KR101533392B1 - Vessels with roll damping mechanism - Google Patents

Vessels with roll damping mechanism Download PDF

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Publication number
KR101533392B1
KR101533392B1 KR1020107008240A KR20107008240A KR101533392B1 KR 101533392 B1 KR101533392 B1 KR 101533392B1 KR 1020107008240 A KR1020107008240 A KR 1020107008240A KR 20107008240 A KR20107008240 A KR 20107008240A KR 101533392 B1 KR101533392 B1 KR 101533392B1
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KR
South Korea
Prior art keywords
jib
ballast
hull
roll damping
ship
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Application number
KR1020107008240A
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Korean (ko)
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KR20100071070A (en
Inventor
알렉셀 베렌즈닛스키
페르디난드 반 헤르드
주프 루덴버그
Original Assignee
아이티알이씨 비. 브이.
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Priority to US96073607P priority Critical
Priority to US60/960,736 priority
Application filed by 아이티알이씨 비. 브이. filed Critical 아이티알이씨 비. 브이.
Priority to PCT/NL2008/000221 priority patent/WO2009048322A1/en
Publication of KR20100071070A publication Critical patent/KR20100071070A/en
Application granted granted Critical
Publication of KR101533392B1 publication Critical patent/KR101533392B1/en

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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B63SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63BSHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B39/00Equipment to decrease pitch, roll, or like unwanted vessel movements; Apparatus for indicating vessel attitude
    • B63B39/02Equipment to decrease pitch, roll, or like unwanted vessel movements; Apparatus for indicating vessel attitude to decrease vessel movements by displacement of masses
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B63SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63BSHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B27/00Arrangement of ship-based loading or unloading equipment for cargo or passengers
    • B63B27/10Arrangement of ship-based loading or unloading equipment for cargo or passengers of cranes
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B63SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63BSHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B35/00Vessels or similar floating structures specially adapted for specific purposes and not otherwise provided for
    • B63B35/44Floating buildings, stores, drilling platforms, or workshops, e.g. carrying water-oil separating devices
    • B63B35/4413Floating drilling platforms, e.g. carrying water-oil separating devices
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B63SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63BSHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B39/00Equipment to decrease pitch, roll, or like unwanted vessel movements; Apparatus for indicating vessel attitude
    • B63B39/02Equipment to decrease pitch, roll, or like unwanted vessel movements; Apparatus for indicating vessel attitude to decrease vessel movements by displacement of masses
    • B63B39/03Equipment to decrease pitch, roll, or like unwanted vessel movements; Apparatus for indicating vessel attitude to decrease vessel movements by displacement of masses by transferring liquids
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66CCRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • B66C23/52Floating cranes
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66CCRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • B66C23/52Floating cranes
    • B66C23/53Floating cranes including counterweight or means to compensate for list, trim, or skew of the vessel or platform
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66CCRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62Constructional features or details
    • B66C23/64Jibs
    • B66C23/66Outer or upper end constructions
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66CCRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62Constructional features or details
    • B66C23/84Slewing gear
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B63SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63HMARINE PROPULSION OR STEERING
    • B63H25/00Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
    • B63H25/42Steering or dynamic anchoring by propulsive elements; Steering or dynamic anchoring by propellers used therefor only; Steering or dynamic anchoring by rudders carrying propellers

Abstract

The present invention relates to a single-vessel ship having a heavy-duty lift crane. The crane (20) includes a jib (24) that can reach beyond the hull of the ship and hoisting means for hoisting the cargo. The vessel has a water ballast system and also includes an active roll damping mechanism. According to the invention, the active roll damping mechanism comprises a solid roll damping ballast (110) movable in the lateral direction of the hull, a sensor for sensing the rolling motion of the hull, and a sensor And a drive and control system 115 that is operative to cause and control the movement of the solid roll damping ballast in response to the control signal.

Description

[0001] VESSELS WITH ROLL DAMPING MECHANISM [0002]

The present invention relates to a single-hull heavy-lift crane vessel and a single-hull coastal drilling vessel.

A heavy lift crane of the type referred to in the preamble of claim 1 has been made commercially available by the applicant for decades ago and is particularly suitable for use in cargo ships and tender ships used in coastal industries, It was installed and used on the same vessel and other vessels. Such monohull vessels with heavy lift cranes are suitable for construction and maintenance of coastal surface and subsea oil and natural gas source development facilities. A heavy lift mast crane with a lift capacity of 3000 tons was dried by the Applicant under the name Heavy Lift and Pipelay vessel, Sapura 3000.

