • the stacked sleepers are mechanically keyed and interlocked between adjoining sleepers to prevent one sleeper from deflecting sideways relative to the long dimension of the sleeper; see FIG. 14. This assures the sleeper stack will remain aligned one sleeper above the other and that the drill pipe loads will follow a path down through the stacked sleepers to the base crossbeam supporting it.
  • the notches 41, 42 in the sleepers preferably are configured to allow the notches to accommodate drill pipe ranging in diameter from 5 inches (12.7 cm) to 6.625 inches (16.8 cm); alternatively, the sleepers can be notched to accommodate a given size of pipe, thereby maximizing the number of stands disposable in a layer of the storage array, and the sleepers can be disconnectable from their indexing drive mechanisms and supporting bases to enable one sleeper to be exchanged for another of different capacity.
  • the sleepers cooperate with pipe stands at locations along the stands between the pin and box features at the opposite ends of each of the individual pipe lengths forming the stands.
  • the sleepers are mounted to be indexed to lift them off the sleeper below and to rotate them out of the pipe bin to expose the next layer of drill pipe stands. Conversely, when a sleeper becomes filled with a drill pipe stand in each notch 41, the next sleeper above is rotated to a position over the stack of sleepers below and then lowered until it rests on the topmost sleeper below. That mechanically locks the two sleepers together and contains the layer of drill pipe below the sleeper between the sleeper supporting the pipe and the one placed over it.
  • Drill pipe stands are moved between the sleepers in the pipe bins and the pipe transporter (i.e., skate cart 18) by means of a special bridge crane illustrated in FIGs. 1B, 2B, 4, 5 and 6.
  • a special bridge crane illustrated in FIGs. 1B, 2B, 4, 5 and 6.
  • Each bridge crane spans the distance between the two crane rails 31 at the ends of the pipe racker.
  • Self-propelled trucks 44 at the ends of the bridge crane run on the rails 31 and drive the crane from one side of the pipe racker to the other.
  • the rails 31 preferably are channel-like in cross-section, and the crane truck wheels preferably run in the channels so that the trucks are captive to the rails; see FIG. 6, e.g.
  • the trucks of each bridge crane are synchronized to make them move together in unison.
  • a set of two or more (preferably three) vertical lift members (columns) 45 are mounted in the crane bridge and are constrained to move only up and down relative to the bridge.
  • the lift columns in each bridge crane are synchronized to move together and are connected at the lower ends by a long beam identified as a strongback 46, also called a spreader bar.
  • the strongback is a carrier for permanent magnet lift heads 47 which function to attach to a stand of pipe and to release it when the magnetic field is broken.
  • the magnetic lift heads which make contact with the drill pipe are in the form of two long permanent magnet bars and preferably are arranged in a manner that they form an upside down trough. While the trough can be "V" shaped (see FIG 23), it is preferred that the trough be semicircular, most preferably with a radius which fits the pipe being handled.
  • the trough lays parallel to the direction of the drill pipe.
  • the magnets preferably are attached to the strongback in a way that the they can rotate and translate in small amounts to allow the them to align themselves with the drill pipe being picked up. Aligning the magnetic heads with the drill pipe greatly increases the contact area between the pipe wall and the magnetic heads and hence maximizes the holding capacity of each magnetic pipe lifter.
  • the pipe stand lift heads are described more fully below with particular reference to FIGs. 21-23.
  • a chosen one of bridge cranes 32, 33 moves sideways on its bridge trucks from a transfer position over the transporter to a discrete position over the drill pipe stand to be transferred; while both cranes can be operated concurrently, it presently is preferred to operate only one crane at a given time.
  • the strongback is lowered by the vertical lift members 45 until the magnetic lift heads 47 are in contact with the drill pipe.
  • the magnetic fields generated by the lift heads are effective to attach the lift heads to the drill pipe.
  • the lift members are then raised to their highest positions in the bridge crane with the drill pipe coupled to the strongback by the magnets.
  • the bridge crane moves from its position over the pipe bin to a position directly over the drill pipe transporter which is located along the center of the racker below the transfer position of the crane.
  • the strongback is lowered until the drill pipe rests on the transporter skate cart, with the pin end of the pipe stand engaged in the pin cart; only then the magnetic fields are killed to release the drill pipe.
  • the bridge crane raises the strongback to its full upper position and then moves to pick up the next stand of drill pipe from a pipe storage bin.
  • Moving drill pipe from the drill pipe transporter to a pipe bin is the reverse of moving the pipe from the pipe bin to the transporter.
  • the bridge crane picks up the drill pipe from the drill pipe transporter at the transfer position of the transporter carriage.
  • the crane moves it to a specified open slot (position) in a pipe bin sleeper set.
  • the pipe stand is released from the lifting heads after the weight of the stand has been accepted by the pipe support sleepers.
  • the bridge crane When a bridge crane is operating semi-automatically, the bridge crane will always stop at its transfer position above the transporter.
  • the pipe is lowered to and released on the transporter only by direct manual command from a control console.
  • the strongback when the strongback is waiting over the transporter to pick up a drill pipe, it will commence lowering and attaching to the drill pipe only when it is commanded to do so from the control console.
  • This feature helps avoid several hazards that otherwise would have to have sophisticated interlocks to prevent.
  • the drill pipe will not be lowered and released when the transporter is not in position to receive it.
  • the drill pipe will not be lowered or released while the transporter is still moving. Adherence to those rules simplifies the racker system controls and timing since the bridge crane always starts a cycle from a "hold” at its transfer position and ends the cycle at the same position. It does not have to be timed to meet the drill pipe transporter.
  • the drill pipe transporter (see FIGs. 8, 9 and 10) moves the drill pipe between the horizontal pipe racker where the drill pipe is stored and the drill floor where the pipe is used.
