. BACKGROUND OF THE INVENTION

Field of the Invention

This invention relates to ships and excavating systems and it more particularly relates to moored off¬ shore vessels, such as drilling and petroleum production vessels. It may equally well function as a shore based heavy duty bearing system, and as a swiveling system for stationary or dynamic loads.

Description of the Prior Art

Offshore vessels used in the drilling and production of petroleum, subsea mining or recovery are often best moored by a plurality of radially positioned anchors or heavy foundations set in the sea floor with mooring lines connected to the vessel. The mooring lines can be steel cables, chains, synthetic fiber ropes or a combination thereof.

Naturally, the vessel moored by this arrangement will turn in response to current, wave, and wind forces. One system allowing the vessel to weathervane employs a turret journaled in the forward part of the hull. This will allow the vessel to head into the environmental excitation vector. The mooring lines are secured to the turret, which remains stationary about a vertical axis during angular movements of the weathervaning vessel.

Priorly, the largest vessel with a turret mooring system had a deplacement of about 30,000 tons, although

larger units have been proposed. The earliest turret was journaled using metal rollers on a steel raceway. Even with roller bearings, it is believed that a power assist mechanism is needed to rotate the turret to allow chang- ing direction of the vessel. The reason for this situa¬ tion resides in the coefficient of friction of met¬ al-to-metal bearing under eccentric and dynamic load (e.g., estimated at u=0.2). Thus, on a vessel of even this modest size, the frictional forces and resulting torques resisting rotation in the turret can be of sig¬ nificant magnitude.

As the water depth increases wherein drilling and especially production and mining operations are desired, the size of the vessel should also increase so as to provide sufficient work room and support capability. The requirement for size naturally also increases with the magnitude of field under exploitation. In the case of a VLCC size vessel, it would measure more than 1,000 feet, and in order to take full advantage of the vessel size, a moonpool or turret diameter exceeding 70 feet is natural. A VLCC size vessel normally ranges from 200,000 to 350,000 tons displacement.

If a turret with roller bearings is to be used on a VLCC vessel, an equally distributed load in the 30,000,000 pounds range would have a frictional resis¬ tance to rotation of about 3,000 tons. It is obvious that anchor ropes cannot safely stand the resulting tortional resistance to turret rotation. Therefore, a power assisted turret rotation arrangement would have to be used to protect the anchor ropes and to protect the bearings from accelerated wear. Even if the bearing surfaces of the turret could be made from a low coeffi¬ cient of friction material such as Teflon, the frictional resistance to rotation would ideally exceed 100 tons, given service loading in the 10,000-15,000 ton range.

Unfortunately, the use of this bearing material would be very expensive at present day prices, and cannot

conceiveably be manufactured in the necessary size, while still retaining tolerances in the ideal range.

Another problem with a turret system for any vessel is in the flexing, especially longitudinally, of the bearing surfaces. For example, the vessel in sag and hog condition changes dimension longitudinally about its neutral axis of about 0.15%. Thus, the bearing housing secured to ^' the vessel varies in elliptical form as the vessel changes from compression to tension conditions alternately of the main deck and bottom. On a turret of the mentioned size (e.g., 70 feet), this elliptical form can be a 2.5 inch change"in major and minor diameters. There are no known steel roller bearing arrangements that can accoiπmodate this elliptical distortion condition and yet retain tolerable friction losses.

The present invention is a unique turret system with a low friction fluid bearing (like water) that can func¬ tion under severe conditions of elliptical distortion while allowing a vessel subject to weathervaning almost unrestricted freedom of rotation and at loads exceeding 30,000,000 pounds on the bearing surfaces. In addition, this new turret provides a compact mounting arrangement for various anchor and riser rope handling systems, including winches, storage and utility compartments, and top mounted skid beams for the support and transportation of extremely heavy machinery.

