Abstract:
The present disclosure relates to a device for lifting and lowering a load in water, including a hoisting gear with a first hoisting rope and a storage drum with a second hoisting rope, which preferably are arranged on a floating unit. In accordance with the present disclosure, a hoisting gear frame is fastened to the first hoisting rope, whose buoyancy in water is variably adjustable. Furthermore, the present disclosure relates to a method for lifting and lowering a load in water by using such a device.

Description:
CROSS REFERENCE TO RELATED APPLICATION 
     This application claims priority to German Patent Application No. 10 2008 059 805.4, filed Dec. 1, 2008, which is hereby incorporated by reference in its entirety for all purposes. 
     TECHNICAL FIELD 
     The present disclosure relates to a device and a method for lifting and lowering a load in water, comprising a hoisting gear with a first hoisting rope and a storage drum with a second hoisting rope, which preferably are arranged on a floating unit. 
     BACKGROUND AND SUMMARY 
     For erecting offshore plants, such as oil rigs, wind turbines or others, in waters with all kinds of properties different components or loads must be lifted, moved or also lowered. It can occur, for instance, that during construction of an offshore plant heavy components or loads must be lowered onto the sea bed. In general, this kind of work is performed from floating units, wherein the load to be transported is carried by a hoisting gear attached to a crane or by a hoisting gear directly mounted on a floating unit. 
     The problem is that these floating units are exposed to heave-related movements. In general, these movements are transmitted even more to the hoisting gears used and, if cranes are used, also to the crane itself. Hence, the load present on the hoisting gear also undergoes accelerations, which lead to an increased weight force of the load which must be borne by the systems. Moreover, in the vicinity of the “splash zone”, i.e. when the load is partly in the water and partly in the air, additional loads are produced as a result of hydrodynamic effects caused by the heave and by movements of the floating unit. The strength of said loads is dependent on the geometry of the floating units employed and on the load to be transported and depending on size can therefore have a considerable influence on the forces occurring in the system. The effects described above altogether require a reinforced construction of the components used for the hoisting gears and the cranes, which leads to a fast increase of the production and maintenance costs of such systems. 
     When the load is lowered further below a certain depth of water, it reaches a region which is calmed to such an extent that the heave has no major influence on the load and the part of the hoisting system lying under water. The load then can rapidly be lowered until it almost touches the sea bed or the place of destination of the load. At this moment at the latest, a suitable control in the hoisting gear used must compensate the movements of the hoisting winch and the crane on the floating units generated by the heave, so that the load can be put down on the sea bed or the place of destination slowly and safely. 
     Such compensating control also is referred to as heave compensation and should ensure that the hoisting rope on which the load is suspended is kept taut, in order to avoid shocks when picking up and putting down the load. Due to the heave, the floating unit or the load undergoes position movements which lead to abruptly varying distances between load and hoisting systems or floating units. The heave compensation of the hoisting winch must react to the respective situation and for instance provide more hoisting rope or wind up some hoisting rope. The problem described above, however, relates to very great loads, whereby such compensating control (heave compensation) involves very high demands as to the capacity of the hoisting winch used. In general, such high powers only can be achieved by incorporating an energy storage device, which likewise leads to greatly increasing production costs, since the availability of such cranes is rather low. 
     Another problem consists in the partly very great depth of water into which the loads to be transported should be lowered. The rope lengths required for this purpose lead to further aspects which must be considered in the use and production of such hoisting systems. For instance, the elastic rope together with the load provides a separate oscillating system, which is superimposed on the moving system of the floating unit. Therefore, a heave compensation means must also compensate these additional oscillations, which presently represents an unsolved problem. 
     When designing such hoisting systems, it is furthermore necessary to consider the transfer of a load from a moving acceleration system, i.e. on the water surface, into a quasi stationary system, i.e. a certain depth of water in which the load is located. 
     The problems with the design of offshore devices for lowering and lifting loads can be summarized as follows:
         strong crane for traversing the splash zone,   the hoisting winch used must be equipped with a heave compensation means,   the hoisting winch used must have a high power or an energy storage system,   gradual transfer from an oscillating system into a rest condition,   additional oscillations.       

     Therefore, it is the object of the present disclosure to provide a device and a method which simplifies hoisting work in the offshore region. 
