WAVE POWER PLANT AND TRANSMISSION RELATED APPLICATIONS

This application claims priority and benefit from Swedish patent application No. 0800395- 6, filed February 20, 2008, and Swedish patent application No. 0802165-1, filed October 10, 5 2008, the entire teachings of which are incorporated herein by reference. TECHNICAL AREA

The present invention relates to a wave power plant for extraction of electrical energy from motions of water waves, a method of extracting electrical energy from more or less intermittent mechanical energy, such as more or less periodical motions in a body, and a transmission for power0 plants to be used when such more or less intermittent mechanical energy is available. BACKGROUND

Wave power has a large potential of becoming cost efficient since the energy density in ocean waves is very high (approximately 1000 times higher than in the wind), this allowing small wave energy converters in relation to the capacity thereof. Furthermore, wave energy is 5 more predictable than for instance wind power since waves are built by the wind during a long period of time and then continues as swell also after the wind has subsided. This results in slow variations in the average energy content of the waves, which gives system advantages when wave energy converters are connected to the general electric power distribution network.

A reason why, in spite of this potential, there are so few competitive solutions today is that0 wave energy is difficult to master. The ocean is a rough environment with high material stress. In stormy weather the energy levels can be a 100 times higher than normal. The wave motion is oscillating and with never ceasing variations in height, length and time period (velocity) from wave to wave, this giving large variations in the energy absorbed by a wave power plant. For direct driven operation, i.e. when the generator in the wave power plant is driven according to5 the momentary motion of the wave, this results in a low utilization of the power plant, i.e. the so called capacity factor takes a low value. The power of the generator shifts between zero and a top level twice every wave period. The top level may also change very strongly from wave to wave. The general electric power distribution network requires relatively stable levels, both in delivered power and voltage, this resulting in that the electrical control systems for this kind of0 wave energy converters must, after the generation, make the levels of these more even. Also, the uneven levels results in a costly over-dimensioning of the total electrical system of a wave power plant in order to obtain a proper handling of the top power levels.

To make wave power competitive a wave power plant is required that can efficiently absorb the wave energy at the same time as the motive force on the generator is levelled, so that5 a higher capacity factor is obtained. Also, a low system complexity and an efficient use of

components are required. The structure of the wave power plant must also be storm proof and have a long life-cycle, and low operational and maintenance costs that can be achieved by a construction allowing long service intervals and includes wearing parts that can be easily accessed. Wave power technology has been developed for a long period of time but so far it has not been possible to arrive at a method or a design of a wave power plant, where it has been possible to combine the necessary properties as described above.

A frequent method of capturing the energy of water waves is to use the vertical motion of the water. Installations that use such technology are sometimes called "point absorbers". One way of using the vertical motion incorporates a buoy having a bottom foundation and an anchor wheel. The bottom foundation is firmly positioned at the sea-floor and is connected to the buoy which follows the ocean surface, i.e. the wave motions. When the surface rises and thereby lifts the buoy, a motive force is created, which is converted to a rotational motion by a driveshaft connected between the foundation and the buoy or by a wire or chain, which runs over an anchor wheel journalled in bearings at the buoy or in the foundation and which at an opposite end is connected to the foundation or the buoy, respectively. The motive force increases due to the increased motion speed of the waves when the wave height becomes higher. The rotational direction and speed of an anchor wheel, is such a wheel is used, is directly dependent on the vertical direction and motion speed of the waves. However, this is not optimal for coupling a conventional generator to the anchor wheel to produce electric energy.

In order to make a wave power plant driving a conventional rotating generator efficient, the vertical motion of the waves must be converted into a unidirectional rotational movement, and the rotation speed of an electrical generator connected to the transmission must be stabilized. In a device, as described above, using a driveshaft, wire or chain, which is secured to the sea bottom or in a frame structure and which runs along or over an anchor wheel journalled in a buoy, this problem can be solved in the following way. When the buoy is lifted by a wave, a motive force over the anchor wheel is created. Thereupon, when the wave falls, an anti-reverse mechanism is disengaged and the anchor wheel is returned by a counterweight. Then, the motive driving is only active during the rise of the wave and ceases completely when the wave sinks, which is not satisfactory. Attempts have been made to reverse the rotation direction, so that an electrical generator driven by the anchor wheel is driven by the counterweight in the same direction also when the wave sinks. It has also been attempted to reverse the rotation direction of the generator. However, changing the rotation direction of a mechanical transmission or of the generator twice for every wave period results in heavy mechanical wear. Even though the rotation direction can made unidirectional by the transmission, the rotation speed follows the

speed of the vertical motion, this causing that the power output from the generator varies according to the speed of the wave motion. This gives to a low capacity factor and high attenuating effects since the mass of the generator all the time alternatingly be accelerated and decelerated. In order to make the motive force and rotation speed of a generator using a mechanical transmission multiple buoys can cooperate, a phase shift existing between the buoys. However, this only works optimally in the case where the buoys are evenly distributed over a wave period, which very seldom occurs the length and speed of the waves always vary. Also, the transmission system becomes more complex and hence hydraulic mechanisms are frequently used in systems of this type. However, hydraulic devices results in complex systems having large transmission losses. A wave power plant of the type described above is disclosed in the published French patent application 2869368, which comprises a floating platform or buoy. Lines run over pulleys at the buoy, one end of the lines being attached to the bottom and the other end carrying a counterweight. The rotation of the pulleys is transferred to generators. The rotation speed and power output from the generator vary according to the motion of the waves. A similar wave power plant is disclosed in U.S. patent 4,242,593, which drives a wheel or pulley in the buoy only when it is rising. A gearbox is provided for gearing up the rotation speed of the wheel or pulley in the buoy to make it suitable to be used for driving a generator. In U.S. patent 5,889,336 and the published Japanese patent application 11-6472 a similar wave energy plant is disclosed including a chain which at one end is attached to a bottom foundation end and at its other end has a counterweight. The chain passes over a chain pulley in a buoy. The chain pulley is connected to a generator through a directly acting transmission, which is arranged so the generator always rotates in the same direction. The rotation speed depends on the speed of the vertical motion of the buoy.

A wave power installation of a somewhat different type is disclosed in U.S. patent 4,241,579. A driveshaft is mounted to be elevated and sunk between the water surface and the bottom. A number of buoys are by wires connected to counterweights and the lines pass around the common driveshaft for driving only when the respective buoy. In the published British patent application 2062113 a wave energy converter is disclosed including a plurality of different drive mechanisms, each one of which comprises a buoy and a counterweight/bottom foundation/additional buoy and which act on a common driveshaft through one-way couplings. In the published French patent application 2339071 a buoy is used, which is connected to one end of a chain and by the chain drives a driveshaft placed above the water surface to rotate. The other end of the chain carries a counterweight, which is also placed above the water surface. The connection to the driveshaft is of a unidirectional type and the driveshaft may be driven by several such buoys through chains.

In the published International patent application WO 2005/054668 a wave energy plant including a buoy which is attached to an end of a line is disclosed. The other end of the line is more or less wound up around a drum placed on the bottom of the sea. The drum is connected to a return spring and a generator and drives the generator in both the rising and sinking motion of the buoy. In the wave energy plant according to the published International patent application WO 03/058054 the buoy acts as an winding drum for a line, the lower end of which is connected to a bottom foundation. A return spring, a gear up mechanism and a generator are located inside the drum. The generator is driven in both the rising and sinking motion of the buoy. SUMMARY It is an object of the invention to provide an efficient wave energy plant.

In a wave energy plant energy from water waves in a pool of water during parts of the motions of the water waves is absorbed for driving an electrical generator. However, part of the absorbed energy is temporarily accumulated or stored in some suitable mechanical way for driving the electrical generator during other parts of the motions of the water waves. Thereby, an equalization over time of the motive force, which drives the electrical generator, can hereby achieved. For the temporary mechanical accumulation of energy a change of potential energy can be used, such as variations of the potential energy of a suitable body. For example, the change of potential energy can be based on elastic forces or on gravitational forces. In the latter case a floating body can be used, i.e. a body having a density lower than that of water, which is located at a varying distance from the water surface and hereby indirectly uses the gravitational forces. The body used for accumulation of energy can in the same case alternatively be a counterweight, i.e. a body having a density higher than that of water, which uses the gravitational forces in a more direct way. The body may in these cases be connected to some elongated means, such as a line, wire or chain, which in the case where it is flexible can be more or less wound around a counterweight drum. The counterweight drum can be journalled at a buoy or at a stationary rack or frame placed on or attached the bottom of a pool of water. The counterweight drum can in one case be mechanically connected to a rotating part of an electrical generator and the weight or buoyancy of the body is used for continuously driving the counterweight drum to rotate in an opposite relative rotational direction compared to the rotational direction of a driveshaft, which is connected to another elongated means, also here for example a line, wire or chain.

The driveshaft is mechanically arranged for a unidirectional rotation only, driven for example by the rising or sinking motions of a water surface or more particularly by alternatingly rising and sinking movements and/or alternating tilting, back and forth movements of a buoy, i.e. a body having a density lower than that of water, which is floating at the water surface, or

alternatively by some other form of oscillatory movement or combination of oscillatory movements in the waves or in the water. The electrical generator is in the above mentioned cases mechanically connected in a transmission path between the driveshaft and the counterweight drum. The electromagnetic coupling between the parts in the electrical generator over the air gap of the generator gives a limited torque in relation to the rotation speed of the generator, the mechanical torque provided by the counterweight drum and the electrical load of the generator. When the driveshaft is rotating faster than the rotational speed in the generator, the counterweight drum is rotated in a first rotational direction, this causing the counterweight to be hoisted up, thereby accumulating potential energy. When the driveshaft is rotating slower than the rotation speed in the generator or is still-standing still, the counterweight drum rotates in a second rotational direction, this causing the counterweight to be lowered, thereby releasing potential energy.

As an energy accumulation device, which uses elastic forces, an elastic or resilient mechanism may be used, in which the energy is accumulated as a tension in a spring or generally as elastic energy. Such an elastic device may in a different case comprise a container for accumulation of energy as a gas pressure. The container may then be connected to a combined compressor or gas pump and a pneumatic motor such as a scroll pump. This device may have one moving part directly connected to one of the parts of the generator.

In such a wave energy plant it is possible achieve, using an energy accumulation device, also called energy storing device, and suitable couplings, an equalization of the kinetic energy of the water waves in an efficient way, so that the generator can be driven to continuously generate electricity at a relatively even level.

Generally, a wave energy plant or in its most common form a power plant using movements, such as more or less periodic motions, of the water of a pool of water, can comprise :

- A buoy or other device, which is arranged at or in the pool of water to be made, in some way, to move by movements of the water in the pool of water. Then, the buoy or the other device is constructed and placed so that it itself, because of movements in the water, obtains movements, which alternate between a movements in one direction and a movement in another direction that is different from the first direction. The movements in the water can comprise wave movements in the water or at the surface of the water, alternating movements, i.e. alternating back and forth movements in the water or at the surface of the water or generally movements alternating between a movement in one direction and a movement in another direction in the water of the pool of water. In the case of a buoy, floating at the surface of the water in the pool of water, this can mean that the buoy, at the up and down movements of the water surface, alternatingly rises

and sinks and/or alternately rocks or tilts back and forth. In general then, the buoy has an average density lower than that of water. The other device arranged at or in the pool of water may for example comprise a body having the same density as or a higher density than that of water, which is designed to follow the movements of the water, or a device that is being alternately compressed and expanded due to pressure differences in the water which occur when water waves pass.

- A driveshaft, which is rotationally journalled at some part of the wave power plant. In different designs, it can be journalled at the buoy or at the other device. Alternatively it can be journalled for rotation at a device that is rigidly attached to the bottom of the pool of water, or generally to some device arranged to counteract the movements of the water in the pool of water, such as a body having a relatively large mass or weight.

- A first elongated means, which both is connected to a device arranged to counteract the movements of the water in the pool of water, for example a fixed point at the bottom of the pool of water or a body having a relatively large mass or weight, or to the buoy, respectively, depending on the place where the driveshaft is mounted, and is connected to the driveshaft. The first elongated means may be a flexible means, such as a line, wire or chain, but it can also be stiff, in that case for example comprising a rack gearing segment.

- An electric generator connected to the driveshaft and comprising two parts that are rotatable in relation to each other, a first part and a second part, often called rotor and stator, respectively. An air gap exists between the two rotatable parts.

- An accumulation device for temporary mechanical storage of energy as described above.