STATEMENT OF INVENTION

In accordance with this invention, there is provided an improved turret rotatable about a vertical axis within a support base (e.g., on a vessel) and operable under differential lateral and vertical loadings. The turret comprises a cylindrical spool carrying at least one radial bearing disk with a round vertical body rotatable about- a vertical axis. The base receives the spool within enclosing walls. A rigid liner mounts within the disk and an elastomeric barrier resides within the base

coextensively with the disk. Annular metal stopper members are fixed between the liner and disk for spacing same a minimum distance. The disk carries radial skirts for fluid throttling between the disk and liner, and the skirts extend between the stopper members so a s to define a plurality of annular segmented cups encircling the disk. A source (e.g., pressurized reservoir) intro¬ duces pressurized liquid into each segmented cup and against the liner for maintaining the spool on its verti- cal level, and symmetrical with its vertical rotational axis in the base.

In the embodiments of the improved turret, the pressurized liquid application may be computer controlled and becomes dynamically captive in a throttled chamber between the spool and base, and dynamic pressure seals. Also, the turret can be provided with annular compart¬ ments to house mooring and riser rope winches and storage in carousel arrangement, together with top mounted skids for support and transportation of heavy machinery.

DESCRIPTION OF THE DRAWINGS

Fig. 1 is a pictorial view illustrating an offshore

VLCC vessel carrying the improved turret for mooring same to radially placed mooring ropes and for controlling a multi-strand riser system extending to a sea floor wellhead template; Fig. 2 is an enlarged cross section taken across the vessel at the turret;

Fig. 3 is an enlarged partial plan taken of the vessel at the turret;

Fig. 4 is a linearized elevation of the turret taken from its center;

Fig. 5 is an enlarged cross section taken through the upper right portion of the turret along lines 5-5 of Fig. 2;

Fig. 6 is an enlarged cross section taken through the turret in Fig. 5 along lines 6-6;

Fig. 7 is an enlarged section taken along lines 7-7 in Fig. 5;

Fig. 8 is an enlarged section taken through the lower right portion of the turret along liens 8-8 in Fig. 2;

Fig. 9 is a hydraulic and control one line schematic showing a liquid pressure system for the improved turret;

Fig. 10 is a diagrammatic presentation of the bear¬ ings (upper/lower) used in the improved turret at one operative connection to pressurized liquid applied by computer control; and

Fig. 11 is a pictorial presentation of the upper portion of the turret at the mooring and riser winches wherein their respective ropes are supplied through spiral rope guides.

In the drawings, the several embodiments of the improved turret have common elements of construction. In regard to these several figures, like elements carry like numerals to simplify description of these improved turret embodiments.

DESCRIPTION OF PREFERRED EMBODIMENTS

Referring to the drawings, and particularly to Fig. 1, there is shown a VLCC vessel 15 carrying the improved turret 16 for mooring to a plurality of mooring ropes 17 connected by anchor chains 18 to anchors 19 set in the seafloor 21. The VLCC vessel 15 can have a length of over 1000 feet at the waterline WL with a displacement of more than 350,000 tons. In order to secure the vessel 15 in operative position above a wellhead template 22, a plurality of the ropes 17 are radially placed relative to the ship. For example, sixteen ropes 17 can be used and each rope can be of seven inch diameter (double braided polyester ^f rope) to withstand a breaking load of 1,250,000 pounds and a working load of 50,000-350,000 pounds. The length of each rope is related to the water depth above the seafloor 21. The usual length-to-depth ratio of each

rope varies with water depth. The mooring lines in a 1,500 foot water depth would typically consist of 800 chains and 3,200'/long ropes.

The mooring ropes 17 are passed over sheeves 24 upon their entrance into the turret 16 so as to reduce sharp corner shear injury to them.

It will be obvious that turret 16 must remain rota- tionally static about a vertical axis in the vessel 15 as the latter turns (weathervanes) in response to wind, wave and current forces. Since the ropes 17 cannot withstand any significant twisting below the turret 16, the vessel must turn freely against the frictional resistance of the bearing mounting about the turret 16. For example, this frictional resistance must be greatly less than obtained by steel-to-steel bearings.

The turret 16 may also carry the several riser ropes 23 that are employed with handling a multiple riser string 26 extending to the wellhead template 22. The riser string 26 can include plural production, control and tubing members that must be held in tension for safe operation. For this purpose, a buoyancy member 25 (e.g., 10,000 tons gross) can be secured onto the string 26 and stabilized by the riser ropes 23 which extend from the turret 16, through sheeves 20 on the member 25 and then secured to the anchor chain 18. The riser ropes 23 are held under sufficient tension to center the member 25 relative to the wellhead template 22. The riser ropes may be of same construction, as the anchor ropes.

