METHOD AND APPARATUS FOR TENSIONING A RISER

Abstract: A tensioner system for a riser (24) of a subsea production well. A plurality of at least three tensioners (37,38) are each pivotally secured to both a lower surface of the production platform (19) and to a tensioner ring (44) that is itself secured to the riser. The tensioner ring may be generally octagonal with arms (60) protruding from alternate faces of the octagon. These arms define the connecting points for the tensioners. The tensioners (37,38) are angulated with respect to the axis of the riser (24), converging toward a single point lying on that axis and defining a first angle. The arms (60) preferably form a second angle with respect to the body of the tensioner ring (44) that is equal to said first angle so that the reaction surface defined by the bottom of the arms is perpendicular to the force lines along which the tensioners act.

Description: The present invention relates to a method and apparatus for connecting a well on the ocean floor with a wellhead "Christmas" tree, (i.e., the flow control valves) on a fixed or relatively fixed platform, such as a floating tension leg platform, or the like. More particularly, the present invention relates to a method and apparatus used in connecting a riser tensioner system between the riser and the relatively fixed platform being known for example from US-A-4 198 179. One aspect of the present invention involves connecting the riser tensioners to the riser in such a manner as to make it unnecessary to pair tensioners to avoid torsional loading of the riser in the event of failure of one of the tensioner cylinders. One of the benefits of a tension leg platform over other floating systems is the very small vertical oscillation that occurs. This enables the wellhead trees to be mounted within a few feet of a platform deck without the need for some complex form of motion compensation system. However, the use of a rigid riser system requires that a riser tensioner system be employed to compensate for the small amount of platform movement that does take place so that buckling or bending of the riser under its own weight will not result in a failure (cracking, breaking, etc.) of the riser. Heretofore, tensioner cylinders have typically been paired so as to disable the opposite cylinder when one tensioner cylinder failed and thereby avoid unbalanced loading that can torque the riser and produce the failure of the riser the tensioning system is trying to avoid. Further, a rigid riser requires a precise measurement of the distance between the well on the ocean floor and the deck of the platform in order to provide a riser of the proper length. As exploration moves into deeper and deeper water, such measurement becomes more and more difficult. From US-A-4 198 179 there is known a riser tensioner having the features of the precharacterising portion of claim 1. The present invention is characterised over the prior art in that the centralising means comprise rollers adapted to permit vertical motion of the riser relative to the platform; and in that each tensioner comprises a piston cylinder arrangement with a rod-mounted piston slidably mounted therein and has a lower end directly coupled to the tensioner ring via a lower universal joint and an upper end directly connected to the platform via an upper universal joint, said universal joints being arranged to permit some relative rotational movement between each tensioner and the platform deck and between each tensioner and the riser. The present invention provides the desired motion compensation and tensioning of the riser by angulating each of the plurality of tensioner cylinders to operate through a common point lying along the center line of the riser below the point of connection to the platform. The piston rod of each cylinder is connected to a tensioner ring that is in turn clamped to the riser. The tensioner ring preferably has a plurality of arms each of which receives a piston rod, extending from its body at an angle that is generally equivalent to the average angle (i.e., the midpoint extension of the piston rod) that the respective tensioner forms with the riser. In this manner, the tensioner ring arm provides a reaction surface that is generally perpendicular to the action line of force exerted on the riser which lies along the piston cylinder and piston rod. By this configuration, the cylinders need not be hydraulically paired in opposing couples. Failure of one cylinder will not result in any torsional forces that are perpendicular to the longitudinal axis of the riser being applied to it, as occurred with many prior art tensioners. Certain embodiments of the invention will now be described, by way of example only, and with reference to the accompanying drawings, wherein: Fig. 1 is a schematic elevational view of a tension leg platform secured in position with production risers connected thereto; Fig. 2 is a schematic side view of a first preferred embodiment of the riser tensioner attachment ring of the present invention showing its usage with an adjustable riser top joint; Fig. 3 is a schematic side view of a second type of the riser top joint with which the present invention may be used; Fig. 4 is a top view of the unitary tensioner ring used in the Fig. 2 embodiment; and Fig. 5 is a top view of one segment of the split segmented riser tensioner ring used with