The buoy or the similar device is arranged and the buoy or the other device, the first elongated means, the device arranged to counteract the wave movements, the driveshaft and the energy accumulation device are connected to each other, so that the connection between the first elongated means and the driveshaft makes the driveshaft rotate, substantially for first movements of the water surface or for first movements of the buoy or the similar device, in only one direction, thereby driving said two part of the electric generator to rotate in relation to each other in a first direction and generate electricity and at the same time also supply energy to the accumulation device. Thus, energy from the rotation of the driveshaft is hereby partly converted to electric energy, which is delivered from the electric generator, partly to energy which is stored in the energy accumulation device. The first movements can for a buoy be the movements into which the buoy is set by either one of the up- or down- going movements of the water surface.

The energy accumulating device is arranged to drive, for substantially second movements, that are substantially different from the first movements, of the buoy or the similar device, said two parts of the electric generator to rotate in the same first rotation direction in relation to each

drives said two parts of the electrical generator to rotate in relation to each other. The second movements can for a buoy be those movements, into which the buoy is set by second of the up and down going movements and thus are substantially different from said either one of the up and down going movements of the water surface. The first movements of the buoy or the other body can take place in a direction, which is mainly the opposite the direction, in which the second movements of the buoy or the other device are made. Thus, the first movements can take place in a forward direction whereas the second movements take place in a backward direction, either as a translation movements, for example up or down, or as a rotational motion, i.e. angularly, or as a combined translation and rotational movement.

The driveshaft may be mechanically connected, for example via a mechanical gear, to the first part of the electric generator. An electromagnetic coupling exists in a conventional way over the air gap between the first and second parts of the electric generator at least when these parts are moving in relation to each other. The energy accumulation device may in one special embodiment be mechanically connected to the second part of the electric generator.

The connection of the energy accumulation device to the driveshaft via the electromagnetic coupling over the air gap between the first and second parts of the electric generator gives a motive force, which counteracts to the rotation of the driveshaft when the driveshaft is rotating, by the connection between the first elongated means and the driveshaft, and thereby is driving the first part of the electric generator. Then, in the above mentioned special embodiment, the second part of the electric generator can rotate in a first direction due to the coupling to the drive shaft through the electromagnetic coupling over the air gap and the first part of the electric generator, when the motive force which is acting on the driveshaft through the coupling between the first elongated means and the driveshaft exceeds the counteracting motive force, energy being accumulated in the energy accumulation device due the mechanical coupling thereof to the second part of the electric generator. At the same time, the first and second parts of the electric generator are rotating in the same first direction in relation to each other. Furthermore, the second part of the electric generator is driven by the energy accumulation device to rotate in the same first direction substantially when the motive force, which acts on the driveshaft through the coupling between the first elongated means and the driveshaft, does not exceed the counteracting motive force. Hereby, the first and second parts of the electric generator are made to continue to rotate in the same first direction in relation to each other also in this case.

As has been mentioned above, a mechanical gear may be arranged for coupling the driveshaft to the first part of the electric generator. The driveshaft is then suitably connected to an input side of the mechanical gear and the first part of the electric generator is mechanically

connected to a first output side of the mechanical gear. In this case, the second part of the electric generator can be rigidly attached to the buoy, if the energy accumulation device is connected to a second output side that is different from the first output side of the mechanical gear. A mechanical gear can generally be regarded to comprise one input side having an input shaft and two output sides, where one of the output sides comprises an output shaft and another output side comprises a housing or enclosure of the mechanical gear, also see the discussion below of only the transmission included in the wave energy plant. For for example a planetary gear, the input side may comprise a shaft connected to the planet gear carrier and the two output sides correspond to shafts connected to the sun gear and ring gear, which may be connected to a second shaft or the housing of the planetary gear.

In the case including a buoy, the buoy can comprise a space which functions as an air pocket and in which at least the main part of the driveshaft is mounted as well as other rotating parts, such as winding drums, in the case where such are provided and couplings between them. Such an air pocket can be a space filled with air, which at its bottom is delimited by a water surface and the other sides of which are different surfaces of the buoy. Then, the air pocket may be formed by a recess in the bottom surface of the buoy.

The energy accumulation device can in one embodiment comprise a counterweight, arranged as a lead, to also move upwards for said first movements of the buoy or the other device, thereby increasing its potential energy. The coupling of the buoy or the other device, the first elongated means, the driveshaft and the counterweight to each other is then suitably arranged so that the counterweight moves downwards, for said second one of the movements of the buoy or the other device, thereby driving the parts of the electric generator to rotate in relation to each other in the first rotational direction. In the case of a buoy, this can for example mean that, for the first movements, when the buoy e.g. is moving upwards, the counterweight is also moving upwards a distance, which is greater than the vertical distance in which the buoy then vertically moves.

The energy accumulation device can in the same embodiments comprise a counterweight drum which is rotationally mounted to the driveshaft and a second elongated means for coupling movements of the counterweight to make the counterweight drum rotate. The second elongated means can be flexible or can be a flexible means such as a line, wire or chain, which at a lower end is attached to the counterweight and at its upper end is more or less wound around the counterweight drum. Furthermore, the driveshaft is connected to drive the first part of the electrical generator to rotate and the counterweight drum can in a first case be coupled to rotate the second part of the electric generator, so that the electric generator generates electric current when its second part is rotated in relation to its first part and at the same time gives a torque

counteracting this rotation. Hereby, the first and second parts of the electric generator can be made to always rotate always in the same first direction in relation to each other.

In a second case a mechanical gear can be connected between the driveshaft and the first part of the electrical generator. In this case the driveshaft is connected to an input side of the mechanical gear, the second part of the electric generator is rigidly attached to the buoy or the other device and the counterweight drum is mechanically coupled to a second output going side different from the first output side of the mechanical gear. The driveshaft can hereby, for said first movements of the buoy or the other device, provide motive forces on both of the output sides of the gear, in order to rotate the first part of the electric generator and to rotate the counterweight drum to elevate the counterweight in relation to the driveshaft. The counterweight drum can, for said second movements of the buoy or the other device, provide a motive force, through its coupling to the second output side of the gearbox, in order to rotate the first part of the electric generator.

Furthermore, in the case including a counterweight and a counterweight drum, an electric cable for the electric connection of the generator can be provided which extends from the generator to the counterweight drum and is partly wound around it, which therefrom extends to a non floatable part which is slidable along the first elongated means and to which it is rigidly connected, so that the sliding part can be maintained at a constant distance beneath the counterweight, and which electric cable extends from the slidable part up to the water surface to be further connected to an electric load. This may allow the wave energy converter to turn in the horizontal plane, such as when the direction of the water waves changes, without causing the electric cable to be entangled with the first elongated means.

An anchor drum can be mounted for unidirectional rotation around the driveshaft and further be coupled to the first oblong organ to make the anchor drum rotate for the first ones of the movements of the buoy or the other device, and thereby also making the driveshaft rotate. The first elongated means can be flexible, i.e. be a flexible means such as a line, wire or chain, which at one end is more or less wound around the anchor drum. A mechanism can be provided for rotating, for the second movements of the buoy or the other device, the anchor drum so that the flexible organ is kept in a tensioned state. Hereby, in can also be counteracted that the wave energy plant is moved away along the surface of the water. The mechanism can for example comprise a mechanical coupling between the energy accumulation device and the anchor drum or comprise an electric motor.

The bearing for the anchor drum, which only allows a unidirectional rotation around the driveshaft, at the same time allows the anchor drum, when rotating in the opposite direction, to drive the driveshaft to rotate in the opposite direction, which is the above said only one direction.

This bearing can comprise a coupling for limiting or disengaging the motive force with which the anchor drum then acts on the driveshaft.

A control system for controlling the electrical load of the electric generator can be provided that is arranged to adapt the rotational speed between the first and the second parts of the electric generator. In the case where the energy accumulation device comprises a counterweight or a floating body, control of the electrical load can also be used for adapt the vertical speed of the counterweight or of the floating body, respectively, whereby it also becomes possible for the counterweight or the floating body, respectively, to only move within an adapted or suitable vertical range. The control system can also be arranged to compensate for variations in the torque, which is caused by the inertia of the mass of the counterweight or the floating body, respectively, by adjustment of the rotation speed between first and the second parts of the electric generator. Hereby it can be achieved that the electric generator is capable of supplying a continuous, even power.

The wave energy converter may have one or more of the following characteristics and advantages:

1. Accumulation of energy according to the description above can be used for equalizing the energy of the water waves and thereby generate electricity at an even level, which gives a high capacity factor of the generator and associated power electronic circuits and connections, and a low complexity of the electric power system. 2. Excess energy from large waves can be accumulated and used over time to compensate for shortage in smaller waves, which contributes to the high capacity factor.

3. Absorption of energy from the water waves can be limited while full power can be maintained even during very heavy wave conditions. This contributes to the high capacity factor, but it also works as a very simple and efficient storm protection system where the wave energy plant all the time works in harmony with the waves, only absorbing the amount of energy that it has a capacity to convert.

4. The power output of the generator can be controlled by the fact that the rotation speed of the generator can be adapted to the average rotation speed of the driveshaft. This brings about that the wave energy plant can deliver an even power level in relation to the current wave climate. 5. The wave energy plant is highly scalable and its capacity and pattern producing electric power can be optimized for specific wave climates for the highest cost efficiency. 6. The wave energy plant has a completely mechanical transmission having a high efficiency, which in simple way converts the oscillating wave movements into a unidirectional rotation, well adapted to a standard electric generator having a rotating rotor. 7. The construction can for example mainly be made from concrete, a cheap material which is

well tested for ocean environment.

8. An electronically adjustable sliding clutch may be used, which is arranged to influence the winding of a line between a bottom foundation and the buoy and which also makes it possible to adjust the force which is needed to maintain the horizontal position of the wave energy plant. 5 Such a sliding clutch may replace and enhance the function of a counterweight, here called a lead, which is often used in similar constructions.

9. An anchor drum, which is mechanically connected to the driveshaft, can be used for more or less winding the second elongated means, according to the wave movements. Several revolutions of the anchor line can be wound around the anchor drum and hence it has no

10 technical limitations for wave heights that the installation can handle. The buoy follows the surface of the water in a harmonic way for all wave sizes without reaching any end position, which contributes to the fact that the wave energy plant can very efficiently absorb wave energy, in spite of varying wave heights and at the same time the strain on the construction during storm conditions is minimized.

15 10. Mechanical couplings may be provided, so that if the electrical generator is supplied with electric energy from an external source and acts as an electrical motor, the anchor drum can be controlled to move to perform a controlled winding of the line. This can confer to the wave energy plant the property that it can be assembled on shore before it is towed to the installation site thereof.

20 11. The installation can be done with a minimum of manual assistance. It is mainly only an electric cable that has to be manually connected, which can be done at the surface of the water from a boat. A bottom foundation, which is connected to the second elongated means, and the counterweight are attached to the buoy during transport to the installation site and then they can be released by control of mechanic couplings/locking devices.

25 12. The wave energy converter can easily be designed to be suitable for different installation depths.

13. A gearbox can be used to increase the rotation speed of the electrical generator, this allowing the use of a smaller and more resource efficient high speed generator. Such a gearbox can also make it possible to permanently fix the second part of the electric generator, the stator, to the

30 buoy, by connecting the gearbox to the counterweight drum, which can simplify the electrical connection and encapsulation of the generator and reduce the rotating mass in the construction.

Generally, as described above, a method of extracting electric energy from more or less periodic movement of a body, such as repeated upward and downward movements and/or tilting movements in two opposite directions can comprise the following steps.

35 - For first movements of the body, these movements can drive two parts of an electric generator

to rotate in relation to each other in a first direction and thereby generate electric current and at the same time provide mechanical energy to an energy accumulation device. - For second movements of the body, which are substantially different from the first movements, the energy accumulation device can drive the two parts of the electrical generator to rotate in the same first direction in relation to each other and thereby generate electric current having the same polarity as during the first movements of the body.

The transmission used in the wave energy converter as described above can independently be used in other cases of power generation, where a driveshaft is driven intermittently, with changing directions and/or with varying speeds and/or torques. Generally, the transmission then comprises a driveshaft that is arranged to be driven and that by some suitable device, if required, always can be made to rotate in one rotational direction. Furthermore, an electrical generator coupled to driveshaft is provided, which generator comprises two parts that can rotate in relation to each other, and an energy accumulation device. The driveshaft drives the two parts of the generator to rotate in relation to each other in a first direction and thereby generate electric current. The energy accumulation device is coupled with the driveshaft and the electric generator, so that the driveshaft by its rotation can also supply energy to the energy accumulation device and so that the energy accumulation device can later deliver its stored or accumulated energy to cooperate in driving the parts of the generator to rotate in the same first direction in relation to each other. Thereby, electric current can be generated having the same polarity, when the rotational speed and/or the torque of the driveshaft is/are insufficient to drive the parts of the generator to rotate at a maintained rotational speed.

