MXPA06003944A - Inline compensator for a floating drilling rig - Google Patents

Abstract

An apparatus and method for protecting against the problems associated with heave of a floating drilling rig are disclosed. The disclosed invention is a unique inline compensator in which a plurality of cylinders housed within a tubular housing and a plurality of low pressure and high pressure accumulators function together to provide a system for compensating for heave in the event a primary heave compensation system fails or becomes inoperative. The typical inline compensator of the present invention utilizes a plurality of hydraulic cylinders that act in opposite directions and that have different piston areas such that the piston rods of the cylinders are extended or retracted at different pressure levels to account for heave. The typical inline compensator of the present invention is self-contained and compact enough to fit in the limited space available on a floating drilling structure. Further, a pair of inline compensators of the present invention can be utilized with coiled tubing operations. In such a case, the inline compensators will not interfere with the tooling necessary to conduct the coiled tubing operations.

Description

IN-LINE COMPENSATOR FOR A FLOATING DRILL PLATFORM This application claims the benefit of the provisional application of E.U.A. number 60 / 509,623 filed on October 8, 2003.

FIELD OF THE INVENTION The present invention relates to an in-line compensating apparatus and to a method for use on floating drilling platforms and reconditioning or extraction vessels. In particular, the invention relates to an in-line compensator apparatus that functions as a reserve system for the primary or main elevation compensation system of a floating drilling platform or a vessel in the event that the primary compensation system of the movement of rising and falling waves is disabled or inoperative.

BACKGROUND OF THE INVENTION Offshore drilling for oil and gas extraction is completed from one of two types of drilling platform: platforms that are supported by the seabed (such as fixed drilling platforms or self-elevating drilling platforms) or platforms that they float on the surface of the water (such as ocean bottom drilling vessels or semi-submersible drilling platforms). Although the drilling operations carried out from these two types of drilling rigs are similar, there is at least one main difference: ocean bottom drilling vessels or semi-submersible drilling rigs move with sea waves, while Fixed drilling platforms or self-elevating platform remain fixed to the seabed. The movement of ocean bottom drilling vessels or semi-submersible drilling platforms with sea waves presents a unique problem in drilling with this type of platform. First of all, in any drilling operation performed from floating platforms, compensation must be taken into account for the tendency of the platform to oscillate - that is, to move up and down with the waves. In particular, as the floating platform moves up and down, the drilling column and the drill that extend below the platform also move up and down. For a drill bit to work as efficiently as possible, the desired or optimum bit weight - that is, the downward force applied to the bit - must be kept as constant as possible. However, the up and down movement of the waves extracts the weight of the bit as the boat or platform ascends to the crest of a wave and places a weight back on the bit as the boat or platform descends to a valley between the waves . This fluctuation in the force applied to the bit severely limits the operator's ability to drill the well. See Ron Baker, A Primer of Offshore Operations, pages 55-63 (Univ. Of Texas Petroleum Extension Servs, second edition 1985). Perhaps more importantly, the up and down movement of the waves generates the potential for bursting due to a fracture or potential rupture of the extraction pipe during testing, reconditioning or completion operations. Specifically, once the well has been drilled, the oil and gas reserves ascend to the floating platform through the extraction pipe that runs from the platform to the well extraction zones - typically thousands of feet below the seabed. . The column of the extraction pipe consists of dozens, if not hundreds of pipe joints - typically with a length of approximately 9.1 m (30 ft) in length - connected together. The extraction pipe is supported and held in tension by the drilling hook and the drill wheel on the drilling platform to avoid lateral bending of the column. The extraction piping is typically held in place in the well by one or more production shutters. Because the extraction pipe is held in place in the well, any rise of the floating drilling platform due to the movement of rising and falling waves will increase the tension in the chain of extraction pipe and may cause the chain to fracture or break. A fracture or rupture of the extraction pipe chain can allow oil or gas inside the pipeline to leak which generates the potential of a blowout. To correct the problems related to the movement of rising and falling waves, the floating drilling platforms are equipped with a compensation system for that movement. The wave rise and fall motion compensation system typically is in the form of an active borehole system for moving up and down waves to a system that is an integral part of the derrick or that is Mounts directly on an extension of the mobile pulley. When functioning properly, these primary systems of compensating the movement of rising and falling waves are able to protect against the effects of such movement. However, the floating drilling platforms of the prior art are generally not equipped with a compensation system for the rise and fall of the reserve waves, or secondary waves, which functions in the event that the primary motion compensation system of the rise and fall of the waves does not work properly or becomes inoperative. In such a situation, the floating drilling rig will have no way to compensate for this movement. A possible reason why the systems for compensating for the rise and fall of reserve waves have not previously been used in ocean bottom drilling vessels or on semi-submersible drilling platforms is the limited space available on the tower of said platforms. floating. In addition, the possible locations on the drilling rig or the drilling floor where a system of compensating for the movement up and down of the reserve waves can be placed is limited by the need to allow access to the production tree on the platform. of drilling. Such access is necessary to carry out numerous drilling operations that include the potential to conduct pipe-biting operations. These space and placement limitations are probably a significant part of the reasons why prior art floating drilling platforms have not yet been equipped with a motion compensation system for raising and lowering reserve waves. Consequently, what is needed is a compensation system for the movement of rising and falling waves that acts as a reserve system for the primary system of compensation of movement of rising and falling waves and that is sufficiently compact to place it in the limited space available on the floating drilling platform. Therefore, an object of the present invention is to provide an apparatus for compensating the wave rise and fall movement which is normally static when the primary system of compensating for the wave rise and fall movement is operating, but which is becomes operational if the primary compensation system of the wave rise and fall movement is malfunctioning or inoperative. A further objective of the present invention is to provide a system for compensation of the rise and fall movement of the reserve waves which is compact and self-contained so that it can be installed in the limited space available on a floating drilling platform. These and other objects will become apparent to those skilled in the art from a review of the following specification.

