Title of Invention

A WAVE POWER APPARATUS COMPRISING A PLURALITY OF ARMS ARRANGED TO PIVOT WITH A MUTUAL PHASE SHIFT

Abstract A wave power apparatus includes a plurality of rotationally supported arms, each of which carries a float (124) at its free end, so that a translational movement of the float caused by a wave results in rotation of the arm. The apparatus comprises power conversion means for converting power transmitted from the wave to the arms into electric power, e.g. a hydraulic system, in which a hydraulic fluid is displaced by the movement of the arms to drive one or more hydraulic motors. The plurality of are arranged in a row such that a wave passing the row of arms causes the arms to successively pivot with a mutual phase shift. Thereby, an even power output may be achieved, and the need for frequency converters may be reduced or eliminated. Preferably, each arm is connected to a hydraulic cylinder of the hydraulic system, whereby a plurality of arms feed hydraulic medium into the hydraulic motor or motors through common hydraulic conduits.
Full Text A WAVE POWER APPARATUS COMPRISING A PLURALITY OF ARMS ARRANGED TO PIVOT
WITH A MUTUAL PHASE SHIFT
Technical field
The present invention relates to a wave power apparatus for converting power of sea or
ocean waves into useful energy, such as electricity. The apparatus according to the invention
specifically aims at providing a system, in which an even power output may be achieved.
Background of the Invention
It is well known that sea waves appear to constitute a nearly unlimited resource of energy
which, if exploited efficiently, may possibly solve a significant proportion of the world's
energy problems. However, despite of many attempts to exploit sea-wave energy, no
commercially successful system for converting sea wave energy into electrical power has
been devised so far.
In general, three different types of wave power apparatuses have been proposed in the prior
art. One such apparatus is disclosed in US 6,476,511, the apparatus comprising a plurality of
buoyant cylindrical body members connected together at their ends to form an articulated
chain-like structure. Each pair of adjacent cylindrical members is connected to each other by
a coupling member, which permits relative rotational movement of the cylindrical members
about a transverse axis. Adjacent coupling members may permit relative rotation about
mutually orthogonal transverse axes. Each coupling member is provided with elements, such
as a set of hydraulic rams, which resist and extract power from the relative rotational
movement of the body members. The apparatus floats freely in the sea surface and is
moored to the sea floor.
A second type of wave power apparatus comprises one or more surface floats capable of
moving along the surface of the sea under the action of waves, and a reference member,
which Is fully submerged In the sea at a certain depth, and which is substantially unaffected
by the waves, cf. for example US 4,453,894. The movement of the float in the surface of the
sea causes the displacement of a hydraulic fluid in a hydraulic system comprising hydraulic
devices which interconnect the surface float or floats and the reference member, whereby
useful energy may be extracted from the hydraulic system. It will be appreciated that this
apparatus is also moored to the sea floor.
Finally, a third type of wave power apparatus is one having one or more arms supported by a
supporting structure carrying one or more floats which are caused to move by the waves. The
energy of moving waves transmitted Into the arms and may be conveyed into a hydraulic
system, as in the system of US 4,013,382, or Into a mechanical system of shafts which, via a
mechanical transmission system, drive one or more electric generators for the production of
electricity, as in the system of WO 01/92644.
The present invention is generally concerned with the third type of wave power apparatuses
mentioned above. It is an object of preferred embodiments of the invention to provide an
apparatus, which allows for an even power output of power conversion means of the
apparatus, i.e. a power output which is substantially constant over time. It is a further object
of preferred embodiments to provide a system which reduces or eliminates the need for
frequency converters. It is a further object of preferred embodiments to provide a wave
power apparatus which may conveniently be taken out of operation, e.g. to prevent
formation of ice on various parts of the apparatus during operation. It is a still further object
of preferred embodiments of the invention to provide an apparatus, which allows for
convenient maintenance access to arms and floats, most preferably to allow for maintenance
access of individual arms and floats in systems comprising a plurality of arms, each provided
with a float. It is a still further object of preferred embodiments to provide an apparatus
which may conveniently be conveyed from an on-shore production facility to the operational
site at the open sea.
Summary of the invention
The present invention provides a wave power apparatus comprising a plurality of arms, each
of which is rotationally supported at one end by a shaft, and wherein each arm carries a float
at its other end, which is opposite to the supported end, so that a translational movement of
the float caused by a wave results in rotation of the arm around the shaft, the apparatus
comprising power conversion means for converting power transmitted from the wave to the
arms into electric power, the plurality of arms being arranged in a row such that a wave
passing the row of arms causes the arms to successively pivot around the shaft, the arms
being arranged at mutual distances, so that the passage of the wave causes the arms to
pivot with a mutual phase shift.
The arms are preferably arranged at mutual distances, so that at all times at least two of the
arms simultaneously deliver a power contribute to the power conversion means. The power
conversion means preferably comprise a hydraulic actuator associated with each arm, the
hydraulic actuators feeding a hydraulic medium into at least one hydraulic motor via shared
hydraulic conduits. Accordingly, an even power output of the power conversion means may
be achieved. This is in particular the case in embodiments of the apparatus comprising a
large number of arms, floats and actuators, e.g. 60, as the sum of the power contributes of
the individual actuators is essentially constant over time. Possible pressure ripples on the
pressure side of the hydraulic motor may be essentially eliminated by means of a spike
suppression device which is known per se, the spike suppression device being arranged in
fluid communication with the shared hydraulic conduits. Preferably, the sum of all power
contributes is essentially constant at a certain wave climate, i.e. wave height and wave
frequency. The hydraulic motor is preferably a hydraulic motor with variable displacement
volume per revolution. Changes in the wave climate may be compensated by means of a
control circuit which controls the displacement volume per revolution of the motor in order to
keep the rpm of the motor essentially constant. In order to generate alternating current at a
given frequency without utilizing a frequency converter, the rpm of the motor should be
controllable within +/- 0,1-0,2%. In case a different type of hydraulic motor is applied or in
case the rpm is not controlled exactly, a frequency controller may be employed for fine-
adjustment of the frequency of the AC current generated.
In preferred embodiments, the apparatus of the present invention comprises at least 5 arms,
such as at least 20 arms, preferably at least 40 arms, preferably 50-80 arms, such as 55-65
arms, e.g. 60 arms. The arms of the apparatus are preferably distributed, such that there is
provided at least five arms, preferably at least 10 arms, per wavelength of the ocean waves.
At the open sea, the wave length of the ocean waves is typically 50-300 m, such as 50-200
m. In protected waters, the wave length of waves is typically 5-50 m.
In preferred embodiments, the apparatus spans over at least two wave lengths. This brings
about the possibility to arrange a row of arms and floats at a relatively large angle with
respect to the wave heading, e.g. at +/- 60°, as the wave length projected onto the
orientation of the row of floats spans over at least 2 x cos(60°) wavelengths, i.e. at least one
wavelength, whereby it is ensured that a power contribute is delivered at all times.
The plurality of arms are preferably arranged in one or more rows, e.g. in a star, V or
hexagon formation as disclosed in WO 01/92644. In order to efficiently exploit the wave
energy, the row of arms is preferably oriented such with respect to the wave heading that the
row forms an angle of within +/- 60° with respect to the wave heading.