In the transmission, the driveshaft can be mechanically connected to the first one of the parts of the electrical generator. In the generator there is, as conventionally, an electromagnetic coupling over an air gap between the first and the second part, at least during their movements in relation to each other, which the coupling gives some torque between the two parts. The energy accumulation device can in a first case be mechanically coupled to the second part included in the electrical generator.

Furthermore, in the transmission a gearbox, e.g. a planetary gearbox, can as described above be connected between the driveshaft and the generator, so that the driveshaft is mechanically connected to the input side of the gearbox or generally to a first rotational part of the gearbox. An output side of the gearbox or generally a second rotational part of the gearbox is then arranged to be driven from the outside to rotate with a varying rotational speed and/or torque in one rotational direction. One of the two parts of the electrical generator is mechanically coupled to another output side of the gearbox, generally a third rotational part of the gearbox, and the energy accumulation device is mechanically coupled to the second part of the generator.

The first and second rotational parts of the gearbox can then cooperate to for example drive the third rotational part of the gearbox to rotate with a rotational speed higher than the rotational speeds that each of the parts by itself can achieve when the other of these parts stands still or is not driven. The gearbox should in any case have the following functions:

- When the first rotational part is driven from the outside, the second and the third rotational parts are also made to rotate.

- When the first rotational part is not rotating, the third rotational part can drive the second rotational part to rotate. The first, second and third rotational parts can also be arranged to rotate around the same geometric rotational axis, i.e. be coaxially mounted.

Additional objects and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. The objects and advantages of the invention may be realized and obtained by means of the methods, processes, instrumentalities and combinations particularly pointed out in the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS

While the novel features of the invention are set forth with particularly in the appended claims, a complete understanding of the invention, both as to organization and content, and of the above and other features thereof may be gained from and the invention will be better appreciated from a consideration of the following detailed description of non-limiting embodiments presented hereinbelow with reference to the accompanying drawings, in which:

- Fig. 1 is a schematic image of a wave power installation comprising four separate wave energy plants, - Fig. 2a is a side view of a wave energy converter including a counterweight,

- Fig. 2b is a front view of the wave energy plant of Fig. 2a,

- Fig. 2c is a sectional view of a wave energy plant having an alternative suspension of a power train,

- Fig. 2d is a different sectional view of the wave energy plant of Fig. 2c, - Fig. 2e is a view from underneath only comprising a buoy including steering fins, an anchor drum and a counterweight drum according to Fig. 2c,

- Fig. 2f is a view from underneath of the wave energy plant of Fig. 2c which also shows an air pump,

- Fig. 2g is a top view of a power train for a wave energy converter mounted in a frame, - Fig. 3 a is a front view of a power train including winding drums, a driveshaft and a generator in

the wave energy plant of Fig. 2a,

- Fig. 3b is a view similar to Fig. 3a in which parts of a generator are schematically shown and in which a spiral spring is used as an energy accumulation device,

- Fig. 3 c is a front view of winding drums having specially designed winding surfaces, - Fig. 3d is a schematic of a power train comprising a generator having a stationary stator,

- Fig. 3e is a front view of a wave energy plant including a frame for interconnecting two counterweights,

- Fig. 3f is a top view of the frame of Fig. 3e for interconnecting two counterweights,

- Fig. 4 is a front view of the wave energy plant of Fig. 2a having a specially designed electric cable connection,

- Fig. 5a is a detail view of an anchor drum and its couplings located at the shaft,

- Fig. 5b is a view similar to Fig. 5a for a different design of the couplings,

- Fig. 5 c is a schematic of an anchor drum having couplings designed in yet another alternative way, - Fig. 5d is a diagram illustrating a control rule for engagement and disengagement of a slipper clutch,

- Fig. 5e is a schematic view of a claw clutch in an engaged state,

- Fig. 5f is a schematic view of a claw clutch in a disengaged state,

- Fig, 6 is a detail view of a mechanical coupling for return feed between an anchor drum and a counterweight drum,

- Fig. 7a is a front view of an alternatively designed wave energy plant including counterweights,

- Fig. 7b is a front view of an alternatively designed wave energy converter including buoys instead of counterweights,

- Fig. 7c is a front view of yet another alternatively designed wave energy converter including counterweights located above the water surface,

- Fig. 7d is a front view of a wave energy plant having an alternative driving operation of the driveshaft by cooperation with a weight suspended in an elastic means,

- Fig. 8a is a front view of a combined wind and wave energy plant,

- Fig. 8b is a side view of the combined wind and wave energy plant of Fig. 8a, - Fig. 8c is a detail view of a power train comprised in the combined wind and wave energy plant of Fig. 8b,

- Fig. 8d is a front view of a wind power plant, in which a transmission of the same kind is used,

- Fig. 8e is a side view of the wind power plant of Fig. 8d,

- Fig. 8f is a detail view of the wind power plant of Fig. 8e having a pneumatic energy accumulation device,

- Fig. 9a is a front view of a wave energy plant having an energy accumulation device designed as an elastic means,

- Fig. 9b shows an alternative connection of the elastic means of Fig. 9a,

- Fig. 10a is a schematic front view of a wave energy plant including an energy accumulation device and a return feed mechanism,

- Fig. 10b is a view similar to Fig. 10a of a wave energy plant converter using the torque which is transferred over the air gap of a generator to obtain energy accumulation,

- Fig. 1 Ia is a schematic of a previously known device for driving a generator in a wave energy plant, - Fig. l ib is an schematic similar to Fig. 11a but of a differently designed device for driving a generator having a stator that also is rotating,

- Fig. 1 Ic is a view from a different side of the device of Fig. 1 Ib,

- Fig. Hd is a schematic similar to Fig. l ib of a device arranged in a different way design for driving a generator having a stationary stator, - Fig. 1 Ie is a view from a different side of the device of Fig. 1 Id,

- Fig. 12a and 12b are views from two sides, illustrating the construction and function of a planetary gear,

- Fig. 12c and 12d are schematic views, illustrating the construction of a variable mechanical gear (CVT/CVET), - Fig. 12e is a view of a planetary gear and a variable gear which are coupled with a generator in a power train,

- Fig. 13a is a front view of a power train having steering rollers for the guidance of lines,

- Fig. 13b is a side view of the power train of Fig. 13a,

- Fig. 13c is a bottom view of the power train of Fig. 13a, - Fig. 14 is a bottom view of a power train including only one generator mounted in a buoy,

- Fig. 15a is a front view of a wave energy plant having an alternative design of a power train including only one generator, the stator of which rotates together with the counterweight drum, one counterweight and an alternative guide mechanism for an anchor line,

- Fig. 15b is a side view of the wave energy plant of to Fig. 15a, - Fig. 15c is a front view of a wave energy plant of Fig. 15a having a different type of divided anchor line,

- Fig. 15d is a side view of the wave energy plant of Fig. 15c,

- Fig. 15e is a bottom view of the power train of the wave energy converter of Fig. 15a,

- Fig. 15f is a bottom view similar to Fig. 15e but including a power train in which the stator of the generator is rigidly attached to the buoy,

- Fig. 15g is a bottom view of a power train similar to Fig. 15f, in which the mechanical components are encapsulated to a larger extent,

- Fig. 15h is a front view of the power train of Fig. 15g,

- Fig. 15i is a view similar to Fig. 15g, in which a return feed mechanism in the power train is driven by an electric motor,

- Fig. 16a is a diagram illustrating a control rule for compensating for varying accelerations and decelerations of the counterweight using the load of the generator,

- Fig. 16b is a diagram illustrating a control rule for compensating for varying accelerations and decelerations of the counterweight using a CVT, and - Fig. 16c is a diagram illustrating a control rule for compensating for varying accelerations and decelerations of the counterweight using the sliding clutch of the return feed mechanism. DETAILED DESCRIPTION

In Fig. 1 , a wave power installation is shown for extraction of energy from the movements of waves at a water surface 6 of a pool of water, e.g. movements of water in a ocean. The wave power installation comprises one or more wave energy plants 1, each including a buoy or a floating body 3, which is located at the water surface, e.g. floating thereon, and which to a higher or lower degree follows the movements of the waves. In the upwards and downwards movements of the water surface 6 the buoy is made to alternating raise or sink and/or alternating tilt back and forth. Thereby a motive force can be created, in the case shown in relation to the bottom 8 of the water pool, such as a part rigidly attached to the bottom, e.g. a bottom foundation 5, which can have a mass large enough to keep it steadily on the bottom. If required, the bottom foundation can of course be attached to the bottom in some way and it may then comprise a simple fastening device having a low mass, not shown. As can be better seen in Figs. 2a and 2b the buoy 3 and the bottom foundation - alternatively the bottom fastening device - are connected to each other by an anchor line 7, e.g. a steel wire. The motive force can as an alternative be created in relation to some kind of movable object such as to a weight suspended in the buoy, see Fig. 7d.

In the shown embodiment the anchor line 7 is at one end attached to the foundation 5 and is at its opposite end attached to a power train 2 and more or less wound around a first winding drum, an anchor drum 9, included in the power train, the winding drum being mounted to rotate about a driveshaft 11. The driveshaft 11 is in a suitable way journalled at the buoy 3. As shown in Figs. 2a and 2b the buoy can at its bottom side comprise downwards protruding stays 13, which can be said to constitute a frame and at which the driveshaft 11 is journalled, e.g. at its two ends. On the driveshaft, in the embodiment shown in these figures, there is also a second winding drum, a counterweight drum 15, on which a line 17 is partly wound at its upper end. The

counterweight line 7 carries at its lower end a counterweight 19. The cylindrical surface of the counterweight drum, on which the line for the counterweight is wound, has in the shown embodiment a diameter that is larger than that of the cylindrical surface of the anchor drum 9, on which the anchor line 7 from the bottom foundation 5 is wound. The first mentioned diameter can e.g. be considerably larger than the latter one, such as a relation in the magnitude of order of 2:1 to 3: 1, but does not have to. The winding drums can also have the same diameter when suitable.

Instead of having the power train 2 mounted under the buoy 3, as shown in Figs. 2a and 2b, the power train can be mounted in a recess in the buoy, a power train room 20, as shown in Figs. 2c, 2d and 2e. Then, the driveshaft 1 1 can be mounted in a substantially central position in the buoy. The stays 13 can be attached to walls of the power train room 20.

Thus, the anchor line 7 and the counterweight 19 are not directly connected to each other as in earlier known constructions. In the earlier known constructions, see the principle picture of Fig. 11a, half the motive force of the buoy 3 is accumulated in the rise of the wave by while the anchor line 7 running over the anchor drum 9', so that a generator 21 for generating electric current can be driven also when the wave thereafter sinks. In the latter case, the generator is either driven in a reverse direction or the rotation movement is rectified by a mechanical or hydraulic transmission solution, not shown. However, in both cases the generator 21 remains to be direct driven according to the momentary vertical movement of the wave. As appears from Figs, l ib and l ie the generator can instead be connected to be driven between the counterweight 19 and the anchor drum 9, so that e.g. a first part of the generator, not shown in these figures, typically corresponding the inner rotating part, the rotor, of a conventionally mounted generator, on one side of the air gap of the generator, not shown, is mechanically connected to the anchor drum and a second part of the generator, not shown in these figures, typically corresponding to the outer stationary part of the generator, the stator, in a conventionally mounted generator, on the other side of the air gap, is mechanically connected to the movements of the counterweight, so that this part can also rotate. Hereby the generator 21 can be driven from two sides with a maintained relative rotational direction between its first part and its second part. When the wave and the buoy 3 raises, the driveshaft 11 is turned forwards by the anchor line 7, which runs around the driveshaft via the anchor drum 9 and which at its other end is anchored to the bottom 8, e.g. to a foundation 5. The counterweight 19 is used to create a resilient resisting force and thereby gives an even torque between the counterweight drum 15 and the driveshaft 11 , which in that way drives the first part and second part of the generator in relation to each other. It is also possible to use other methods to achieve such a driving operation, e.g. gas pressure or a spring for providing a constant force, as will be described below.