     In accordance with the present disclosure, this object is solved by a device for lifting and lowering a load in water, comprising a hoisting gear with a first hoisting rope and a storage drum with a second hoisting rope, which preferably are arranged on a floating unit, wherein a hoisting gear frame is fastened to the first hoisting rope, whose buoyancy in water is variably adjustable. For this purpose, the device includes a hoisting gear with a first hoisting rope and a storage drum with a second hoisting rope, which preferably are arranged on a floating unit, wherein a hoisting gear frame, whose buoyancy in water is variably adjustable, is fastened to the first hoisting rope. The storage drum serves to wind up the second hoisting rope, wherein the portions of the hoisting rope to be wound up are not exposed to any forces. The first hoisting rope of the hoisting gear is fastened to said hoisting gear frame, which forms an independent floating unit. By means of suitable measures, the buoyancy of the hoisting gear frame can be adjusted. Buoyancy is defined as a force acting against gravity. This means that a force can be generated by this variable buoyancy, which acts against the gravity of the hoisting gear frame, can compensate the same and thus can bring the hoisting gear frame into a “floating condition”. In accordance with the present disclosure, a changed weight force of the hoisting gear frame, for instance due to a load suspended on the hoisting gear frame, can be compensated by increasing the buoyancy. The hoisting gear frame of the present disclosure thus is capable of holding itself at a predefined depth of water without any further drives. 
     Advantageously, the hoisting gear frame comprises an overpressure hoisting gear frame, whereby the buoyancy of the overpressure hoisting gear frame can be adjusted. The overpressure hoisting gear frame includes an air cell, wherein the buoyancy of the hoisting gear frame is increased when filling the air cell with air and the buoyancy of the overpressure hoisting gear frame is reduced when draining the air from the air cell. 
     Advantageously, a traction sheave drive is arranged in the overpressure hoisting gear frame, which drives a second hoisting rope. A traction sheave drive consists of at least one traction sheave over which an associated hoisting rope is guided. The rope is not attached to the traction sheave, but is retained and moved by friction. To increase the contact surface and hence the friction, the traction sheave has grooves into which the hoisting rope is pressed by the tensile stress. 
     Preferably, the traction sheave drive comprises at least two traction sheaves. 
     In a furthermore advantageous way, the at least two traction sheaves of the traction sheave drive are independently controllable. As a result, a uniform structure of the rope system can be ensured. 
     Advantageously, the second hoisting rope is guided from the storage drum over the traction sheave to the load to be moved and is fastened to the load with its rope end. Thus, the weight force of the load only is applied in the region of the hoisting rope between traction sheave and load. In the region of the rope between storage drum and traction sheave, no tensions are applied to the hoisting rope, whereby the required power of the storage drum for winding up the hoisting rope is reduced to a minimum. 
     Alternatively, the second hoisting rope in the hoisting gear frame can be driven by a hoisting winch, wherein the second hoisting rope is guided from this hoisting winch to the load and is fastened to the same. 
     Advantageously, a fiber rope is used as second hoisting rope. 
     The use of a steel rope as second hoisting rope can also be advantageous. 
     Preferably, the second hoisting rope is dimensioned such that its load bearing capacity is appropriate for the load to be borne and relatively small hoisting load coefficients can be employed. The second hoisting rope performs the hoisting work on the load in a depth of calmed water. As a result, the above-mentioned influences on the hoisting system must only be considered to a small extent when dimensioning the hoisting rope. 
     Advantageously, an arrangement of a holding brake is provided, which acts directly on the second hoisting rope. This should prevent a fast unintended lowering of the load from the hoisting gear frame. 
     Furthermore advantageously, an additional cable drum for a supply cable is provided on the floating unit. The drive units for the storage and cable drums can be arranged on the floating unit individually or jointly. 
     Advantageously, said supply cable comprises a control line and/or a power supply line. Preferably, the supply cable is connected to the hoisting gear frame and the traction sheave drive or hoisting winch drive arranged therein is controlled by the control lines and supplied with electricity from the floating unit by the power supply lines. 