  • the transporter pipe carriage arrangement preferably is comprised of the long skate cart 18, a second cart-like device identified as a pin cart 49, and drive systems (not shown in FIGs. 8, 9, and 10) to move the skate and pin carts.
  • the pin cart is carried by and is driven along the skate cart.
  • the skate cart preferably is about 88 feet (26.8m) long and the drill pipe stand being transported will range from about 91 feet (27.7m) long to about 95.5 feet (29.1m) long.
  • the drill pipe stand being transported on the skate cart will extend at its rear or box end beyond the rear end of the skate cart from 3 feet (.9m) to 8 feet (2.4m).
  • the remaining length of the drill pipe will be cradled on the skate cart, and the forward pin end of the pipe stand will be carried in pin cart 49.
  • the skate cart rides on wheels that run captively in channels affixed to the skate truss. The channels are installed on the skate truss 19 and run from the end of the pipe racker farthest from the drill floor to the drill floor.
  • the pin cart rides on wheels which captively engage tracks mounted on the skate cart, thus allowing the pin cart to move relative to the skate cart.
  • the pin (forward) end of the pipe rests in the pin cart while the box (rear) end of the drill pipe extends over the other end of the skate cart.
  • the box end of the drill pipe is raised by a low-lift pipe lifter 52 and is held about 4 to 5 feet(1.2 to 1.5 m) above the drill floor.
  • An elevator typically carried by the traveling block in the drill rig derrick, is attached to the box end of the drill pipe so held above the drill floor, and the box end of the drill pipe is lifted up above the drill floor by the drawworks and traveling block.
  • the skate cart will continue to travel toward the drill floor until it reaches its rearward limit. Then the pin cart holding and supporting the pin end of the drill pipe will move along the skate cart toward the drill floor with the pin end of the pipe as the pipe is raised and rotated from a horizontal to a vertical position in the derrick.
  • the drill pipe becomes nearly vertical, it is lifted off the pin cart and installed in the working drill string; before the drill pipe is lifted off the pin cart and until it has been made part of the working drill string, it is held in the head 72 of pipe stabber 73.
  • the pin cart is moved back to the other end of the skate cart, preferably as the skate cart is returned to its position forward in the pipe racker.
  • FIGs. 5 and 6 show in elevation views the port and starboard pipe storage bins.
  • one bin is shown full and the other is shown empty with all movable sleepers 38 removed from the bin volume.
  • each sleeper 38 has a deployed position in which it extends from its supporting outboard column 25 to the adjacent centerline column.
  • Each sleeper also has a retracted position which is disposed at a 90° relation to its deployed position and in which the sleeper is outside the outboard side of the bin as defined by the inboard faces of the outboard columns; see, e.g., FIGS. 1B, 4, 7, 11, 12, 17 and 18.
  • each bin there can be 18 movable sleepers 38 in each bin in association with each outboard racker column 25; fewer or more sleepers can be provided, as desired.
  • That set of 18 sleepers is composed of a group of 9 even numbered sleepers and a group of 9 odd numbered sleepers.
  • the odd numbered sleepers in the set are associated with the aft face of the adjacent outboard column, while the even numbered sleepers in that set are associated with the forward face of that same column.
  • FIG. 12 shows 19 movable sleepers associated with a racker column.
  • each sleeper 38 is connected to a base 54 which preferably is L-shaped in plan view.
  • Each base has a major leg defined by an elongate frame 55 which is parallel to the related sleeper.
  • Each base also has an arm 56 which extends laterally from one end of the frame and to which one end of the sleeper is connected.
  • the end of frame 55 opposite from arm 56 defines a vertically oriented sleeve-like hub 57 which encircles two vertical bearing tubes 58 in one form of sleeper mounting and indexing arrangement of this invention; see FIG. 11A.
  • the bearing tubes 58 are vertically in line with each other, one being at the bottom of the hub 57. the other at the top of the hub 57.
  • the two bearing tubes 58 are separated by a distance of about 3 inches (7.6 cm).
  • the separation between the bearing tubes 58 provides an opening through which a fork 62 can move to engage with or disengage from a vertical, notched shaft 60 in FIG. 11A.
  • shaft 60 Adjacent each of those openings between the bearing tubes 58 in each sleeper hub, shaft 60 is notched in parallel diametrically opposed locations; the notches form aligned horizontal keyways in the shaft, as at 63 in FIG. 11A.
  • the vertical shaft 60 preferably is of sufficiently long extent that it is common to all the sleepers in a group; there are two shafts 60 associated with each outboard column 25, one for each sleeper group at that column.
  • Each shaft 60 is axially and angularly movably mounted to the column 25 via support brackets 59 spaced along the vertical length of the shaft 60 between vertically adjacent sleepers.
  • Each bracket 59 is comprised of a structure attached to the column on one end and attached to a vertically oriented sleeve-like hub and a tube bearing similar to the sleeper hub 57.
  • the vertical shaft 60 is free to move vertically and to rotate in all the support brackets 59, and in the sleeper hubs 57 except when a selected fork 62 is engaged in a corresponding pair of aligned notches on the shaft. In that case, the sleeper associated with the engaged fork will move angularly and vertically with the shaft 60.
  • Axial and angular motions of each shaft are produced by suitable drive mechanisms 53 (see FIG. 1B) which can be located along side the racker base 24 and to which the lower end of the shaft extends.
  • each sleeper base frame preferably carries a double acting ram 61, preferably a pneumatic ram, which is coupled adjacent the base hub to a horizontally slidable fork 62 which opens toward shaft 60.
  • the fork is movable horizontally through the opening between the bearing tubes 58 in the adjacent hub 57 into engagement of its two legs in the keyway notches 63 in the shaft.
  • Engagement of a fork with the shaft connects the corresponding sleeper and its base to the shaft so that the sleeper can be moved vertically and angularly by axial and angular motion of the shaft.
  • Each fork can be fully disengaged from the shaft 60.