In Figs. 1 Ia, 1 Ib, and 1 Ic the arrows 111 show absorption of wave energy. The absorption level varies according to the momentary movement and movement direction of the wave. When the driveshaft 11 is turned forwards by the anchor drum 9, also the generator 21 follows the rotation, so that the counterweight line 17 starts to be wound around the counter weight drum 15, which can be a part of or be rigidly attached to the second part of the generator, see the arrows 113, and so that the counterweight is moved upwards. Hereby, potential energy is stored in the counterweight at the same time as a torque appears over the generator (torque = weight of the counterweight * acceleration of gravity (i.e. the gravitational force acting on the counterweight) * radius of the counterweight drum). The torque makes the second part of the generator start rotating in relation to the first part, which is mechanically connected to the driveshaft 11, so that the counterweight line 17 starts to unwind from the counterweight drum 15, and hereby potential energy accumulated in the counterweight 19 is converted to electricity, see the arrows 115. The faster the generator parts rotate in relation to each other, the more electric power is generated, and then also a higher counteracting force is obtained in the generator 21, i.e. the electromagnetic coupling between the two parts of the generator becomes stronger. When the counterweight 19 reaches a certain velocity, the pulling force from the counterweight becomes equal to the counteracting force in the generator, this resulting in that the rotation speed of the generator and the power output from the generator is stabilized in an equilibrium state.

This way of connecting and driving the generator 21 can give great advantages, since the generator can be used much more efficiently compared to what have been earlier possible. The same relative rotational direction between the generator parts is maintained all the time and the generated electric power is kept at a substantially even level, which requires a minimum of subsequent electric treatment of the electrical voltage generated by the generator. The arrangement of the generator can also give advantages from a storm safety point of view, since the motive force over the generator and transmission is limited.

The design of the transmission unit 2 and the function thereof will now be described in more detail with reference in particular to Figs. 2a, 2b and 3a.

During the movements of the waves the distance between the buoy 3 and the bottom foundation/bottom fastening device varies. The anchor drum 9 is turned, due to the coupling with the anchor line 7, in a first direction when the water surface 6 rises, and is then locked to the driveshaft 11 , which thereby is rotated by the anchor drum. When the water surface at the buoy sinks, the driveshaft is locked from rotating backwards in the opposite direction by anti-reverse mechanisms 53 in the shaft stays 13, see Figs. 5a and 5b. To be capable of turning the anchor drum backwards, in a second, opposite direction, and to keep the anchor line in a tensed state when the water level 6 at the buoy 3 sinks, a return feed mechanism of some kind sort is required

as will be described below. The driveshaft 11 is in turn connected to the generator 21. The coupling between the driveshaft and the generator can be fixed or it can as illustrated comprise a mechanical gear 23, which e.g. has a fixed teeth relation or fixed gear ratio, and which gears up the rotation speed of the generator. Hereby one of the parts of generator that are rotatable in relation to each other, here for the sake of simplicity called rotor and stator, e.g. an inner generator rotor 21 ', compare Fig. 3 a, to rotate in the first direction. The other rotatable part of the generator, e.g. an outer stator 21" is rigidly mounted to the counterweight drum 15. The generator parts are separated by an air gap 21 "'.

Due to the winding of the counterweight line 17 around the counterweight drum 15 during the forward feeding of the driveshaft 11, a relatively constant motive force or a relatively constant torque acting on the driveshaft 11 is achieved, which through the connection between the rotor 21' and the stator 21" of the generator 21 drives the generator to rotate and generate electric current. When the torque from the anchor drum 9 exceeds the counteracting torque, that is derived from the electromagnetic coupling over the air gap between the rotor and the stator of the generator, when these parts are rotating in relation to each other, more of the counterweight line 17 is wound around the counterweight drum 15 and the excess energy, to which this higher torque corresponds, is accordingly accumulated the hoistening of the counterweight 19. Thereafter, when the buoy 3 starts to rise with a decreasing speed, to thereupon sink when the water surface 6 sinks, also the rotational speed of the driveshaft 11 and the rotor 21 ^' in the first rotational direction is also reduced. When the torque from the anchor drum 9 becomes lower than the counteracting torque in the generator 21 according to the discussion above, the counterweight line 17 starts to unwind from the counterweight drum at an increasing speed, until of the driveshaft is blocked from rotating in the reverse direction by an anti-reverse mechanism 53 in the driveshaft stay 13, see Figs. 5a and 5b, and the speed of the backward rotation of the counterweight drum is stabilized by the equilibrium state between the generator and the counterweight 19. The potential energy accumulated in the counterweight hence continues to drive the generator 21 also in this phase, with a correspondingly even torque as in the previous phase.

As has been mentioned above, the wave energy is absorbed from the traction force that arises between the buoy 3 and the bottom foundation/bottom fastening device 3 during the rise of the wave. The buoy 3 follows the movements of the wave and thereby moves the driveshaft 11 , on which the anchor drum 9 is mounted, upwards in relation to the bottom foundation. A rotational movement arises which drives the transmission. The vertical movement of the wave is converted into a rotational movement, the speed of which can then be geared up to be suitable for driving the generator 21. It is the speed of the vertical movement of the wave that determines

the amount of energy that can be extracted. The bigger wave, the faster vertical movement and the more energy can be absorbed. Different from the energy in the wave, the vertical speed of the movement does not increase with the square of the wave height, but follows a more linear pattern. But the larger the wave is, the less impact has the attenuating effect of the buoy 3, this resulting in that the vertical movement and the motive force of the buoy rapidly increase when the wave height increases from a low level to level out towards the linear pattern the higher the wave becomes.

The anchor drum 9 is in a suitable way mechanically connected to the drive shaft 1 1. Such a mechanical coupling can include the following two functions. 1. During the rise of the wave the anchor drum 9 shall hook on to the drive shaft 11 , so that the driveshaft is rotated together with the rotational movement of the anchor drum. When the wave sinks, it shall be possible to disengage the anchor drum, so that the anchor drum can be rotated in the reverse direction. Furthermore, the driveshaft 11 shall be blocked from changing its rotational direction when the wave sinks. The drive shaft is in this manner fed forward by the anchor drum in the same rotational direction every time the wave rises and the motive force, and thereby rectifies the motive force absorbed from the wave motions. This makes it possible to drive the generator in a single rotational direction.

2. The absorption of wave energy can be limited by the use of a sliding clutch 55, which consequently can word as an overload protection, see Figs. 5a, 5b and 5c. Such a sliding clutch also makes it possible to completely disengage the absorption of energy from the movements of the waves, by letting the anchor drum 9 slide against the driveshaft 11 during the rise of the wave, when the accumulation level reaches its upper limit, i.e. when it is not possible to wind more of the counterweight line 17 around the counterweight drum 15 without risking that the counterweight 19 comes to close to and damages the counterweight drum 15 and the buoy 3. The sliding clutch can also be used to limit the torque to which the transmission is submitted. When the wave sinks, the buoy 3 and the counterweight 19 will be retarded, which gives an increased g- force and hence an increased torque in the transmission. When the wave turns and rises again, the g-force will increase further by the anchor drum 9 starting to be turned forward and lifting the counterweight in relation to the buoy at the same time as the buoy is lifted by the wave. For a too high load the sliding clutch slides and thereby somewhat reduces the acceleration, which in turn also reduces the torque to which the transmission is submitted.

A mechanical coupling between the anchor drum 9 and the driveshaft 11, which provides these functions, can be designed in different ways. Such a coupling can comprise one or more anti-reverse mechanisms and a sliding clutch as will be described below. Thus a freewheel mechanism or an anti-reverse mechanism 51, see Fig 5 a, for the coupling

of the driveshaft 11 to the anchor drum can be provided, which is herein called the anti-reverse mechanism of the anchor drum. In this case, the driveshaft passes through the anchor drum undivided. The anti-reverse mechanism 51 of the anchor drum can be designed like a one way bearing, which is mounted around the driveshaft. When the buoy 3 rises, the anchor drum 9 and the driveshaft 11 is turned, as above, in the first rotational direction, by way of the anchor drum hooking on to the driveshaft with the use of this return blocking mechanism 51. When the buoy 3 sinks, the return blocking mechanism in the anchor drum 9 is released and the anchor drum 9 can be reversed, rotated in the opposite rotational direction, to wind up the anchor line 7, such as will be described below, meanwhile the driveshaft 11 is blocked from rotating in the opposite rotational direction by another return blocking mechanism 53, which is acting between the driveshaft and the stay 13 and which is here called the shaft stay return blocking mechanism 53. This return blocking mechanism can be arranged at or in the stay bearing 54 for the driveshaft 11. In this way the driveshaft is always turned in the first rotation direction every time the buoy 3 rises and it can never be turned in the opposite direction. If so is required, the transmission unit 2 can be designed, so that motive force, with which the anchor drum 9 acts on the driveshaft 11, can be disengaged also in the first rotational direction. This can be achieved by a controllable return blocking mechanism 51 of the anchor drum, or preferably with the use of a sliding clutch 55 for the anchor drum, as will be described below. The drive of the driveshaft 11 can then be disengaged, when the accumulation of energy reaches its maximum accumulation level, i.e. when the counter-weight 19 cannot be hoisted up any higher without the risk of damaging the anchor drum 15 and/or the buoy 9. This disengagement of the drive of the driveshaft is then ended, when the buoy 3 starts sinking, so that the anchor drum 9 drives the driveshaft 11 anew when the wave starts rising again. The energy absorption of the wave energy converter is hereby limited and overload of the transmission and the generator 21 can be prevented, when the average wave height exceeds the level, at which the wave energy converter reaches its maximum capacity, i.e. rated power. Even though the energy absorption is hereby temporarily disengaged, the generator can be driven to produce maximum power output, as long as the potential energy stored in the counterweight can be used. The load on the generator 21 and the transmission 23 can hereby be limited at the same time as maximum power output can be maintained, as soon as the average energy level in the waves is high enough.

An alternative method for disengagement of the driveshaft 11 from the anchor drum 9, to limit the energy absorption, is that both engagement and disengagement is done when the torque, which is transferred between the anchor drum and the driveshaft, is zero. In this case a claw coupling 55" can be used instead of a sliding clutch, see Figs. 5e and 5f. When the

counterweight 19 has exceeded an upper limit, the claw coupling is disengaged as soon as the torque has been reduced to zero, see fig 5f. The claw coupling is engaged again, see Fig. 5e, when the counterweight has reached a certain lower limit, and when the torque is zero again, which may be several wave periods later. The upper limit, as above, must provide enough safety margins so that the counterweight 19 doesn't reach the counterweight drum 15 even if an extreme wave comes. Advantages with this method includes that the disengagement mechanism can manage a higher torque being transferred, low energy consumption only during transition, and minimum of mechanical wear from the disengagement. The disadvantage is that a longer counterweight line 17 is required, which can be limiting in some cases. The anchor drum's 9 sliding clutch 55 can be mounted between the anchor drum's return blocking mechanism 51 and the anchor drum, as schematically shown in Fig. 5 a. The by the sliding clutch transferred torque between the anchor drum and the drive shaft 1 1 can preferably be controllable in accordance with some suitable electrical signal, by which the maximum energy absorption level in the system can be adjusted. In an alternative design the mechanical return blocking mechanism of the anchor drum 51 , does not exist, see Fig. 5b. The driveshaft 11 is also in this case passing through the anchor drum 9 undivided. Instead the anchor drum's sliding clutch 55 is used as a return blocking mechanism. The sliding clutch is mounted around the drive shaft 11 with one of its coupling sides and mounted to the anchor drum 9 with its other coupling side. The torque transfer in the sliding clutch 55 is controlled to also give the function of a return blocking mechanism.

In yet another alternative design there is a detached sliding clutch 55 ' without mechanical return blocking mechanism, see Fig. 5c. The driveshaft 11 is in this case divided and the anchor drum 9 is firmly attached to the first part of the driveshaft 1 1 '. There is a sliding clutch 55' between the first part 1 1 ' and its second part 1 1 " of the driveshaft, to the side of the anchor drum. The first part of the shaft 11 ' is journalled in bearing to an inner stay 13 ' between the anchor drum and the sliding clutch at bearing 54'. The sliding clutch 55 ' is, as above, used as a return blocking mechanism and its torque transfer is controlled in the same way as when the sliding clutch is enclosed in the anchor drum 9.