BRIEF DESCRIPTION OF THE INVENTION An apparatus is described for providing a compensation system for the up and down movement of reserve waves. The disclosed invention is a single inline compensator in which a plurality of cylinders housed within a tubular housing and one or more low pressure and high pressure accumulators function together to provide a system for compensating for the up and down movement of the waves in case the primary compensation system of the wave rise and fall movement fails or becomes inoperative. The in-line compensator of the present invention utilizes a plurality of hydraulic cylinders which act in opposite directions and which have different piston areas such that the piston rods of the cylinders extend or retract at different levels of pulling force (ie say, of tension) to respond to the movement of rising and falling waves. The in-line compensator of the present invention is self-contained and compact enough to place it in the limited space available on a floating drilling structure. In one aspect, the present invention relates to an in-line compensator apparatus for a floating vessel comprising an outer housing sealed at both ends by end caps; a first inner cylinder housed at least partially inside the outer housing, the first inner cylinder has a first diameter and has a piston head and a piston rod therein; the second inner cylinder is housed at least partially inside the outer housing, the second inner cylinder has a second diameter and has a piston head and a piston rod, wherein the cross-sectional area of the piston head of the first cylinder Inner is larger than the cross-sectional area of the piston head of the second inner cylinder, the piston rod of the first inner cylinder extends through an end cap of the outer housing and has a connection projection on the end of the rod. of piston outside the outer housing, and the piston rod of the second inner cylinder extends through the other end cap of the outer housing and has a connection projection on the end of the piston rod outside the outer housing so that piston rods can extend and retract in response to the movement of rising and falling waves of the floating boat; one or more low pressure accumulators in communication with the low pressure side of the piston heads of the first and second inner cylinders; and a high pressure accumulator in communication with the high pressure side of the piston heads of both the first and the second inner cylinders, the high pressure accumulator comprises the open volume surrounding the inner cylinders within the outer housing. In one aspect, the present invention relates to an in-line compensator apparatus for a floating vessel comprising an outer housing sealed at both ends by end caps; a first inner cylinder housed at least partially within the outer housing, the inner cylinder having a piston head and a piston rod therein; a plurality of inner cylinders of a second diameter housed at least partially within the outer housing, the plurality of inner cylinders each having a piston head and a piston rod therein, wherein the plurality of inner cylinders are spaced around of the circumference of the inner cylinder of a first diameter, the total cross-sectional area of the piston head of the plurality of inner cylinders is greater than the cross-sectional area of the cylinder piston head, inner of a first diameter, the piston rod of the inner cylinder of a first diameter extends through an end cap of the other housing and has a connection projection on the end of the piston rod outside the outer housing, and the piston rods of the plurality of inner cylinders extend towards the other end cap of the outer housing and each has a connecting projection on the end of the piston rod outside the outer housing such that the piston rods can extend and retract in response to movement of rise and fall of the waves of the floating boat; one or more low pressure accumulators in communication with the low pressure side of the piston heads of both the inner cylinder of a first diameter and the plurality of inner cylinders; and a high pressure accumulator in communication with the high pressure side of the piston heads of both the inner cylinder of a first diameter and the plurality of inner cylinders, the high pressure accumulator comprises an open volume surrounding the inner cylinders inside the outer housing. In another aspect of the present invention the in-line compensator apparatus comprises a means for connecting the in-line compensator to the hoist system of the floating vessel and systems connected to the bottom of the sea such systems include, but are not limited to, a head of extraction on the floating vessel, a drilling column of a floating drilling platform, extraction pipe and / or other tubular components of the well that extend from a floating vessel to the bottom of the sea.

BRIEF DESCRIPTION OF THE DRAWINGS The following figures are part of the present specification and are included to further demonstrate certain aspects of the present invention. The invention can be better understood with reference to one or more of these figures in combination with the detailed description of specific embodiments presented therein. Figure 1 is a cross-sectional view of a typical ocean bottom drilling vessel (seen from the stern of the ocean bottom drilling vessel) showing various components of the ocean bottom drilling vessel used in drilling for deposits of oil and gas further in Figure 2 is a side view of an in-line compensator according to an embodiment of the present invention. Figure 3 is an end-facing end view of the line compensator of Figure 2, seen along line AA shown in Figure 2. Figure 4 is a horizontal cross-sectional view of a compensator in line of figure 2 which is seen along the line BB shown in figure 2. Figure 5 is a vertical cross-sectional view of an in-line compensator of figure 2 which is observed along the line CC shown in figure 2. Figure 6 is a three-dimensional diagrammatic view of an in-line compensator according to an embodiment of the present invention.

Fig. 7 is a side view of in-line compensator shown in Fig. 6. Fig. 8 is a downward-facing end view of the in-line compensator of Fig. 7 seen along the line DD shown in Fig. 7. Figure 7. Figure 9 is an end-facing end view of the in-line compensator of Figure 7 seen along the line EE shown in Figure 7. Figure 10 is a horizontal cross-sectional view of the inline compensator of Figure 7 seen along the line FF shown in Figure 7. Figure 11 is a vertical cross-sectional view of the in-line compensator of Figure 7 seen along the line GG that is shown in Figure 8. Figure 12 shows a pair of typical in-line compensations according to one embodiment of the present invention installed between the hoisting frame and the extraction head (or surface tree) of a drilling platform. Typical floating n Figure 12 shows the in-line compensators, in the normal operating position when the primary compensation system of the wave rise and fall motion works properly. Figure 13 shows the in-line compensators of Figure 12, in a fully extended position. The in-line compensators shown in Figure 13 are operating in place of the primary system for compensation of motion of rising and falling waves, inoperative and has been fully extended to respond to the increase of the floating drilling platform as it rises to the crest of a wave. Fig. 14 shows the in-line compensators of Fig. 12 in the fully retracted position. The in-line compensators shown in Figure 14 are functioning in place of the primary compensation system of the inoperative wave rise and