     What is advantageous is the use of a crane with a hoisting winch for said hoisting gear. The crane can have a slewable, telescopable boom with a deflection pulley arranged at the tip of the boom. What is likewise possible is the use of a lattice mast crane or other crane configurations known according to the prior art. 
     Advantageously, the hoisting winch of the hoisting gear or of said crane comprises a heave compensation. The heave compensation serves to compensate the heave-related movements of the individual components of the device and thus should ensure an appropriate constant tightening of the hoisting rope between hoisting winch and hoisting gear frame or the load. 
     In a furthermore advantageous way, at least one further hoisting gear, preferably a crane, can be provided for lifting the load or the hoisting gear frame. The same either can support the first crane or be used for instance for lowering the load through the splash zone. The hoisting gear, in particular the hoisting winch, likewise can comprise a heave compensation, so as to compensate external influences, such as the heave, on the hoisting system. The additional further hoisting gears can be arranged together with or separate from the first hoisting gear. It may be advantageous, for instance, to separately arrange a further hoisting gear on a further independent floating unit. Furthermore, coupling the hoisting gears used in terms of control is also possible, wherein either some or all hoisting gears together are controlled from a central control unit. 
     In accordance with a further aspect of the present disclosure, the air cell in the overpressure hoisting gear frame is controlled by the control lines of the supply cable. As a result, the buoyancy and the adjustable drive of the traction sheaves can be controlled centrally from the floating unit. By emitting certain control signals, the crane operator thus can accomplish lifting or lowering of the load or manually configure the buoyancy of the overpressure hoisting gear frame. Preferably, the buoyancy of the overpressure hoisting gear frame is controlled via compressed air by means of the air cell. It is possible to supply said compressed air to the air cell via a supply cable, but alternative ways of supplying the air cell with compressed air are also conceivable. 
     In an advantageous way, the control of the air cell is effected in dependence on the respective force applied to the first hoisting rope. For this purpose, the force applied to the first hoisting rope is determined by a non-specified device for measuring the force on the hoisting rope. The same represents the difference between the weight force of the hoisting gear frame and the buoyant force of the hoisting gear frame. If this difference tends towards the value 0, the hoisting gear frame is in a kind of floating condition in the water. However, if the weight force of the hoisting gear frame is influenced from outside, for instance by suspending a load, a force must be borne by the first hoisting rope which corresponds to the difference between buoyant force and weight force of the hoisting gear frame. By increasing the buoyant force of the hoisting gear frame by means of a suitable control of the supply of compressed air, advantageously automated by an electric control unit, the force applied to the second hoisting rope can be minimized to a predefined value. 
     In accordance with the present disclosure, the object mentioned above is solved by a method for lowering or lifting a load in the offshore region by using the devices described above with the method steps comprising the following:
     a. picking up a load from a transportation unit by a hoisting rope fastened to the load and connected with a second hoisting system or crane and lowering the load through the splash zone down to a defined depth with calmed water;   b. tightening the second hoisting rope by means of the traction sheave drive or the hoisting winch of the overpressure hoisting gear frame;   c. controlling the buoyancy of the overpressure hoisting gear frame;   d. knocking off the hoisting rope of the second hoisting system or crane from the load; and   e. lowering the load by means of the traction sheave or hoisting winch drive down to the predefined deposition point.   

     In the first step, the load to be transported is picked up from a transportation unit by a hoisting rope fastened to the load and connected with a second hoisting system or crane. The load is loosely connected with the second hoisting rope of the hoisting gear frame, which is fastened to a first hoisting rope of a first hoisting gear. 
     By means of the second hoisting system directly fastened to the load, the load now is lowered through the “splash zone” down to a depth of calmed water. By controlling the traction sheave drive or the hoisting winch of the hoisting gear frame, the second hoisting rope is tightened, whereby a tension is obtained between load and hoisting gear frame. At the same time, the buoyancy of the hoisting gear frame is incrementally increased by the control, preferably by the electric control unit. Thus, the second hoisting rope of the traction sheave drive gradually takes over the load from the hoisting gear of the second hoisting gear system. 
     After 100% of the load are transferred to the second hoisting rope of the hoisting gear frame and the buoyancy of the hoisting gear frame is suitably adapted, the hoisting rope of the second hoisting gear is knocked off from the load. Thus, the weight force of the load only is applied to the second hoisting rope of the hoisting gear frame. 