It has been found that the efficiency of the apparatus according to the invention increases
with increasing buoyancy of the float with regard to Its dry weight. Accordingly, In preferred
embodiments of the invention, the buoyancy of the float is at least 10 times its dry weight,
such as at least 20, 30 or 50 times, preferably 20-40 times. For example, the dry weight of a
float is typically 100 kg or less pr. meter cube of buoyancy, the buoyancy of salt water being
typically approximately 1050 kg/m3. A float is typically made from hard low weight foam
materials or balsa wood, which are coated with a composite, such as reinforced glass fiber
composites or a combination of glass fiber and carbon fiber composites. Alternatively, a float
may be made from a sandwich layer of reinforced fiber materiel with hard foam being
provided in the middle of the sandwich and at the bottom and at the top of the float, with the
foam layers being separated by a honeycomb structure of reinforced fiber materials.
Efficiency also increases with increasing diameter of the float relative to its height. Preferably,
the diameter of the float Is at least 5 times Its height, such as at least 7 times, such as at
least 10 times, or 5-20 times. In preferred embodiments, the float has an essentially circular
cross-section, and in order to improve fluid dynamical properties of the float, it may have a
rounded edge portion, which acts as a streamlining.
The power conversion means preferably comprise a hydraulic driving system with a
hydraulically driven motor. For example, each arm may be connected to the hydraulic driving
system by means of at least one actuator which causes a hydraulic medium of the hydraulic
driving system to be displaced into a hydraulic motor, the actuator(s) being arranged to
displace the hydraulic medium to the motor via hydraulic conduits. In case of several arms
and several actuators, the hydraulic medium is preferably displaced to the motor via shared
hydraulic conduits. In other words, several hydraulic actuators may feed hydraulic medium
into one single hydraulic motor via a shared system of hydraulic conduits. Most preferably,
the hydraulic medium is not accumulated in a hydraulic storage tank for accumulating
hydraulic medium under pressure, from which pressure is released to the motor. Accordingly,
the actuators feed hydraulic medium directly into the hydraulic motor. However, as discussed
below, a battery of hydraulic accumulators may advantageously be applied for an entirely
different purpose, i.e. for forcing a float into a wave near a wave trough. As in preferred
embodiments, a plurality of actuators simultaneously transmit power to the motor, there is
no need for a hydraulic storage tank, as the motor will be capable of running at a
substantially constant speed and at a substantially constant power Input thanks to the
delivery of power in the shared hydraulic system from a plurality of actuators at a time.
It should be understood that there may be foreseen more than one single hydraulic motor.
Preferably, two, three or more motors may be arranged in parallel at the end of the shared
hydraulic conduit. Thus, the power delivered through the shared hydraulic condu/t may drive
several motors. If, for example the hydraulic driving system produces 4 MW, eight motors
delivering 5O0 kW each may be coupled in parallel at the shared hydraulic conduit. The
motors may deliver the same nominal power output, or they may deliver different nominal
power outputs. For example, one motor may deliver 400 kW, one may deliver 500 kW, etc.
AN hydraulic motors may also be linked through the same through-going shaft, which drives
at least one common electric generator, or all hydraulic motors may drive one cog wheel
which drives at least one common electric generator
In order to allow the hydraulic system to force the arm(s) and float(s) in any desired
direction, each actuator may comprise a double-acting cylinder which may be used to extract
energy from the arm Into the hydraulic system and to feed energy from the hydraulic system
into the arm, e.g. to drive the float into a wave near a wave trough as explained in detail
below in connection with the hydraulic accumulators.
In preferred embodiments, the apparatus comprises means for forcing the float(s) into the
waves at wave troughs, so as to increase the vertical distance traveled by the float to
Increase the power output In a wave cycle. Such means may e.g. comprise one or more
hydraulic accumulators for intermittently storing energy in the hydraulic driving system. The
energy stored in the hydraulic accumulators may advantageously be derived from the release
of potential energy as the float is taken out of the water a wave crest. In other words, as a
float moves from a submerged position In a wave near a wave crest to a position above
water, potential energy is released. This energy may be accumulated In the accumulator or In
a battery of accumulators, wherein different accumulators are charged at different pressures,
e.g. at pressure steps according to the number of accumulators. In embodiments
incorporating such hydraulic accumulators, the hydraulic driving system may be controllable
to release the energy stored in the accumulator(s), when a float is passed by a wave trough,
so as to drive the float carried by the arm into the wave. To improve the efficiency of the
accumulator system, there may be employed a plurality of accumulators, such as at least 2,
such as 3-20, such as typically 6-12, which preferably store hydraulic medium at different
pressure steps. In preferred embodiments, the float is driven a certain distance into the wave
near a wave trough, and subsequently the float Is allowed to move upwardly In the wave, but
yet submerged in the wave, and at the wave crest the float is released, I.e. allowed to move
out of the water. As described above, the energy released as the float is released at the wave
crest is used to charge the one or more hydraulic accumulators, at which energy Is stored for
driving the float into the wave. Accordingly, the potential energy released as the float moves
out of the wave near the wave crest is not lost. On the contrary, it is utilized for driving the
float into the wave at the wave trough, whereby the total vertical distance traveled by the
float Is increased. Consequently, the power output of a wave cycle is increased. It Is
estimated that, at a wave height of 1.5 m, the vertical distance traveled by the float may be
Increased from approximately 0.75 m to approximately 1.5 m, thus doubling the power
output. The energy utilized to drive the float into the wave at the wave trough causes
essentially no loss in the driving system, as the energy is provided by the release of the float
at the wave crest.
In order to allow for accurate control of the system, each cylinder, or at least selected ones
of the cylinders, may be provided with a sensor for determining a position and/or rate of
movement of the cylinder's piston, the sensor being arranged to transmit a signal to a control
unit of the cylinders and associated valves, so that the transmission of energy from the
individual cylinders to the remaining parts of the hydraulic driving system is Individually
controllable in response to the signal representing the individual cylinder's piston's position
and/or rate of movement. Thus, the cylinders may be individually controllable, and a cylinder
may be withdrawn from operation, e.g. for maintenance, while the remaining cylinders keep
operating, so that the entire system will be essentially unaffected by the withdrawal of a
single cylinder. The sensor is preferably also utilized to control the depressing of the float into
the water, i.e. to control release of pressure of the battery of accumulators as described
above. The sensor may further be utilized to control charging of the accumulators, i.e. to
determine the passage of a wave crest. Moreover, the sensor Is useful to control releasing of
the float at a wave crest, I.e. to prevent a catapult-like shoot-out of the float. The sensor
may also be used for monitoring the power output of each individual actuator In the hydraulic
driving system, so that the power output of the individual actuators and the entire apparatus
as such may be optimized.
Whereas some prior art systems rely on submerged reference members for supporting those
means which convert sea wave power into useful power or on shore-supports, it has been
found that wave energy is most efficiently exploited on the open sea. Accordingly, the
apparatus of the invention preferably comprises a supporting structure which is fixed to the
sea floor. In a presently preferred embodiment, the supporting structure is fixed to the sea
floor by means of a suction anchor, or alternatively by a gravity foundation, or fixed to a
rocky seabed with studs. The supporting structure may advantageously comprise a truss
structure, with the suction anchor being arranged at a first nodal point of the structure. At
least one arm and preferably all arms of the apparatus are supported at second nodal points
of the truss structure, most preferably at a summit of a triangular substructure of the truss
structure. The triangular substructure may define two vertices at the sea floor, with a means
for attaching the structure to the sea floor in each of the corners. Preferably, the means for
attaching are at least partially embedded in the sea floor, e.g. under by gravity foundation or
a suction anchor. As the means for attaching are arranged at the nodal points of the truss
structure, vertical forces in the truss structure caused by the buoyancy of the floats may
efficiently be counteracted. A truss structure as described above ensures a maximum degree
of stability of the system while allowing for a low overall weight of the supporting structure.