the type riser top joint shown in Fig. 3. A tension leg platform is shown in Fig. 1 generally at 10. While the riser tensioner of the preferred embodiment is peculiarly designed for use with a tension leg platform, it will be appreciated that such a tensioner might be utilized with other fixed and relatively fixed (i.e., floating systems with minimal vertical motion) platforms, as well. Platform 10 is secured to the ocean floor 11 by a plurality of tendons 12. A plurality of risers 14 extend between the individual wells in template 16 and a wellhead deck 18 of platform 10. As seen in Fig. 2, riser 14 extends through a hole 20 in deck 18 that permits some relative motion between the deck 18 and riser 14 that occurs as a result of wave action on the platform 10. The riser top joint of the preferred embodiment is depicted in Fig. 2 generally at 22. Lower end 24 is internally threaded to connect with standard riser joint in a conventional manner. Note, although a straight-walled thread is depicted, a tapered thread may be used if desired. The internal diameter of section 22 is to be the same as any other riser section in the particular string 14. The first outer diameter 26 will match that of the remainder of the riser. However, a second outer diameter is formed by a plurality of generally annular protrusions 28 that are generally equally spaced. In the embodiment shown in Fig. 2, generally cylindrical protrusions 28 are formed by a continuous helical groove 30 formed on the outer surface of riser top joint 22. In the alternate top joint embodiment depicted in Fig. 3, annular protrusions 28 are formed as cylindrical protrusions of a specified length and particular spacing rather than as a continuous helical groove. These design characteristics (length and spacing) will be selected in accordance with the particular needs of the application such as tensioner load parameters, accuracy of water depth measurement, etc. The surface of the riser may be scored as at 31 adjacent the bottom of each protrusion 28 for reasons to become apparent hereinafter. In both the Fig. 2 and the Fig. 3 top joint configurations, top joint 22 extends through hole 20 in such a manner that a first plurality of annular protrusions 28 extend above the top surface 19 of deck 18 while a second plurality extend below the bottom surface 17 of the deck 18. The first plurality of protrusions 28 serve as a plurality of connection points for well tree 32. Well tree 32 may be attached at any of the potential connection points by cutting off excess length of the riser guided initially by a thread groove or by the appropriate score line 31, installing either a unitary or a split segmented collar 34 at a position spaced from the top end of the riser top joint, attaching well tree 32 to the top end of joint 22 and positioning packoff 36 upon collar 34. With respect to the utilization of the embodiment employing helical groove 30, the top 4 to 8 turns of the groove will be machined off after the riser joint has been cut to length so packoff 36 will have a smooth surface to engage. The second plurality of protrusions 28 below the lower surface 17 of the deck 18 provide a series of connection points for a second unitary or split collar tensioner ring 40 which in turn, is a connector for a series of riser tensioners 38. While any type of riser tensioner may be used, riser tensioners 38 are preferably of the pneumatic-hydraulic variety described and claimed in U.S. Patent 4,379,657, which is hereby incorporated by reference. Note, however, the paired cylinder concept employed within said patent has been made unnecessary by angling the riser tensioners 38 and, hence the action lines for the load forces so that those lines pass through the center line of the riser eliminating torsional loading. Therefore, each cylinder 38 will have its own set of air and hydraulic accumulators (not shown) with the oil accumulator connected to the rod side of the piston and the air accumulator connected to the oil accumulator as described in said patent. The unitary designed collar tensioner ring 40 shown in Fig. 4 is preferably used with the Fig. 2 embodiment while the split segmented collar design of Fig. 5 is more appropriate with the Fig. 3 configuration. The configuration of the riser tensioners 38, collar 40 and deck 20 of the Fig. 3 embodiment are substantially identical to the Fig. 2 device and, accordingly have been shown schematically, depicting only the differences between the two embodiments. The unitary design tensioner ring 40 shown in Figs. 2 and 4 has a throughbore 42 of sufficient diameter to clear the outer diameter of spiral groove 30. As best seen in Fig. 4, ring tensioner 40 has a generally octagonal body with mounting arms 60 extending from alternate faces of the octagon. Each arm 60 has an opening 62 to receive the end of piston arm 37 and is provided with upper (64) and lower (66) reinforcing webs to strengthen ring 40. Each of these arms 60 is angulated somewhat with respect to the plane of the rest of the body (see Fig. 2) and preferably forms an angle equal to the average angle the riser tensioner 38 forms with center line of riser 14. In this manner, the plane of each arm 60 will form a reaction surface that is generally perpendicular to line of force acting along the center line of the tension cylinder 38 and rod 37. While this angle will be a function of design (length of tensioners, diameter of ring, point of cylinder attachment, etc.), these angles will generally fall in the range of from about 10° to about 25°. Since each of the plurality of tensioners 38 acts through a common point, should one cylinder fail, there is no tendency to torque or bend the riser as was the case with previous configurations. Hence, there is no need to pair the operation of opposed cylinders and each tensioner 38 will be independently provided with its own hydraulic and air reservoirs (not shown). While any number of tensioners 38 can be used, it is preferred that a minimum of three be used (in which event the body of the ring 40 would preferably be hexagonal) and, more preferably, a minimum of four. A conventional slip mechanism 44 comprised of camming ring 45, wedges 46 with internally arcuate, threaded surfaces 48 and a clamping plate 50, is bolted to tensioner ring 40 by a plurality (one shown) of securing bolts 52. Camming ring 45 forces wedges 46 into engagement with spiral groove 30 and clamping plate 50 holds the wedges 46 in engaged position. A lateral pin 54 can be utilized to prevent relative rotation between camming ring 45 and wedges 46 and, hence, between tensioner ring 40 and top joint 22. The split segment tensioner ring 40 of the Fig. 3 embodiment is shown in Fig. 5. The details of the configuration are similar with this alternate design being formed with two flanges 51 to permit the segments to be bolted together. As depicted schematically in Fig. 3, the inner diameter of opening 42 conforms generally to base diameter 26 to facilitate its connection to the stepwise variable riser top joint embodiment. Lateral stabilizing rollers 56 engage the external surface of collar 34 to keep the riser 14 centered within opening 20. In the Fig. 2 embodiment only a short portion 35 at each end of collar 34 is full thickness (i.e., has a minimum internal diameter) and is threaded to engage the spiral groove 30 of top joint 22. In the Fig. 3 embodiment, sections 35′ are full thickness to fill in the spaces between annular protrusions 28 and one section of split segment collar 34 is tapped as at 33 to receive connecting bolts (not shown) counter sunk in the other split segment. This provides a smooth external surface for stabilizing roller 56 to engage and facilitates their operation. The four riser tensioners 38 (two shown) are each interconnected to the platform deck 18 by a modified ball-and-socket joint 39 that permits some rotational movement between the tensioner 38 and deck 18 that will occur as the piston arm 37 of tensioner 38 extends and retracts to maintain a uniform tension on riser 14. A similar modified ball-and-socket connection 41 is used to connect the ends of piston arms 37 to tensioner ring 40 to permit the same rotational motion between tensioners 38 and tensioner ring 40. It will, of course, be appreciated that any number of riser tensioners 38 may be used. The riser tensioner system of the preferred embodiment provides a greatly simplified means of tensioning a production riser 14 without subjecting it to unbalanced forces that could lead to bending or breaking of the riser or production tubing contained within. The tensioner ring provides a plurality (three or more) of connecting points in arms 60 that is equal to the number of tensioner cylinders 38 to be used. The arms 60 preferably are each angled with respect to the plane of body portion of the ring 40 with the specified angle being equal to the angle formed between the tensioner and the riser so the reaction surfaces formed thereby will be generally perpendicular to the action lines of force for tensioners 38. In the event of failure of one of the system's tensioners, the system will continue to operate effectively and no extraordinary effort need be made to replace the inoperative tensioner. Rather, the defective part may be replaced when it becomes convenient (e.g., after a storm has passed). In addition, the adjustable riser top joint 22 of the preferred embodiment obviates the need for a precise measurement between the well 42 on the ocean floor and the upper surface 19 of deck 18. The top joint 22 may be merely be connected to the top of riser 14 to extend through hole 20 in deck 18 with pluralities of protrusions above and below deck 18 to provide attachment points. The top of the riser joint 22 may then be cut to length and the well tree 32 and riser tensioners 38 installed using unitary or split segmented collars 34 and 40 respectively. The Fig. 2 embodiment provides significant flexibility since thread 30 provides continuous adjustment capability. Riser tensioners 28, acting through tensioner ring 40, provide a continuous substantially uniform tension on riser 14 despite relative movement of platform deck 18. This eliminates the threat of buckling, crimping or otherwise damaging the riser 14. Both the continuously adjustable riser top joint of the Fig. 2 embodiment and the stepwise adjustable riser of Fig. 3 increase the tolerance in measuring the distance between the ocean floor and the intended position of the well tree thereby facilitating installation by providing a plurality of acceptable installation positions. In addition, each of the embodiments of the riser top joint provides a second plurality of acceptable connecting points for a riser tensioner ring, preferably of the the type disclosed herein.