  • sleeper 38 of FIG. 11 which lies in the bottom left portion of FIG. 11. That sleeper is in its retracted position and is supported about midway along its length in a holder and support bracket 64 carried by a racker side member 34. That sleeper is to be moved to its deployed position in the adjacent pipe storage bin; the other sleeper depicted in FIG. 11 is shown in its deployed position. Movement of a sleeper from its retracted position to its deployed position is achieved by the following operations:
  • the control arrangement for system 10 preferably includes sensors and interlocks which monitor the retracted/deployed status of each sleeper in each pipe storage array, and which assure that only the proper sleepers are engaged with and moved by shafts 60 at any time during loading or unloading of drill pipe into or from each pipe storage bins. If, for some reason, one or more sleepers in a set fails to deploy or to retract when commanded, the operator is alerted and a signal is provided to the control system to prevent the crane in service from lowering pipe until the sleeper positioning issue has been addressed. It is preferred to index the set of sleepers for a given layer of a bin in unison.
  • FIG. 11 shows the benefit of mounting each movable sleeper 38 to an L-shaped base 54. That geometry of the sleeper base enables the hinge structures, about which the bases swing as the sleepers move between their deployed and retracted positions, to be located adjacent to the outboard corners of the outboard columns 25 of the racker. When the sleepers are retracted, they are located outside the adjacent pipe storage bin. When they are deployed, the L-shaped sleeper bases wrap around the adjacent column so that the sleepers extend transversely across the bin and span the space between the corresponding outboard column and the related center column.
  • FIG. 11 also shows that a brace 65 can be connected from the unhinged end of each sleeper base frame to a point on the sleeper which is near its midlength. Braces 65 can lie in planes between the upper and lower surfaces of the sleepers and so will not interfere with the drill pipe lengths racked on the deployed sleepers.
  • FIGs. 5 and 12 e.g., show how the odd and even numbered sleepers in each sleeper set interdigitate in their deployed positions.
  • Each bridge crane lift column 45 preferably is driven vertically, in one method, by a pair of drive motors 67 (see FIG. 4, e.g.) which drive pinions meshed with a respective one of a pair of racks which are carried along opposite sides of the lift columns.
  • the lift columns maybe raised and lowered by a single shaft having three pinions to engage the corresponding racks on the three lift columns.
  • control subsystem of system 10 receives information about the current position of each bridge crane 32, 33 and about the vertical position of the pipe lifting heads 47 carried by each bridge crane. It is also important that all lift columns on a bridge crane be operated in close synchronism, and that the self-propelled trucks 44 at the opposite ends of each bridge crane be operated in close synchronism. Synchronizing and position informative signals preferably are generated by each lift column drive mechanism and by each bridge crane truck as they are operated. Those signals can be generated in similar ways. For example, as a bridge crane traverses racker 11 on its support rails 31, it can operate switches which are spaced along each track. Also, as each crane truck moves, rotation of one of its drive shafts can operate an encoder.
  • the encoder output signals generated by the trucks at the opposite ends of the crane can be compared and the result used to synchronize the operation of the trucks. Operation of the switches along the crane rails can be used to periodically reset the encoders.
  • the combination of switch signals and encoder signals can provide high precision information about the location traversely of the racker of the pipe lifter heads carried by the crane. Similar switches and encoders can be used in the lift column drives to synchronize the motions of the several columns in each crane and to provide high-precision information about the vertical position of the crane's pipe lifter heads.
  • Switches operated by the sleepers can indicate whether a sleeper is deployed or retracted. Combining the disposition of the sleepers and their known height with the vertical position of the lift columns is sufficient information to accurately position the vertical lift columns and the magnetic heads to pick up or set down pipe in the sleepers. Also, it is preferred that the sleepers have associated with them sensors which are effective to detect the presence of personnel on the sleepers or on the top pipe stands supported by the sleepers.
  • FIG. 6 shows that the bridge cranes 32, 33 can have stowed positions outboard of the pipe storage bins on the positions of rails 31 which extend laterally away from the pipe storage bins.
  • the lift columns for the cranes can be lowered to essentially fully depend from the crane truss (bridge) structures and trucks.
  • the crane lift columns and the structures carried by the lower ends of those columns can be secured from pendulous motion by being connected to keeper brackets 68 which preferably extend outwardly from the racker sides.
  • This storage ability for the bridge cranes and their lift columns is especially useful in the context of use of racker 10 on a floating vessel. Weather or sea state conditions may make it prudent and desirable to discontinue drilling operations for a time. During that time, the cranes are stowed as described and their lift columns are secured from pendulous motions which otherwise could result in damage to them or to other components of the racker.
  • FIGs. 8 and 9 respectively are top plan and side elevation views of skate cart 18.
  • the skate cart has an elongate horizontal, rather narrow truss-like frame 70 shown in FIG. 8. At spaced locations along its sides, frame 70 is supported by wheels which run captively in tracks which extend along the top of the skate truss 19.
  • the skate cart is drivable back and forth along the skate truss by a drive motor 71, preferably located under the cart rails near the rear end of racker 11 at a location which is under the cart when the cart is either at its forward limit of travel or at its rearward limit of travel.
  • the motor preferably is an electric motor which rotates a pinion which meshes with a rack carried by frame 70.
  • the skate cart drive preferably includes a brake which is operable to stop the cart and to hold it at any position with in its range of travel. Also, it is preferred that horizontally disposed shock absorbers are carried by fixed structures at the opposite limits of skate cart motion to cooperate with the skate cart as it moves back and forth during operation of system 10.
  • the forward limit of travel of the skate cart is shown in FIG. 1B.
  • the rearward limit of travel of the skate cart is within the perimeter of drilling rig floor 17 toward well centerline 23 from the forward edge of the rig floor and from a horizontal pipe stop 130 shown in FIG. 17.