It has been found that one general problem In prior art systems is to prevent extreme
impacts occurring during storms and hurricanes from damaging the floats, arms and other
parts of the wave power apparatuses. Embodiments of the present invention therefore
provide features wh ich makes it possible for the wave power apparatus to withstand extreme
sea wave conditions. Such embodiment comprise a hydraulic lifting system for lifting the float
out of the ocean and for locking the float in an upper position above the ocean surface.
The hydraulic lifting system preferably comprises one or more pumps for pumping hydraulic
medium into the cylinders for lifting them out of the ocean.
Thanks to the hydraulic lifting system, the float may be withdrawn from the ocean and kept
in a locked position above the ocean surface at the occurrence of e.g. storm or prior to the
occurrence of icing. Thus, the only impact on the float when it is withdrawn from the ocean is
the Impact of wind, the forces of which are significantly smaller than the forces of waves. In
one embodiment, the arms may be lifted out of the water by generating a hydraulic pressure
in the hydraulic lifting system, which causes the arms to be displaced out of the ocean, and
by appropriately shutting a valve, preferably by means of a conical locking pin, so as to
maintain the lifting pressure. The hydraulic lifting system may be controlled from a remote
on-shore location, or by a control system which forms part of the wave power machine, and
which acts in response to a signal Indicative of a stormy condition, e.g. to a signal from an
electronic device for continuously determining the velocity of wind. The control system may
be programmed to withdraw the float and arm from the water at a predetermined wave
height. For example, this wave height may be a certain fraction, e.g. 30%, of the largest
predicted wave referred to the operation site of the apparatus, the so-called "100-year
wave". At an ocean depth of 20 m, this height is approximately 18 m, and the control system
accordingly takes the float and arm out of the ocean at a wave height of approximately 6 m.
The wave height may be determined by a mechanical, optical, electro magnetic or acoustical
system, e.g. a pressure transducer system with a pressure transducer arranged on the sea
floor, an echo sound system arranged at the floats, an echo sound system arranged on a
fixed supporting structure of the apparatus and pointing upwards towards the surface of the
waves, or operating in air pointing downwards toward the water surface, or a sensor system
with light transmitting or light receiving means arranged on the floats and/or on the fixed
supporting structure, such light being, e.g., laser light. Alternatively, there may be provided a
radar system at the structure. The pressure of a hydraulic medium in the lifting system may
be generated by a pump forming part of the hydraulic lifting system. Alternatively, the
pressure may be generated by releasing pressurised hydraulic medium from an appropriate
hydraulic accumulator. The accumulator may e.g. be charged by a hydraulic driving system
which, in one embodiment of the invention, is comprised in the power conversion means. For
example, the accumulator for delivering the hydraulic lifting pressure may be an
accumulator, or a plurality of accumulators in a so-called accumulator battery, for forcing the
float into the wave at a wave trough as described in detail below.
The hydraulic lifting system is preferably adapted to individually lift each float out of the
ocean. For example, the lifting system may comprise a plurality of hydraulic circuits, each of
which Is associated with one of the arms, and each of which comprises valve and/or pump
means for pressurising the hydraulic circuit for lifting the arm and float out of the ocean. In
one embodiment the hydraulic lifting system comprises fewer pumps than circuits, so that
the or each pump is connected to a plurality of circuits, each circuit with associated valves
being designated to one arm. In preferred embodiments of the invention, the power
conversion means and the arms are arranged such that those arms, which are kept in the
ocean, may deliver power to the power conversion means, while one or more other arms are
kept lifted out of the ocean. Embodiments incorporating the power conversion means of WO
01/92644, which is hereby incorporated by reference, may allow for free-wheeling, around a
driving shaft of the power conversion means, of arms which are lifted out of the ocean.
Embodiments relying on hydraulic power conversion means, in which movement of the arms
generates pressure in a hydraulic driving system, may comprise means for taking out of
operation those power conversion means, e.g. those hydraulic actuators, which are
associated with an arm, which has been lifted out of the ocean. In a presently preferred
embodiment, an arm may be lifted out of the ocean and locked in an elevated position by the
arm's actuator, e.g. a double-acting cylinder, which may be used to lift and lock the arm.
Preferred embodiments of the present invention also provide a solution to the problem of
providing a stable rotational support of the arm or arms, which is less vulnerable to
horizontal force components. It has been found that the structure of US 4,013,382 Is likely to
become unstable due to horizontal force components generated by waves. More specifically,
the bearings of the connecting rods are constituted by simple pins, and any slight slack in
such bearings might cause irreparable damage to the connecting rods and their support. The
apparatus of US 4,013,382 is therefore unsuitable for installation at the open sea, i.e. at
relatively large wave forces. The structure disclosed in WO 01/02644 also suffers from the
disadvantage that even the slightest slack in the one-way bearings which support the rocker
arms and which connect the rocker arm pipes and the force shaft might damage the
bearings. Moreover, the apparatus of WO 01/02644, in which a total of some 40 rocker arms
are supported by one single force shaft, requires an immensely strong force shaft which, due
to its dimensions required in order for it to be able to transmit the required power, would be
unfeasible due to its weight conferred by Its large dimensions, such large dimensions being
necessary due to the momentum transmitted from the arms to the force shaft. Preferred
embodiments of the apparatus according to the present Invention provide an improved
support of the arms which makes the apparatus less vulnerable to horizontal force
components. Therefore, in a preferred embodiment, the apparatus of the invention comprises
a pair of pre-stressed and essentially slack-free bearings. The bearings are thus capable of
efficiently counteracting radial and axial forces and consequently to withstand horizontal
force components conferred by waves. The term "slack-free bearing" should be understood to
comprise any bearing, which is slack-free in a horizontal and axial direction. For example, the
pair of bearings may comprise two conical bearings with their conical faces being opposite to
each other. In one embodiment, the bearings are pressure-lubricated.
In another embodiment, the bearing comprises an inner and an outer ring or cylinder, the
inner ring being secured to a rotational shaft of the arm, and the outer ring being secured to
a fixed support, the bearing further comprising a flexible material between the inner and the
outer ring. During operation, the inner ring rotates relative to the outer ring, thereby twisting
the flexible material. In order to adjust the stiffness of the flexible material, there may be
provided at least one cavity or perforation in the material. The flexible material may, e.g.,
comprise a spring member, such as a flat spring. By appropriate positioning of the
perforation(s) or by appropriate design of the spring member(s), the bearing support may be
designed to have a larger force-bearing capacity In one direction than In another direction.
The arm is preferably supported by the bearings at two mounting points which are offset
from a centre axis of the arm, the centre axis of the bearings being coincident with an axis of
rotation of the arms. As each arm is connected to and supported by individual bearings, a
stable rotational support for the arms is achieved. In particular, as the two bearings are
preferably arranged at a mutual distance along the axis of rotation of the arm, an impact at
the axis resulting from a horizontal force component on the float may be counteracted.