fall motion and have been fully retracted in response to the descent of the floating drilling platform as it descends to the breast, between waves. Figure 15 is a block diagram showing the manner in which the cylinders and accumulators of the in-line compensator according to one embodiment of the present invention work together to compensate for the rise and fall movement of the waves during the operation of the compensator. online. Figure 16 is a graph showing the relationship between the stroke length of the pistons of a typical in-line compensator versus the pull force on the piston rods during the operation of the in-line compensator according to an embodiment of the present invention . Figure 17 is a graph showing the pressure within the cylinders and within the common accumulator of a typical in-line compensator versus the stroke length of the pistons during the operation of the in-line compensator, in accordance with one embodiment of the present! nvention DETAILED DESCRIPTION OF THE ILLUSTRATIVE MODALITIES The following examples are included to demonstrate preferred embodiments of the invention. It should be appreciated by those skilled in the art that the techniques described in the examples that follow represent techniques discovered by the inventors to work well in the practice of the invention and therefore can be considered to build preferred modes for their practice. However, those skilled in the art, based on the present disclosure, will appreciate that many changes can be made in the specific embodiments which are described and still obtain a similar or similar result without departing from the spirit and scope of the invention. With reference to figure 1, various components of a ship are shown for perforations of the typical ocean floor. As shown in the figure, the ocean bottom drilling vessel has a drilling floor that supports a riser tube tensioning system that keeps the extraction riser in tension (the conduit extending from the vessel for drilling). from the ocean floor to the underwater Christmas tree or the wellhead). The drilling lathe for the platform is also mounted on the floor of the platform. On some floating drilling rigs, the drilling lathe will have an active drilling lathe system of the wave rise and fall motion as the primary compensation system for wave rise and fall motion. A derrick extends upwards, above the floor of the platform. The derrick contains the main hoist and the tubular components used in the drilling operations. Specifically, as shown in Figure 1, the drilling line, or stable line, runs from the drill wheel to the top of the drill tower where it is integrated in the saddle assembly. From the pulley stand, the drill line runs down and is clamped on the drill wheel, the scroll block can be raised or lowered during drilling operations. The upper impeller, which is installed just below the displacement block as shown in Figure 1, is used to rotate the bore column during drilling operations. The primary compensation system for the wave rise and fall movement for the ocean bottom drilling vessel shown in Figure 1 is an active drilling lathe system with wave rise and fall motion or a drilling system. upper compensation mounted on top of the tower. As discussed in the above, if this primary system of compensating for the movement of rising and falling waves is disabled or becomes inoperative for some reason, the ship for drilling of the ocean floor has no way to respond to the movement of rise and fall of the waves of the vessel without a reserve system or secondary compensation of the wave rise and fall movement such as that described herein. Referring now to Figure 2, a side view of the typical in-line compensator 10 is shown, in accordance with a preferred embodiment of the present invention. The in-line compensator shown in Figure 2 comprises a tubular housing 20 closed at both ends by end caps 60 and 70 which are connected to the tubular housing 20. Figure 2 shows the end caps 60 and 70 attached to the tubular housing 20; however, the end caps 60 and 70 can be connected to the tubular housing 20 by any suitable connection means capable of withstanding high pressures and capable of providing a tight connection to both the air and fluids. Running longitudinally along the length of the tubular housing 20 is a series of pipes comprising a low pressure accumulator 30 and a low pressure accumulator 35 (shown in Figure 3). As shown in more detail with reference in figure 5, the low pressure accumulator 30 and the low pressure accumulator 35 are in communication with the low pressure side of the piston head 90 and the piston head 100 through the end cap 60. In the embodiment shown in Figure 2, the inner cylinder 40 extends into the tubular housing 20 through the end cap 60. The piston rod 45 runs longitudinally inside the inner cylinder 40 and, as shown in FIG. 5, joins the piston head 90. A connecting projection 48 is connected to the piston rod 45. The connection projection 48 can be connected to the piston rod 45 by any suitable connection means including, but not limited to a connection projection 48 threadably coupled to the piston rod 45, a connection projection 48 welded to the piston rod 45, a projection 48 for connection with a bolt or with a screw to the piston rod 45 or a connection projection 48 which can be integrally formed with the piston rod 45. When used, the connection projection 48 connects the in-line compensator 10 to the location of the floating drilling platform (as discussed in more detail with reference to Figures 12 to 14). Similarly, the inner cylinder 50 extends into the tubular housing 20 through the end cap 70. The piston rod 55 runs longitudinally inside the inner cylinder 50 and, as shown in FIG. 5, joins the piston head 100. The connecting projection 58 is connected to the piston rod 55. The connection projection 58 can be connected to the piston rod 55 by any suitable connecting means including, but not limited to, threaded coupling connecting the connecting projection 58 to the piston rod 55, the welding that connects to the piston rod 55. projection 58 connecting to the piston rod 55, a nut or screw connecting the connecting projection 58 to the piston rod 55 or a connecting projection 58 which can be formed integrally with the piston rod 55. When used, the connection projection 58 connects the in-line compensator 10 in place on the floating drilling platform (as discussed in more detail with reference to Figures 12 to 14). Figure 3 is a view of the end cap 60, as seen along the line AA shown in Figure 2. As can be seen in Figure 3, the tubing of the low accumulators 30 and 35 The pressure passes through the end cap 60 in such a manner that it enters the tubular housing 20 and is in fluid communication with the low pressure side of the piston head 90 and the piston head 100 within the tubular housing 20 (as shown in FIG. shown in figure 5). The operation of the low pressure accumulator 30 and the low pressure accumulator 35 will be discussed in more detail with reference to the operation of the in-line compensator of the present invention. Figures 2 and 3 also show the low pressure accumulator 30 and the low pressure accumulator 35 attached to the outer surface of the tubular housing 20. The low pressure accumulators 30 and 35 can be attached to the tubular housing 20 in any manner capable of holding the fixed accumulators in place during the operation of the in-line compensator. In the preferred embodiment, the low pressure accumulators 30 and 35 are attached to the outer surface of the tubular housing 20 with the tube supports.