  • the pipe stop is a horizontal bar which is located about 4 to 5 feet (1.2 to 1.5 m) or so above the rig floor adjacent the forward limit of travel of a horizontally reciprocable pipe handling head 72 of a pipe stabber 73; see FIGs. 1A and 2A.
  • the pipe stop limits the rearward motion of the pin end of a pipe stand 43 which has its box end engaged in a pipe elevator and raised in the rig derrick above the rig floor in the course of moving the pipe stand from racker 11 into connection with the upper end of a pipe string supported along the well centerline substantially at or above the rig floor.
  • the pipe stop comes into effect when the pin cart 49 on the skate cart also is at its rearward limit of movement along the skate cart.
  • the pipe stop holds the lower end of the essentially vertical pipe stand in a position for engagement of the stand, adjacent its lower end, by the gripper mechanism which is part of the pipe stabber head 72.
  • the stand When the stand has been engaged by the pipe stabber, the stand is raised so that the pin end clears the pipe stop.
  • the stabber then is operated to move the lower end of the pendulously supported pipe stand along a fixed path into alignment with the well centerline where it can be connected to the upper end of the pipe string.
  • Pin cart 49 is a small carriage which is captive to and moves in tracks atop and along the length of the skate cart.
  • the skate cart is shown in FIGs. 2B and 9 at its forward limit of travel along the skate cart; the skate cart also is at its forward limit of travel.
  • the pin cart is shown in FIG. 10 at its rearward limit of travel along the skate cart within the lengthwise extent of low lift mechanism 52.
  • the pin cart is driven along the skate cart by a drive motor 75 which preferably is located at the forward end of the skate cart and preferably is an electric motor. Motor 75 preferably is coupled to the pin cart by a cable loop which is arranged for powered movement of the pin cart in either direction along the skate cart.
  • the pin cart defines a rearwardly and upwardly open receptacle into which the pin end of pipe stand 43 can fit.
  • the pin cart is capable of accepting a substantial vertical load from a pipe stand as the stand moves from a horizontal position on the skate to a nearly vertical position in the derrick, or vice versa.
  • the pin cart drive preferably includes a brake and an overrunning clutch which permits the pin cart to be moved. by a pipe stand engaged with the cart, at a speed different from the cart speed corresponding to the operation of the pin cart drive motor.
  • the skate cart carries low lift mechanism 52.
  • the low lift mechanism is provided to raise the rear box end of a pipe stand from the skate cart, as the skate cart approaches the rig floor, an amount which is adequate to place the stand box end above the pipe stop adequately that the stand box end can be reached by elevators for lifting into the rig derrick.
  • the box end of the stand is then engaged by the pipe elevators which are supported by the rig's traveling block, e.g.
  • the traveling block and the elevators are used to raise the stand box end into the derrick as the stand's pin end is moved by the pin cart, or by the pipe stand itself, further toward the rig floor.
  • the low lift mechanism is retracted (lowered) when the box end of the stand has been lifted from it, so that the rear end of the low lift mechanism can pass beneath the pipe stop toward the center of the rig floor (see FIG. 1A).
  • the presently preferred low lift mechanism preferably is pneumatically powered and preferably includes a pair of pneumatic rams 76; see FIG. 10, e.g.
  • the rams 76 are mounted to the skate cart sides on opposite sides of the pin cart path of movement.
  • Each ram is connected to a crank arm 79 which is coupled to a corresponding one of two lift arms 77 so that extension and retraction of the rams causes the rearmost ends of the lift arms to raise and to lower.
  • the preferred coupling between crank arms 79 and lift arms 77 are meshed gear sectors carried by each of the arms concentric to the pivot axes of the arms.
  • the rear ends of the lift arms mount between them a pipe support roller 78, rotatable about a horizontal axis, which preferably has a linearly tapered hourglass configuration.
  • the lowered position of roller 78 is defined to support a pipe stand on the skate cart at a location on the stand adjacent the stand box end.
  • the low lift mechanism is operable in a reverse manner to lower to the skate cart the box end of a pipe stand being transferred from the derrick to the pipe racker for storage.
  • the structure of the low lift mechanism forward of roller 78, i.e., between the roller and rams 76, is arranged on the opposite sides of the skate cart clear of the pin cart's path of movement.
  • the pin cart 49 can move within the length of the low lift mechanism to the extreme rear end of the skate cart.
  • the pin cart can be positioned within the perimeter of the rig floor closely adjacent to pipe stop 130 when it and the skate cart are at their rearward limits of travel.
  • a high lift mechanism 80 also is present there, preferably attached to the pipe stabber. Also there, adjacent to the pipe stabber, and also on the opposite side of the path along which the pipe stand moves, is a pipe guard 132 to contain pipe in the pipe path. See FIGs. 15 and 16.
  • the high lift 80 can be used to advantage during drilling operations.
  • the drill pipe string can be held by a top drive unit which rotates the drill string and which holds the drill string at an essentially constant load at the drill bit by means of vertical motion compensation equipment known to the offshore drilling industry.
  • This constant bit load can be maintained even as the ship heaves up and down in the seas.
  • the drill pipe When it becomes necessary to add more pipe to the drill string, the drill pipe is seated into slips in a rotary table and disconnected from the top drive.
  • the top drive is raised to the top of the derrick with the next stand of pipe in its elevators.
  • the new stand of pipe When the new stand of pipe is vertical, it is lowered into the box end tool joint at the top of the drill string, whereupon drilling may continue.
  • the pipe string is raised about 15 feet (about 4.6m) above the drill floor before being set in slips.
  • the high lift can be used to elevate the drill pipe box end from the low lift level to a greater height where the top drive elevators can reach it.
  • the high lift has a carriage 135 which is raised and lowered preferably by a pneumatically driven chain.
  • FIG. 15 shows carriage 135 in upper and intermediate positions while FIG. 16 shows the carriage at upper, intermediate and lower positions.