Claims: A tensioner system for tensioning a riser (14) and for compensating for relative movement between said riser and a platform (10), said riser having a longitudinal axis, said apparatus comprising: a plurality of at least three riser tensioners (38) interconnected between said platform and said riser; said tensioners, in their median positions, acting along force lines which define a first angle with respect to said riser and which pass through a common point lying along the longitudinal axis of said riser; a tensioner ring (40) surrounding a portion of said riser and having a plurality of attachment points (41) for connecting said tensioners at a first radial distance from said riser, said plurality of attachment points being equal in number to said plurality of tensioners; means (44) for securing said tensioner ring to said riser; means (41) for pivotally attaching an end of each of said tensioners to one of said attachment points; means (39) for pivotally attaching a second end of each of said tensioners (38) to said platform at a point above said tensioner ring at a second radial distance greater than said first; and means (56) for maintaining said riser laterally centrally within an opening (20) in said platform; characterised in that said centralising means comprise rollers (56) adapted to permit vertical motion of the riser relative to the platform; and in that each said tensioner comprises a piston cylinder arrangement (38) with a rod-mounted piston (37) slidably mounted therein and has a lower end directly coupled to said tensioner ring via a lower universal joint (41) and an upper end directly connected to the platform via an upper universal joint (39), said universal joints being arranged to permit some relative rotational movement between each tensioner (38) and the platform deck and between each tensioner and the riser (14). The riser tensioner system of claim 1 wherein said plurality of said tensioners (38) comprises at least four piston cylinders (38). The riser tensioner system of claim 1 or 2 wherein said tensioner ring (40) comprises a body (40) lying in a first plane with arms (60) extending from faces of said body. The riser tensioner system as claimed in claims 2 and 3 wherein the body is octagonal and the arms (60) extend from alternate faces thereof. The riser tensioner system of claims 2, 3 or 4 wherein the arms (60) of said tensioner ring (40) define a second angle with respect to said first plane of said body. The riser tensioner system of claim 5 wherein said first and second angles are generally equal such that reaction surface defined by said arms (60) are substantially perpendicular to said force lines. The riser tensioner system of any preceding claim wherein said first angle falls in the range from about 10° to about 25°. The riser tensioner of claim 7 wherein said second angle falls in the range from about 10° to about 25°. The riser tensioner system of any preceding claim wherein said tensioner ring (40) has a throughbore (42) which has a diameter greater than a maximum diameter of said riser (14). The riser tensioner system of any of claims 1 to 8 wherein said tensioner ring (40) has a throughbore (42) that is slightly greater than a first diameter (26) of said riser (14) but less than a second larger diameter (28). The riser tensioner system of claim 10 wherein said tensioner ring (40) is formed of two identical halves with flanges (51) to enable the halves to be bolted together around said first diameter (26).

Inventors: DELGADO, JORGE H., MYERS, RODERICK J.
Applicants: CONOCO INC.
Application year: 1987
Main classification: E21B19
IPC codes: E21B19