When the sliding clutch 55, 55' is used as a return blocking mechanism, it can be controlled as visualized in Fig. 5d. It then alternates between transferring full torque and no torque at all. The anchor drum 9 rotates forward, meanwhile the wave is rising, and is then fed backwards by the below described return feeding mechanism, when the wave is sinking. The alternation in torque transfer hence occurs when the rotational direction of the anchor drum is turned. The rotation of the anchor drum 9 and the rotation of the counterweight drum 15 can also

be coupled via a mechanical coupling, the above mentioned return feeding mechanism, beside with the help of the electromagnetic coupling through the generator 21. This can be achieved with help of, among other things, a second sliding clutch 25, here called the return feeding sliding clutch, see Fig. 6, which is used for controlling the level of torque, which shall be transferred from the counterweight drum to the anchor drum. The level of this torque can also be adjustable or dirigible. This torque can be used to reverse the anchor drum 9 and by that secure that the anchor line 7 to the bottom foundation 5 is kept in a tensed state, meanwhile the buoy 3 sinks. This torque can also be used for counteracting the driftage of the buoy, away from the sea floor foundation, due to currents and wind at the water surface 6. The return feeding sliding clutch 25 can as shown be mounted in one of the stays 13, in which the driveshaft 11 is journalled in bearings. Gearwheel 27, 29 runs against the edges 31, 33 on the wind up drums 9 and 15 respectively and these edges can then in the corresponding way be toothed. The gearwheels 27 and 29 is connected to the input- and output- shafts of the sliding clutch 25 and their size in relation to the gearwheels 31, 33 at each wind up drum respectively, is adapted to provide high enough gear ratio for the rotation speed of the anchor drum 9 to be high enough to wind up the anchor line 7 fast enough to keep it tense, when the floating body 3 sinks as fastest. In the shown design the gearwheels 27, 29 is coaxially journalled in bearings and directly connected to the two clutch disks 57 in the return feeding sliding clutch 25, which are pressed against each other with a controllable force, so that when so is required, a torque of desirable magnitude can be transferred between the counterweight drum 15 and the anchor drum 9. One alternative return feeding mechanism for the anchor drum is to use an electrical motor in a corresponding way as shown in Fig. 15i.

The gear 23, that connects the driveshaft 11 to the generator 21, can give a stepped up rotational speed of the driveshaft so that a higher rotational speed in the generator is obtained, which enables the use of a high speed generator. Since the power output from the generator is proportional to the mass of its rotor 21 ' and its stator 21 " and to the rotational speed of the generator, this is of very high importance. Further on, the gear 23 can in general be or comprise a variable gear, where it can comprise e.g. a gear with fixed gear ratio such as a planetary gear 35, arranged as input stage, see Fig. 12e. The outgoing shaft of the planetary gear is then connected to the input shaft of a variable gear 37 (CVT), of which output shaft is connected to the first of the generator's part, like its rotor 21 '. The generator stator 21 ", and the casing of these gears is fixed to each other and the counterweight drum 15 and can rotate freely as one unit around the driveshaft 11. The gear ratio between the driveshaft 11 and the first part of the generator 21 ^' is in this case given by the product of the gear ratio of the planetary gear 35 and the gear ratio of the variable gear 37.

The maximum rotational speed, that the generator 21 can handle, depends on the choice of generator. A suitable range for the generator's nominal rotational speed is around 1500 to 3000 rpm depending on its maximum capacity, for which the wave energy converter 1 is dimensioned. To gear up the generator to such a rotational speed a gear ratio in the magnitude of 100 to 200 times is required, where the gear ratio also depends on the radius of the anchor drum and the medium motion speed of the buoy where full power shall be reached. When the rotational speed is stepped up, the torque is at the same time stepped down with the same gear ratio, which brings a very high input torques in the gear 23. A high gear ratio can cause high transmission losses. A planetary gear 35 as above provides a high fixed gear ratio, can manage very high input torques and has a good efficiency. The variable gear stage in the gear 37 can be used to adapt the generator's revolution speed to the actual medium wave height. Such a variable gear can e.g. be a step less variable gearbox or a hydraulic gearbox.

Alternatively, the transmission unit 2 can be designed with other mechanisms for accumulation of energy from the rise of the water surface 6, e.g. as elastically stored energy. Any counterweight is then not required, and can instead be replaced by a spring, typically a coil spring 69, see Fig. 3b. The inner end of such a coil spring is then mounted to the stay 13, while its outer end is mounted to the casing of the gear 23 and is thereby coupled with the generator 21 , to its second part. Energy can also be accumulated as gas pressure which will be described below. In the so far described designs, one single anchor drum 9 and two counterweight drums 15 located on either side of the anchor drum can exist, as shown in the corresponding figures. One gear unit 23 and one generator 21 is included in each counterweight drum. One counterweight drum 15 is hence connected to either end of the driveshaft 11 , i.e. the driveshaft is mounted between the two counterweight drums and the driveshaft is journalled in bearings in the stay or the frame 13.

The movements of the two counterweight drums 15 can be synchronized with the use of a link shaft 58, that is journalled in bearings in the stay 13 parts and has gearwheels 29 at both its ends, which concurs with the toothed edges of the counterweight flanges 33, see Fig. 2f. The generator arrangements 21 are freestanding but the counterweight 19 must be kept on the same horizontal level so that the distance between the counterweight and the anchor drum is the same in both arrangements. Otherwise the centre of gravity in the wave energy converter 1 can be displaced, so that the power unit can turn in a faulty manner against the waves, with deteriorated capture ratio between the waves and the buoy 3 as a consequence. The link shaft 58 is in the showed design also used for achieving the return feeding mechanism from the counterweight drums 15 to the anchor drum 9. For this it also has a gearwheel 27, which concurs with a ring

gear on one of the anchor drums flanges 33 in a similar way as for the return feeding mechanism shown in Fig. 6.

The motion of the two counterweight drums 15 can be synchronized thanks to a link shaft 58 which is journalled in bearings in the stay 13 parts and has gearwheels 29 at both ends, which concur with gear rings on the counterweight drums' flanges 33, see Fig. 2f. The generator arrangements 21 are freestanding but the counterweights 19 must be kept on the same horizontal level, so that the distance between the counterweight and anchor drum is the same in both arrangements. In other case the wave energy converter's 1 centre of gravity may be displaced, so that the wave energy converter can turn incorrectly towards the waves with decreased power transfer between the wave and the buoy as a consequence. The link shaft 58 is in the presented design also used for achieving the return feeding from the counterweight drums 15 to the anchor drum 9. For this purpose it also has a gearwheel 27, which concur with a gear ring on one of the anchor drum's flanges 33 in a similar way as for the in Fig. 6 presented return feeding mechanism. Since the link shaft 58 is made in one piece, to be able to rigidly connect the rotational motion of the counterweight drums 15, another type of sliding clutch for the return feeding mechanism must be used. The sliding clutch of the return feeding mechanism 25 ' is in this case located between the larger gearwheels 27, which concurs with the flanges 31 of the anchor drums 9, and the through going link shaft 58, at which the gearwheels are fixedly mounted. Instead of driving with the help of concurring gearwheels as shown in the figures, a belt-drive or chain-drive can for example be used.

The stay 13 includes in the designs in accordance with Figs. 2a - 2b two from the buoy's 3 underside protruding stay parts, each of which includes a bearing 54 with a return blocking mechanism 53 for the driveshaft 11, also compare Figs. 5a and 5b. Such a design of the transmission unit 2 with an along the driveshaft centralized anchor drum 9 and on both sides of this arranged counterweight drums 15 with belonging gear 23 and generator 21, gives a symmetrical weight load on the buoy and also a more symmetrical load due to currents in the water compared to the case where only one counterweight drum with belonging generator and counterweight 19 is used, which is connected to one end of the driveshaft 11. The transmission unit 2 with the anchor drum 9, the driveshaft 1 1, the counterweight drums 15, the gear mechanisms 23 and the generators 21, can as an alternative be carried in a machine body or in a driveshaft frame 141, as shown in Fig. 2g. The machine body includes a surrounding frame shaped part 143 and a number of shaft stays 145, which runs between the long, opposite sides of the frame part and which corresponds to the above described stays or stay parts 13. The shafts of the transmission unit are journalled in bearings in the shaft stays. The

number of shaft stays is dependent on different design alternatives. The frame 141 is secured to the buoy.

In the case where a planetary gear 35 is used, a somewhat different design is possible. A planetary gear is composed by a planet carrier 161, at which a number of planet gears 163 are journalled in bearings in an orbit on the inside of a ring gear 165 and around a sun gear 167, at which the planet gears are in gear wheel engagement, see Fig. 12a. When the planet carrier rotates and the outer wheel, the ring gear, is fixed, the planet holder drives the inner wheel, the sun gear, to rotate, which steps up the rotation speed? Alternatively the sun gear 167 can be driven by the rotation of the ring gear 165 while the planet holder 161 is held in a fixed position, which also steps up the rotation speed. As above, this can be utilized, so that the planetary gear 35 and the generator 21 e.g. is located inside the counterweight drum 15 and at first hand so that both the planetary gear's ring gear 165 and the generator 21 " are fixed to the counterweight drum, compare e.g. Fig. 2b.

Alternatively only the planetary gear 35 can be located inside the counterweight drum 15 with the ring gear 165 fixed with the counterweight drum. The generator stator 21 " is then instead fixed to the buoy 3 as with the frame 141, see Fig. 2g and also Fig. 3d. The drive shaft 11 is journalled in bearings and can rotate freely both at the entrance and exit of the counterweight drum. The shaft load, which is given by the counterweight 19, is taken up by the driveshaft, which is carried by the shaft stay 145 in the driveshaft frame 141. The planetary gear 35 thereby gets a low shaft load. The system function remains the same but such a design can simplify the electrical connection and encapsulation of the generator 21 and also simplify the access at service and maintenance. The levy in mass can also be reduced, i.e. the total angular momentum, since the stator 21 " in this case doesn't need to be rotated, which can be of some significance. Also other types of gearboxes can be used in a similar way, at which e.g. the casing or the cover of the gearbox is fixed with the counterweight drum 15. A planetary gear's ring gear in this case corresponds to the gearbox's house or casing.

The gear ratio in a planetary gear is given by the difference between the number of teeth on the planet gear and the sun gear. In Fig. 12a a planetary gear is shown with one gear steps but it is possible to build in additional gear steps. This can then be according to the principle that two or more planetary gears are coupled with the ring gears fixed to each other. Up to three steps are commonly used which gives relatively low transmission losses. Every step is usually chosen with a gear ratio between 5 and 10, which gives a gear ratio up to 300 with three steps. The higher power the wave energy converter 1 is dimensioned for, the larger diameter the anchor drum 9 needs to have, since the anchor line 7 requires a larger diameter at larger dimensions. An increased diameter of the anchor drum leads to lower rotation speed in relation to the vertical

motion of the wave, which leads to that a wave energy converter with larger capacity require a higher gear ratio to achieve the correspondent rotation speed in the generator 21.

In Figs. Hd and l ie is in the same way as in Figs, l ib and l ie schematically presented how the drive of the generator 21 can be achieved for a generator with a with the buoy 3 fixed stator.

The buoy 3 will at the wave motions apart from moving vertically also always change its angular orientation around a horizontal position, which is taken at a completely calm sea. The driveshaft 1 1 then rocks sideways all the time, which can get the anchor line 7 and the counterweight line/lines 17 to slide and rub against each other on the anchor drum 9 and the counterweight drum/drums 15. A track guiding mechanism can then be used, which see to it that resp. lines are winded up in a regularly way. One possibility is to use helicoidal grooves 39, 41, 43, 45 on the drums' 9, 15 cylindrical winding up surfaces, see Fig. 3c. When two counterweight drums are utilized, the direction of their helicoidal grooves can be opposite, i.e. one of the helicoidal grooves 39, 41 is right handed while the other helicoidal grooves 43, 45 is left handed, to maintain a symmetrical load on the wave energy converter 1, due to the motive force relating to the counterweights 19 and the anchor line 7, to some extent. Helicoidal grooves according to 39, 41, 43 and 45 with a shape that follows the profile of the lines can also significantly increase the length of life of the lines since the contact surface between line resp. the wind up drum is increased. If only one anchor line 7 is used, the point where this line affects the anchor drum 9 is moved along the axis, when the line is more or less is winded up and unwound. To achieve a more symmetrical load in the case with two counterweight drums 15 the anchor line 7 ^' can be in a loop, so that it runs from one side of the anchor drum at helicoidal groove 41 , down to the sea- floor foundation 5 and via a pulley 40, which is journalled in bearing to the sea- floor foundation 5, and back up again to the other side of the anchor drum via helicoidal groove 43. The anchor line is then in both its ends more or less winded up on the anchor drum wind up surface in two segments with helicoidal grooves 41 and 43, which have helicoidal grooves in opposite directions. It is also possible to divide the anchor line by a Y-coupling located a distance under the wave energy converter, see Fig. 15a and the description below. As will be described below, two anchor drums 9v, 9h can be placed on either side of a centrally located counterweight drum 15. Helicoidal grooves for resp. line 7, 17 can then be arranged in a way corresponding to what is shown in fig 3 c. The counterweight drum can then have two segments with helicoidal grooves with opposite directions, this is not shown.

