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
  • E21B19/002—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
  • E21B19/004—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 supporting a riser from a drilling or production platform
  • E21B19/006—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 supporting a riser from a drilling or production platform including heave compensators
• • 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

Definitions

• Floating drilling platforms are sometimes used for offshore drilling operations and include a hoisting system for raising and lowering equipment, such as a drill string, to a subsea wellsite. Because these platforms float at the surface of the water and are not anchored to the seabed with legs, the platforms can vertically rise and fall (i.e., heave) with waves in the water. Heave compensation can be used to counteract the vertical heaving motion and reduce movement of the drill string or other hoisted load with respect to the seabed.
• heave compensators have been used in an effort to maintain a constant weight on bit for a hoisted drill string and reduce deviation of the drill string with respect to the seabed as the drilling platform rises and falls with the waves.
• Simple heave compensators acting as shock absorbers have been provided between traveling blocks and drill strings hoisted with a drawworks system.
• Active heave compensation has also been used, in which heaving motion of the drilling platform is measured and used to actively control the position of the drill string.
• the weight of the equipment to be hoisted by offshore rigs e.g., drill strings, casing strings, and wellhead equipment
• Multi-part block-and-tackle arrangements have been used with drawworks for hoisting on drilling rigs, in which hoisting lines are reeved through sheaves of crown and traveling blocks to provide a mechanical advantage.
• One approach to increasing the hoisting capabilities of such arrangements is to add more lines and sheaves and increase the size of the hoisting lines.
• Drilling platforms have also been provided as hydraulically driven "cylinder rigs," which use large hydraulic cylinders instead of drawworks. The hydraulic cylinders in such rigs can provide both the main hoisting function and a heave compensating function.
• Embodiments of the present disclosure generally relate to hoisting systems having heave compensation functions.
• hoisting systems include both active heave compensation at drawworks (or winches) of the systems and passive heave compensation.
• some of the hoisting systems described below have single -part lines reeved over a crown block without any mechanical advantage from a multi-part block-and-tackle reeving.
• active heave compensation and passive heave compensation are provided at a winch that includes a planetary gear system, which allows both active and passive heave compensation to be applied to a rotating drum of the winch.
• FIG. 1 generally depicts a floating drilling rig with a hoisting system in accordance with one embodiment of the present disclosure
• FIG. 2 is a block diagram representing a hoisting system having both active and passive heave compensation functions in accordance with one embodiment
• FIGS. 3-7 show examples of hoisting systems having active and passive heave compensation in accordance with various embodiments
• FIG. 8 is a front perspective view of a winch having both active and passive heave compensation in accordance with one embodiment
• FIG. 9 is a sectioned view of the winch of FIG. 8;
• FIG. 10 is a detail view of the sectioned winch of FIG. 9 and shows a planetary gear system for driving rotation of a drum of the winch in accordance with one embodiment
• FIG. 11 is a cross-section of the winch of FIG. 9 showing planetary gears disposed between a sun gear and a ring gear in accordance with one embodiment;
• FIG. 12 is a block diagram of various active drive inputs and passive heave compensation systems that can be connected to a gear system to drive rotation of a drum of a winch in accordance with various embodiments;
• FIG. 13 is a schematic of a winch system with active heave compensation provided by electric motors and passive heave compensation provided by hydraulic motors in accordance with one embodiment
• FIG. 14 is a block diagram of a sun gear that can be operated by hydraulic cylinders via a crankshaft to drive rotation of a drum of a winch in accordance with one embodiment.
• FIG. 1 a system 10 is illustrated in FIG. 1 in accordance with one embodiment.
• the system 10 is an offshore drilling rig in the form of a floating vessel 12. More specifically, the floating vessel 12 is generally depicted as a drillship in FIG. 1, but the floating vessel could be provided in another form, such as a semi-submersible drilling rig, in other embodiments.
• the vessel 12 includes a hoisting system for raising and lowering equipment with respect to a drill floor of the vessel, which facilitates well drilling and completion operations.