     Subsequently, the load is lowered down to the predefined deposition point, for instance the sea bed, by means of the traction sheave or hoisting winch drive. 
     Advantageously, the control of the buoyancy of the hoisting gear frame is coupled to the resultant residual force on the first hoisting rope. This means that during transfer of the load from the hoisting rope of the second hoisting system to the second hoisting rope of the hoisting gear frame, the buoyancy of the hoisting gear frame must be increased continuously. Preferably, these steps of increasing the buoyancy are suitably adapted to the resultant residual force measured on the first hoisting rope, which can be performed manually or also automatically. 
     In a furthermore advantageous way, the vertical position of the hoisting gear frame in the water with respect to the watercourse bed is ensured, or maintained, by the heave compensation of the first hoisting system or crane. In particular the movements of the floating unit, which are caused by the heave, must be compensated automatically. In the case of a wave crest, for instance, more hoisting rope must be provided by the heave compensation of the first hoisting system, in order to prevent the hoisting gear frame from being lifted inadvertently by the first hoisting rope. 
     Alternatively, said requirement of the heave compensation of the first hoisting gear, i.e. ensuring, or maintaining, the vertical position of the hoisting gear frame in the water with respect to the watercourse bed, can be ensured by the second hoisting system. 
     Further features, details and advantages of the present disclosure will be explained in detail below with reference to an embodiment illustrated in the drawing. 
    
    
     
       BRIEF DESCRIPTION OF FIGURES 
         FIG. 1  shows a device for lowering or lifting a load in the offshore region in a configuration of a preferred embodiment of the present disclosure. 
         FIG. 2  shows an example method for lowering or lifting the load in the offshore region. 
     
    
    
     DETAILED DESCRIPTION 
     The only Figure shows a “strong” crane  17  on a unit  21  floating on the water surface  20 , with the load  15  to be borne being fastened to its hoisting rope  18  in a fastening point  19 . The construction of the strong crane  17  is dimensioned such that the load can be lowered through a so-called “splash zone” down to a predefined water depth h. In said “splash zone”, the regular weight force FL of the load  15  acting on the material used is amplified by external influences resulting from the movements of the load and the floating units, and thus requires a distinctly stronger design of the crane components of the crane  17 . 
     From the water depth h, the load is located within a calmed system, i.e. external circumstances, such as the heave of the watercourse, only have a negligeable influence on the load. 
     Furthermore, a first “weak” crane  2  with a hoisting rope  4 , which is fastened to a hoisting gear frame  13  in a fastening point  12 , is arranged on another unit  1  floating on the water surface  20 . The hoisting rope  4  is driven by the hoisting winch  3  mounted on the crane  2  and deflected via a deflection pulley  11 . In addition, a storage drum  5  and a cable drum  6  are provided on the floating unit  1 . From the cable drum  6 , a supply cable  8  is guided over a deflection pulley  9  to the hoisting gear frame  13  and can be wound up on and unwound from the cable drum  6  depending on the water depth of the hoisting gear frame  13 . 
     In the Figure, the hoisting gear frame  13  reveals a traction sheave drive with two traction sheaves  14  to be actuated or driven separately. Said hoisting rope  7  is guided from a fastening point  16  on the load  15  to the traction sheaves  14  of the hoisting gear frame  13 . The traction sheave mechanism known to one of skill in the art can lift or lower the load  15  by the traction sheaves  14  via the hoisting rope  7 . Furthermore, the loose end of the hoisting rope  7  is directed from the traction sheaves  14  over the deflection pulley  10  to the storage drum  5 . In the ideal case, however, no force or tension acts on the hoisting rope  7  in the region between the traction sheaves  14  and the storage drum  5 . Thus, a relatively small power is required for the process of winding and unwinding the hoisting rope  7  of the storage drum  5 . 
     The applied forces on the system are represented in the Figure by the corresponding arrows. The arrow with the designation FL shows the weight force of the load  15 , the arrow with the designation FA shows the buoyant force of the hoisting gear frame  13 , and the arrow with the designation Fr shows the resultant force acting on the hoisting rope  4 . In simple terms, the resultant force Fr is calculated from the difference of weight force FL and buoyant force FA. For controlling the traction sheave drive or the hoisting winch drive of the hoisting gear frame  13 , the supply cable  8  is used. 