As an alternative or a complement to the helicoidal grooves on the winding up drums 9, 15 guide rollers 171 can be used to guide both counterweight lines 17 and the anchor line 7 around

resp. wind up drum, see Figs. 13a, 13b and 13c. The guide rollers are driven by threaded rods

173, which are rotated in pace with the drums. The threaded rods for resp. counterweight drum 15 has screw-threads in the opposite direction as seen in Fig. 13 a, so that the counterweight lines 17 is guided in opposite direction to each other, which is important for the centre of gravity of the wave energy converter to remain centralized.

Two threaded rods 171 are used for each winding up drum 9, 15 and these two are rotated by a common teeth belt or chain 175, which turns belt- or chain-wheels 177. The guide ends of the guide rollers 171 are connected to end pieces 179, through which the threaded rods passes and which guides the guide rollers along the threaded rods. The guided rollers are journalled in bearings at the end pieces and can rotate along with resp. line 7, 17 to minimize friction and wear. The ends of the threaded rods 173 are journalled in bearings at the driveshaft stay 141.

Yet another alternative to achieve safe wind up is to use trawl drums, not shown, as is known from the fishing industry.

To minimize the risk that the counterweights 19, in the case where two counterweights are used, and their lines 17 tangled with each other the counterweights can be mechanically connected together by a suitable stiff mechanical structure, which holds them physically separated from each other. E.g. a counterweight frame 151 can be used, see Figs. 3e and 3f. The counterweight frame can be shaped so that it does not rub against the anchor line 7 and also prevent entanglement with it, e.g. with a rectangular, quadratic or rhombic shape according to Fig. 3 for with the shape of a closed curve, such as a round curve, not shown.

The buoy 3 can generally have the shape of a plate, which can be oblong. Such an oblong plate can then in a convenient way be positioned, so that it mostly has its longer end towards the wave direction. The width of the buoy 3 can be adapted to the average wave length of the waves at the sea surface, so that the buoy has a larger width at larger medium wave length. Different methods can be used to stabilize the buoys' position in relation to the wave direction. The rotating motion of the water particles through the waves in combination with the traction force towards the centre above the foundation 5 can be utilized by introducing fins, see Figs. 2d and 2e. on the buoy's 3 underside. Further the buoy's shape can be adapted. The driveshaft 11 can instead of being centralized under the buoy as shown in Figs. 2a and 2b, in parallel with the plates length going direction, be a bit displaced in the direction towards the waves.

For the mounting of the transmission unit 2 inside the buoy 3, as shown in fig 2c, 2d and 2e, the buoy must have such a size, that it can hold the transmission unit. Seen from the side, in parallel with the driveshaft 11 the buoy can in this case have the shape in the form of an ellipse, i.e. generally an elliptic cylinder. It can have a relatively large section area against the water surface 6 at the same time as it can be pulled against the wave direction with less water

resistance compared to a completely rectangular section area. The buoy 3 can have one or more fins 4 in its back part, seen from the wave direction, which can contribute to steering the buoy straight against the wave direction.

The transmission unit 2 in this design can be mounted in the transmission unit space 20, whereby the transmission unit in whole or partly can be made dry and thereby be protected against growth and corrosion and a simpler and cheaper sealing solutions can also be used, see Figs. 2c, 2d, 2e and 2f. When the transmission unit space 20 is made dry, it also contributes with its buoyancy to the buoyancy of the buoy 3. The transmission unit space can for this purpose at the top be sealed by a cover or a service hatch 121, so that the transmission unit space constitutes an air pocket. To create and maintain the drainage of the transmission unit space 20 an air pump 123 can be used. The air pump can be driven by the link shaft 58, e.g. through a belt 125, and pump air into the transmission unit space which gets the water level to be pushed down, so that the transmission unit 2 is maid dry and the desired air pocket is achieved. The air pump can be mounted at one of the shaft frames 145, at which the driveshaft 11 is journalled in bearings. The air pump 123 can alternatively be driven by an electrical motor, not shown.

When the wave energy converter is taken into operation, the service hatch 121 over the transmission unit 2 is closed and the water level in the transmission unit space 20 is pushed down by the air pressure, which the air pump 123 produces. The water level outside varies during the wave period correspondingly to the motive force between the sea floor foundation 5 and the wave and also the mass-moment of inertia in counterweight 19 and buoy 3. At service first of all the anchor drum 9 is disconnected, then the pressure in the transmission unit space is levelled to the air-pressure outside, so that the water level rises, and thereafter the service hatch 121 can be opened and service be performed. With the right dimensioning and when the motive force from the foundation 5 is disconnected the water level can be levelled just below the driveshaft 11, so that sealings and air pump 123 never gets under the water surface 6.

At major service the complete driveshaft frame 141 with including components as shown in fig 15g, 15h and 15i, can be lifted out and replaced with a replacement unit. The counterweight 19 can be hitched under the buoy 3 meanwhile the exchange is performed. Service of the wave energy converter's transmission, generator and electronics can then be performed ashore.

In the design with the transmission unit 2 and the driveshaft 11 placed centrally in the buoy 3 the buoy's angular modulation can be used more efficiently. The buoy does follow the water surface, which gives an angular modulation at troughs and wave crests. When the wave rises, the driveshaft 11 rotates and the shaft stays 145 are then disengaged, so that the buoy 3 can rotate backwards with the wave's waterline without affecting the drive. When the waves turns

downwards, the driveshaft is locked against the shaft stays, which causes the driveshaft to turn forward in pace with that the buoy following the angular modulation of the wave. This in turn gets the counterweight drum 15 to rotate in forward direction and act to accumulate energy in the counterweight 19 in the same way as during the vertical motion in up going direction. The larger diameter the anchor drum 9 has, the lower input rotation speed the system gets in relation to vertical motion, while rotation speed from the angular modulation is the same irrespective of the anchor drum's diameter, The wave energy converter 1 can in this way be dimensioned with a larger anchor drum 9 to achieve an enhanced effect from the angle modulation in relation to the motive force from the vertical motion but must then also have a large enough width to withstand the in the same pace increased torque, which is transferred to the buoy 3 from the counterweight 19, when the driveshaft 1 1 is locked against the shaft stays 145.

The function of the wave energy converters 1 is with advantage controlled by a computerized control system, not shown, which especially controls the counterweight span level and compensates for varying accelerations and retardations to achieve as equalized power level as possible in relation to the current wave climate. The control system can also be used for controlling the torque transfer in the anchor drum's sliding clutch 55, 55' and the return feeding's sliding clutch 25, 25 ', control of locking mechanisms, not shown, control hitching of counterweight 19 and sea-floor foundation 5 in the driveshaft frame 141 at transport and service, and also logging of system function and wave data. The control system is supplied with energy from a battery, not shown, which is continuously charged by the generator 21.

The control system controls the counterweight span level and monitors the wave energy converters 1 functionality with the help of sensors, not shown, especially for rotation angles/speeds of the rotatable parts, the generator's 21 electrical power output and the buoy's 3 movements. The control system can control the counterweight span level by analysing data from a sensor, not shown, that is mounted in the counterweight drum 15 and which continuously tells the system, at which angle it has in relation to the gravitational direction or the shaft stay 13. The control system can thanks to this track the counterweight 19 position and turning points by calculating the number of revolutions of the counterweight and exactly where it turns. The turning points for each individual wave period are logged. An algorithm calculates if the counterweight span has a tendency to drift upwards or downwards by analysing the turning points during a time period. If the counterweight span is drifting upwards, the counterweight 19 can be lowered in a quicker pace, which leads to that a higher power output is generated from the generator 21 and vice versa. The length on the time period is decided from the accumulation capacity, i.e. the length of the counterweight line 17. The higher capacity, the longer time period

can be used in the calculation, which in turns gives smaller adjustments of the generator's power output.

Two sensors, not shown, measure the electrical power output and the rotation speed of the generator 21. These values are recalculated by the control system to show the torque level over the generator. The control system use the torque value to compensate for the counterweight's 19 g- force, which varies due to the mass-moment of inertia and affection by the acceleration force and water resistance, which arises due to the buoy's 3 motions in combination with variations of the driveshaft's 11 rotation speed. At a trough, the counterweight 19 is accelerated in a direction away from the gravitational direction, which gives an increased g-force, and at a crest the counterweight is acceleration a direction back to the gravitational direction, which gives a lower g-force. By regulating the counterweight's velocity of fall in accordance with the varying torque, which loads the generator 21, the power level can be stabilized.

As given from the discussion, for the counterweight's 19 turning points not to drift to the end positions of the counterweight, the counterweight's velocity of fall, i.e. the medium rotation speed of the counterweight drum 15, must be balanced against the driveshaft's 11 rotation speed. When the medium turning point is moved downwards, the counterweight's velocity of fall must be reduced, which leads to a reduced power output from the generator 21 and vice versa. By regulating the counterweight's velocity of fall and thereby the counterweight span level the power output from the generator can be kept as even as possible in relation to mean energy level in the current wave climate.

Regulation of the counterweight span level can be achieved in different ways. Regulation of the electrical load on the generator is likely the simplest and most cost efficient but there are also other possibilities as described below.

The mechanical resistance in the generator 21 depends on the electrical load, which is laid over the generator's poles. When the electrical load is increased, the electromagnetic coupling over the air gap 21 " in the generator is increased and thereby the mechanical resistance in the generator, which gets the counterweight 19 to fall slower, since the state of equilibrium between the generator and the counterweight is moved to a lower rotation speed and vice versa, se the regulation rule, which is shown in the diagram in Fig. 16a. Since the generator's power is a product of the rotation speed and the torque, the power level becomes even, meanwhile the rotation speed varies in the opposite direction to the g-force and the input torque. This works due to that the top rotation speed in a generator in general is higher than the nominal rotation speed.

The generator should manage a top rotation speed that is at least 50% higher than the nominal.

At a constant electrical load a state of equilibrium becomes present, i.e. the rotation speed of the generator 21 becomes present, which gives an equally high mechanical resistance in the

generator as the motive force given by the counterweight 19, as earlier described. By regulating the generator's ingoing mechanical torque the state of equilibrium is displaced and thereby the rotation speed, at which the state of equilibrium becomes present. The input torque can be adjusted with a gear box with a so called variable gear ratio 37, CVT ("Continuous Variable

5 Transmission"), which can constitute or be included in the gear 23. A lower gear ratio gives a higher torque and a lower rotation speed, which in turn balance each other out, but a higher torque also makes the state of equilibrium, between the generator 21 and the counterweight 19, to take place at a higher rotation speed, which increases the counterweight's velocity of fall, and vice versa, compare with the regulation rule, which is shown in diagram 16b. One type of CVT

10 is CVET ("Continuous Variable Electronic Transmission") with input- output shafts aligned, as schematically shown in Figs. 12c, 12 d. These figures are only symbolic, since the manufacturer does not want to reveal details regarding its mechanical design. Variable transmission gear boxes usually only manage limited torques and a relatively low maximum gear ratio. To minimize the ingoing torque and increase the gear ratio a planetary gear 35 can be coupled in before the

15 variable transmission, as shown in Fig. 12c.

The return feeding's sliding clutch 25, 25' between the counterweight drum 15 and the anchor drum 9, which according to above can be used for keeping the anchor line 7 tensed, can at the same time be used for reducing the torque given by the counterweight 19, which displaces the generator's 21 and the counterweight's 19 state of equilibrium in the same way as a variable

20 gear does, see the regulation rule shown in diagram in Fig. 16c and also compare with the diagram in fig 16b. Full power of the generator and full speed of the counterweight is reached, when the return feeding mechanism's sliding clutch 25, 25 ' is completely disengaged, so that the full torque from the counterweight loads the generator. When the medium wave height sinks, the torque in the return feeding's sliding clutch increases, which lowers the torque over the generator

25 21 and hereby the counterweight's velocity of fall is reduced. As sliding clutch e.g. a magnetic particle clutch can be used, which gives low heat losses at low rotation speeds. The torque can be regulated very precisely with the help of the level of a feeding current, so that the higher the current the higher the transferred torque becomes and thereby also the higher break action.

By using a cone shaped counterweight drum, not shown, the radius for the counterweight

30 line 17 point of contact around the counterweight drum can be increased the higher the counterweight 19 is winded up. The radius and thereby the torque increases the higher the counterweight is hoisted up and thereby makes the generator 21 to rotate faster. In this way, the counterweight's 19 velocity of fall and the generator's power output increases with an increased medium wave height. This principle for regulation of the counterweight's span is self-regulating

35 and hence does not need to be regulated by a control system as the other methods, but lacks the

ability to compensate for variations in the counterweight's g-force or the force with which the counterweight affects the drive package, i.e. mainly the motive force in the counterweight line.