In alternative embodiments of the present invention, the low-pressure accumulators 30 and 35 can also be housed within the tubular housing 20, or a low-pressure accumulator can be accommodated within the tubular housing 20 and another low-pressure accumulator can be attached to the tubular housing 20. outer surface of the housing 20 tubular. A person skilled in the art will appreciate that, based on the size of the tubular housing and the volume available within the tubular housing 20, various combinations of the placement of the low pressure accumulators 30 and 35 can be used. However, it is an object of the present invention to provide an in-line compensator that is self-contained and therefore, the low-pressure accumulators 30 and 35 must remain attached or must be housed within the tubular housing 20. By providing an in-line compensator that is self-contained, the present invention eliminates the need for additional space for separate external accumulators that must be placed on the floor of the platform and eliminates the need for additional piping running from the external accumulators to the in-line compensator. However, as those skilled in the art will appreciate, external accumulators with the present invention can be used without departing from the operation of the in-line compensator. Figure 3 also shows high pressure accumulator pipes 65 connected to the inner cylinder 40 and passing through the end cap 60 into the tubular housing 20. As shown in more detail with reference to Figure 5, the pipe 65 of the high pressure accumulator allows fluid communication between the high pressure sides of the piston head 90 and the piston head 100 and the high pressure accumulator 80 inside the tubular housing 20. Figure 4 is a horizontal cross-sectional view of the in-line compensator of Figure 2 seen along the line BB shown in Figure 2. As can be seen in Figure 4, the tubular housing 20 houses a cylinder 40 interior and a cylinder 50 interior. The cylinder 40 -interior contains a piston rod 45 which extends through the end cap 60 and is connected to the connection projection 48 (as discussed above). Similarly, the inner cylinder 50 contains a piston rod 55 that extends through the end cap 70 and connects to the connecting projection 58 (as discussed above). As can be seen in Figure 4 (and as shown in more detail with reference to Figure 5), the inner cylinder 40 has a smaller diameter and is centered within the inner cylinder 50. The open area surrounding the inner cylinder 50 and the open area of the high pressure side of the piston heads 90 and 100 within the inner cylinders 40 and 50, respectively, are in fluid communication with each other and serve as an accumulator 80 of high pressure in a preferred embodiment of the present invention. The high pressure accumulator 80 comprises hydraulic fluid that fills a specified amount of this open volume within the tubular housing 20.