  • the carriage can have an arm 82 which will articulate from a vertical, upright position down to a horizontal position, and a pneumatic ram 136 to rotate the arm from one position to the other.
  • the arm is connected in a manner that a pipe striking the arm from below will raise the arm. When a pipe is lowered onto the arm from above, the arm is stopped in the horizontal position and holds the pipe in the cradle on the arm.
  • the high lift is normally stowed in the upmost position with the arm rotated to the vertical position out of the way of pipe being tripped in or out of the well.
  • the high lift carriage is lowered to the lowest most position and the arm 82 is rotated to the horizontal position where it remains until the pipe skate cart is moved aft with the next stand of drill pipe.
  • FIGs. 1, 2, and 7 illustrate the provision of walkways 84 and ladders 85 on the racker to afford access of personnel to it.
  • FIGs. 17-20 A second form of the sleeper indexing arrangement, somewhat different from the arrangement described above with reference to FIGs. 11 and 11A, is illustrated in FIGs. 17-20 and is presently more preferred.
  • a vertical shaft 60 is associated with each group of sleepers 38 at each sleeper station of each pipe storage bay. Each shaft 60 is located adjacent the forward or aft outboard corner of a racker column 25, as appropriate. Each shaft 60 is supported for rotation and axial movement in a series of bearings 90 which are spaced along the shaft and are mounted in brackets 91 (see FIG. 20) affixed to the adjacent racker columns 25. Each bracket 91 and bearing 90 is located below the downward limit of travel of a respective sleeper base 54 and defines that limit.
  • the shaft is traversely notched at diametrically opposed locations to define a pair of horizontal keyway slots 63.
  • a fork 62 is mounted for slidable movement within the sleeper base.
  • the sleeper base has a terminal hub 57. which surrounds the shaft and mounts the base to the shaft for rotation about and axial movement along the shaft.
  • the fork is reciprocated in the sleeper base by a double-acting ram 61. The fork thus is moveable by the ram 61 into and out of engagement with the vertical shaft 60 at the keyway slots 63.
  • Engagement of a fork 62 in keyway slots 63 of a shaft 60 releasably connects the corresponding sleeper base and hub to the shaft so that the base and hub follow axial and angular motion of the shaft.
  • Each vertical sleeper indexing drive shaft 60 is rotatably supported vertically at its bottom end on a pedestal or platform 92 defined at the upper end of the piston 93 of a vertically disposed ram 94 located below the shaft; see FIG. 18. That ram is operated to raise and to lower the corresponding shaft. Also, there is a shaft angular drive assembly 95 coupled to each vertical shaft above the corresponding vertical drive ram. Each assembly 95 preferably includes a crank arm 96 affixed to the shaft and a double-acting horizontally disposed ram 97 pinned between the end of the crank arm and the racker base 24.
  • each horizontal ram 97 between its shaft crank arm and the racker base is arranged to enable the angular drive assembly to accommodate and to follow vertical motion of the shaft by an amount which is adequate to lift a stowed sleeper 38 out of engagement with a sleeper support 64 and adequate to lift a deployed sleeper out of engagement with a deployed sleeper below it.
  • FIG. 19 shows that the horizontal drive ram 97 for the aftmost shaft associated with a pipe storage bay preferably is located adjacent the rear end of the racker base.
  • the forwardmost horizontal drive ram associated with a pipe storage bay preferably is similarly located relative to the front end of the racker base. All other horizontal drive rams are located adjacent the sides of the racker base.
  • FIG. 17 shows a presently preferred arrangement for securing the lower end of a bridge crane lift column 45 from movement when the lift column is stowed when at its lowest position in the bridge crane.
  • a dummy section 98 of drill pipe is supported in a horizontal fore-and-aft position outboard of the adjacent vertical 94 and angular 95 drives for a sleeper indexing drive shaft 60.
  • the pipe dummy section is located vertically below the place occupied by a corresponding magnetic lifting head when a bridge crane is in its stowed position as described above.
  • the dummy pipe section is carried on a support bracket 99 mounted to the outer face of the racker base.
  • the magnetic lift head 47 carried by the lift column can make contact with the top of the dummy pipe section, and a mechanical safety latch 105 associated with the magnetic lift head can be engaged around and below the dummy pipe section. Such forms of contact with the dummy pipe section cooperate to lock the lower end of the lift column to the dummy pipe section.
  • a drill pipe dummy section preferably is provided for each lifting head in each bridge crane at spaced locations along the outboard sides of the racker base.
  • FIGs. 21-23 show details of a presently preferred magnetic lift unit or head 47. several of which are carried by each racker bridge crane spreader bar 46 at spaced locations along the bar.
  • the central part of each lift head is occupied by an elongate magnet assembly 101 (see FIGs. 21 and 23) which includes a pair of slab-like permanent magnets 102.
  • the magnets are in spaced parallel relation to each other and are in planes parallel to the length of the spreader bar.
  • a pipe contact element 103 made of a material which does not interfere with the magnetic field created by the magnets, is replaceably carried by the bottom face of each magnet, as shown in FIG. 23.
  • Each contact element has a sloping or accurately curved face which opens downwardly and also toward the adjacent element 103.
  • the material which defines the pipe contact elements is softer than the metal of the pipe stands 43 to prevent the pipe stands from being scratched by the contact elements.
  • all other components of the racker (and also of the skate and pin carts, the low and high lift mechanisms, and the pipe stabber, e.g.) which can or will contact a pipe stand either are made of materials which are softer than the pipe stands, or have their pipe stand contacting surfaces defined by relatively soft and replaceable wear pieces or inserts.
  • Each lift head 47 preferably also includes a pair of safety latch assemblies 105; see FIG. 22.
  • a latch assembly 105 can include a vertically slidable upper jaw member 106 carried by the adjacent end of the magnet assembly.