In general, heavy lift crane vessels are equipped with a water ballast system to compensate for the static heel caused by the weight of the jib, so that during the lifting operation, Allow the cargo to hang when done. Usually such a water ballast system includes water ballast tanks and associated pumps in the hull of the ship. Generally, the capacity of the pump limits the ballast movement and substantially limits the speed of the jib of the crane.

A further known method of stabilizing a crane vessel by means of an active roll damping mechanism is known. Such a mechanism actively suppresses rolling motion. The rolling motion is a moment of rotation about the longitudinal axis of the ship, which is generated by a wave-excited moment which periodically confronts the moment of the ship. Due to the cargo hanging from the heavy lift crane in the crane vessel, a large roll moment may cause a large roll excursion.

An example of an active roll damping mechanism for the use of Voith Schneider Propellor is disclosed in U.S. Patent Publication No. 2007/0123120. A disadvantage of such an active roll damping device is the capacity limitation of vessels with heavy lift cranes, especially for vessels with heavy lift cranes having lift capacities of 1500 tons or more.

It is an object of the present invention to provide a single-hull vessel with a heavy-duty lift crane and a vessel with an improved active roll damping mechanism.

It is an object of the present invention to provide a solid roll damping ballast capable of moving in the lateral direction of the hull, a sensor for sensing the rolling motion of the hull, A heavy lift crane vessel is provided having an active roll damping mechanism including a drive and control system operated to cause and control the movement of the solid roll damping ballast.

Thus, active roll stabilization is achieved by causing a counteracting moment by actively controlled solid ballast means. The sensor senses the rolling motion, and the drive and control system controls the reaction moment as desired.

The machine can be used in a dynamic mode in which the transverse motion of the solid ballasts is adapted to correspond to a sea wave caused by the rolling motion of the vessel, Static or semi-static which is used to correspond to a heel induced by the ballast in the jib or the (light) cargo suspended from the crane (for example during slewing) Mode.

The vessel equipped with a heavy lift crane can be operated at a high rotational speed of the jib according to the active roll damping mechanism. Obviously, the "slower" water ballast may be used simultaneously to correspond to the heel of the vessel while the jib is rotating (e.g., hanging a light cargo).

The present invention also relates to a single-shaft coastal drilling vessel used in the coastal oil and natural gas drilling industry. The ship according to the present invention comprises an active roll damping mechanism, wherein the active roll damping mechanism comprises a solid roll damping ballast movable in the transverse direction of the hull, a sensor sensing the rolling motion of the hull, And a drive and control system operative to cause and control movement of the solid roll damping ballast in response to sensing of the sensor to provide roll stability.

The single-hull coastal drilling vessel of the present invention may also have one or more of the features described herein in connection with a single-hull heavy-duty crane vessel, and vice versa.

Charles De Gaulle, a French nuclear aircraft carrier, has a computerized and integrated stabilization system, which is designed to operate horizontally in the range of 0.5 degrees to operate the aircraft, even if the sea state is 5/6. It is designed to maintain stability within Like the two pairs of active stabilizing fins and a pair of rudders in the aircraft carrier, the system consists of two sets of two rail tracks for trains carrying 22 tonnes of weight Lt; RTI ID = 0.0 > computer-controlled < / RTI > compensation unit. These tracks lie transversely under the flight deck. These systems are designed to control roll, yaw and surge and compensate for wind and heel. Further progress of such an aircraft carrier stabilization system is disclosed in U.S. Patent No. 6,349,660. Further advancement of such a system for small vessels comprising a ballast body train mounted on U-shaped tracks is disclosed in European Patent Publication No. 1304289.

The heavy lift crane vessel according to the present invention preferably comprises a mast crane having a maximum hoisting capacity of at least 3000 tonnes, more preferably a mast crane with a hoisting capacity of 5000 tonnes or more.

The height of the mast of the crane preferably exceeds 75 meters, and the length of the jib may exceed 75 meters.

The radius of the hoisting cable is guided by the hoisting cable guide at the outer end of the jib and can be referenced according to the whip hoist and can be 122 meters.

The single-vessel ship with a mast crane in accordance with the invention is preferably suitable for handling large submarine modules, for example from 3000 meters deep to 600 tons.

In a preferred embodiment of the present invention, the crane is installed at the stern of the ship.

Preferably, the heavy lift crane vessel is provided with or equipped with S-type pipelaying equipment.

In a preferred embodiment, the vessel according to the invention also comprises dynamic position control means and is preferably operable with the active roll damping mechanism during hoisting or drilling operations.

The active roll damping mechanism according to the invention comprises a solid roll damping ballast movable in the lateral direction of the hull.

In the heavy lift crane vessel, the total mass of the roll damping ballast is preferably between 500 and 2500 tons, more preferably between 1000 and 2000 tons, for example between 1000 and 1500 tons.