Referring now to Fig. 2, the turret 16 is mounted within the moonpool 29 formed as a stepped cylindrical opening of varying diameter in the vessel 16. More particularly, the moonpool is defined by enclosing walls 31 which form a watertight enclosure within the hull of the vessel 16. These walls 31 extend between the vessel bottom 32, through the main deck 33 and terminate at top of upper turret bearing surface. The turret 16 extends as a tubular structure from the bottom 32, through a

circular opening in the main deck 33, and it can termi¬ nate at the top or housedeck 34.

The turret 16 resembles a cylindrical spool carrying at least one radial bearing disk. Preferably, it has a round tubular vertical body 36 with upper and lower radial bearing disks 37 and 38, respectively. These disks are frusto-conical surfaces formed by the exterior wall plates of the turret, and these wall plates 39 and 41 merge into the exterior cylindrical wall 42 providing the body 36. The interior cylindrical wall 43 defines the remainder of the turret about the moonpool 29. The sheeves 24 for handling the mooring ropes 17 can be mounted by a complete fairleader assembly on supports 44 at the lower part of the wall 43 on the turret 16. The disk 37 is formed in a stepped arrangement to reduce the vertical moment arms about bearing surfaces and to minimize the circular opening diameter required in the main deck 33. The disk has a first part 37A adjacent the wall 42 which radially connects with a cylindrical part 37B in traverse of the main deck and a third part 37C in its ultimate outward extension which terminates adjacent to the interior cylindrical wall 46 in the superstructure 47 below the house deck 34.

The upper turret is configured by bulkheads 48 into spaced annularly disposed compartments 51 and 52 respec- tively, above and below a circular deck 53. The compart¬ ments 51 can house winches 54 for handling the mooring ropes 17 while the compartments 52 can house on circular deck 57 the winches 56 for handling the riser ropes 23 or vice versa. Surrounding the compartments 51 are rope storage annulus 58 and utility annulus 59, which will be described in more detail hereafter.

As best seen in Fig. 4, the arrangement of the compartments 51 are angularly staggered or offset rela- tive to the compartments 52 ^' . As a result, the ropes 17 fall from the winches 54 in a spaced, side-by-side rela¬ tionship to the ropes 23 (shown by chain lines). Since the ropes 23 fall downwardly in small angles from the

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winches 56, a lower guide 61 can be used to control them rather than a sheeve. With this arrangement for the turret 17, the several compartments etc. are carried in unison as in a carousel encircled by vessel 15. As seen in Figs. 1, 2 and 3, the top of the turret at the house deck 34 is a circular work deck 62 that is arranged to handle the various deck machines and other equipment employed for drilling, production, mining or other subsea operations. The deck 62 has a recess mount- ing a circular skid beam 63, and also mounting parallel straight skid beams 64, which may be lined up upon turret rotation with beams 66 on the house deck 34. The -various equipment used on the vessel can be moved to and from the turret by sliding over these skid beams. For example, large capacity winches 67 can be mounted to the skid 63 for furnishing mooring lines. These winches can be supported by stanchions 68 which extend between the decks 53 and 62.

The unique bearing arrangement to journal the turret within the vessel can be seen best in Figs. 5-8. More particularly, the vessel carries a supporting base 69 to receive the turret. The base 69 is formed by connected walls 71, 72, 73, 74 and 76 that encircle the turret as the composite wall 31 and provide a water tight barrier about the moonpool 29 within the vessel. The wall 71 has an upturned lip 78 secured to a circular deck plate 79 carried on the wall 46. The walls 71-74 and 76-78 are spaced a small distance (e.g., 10 inches) from the walls of the turret. ^' In this space, a stiff or rigid metal liners 80 and 81 and elastic medium 82 are integrally carried on the walls 71-78, and form essentially the supporting base 69 of the turret. However, the liners could be made of one element. Annular semicylindrical metal supports or stoppers 83-88 are integrally carried on the liner 81. These stoppers cooperate wiπh the turret, especially the bearing disks 37 and 38 to (1) provide a certain minimum spacing (e.g. , 2 inches) be¬ tween the disks and liners, and (2) in combination within