It is possible to design a wave energy converter 1 for automatic installation. The starting position is then, that the sea- floor foundation 5 and the counterweight 19 is hitched at the

5 stay's 13 parts or at the frame 141 with corresponding lines 7, 17 completely winded up. The wave energy converter is connected to the electrical distribution network and the control system is started. The disengagement mechanism for the return blocking mechanism of the anchor drum is put in locked position according to a control signal from the control system, so that the anchor drum 7, cannot be disconnected, despite that the counterweight /-s are in their top positions. In

10 the shown designs this means that the sliding clutch 55 mounted around the return blocking mechanism of the anchor drum 51 is put on maximum force- or torque transfer, which is enough to carry the entire weight of the sea-floor foundation. The sliding clutch 25 of the return feeding mechanism can be disengaged.

Then the control system loosens the hitches, not shown, that holds the counterweight

15 19 and the sea- floor foundation 5, whereby the sea-floor foundation starts to fall towards the bottom 8 of the sea-floor. The anchor drum's line 7 is then unwound and the driveshaft 11 starts to rotate and drive the generator/generators 21. The control system regulates for maximum power and thereby the sea- floor foundation's 5 velocity of fall is slowed down as much as possible, by the electrical power that is produced. Further on the buoy 3 is preferably equipped

20 with an echo-sounder, not shown, that measures the water depth on the site, where the installation takes place. The anchor drum 9 is equipped with the same type of sensor, not shown, as is mounted on the counterweight drum/-drums 15 and the control system can in this way measure how much of the corresponding anchor line 7 that is unwound from the anchor drum. The control system can with help of these values calculate when the sea- floor foundation 5 starts

25 to approach the bottom 8. To reduce the force of impact the sea-floor foundation's velocity of fall is slowed down by means of the return feeding sliding clutch 25. When the sea-floor foundation 5 reaches the bottom 8, the driveshaft 11 stops to rotate and the counterweight/- counterweights 19 instead starts to fall and continues to drive the generator/-generators 21. The disengagement mechanism for the anchor drum's 9 rotation in relation to the driveshaft is

30 activated, so that the anchor drum can rotate in one direction in relation to the driveshaft. In the shown design this means, that the sliding clutch 55 in the anchor drum is put in normal mode, which means that the by the sliding clutch transferred force is reduced so that the force is not enough to lift the sea-floor foundation 5. The control system is thereby put into operation mode.

The outer electrical connection of the generator 21 can be achieved without the use

35 of slip rings, brushes and similar, even when the generator stator" 21 is mounted inside

counterweight drum 15. The generator stator 21 " includes, in a conventional way, electrical windings, in which electrical power is induced at rotation and which are connected to an electrical cable 41, which is partly winded up on the counterweight drum in parallel with the counterweight line 17, see Fig. 4, but closer to the anchor drum 9. The electrical cable extends from the counterweight drum 15 down to a movable connector 43, which can move along the anchor line 7. At the connector the electrical cable 41 is connected to yet another electrical cable 45, which e.g. extends to a special connector buoy 45. Hereby the wave energy converter 1 can manage to rotate, when the waves change direction, without lines and cables getting entangled with each other. Since the first electrical cable 41 is winded up on the same drum as the counterweight 19, the connector 43 to will slide along the anchor line 15 with mainly always the same distance below the counterweight. Hereby it can be avoided that the counterweight and the electrical cables 41, 45 comes to close to each other.

At an alternative way for energy accumulation the energy can be absorbed as a gas pressure in one or more tanks. Such a wave energy converter 1 is schematically shown in Fig. 9a. Here the anchor drum 9 only needs to be connected to the driveshaft 11 via a return blocking mechanism 53, compare the return blocking mechanism in the shaft stay 13 in Figs. 5a and 5b. Any stays are not required, the driveshaft can instead be journalled in bearings directly in the generator housing or the generator casing 71, which replaces the counterweight drum 15 and which in this case can enclose a fixed gear mechanism such as a planetary gear 35, generator 21 and a compressor/gas pump 73. The casing is fixed to the buoy 3, such as to its underside as shown in the figure or also centralized in the buoy, if a transmission unit space 20 according to above is used for mounting of the transmission unit 2. From the compressor/gas pump 73 a gas pipe 75 runs to the gas tanks 77, preferably located at or in the buoy. The gas tanks are also coupled to an over pressure valve 79 and a pneumatic motor 81. At this motor's outgoing shaft 85, gearwheel 87 is located, which acts together with teeth on the anchor drum's 9 flange 31.

The compressor/gas pump 73 can be a so called scroll pump and it then has a movable part 89, which is fixedly connected with the generator 21 stator 21 ", and one to the housing 71 fixed part 91. The driveshaft' s return blocking mechanism 53 here acts against the housing. When the driveshaft 11 is turned by the rising buoy 3 in this design, a gas pressure is built up, by the scroll pump 73, in the gas tanks 77. This gas pressure corresponds to accumulated energy. In pace with the increasing gas pressure, the counteracting force against the driveshaft rotation also increases. Higher waves, that give rise to a quicker medium rotation speed of the driveshaft 11 , thus build up a higher gas pressure and which thereby gives a higher counteracting torque between the generator rotor 21 ' and stator". The control system hence does not need to

actively control and optimize the operation since the equalization occurs through inertia in the pneumatic pressure. Since the energy accumulation take place by a pneumatic pressure being built up, the overpressure valve 79 can possibly be used instead of the sliding clutch 53 between the anchor drum 9 and the driveshaft 11. The sliding clutch though has an advantage by that it protects against thrust strains. When the anchor drum 9 does not turn by its coupling to the anchor line 7, as when the buoy 3 is sinking, it instead turns backwards to stretch the anchor line by that the pneumatic motor 81 rotates and drives the gearwheel 87, which acts on the flange 31 of the anchor drum.

Even with the use of gas return pressure it is possible to let the generator stator 21 " be fixed to the buoy 3 and instead connect the compressor 73 to the planetary gears 35 ring gear 165, see Fig. 9b. In this case is the generator's stator is fixed to the generator housing 71. The generator chassis 91 is also fixed to the generator housing, meanwhile the compressor's 73 gear 95 on its driveshaft 93 is connected to the planetary gear's ring gear, either directly as is shown or via a teeth belt/chain. The ring gear rotates freely around the ingoing driveshaft 11. This design of the transmission unit 2 can have the following advantages:

- No sling clutches are required in the anchor drum 9 or in the return feeding mechanism.

- No counterweights are required and thereby there is no g- force and no counterweight span that must be regulated, since the higher wave, the higher gas pressure and torque over the generator 21. - Possible problems with counterweights and lines, outer electrical cables, effect of accelerations, centre of gravity etc. can come down completely or be reduced.

- The case that no counterweight is used gives lower movable weight and thereby the sea-floor foundation 5 can also be made smaller, i.e. with smaller mass. The buoy's 3 lifting force can also be reduced with as much. - Manage shallower installation depth

- Only the anchor drum needs to be exposed to the ocean water meanwhile other components can be encapsulated.

- The housing for the gear mechanism and the generator can be made with smaller diameter than the one in the earlier described design used counterweight drum. The same type of transmission unit 2 as have been described above can be used in other designs of the wave energy converter as becomes evident from Figs. 7a, 7b and 7c. Instead of the sea- floor foundation there are here sea- floor fastening devices 61, 63 fastened to the sea-floor. 8. These sea-floor fastening devices are shaped like frames or pillars, which reach upwards from the sea- floor, and the driveshaft 11 in the transmission unit is journalled in bearings in the frames or at the pillars. In Figs. 7a and 7b two vertical pillars are used, which are located completely

beneath the water surface 6 and stretches up from the sea- floor, and the driveshaft 11 in the transmission unit is journalled in bearings to these pillars. In the designs according to Figs. 7a and 7b the anchor line 7 is fixed to the buoy. In Fig. 7b the transmission unit is mounted so close to the bottom of the pool of water that the counterweights are instead shaped like floating bodies 19 ^' . The frame according to Fig. 7c includes two vertical pillars, which reaches upwards from the bottom 8 over the water surface 6 at the side of the buoy 3. The pillars are at the top connected by a horizontal beam 64, which is located above the buoy and from which stay parts similar to the stay 13 above protrudes downwards. The driveshaft 11 in the transmission unit is journalled in bearings in these stay parts. It can be especially observed, that at the design according to Fig. 7c, energy is absorbed from the waves only when the water surface 6 and the buoy 3 sinks in contrary to the other designs, where energy is only absorbed from the waves, when the water surface and the buoy rises. Hereby the buoy must be given a weight that is greater than the counterweight's 19 and be given enough volume/buoyancy, so that it shall still be able to stay afloat at the water surface 6. This is shown in Fig. 7c by that the buoy 3 is fixed with a ballast 5". In this design the counterweight 19 line 17 is winded up around the counterweight drum 15, when the wave sinks, which significantly reduces the motion span and variation in g-force. With the right dimensioning and with periodical waves the counterweight can in principle be held still. It is also possible to keep the counterweight above the water surface 6, which gives a higher motive force in relation to the counterweight's mass. This design is especially suited for places, where there are already foundations, e.g. at wind power plants, where the counterweight and its line 17 can run inside the mast, or at oil platforms.

An alternative design of a wave energy converter 1 with a transmission unit 215 according to Fig. 15a with a centrally, between two anchor drums 9v, 9h located counterweight drum 15 is shown in Fig. 7d. In this variant the driveshaft 11 is driven by a weight or load 211, which hangs beneath the buoy 3 in an elastic organ 213, which for example can include springs or air springs. At the weight the anchor lines are also fixed. The weight 211 can have a considerable mass compared to the buoy 3 or generally in relation to other parts of the wave energy converter. The forward drive of the driveshaft occurs through joint action between the buoy 3 and the weight 211. When the buoy after having passed a wave crest sinks, the buoy also moves downwards. Then when the buoy slows down and turn in the next trough, the weight 211 continues due to its inertia to first move downwards, which stretches and prolongs the elastic organ 213 and unwinds the anchor lines 17 so that the anchor drums 9v and 9h is rotated and in turn drives the driveshaft to rotate. When the elastic organs are prolonged, their traction force on the weight 211 increases, so that its ongoing motion downwards is gradually stopped. Thereafter the force from the elastic organs becomes so great, that the weight will move upwards. This consequently occurs at the

buoy's 3 rising movement. When the buoy 3 then slows down again to turn in the next crest, the weight continues to move upwards due to its mass-moment of inertia. The elastic organs 213 are then pulled together and thereby their traction force on the weight 211 is reduces, so that it is no longer balanced by the gravity force, which affects the weight. At the same time the anchor 5 drums 9 can be returned and tense the anchor lines 7 for the next drive of the driveshaft 11. The weight is then gradually slowed down to a stop and after that again starts to move downwards.

The counterweight 7 runs through a through going hole in the weight 211 down to the counterweight 19, which moves with a phase shift to the wave motion, which can reduce its vertical motion and reduce the size of its accelerations and retardations at the wave motion, so

10 that the torque, which loads the generator 21, becomes a bit more even, which thereby requires less regulation of the rotation speed. Such a design can e.g. be advantageous at large water depths, where it can be difficult to use an anchor line 7 fixed at the bottom 8 for driving of the driveshaft.

In one design, in which the wave energy converter is mounted in a wind power plant, it is

15 possible to integrate the transmission from the turbine blades with the drive from the waves, so that the same gearbox and generator can be used, see Figs. 8a, 8b and 8c. The transmission can closest be compared to the one shown in Figs. 15a, 15b and 15e, which shall be described below. The transmission model with a fixed stator according to Fig. 15f can also be used in a similar way but this is not described further here. The main difference is the mounting of the planetary

20 gear 25 in relation to the generator's stator. The function in the planetary gear is in this design to combine the drive from the wind- and wave motions, by letting the wind power plant's rotor rotate the planet gear carrier 161, while the buoy 3 with ballast 5" drives the ring gear 165 of the planetary gear, see also Figs. 12a and 12b. In this way, the rotation and torque, which are obtained from the wind- resp. wave motions, can be added to each other and together drive the

25 sun gear 167. Neither planet carrier nor ring gear is allowed to rotate backwards, which for the planet carrier is achieved by the back locking mechanism 53 in the shaft stay 13 and for the ring gear by slipper clutch 201, which has a function similar to a back locking mechanism. The slipper clutch 201 has the equivalent function as the anchor drum's slipper clutch, see Fig. 5b and descriptions thereof, but is in this design located between shaft stay 13 and planetary gear

30 35, which makes it possible to limit the torque and energy absorption for both wind- and wave motions with one and the same slipper clutch.