In the drilling vessel, the total mass of the roll damping ballast is preferably between 100 and 750 tons, more preferably between 200 and 400 tons, for example 300 tons.

Preferably, the present roll dampening mechanism is configured such that, unlike a known aircraft carrier system having trains of ballast bodies mounted on a pair of tracks, a single ballast body is mounted and guided along a set of associated tracks . This makes it possible to avoid any problems associated with the internal connection of the ballast bodies within the trains of the ballast bodies. In addition, this allows the center of gravity of the ballast body to be shifted as much as possible outward relative to the centerline of the ship, thereby obtaining an increased restoring moment.

Preferably, the ballast body is embodied as a set of metal blocks or a unitary metal block secured to one another to form a single solid body having a weight of at least 100 tons, such that it is a compact ballast body.

Preferably, the ballast body has a height with a greater value in its transverse direction so that the center of gravity of the ballast body can be moved as far as possible outward relative to the centerline of the vessel, .

The wave-excited moment against the crane vessel generally has a waveform with a period of 5-25 seconds. In order to move large solid roll damping ballasts at such high frequencies, a drive system with a very large output capacity of several megawatts (MW) is needed. The preferred embodiment has an output capacity greater than 2.5 megawatts, such as 3 or 4 megawatts.

When properly adjusted, the roll damping ballast mechanism is designed so that the static heel of a crane vessel with a high-weight lift mast crane of 5000 tons is less than 3 degrees below 9 degrees with respect to horizontally extending jibs transverse to the vessel Of the total.

Just as there has been great progress in feasibility in the coastal state, the active roll damping mechanism provides a significant advance in the performance of the crane-ship for light cargo operations.

The roll damping mechanism can compensate for static heel caused by the slew motion of the crane hoisting the light cargo. The reaction time of the system is preferably faster than the slew speed of the crane, wherein the speed of the crane operation is not limited by the new anti-heel system.

The principle of the machine is to generate a restoring moment. When rotating the crane with light cargo, this restoring moment will compensate for the heel moment caused by the weight of the jib of the crane. In roll motion, the restoring moment will compensate for the roll moment caused by the wave.

The active roll damping mechanism on the single-hull drilling vessel may be used to determine the feasibility of the off-shore environment and weather conditions in the coastal state, for example, where the need to use more expensive semi-submersible drilling vessels is avoided .

Embodiments with additional advantages are described in the dependent claims and in the following description with reference to the drawings below.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic illustration of a coastal ship with a heavy lift mast crane suitable for pipeline piping to the seabed;
Fig. 2 is a partially elevational view of the hoisting crane at the rear portion of the ship shown in Fig. 1,
Figure 3 shows a hoisting crane according to Figure 2 in another direction,
Figure 4 is a top view of the hoisting crane shown in Figures 2 and 3,
5 is a cross-sectional view of the hull of the ship according to Fig. 1,
6 is a view showing a single-shaft coastal drilling vessel,
Fig. 7 is a cross-sectional view taken along line VII-VII in Fig. 8,
Fig. 8 is a plan view showing a portion of the ship according to Fig. 6,
Fig. 9 is a plan view showing a portion according to Fig. 8 at a lower deck height, Fig.
Fig. 10 is a longitudinal sectional view of the ship according to Fig. 6; Fig.

Figure 1 shows a coastal heavy lift crane vessel suitable for pipeline pipeline to the seabed.

The ship 1 is provided with a single deck 3 having a working deck 3 in front of the hull 2 and an upper structure 4 for a cabin room of the crew.

The vessel 1 is provided with a water ballast system including, for example, a half-roll tank 12. A water ballast system is known in the art such as an open-bottom tank system that reduces roll by modifying the roll resonance period.

In this embodiment, the vessel 1 comprises a length of 180 meters and a beam of 46 meters.

In this embodiment, the vessel 1 is provided with an S (not shown) having one or more welding stations on the working deck 3, with respect to the coupling pipeline section 9a in a substantially horizontal direction. -Type pipeline-pipeline-laying equipment. There are also known on the working deck 3 what is known as a tensioner 8 for carrying the weight of the pipeline 9 hanging down from the ship 1. The vessel may be equipped with another type of pipeline-piping equipment, for example a (not bendable) reel laying apparatus.

The ship 1 also includes a stinger 5 which projects the hull 2 of the ship 1 from the rear portion of the ship 1 and projects the hull 2 to the hull 2, Which can rotate about a substantially horizontal pivot structure 6, and form a lower curved support for the pipeline moving towards the underside.