the skirts to provide an automatic throttling function, thus maintaining a centering dynamic fluid overpressure positioning the turret 16 within the base 69 during rotation and consequently accommodating eccentric loads. In normal operation of the turret (as with symmetrical or no loads), the turret will be centered with an equidistant clearance between all stoppers and respective disks. The supporting medium will be pressurized liquid, preferably water, introduced into the space 91 existing between the turret 16 and the liner 81 on the supporting base 69. Even though the turret may be subject to great (e.g., 30,000,000 pound) symmetrical or asymmetrical loading, the pressure of the liquid will be nominal (e.g., 40 psig range) because of the large surface areas of disks 37. Annular seals 80 and 90 seal the top and bottom of the turret 16 to the liners 80 and 81 so that space 91 becomes a near liquid tight chamber to receive pressurized fluid.

For example, the turret 16 may have a nominal diame- ter of about 120 feet with the annular surface area of the disk 37 being the difference from the turret light opening of about 70 feet. The pressurized liquid acting in space 91 represents a negligible friction at low relative angular velocities between the vessel and the turret. The resulting friction is practically speaking reduced to that of the seals 80 and 90. With seals as described herein, the friction is held at approximately 10 tons when the bearing load is about 15,000 tons, and a low angular velocity may be assumed. No twisting of the ' mooring ropes 17 occurs as the turret 16 remains free in the base 69 as the vessel weathervanes under action of wind, waves or currents.

If for any reason metal-to-metal contact between disks and stoppers occurs, the elastic medium 82 will allow the liners 80 and 81 to adjust and absorb such force without noticeable additional or deforming load on the enclosing walls 71-78. Stated in a different manner, the elastic medium 82 (of polymeric material) as a

cushion allows the liners to float a few inches apart from the encircling walls so as to distribute the load under abnormal conditions, and until the pressurized liquid can restore the turret to its normal vertical axis and elevation in the vessel. Although intermittent slabs of synthetic rubber or other polymeric material is shown for the medium 82, it may be considered an equidistant clearance material between the stoppers 83-88 and the adjacent disks 37 and 38. The medium 82 may alternatively be formed by porous elastomeric polymers, or inflated spheres of suitable compressibility, suspended in a pressurized, incompressible liquid medium, such and water. This will constitute a liquid, elastic barrier with very quick response characteristics between the vessel 15 and liners.

The pressurized liquid is employed in a manner that the "down side" of the disk 37 can be restored without requiring excessive pressure in the space 91. For this purpose, and also as a dimensional tolerance means of adjustment, the disks 37 and 38 are provided with a plurality of angularly spaced, radially aligned resilient skirts 92 and 93, respectively. For example, each disk may carry eight equally spaced skirts. These skirts extend between a pair of adjacent stoppers so as to define a plurality of annular cups which encircle each of the disks. These skirts are preferably of a resilient material to accommodate variations in spacings between parts of the disk and the liner.

For example, the disk 37 at its upper part 37C carries skirts 92a-h between stoppers 84 and 85, at lower part 37A and skirts 92 i-o are carried between stoppers 86 and 87. The lower disk 38 carries skirts 93a-h be¬ tween the stoppers 88 and 89. It is important to note that the skirts provide a considerable throttle function to the liner 82 during eccentric movements of the turret. When the ^' turret approaches seating upon the stoppers, a relatively fluid tight perimeter is established for the segmented cups between such stoppers. Thus, these