Similarly, the open area within the cylinder 50 on the low pressure side of the piston head 100 is in communication with the open area within the inner cylinder 40 on the low pressure side of the piston head 90. As discussed in the foregoing, and as shown in more detail with reference to Figure 5, the low pressure sides of the piston heads 90 and 100 are in communication with the low pressure accumulators 30 and 35. Figure 5 is a cross-sectional view of a preferred embodiment of the in-line compensator 10, seen along the line CC shown in Figure 2. As can be seen in Figure 5, the piston head 90 is shown in FIG. joins (or is formed integrally) with the piston rod 45 inside the inner cylinder 40. In a similar way, the piston head 100 is joined (or formed integrally with) the piston rod 55 inside the inner cylinder 50. As discussed in more detail in the following, with reference to Figures 15-17, the size of the piston heads defines the piston area which, together with the accumulator pressure, controls the amount of force that the pistons of the pistons have. inner cylinders 40 and 50 can compensate during the operation of in-line compensator 10. As can be seen in Figure 5, the low pressure accumulators 30 and 35 are in communication with the low pressure sides of the piston heads 90 and 100 contained within the inner cylinders 40 and 50, respectively. The communication between the low pressure side of the piston head 90 and the low pressure side of the piston head 100 is facilitated by the ports 110 in the wall of the inner cylinder 40. Figure 5 also shows a high pressure accumulator pipe 65 in fluid communication with the high pressure sides of the piston heads 90 and 100 via a high pressure accumulator 80. Fluid communication between the high pressure side of the piston head 90 and the high pressure side of the piston head 100 is facilitated through the high pressure accumulator line 65 (via the ports 120) and through the ports 130 on the interior cylinder wall 50. Furthermore, to protect the piston head 90 from shock, the low pressure end of the inner cylinder 40 with too great a force when the piston rod 45 retracts, the low pressure end of the inner cylinder 40 may be equipped with a hydraulic shock absorber 140. As shown in Figure 5, if a hydraulic shock absorber 140 is used on the inner cylinder 40, the piston head 90 may have a extension rod 150 attached thereto (or formed integrally therewith) to strike the hydraulic shock absorber 140. . Referring now to Figure 6 there is shown a three-dimensional diagram view of an alternative mode of the inline compensator 200. The in-line compensator shown in Figure 6 comprises a tubular housing 220 closed at both ends by end caps 260 and 270 which are connected to the tubular housing 220. Figure 6 shows the end caps 260 and 270 fastened to the tubular housing 220; however, the end caps 260 and 270 can be connected to the tubular housing 220 by any suitable connection means capable of withstanding high pressures and capable of providing a tight connection to both the air and the fluids. Running longitudinally along the length of the tubular housing 220 is a series of pipes comprising a low pressure accumulator 230 and a low pressure accumulator 235. In the embodiment of the present invention shown in Figure 6, the low pressure accumulator 230 is in communication with a group of three inner cylinders 310 through the end cap 260. Similarly, although not shown in Figure 6, the low pressure accumulator 235 is in communication with only one cylinder 300 through the end cap 270. In the embodiment shown in Figure 6, the projection plate 245 is connected to a single piston rod 290 which extends into the tubular housing 220 through the end cap 260. The U-shaped projection 240 is connected to the projection plate 245. The projection 240 can be connected to the projection plate 245 by any suitable connection means or it can be formed integrally with the projection plate 245. Similarly, the projection plate 255 is connected to three piston rods 280 that extend into the tubular housing 220 through the end cap 270 (as shown in greater detail in Figure 7). The U-shaped projection 250 is connected to the projection plate 255. The projection 250 can be connected to the projection plate 255 by any suitable connection means or it can be formed integrally with the projection plate 255. Figure 7 is a side view of the in-line compensator 200 shown in Figure 6. In Figure 7 the connection of the projection plate 255 of the piston rods 280 is shown in greater detail. In the embodiment of the present invention shown in Figure 7, the piston rods 280 are connected to the projection plate 255 by fasteners 256 screwed onto the threaded ends of the piston rods 280 that extend through the plate. 255 of projection. In a similar manner, the piston rod 290 can be connected to the projection plate 245. A person skilled in the art will appreciate that the piston rods 280 and the piston rod 290 can be connected to the projection plate 255 and the projection plate 245, respectively, by any suitable connection means capable of withstanding the high forces of tension imparted to the piston rods during the operation of the in-line compensator. Figure 8 is a view of the end cap 270, as seen along the line DD shown in Figure 7. As can be seen in Figure 8, the rod plate 255 is connected to the rod 250 and is specially shaped so that the projection plate 255 can be attached to multiple piston rods 280 (three are numbered, as shown in FIG. 7) via fasteners 256.

Figure 8 also shows the tubing of the low pressure accumulator 235 passing under the projection plate 250 so that it can be connected to the end of the inner cylinder 300 through the end cap 270. The operation of the low pressure accumulator 235 and the low pressure accumulator 230 will be discussed in more detail with reference to the operation of the in-line compensator of the present invention. Figure 9 is a view of the end cap 260, as seen along the line EE shown in Figure 7. The projection plate 245 is connected to the projection 240 and, although not shown, is connects to single piston rod 290 (as shown in figure 6). Figure 9 also shows the tubing of a low pressure accumulator 230 connected to the ends of the inner cylinders 310 through the end cap 260. Figure 10 is a cross-sectional view of the mode of the in-line compensator 200 seen along the line F-F shown in Figure 7. As can be seen in Figure 10, the tubular housing 220 accommodates a plurality of individual cylinders - single internal cylinder 300 and a group of three smaller inner cylinders 310. The inner cylinder 300 contains a piston rod 290 that extends through the end cap 260 and connects to the projection plate 245 (as discussed above). Similarly, the three inner cylinders 310 contain piston rods 280 which extend through the end cap 270 and which connect to the projection plate 255 (as discussed above).

The open area surrounding the inner cylinders 300 and 310, shown in Fig. 10, serves as a high-pressure accumulator 350. The high pressure accumulator 350 comprises hydraulic fluid that fills a specified amount of the open volume of the interior of the tubular housing 220. The high pressure accumulator 350 is in fluid communication with the high pressure side of the pistons inside the inner cylinders 300 and 310 (as shown by the block diagram of the on-line compensator operation shown in Fig. 15) . In alternative embodiments of the present invention, the high pressure accumulator may comprise separate individual accumulators, for each inner cylinder or groups of inner cylinders. A person skilled in the art will appreciate that various configurations can be used for the high pressure accumulator without departing from the objects of the present invention. Figure 10 also shows a low pressure accumulator 230 and a low pressure accumulator 235 attached to the outer surface of the tubular housing 220. The low pressure accumulators 230 and 235 can be attached to the tubular housing 220 in any manner capable of holding the fixed accumulators in place during the operation of the in-line compensator. The preferred method of attaching the low pressure accumulators 230 and 235 to the outer surface of the tubular housing 220 is with tube supports. As indicated in the foregoing, alternative embodiments of the present invention may use low pressure accumulators 230 and 235 housed within the tubular housing 220, or a low pressure accumulator may be accommodated within the tubular housing 220 and a low pressure accumulator it can be attached to the outer surface of the tubular housing 220. A person skilled in the art will appreciate that, depending on the size of the tubular housing 220 and the volume available within the tubular housing 220, various combinations may be used for the placement of the low pressure accumulators 230 and 235. Figure 11 is a cross-sectional view of the in-line compensator 200 which is seen along the line GG shown in Figure 8. As can be seen in Figure 11, the piston head 291 is attached (or is formed integrally with) the piston rod 290 within the inner cylinder 300. Similarly, the piston heads 281 are attached (or integrally formed) to the piston rods 280 within the interior cylinders 310. As discussed in more detail in the following, with reference to Figures 15-17, the size of the piston heads defines the piston area which, together with the pressure of the accumulator, controls the amount of force that the pistons of the pistons have. Internal cylinders 300 and 310 can compensate during operation of the in-line compensator 200. Figure 11 also shows the connection of the low pressure accumulators 230 and 235 to the low pressure sides of the pistons contained within the inner cylinders 300 and 310. Although the embodiments of the present invention discussed herein use a larger inner cylinder and a smaller inner cylinder (Figures 2 to 5), or a larger inner cylinder and a group of three smaller inner cylinders (Figures 6). to 11), the number and size of the inner cylinders housed within the tubular housing 20 or 220 may vary based on the application - as discussed in more detail in the following, with reference to Figures 12-17.