In this embodiment, the ship includes a heavy-weight lift crane 20, which is disposed near the same side of the hull as the stator 5, that is, at the stern of the hull 2 , And a hoisting crane (20) includes a vertical structure fixed to the hull (2). The hoisting crane 20 will be described in more detail below. Here, the crane 20 is disposed above the position where the pipeline 9 leaves the working deck 3 on the longitudinal axis of the vessel 1.

The hoisting crane 20 shown in detail in Figures 2 to 4 comprises a substantially hollow vertical column 21 with a lower portion 22 fixed to the hull 2 of the vessel 1. In addition, the column 21 includes an upper portion 23.

The hoisting crane 20 includes a jib 24, shown in two different positions in Fig. The annular bearing structure 25 extends around the vertical post 21 and guides and carries the jib connection member 26 so that the jib connection member 26 and the jib 24 are positioned around the post 21 It can rotate.

In this case, the jib connection member 26 forms a substantially horizontal rotation axis, so that the jib 24 can also rotate up and down. And at least one drive motor (27) for replacing the jib connection member (26) along the annular bearing structure (25). The annular bearing structure 25 extends over the periphery of the post 21 and over the support of the annular element 28 of the jib connection member 26 through a running wheel And one or more guide lines. A jib safety support 29 is disposed in the element 28 at two locations. For example, the drive motor 27 can drive a pinion that engages with a toothed line around the column 21.

And a topping winch 30 having a topping cable 31 that engages the jib 24 to rotate the jib 24 up and down.

The hoisting cranes 20 are also connected to a hoisting cable 36 and a hoisting hook 37 to include a hoisting winch 35 for lifting or lowering the cargo.

An upper cable guide 40 having a cable pulley assembly 41 for the topping cable 31 and a cable pulley assembly for the hoisting cable 36 is mounted on the upper portion 23 of the column 21. [ ).

One or more cable pulley assemblies 43 for the hoisting cable 36 and cable pulley assemblies 44 for the topping cable 31 are disposed on the jib 24. The number of cable portions for each cable can be chosen by one of ordinary skill in the art.

In this case the winches 30 and 35 are arranged in the lower part 22 of the vertical pillar 21 so that the topping cable 31 and the hoisting cable 36 are connected to the winches 30 and 35 44 extend upwardly through the hollow vertical post 21 to the upper cable guide 40 and onto the cable guides 43, 44 on the jib 24.

The upper cable guide 40 includes a rotatable bearing structure of the structure in which the cable pulley assemblies are mounted, and the rotary bearing structure includes, for example, one or more cloud lines around the top of the column 21, It has a rolling wheel that engages the tracks. As a result, the upper cable guide 40 may follow the rotational movement of the jib relative to the vertical post 21 and may have substantially the same angular position as the jib 24.

The upper cable guide 40 includes an associated drive motor assembly to allow the upper cable guide 40 to follow the rotational motion of the jib 24 relative to the post 21, An example is preferred.

The jib winch 31 and the hoisting winch 35 are disposed on a rotatable winch support 50 rotatable about a rotational axis substantially parallel to the vertical post 21. The movable winch support (50) is movably mounted to the vertical post (21). The winch support 50 is located in the vertical crane structure and is preferably located in the lower region 22 below the circular cross section of the column 21 and mechanically separated from the upper cable guide 40 have. The support 50 may, for example, be disposed in the hull of the vessel below the column, and the lower portion may have an extension extending into the hull.

In the above-described embodiment, the winch support 50 is a substantially circular platform mounted in the annular bearing 51 in this environment, and the annular bearing has winches 31, 35 disposed on the platform. In this case, the annular bearing 51 allows the platform to rotate about a vertical axis that is consistent with the rotation axis of the upper cable guide. The bearing may be suitably designed to include a cart operating along a circular track.

The rotatable winch support 50 includes an associated drive motor assembly 52 that causes the winch support 50 to move so that the winch support 50 is movable relative to the vertical post 21, And maintains a substantially constant direction with respect to the jib 24 in the case of rotational movement of the jig 24. Also, since the movement of the winch support is again the result of the rotational movement of the jib 24, the orientation of the winch support 50 relative to the upper table guide 40 is maintained substantially constant.

There is an angle sensor 60 for sensing the position of the element 28 of the jib connection member 26 with respect to the vertical post 21 and the drive of the winch support 50 The motor assembly (52) includes an associated control means (53) in operative contact with the angle sensor (60).

Each of the winches 31, 35 includes an associated electric (or hydro-hydraulic) winch drive motor assembly 38, 39 disposed on the movable winch support 50. The required electrical energy is supplied by a generator located elsewhere on the ship at a distance from the movable winch support 50. One or more sliding contacts (not shown) are provided in electrical connection between these generators and the winch drive motor assemblies 38, 39.