It will, accordingly, be appreciated that the structure of the present apparatus is more stable
than the structure of prior art devices. As the present apparatus is primarily intended as an
off-shore construction, stability is a major concern due to costs of maintenance at off-shore
sites. Maintenance costs at off-shore sites are typically on average 10 times higher than
maintenance costs at on-shore sites.
Brief description of the drawings
Preferred embodiments of the invention will now be further described with reference to the
drawings, in which:
Figs. 1 and 2 are cross-sectional illustrations of an embodiment of a wave power apparatus
according to the Invention;
Figs. 3-5 show three embodiments of a truss structure of an embodiment of a wave power
apparatus according to the present invention;
Fig. 6 illustrates a honeycomb structure of a float;
Fig. 7 illustrates a supporting structure for an arm of the apparatus of Figs. 1 and 2;
Figs. 8-13 show various bearing assemblies for an arm of the apparatus;
Fig. 14-17 show diagrams of a hydraulic driving system of an embodiment of an apparatus
according to the invention;
Fig. 18 shows a diagram of a hydraulic lifting system for lifting the floats out of the ocean;
Fig. 19 illustrates a wave power apparatus with an array of floats extending across two wave
crests;
Fig. 20 shows hydraulic pressure as a function of time in a feed line of the hydraulic driving
system of a prior art wave power apparatus and in an embodiment of the apparatus
according to the present invention, respectively;
Fig. 21 illustrates two different travel paths of a float across a wave,
Fig. 22 shows a diagram of a hydraulic driving system with accumulators for forcing the floats
Into the waves at wave troughs;
Fig. 23 illustrates the stepwise accumulation of energy in a hydraulic storage system;
Figs. 24 and 25 are diagrammatic illustrations of the movement of waves and floats.
Detailed description of the drawings
The below description of the drawings discloses a variety of features and options comprised
in various embodiments of the wave power apparatus according to the invention. The
operating principles of the broadest aspect of the invention will be appreciated best from the
description of the embodiments of Figs. 1 and 14-20.
Figs. 1 and 2 show a cross-section of wave power apparatus 102 comprising a truss structure
104 which may e.g. be of a so-called space truss structure. The truss structure, which is also
illustrated In Figs. 3-5, comprises an essentially triangular lower part with first, second and
third force members 106,108,110, and an essentially rectangular upper part 111. The
rectangular upper part may be used for accommodating hydraulic and electric equipment,
including the hydraulic driving and lifting system, and it may further be used as a as catwalk
or footbridge for maintenance personnel. As illustrated In Figs. 3-5, the rectangular upper
part extends a distance perpendicular to the plane of Figs. 1 and 2, whereas there is provided
a plurality of distinct lower triangular lower parts. The truss structure defines first, second,
third, fourth, fifth and sixth nodal points 112,114,116,117,118 and 120. Preferably, the force
members are essentially rigid, so that they may withstand tension and compression. The first
and second nodal points 112,114 are provided at the sea floor and are retained at the sea
floor by means of, e.g., suction anchors 121 indicated in Figs. 3-5. Alternatively the first and
second nodal points 112,114 may be supported by a concrete foundation at the sea floor.
Arms 122 carrying floats 124 are rotatlonally supported at or near the third and fourth nodal
points 116, 117. Figs. 3-5 show a perspective view of the truss structure for supporting a
plurality of arms on either side of the structure. It should be understood that the truss
structure of Figs. 3-5 may have a wider extent than actually depicted in Figs. 3-5, so that it
comprises e.g. twenty or thirty triangular sections, whereby an arm may extend away from
the truss structure at each of the nodal points 116,117. A plurality of truss structures as
those of Figs. 3-5, such as three, six or more truss structures, may be arranged in a star, V-
or hexagonal arrangement in order to increase the number of arms and floats included in an
installation comprising the apparatus of the invention or a plurality of apparatuses according
to the invention.
The third, fourth, fifth and sixth nodal points 116,117, 118,120 are provided above the
surface of the sea at a height sufficient to ensure that they are also above the sea surface
when waves are high under stormy conditions. For example, the nodal points 116,117, 118
and 120 may be provided at 20 meters above the surface of the sea when the sea is smooth.
In order to transform the energy of the waves into hydraulic energy, the wave power
apparatus 102 comprises a plurality of arms 122, each of which at one end comprises a float
124 and at the opposite end is connected to a shaft 126. The arms are adapted to rotate
around the shafts 126. Each arm 122 is attached to a hydraulic actuator, such as a hydraulic
cylinder 128 comprising a piston 130. The hydraulic cylinder 128 is pivotally connected to
the arm in a first attachment point 132 and to the truss structure 104 in a second attachment
point 134. The second attachment point is preferably located at a nodal point, i.e. along an
edge portion of an essentially rectangular structure arranged on top of the triangular main
structure of the truss structure. The floats 124 move the arms up- and downwardly
influenced by the movement of the waves. When the arms move upwardly and downwardly,
the piston 130 is moved, and thus the wave energy is transformed into hydraulic energy
which may be converted into useful electric energy as described below in connection with
Figs. 14-18 and 22.
As shown in Fig. 2 the hydraulic cylinders 128 are adapted to lock the arms 122 in an
elevated position wherein waves can not reach the arms 122 and floats 124, the arms being
drawn to their elevated positions by the cylinders 128. It Is thereby possible to protect the
arms 122 and floats 124 during a storm or when ambient temperatures near or below the
. freezing point of the water of the ocean risk to cause formation of ice on the floats. The
hydraulic cylinders 128 are connected to a hydraulic lifting system for locking the hydraulic
cylinder in the elevated position, the hydraulic lifting system being discussed in further detail
in connection with Fig. 18 below. The floats 124 may be pivotally connected to the arms 122.
Accordingly/ when the arms are elevated during a storm, the floats may be rotated to a
position wherein they are essentially parallel to the wind direction. Thereby, the surface
which the wind acts on is limited and thus the force acting on the floats 124 is reduced and
the torque transferred to the truss structure 104 via the arms 122 is reduced. Furthermore
the floats are designed with an aerodynamic shape with rounded edges (not shown), so as to
reduce the wind forces on the apparatus.
As shown in Figs. 3-5, the truss structure 104 may include diagonal force members 113, 115
(not shown in Figs. 1 and 2) for providing a further support at the nodal points 116, 117.
In Figs. 4 and 5, the truss structure is loaded with a weight acting downwardly to reduce the
upwards forces at the anchors 121. The weight is brought about by a longitudinally extending
weight, such as a water tank 123 (Fig. 4), or by a plurality of distinct weights, such as water
tanks 125 (Fig. 5).
Fig. 6 shows a structure of an essentially hollow float 124 comprising a honeycomb structure
127, which supports the outer walls of the float.
Fig. 7 shows one of the arms 122 which is pivotally attached to a float 124 and Is adapted to
rotate around a shaft 126. The arm is connected to the shaft at first and second attachment
points 136, 138 which are offset from the centre axis 140 of the arm. The shaft 126 is
rotatably supported by a fixed support structure 142 comprising two bearings 144 arranged
to counteract radial and axial forces.