Operation of the In-Line Compensator Having described the in-line compensator components of the present invention, the operation of the on-line compensator will be described with reference to Figures 12 to 17. The operation of the in-line compensator of the present invention will be described with reference to the mode that uses a larger inner cylinder and a group of three smaller inner cylinders (figures 6 to 11). Specifically, with reference to Figures 12 to 14, a pair of in-line compensators 200 according to one embodiment of the present invention, are shown installed between the lifting frame 400 (which is connected between the lower part 500 of the tube and the hoist 510) and the extraction head 450 of a typical floating drilling platform are placed in an early extraction distribution. Installed in this manner, the in-line compensators 200 hang above the floor of the platform, from the floating drilling platform. As can be seen in Figure 12, the projections 250 of the in-line compensators 200 are connected to the extraction head 450 via a connecting means 460. Similarly, the projections 240 of the in-line compensators 200 are connected to the lifting frame 400 via the connecting means 410. In the position shown in Fig. 12, the piston rods 290 fully extend, while the piston rods 280 completely retract. In the fully extended position, the piston rods 290 extend above the end cap 260, approximately 6 meters. A person skilled in the art will appreciate that the extension - or "stroke" - of the piston rods 290 may be increased or decreased depending on the application for which the line compensators are used. As will be discussed in the following with reference to Figs. 16-17, the position shown in Fig. 12 represents the "static" operating position of the in-line compensators 200 -that is, the position where the primary system compensation of the movement of rising and falling waves works properly. Figures 13 and 14 show the in-line compensators 200 in the "operational mode" -that is, the in-line compensators 200 are now operating due to the primary compensation system of the wave rise and fall movement that has become inoperative. With reference to Figure 13, the piston rods 280 of the in-line compensators 200 are shown fully extended. In this position, the floating drilling rig has ascended to the crest of a wave, and needs the piston rods 280 to extend. In the extended position, the piston rods 280 extend about 6 meters and, therefore, can support a 6 meter riser tube on the floating drilling platform due to the wave rise and fall movement. A person skilled in the art will appreciate that the extension - "stroke" - of piston rods 280 can be increased or decreased, depending on the application for which in-line compensators are used. With reference to Figure 14, both piston rods 290 and piston rods 280 are in their fully retracted position. In this position, the floating drilling rig has descended to the bosom between waves, and it needs the piston rods to retract. Given the extended length of 6 meters for both piston rods 280 and 290 (shown in Figure 13), in-line compensators 200 are capable of accommodating a difference of 12 meters between the crest of a wave and the sine between waves as the floating drilling platform follows the movement of rising and falling waves. Referring now to Figures 15 to 17, a more detailed discussion of the operation of the in-line compensator of the present invention is provided. In operation, the typical in-line compensator of the present invention is a passive hydraulic system with two or more cylinders or groups of cylinders working "spine-to-spine". That is to say, when the primary compensation system for the wave rise and fall movement works as normal, the in-line compensator will only be a static system. If the primary system of compensating for the wave rise and fall movement fails, the in-line compensator of the present invention will function to compensate for the rise and fall movement of the waves of the floating drilling platform. In the online compensator mode discussed with reference to figures 15 to 17, the in-line compensator comprises a total of four hydraulic cylinders - the inner cylinders 300 and 310 shown in Fig. 10. In operation, the piston of the "cylinder 1" -which is shown as inner cylinder 300 in Fig. 10- it works in one direction while the three pistons of the "group 2 cylinder" - which are shown as inner cylinders 310 in figure 10 - work in the opposite direction. Additionally, the piston area within the two cylinder combinations is different. The total piston area of the cylinder of group 2 is larger than the piston area of the single piston of cylinder 1. The side of the piston rods - or high pressure side - of the pistons in cylinder 1 and cylinder 2 is fluidly connected together in a closed circuit hydraulic system with a high pressure accumulator (shown as in number 350 in Figure 10). As such, at the "point of operation" shown in FIGS. 16 and 17, the pressure on the piston rod side of the pistons in cylinder 1 and in the cylinder of group 2 will be the same. The piston head - or the low pressure side - of the pistons is referred to as the "air" or "gas" side of the pistons. By way of example, figures 16 and 17 graphically show the operation of the in-line compensator, according to the modality shown in figures 12 to 14. The closed circuit hydraulic system of the "preload" line compensators at a defined pressure , determined by the specific application. For the given application, shown in Figures 16 and 17, the hydraulic system pre-load pressure will correspond to a pulling force of approximately 70 metric tons and the tension of the extraction pipe is assumed to be approximately 100 metric tons . At this preload pressure, the piston rods of both cylinder 1 and cylinder of group 2 are fully retracted. To place the compensators in line in the static mode shown in Figure 12, the piston rods 290 of the cylinder 1 extend when a pulling force is applied on the rods. When the pulling force on the piston rods 290 has reached approximately 85 metric tons, the piston rods 290 of the cylinder 1 are fully extended. Once the in-line compensators have been installed and are ready for operation, the in-line compensators will act as a static system between the approximately 85 metric tons and 115 metric tons. This static force interval is known as the "working interval" -that is, the interval in which the primary compensation system of the wave rise and fall movement works properly and the in-line compensator is static. Insofar as the pulling force on the in-line compensators remains in the range between 85-115 metric tons, the piston rods of cylinder 1 will remain fully extended and the piston rods of the cylinder of group 2 will remain fully retracted. This working interval is shown in Figure 16 as a vertical line. If the primary system of compensating for the wave rise and fall movement fails, the on-line compensator begins to work. While the floating drilling rig rises in a wave, the tension of the production pipeline - and therefore the pulling force of the in-line compensator - will increase to 115 metric tons and more. At approximately 115 metric tons, the piston rods of the group 2 cylinder begin to extend and continue until they have fully extended (resulting in a total "extension" of 12 meters for in-line compensators) to approximately 145 metric tons (as shown in figure 16). As the floating drilling platform descends to the bosom between waves, the tension in the extraction pipe - and therefore the pulling force of the in-line compensator - will decrease. As the pull force of the in-line compensator decreases, the piston rods of the cylinder of group 2 are retracted. When the pulling force decreases to approximately 115 metric tons, the piston rods of the cylinder of group 2 are completely retracted. As the pulling force continues to decrease below approximately 85 metric tons, the piston rods of cylinder 1 will also retract to respond to the platform at the bottom of the breast. When the pulling force decreases to approximately 70 metric tons, the piston rod of cylinder 1 has been completely retracted (resulting in a total "extension" of 0 meters for the in-line compensator). The expansion and retraction cycle of the piston rods of the in-line compensator continues as necessary to respond to the frequency of the waves found on the floating drilling platform. With reference to Figure 17, the pressure on the high pressure side of the pistons of cylinder 1 and of the cylinder of group 2 as well as the pressure inside the high pressure accumulator is shown as a function of the extension - or stroke - of the piston rods. Viewing Figure 17 and Figure 15 together show how the high-pressure accumulator 350, or a common accumulator, operates with the in-line compensator pistons during operation. Specifically, as the piston rods of cylinder 1 extend, as the pulling force of the rod increases, the fluid side pressure of the cylinder 1 piston increases, forcing the fluid into the common accumulator and thereby increasing the pressure in the common accumulator. In the example discussed herein, in the fully retracted position, the fluid pressure in the cylinders and in the common accumulator is approximately 138 bars (see Figure 17). As the pull force of the piston rods of cylinder 1 increases, the fluid pressure in all cylinders and the common accumulator increases to approximately 163 bars in the fully extended position of the piston rod of cylinder 1. If the force of Pulling of the in-line compensator continues to increase (due to a failure of the primary system to compensate for the movement of rising and falling waves), the piston rods of the cylinder of group 2 will be extended causing the pressure of the piston fluid side in all the cylinders and the fluid pressure in the common accumulator is increased. In the example discussed herein, the fully extended position, the fluid pressure in all the cylinders and in the common accumulator is increased to approximately 207 bars (see Figure 17). The increased pulling force that can be applied to the piston rods of the cylinder of group 2 is attributable to an increased total piston area of the cylinder of group 2. As discussed in the foregoing, the mode of the in-line compensator shown in Figure 10 has a large inner cylinder 300 (cylinder 1) and three smaller inner cylinders 310 (group 2 cylinder) housed in a tubular housing 220. The piston area in cylinder 1 is smaller than the combined piston area of the pistons in the group 2 cylinder. This difference allows the piston rods of the group 2 cylinder to remain retracted until greater pulling forces are achieved. It is this difference in the piston area between the two groups of cylinders coupled with the pressure inside the common accumulator that determines the working range of the in-line compensator. Although the operating point for the in-line compensators of the example discussed herein is 100 metric tons (as shown in Figure 16), a person skilled in the art will appreciate that this point of operation can be changed by varying several factors that include the number of cylinders, the size of the piston rods and the diameter of the pistons. Additionally, although the in-line compensator embodiments discussed herein comprise a single larger inner cylinder and a single smaller inner cylinder (Figures 2 to 5) or a single larger inner cylinder and three smaller inner cylinders (Figures 6 to 11) ), a person skilled in the art will appreciate that the alternative embodiments may use two and two cylinders, two and three cylinders or any combination that is required for the given application. For example, in alternative embodiments used in deep water operations, the in-line compensator of the present invention can be made with variable cylinder sizes and numbers to provide a greater range of working force through an increased pressure difference between the two groups of cylinders. In addition, the race of the preferred modality of the on-line compensator is +6 meters (12 meters in total). A person skilled in the art will appreciate that this stroke length can be adjusted by changing the length of the piston rods and cylinders. By allowing to vary the stroke lengths, the customer can control the stroke length to fit his given application and size limitations. In addition, although the discussion herein with respect to Figures 12 to 17 is in reference to a pair of in-line compensators that work together, a typical application will have a single in-line compensator installed directly on the header of the platform extraction. floating drilling. The in-line compensator can not be used in applications in which pipe routing operations will be carried out, however, because the injector head of strapping tubing must be installed directly above the extraction shaft. By using two in-line compensators of the present invention, operators are allowed to provide a compensation system for the movement of the rise and fall of reserve waves that still allows carrying out pipe-biting operations. In particular, by using two smaller compensators of the present invention as shown in Figures 12-14, an operator will still have space and height for the injector head to be installed between the two compensators. Although the apparatuses, compositions and methods of this invention have been described in terms of preferred or illustrative embodiments, it will be apparent to those skilled in the art that variations may be applied to the process described herein without departing from the concept and scope of the invention. . All such substitutes and similar modifications will be apparent to those skilled in the art and are considered to be within the scope and concept of the invention as set forth in the following claims.