stoppers cooperate with the skirts and disk in an . automatic valve which throttles the segmented cups on the downside displacement of the turret in the base. For example, the disk 37, at part 37C is segmented into the cups 94-100 by the stoppers 84 and 85 and skirts 92a-h. In similar arrangement, the disk 38 is segmented into cups 107-114 by ^' the stoppers 88 and 89 and the skirts 93a-h. Skirts 93a-h may alternatively be made from a suitable metal material. The throttling tolerances of the skirts may be insured by a positioning mechanism illustrated in Fig. 7. The skirt is held between sidewalls 102 and 105 which are part of an enclosing fluid chamber 103 also defined by end walls 104 and 106 in the disk 37. The skirt 92A is urged into engagement with the liner 81 by a follower 107 through a suitable mechanism such as a jack screw 108 threadedly mounted in cover plate 109 secured to disk 53. The skirts maintain the desired fluid seal as the turret rotates and swings within the base 69. The remaining skirts 92i-o and 93a-h may be provided with a similar positioning mechanism. However, the skirts may also be made from metal and actually welded in place. In that case the skirts are preferably fitted in the installation phase of the turret, such that the skirt installation also constitutes a final adjustment of system tolerances in a mechanical sense.

The liquid pressures in way of disk 37 create an upward force, a lift. Conversely the pressures in way of disk 38 creates a downward force on the turret. The differential force between disk 37 and 38 is the net balancing and vertically positioning force on the turret. The function of the lower disk 38 may be compared to that of a feed-back signal in a closed control loop, and the sensitivity of the system decreases with the horizontal projection of the disk 38. Conversely the lifting capac¬ ity at a given nominal pressure reduces with an increas¬ ing horizontal projection of disks 38. The actual

pressure in way of disk 38 equals original feeding pressure less dynamic losses, and plus static head differential.

If assuming an increasing downward load on the turret, it will tend to sink within the base. However, now the throttling of liquid flow in way of upper disk's 37 skirts, stoppers, and liner becomes more pronounced, the dynamic pressure losses increase, and the resulting pressures and downward force at the lower disk 38 re- duces.

Since a larger volume of liquids is needed in way of lower disk 38 cups, an underpressure zone will be estab¬ lished until the turret is stabilized. Thus, the effect in way of the lower disk 38 will-assist in enhancing the adjustment of the differential balancing force, and reduces movement of the turret. Thus, the geometric lay-out is largely self-adjusting to varying load. In the case of a lesser downward pointing load, the opposite effects will occur, and the last statement prevails. Assuming an eccentric downward load on top of the turret, it will naturally tend to drop on the side the eccentric load is applied. Thereby, an overpressure • arises in way of upper disk's 37 cups directly underneath such load, and a tendency to underpressure will occur on the upper disk 37 opposing side, all due to distance variations between the disc/skirts and liners. In the lower disks 38, for the same reason an underpressure zone will occur on the side of- the eccentric load, and ^' con¬ versely an overpressure on the opposite side. These emerging differential pressures will result in differen¬ tial forces acting on the moment arms Ml, M2 and M3. All arms are of substantial extention, and the resulting restoring moments will ascertain substantial stability against turret tilting in the base, even without any extra outside controlling measures. Significantly, 'the liquid passageways or space 91 through the turret are kept narrow compared to their length and liquid volumes. The integrating effect of this inherent dynamic throttle,

will eliminate the necessity of compensation from an outside service system as far as dynamic impacts of relative short duration. (The described service system involving a computer and gas pressurized liquid contain- ers for quick responses is nevertheless shown in a form that will service a system with needs for responsiveness greater than that of the turret configuration.)

The pressurized liquid is applied to each disk by the arrangement shown in Fig. 9. A plurality of sensors 116-123 and 116A-123A (e.g., sensors for measurement of vertical relative displacement) are placed, circumferen- tially about the turret on the walls 72 and 42. Pref¬ erably, there is an equal number of sensors to the number of segmented cup compartmentations in the disks. The sensors connect to signal devices "L" which provide an output signal proportional to the vertical spacing be¬ tween the opposing sensors. The signal (indicated by chain line 124) is received at a computer 127 which based on these signals computes an output signal to initiate desired controlling function in application of pres¬ surized liquid into the segmented cups.

The computer 127 has a plurality of outputs that are directed to motor control valves 128-135 associated with the disk 37, and motor control valves 136-143 associated with the disk 38. Each valve connects by an outlet into the individual disk cups between the disk and the liner 81. For example, the valve 128 connects by a manifold 144 to inlets 146 and 147, and the valve 136 connects to outlet 148. In the present arrangement, pressurized liquid is introduced by the valves 128-135 underneath the disk 37, conduits through space 91, and then exits by valves 136-143 on the overside of the disk 38.