In order to provide an essentially maintenance-free bearing support for the rotation of the
arms 122, the present inventors have proposed bearings as those shown in Figs. 8-13. The
bearings of Fig. 8-13 may be incorporated as a bearing 144 in the bearing structure
illustrated in Fig. 7 and are particularly well suited for supporting an shaft, the rotational
amplitude of which is 30 degrees or less during normal operation, i.e. ±15 degrees or less,
such as 20 degrees or less, i.e. ±10 degrees or less. When the arm Is to be pivoted to the
secured position of Fig. 2, the fixing of the outer ring 147 may be loosened, so that a larger
rotational amplitude is allowed, e.g. ±40 degrees. Traditional roller or ball bearings have a
short life time at such small rotational amplitudes, as their lubrication medium usually only
fulfils its purpose to the desired extent at continuous rotation at a higher rotational speed
than the one conferred by the arms 122. The bearing of Fig. 8 includes an inner ring or
cylinder 145 and an outer ring or cylinder 147, between which there is provided a flexible
substance 149, e.g. a rubber material. The inner ring 145 is secured to the rotating shaft,
and the outer ring 147 is secured to the stationary support of the shaft. Thanks to the
elasticity of the flexible substance 149, the inner ring may rotate relative to the outer ring, so
as to allow the supported shaft to rotate with respect to its support. As the outer ring 147 is
supported by or fitted into a fixed structure, e.g. squeeze fitted along its outer periphery,
there is provided an axial and a radial support of the shaft. The stiffness of the flexible
substance 149 may be adjusted by providing cavities 151, such as bores or perforations, In
the material. The maximum load supportable by the bearing may be Increased by increasing
the length of the bearing (i.e. transverse to the plane of Fig. 8). The number and dimensions
of the cavities 151 may be selected to fit a particular purpose, e.g. to minimise notch
sensitivity or to maximise the axial force to be counteracted by the bearing. A like bearing
344 is shown in Fig. 9, which has fewer cavities 151 to increase the force-bearing capacity of
the bearing in one direction.
Similar wriggle bearings 346, 348 and 354 are shown in Figs. 10, 11 and 12, respectively.
These bearings comprise inner and outer rings 145,147 with one or more flat springs being
interposed between the rings. In Fig. 10, there is provided two flat springs 147, each of
which forms the shape of the number 3. The arrows 345 and 347 indicate that the force-
bearing capacity is larger in the vertical direction (arrows 345) than in the horizontal
direction (arrows 347). In the bearing 348 of Fig. 11, there is provided one flat spring
element 352, which defines a plurality of cavities 353. Arrows 349 and 350 indicate that the
force-bearing capacity of the bearing is larger in the vertical and horizontal directions than in
non-horizontal and non-vertical directions (arrows 350). Bearing 354 of Fig. 12 comprises
two H-shaped flat spring elements 362, each defining an outer and an inner portion 364 and
366 as well as an interconnection portion 368. The stiffness of the bearing may be chosen by
adequate selection of the geometry of the spring elements 362. For example, the
interconnecting portion 368 may be formed as an S. Arrows 355 and 357 indicate that the
force-bearing capacity is larger in the vertical direction than in the horizontal direction.
The inner and outer rings 145, 147 of Figs. 8-12 may be made from steel or from carbon
fibre materials. The flat springs 342, 352 and 362 may likewise be made from steel or carbon
fibre materials.
The bearing principles of Figs. 8-12 may also be used for providing a support for the
hydraulic cylinders 128.
Fig. 13 shows a bearing support for an arm 122, the support comprising two flat springs 372
and 374. The first flat spring 372 increases the torsion stiffness as well as the transverse
stiffness of the bearing. The flat springs may be made from carbon fibre materials.
In the hydraulic diagram of Fig. 14, there is shown a plurality of cylinders 128 with respective
pistons 130 which are upwardly and downwardly movable as the arms 122 and floats 124
move in the waves, cf. the above description of Fig. 1. Whereas there are shown three
cylinders in the diagram of Fig. 14, it should be understood that the apparatus according to
the invention typically comprises a larger number of cylinders, e.g. 60 cylinders. The
cylinders 128 are shown as double-acting cylinders connected at their upper ends to feeding
conduits 176 for a hydraulic medium of the system. In each feeding conduit 176 there is
provided a pressure valve 178. The feeding conduits 176 merge into a common main conduit
180, which feeds into a hydraulic motor 182 with variable volume displacement per
revolution. In the feeding conduits 176 and common main conduit 180, there is maintained
an operating pressure p0. The pressure p0 may advantageously also be the threshold
pressure of valve 178, at which the valve switches between its open and closed state. The
hydraulic motor drives an electric generator 184, and at the exit of the hydraulic motor, the
hydraulic medium is led to a reservoir 186. From the reservoir 186, the hydraulic medium
flows back to the cylinders 128 via a common return conduit 188 and branch return conduits
190.
In each of the cylinders 128, the piston 130 divides the cylinder in upper and lower chambers
192, 194 which are interconnected via conduits 196 and 198. In each of the conduits 196
there Is provided a two-way valve 200, and in parallel thereto there is provided, in conduit
198, a pressure valve 202 and a series flow control valve 204. Finally, each cylinder is
provided with a control element 206 for determining the position and/or rate of movement of
the piston 130 of the cylinder 128.
When the two-way valve 200 is open, the piston 130 may move freely when the arms 122
(see Fig. 1) move In the waves. When the control element 206 determines a certain position
and/or rate of movement of the piston 130, a control signal is passed to the valve 200
causing the valve 200 to shut. As the pressure valve 178 is shut, the piston 130 will be
locked while the wave continues to rise until the buoyancy of the float Is large enough to
overcome the operating pressure p0 In the feeding and main conduits 176,180, so as to open
the pressure valve 178. It will thus be understood that the float 124 (see Fig. 1) is at least
partially submerged in the wave when the valve 178 opens (cf. also the below discussion of
Fig. 21). Once the pressure valve 178 has opened, the hydraulic medium is fed to the motor
182. When the float passes the wave crest, the float Is still submerged, but the pressure in
the upper part 192 of the cylinder 128 drops, and pressure valve 178 shuts. Subsequently,
the two-way valve 200 opens, and hydraulic medium is displaced from the lower cylinder part
194 to the upper cylinder part 192, as the float moves down the wave from the wave crest to
the wave trough.
It will be appreciated that, due to the large number of cylinders 128, it is at all times ensured
that at least two of them, and preferably several, deliver a flow of hydraulic medium to the
motor 182. Thereby, an even power output from the generator 184 may be ensured,
preferably without any need for frequency converters.
The above description of Fig. 14 also applies to the Fig. 15, however in the embodiment of
Fig. 15 there is provided a plurality of hydraulic motors 182,208,210 are provided. Each of
the hydraulic motors 182,208,210 is connected to respective electric generators
184,212,214. In the embodiment of Fig. 15, only three hydraulic motors and electric
generators are provided, but in other embodiments the wave power apparatus comprises a
higher number of motors and generators. For example 5, 10 or 20 motors and generators
may be provided. The capacity of the hydraulic motors and their corresponding electric
generators may be chosen so as to make it possible generate different levels of energy. In
one example, the three generators may be able to produce 0.5 MW, 0.5 MW and 2 MW,
respectively. Thus, in order to produce 1 MW, the hydraulic motor of the two 0.5 MW
generators may be connected to the common main conduit 180, whereas the third generator
should be disconnected from the main conduit 180. At sites where the wave energy Is
substantially constant over time, the capacity of the generators and their corresponding
hydraulic motors may each be chosen to be at the highest possible level in order to reduce
the total number of hydraulic motors and generators. At sites at high fluctuation of the wave
height and wave frequency, the capacity of the generators may be chosen from a binary
principle e.g. 1 MW, 2 MW and 4 MW. By choosing the generators from a binary principle it is
possible to couple said generators in and out in using the below pattern so as optimise the
utilisation of the wave energy.