Claims (72)

1. NOVELTY OF THE INVENTION CLAIMS 1. - An in-line compensator apparatus for a floating vessel, comprising: an outer housing sealed at both ends by end caps; a first inner cylinder housed at least partially inside the outer housing, the first inner cylinder has a first diameter and has a piston head and a piston rod therein; the second inner cylinder is housed at least partially within the outer housing, the second inner cylinder has a second diameter and has a piston head and a piston rod therein, wherein the cross-sectional area of the piston head of the first inner cylinder is larger than the cross-sectional area of the piston head of the second inner cylinder, wherein the piston rod of the first inner cylinder extends through an end cap of the outer housing and has a connecting projection on the end of the piston rod outside the outer housing, wherein the piston rod of the second inner cylinder extends through the other end cap of the outer housing and has a connecting projection on the piston rod end outside the piston rod. external housing, where the inline compensating device is operable with the boat lifting system flo so that the piston rods can extend and retract to respond to the movement of rising and falling waves of the floating boat; one or more low pressure accumulators in communication with the low pressure side of the piston heads of the first and second inner cylinders; and a high pressure accumulator in communication with the high pressure side of the piston heads of the first and second inner cylinders, the high pressure accumulator comprises the open volume surrounding the inner cylinders within the outer housing.
2. 2. The line compensator apparatus according to claim 1, further characterized in that the first inner cylinder passes through an end cap of the outer housing.
3. 3. The line compensator apparatus according to claim 1, further characterized in that the second inner cylinder passes through an end cap of the outer housing.
4. 4. The line compensating device according to claim 1, further characterized in that the pipe of one or more pressure accumulators pass through an end cap of the outer housing.
5. 5. The line compensator apparatus according to claim 1, further characterized in that the pipe of the high pressure accumulator passes through an end cap of the outer housing.
6. 6. The line compensator apparatus according to claim 1, further characterized in that one or more of the low pressure accumulators are attached to the outer surface of the outer housing.
7. 7. The line compensator apparatus according to claim 6, further characterized in that one or more low pressure accumulators are attached to the outer surface of the outer housing by tube supports.
8. 8. The line compensator apparatus according to claim 1, further characterized in that one or more low pressure accumulators are housed at least partially inside the outer housing.
9. 9. The line compensator apparatus according to claim 1, further characterized in that one or more of the low pressure accumulators are attached to the outer surface of the outer housing and one or more of the low pressure accumulators are housed within the outside accommodation.
10. 10. The line compensator apparatus according to claim 1, further characterized in that it further comprises the low pressure end of the first inner cylinder having a hydraulic shock absorber.
11. 11. The in-line compensator apparatus according to claim 10, further characterized in that the piston head inside the first inner cylinder has an extension rod for hitting the hydraulic shock absorber. 12. - The line compensator apparatus according to claim 1, further characterized in that the connection projections are attached to the piston rods. 13. The line compensator apparatus according to claim 1, further characterized in that the connection projections are formed integrally as part of the piston rods. 14. The in-line compensator apparatus according to claim 1, further characterized in that the in-line compensator is usually static but becomes operational if a primary system of compensating for the movement of rising and falling waves in the floating vessel becomes inoperative. 15. An in-line compensator apparatus for a floating vessel, comprising: an outer housing sealed at both ends by end caps; an inner cylinder of a first diameter housed at least partially inside the outer housing, the inner cylinder having a piston head and a piston rod therein; a plurality of inner cylinders of a second diameter housed at least partially within the outer housing, the plurality of inner cylinders each having a piston head and a piston rod therein, wherein the plurality of inner cylinders are spaced around of the circumference of the inner cylinder of a first diameter, wherein the total cross-sectional area of the piston heads of the plurality of inner cylinders is greater than the cross-sectional area of the piston head of the inner cylinder of a first diameter , wherein the piston rod of the inner cylinder of a first diameter extends through an end cap of the outer housing and has a connection projection on the end of the piston rod outside the outer housing, wherein the piston rods of the plurality of inner cylinders extend through the other end cap of the externally and each has a connection projection on the end of the piston rod outside the outer housing, wherein the in-line compensator apparatus is operable with a hoist system of a floating vessel such that the piston rods can be extend and retract in response to the movement of rising and falling waves of the floating boat; one or more low pressure accumulators in communication with the low pressure side of the piston heads of both the inner cylinder of a first diameter and the plurality of inner cylinders; and a high pressure accumulator in communication with the high pressure side of the piston heads of both the inner cylinder of a first diameter and the plurality of inner cylinders, the high pressure accumulator comprises an open volume surrounding the inner cylinders inside the outer housing. 16. The line compensator apparatus, according to claim 15, further characterized in that the inner cylinder of a first diameter passes through an end cap of the outer housing. 17. - The line compensator apparatus, according to claim 15, further characterized in that the plurality of inner cylinders pass through an end cap of the outer housing. 18. The line compensating device, according to claim 15, further characterized in that the pipe of one or more of the low pressure accumulators passes through an end cap of the outer housing. 19. The line compensator apparatus, according to claim 15, further characterized in that the high pressure accumulator pipe passes through an end cap of the outer housing. 20. The in-line compensator apparatus, according to claim 15, further characterized in that one or more low pressure accumulators are attached to the outer surface of the outer housing. 21.- The online compensating device, according to claim 20, further characterized in that one or more low pressure accumulators are attached to the outer surface of the outer housing by tube supports. 22. The online compensating apparatus according to claim 15, further characterized in that one or more low pressure accumulators are housed at least partially inside the outer housing. 23. The line compensator apparatus, according to claim 15, further characterized in that one or more of the low pressure accumulators are attached to the outer surface of the outer housing and one or more of the low pressure accumulators are housed by at least partially inside the outer housing. 24. The online compensating device, according to claim 15, further characterized in that the connection projections are attached to the piston rods. 25. The in-line compensator apparatus, according to claim 15, further characterized in that the connection projections are formed integrally as part of the piston rods. 26. The in-line compensator apparatus, according to claim 15, further characterized in that the in-line compensator is normally static but becomes operational if the primary system of compensating for the movement of rising and falling waves in the floating vessel is It becomes inoperative. 27.- An in-line compensating device for a floating vessel, comprising: an outer housing; one or more upwardly facing inner cylinders housed at least partially within the outer housing, one or more of the inner cylinders facing upwards have a first diameter and have a piston head and a piston rod thereon; one or more of the downward facing inner cylinders housed at least partially within the outer housing, one or more of the inner cylinders facing downwards each have a second diameter and have a piston head and a piston rod therein , wherein the total cross-sectional area of the piston heads of one or more of the inner cylinders facing downwards is greater than the total cross-sectional area of the piston heads of one or more of the inner cylinders facing upwards; wherein the piston rods of one or more of the inner cylinders facing downwards extend downwards and the piston rods of one or more of the inner cylinders facing upwards extend upwards so that the piston rods can be extend and retract in response to the movement of rising and falling waves of a floating boat; one or more low pressure accumulators in communication with the low pressure side of the piston heads of the inner cylinders facing upwards and downwards; and one or more high pressure accumulators in communication with the high pressure side of the piston heads of the inner cylinders oriented up and down. 28. The online compensating device, according to claim 27, further characterized in that the outer housing is sealed at both ends by end caps. 29. The online compensating apparatus, according to claim 28, further characterized in that one or more of the inner cylinders facing downwards pass through an end cap of the outer housing. 30. The in-line compensator apparatus, according to claim 28, further characterized in that one or more of the inner cylinders facing upwards pass through an end cap of the outer housing. 31. The line compensating device, according to claim 28, further characterized in that the piston rods of one or more of the inner cylinders facing upwards pass through one of the end caps of the outer housing and the rods piston of one or more of the inner cylinders facing downwards pass through the other end cap of the outer housing. 32.- The in-line compensator apparatus, according to claim 31, further characterized in that the ends of the piston rods of one or more of the inner cylinders facing upwards extending through the end cap have, each one, a means for connecting the compensating apparatus and line to the lifting equipment of the floating vessel. 33.- The in-line compensator apparatus, according to claim 32, further characterized in that the means for connecting the in-line compensator to the hoisting equipment of the floating vessel is attached to the piston rods. 34.- The in-line compensator apparatus, according to claim 32, further characterized in that the means for connecting the in-line compensator to the lifting equipment of the floating vessel is formed integrally as part of the piston rods. 35. - The in-line compensator apparatus, according to claim 32, further characterized in that the ends of the piston rods of one or more of the inner cylinders facing downwards extending through the end cap each have a means to connect the compensating device in line to equipment to support tubular sections of the floating vessel. 36. The in-line compensator apparatus, according to claim 35, further characterized in that the means for connecting the in-line compensator to the equipment for supporting tubular sections of the floating vessel is attached to the piston rods. 37.- The in-line compensator apparatus, according to claim 35, further characterized in that the means for connecting the in-line compensator to the equipment for supporting tubular sections of the floating vessel is formed integrally as part of the piston rods. 38.- The in-line compensator apparatus, according to claim 35, further characterized in that the means for connection connects the compensating apparatus in line between a lifting frame and an extraction head on a floating drilling platform. 39.- The online compensating apparatus, according to claim 28, further characterized in that the pipe of one or more low pressure accumulators passes through an end cap of the outer housing. 