• the depicted hoisting system includes a derrick 14 constructed on the drill floor of the vessel 12.
• Various equipment and other loads can be supported by one or more hoisting lines 20 of the hoisting system.
• the supported load includes a top drive 16 and a drill string 18 suspended from the top drive 16.
• the drill string 18 extends through a hole in the drill floor of the vessel 12 and can be rotated by the top drive 16 to facilitate drilling of a subsea well.
• the hoisting system could be used for hoisting other loads, such as casing strings, wellhead equipment, and other subsea well components.
• the hoisting system includes a drawworks 22, which can be provided on the drill floor with the derrick 14, as shown in FIG. 1, or at another location.
• the drawworks 22 includes a rotatable drum 26 (FIG. 2) that can reel in and reel out the hoisting line (or lines) 20 wound on the rotatable drum.
• Each hoisting line 20 can be reeved over a sheave in a crown block 24 coupled to the derrick 14 and connected to the supported load so that the reeling in and reeling out of the hoisting line 20 via the drum 26 raises and lowers the supported load.
• the hoisting system includes both active heave compensation and passive heave compensation to compensate for heaving motion of the floating vessel 12 from wave action at the surface of the water.
• FIG. 2 One such embodiment is generally depicted in FIG. 2 by way of example.
• a load 30 is supported by a hoisting system including the crown block 24 and the drawworks 22 with the rotatable drum 26.
• one or more hoisting lines 20 can be wound from the drum 26 and reeved over the crown block 24 to support a given load 30.
• the hoisting lines 20 can be coupled to the load 30 by a traveling block suspended from the crown block 24 with the hoisting lines 20. But the traveling block is omitted in some embodiments.
• heave of the vessel 12 causes the load 30 to move up and down with respect to the underlying seabed.
• such movement can cause a drill bit at the end of the drill string 18 to be pulled off the bottom of the well (with upward heave) or to be pushed with greater force against the bottom if the well (with downward heave).
• the hoisting system in FIG. 2 includes an active heave compensation system 34 and a passive heave compensation system 36.
• a motion reference unit 32 can be used to detect the heave of the vessel 12.
• the active heave compensation system 34 uses the measured heave to actively compensate for heaving motion through control of the drawworks 22.
• the active heave compensation system 34 can include a controller (e.g., a programmable logic controller or a programmed general-purpose computer) that receives the measured heave as an input and controls operation of the drawworks 22 to raise and lower the load 30 (with respect to the drill floor) to compensate for the heaving motion.
• the controller can control operation in any suitable manner, such as by sending command signals to motors of the drawworks 22 that control rotation of the drum 26. These motors can be considered part of the active heave compensation system 34 as well.
• the passive heave compensation system 36 can also be used to counter heaving motion of the vessel 12.
• the passive heave compensation system 36 can counter heave without requiring external power.
• the passive heave compensation system 36 can include one or more hydraulic devices (e.g., hydraulic cylinders or hydraulic motors) that passively store and release energy from the heaving motion of the vessel 12 to move the load 30 with respect to the drill floor to reduce the deviation of the load 30 from its position with respect to the seabed.
• the passive heave compensation system 36 could also include an active component (e.g., a hydraulic cylinder that passively compensates for heave and that can also be actively driven for further heave compensation).
• FIGS. 3-7 Various examples of hoisting systems having both active and passive heave compensation are generally depicted in FIGS. 3-7 in accordance with certain embodiments.
• the hoisting system includes a drawworks 22 with active heave compensation applied by rotating the drawworks drum, such as described above.
• the drum 26 of the drawworks 22 can be driven in any suitable manner, such as by electric or hydraulic motors.
• passive heave compensation is provided by hydraulic cylinders that are used to move sheaves in the hoisting system to counter heaving motion of the floating vessel 12. But hydraulic motors or other devices could also or instead be used for passive heave compensation.