  • Each assembly 105 also can include a lower jaw member 107 which is pivotable about an axle 108 fixed to the magnet assembly and moved about that axle by operation of a double acting ram 109 pinned between a crank arm of a jaw member 107 and a plate 110 carried atop the magnet assembly.
  • the lower jaw member is moved to the side of the bottom recessed end of the upper jaw member when the lift head is being moved into or out of contact with a pipestand, but otherwise is in the position shown in FIG. 22 when the lift head has contact with a pipe stand.
  • Each lift head assembly 47 can be mounted to its bridge crane spreader bar 46 by a pair of plates 112 and 113.
  • Plate 112 is affixed to the upper central part of the head's magnet assembly 101 and preferably is in a plane parallel to the length of the magnet assembly.
  • Plate 112 can be pinned, as at 114, to a lower tongue of plate 113 which is carried by the spreader bar.
  • Plate 113 can be pinned, as at 115, to the spreader bar via a vertical slot 116 in that plate.
  • the lift head 47 can pivot about pin 114 and adjust itself to the attitude of a pipe stand being picked up either from a pipe storage bay or from the skate cart.
  • the slidable lost-motion connection of plate 113 to the spreader bar allows the connection of the lift head to the spreader bar to accommodate downward movement of the spreader bar after the lift head has made contact with a pipe stand.
  • a shock absorber 118 is provided at each end of a lift head 47 to cushion movement of the spreader bar toward the lift head.
  • the shock absorber can be a dashpot whose piston shaft is urged upwardly by a compression spring engaged between the upper end of the shaft and the dashpot body; see FIG. 21.
  • Each latch assembly 105 (see FIG. 22) is a backup mechanical holder and safety mechanism in the lift head; it is not relied upon, during normal operation of system 10, to support a pipe stand being transported by a racker bridge crane.
  • the several magnet assemblies carried by a bridge crane are intended to hold a pipe stand in the crane.
  • the magnetic forces which hold a pipe stand in a bridge crane preferably are generated by permanent magnets.
  • An electrically powered and selectively operable degausser 120 is included in each lift head. The degausser is operated to null the field created by the permanent magnets when a pipe stand is to be released from a bridge crane or is to be picked up by the crane.
  • Anelectrical power cable 122 is connected between a reel 123 on the crane body and the crane spreader bar 46, as shown in FIG. 17.
  • Compressed air supply 124 and return 125 lines are connected from reels 126 and 127 on the crane body to the spreader bar.
  • a pair of guide roller arrays 128 are carried in the top and bottom of the truss-like body of each bridge crane in cooperation with each crane lift column 45.
  • the lift columns preferably are square in cross-section.
  • the guide roller arrays cooperate with the lift columns to constrain and hold the columns stiff against pendulous motions relative to the crane body and to move essentially only normal to the bridge crane.
  • the structures and mechanisms of a presently preferred pipe storage and handling system are constructed for operation in the temperature range of 14°F to 100°F (-10°C to 38°C).
  • Those structures and mechanism reflect three different sets of environmental conditions, namely; operating conditions in which heave motions of +/- 3.7 meters at 8 second period, roll motions of+/- 4° at 12 seconds, and pitch motions of +/- 4°at 9 seconds, are tolerable; waiting on weather conditions (in which system components are stowed in their normal secure and stowed positions) of +/- 60 meters heave at 9 seconds, +/- 10° roll at 12 seconds, and +/- 6° pitch at 10 seconds; and survival conditions (sea fastenings in place or engaged) of +/- 8.3 meters heave at 10 seconds, +/- 35° roll at 15 seconds, and 10° pitch at 10 seconds.
  • the system components are sized to withstand loads associated with drillship motions during transit of 36 feet (11m) heave, 25
  • the design operating rate of the system is one 5000 pound (2273 Kg) triple pipe stand per minute, both for delivery of stands to the drill floor and removal of stands from the drill floor, using both bridge cranes in synchronism.
  • the bridge cranes have a nominal working speed of 60 to 75 feet (18.3 to 22.9 m) per minute when fully loaded, and also a low speed mode in the range of 2 to 4 feet (0.6 to 1.2 m) when subjected to side forces of 0.5g opposing crane motion. When subjected to opposing side loads in the range of 0.5 to 1.0g the crane drives may stall but they hold cranes in position.
  • the vertical drive mechanisms of the cranes have a nominal operating speed of 75 to 90 feet (22.9 to 27.4 m) per minute with a slow speed mode in the range of 3 to 5 fpm (0.9 to 1.5 mpm) useful when opposing dynamic loads of +/- 0.5g are present due to ship motion.
  • the crane vertical drives may stall but they hold the vertical position when subject to opposing dynamic forces from 0.5 to 1.0g.
  • Horizontal and vertical drive mechanisms in the cranes have brakes which lock the crane components in position when not being actively driven by an operator or by the control system ; the crane brakes are effective under both operating and waiting on weather conditions.
  • the bridge cranes can be operated from either one of two control stations.
  • a primary control station 138 is provided in the driller's house 139 at the drilling rig floor; see FIG. 2A. That station is called the pipe handling control console.
  • a secondary control station 140 called the pipe racker control console, is located on a platform 141 adjacent the forward end of the skate cart truss; see FIG. 2B.
  • the cranes are operated from the primary control station in the automatic mode.
  • the cranes are operable in either a manual mode or the automatic mode from the secondary control station. If a crane is not selected for operation, it is stowed in its parking position outboard of the pipe storage bays.
  • the crane controls include a zone control feature which prevents a crane from hitting structure in either operating mode.
  • Control interlocks prevent a crane from hitting the skate with a pipe when the skate is in motion.
  • the crane halts above the transfer position of the skate; a manual command is required to lower or retrieve pipe to or from the skate.
  • the crane's automatic cycle resumes to pick up or stow the next stand of pipe from or in the desired pipe storage bay.