In the various ones not shown above, the winch support 50 is rotatable with respect to a vertical shaft, which shaft has one or more sliding contacts. In such an embodiment, the deep-water cable extends through the center of such a shaft.

Preferably, via one or more slip contacts, a power current supply is made to the electrical equipment on the winch support (50).

The hoisting cranes 20 are provided with a cap 70 for the person operating the hoisting cranes in such a way that the cap 70 can be moved to the position where the jib 24 is secured, (Not shown), so that the cap 70 can rotate with the jib relative to the vertical post 21.

The cap 70 has at least a control member (not shown) for operating the winch 35 of the hoisting cable 36 and for operating the winch 31 of the topping cable 31. The winch drive motor assemblies 38, 39 include associated control means (not shown) for wireless communication with associated control members in the cap 70. For example, a plurality of wireless transmit / receive units are disposed around or in the vicinity of the vertical column, in the path of the cap 70 around the vertical column.

The control means, e. G. Electrical control equipment, for one or more winches on the winch support 50 is preferably also located on this winch support 50.

From the figures, preferably the vertical post 21 has a substantially continuous outer wall. In this case, the horizontal cross section through the vertical column is substantially circular from the jib connection member to the upper portion 23, and the cross section gradually decreases toward the upper portion of the column. The lower portion 22 of the column 21 is substantially rectangular so that the lower portion 22 is easily welded or welded to the longitudinal and crossing bulkhead in the hull 2 of the vessel 1 Bolted) by means of bolts. In various forms not shown, the vertical column may be in the form of a frame partially or wholly of bar.

The load-bearing connection structure 80 for securing the stinger to the desired position in FIG. 1 is connected to the hoisting crane 20 (see FIG. 1) at a location on the ship hull 2 at the point 6 where it engages the stinger 5 (In the case of the vicinity of the annular bearing structure for the jib 24) of the ship hull 2 and a point 6 which is engaged with the stinger 5 on the ship hull 2, (5).

The vessel 1 can be used to pipe the pipeline 9 and can also be used for hoisting operations, such as hoisting operations performed in the coastal industry, for example, installing platforms, underwater installations.

5 shows a cross-sectional view of the ship 1. As shown in Fig. Below the main deck 100 on the hull of the ship, preferably between the decks 120 as shown here, the vessel includes a room 101 (the room where the roll damping mechanism is located) do. Wherein such a machine includes a plurality of solid ballast bodies 110 that can be alternately transferred in the transverse direction of the hull.

The lateral distance for movement of the solid ballast bodies 110 is at least 10 meters to both sides of the centerline of the vessel, more preferably at least 15 meters. The entire beam of the ship, except for the outer shell of the ship hull, is more preferably made to be able to move the solid ballast bodies 110.

Preferably, the ballast body 110 is a solid metal block or a plurality of solid metal blocks or plates. Optionally, the ballast body comprises, for example, one strand of cable or chain for underwater operation. In an alternative embodiment, the ballast body comprises equipment or reservoirs (such as replacement parts) associated with the ship.

Wherein each ballast body 110 has rollers 111 and the vessel includes one or more straight lines extending transversely with respect to the vessel and including opposite ends about the sides of the hull. Obviously, different guide and bearing arrangements than one or more lines and rollers on the ballast body can be foreseen.

In this embodiment, the drive arrangement for each of the ballast bodies 110 comprises a cable arrangement with two winches 115 and cables 116, 117, . The winch 115 is preferably a winch with a drum including a double helical groove for the cables. For example, each of the winches has a capacity of 400 KW. Preferably, multiple ballast bodies and associated drive devices, for example, four or five such ballast bodies, are located side by side within the room.

Wherein each said ballast body has an oil damper (oleo damper) with a damper on the opposite lateral side, preferably a stroke of at least 0.25 meters.

The hull also has water ballast tanks 125 and roll dampening water tanks 128.

In addition, the drive arrangement for the at least one ballast bodies includes a control system capable of triggering and controlling the movement of the solid roll damping ballast bodies in order to provide roll stability in response to the sensing of the sensor.

The roll damping mechanism may be employed in a semi-static manner, wherein the one or more ballast bodies are substantially static or damped by the cargo on the ship when there is or is no cargo suspended from the crane For example, to block the heel that is caused by rotating the jib of the crane, to inhibit the slowly changing heel. The heavy lift crane rotates the jib to the lateral position of the vessel to generate a large heel so that the weight can be compensated for (partially or wholly) by a suitable semi-static operation of the roll damping mechanism Lt; RTI ID = 0.0 > jib. ≪ / RTI >

One embodiment of a single-shaft coastal drilling vessel having a roll damping mechanism according to the present invention will be described with reference to Figs. 6 to 10. Fig. The roll damping mechanism has the same basic design as the roll damping mechanism described with reference to the heavy lift crane vessel, and characteristics relating thereto, for example, preferred characteristics, can be included in the embodiment for the drilling vessel.