The pressurized liquid is made available to valves 128-135 through circular manifold 149 and recovered from circular manifold via valves 136-143. The pressurized liquid is always held at a controlled and balancing head pressure in the system. For this purpose, the supply tank 152 is filled with compressed gas (e.g., air) by

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compressor 153 which is controlled by a pressure regula¬ tor 154. The outlet 156 from the tank 152 is applied to supply tanks 157 and 158 individually through motor control valves 159 and 161. These valves 159 and 161 are controlled by signals 162 and 163 from the computer 127, in response to feedback signals 164 and 166 from pressure sensors 167-168 versus calculated necessity. As a re¬ sult, there are zones 169 and 171 of pressurized gas within the tanks 157 and 158. The integrated mean rela- tive vertical position of sensors 116A-123A versus exist¬ ing pressures will be the main computer input for cal¬ culating necessary mean and differential fluid pressures in tanks 157 and 158. Make-up liquid from a suitable source 170 (e.g., vessel's fresh water supply or seawater) is introduced by a pump 172 into the system by tank 157 through a motor control valve 173 actuated by level controllers 174 and 176. Liquid from the tank 158 is transferred into the tank 157 by the circulation pump 177 through a motor control valve 178 in regulation by a signal 179 from the computer 127. This flow equals the total system flow less fluid losses.

The manifold 149 receives pressurized liquid by a line 181 from the tank 157. The manifold 151 delivers returning pressurized liquid by a line 182 into the tank 158. A dual flow sensor 183 monitors the lines 181 and 182 for normal operation, and abnormalities (e.g., large leaks) are signals 184. sent to computer 127 for increas¬ ing liquid supply by ^~ opening valve 173.

Referring to Fig. 10, a description of typical operation of the pressurized system will be given. The disks 37 and 38 are shown in schematic with the plurality of segmented cups formed by the skirts and annular stop¬ pers. The several inlets and their connection via the motor control valves are also illustrated, and the space 91 is shown in phantom as the fluid conduit from the disk 37 to the disk 38.

When the turret 16 is centered in the base 69, the sensors 116-123 provide equal signals to the computer 127

so that equal pressure is maintained in all cups by the motor control valves. This pressure balances the total load versus resulting lift in way of disks. For example, the pressurized liquid can be delivered to manifold 49 at 40 psig and is returned to manifold 136 at nearly the same pressure, less frictional induced drop, but plus the hydrostatic differential component.

If the turret is subject to an eccentric load, for example, it being displaced downward in way of sensor 116A, and upward in way of sensor 120A, the sensors 116 and 120 indicate the low and high sides of the disks relative to a programmed setpoint. The computer 127 by signals 186 and 187 increases the flow (and pressure) of the liquid entering the downside cups (e.g., cup 94). The resultant liquid pressure forces action on the disk 37 to restore the turret to its vertical axis and range, even while it is rotating. The same control system is applied to the cups 107-114 of the disk 38 using the respective motor control valves 136-143. In the above case, cup 107 is vented through opening valve 136, and an underpressure zone arises. Although the liquid differen¬ tial pressure magnitude is not great, the moment arms and the large surface areas of the disk provide a hydraulic force (in the liquid trapped within the cups) capable of handling very large eccentric loads on the turret. Another great advantage of this unique bearing arrangement to journal the turret is the ability to accommodate eccentric distortion of the parts, especially the base 69 and liners 80-and 81 positions. It will be apparent that the vessel 16 undergoes significant flexing in the form of sag, hog and tortional changes of its dimension, especially in the longitudinal axis of its hull. Assuming that the vessel construction is conven¬ tional, the hull undergoes about a 0.15% longitudinal distortion in tension and compression.