• the passive heave compensation devices in some instances include an active component as well, such as a hydraulic cylinder that passively compensates for heave but can also be selectively driven by equipment on the vessel 12 to actively compensate for heave.
• an active component such as a hydraulic cylinder that passively compensates for heave but can also be selectively driven by equipment on the vessel 12 to actively compensate for heave.
• a hoisting system is shown as having passive heave compensation that rotates the drawworks drum 26 along with the active heave compensation. While a single hoisting line 20 is depicted in each of FIGS. 3-7, it is noted that the hoisting systems represented in these figures could use multiple hoisting lines 20, and that additional elements (e.g., hydraulic cylinders for passive heave compensation) can be added for use with the additional hoisting lines 20.
• one approach to increasing hoisting capacity of a hoisting system is to increase the number and size of the hoisting lines.
• the hoisting lines can also be reeved between additional sheaves in the crown block and the traveling block to increase the number of parts in the lines that run between the crown block and the traveling block to increase the mechanical advantage.
• a drawback to this approach is that it adds friction to the system and reduces the traveling speed of the hoisted load relative to the rotational speed of a drawworks drum. The added friction is amplified in an active heave compensating drawworks, negatively affecting the goal of achieving a constant weight-on-bit during heaving motion of a drilling vessel.
• typical 1000-ton or 1250-ton hoisting systems can have multi-part hoisting lines with sixteen parts in a block- and-tackle reeving and sixteen or seventeen sheaves, and use a two-inch diameter wire rope.
• Such systems can have losses of approximately 15 % or 20 % due to the reeving efficiencies alone. Further accounting for the inertia effects of the rotating systems and the high speed of the hoisting lines, the overall efficiency of such approaches can be around 55 %.
• Certain embodiments of the present technique include a hoisting system using one or more single-part hoisting lines to reduce the friction and inertia effects associated with the conventional approach of adding sheaves and increasing the number of parts of the line in the reeving to increase the mechanical advantage. It is noted that FIGS. 3-5 and 7 depict such single-part hoisting line arrangements, while FIG. 6 depicts a multi-part hoisting line arrangement.
• a 1500-ton hoisting system using a drawworks with a single-part hoisting line, with no mechanical advantage from multi-part block-and-tackle reeving is estimated to have lower friction losses (e.g., approximately 30 % lower) compared to a conventional drawworks of the same capacity. This reduction may be of particular use in an active heave compensating system where high line speed and accelerations may often occur to compensate for heaving motion of the floating vessel 12.
• the single-part hoisting system can eliminate the cut-and-slip procedures periodically required for conventional multi-part block- and-tackle reeving systems.
• multiple single -part lines 20 can be wound from the drawworks 22 and used to suspend the load 30 so that there is no single point of failure that would allow the load 30 to drop from a broken line 20.
• the single- part reeving can include one or more wire ropes connected directly to a live top drive load 30 and anchored to the rotating drawworks drum 26.
• each of the depicted hoisting systems include active heave control on a drawworks 22 (e.g., electric motors coupled to the rotating drum 26 of the drawworks 22) and a single -part line 20 reeved over the crown block 24 from the drawworks 22.
• a drawworks 22 e.g., electric motors coupled to the rotating drum 26 of the drawworks 22
• a single -part line 20 reeved over the crown block 24 from the drawworks 22.
• the single-part line 20 can be coupled to the load 30 (e.g., top drive 16 and attached drill string 18 or casing string).
• the passive heave compensation system includes a hydraulic cylinder 40 connected to the crown block 24 with a tension line 42 passed over a stationary turning sheave 44 suspended above the crown block 24.
• the crown block 24 is allowed to travel vertically with respect to the turning sheave 44 in response to operation of the hydraulic cylinder 40.
• multiple hydraulic cylinders 40, tension lines 42, and turning sheaves 44 can also be used.
• the hydraulic cylinders 40 can be located at the drill floor level with the drawworks 22, rather than positioned high in the derrick 14 (e.g., near the crown block 20).