The general drilling vessel 200 is used for coastal drilling operations such as oil and natural gas exploration, well servicing and / or other drilling related operations (for example, maintenance and / or placement of subsea equipment) .

The hull 202 includes a crew room and a bridge 203 on the bow side, which includes a helicopter platform.

The vessel includes, for example, a water ballast system including a semi-roll tank 207, preferably the water ballast system is arranged to take roll motion suppression into account.

Preferably, the hull 202 of the vessel 200 comprises a single hull 205 and is preferably centered on the longitudinal axis of the vessel.

In this embodiment, multiple firing line hoist systems 210 are mounted on the hull 202 substantially on top of the single hull 205 so that preferably the single hull 205 The front half and the rear half are accessible to front and rear sides of the system 210. It will be appreciated that a single firing line hoist system may be an alternative form of the vessel.

In a preferred embodiment, the multiple firing line hoist system 210 comprises:

- a base and an upper side connected to the hull of the drilling ship, such as a transverse girder, wherein the first side 212 (the rear side in this embodiment) and the opposite second side 213 (in this embodiment, A mast 211 having a hollow structure including the front portion,

- a first hoist comprising a cargo attachment means (214) supported by the mast and displaced along a first firing line (214a) extending outside and adjacent to the first side (212) of the mast Sting devices,

- a second hoisting device supported by the mast and comprising cargo attaching means (215) displaced along a second firing line (215a) outside and adjacent to the second side (213) of the mast .

Each of the first and second hoisting devices includes one or more associated winches and one or more cables for manipulating the position of each of the cargo attachments with respect to the mast. Preferably, the winches are located within the mast 211, most preferably at the base of the mast, but may also be located elsewhere.

Details of the mast 211 and the hoisting devices can be derived from U.S. Patent No. 6,763,898 incorporated herein by reference.

BOP reservoir is present, preferably within the hull of the ship adjacent to the single hull 205.

Wherein the first hoisting device can be employed to pull up and down the BOP with the seabed. The vessel includes a riser storage although not shown in the figure.

One or more working decks are preferably present near the mast, for example in front of and behind the mast, to cover a portion of the single-stranded body 205. The working deck can be moved and / or can comprise movable deck parts.

In the present embodiment, the ship 200 is provided with a rotary drilling drive device, referred to as an upper drive device 216, on the front portion of the mast to allow drilling through the forward firing line 215a. It is self-evident that the rotary drilling drive can be (optionally) located behind the mast. Similar to the riser reservoir and the manipulation system may be disposed in the front portion of the mast.

Fig. 7 generally shows a cross section of the ship 1 corresponding to the tail wing of the single-stranded body 205. Fig. Within the hull of the vessel, below the main deck, the vessel comprises a chamber (250) in which the roll dampening mechanism is located. The machine here includes two solid ballast bodies 260 arranged side by side and can be moved laterally of the hull.

As shown, the lateral distance to the movement of the solid ballast bodies 260 is at least 5 meters, more preferably at least 7.5 meters, to both sides of the centerline of the vessel, and in this embodiment 9 meters do. FIGS. 7 and 8 illustrate the positions of the bodies 260 and the positive ends of the bodies 260 'and 260' '.

Preferably, the ballast body 260 is a solid metal block or a plurality of solid metal blocks or plates. In this embodiment, the weight of each ballast body is between 100 and 200 tons, for example 150 tons.

Wherein each ballast body 260 has lower rollers 261 that roll on a line 262 associated with the vessel and the lines are straight and have opposite ends on opposite sides of the chamber 250 in the vessel lt; / RTI > Preferably, one or more lines are also installed on the path of the ballast body, and the ballast body has upper rollers rolling on the upper lines 263. These lines are shown in FIG.

In this embodiment, the drive for each of the ballast bodies 260 includes a cable arrangement and winch 270 with cables 271, 272 that can move the ballast body in both directions. Preferably, the winch 270 is disposed at a height of the bottom of the associated path of the ballast body, as shown in FIG. The winch may include a drum having a double spiral groove for the cables. For example, each winch can have a capacity of hundreds of kilowatts.

The drive for one or more ballast bodies 260 also includes a winch < RTI ID = 0.0 > (e. G., ≪ / RTI > actuated to < RTI ID = 0.0 > cause and control movement of positions relative to the solid roll damping ballast bodies in response to sensing of one or more suitable sensors to provide roll stability Control system.