These elliptical distortions will primarily be ab¬ sorbed in the elastomeric barrier 82. However, should the liners be affected by these relatively slow acting

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distortions, the watermasses between the base 69 and turret 16 will also have the ability to shift without significant pressure disturbance in the way of the lift¬ ing areas underneath disk 37 and above disk 38. Fig. 6 shows a seal arrangement well adapted to the improved turret of this invention. This seal arrangement maintains fluid tightness during rotation of the turret, especially under eccentric loading or changes in shape of its parts. The disk 37 has an upright cylindrical wall 188 which extends to the circular top deck 53. A shoul¬ dered recess 189 is defined in the wall 188, and it is enclosed by an annular cover 191. An annular resilient sleeve 192 is seated in this recess 189 and secured in place by the cover 191. The sleeve 192 is provided with mounts, such as dovetail grooves 193 in which are re¬ ceived projections 194 which may be a flurocarbon (e.g., Teflon material) sealing ring 196. The exterior face of the ring 196 is provided with interleafed sealing sur¬ faces 197 which can be saw-toothed in cross sectional configuration.

The base 69 carries a complementary sealing ring 198 which has interleafed sealing surface 199 engaged by the surfaces 197 sufficiently to form a tortous path type seal between liquid and atmosphere or watermasses. This sealing pressure can be provided by any mechanism, but preferably it is pressure actuated. For this purpose, an annular resilient sleeve 201 mounts the ring 198 by receiving its projections 202 with dovetail recesses 203. The sieeve 201 has ah inverted u-shaped cross section providing a cylindrical chamber 204 open at one end to the pressurized liquid in space 91. The upper end 206 of the sleeve 201 is closed, and held by a ridge 207 within a groove 208 of a removeable circular cover 209. The exterior cylindrical side 211 of the sleeve 201 extends downwardly along the liner 81 to a tapered end 212 which is secured by a mounting ring 213 fixed to the liner 81.

With this seal arrangement for the seal 80, its parts can be easily removed and installed after the

covers 191 and 209 uncover the recess 189 and space 91. The pressurized liquid acts through chamber 204 to force the ring 202 radially inwardly and thereby provide auto¬ matic fluid sealing engagement between the rings 196 and 198. Since these rings may be of a material with a very low coefficient of friction, and since their surfaces will be water lubricated, they produce only a relatively very insignificant increase in torque required to rotate the turret 16 within the base 69. Also, the seal ar- rangement accommodates relative movement between the turret and base responsive to heavy eccentric loading or elliptical changes in base shape.

The improved turret 16 is provided with a guide arrangement for conventionally feeding the large diameter mooring and riser ropes to their respective traction winches. As seen in Fig. 11 (with reference also to Fig. 2), the storage compartment is provided with a plurality of mooring and riser rope guides 216 and 217 for each set of rope winches. These guides are spiral and at their inner ends feed rope directly to the drums on the winches. The guides outer ends extend above the utility compartments and traverse the cover 62. Rope tensioning machines 218 and 219 can be mounted on the housing deck 34 for proper rope handling procedures. Usually, coiled supplies of rope are carried above deck, although in some vessels, a below deck storage arrangement could also be used to advantage. Although only one pair of mooring and riser rope guides arrangement are shown in Fig. 11, it will- be apparent that there are as many pairs of guides as their are mooring and riser ropes used in the turret 16. In the present embodiment, there would be sixteen sets of mooring and riser rope guides, totaling 32, on the turret 16. The several cables concerning the utility compartments can be suitably arranged. As a result, the turret 16 can rotate about its vertical axis and yet the mooring and riser ropes will be continuously supplied to their respectful winches. The winches can be of any type such as selected from the winching types of cathead

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winches for chains, and drum and liner winches for syn¬ thetic and/or steel rope.

Many parts of the vessel 16 have been shown schemat¬ ically, and it is understood that their position and construction follow conventional shop building prin¬ ciples. Details of construction have been shown only where necessary to a description of the present improved -turret.

From the foregoing, there has been provided an improved turret for mooring a vessel and the vessel can weathervane about the turret to which is secured the several mooring and riser ropes, and the riser string or other subsea mechanism. It will be apparent that certain changes and alterations in this turret arrangement can be made without departing from the spirit of this invention. These changes are contemplated by and are within the scope of the appended claims which define the invention. Additionally, the present description is intended to be taken as an illustration of this invention.