The system of Fig. 16 Is similar to the system of Fig. 15, however in the system of Fig. 16
there is only provided one single electric generator 184, which is driven by the hydraulic
motors 182, 208 and 210 via a gearbox 185. The hydraulic motors may e.g. drive a toothed
rim of a planet gear. Alternatively, as shown in Fig. 17, the hydraulic motors 182, 208 and
210 may drive one common generator 184 via a common, through-going shaft 187.
Fig. 18 illustrates a hydraulic lifting system for lifting the floats 124 out of the ocean and for
keeping them in an elevated position, In which the waves cannot reach the floats. Fig. 18 also
includes a hydraulic driving system similar to the driving system described above in
connection with Figs. 14-17. To the extent that the same or similar elements are
incorporated in the driving system depicted in Fig. 18 as those depicted in Figs. 14-17, the
reference numerals of Fig. 6 are used in Fig. 8, and reference is made to the above
description of Figs. 14-17 for a description of such elements and their functionality. The
hydraulic lifting system of Fig. 18 is adapted to individually lift one or more floats 124 out of
the water and to decouple the cylinders of the lifted floats from hydraulic driving system. The
system of Fig. 18 Includes, in addition to the common return conduit 188, a conduit 266
connecting the reservoir 186 to a pump 268 driven by a motor 270, Conduit 272 connects
the downstream side of the pump 268 to a number of one-way valves 274, the number of
one-way valves being equal to the number of floats and cylinders 128. Conduits 276 connect
respective downstream sides of the valves 274 to respective two-way valves 278 and one-
way valves 280, downstream of which the conduits 276 merge into one common conduit 282.
The conduits 276 communicate with the lower cylinder chambers 194 and conduits 198 via
conduits 284. Further, the conduits 276 communicate with the upper cylinder chambers 192
and feeding conduits 176 via the conduits 196. Finally, two-way valves 286 are provided in
the branch return pipes 190, and two-way valves 288 are provided in conduits 198.
When an arm is to be lifted out of the water, valve 278, valve 286 and valve 288 shut. Valve
274 and 280 open, and the pump 268 may force hydraulic medium into the lower cylinder
chamber 194, and the arm associated to the cylinder in question is elevated. Hydraulic
medium in the upper cylinder chamber 192 Is conducted to the reservoir 186 via valve 280.
The control element 206 detects that the arm and with it the piston 130 has reached its
desired position, e.g. its uppermost position, and a signal is passed to valves 274 and 280
causing them to shut. The piston 130 is consequently locked, and the arm is secured in a
position, in which the float 124 is lifted out of the water. The arm 122 may be further
supported by a pawl (not shown) engaging the arm.
Fig. 19 is a diagrammatic illustration showing a plurality of floats 124 and 164 which are
coupled to a hydraulic driving system via cylinders as described above in connection with
Figs. 14-18. In Fig. 19, those floats which are located at wave crests 146,148 are referred to
by reference numeral 164, whereas all other floats are referred to by reference numeral 124.
There is, however, no structural difference between the floats 124 and the floats 164. First,
second and third wave crests 146,148,150 are indicated by double lines in Fig. 19, and first
and second wave troughs 152,154 are indicated by single lines in the figure. The direction of
movement of the wave fronts is indicated by a first arrow 156, the wave length being
indicated by a second arrow 158 and the rising and falling parts of the waves are indicated by
third and fourth arrows 160,162, respectively. As indicated in Fig. 19, those floats 164, which
are at the wave crests 146 and 148 have thus just completed their upwards movement
caused by the waves. Those floats 124 which are between the first wave crest 146 and the
first wave trough 152 are on their way upward in the wave, whereas those floats which are
between the second wave crest 148 and the first wave trough 152 are moving down along a
downstream side of the wave. As the array of floats 124, 164 spans over a full wave length, a
plurality of floats Is on their way upwards In a wave at any moment, whereby It is ensured
that a plurality of floats deliver a power contribute to the hydraulic driving system at any
time. As described above with reference to Figs. 14-17, each of the floats actuates a
hydraulic cylinder, and hydraulic pressure is created in the main conduit 180 (cf. Figs. 14-
17). As a plurality of the floats are moving upwards at the same time, a plurality of hydraulic
cylinders provide hydraulic pressure simultaneously. Accordingly, thanks to the provision of
the common main conduit 180 connected to a plurality of cylinders with respective floats and
thanks to the extent of the array of floats over at least a full wave length, the pressure
fluctuations In the common main conduit 180 and thus the pressure fluctuations at the input
to the hydraulic motor 182 or motors 182, 208, 210 may be kept low. As the hydraulic
motors 182, 208 and 210 are motors with variable displacement per turn, the rpm of the
motors may be kept essentially constant. This in turn confers the effect that the frequency of
AC current generated by the generator 184 or generators 184, 212 and 214 is essentially
constant, whereby it is achieved that, in preferred embodiments of the invention, AC current
may be generated without the need for frequency converters.
In Fig. 19, the wave direction defines an angle 8 with respect to the row of floats. The wave
direction is parallel to the row of floats when e = 0°. It will be understood that the larger the
angle 9 is to 0° the longer must be the row of floats In order to ensure that at any given
moment at least one float Is moved upwards by a wave to deliver a pressure contribute in the
common main conduit 180 (cf. Figs. 14-17) of the hydraulic driving system.
In designing the system the typical wave length and directions of the location should be
taken into account in order to ensure a substantially constant hydraulic pressure in the
system. In preferred embodiments of the invention, the relationship between the wave
direction (angle G) and the length of the wave power apparatus, i.e. the length spanned by
the floats 124, 164, may be determined by the following formula:
Fig. 20 shows the hydraulic pressure 242 in the common main conduit 180 (cf. Figs. 14-17)
as a function of time 240. The first curve 244 shows the hydraulic pressure in a feed line of a
typical prior art wave power apparatus with hydraulic cylinders feeding one accumulator with
a hydraulic motor. As indicated in Fig. 20, the hydraulic pressure fluctuates with a wave
period 246. The hydraulic pressure 248 in an embodiment of the wave power apparatus of
the present Invention comprising a plurality of arms, floats and cylinders and no
accumulators fluctuates with a lower amplitude.
Fig. 21 illustrates two different travel paths of a float across a wave which moves In the
direction of arrow 171. The upper part of Fig. 21 Illustrates a flow path, at which no
measures are taken to increase the vertical travel distance the float 124 when the float is
passed by a wave. The lower part of Fig. 21 illustrates a flow path, at which the vertical
travel distance of the float is increased by actively forcing the float 124 into the water at the
wave trough 152.