The sensor for sensing the roll motion may be any sensor or sensor system including, for example, one or more sensors and associated computers, and associated controls for appropriately controlling the operation of the drive means for the solid roll damping ballast bodies Provide information. For example, it may be an angle sensing sensor comprising one or more rotational motion sensors providing the angle information of the vessel, or it may be an angle sensing sensor, or it may comprise a height of a wave, a period of a wave (such as a sensor system based on infrared and radar) Can be a sensor that measures or interprets the same actual wave-motion, and can also be an existing stored (e.g., stored) wave form such as the area specificities (e.g., based on buoy measurements) Lt; RTI ID = 0.0 > data. ≪ / RTI > The sensor system may also utilize wind speed and / or wind direction measurements, or may use other variables that affect the motion of the ship (not limited to roll motion).

Here, each said ballast body has an oil damper (oleo damper) with a damper on the opposite lateral side, preferably with a stroke of at least 0.25 meters.

Operation of the roll dampening mechanism in the vessel 200 may reduce the roll of the drilling vessel and may increase the operational stability of the vessel when, for example, the drilling operation is performed in an adverse situation.

Specific disadvantages arise when operating the BOP or similar equipment. As is known in the art, Blow Out Preventers are often bulky and very heavy equipment. When the roll dampening mechanism is actuated, the operation of the BOP, such as to bring it from the storage position into the firing line or vice versa, is greatly facilitated, thereby reducing the roll of the vessel.

In general, the operation of the roll dampening mechanism with movable ballast bodies allows precise control of the cargo on the drilling rig during drilling operations and contributes to the effect of a heave compensator operating on the drilling rig. .

The active use of the roll dampening mechanism on the drill rig also has the advantage of being able to assemble (and disassemble) the riser device, wherein the riser portion is connected from one end to the other. Generally, the hanging riser device has a vertical direction, so that the rolling motion of the ship causes misalignment between the suspended riser and the new riser portion to be connected to the riser device. Many connectors on the riser section allow only minor misalignment, and in general the connection process is hampered by the rolling motion. By using the roll dampening mechanism during this process, it is possible to reduce and alleviate misalignment, thus helping to be an efficient process.

In general, the roll damping machinery is geographically considering the placement of single hull drilling vessels and so far, a large and costly semi-submersible drilling vessel was required to achieve a stable drilling situation.

Preferably, for each of the vessels shown in the figures, the roll damping mechanism is formed such that a single ballast body is mounted on and guided by a set of associated lines. Whereby the center of gravity of the ballast body can be shifted as far as possible to the center line of the ship, thereby obtaining an increased restoring moment.

Also preferably, for each of the vessels shown in the figures, the ballast body may be embodied as a single metal block, or may be embodied as a single block of solid bodies having a weight of at least 100 tons, And is implemented as a set of metal blocks.

Also preferably, for each of the vessels shown in the figures, the ballast body has a height greater than the length of the ballast body in the transverse direction so that the center of gravity of the ballast body is as close as possible to the centerline of the vessel So that an increased restoring moment is obtained.

Claims (19)