• the hoisting system includes a hydraulic cylinder 48 mounted high in the derrick 14 with the crown block 24.
• the crown block 24 in this embodiment is directly connected (without a tension line 42) to the hydraulic cylinder 48 and allowed to move vertically in response to heave.
• the hoisting system includes the hoisting line 20, the
• drawworks 22 with active heave compensation a fixed crown block 24, and a passive heave compensation system including a sheave 52 and a hydraulic cylinder 54.
• the hoisting line 20 extends from the drawworks 22 and is reeved about the sheave 52 and over the crown block 24.
• the hydraulic cylinder 54 is mounted below the drawworks 22 and coupled to the sheave 52, allowing the sheave 52 to move with respect to the drawworks 22 to compensate for heaving motion of the floating vessel 12.
• the hoisting system of FIG. 6 includes the drawworks 22 with active heave compensation and a hoisting line 20 reeved between the crown block 24 and a traveling block 56 for supporting the load 30.
• the hoisting line 20 can be reeved as a two-part line, as presently shown (with parts 58 running between the crown block 24 and the traveling block 56). In other embodiments, the line 20 can be reeved with more than two parts, such as in a four-part line arrangement.
• Passive heave compensation is provided by a hydraulic cylinder 60 coupled to act on the crown block 24.
• active and passive heave compensation are both applied via the drawworks 22.
• the active heave compensation can be provided via electric motors driving rotation of the drum 26 of the drawworks 22 and the passive heave compensation can be provided by a hydraulic component, such as a hydraulic cylinder or motor.
• a hydraulic component such as a hydraulic cylinder or motor.
• Additional examples of hoisting systems having drawworks or winches with both active and passive heave control are provided in FIGS. 8-14 and described below. While the winches described below could be used as a drawworks on a drilling rig, it is noted that the winches could also or instead be used in other applications (e.g., in hoisting systems on other vessels not used for drilling, or on floating docks).
• a depicted heave-compensated system 70 includes a drawworks or winch 72 having a rotatable drum 74 mounted on a frame. Hoisting lines 20 are wound on the drum 74. Although omitted here for the sake of clarity, it will be appreciated that portions of the hoisting lines 20 extend from the drum 74 and can be used to support a hoisted load. In some instances the winch 72 could be used with a crown block and a derrick, but in other embodiments the winch 72 could be used without one or both of those additional components. Further, the hoisting lines 20 can be provided as single-part lines (rather than multi-part lines) for supporting the hoisted load.
• Motors 78 can be operated to drive rotation of the drum 74 to reel in or reel out the hoisting lines 20 to raise and lower an attached load 30. Any suitable motors 78 could be used.
• the motors 78 can include electric motors, for example.
• the motors 78 can also provide active heave control via the drum 74, in which case the motors are actively controlled to compensate for heave as generally described above.
• Passive heave compensation can be applied to the winch 72 by hydraulic cylinders 82.
• These cylinders 82 are depicted with cylinder housings 84 with extendable rods 86 connected to sheaves 92. In at least some instances, other sheaves are coupled below the cylinders 82.
• the hydraulic cylinders 82 are provided in a jigger winch assembly with tension lines 96 to rotate a ring gear 98 of a planetary gear system of the winch 72, although other arrangements could instead be used.
• the planetary gear system includes the ring gear 98, planetary gears 102, and a sun gear 104.
• a carrier 106 is coupled to rotate with the planetary gears 102 as they orbit the sun gear 104 in operation.
• the active drive system here the motors 78, which provide both a primary hoisting function and active heave compensation
• the motors 78 are connected to drive rotation of a gear 110 of a slew bearing 112.
• the gear 110 is coupled to a sun wheel 114 having the sun gear 104 such that the motors 78 rotate the sun gear 104 via the wheel 114 and the gear 110.
• the planetary gears 102 are mounted on axles 118 coupled to the carrier 106, which is coupled to drive the drum 74. This allows the orbit of the planetary gears 102 to drive rotation of both the carrier 106 and the drum 74.