The generator 21 is mounted alone in the counterweight drum 15 with connected counterweight 19, which gives the same equalization capabilities as is described for the other designs. The return feeding of the anchor drums is also done in the same way from the

35 counterweight drum 15 via ring gear 29 and tooth band/chain 175 to the link shaft 58, which in

turn is coupled in the corresponding way to the anchor drums 9v and 9h. The diameter of the anchor drums 9v and 9h in combination with the buoy 3 and the weight of the ballast 5", determines the torque which is put over the ring gear 165 of the planetary gear, and which rotation speed the ring gear gets. These parameters are chosen to match the torque from the wind turbine and the generator's size. As long as the torque, which is obtained from the drive of wind and wave, is higher than the counteracting torque, which is given by the counterweight 19, energy can be accumulated in the counterweight 19 from both wind- and wave motions. Since the torque from the wind power plant's rotor 204 varies dependency on the wind- force while the torque from the wave drive is constant, it may be necessary to mount a variable transmission gearbox before the planetary gear in the same way as shown in Fig. 12e, but the variable transmission gearbox in this design adjusts the torque from the wind drive to the wave drive after the current wind-force. To prevent the tower 207 of the wind power plant to be damaged by the buoy 3, some kind of sledge mechanism is used, not shown, which guides the buoy along the tower of the wind power plant. Breaking gearboxes is a big problem for today's wind power plants. The transmission of the wave energy converter can also be used in a wind power plant without wave drive to utilize its capabilities to limit the torque and energy absorption. In this case the same type of transmission design as described in Fig. 3d can be used but without the anchor drum 9. The wind power plant's rotor is directly connected to the driveshaft 11, as shown in Figs. 8d and 8e. The counterweight can run inside of the wind power plant's tower 207. When used in a wind power plant, gas return pressure can also be used instead of a counterweight as shown in Fig. 8f. This transmission design is described in more detail in connection to Fig. 9b. The counterweight can then be left out and its mass-moment of inertia will then not have any effect, which can be of an advantage.

In the designs described above, the electromagnetic coupling between the generator's 21 rotor and stator is utilized in most cases, while in other cases an in a special way designed transmission is used for achieving a continuous drive of the generator. Energy accumulation and return feeding can be done in different ways. In general, a wave energy converter 1 can include components as will be seen in Fig. 10a. An anchor drum 9 included in a transmission unit 2 is in a suitable way mechanically coupled to both a buoy 3 and to an object 8', which can be considered to have a more fixed position than the buoy and which can be constituted by the bottom, e.g. a bottom fastening device 5', also see Fig. 10b, at which at least one of these two mechanical couplings 7", 7'" includes an oblong organ, such as a flexible organ, typically a line or a wire, but also a stiff shaft can be used in special cases. The anchor drum can be located in a suitable way in relation to the buoy such as under, inside or above. It can rotate in two directions as shown by arrows 101, 102. The anchor drum 9 drives a driveshaft 11 at its rotation in one

direction, which can then only rotate in one direction, shown by the arrow 103. The driveshaft is mechanically coupled to the generator 21, whereby the coupling is symbolically shown at 23'. The coupling and/or the generator is set up in a way that a part of the rotational energy is accumulated in an energy accumulation device 105 at the rotation of the driveshaft 1 1. When the driveshaft is not able to turn the generator, the energy accumulation device drives the generator instead. The energy stored in the energy accumulation device can also be used for returning the anchor drum 9 and for this purpose the energy accumulation device can be coupled to the return feeding mechanism 107.

In the case which utilizes the electromagnetic coupling between the generator's 21 two, in relation to each other rotatable parts, the driveshaft 11 is mechanically coupled to the first part 21 ' by means of the coupling 23', for driving this part to rotate in the direction shown by the arrow 23, at which the electromagnetic coupling between the generator's parts gives a torque corresponding to the driveshaft' s rotation and also gets the other part 21 " to rotate in the same direction, se Fig. 10b. The generator's second part 21 " is in some way coupled, so that it at the rotational motion, because of the driveshaft' s rotation, accumulates a part of the rotational energy in the energy accumulation device 105. When the rotation speed of the driveshaft is low, where it no longer is capable of turning the generators second part, the energy accumulation device instead drives the generators second part to rotate in the opposite direction as before.

In the designs described above, two generators 21 are used. However, since the generator with belonging power electronics and gearbox, if any, is a relatively costly part of the wave energy converter 1, designs with only one generator can be more cost efficient. Below shall possible designs with only one generator be described.

In a first design with two counterweights 19 and one to the buoy 3 fixed stator of the generator 21, see Fig. 14, there is also, as shown in e.g. Fig. 26, a return feeding or link shaft 58. The link shaft couples the movement of the two counterweight drums together, so that the motive force from the right counterweight drum 15h is transferred to the left counterweight drum 15 v. The left counterweight drum includes a planetary gear 35, which steps up the rotation speed of the generator, and also limits the torque by means of the ring gear's coupling to the left counterweight drum and the counterweight 19. The location of the wind up drums are moreover the same as in the above described designs and therefore, the buoy 3 in a wave energy converter designed in this way, gets about the same stability or positioning towards the wave as in the design with two generators. The generator 21 can be mounted in a separate generator housing 181 with the generator's stator 21 " fixed to the buoy, as shown in the figure, or alternatively in or at the left counterweight drum 15 v. As shown, the link shaft 58 can be placed in front of the driveshaft 11 seen in the wave

direction. This gives a better spacing when drifting away from the sea floor foundation 5. The drifting brings the anchor lines 7, which cannot be allowed to come into contact with the driveshaft frame 141, to stretch out in a direction in relation to the counterweight line in a slanting angle. Alternatively, the link shaft 58 can be placed above the driveshaft 11, either in a 5 slanting position or straight above.

Further on it is possible to design the transmission unit 2, so that only one counterweight 19 is used without the wave energy converter loosing stability or positioning towards the wave direction. Instead such a design can, see Fig. 15a for a front view and 15b for a side view, enhance the positioning in relation to the wave direction. The anchor line 7 is divided in a Y-

10 coupling 191 into two sub lines and these are led to be winded up around one anchor drum 9v, 9h each, which are positioned on each side of the single counter weight drum 15'. Guide rollers 193, corresponding to the ones described for Fig. 13 a, 13b and 13 c, diverts the sub lines, so that they are winded up correctly on the anchor drums. The counterweight 19 runs free despite that the anchor lines joins in a Y-coupling, since the point at the counterweight drum and anchor

15 drum where the resp. line is winded up is on the opposite side of the driveshaft 11. The driftage from the foundation 5 also gives an angle for the anchor line 7, 7', which gives extra margins. For further safety margins the Y-coupling 191 can be placed below the lowest possible position of the counterweight 19, not shown.

In Figs. 15c and 15d an alternative of a straight wind up of the divided anchor lines 7'

20 around the anchor drum 9v and 9h is shown. A rod 221 holds the lines on a distance from each other and is placed just above the Y-coupling 191. To decrease the risk of collision between sub anchor lines 7' and the counterweight 19, the rod 221 can be placed below the lowest possible position of the counterweight. One advantage with this alternative is that the part of the anchor line 7, which connects the rod 221 with the sea- floor foundation 5, can be more or less stiff and

25 e.g. be designed as a ground cable or chain, while the sub anchor lines 7' can be more flexible for wind up around the anchor drums 9v and 9h. Further on the rod 221 can be designed to carry the load of itself and the undivided anchor line 7, which then leads to that a lower force is required for driving the return feeding, not shown in these figures.

In Fig. 15e the transmission unit in a wave energy converter is shown according to Figs.

30 15a and 15b seen from below and with more details. The driveshaft 11 is here fixed only one of the anchor drums, e.g. as shown with the left 15v. The left anchor drum 9v, the driveshaft and the one and only anchor drum 15' has the same function and structure as in earlier described designs, in which the generator 21 is build-in to the counterweight drum. The second anchor drum, the right drum 9h, is journalled in bearings so that it can rotate freely but its motive force

35 is transferred to the left anchor drum 9v by means of a link shaft 58. The link shaft can be

coupled via thereon mounted chain- or gear-wheels 203 to the anchor drums by means of chains or tooth bands 205, which also runs over the toothed flanges 31. Alternatively the gearwheels 203 can be directly connected to the anchor drums' flanges, in the same way as shown in Fig. 2f. The return feeding of the anchor drums is done in the corresponding way as earlier but the slipper clutch 25" is in this case coupled to the counterweight drum 15'.

In Fig. 15f an alternative to the transmission unit according to Fig. 15e is shown. According to Fig. 15f the generator's stator 21 " is fixed to the buoy 3 in a corresponding way as shown in Fig. 2g. The generator casing 71 is placed on one side of the single, centrally placed counterweight drum 15', which results in that the transmission unit 2 must be made wider. The anchor drums 9v, 9h must be placed with an equal distance from the counterweight drum for the traction force by the counterweight 19 and the foundation 5 via the counterweight lines 7' shall remain centred in the wave energy converter. This leads to that more stay parts or shaft stays 13, 145 are required to carry the parts of the transmission units. It is possible to use the same design of the anchor drums as described above for Fig. 15e. However, in this case it can be motivated to simplify the left anchor drum 9v by using an displaced or free lying slipper clutch 55' and use the extra space in the transmission casing space 20 for the transmission unit 2, so that the left anchor drum 9v can be fixed to the driveshaft's first part 11 ' in the same way as earlier described for Fig. 5c while the driveshaft's second part 11 " on the other side of the slipper clutch comprises or is directly connected to the ingoing shaft to the gear 23 and the counterweight 15' rotates around this second part.

In Figs. 15g and 15h an alternative transmission unit according to Fig. 15f is shown, in which the mechanics is to a larger extent encapsulated. The power transmission between driveshaft 11 ', 11 " and the link shaft 58 can in this design preferably be done via gearwheels 209. A high gear ratio as shown in the figure is used for increasing the rotation speed of the link shaft and decreasing the torque which gives less wear and smaller dimensions of the power transmission. In this design only the drums 9v, 9h, 15' are exposed to the sea water in the transmission housing 20. The generator 21 with all belonging power electronics and the link shaft 58 including the power transmission are encapsulated in a climate controlled environment 195. The return feeding 26 has in this design been placed on the high speed side of the gear 35, but could also be placed on the low speed side. One advantage with placing the return feeding 26 on the high speed side is that the space will be used more efficiently since it requires a higher gear ratio in the return feeding compared to the link shafts power transmission 210. A high speed rotation in the slipper clutch gives higher transmission losses though.

In Fig. 15i an alternative to return feeding, which is described in relation to Fig. 15g is shown. Here an electric motor 223 is used instead, which is directly connected to any of the

gearwheels 209 on the link shaft 58. The electric motor gets power from the battery, not shown, which drives the control system and other electronics, not shown. The electric motor is controlled by the control system which in that way can optimize the return feeding. It is also possible to drive the return feeding by means of a spring mechanism, such as e.g. a coiled spring or a constant power spring, not shown.

A wave energy converter has here been described which can have one or more of the following advantages:

- The counterweight drum / drums limit the maximum resistance in the system and give a sharp limit for the torque acting over the generators. - The energy accumulation is very simple and efficient and can store energy over long time intervals at the same time as the motive force can be held constant in relation to the average wave height during the time interval.

- The wave energy converter can be dimensioned to utilize the depth on the installation site in an optimal way for the accumulation and for decreasing the weight of the counterweight. - The storage of energy is stopped automatically when "the accumulator is full" and this can be achieved without the generator losing power.

- The scalability is very good and the wave energy converter can be dimensioned to reach maximum capacity at a selected wave height to get a better utilization factor of the generator.

- It is not necessary to over dimension the whole system to be able to handle absorption of energy at rare occasions when the mean wave height is considerably higher than normal.

- The buoy continuously follows the wave motions independently of how large the waves are. The force limitation in the anchor drum efficiently protects the device from thrusts and overloads.

- The motive force is constant in relation to the gear ratio which enables the use of all types of generators, incl. synchronous AC generators, which are working with constant or variable rotation speed.

- Minimal manual efforts at installation, short course of installation which generators electricity already when the foundation is being lowered down.

- Mainly simple and durable construction. - Very high utilization factor of the generator and transmission.

- Long service intervals.

While specific embodiments of the invention have been illustrated and described herein, it is realized that numerous other embodiments may be envisaged and that numerous additional advantages, modifications and changes will readily occur to those skilled in the art without departing from the spirit and scope of the invention. Therefore, the invention in its broader

aspects is not limited to the specific details, representative devices and illustrated examples shown and described herein. Accordingly, various modifications may be made without departing from the spirit or scope of the general inventive concept as defined by the appended claims and their equivalents. It is therefore to be understood that the appended claims are intended to cover all such modifications and changes as fall within a true spirit and scope of the invention. Numerous other embodiments may be envisaged without departing from the spirit and scope of the invention.