In the upper part of Fig. 21, at position 172a, the float 124 is moving downwards with the
wave until the float reaches the wave trough 152 at position 172b. At this point the hydraulic
cylinder is locked as pressure valve 178 shuts (cf. Figs. 14-17), two-way valve 200 being also
shut, and accordingly the float moves horizontally into the wave to position 172d via position
172c. As the wave rises, pressure builds up in the upper chamber 192 of the cylinder 128
and In the conduit upstream of the pressure valve 178 (cf. 14-17). At position 172d, the
pressure is sufficient to overcome the threshold pressure of pressure valve 178, which opens,
whereby the float 124 is allowed to move upwards in the wave to position 172f via position
172e. During this movement, the hydraulic cylinder 128 of the float 124 feeds hydraulic
medium into the common hydraulic conduit 180, whereby a power contribute is delivered to
the hydraulic motor 182 or motors 182, 208, 210. At position 172f, when the passing wave is
about to descend, the pressure in the feeding conduit 176 drops below the shut-off threshold
of pressure valve 178, which shuts. As soon as the pressure valve 178 shuts and two-way
valve 200 opens, the float 124 is uncoupled from the common hydraulic conduit 180 and the
buoyancy of the float 124 causes it to move essentially vertically out of the water to position
172g. As the wave descends, the float 124 moves downwards with the wave to position
172h, and the float starts a new cycle in the next wave. The float 124 travels a vertical
distance 168. From the above description of Fig. 21, it will be appreciated that the power
contribute of each individual float 124 and associated cylinder 128 to the hydraulic driving
system is conferred during the vertical movement of float.
In order to Increase the power output of the wave power apparatus it is thus desirable to
increase the vertical travel distance of the float 124. The lower part of Fig. 21 illustrates an
alternative travel path of the float 124 across the wave, in which measures are taken to
increase the vertical distance travelled by the float 124. At position 174a, the float 124 is
descending at the downstream side of a wave. At position 174b, the float 124 has reached
the wave trough 152. At this point, the float is forced downwards under the water to position
174c, and pressure valve 178 and two-way valve 200 shut (cf. Figs. 14-17). As the pressure
upstream of the pressure valve 178 exceeds the threshold shut-off pressure of the pressure
valve 178, the valve 178 opens, and the float 124 moves to position 174g via 174d, 174e
and 174f. At position 174f, pressure valve 178 shuts and two-way valve 202 opens, and the
buoyancy of the float 124 causes the float to move essentially vertically out of the water to
position 174h, from which the float descends on the downstream side of the wave to position
1741, and the above cycle is repeated. Thanks to the forcing into the water of the float at the
wave crest 152, i.e. from position 174b to position 174c, the vertical distance 170 travelled
by the float is significantly larger than the vertical distance 168 travelled in embodiments, in
which the float is not forced down into the wave at or near a wave trough, cf. the upper part
of Fig. 21. Thus, the power contribute of the cylinder 128 of a float 124 is also significantly
larger in respect of the path of the lower part of Fig. 21 than in respect of the path of the
upper part of Fig. 21.
Evidently, a net gain in terms of overall power output of the wave power apparatus arises
only if the power utilized for forcing the float 124 into the wave at the wave trough 152 Is not
deducted from the power output of the apparatus. Fig. 22 shows a modified embodiment of
the hydraulic driving system of Fig. 14, which may accumulate potential energy released as a
float 124 moves vertically out of a wave at or near a wave crest, i.e. from position 174g to
position 174h in the lower part of Fig. 21. This energy, which is lost in the embodiments of
Figs. 14-17, is used to force the float 124 Into the wave.
More specifically, Fig. 22 shows a hydraulic diagram with first, second, third and fourth
accumulators 216, 218,220,222 for forcing the floats down under the waves at wave troughs.
In addition to the system of Fig. 14, the hydraulic system of Fig. 22 comprises the hydraulic
accumulators 216,218,220,222, which are arranged at one end of hydraulic accumulator
conduits 224,226,228,230, which are connected to the feeding conduits 176 via first, second,
third and fourth two-way valves 232,234,236,238. Once a float has passed a wave crest, the
pressure valve 178 shuts as described above in connection with Fig. 14, and the float 124
moves out of the wave from its submerged position in the wave. The hydraulic medium,
which is thereby displaced from the upper part 192 of the cylinder, Is conducted to the
accumulators 216,218,220,222 via the valves 232,234,236,238 and the accumulator
conduits 224,226,228,230. In one embodiment, the valves 232,234,236,238 are arranged
and controlled such that the first valve 232 shuts at a first pressure pi, pi being lower than
the operating pressure pO in the main conduit 180. The second valve 234 opens at the first
pressure pi and shuts again at a lower, second pressure p2. The third valve 236 opens at the
second pressure p2 and shuts again at a lower, third pressure p3. The fourth valve 238
opens at the third pressure p3 and shuts again at a lower, fourth pressure p4. At a yet lower
pressure p5, the two-way valve 200 opens.
At a wave trough, the valve 200 shuts, the fourth two-way valve 238 opens, and the
pressure In the fourth accumulator 222 is utilized to force the float under the water. As the
fourth two-way valve 238 shuts, the third two-way valve 236 opens, and the pressure in the
third accumulator 220 is utilized to force the float further under the water. Hereafter the third
two-way valve 236 shuts, and the second two-way valve 234 opens, and the pressure in the
second accumulator 218 Is utilized to force the float even further under the water.
Subsequently, the second two-way valve 234 shuts, and the first two-way valve 232 opens
such that the pressure in the first accumulator 216 is used to force the float further under the
surface of the water. Finally, the first two-way valve 232 shuts, and the pressure valve 178
opens.
It will thus be appreciated that at least a portion of the potential energy released as the float
124 moves vertically out of the wave from position 174g to position 174h (cf. the lower part
of Fig. 21) may be utilized for forcing the float Into the water at a wave trough 152 In order
to increase the power output of the wave power apparatus. Accordingly, the forcing down of
a float by in the manner described above may be regarded as a way of utilizing the potential
energy released at wave crests, which energy would otherwise be lost.
There may be provided more than four accumulators 216, 218, 220 and 222. For example,
there may be provided six, eight, ten, twelve, twenty or even more accumulators.
Fig. 23 generally shows a graphical representation of the accumulation of energy in N steps,
I.e. In N accumulators corresponding to the accumulators 216, 218, 220 and 222 of Fig. 22.
The first axis Indicates the vertical displacement d0 250 of the float in water, and the second
axis indicates the force F0 252. The area of the hatched triangle covering half of the diagram
of Fig. 23 indicates the ideal maximal energy, which is available. However, in order to utilize
this energy, the system should comprise an infinitive number of steps, i.e. an infinite number
of accumulators. In other words, the larger the pressure difference is between two steps, the
larger is the loss of energy for each step. In Fig. 23, the energy loss is indicated by hatched
triangles 254. Each triangle indicates that the float is displaced a vertical distance Ad. The
area of each of the small triangles is half height times length. Thus, the loss at each step
may be determined by the following formula:
Wherein
F0 is the excursion force when the float is forced the distance d0 under the water,
Ad = do/N, and
N is the number of steps.
The total loss of energy i.e. the sum of the small triangles, is defined by the following
formula:
Accordingly, the larger the number of step N, the smaller Is the total loss of energy.
The effect of the accumulators discussed above in connection with Figs. 22 and 23 is shown
in Fig. 24, in which curve 256 shows the movement of the float in the wave as a function of
time, and curve 258 shows the shape of a wave as a function of time. There is a partial
overlap of the curves 256 and 258 at the downstream, i.e. descending, side of a wave, At
260, two-way valve 200 shuts (cf. Fig. 22) while pressure valve 178 is also shut, and the
float is locked. At 262, the float moves out of the wave and delivers energy to the
accumulators 216,218,220 and 222. In Fig. 25, curve 264 shows the actual depression of
the float in the wave.