  • a crane interlock which prevents the cranes from running into each other
  • a skate interlock which halts the crane above the skate track until a manual command is given to the crane
  • a sleeper interlock which prevents a crane from lowering its pipe lifting heads to pick up height over the sleepers until the proper sleepers are in the correct position for the operation
  • structural zone interlock described above.
  • Controls for the sleeper indexing mechanisms preferably are located at the forward secondary control console which is so positioned that the operator can see clearly into both pipe bays or can move easily to see into either of them.
  • the sleeper-related controls at that console preferably include controls for the following functions: select port or starboard bay, select drill pipe layer (1, 2, 3, ...), stowed or deployed position of the sleepers for each pipe layer, commanding stow or deploy sleeper motion, an alarm (sound and light) which indicates that one or more sleepers did notrespond to a positioning command, and a sleeper lock useful when personnel are present or racked pipe stands.
  • the sleeper stow and position commands signals preferably are also provided to the crane control programming pertinent to the sleeper control interlock.
  • the skate cart and pin cart drive rates are defined consistent with the one per minute pipe stand delivery/recovery rate.
  • the skate drive preferably is operable to produce skate speeds up to 450 feet (137 m) per minute and to accelerate from a dead stop to full speed in 4 seconds.
  • the pin cart drive preferably is operable to produce pin cart speeds upto 600 feet (183 m) per minute, and to accelerate the pin cart when unloaded from a dead stop to full speed in 2 seconds.
  • the pin cart drive forces the pin cart into contact with the pin end of a pipe stand while the stand is being raised by the derrick elevators without pushing the stand through the elevators.
  • an overrunning clutch in the pin cart drive enables the pin cart to overrun its drive in response to loads on the cart by a pipe stand being placed on the skate cart.
  • the skate cart and pin cart drives preferably are of the variable speed kind.
  • the skate cart can make a 112 foot (34m) round trip in one minute on a continuous basis.
  • the pin cart travel is about 80 feet (24.4 m) along the skate cart. Its drive can return the empty pin cart to its receiving position in 30 seconds.
  • a brake for the skate cart can stop the skate cart in two seconds once per minute when loaded and twice per minute when unloaded.
  • a pin cart brake can halt the pin cart from full speed in one second, and can effect two braking operations per minute on a continuous basis.
  • the skate and pin cart drives are controllable from primary control station 138.
  • Controls for operating pipe low lift mechanism 52, pipe stabber 73 and pipe high lift mechanism 80 are located at primary control-station 138.
  • the high lift mechanism can lift the box of a pipe stand to an elevation of 22 feet (6.7 m) above the rotary table located in the drilling floor at the drilling axis.
  • the low and high lift mechanism can lift 2500 pounds (1140 Kg).
  • the low lift operating rate is 4 feet (1.2 m) per second.
  • the high lift operating rate is 2 feet (0.6 m) per second.

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Claims (16)

  1. Appareil d'entreposage de tiges de forage (11) ayant
    des éléments de support de tiges horizontaux (38, 39) pouvant être disposés dans un compartiment d'entreposage de tiges (28, 29) à des postes multiples espacés le long de la longueur du compartiment pour supporter individuellement des longueurs horizontales multiples de tiges de forage (43) dans un groupement de couches multiples espacées verticalement et de longueurs multiples de tiges de forage dans chaque couche, et caractérisé en ce que
    des mécanismes d'entraînement pouvant être actionnés sélectivement (53-65 ; 60-65, 90-97) sont rattachés aux éléments de support des tiges (38) et peuvent être actionnés pour bouger ces éléments individuellement entre des positions déployées sensiblement fixes dans lesquelles les éléments de support (38, 39) sont dans le groupement et des positions rétractées horizontales dans lesquelles les éléments de support (38, 39) sont enlevés du groupement.
  2. Appareil tel que revendiqué dans la revendication 1, les éléments de support des tiges (38, 39) étant disposés de façon à supporter les longueurs des tiges (43) sans soumettre aucune longueur de tige aux charges dues aux tiges et aux éléments de support au-dessus d'elles dans le groupement.
  3. Appareil tel que revendiqué dans la revendication 1, l'élément de support le plus bas (39) à chaque poste étant fixé, et chaque autre élément de support (38) dans le poste quand il est disposé dans le groupement étant engagé avec l'élément de support en dessous de lui et étant supporté par celui-ci.
  4. Appareil tel que revendiqué dans la revendication 3, les éléments de support des tiges (38, 39), lorsqu'ils sont engagés l'un avec l'autre, étant clavetés contre tout mouvement relatif dans des directions le long des longueurs des tiges (43) supportées dans le compartiment.
  5. Appareil tel que revendiqué dans l'une quelconque des revendications précédentes, les mécanismes d'entraînement 53-60, 90-97 pouvant être actionnés pour soulever et abaisser les éléments de support des tiges (38).
  6. Appareil tel que revendiqué dans l'une quelconque des revendications précédentes, les mécanismes d'entrainement (53-60, 90-97) comprenant à chaque poste un arbre vertical rotatif (60) auquel est associé un groupe d'éléments de support de tiges (38), chaque élément de support dans le groupe ayant un cadre d'extrémité (54) à travers lequel l'arbre passe de manière à pouvoir tourner, un accouplement (62) pouvant être engagé sélectivement entre chaque élément de support des tiges (38) et l'arbre (60) afin d'empêcher l'arbre (60) de tourner par rapport à l'élément de support des tiges, et un mécanisme d'entrainement d'arbre (95) pouvant être actionné pour tourner l'arbre (60) d'une quantité sélectionnée dans l'un ou l'autre sens autour de son axe.
  7. Appareil tel que revendiqué dans la revendication 6, l'arbre (60) pouvant être bougé axialement à travers chaque élément de support des tiges (38), chaque accouplement (62) pouvant être actionné pour fixer l'élément de support des tiges associé afin d'isoler le mouvement axial de l'arbre par rapport à celui-ci, et le mécanisme d'entraînement de l'arbre (94) pouvant être actionné pour élever et abaisser l'arbre (60) d'une quantité sélectionnée.