     A method for lifting and lowering the load in water with the configuration of  FIG. 1  is now illustrated with regard to  FIG. 2 . Specifically,  FIG. 2  shows a method  200 , which includes at  202 , picking up the load from the transportation unit by the hoisting rope fastened to the load and connected with the second hoisting system or crane and lowering the load through the splash zone down to a defined depth at which the water is sufficiently calm. Then, at  204 , the method includes tightening the second hoisting rope by the traction sheave drive or the hoisting winch of the overpressure hoisting gear frame. Then, at  206 , the method includes controlling, e.g., automatically adjusting in response to operating conditions, the buoyancy of the overpressure hoisting gear frame. Then, at  208 , the method includes knocking off the hoisting rope of the second hoisting system or crane from the load. Then, at  210 , the method includes lowering the load by the traction sheave or hoisting winch drive down to the predefined deposition point. 
     A holding brake  22  may be provided which directly acts on hoisting rope  7 . One or more drive units  23  for the storage and cable drums may be arranged on the floating unit  1  individually or jointly. The hoisting winch  3  may comprise a heave compensation  24 . A measuring device  25  may be arranged on the hoisting rope  4  to measure a resultant force applied on the hoisting rope. 
     In one specific example for lowering the load  15  onto a certain region, for instance the watercourse bed, the following more detailed method for lowering or lifting a load can be realized, which can be subdivided into the following method steps:
     1. In the fastening point  19 , the load  15  is fastened to the hoisting rope  18  of the crane  17 , which is located on the floating unit  21 . At the same time, the hoisting rope  7  is also connected with the load  15  in a fastening point  16 , with no tensions or forces, however, acting on the hoisting rope portion of the hoisting rope  7  between hoisting gear frame  13  and load  15 .   2. By means of the crane  17 , the load  15  now is transferred from a non-illustrated transportation unit onto the water surface  20 , wherein at the same time the hoisting gear frame  13  connected with the load  15  likewise is put down onto the water surface  20  by means of the crane  2  via a hoisting rope  4  connected in the fastening point  12 .   3. The load  15  and the hoisting gear frame  13  are moved by the two cranes  2 ,  17  through the splash zone down to a depth h with calmed water. The rocking movements of the floating units  1 ,  21  and of the load  15  and the hoisting gear frame  13  must be compensated by the heave compensations of the two cranes  2  and  17 . Furthermore, the heave compensation of the crane  2  ensures that the hoisting gear frame  13  does not change its vertical position with respect to the sea bed.   4. Upon reaching the depth h, the hoisting rope  7  slowly is tightened by the traction sheave drive by means of the traction sheaves  14  of the hoisting gear frame  13  and thus slowly takes over the load  15  from the hoisting rope  18  of the crane  17 . When the hoisting rope  7  is tightened, the buoyancy of the hoisting gear frame  13  at the same time is varied such that the resultant force Fr on the hoisting rope  4  of the crane  2  remains constant and the hoisting gear frame floats in a predefined depth. The power of the heave compensation of the crane  2  is not changed thereby.   5. The control of the traction sheave drive of the hoisting gear frame  13  and the control of the buoyancy with the force FA is effected with reference to the signals transmitted via the control line of the supply line  8 . The drive of the traction sheave drive of the hoisting gear frame  13  is supplied with electricity by a power supply in the supply cable  8 .   6. When the hoisting rope  7  has taken over 100% of the load  15  from the crane  17 , the hoisting rope  18  of the crane  17  is knocked off from the load  15 .   7. The load  15  is moved down to the sea bed by means of the traction sheave drive and slowly put down. Lowering the load  15  by the hoisting system of the hoisting gear frame  13  now can be effected shock-free, since the hoisting gear frame  13  and the load  15  are located in a calmed water depth h. This water depth can be interpreted as a quasi stationary system.   

     The lifting operation is performed in the opposite order. The load  15  is lifted by the hoisting gear frame  13  and the hoisting rope  7  and lifted from the calmed water depth h through the splash zone onto a non-illustrated transportation unit by means of the crane  17 .