  1. A hollow vertical column 21 comprising a lower portion 22 and an upper portion 23 fixed to the hull,
    The other end of the jib is connected to the other end of the jib as well as to the hull of the ship as the jib An extended jib 24 that is also moving out of the hull within a distance that can be made,
    A jib connection member 26 rotatable with respect to the column 21 and forming a horizontal rotation axis so that the jig can be rotated up and down,
    A topping means (30, 31) for rotating the jib (24) up and down, including a jib winch (30) and a jib hoisting cable (31)
    One or more hoisting cable guides (43) on said jibs of the hoisting cranes; And
    (35, 36) for hoisting a cargo comprising a hoisting cable (36) extending from the hoisting winch (35) and the hoisting cable guide on the jib to a hoisting winch A single-stranded ship (1) having a crane (20), said single-
    Water ballast system,
    Further comprising an active roll damping mechanism,
    Wherein the active roll damping mechanism comprises:
    - a set of metal blocks which are movable in the transverse direction of the hull and are comprised of a plurality of monolithic metal blocks fixed to one another to form a single solid body having a weight of at least 100 tonnes, Or as a monolithic metal block, the solid roll damping ballast (110), the solid roll damping ballast
    A sensor for sensing the rolling motion of the hull, and
    And a drive and control system (115) operative to cause and control movement of said solid roll damping ballast in response to sensing of said sensor to provide roll stability.
  2. A single-hull coastal drilling vessel (200) comprising a drilling structure (211) having at least one drilling station so that drilling of the seabed can be performed from a ship,
    Said single-shaft coastal drilling vessel comprising an active roll damping mechanism, said active roll damping mechanism comprising:
    - a set of metal blocks which are movable in the transverse direction of the hull and are comprised of a plurality of monolithic metal blocks fixed to one another to form a single solid body having a weight of at least 100 tonnes, Or as a monolithic metal block, the solid roll damping ballast (260), the solid roll damping ballast
    A sensor for sensing the rolling motion of the hull, and
    And a drive and control system (270) operative to cause and control movement of said solid roll damping ballast in response to sensing of said sensor to provide roll stability.
  3. The ship of claim 1, wherein the total mass of the solid roll damping ballast (110) is at least 800 tons.
  4. 3. A watercraft as claimed in claim 2, wherein the total mass of the solid roll damping ballast (260) is between 100 and 750 tons.
  5. 5. A watercraft as claimed in any one of claims 1 to 4, characterized in that the vessel (1; 200) comprises dynamic position control means.
  6. 5. A watercraft as claimed in any one of the preceding claims, characterized in that the roll damping mechanism comprises a single ballast body (110; 260) mounted and moving along a set of associated tracks.
  7. 2. A watercraft as claimed in claim 1, wherein the total mass of the solid roll damping ballast (110) is between 1000 and 3000 tons.
  8. The ballast according to any one of claims 1 to 4, characterized in that the ballast body (110; 260) has a height between 1.5 and 4 meters, which is greater than the length of the ballast body in the transverse direction of the ship Ship.
  9. The ship of claim 1, wherein the heavy lift cranes are capable of hoisting at least 5000 tonnes of cargo.
  10. 3. The apparatus of claim 1, wherein the crane comprises an upper cable guide (40) located at the upper portion (23) of the vertical post, the upper cable guide (40) comprising a rotary bearing structure, Wherein the jig is operable in accordance with the rotational movement of the jib relative to the vertical post and adopts the same angle as the jib.
  11. The hoisting machine according to claim 1, characterized in that the hoisting winch (35) is arranged in the vicinity of the lower part of the vertical post (21) so that the hoisting cable extends from the winch through the hollow vertical column to the upper cable guide And extends to a hoisting cable guide on the jib.
  12. 2. A winch winch according to claim 1 wherein said jib winch and said hoisting winch are disposed on a rotatable winch support which is rotatable about a rotation axis parallel to said vertical post, A support pedestal 50 is mounted for movement relative to the vertical post 21 and the winch support 50 includes a drive motor assembly 52 for moving the winch support 50, Wherein the winch support (50) maintains a constant direction with respect to the jib (24) when the jib rotates with respect to the vertical post (21).
  13. The ship according to claim 1, characterized in that the vertical column (21) comprises a continuous outer wall.
  14. The ship according to claim 1, wherein a horizontal cross section through the vertical column (21) is circular and the cross section gradually decreases toward the upper part of the column.
  15. The ship according to claim 1, wherein the lower portion of the column (21) is rectangular.
  16. 3. The hoist system of claim 2, wherein the vessel comprises a portal 205 and a multiple firing line hoist system 210, wherein the multiple firing line hoist system is disposed over the portal, As a vessel extending to two opposite sides, the multiple firing line hoist system 210,
    A mast 211 having a hollow structure including a base and an upper side connected to the hull of the drilling ship, such as a transverse girder, and including a first side 212 and an opposite second side 213,
    - a first hoist comprising a cargo attachment means (214) supported by the mast and displaced along a first firing line (214a) extending outside and adjacent to the first side (212) of the mast Sting devices,
    - a second hoisting device supported by the mast and comprising cargo attaching means (215) displaced along a second firing line (215a) outside and adjacent to the second side (213) of the mast Characterized in that it comprises a vessel.
  17. 17. A watercraft as claimed in claim 16, wherein a roll dampening mechanism (260, 270) is disposed in the chamber (250) below the deck of the ship adjacent to the door (205).
  18. A method of operating a single-hull craft as claimed in any one of the preceding claims, characterized in that the roll damping mechanism is used for a counter heel generated by rotation of the jib.
  19. Use of a vessel (200) according to claim 2, characterized in that the roll damping mechanism is used in a counter roll during a drilling or BOP operation.
KR1020107008240A 2007-10-11 2008-10-09 Vessels with roll damping mechanism KR101533392B1 (en)

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US96073607P true 2007-10-11 2007-10-11
US60/960,736 2007-10-11
PCT/NL2008/000221 WO2009048322A1 (en) 2007-10-11 2008-10-09 Vessels with roll damping mechanism

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EP2207713A1 (en) 2010-07-21
DK2207713T3 (en) 2013-06-17
US20100307401A1 (en) 2010-12-09
EP2207713B1 (en) 2013-03-20
CN101918271A (en) 2010-12-15
WO2009048322A1 (en) 2009-04-16
CN101918271B (en) 2013-09-11

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