• the passive heave compensation system (here including the cylinders 82) is connected to the ring gear 98. This allows a combination of active and passive adjustment of the rotational position of the drum 74 through a differential regulation principle.
• active heave In the embodiment depicted in FIG. 10, active heave
• differential heave compensation systems 120 include active drive input devices 122 (which can have active heave compensation) and passive heave compensation devices 124 (which can also be considered passive drive input devices) coupled to elements of planetary gear systems 126 to drive rotation of a drum 128.
• active drive input devices 122 which can have active heave compensation
• passive heave compensation devices 124 which can also be considered passive drive input devices
• a differential heave compensation system 120 with motors 78 coupled to the sun gear 104 as the active drive input devices 122, hydraulic cylinders 82 coupled to the ring gear 98 as the passive heave compensation devices 124, and a drum 74 coupled to the planetary gears 102 and carrier 106.
• the active drive input devices 122 can include actively driven hydraulic motors or hydraulic cylinders
• the passive heave compensation devices 124 can include a passively operating hydraulic motor.
• the differential heave compensation systems 120 can be used in embodiments using single-part lines or other embodiments having multi-part lines.
• the active devices 122, the passive devices 124, and the drum 128 could be connected to the ring gear, sun gear, and the set of planetary gears in any combination. It is noted that there are six permutations of coupling each of the active devices 122, the passive devices 124, and the drum 128 with one of the ring gear, the sun gear, and the planetary gears of the gear set 126. For instance, the connections of the active drive devices 122 and the passive heave compensation devices 124 could be switched from the arrangement of system 70, with the active devices 122 coupled to the ring gear and the passive devices 124 coupled to the sun gear. In other
• the drum 128 could be connected to the sun gear or the ring gear instead of the planetary gears, which could be driven by the active devices 122 or the passive devices 124.
• these embodiments use a differential system on a planetary gear arrangement principle, a regular differential may also be used (e.g., in the case of passive and active drive inputs each being provided by motors).
• the differential system with a planetary gear arrangement can be used to hoist a load by rotating the drum 128.
• the system can be considered to have two types of mechanical input (active drive and passive drive) and one mechanical output (to rotate the drum).
• the differential can be controlled in such way that drum motion is from active input alone, from passive input alone, or from the simultaneous combination of both inputs.
• Drum movement is then controlled by the sum of any moving inputs.
• the drum can have either one or more wire ropes or chains, and might have one or more layers.
• Drum output speed varies dependent on direct acting hoisting or via block-and-tackle systems.
• a passive drive input can be characterized as one that does not require an external power source to be able to perform the desired motion compensation. If the compensation is taken care of by the passive side, rig power consumption is at a minimum.
• a semi- active system is typically used when passive compensation is performed by hydraulic motors; in such cases power consumption can be used just to control displacement of motors.
• the passive side can also be used as a regenerative device for hoisting, in which motors are used for braking when lowering and charging accumulators and the stored energy is then used for hoisting the traveling load.
• the passive system can also have a parallel active system attached. This system can be used either as a performance booster while in a constant tension mode (maintaining a tension level on the hoisting line) or as an energy saver when in active heave compensation mode.
• the passive drive inputs can include any suitable devices and arrangements.
• the passive drive inputs are provided as hydraulic cylinders with wire or chain connections. In at least some instances, these wire or chain connections are passed over eccentric sheaves before entering the system to
• the passive drive inputs can instead include hydraulic motors with or without a semi-active part.
• the passive drive inputs could also be provided by hydraulic cylinders connected to the planetary gear system with a crankshaft (as depicted in FIG. 14 and discussed below), hydraulic cylinders with an active part, or hydraulic cylinders with rack-and-pinion connections for rotation.
• the active side (i.e., the active drive inputs) can be characterized as the part of the system used for hoisting, and also for active heave compensation.
• the active part is dependent on an external power source to drive rotation of the drum.