  8. Appareil tel que revendiqué dans la revendication 6 ou 7, les éléments de support des tiges (38) à chaque poste comprenant deux groupes d'éléments de support mobiles, les éléments de support alternés étant des éléments d'un groupe respectif auquel un arbre respectif d'une paire d'arbres verticaux (60) est associé.
  9. Appareil tel que revendiqué dans l'une quelconque des revendications 1 à 8, comprenant un appareil de levage des tiges (32, 33) qui peut être disposé au-dessus du groupement et qui peut être actionné pour bouger les longueurs de tiges individuelles dans une attitude horizontale entre le groupement et une position de transfert latéralement par rapport au groupement.
  10. Appareil tel que revendiqué dans la revendication 9, l'appareil de levage des tiges (32, 33) comprenant une pluralité d'unités de levage de tiges magnétiques pouvant être commandées (47) qui peuvent être engagées avec une longueur de tige (43) dans des emplacements espacés le long de la longueur.
  11. Appareil tel que revendiqué dans la revendication 9 ou 10, le compartiment (28, 29) étant espacé dans une direction sensiblement parallèle à la longueur du compartiment depuis un endroit d'utilisation (15) des longueurs de tiges (43), et comprenant un mécanisme de distribution de tige (18) pour bouger la tige dans une attitude horizontale entre une position de transfert adjacente au compartiment (28, 29) et l'endroit d'utilisation de la tige, ce mécanisme de distribution de tige (18) comprenant une voie (19) s'étendant depuis la position de transfert vers l'endroit d'utilisation de la tige (15), un chariot allongé (70) qui peut être entraîné dans chacune de deux directions opposées le long de la voie vers et depuis la position de transfert, ce chariot (70) ayant une longueur adéquate pour supporter une longueur de tige en alignement avec lui à une extrémité de la longueur de tige et à un emplacement le long de la longueur de tige près de son autre extrémité, et qui comprend un petit chariot (49) qui peut être entraîné dans chacune de deux directions opposées le long du chariot (70) et définissant un réceptacle ouvert vers le haut pour recevoir et soutenir la une extrémité d'une longueur de tige supportée sur le chariot.
  12. Appareil tel que revendiqué dans la revendication 11, le chariot (70) comprenant un appareil de levage de tige (52) qui peut être actionné pour soulever l'autre extrémité d'une longueur de tige reçue d'une distance sélectionnée au-dessus du chariot.
  13. Méthode d'entreposer des tiges de forage pour puits de pétrole et de gaz (43) dans laquelle un nombre sélectionné de longueurs de tiges sont disposées, comme une première couche inférieure, individuellement dans des encoches ouvertes vers le haut (41) d'un ensemble de supports de tiges immobiles (39) disposés transversalement aux longueurs de tiges à des postes espacés le long des longueurs, et d'autres nombres de longueurs de tiges (43) sont disposées dans d'autres ensembles de supports de tiges pourvus d'encoches similaires (38) placés à chaque poste au dessus des supports en dessous dans un groupement immobile de couches multiples de longueurs de tiges multiples, et caractérisé par le mouvement sélectif des supports de tiges entre des positions déployées dans le groupement et des positions rétractées horizontales dans lesquelles les supports de tiges sont enlevés du groupement.
  14. Méthode telle que revendiquée dans la revendication 13, comprenant l'opération supplémentaire consistant à bouger chaque ensemble de supports de tiges (38) dans des positions rétractées hors du groupement lors de l'enlèvement de toutes les longueurs de tiges de la couche supportée par cet ensemble afin d'exposer la couche inférieure suivante dans le groupement, et à bouger l'ensemble supérieur suivant de supports dans des positions déployées dans le groupement lors du remplissage d'une couche de longueurs de tiges dans le groupement.
  15. Méthode telle que revendiquée dans la revendication 14, dans laquelle le mouvement des supports de tiges (38) des positions déployées dans les positions rétractées comprend le soulèvement des supports déployés hors de contact avec les supports en dessous dans le groupement, et le pivotement de chaque support soulevé autour d'un axe (60) à une extrémité du support.
  16. Méthode telle que revendiquée dans la revendication 15, dans laquelle le mouvement des longueurs de tiges individuelles vers les supports de tiges et depuis ceux-ci comprend l'engagement d'une longueur de tige par le haut à des emplacements espacés le long de la longueur par une pluralité de têtes de levage magnétiques (47).
EP00970530A 1999-09-29 2000-09-29 Rangement horizontal de tiges de forage et systeme de distribution Expired - Lifetime EP1226330B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US15666299P 1999-09-29 1999-09-29
US156662P 1999-09-29
PCT/US2000/027043 WO2001023701A1 (fr) 1999-09-29 2000-09-29 Rangement horizontal de tiges de forage et systeme de distribution

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EP1226330A1 EP1226330A1 (fr) 2002-07-31
EP1226330A4 EP1226330A4 (fr) 2005-03-23
EP1226330B1 true EP1226330B1 (fr) 2006-07-19

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EP (1) EP1226330B1 (fr)
KR (1) KR100478817B1 (fr)
AT (1) ATE333565T1 (fr)
AU (1) AU7989700A (fr)
DE (1) DE60029466D1 (fr)
WO (1) WO2001023701A1 (fr)

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Also Published As

Publication number Publication date
EP1226330A1 (fr) 2002-07-31
KR100478817B1 (ko) 2005-03-28
WO2001023701A1 (fr) 2001-04-05
AU7989700A (en) 2001-04-30
KR20020043599A (ko) 2002-06-10
ATE333565T1 (de) 2006-08-15
DE60029466D1 (de) 2006-08-31
EP1226330A4 (fr) 2005-03-23

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