40. - The in-line compensator apparatus, according to claim 28, further characterized in that the pipe of one or more of the high-pressure accumulators passes through the end cap of the outer housing. 41. The in-line compensator apparatus, according to claim 27, further characterized in that one or more of the low pressure accumulators are attached to the outer surface of the outer housing. 42. The in-line compensator apparatus, according to claim 41, further characterized in that one or more of the low pressure accumulators are attached to the outer surface of the outer housing by tube supports. 43.- The online compensating device, according to claim 27, further characterized in that one or more of the low pressure accumulators are housed at least partially inside the outer housing. 44. The in-line compensator apparatus, according to claim 27, further characterized in that one or more of the low-pressure accumulators are attached to the outer surface of the outer housing and one or more of the low-pressure accumulators are housed by at least partially inside the outer housing. 45. The in-line compensating apparatus, according to claim 27, further characterized in that one or more of the high-pressure accumulators comprises the open space surrounding the inner cylinders within the outer housing. 46. The in-line compensating apparatus, according to claim 27, further characterized in that one or more of the high-pressure accumulators comprises external accumulators attached to the outer surface of the outer housing. 47. The in-line compensator apparatus, according to claim 27, further characterized in that the in-line compensator is normally static but becomes operative if the primary system of compensating for the rise and fall of the waves in the floating vessel is It becomes inoperative. 48.- A method to compensate the movement of the outgoing and descending waves of a floating boat, comprising: providing a compensation system for the movement of rising and falling waves that has an outer housing sealed at both ends by caps of end, the outer housing houses at least partially a first inner cylinder and a second inner cylinder; provide each of the first and second inner cylinders with a piston head and a piston rod therein, wherein the cross-sectional area of the piston head of the first inner cylinder is larger than the cross-sectional area of the piston head. piston head of the second inner cylinder, and wherein each of the piston rods of the first and second inner cylinders extend through an end cap of the outer housing and have a connecting projection on the end of the piston rod outside of the accommodation exterior; providing one or more low pressure accumulators in communication with the low pressure side of the piston heads of both the first and the second inner cylinders; providing a high pressure accumulator in communication with the high pressure side of the piston heads of both the first and second inner cylinders, the high pressure accumulator comprising the open volume surrounding the inner cylinders within the outer housing; positioning the outer housing so that the piston rod of the first cylinder extends upwards and the piston rod of the second inner cylinder extends downward; connect the compensating device in line in such a way that it is operable with the lifting system of the floating vessel; allowing the piston rods of the first and second cylinders to extend and retract in response to the up and down movement of the waves of a floating vessel. 49. The method according to claim 48, further characterized in that the piston rod of the second inner cylinder normally extends between the compensation system of the movement of rising and falling waves is in static mode. 50. The method according to claim 49, further characterized in that the piston rod of the first inner cylinder is normally retracted when the system of compensation of the movement of rising and falling of the waves is in the static mode. 51. - The method according to claim 48, further characterized in that the piston rod of the first outer cylinder extends in response to the rise of the floating vessel to the crest of a wave when the compensation system of the up and down movement of the Waves is operational. 52. The method according to claim 51, further characterized in that the piston rod of the second inner cylinder retracts in response to the descent of the floating vessel to the bosom between waves, when the compensation system of the up and down movement of The waves is operational. 53. The method according to claim 52, further characterized in that the piston rod of the first inner cylinder retracts in response to the descent of the floating vessel to the bosom between waves, when the compensation system of the up and down movement of The waves is operational. 54.- A method to compensate the movement of rise and fall of the waves of a floating boat, comprising: providing a compensation system for the movement of rising and falling waves that has an outer housing sealed at both ends by caps of end, the outer housing houses at least partially an inner cylinder of a first diameter and a plurality of inner cylinders of a second diameter; provide each of the inner cylinders with a piston head and a piston rod therein, wherein the total area without cross section of the piston heads of the plurality of inner cylinders of a second diameter is greater than the area in cross section of the piston head of the inner cylinder of a first diameter, and wherein each of the piston rods of the inner cylinders extends through the end cap of the outer housing and has a connection projection on the end of the piston rod outside the outer housing; providing one or more low pressure accumulators in communication with the low pressure side of the piston heads of the inner cylinders; providing a high pressure accumulator in communication with the high pressure side of the piston heads of the inner cylinders, the high pressure accumulator comprises the open volume surrounding the inner cylinders within the outer housing; positioning the outer housing so that the piston rod of the inner cylinder of a first diameter extends upward and the piston rods of the plurality of inner cylinders extend downward; connect the inline compensator apparatus in a manner that is operable with the flotation boat lifting system; allow the piston rods of the inner cylinders to extend and retract in response to the up and down movement of the waves of the floating vessel. The method according to claim 54, further characterized in that the piston rod of the inner cylinder of a first diameter normally extends when the system of compensation of the movement of rising and falling of the waves is in the static mode. 56. The method according to claim 55, further characterized in that the piston rods of the plurality of inner cylinders are normally retracted when the compensation system of the wave rise and fall motion is in the static mode. 57.- The method according to claim 56, further characterized in that the piston rods of the plurality of inner cylinders extend in response to the rise of the floating vessel to the crest of a wave when the compensation system of the upward movement and descent of the waves is operational. 58. The method according to claim 57, further characterized in that the piston rod of the inner cylinder of a first diameter is retracted in response to the descent of a floating vessel to the valley between waves, when the system of compensation of the movement of rise and fall of the waves is operational. 59. The method according to claim 58, further characterized in that the piston rods of the plurality of inner cylinders are retracted in response to the descent of the floating vessel to the valley between waves when the compensation system of the up and down movement of the waves is operational. 60. - A method for compensating the movement of rising and falling of the waves of a floating boat, comprising: providing a compensation system for the movement of rising and falling waves that has an outer housing sealed at both ends by end caps, the outer housing houses at least partially one or more of the inner cylinders facing upwards and one or more of the inner cylinders facing downwards, providing each of the inner cylinders with a piston head and a piston rod in the same, wherein the total cross-sectional area of the piston heads of one or more of the inner cylinders facing downwards is greater than the cross-sectional area of the piston heads of one or more of the inner cylinders facing upwards and wherein each of the piston rods of the inner cylinders extends through the end cap of the former housing terior and have a connection projection on the end of the piston rod outside the outer housing; providing one or more low pressure accumulators in communication with the low pressure side of the piston heads of the inner cylinders; provide a high pressure accumulator in communication with the high pressure side of the piston heads of the inner cylinders; positioning the outer housing so that the piston rods of one or more of the inner cylinders facing downward extend downward and the piston rods of one or more of the inner cylinders facing upward extend upwards; connect the compensating device in line in such a way that it is operable with the lifting system of the floating vessel; allow the piston rods of the inner cylinders to extend and retract in response to the up and down movement of the waves of a floating vessel. 61.- The method according to claim 60, further characterized in that the piston rods of one or more of the inner cylinders facing upwards are normally extended when the compensation system of the rising and falling movement of the waves is in the static mode 62. The method according to claim 61, further characterized in that the piston rods of one or more of the inner cylinders facing downwards are normally retracted when the compensation system of the wave rise and fall movement is in the static mode 63.- The method according to claim 62, further characterized in that the piston rods of one or more of the inner cylinders facing downwards extend in response to the rise of the floating vessel to the crest of a wave when the system of Compensation of the movement of rising and falling waves is operational. 64.- The method according to claim 63, further characterized in that the piston rods of one or more of the inner cylinders facing downwards are retracted in response to the descent of the floating vessel into the valley between the waves when the compensation system of the wave rise and fall movement is operational. The method according to claim 64, further characterized in that the piston rods of one or more of the inner cylinders facing upwards are retracted in response to the descent of the floating vessel to the valley between the waves when the compensation system of the wave rise and fall movement is operational. 66.- The method according to claim 60, further characterized in that it comprises additionally joining one or more low pressure accumulators to the outer surface of the outer housing. 67.- The method according to claim 61, further characterized in that one or more low pressure accumulators are attached to the outer surface of the outer housing by tube supports. 68.- The method according to claim 60, further characterized in that it further comprises housing one or more low pressure accumulators at least partially within the outer housing. 69. The method according to claim 60, further characterized in that it further comprises joining one or more of the low pressure accumulators to the outer surface of the outer housing and at least partially housing one or more low pressure accumulators within the housing Exterior. 70. - The method according to claim 60, further characterized in that it further comprises forming one or more of the high pressure accumulators outside the open space surrounding the inner cylinders within the outer housing. 71. The method according to claim 60, further characterized in that it further comprises providing one or more high pressure accumulators as external accumulators attached to the outer surface of the outer housing. The method according to claim 60, further characterized in that it further comprises providing one or more of the high pressure accumulators as an external accumulator attached to the outer surface of the outer housing and forming one or more of the high pressure accumulators outside the open space surrounding the inner cylinders within the outer housing.