• the active drive inputs can be provided in any suitable form, such as an electric motor, a hydraulic motor, or a hydraulic cylinder.
• the electric and hydraulic motors provided as active drive inputs could be used with or without gearboxes and with or without brakes in various embodiments.
• multiple input drive devices may be used, which can provide redundancy and increased performance.
• multiple input drive devices whether active or passive
• only two can be used if compensating lower loads to increase performance (from an accumulator bank for the four cylinders being made available to only half of the cylinders).
• a further example of a differential heave compensation system 120 is depicted in FIG. 13.
• the system 120 includes active drive input devices 122 in the form of electric motors 132 coupled to planetary gear systems 126 via gearboxes 134.
• the system 120 depicted here also includes passive heave compensation devices 124 in the form of variable displacement hydraulic motors 138 coupled to the planetary gear systems 126 via gearboxes 140.
• the gearboxes 134 and 140 could be omitted.
• the ring gear of the gear system 126 can be provided with external teeth, and the hydraulic motors 138 can act on the ring gear via the external teeth to provide passive heave compensation.
• the hydraulic motors 138 act as hydraulic pumps to absorb the energy from the hoist when the vessel heaves upward and act as motors (turning the opposite direction) when the vessel heaves downward.
• a hydraulic accumulator 144 is connected to the hydraulic motors 138 and to gas storage bottles 146.
• similar gas storage bottles attached to the hydraulic cylinders 82 provide the volume allowing the extension and retraction of the cylinder rods 86 for passive heave compensation.
• the compensating load value is regulated by increasing or decreasing the charge pressure (e.g., of nitrogen) in these storage volumes. In the embodiment shown here in FIG. 13, however, the compensating load value is regulated by changing the displacement of the hydraulic motors 138 while maintaining a constant charge pressure in the gas storage bottles 146.
• the compensation system 120 in FIG. 13 includes a hydraulic power system 150 for actively controlling displacement of the hydraulic motors 138.
• the hydraulic power system 150 can include one or more main power units 152 that draw hydraulic fluid from a reservoir 156 and route the hydraulic fluid through a valve block 154 to the hydraulic motors 138.
• the compensating load value changes due to the compression and decompression of the gas in the storage bottles as the cylinders extend and retract. This load variation can be negated through the use of an active set of cylinders acting on the passive cylinders. But the active cylinders could be quite large, requiring a hydraulic power unit of substantial size.
• the displacement of the hydraulic motors can be actively increased and decreased on the fly to maintain a more constant compensating load value to negate the change in pressure in gas storage bottles 146 as the vessel heaves up and down.
• the main power unit 152 can be used to compensate for leakage of the hydraulic motors 138, but there would be no additional power unit demand to provide the active override to obtain a more constant compensating load value. Consequently, a smaller main power unit 152 can be used in the system of FIG. 13 compared to that of passive cylinder embodiments.
• passive heave compensation can be provided by one or more hydraulic cylinders via a crankshaft coupled to the planetary gear system.
• a passive heave compensation system 160 includes hydraulic cylinders 162 connected to drive a crankshaft 164 that is coupled to a sun gear 166 (e.g., of the planetary gear system 126).
• the active drive input can be connected to the ring gear and the drum 128 can be connected to the set of planetary gears such that the drum 128 can be rotated by the active drive input and the passive drive input (e.g., the cylinders 162).
• embodiments disclosed herein include an electrically driven winch or drawworks for normal hoisting functions and active heave compensation combined with a hydraulic passive heave compensating system with much less complexity than the all-hydraulic designs. This reduction in complexity enables lighter hoisting systems to be used and facilitates installation and servicing. The present systems may also have reduced power consumption compared to certain previous designs. Further, moving the passive heave compensation system to the drill floor from high in the derrick provides a lower center of gravity. And in the use of single -part lines in some embodiments enables a faster hoisting speed while maintaining a reasonable rotation speed of the drum of the winch.

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• 2015
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