We Claim:
1. A wave power apparatus comprising:
- a plurality of arms, each of which is rotationally supported at one end
by a shaft, and wherein each arm carries a float at its other end, which
is opposite to the supported end, so that a translational movement of
the float caused by a wave results in rotation of the arm around the
shaft,
- power conversion means for converting power transmitted from the
wave to the arms into electric power, the plurality of arms being
arranged in a row such that a wave passing the row of arms causes
the arms to successively pivot around the shaft, the arms being
arranged at mutual distances, so that the passage of the wave causes
the arms to pivot with a mutual phase shift, the power conversion
means comprising a hydraulic driving system with a hydraulically
driven motor,
wherein each arm is connected to the hydraulic driving system by means
of at least one hydraulic cylinder which causes a hydraulic medium of the
hydraulic driving system to be displaced into the motor, the cylinders
being arranged to displace the hydraulic medium to the motor via
common hydraulic conduits,
characterized in that
each cylinder is provided with a sensor for determining a position and/or
rate of movement of the cylinder's piston, the sensor being arranged to
transmit a signal to a control unit of the cylinders and associated valves,
so that the transmission of energy from each individual cylinder to the
remaining parts of the hydraulic driving system is individually controllable
in response to the signal representing the individual cylinder's piston's
position and/or rate of movement.
2. A wave power apparatus as claimed in claim 1, wherein the row of
arms is oriented such with respect to the wave heading that the row
forms an angle of within +/- 60° with respect to the heading.
3. A wave power apparatus as claimed in claim 1 or 2, wherein each of
the arms intermittently transmits power to the power conversion means
when a wave passes the float of the arm, the arms and floats being
arranged with such mutual distances that, at all times, at least two arms
and floats simultaneously deliver a power contribute to the power
conversion means.
4. A wave power apparatus as claimed in any of the preceding claims,
wherein buoyancy of the float is at least 10 times its dry weight.
5. A wave power apparatus as claimed in any of the preceding claims,
wherein the diameter of the float is at least 5 times its height.
6. A wave power apparatus as claimed in any of the preceding claims,
wherein the plurality of arms comprises at least five arms per wavelength
of waves.
7. A wave power apparatus as claimed in any of the preceding claims,
wherein the plurality of arms comprises at least five arms spanning over a
total length of 50 - 200 m.
8. A wave power apparatus as claimed in any of the preceding claims,
wherein the arms and the floats are made from a material which has a
density of at most 1000 kg/m3.
9. A wave power apparatus as claimed in claim 1, wherein the at least
one hydraulic cylinder of each arm comprises a double-acting cylinder.
10. A wave power apparatus as claimed in claim 9, wherein the hydraulic
driving system comprises at least one hydraulic accumulator for
intermittently storing energy in the hydraulic driving system, and wherein
the hydraulic driving system is controllable to release the energy stored in
the accumulator, when a float is passed by a wave trough, so as to force
the float carried by the arm into the wave.
11. A wave power apparatus as claimed in claim 1 and 10, wherein the
hydraulic medium is fed to the hydraulic accumulator via the common
hydraulic conduits.
12. A wave power apparatus as claimed in any of the preceding claims,
wherein the shaft and the power conversion means are supported by a
supporting structure which is anchored to the sea floor by means of a
suction anchor or a gravitational support.
13. A power apparatus as claimed in claim 12, wherein the supporting
structure comprises a truss structure, and wherein the suction anchor is
arranged in a first nodal point of the truss structure.
14. A wave power apparatus as claimed in claim 13, wherein the at least
one arm is supported by the truss structure in a second nodal point
thereof.
15. A wave power apparatus as claimed in claim 14, wherein said second
nodal point is arranged at a summit of a triangular substructure of the
truss structure, and wherein the triangular substructure defines two
vertices at the sea floor, with an anchor in each of the corners.
16. A wave power apparatus as claimed in claim 15, wherein the truss
structure comprises a polygonal substructure, preferably a rectangular
substructure, arranged above the triangular substructure.
17. A wave power apparatus as claimed in any of claims 12-16, wherein
the supporting structure comprises a ballast for providing a downward
force on the supporting structure, the ballast being arranged above sea
level.
18. A wave power apparatus as claimed in claim 17, wherein the ballast
comprises at least one ballast tank or ballast container.
19. A wave power apparatus as claimed in any claims 12-18, wherein the
arm is connected to the shaft at at least two points along the shaft, which
are offset from a centre axis of the arm, and wherein the shaft is
rotatably supported by a fixed support structure which comprises two
bearings arranged to counteract radial and axial forces.
20. A wave power apparatus as claimed in claim 19, wherein the bearings
are pre-stressed in an axial direction.
21. A wave power apparatus as claimed in claim 19 or 20, comprising a
plurality of arms and a plurality of shafts, so that each arm is supported
by its own shaft, each arm being connected to its own shaft at at least
two points along the shaft, which are offset from a centre axis of the arm,
wherein each shaft is rotatably supported by the fixed support structure
by two bearfngs arranged to counteract radial and axial forces.
22. A wave power apparatus as claimed in any of claims 19-21, wherein
each of the bearings comprises an inner and an outer ring or cylinder, the
inner ring being secured to a rotational shaft of the arm, and the outer
ring being secured to a fixed support, the bearing further comprising a
flexible material between the inner and the outer ring.
23. A wave power apparatus as claimed in claim 22, wherein the flexible
material comprises at least one cavity or perforation.
24. A wave power apparatus as claimed in claim 22 or 23, wherein the
flexible material comprises at least one spring member, such as a flat
spring.
25. A wave power apparatus as claimed in any of the preceding claims,
comprising a hydraulic lifting system for lifting the float out of the ocean
and for locking the float in an upper position above the ocean surface.
26. A wave power apparatus as claimed in claim 9 and 25, wherein
the double-acting cylinder forms part of the hydraulic lifting system,
so that the cylinder is controllable to lift the float out of the ocean.


A wave power apparatus includes a plurality of rotationally supported
arms, each of which carries a float (124) at its free end, so that a translational
movement of the float caused by a wave results in rotation of the arm. The
apparatus comprises power conversion means for converting power transmitted
from the wave to the arms into electric power, e.g. a hydraulic system, in which a
hydraulic fluid is displaced by the movement of the arms to drive one or more
hydraulic motors. The plurality of are arranged in a row such that a wave passing
the row of arms causes the arms to successively pivot with a mutual phase shift.
Thereby, an even power output may be achieved, and the need for frequency
converters may be reduced or eliminated. Preferably, each arm is connected to a
hydraulic cylinder of the hydraulic system, whereby a plurality of arms feed
hydraulic medium into the hydraulic motor or motors through common hydraulic
conduits.

Documents:

01035 kolnp-2006 abstract.pdf

01035 kolnp-2006 form-3.pdf

01035 kolnp-2006 form-5.pdf

01035 kolnp-2006 international publication.pdf

01035-kolnp-2006 claims.pdf

01035-kolnp-2006 correspondence others.pdf

01035-kolnp-2006 description (complete).pdf

01035-kolnp-2006 drawings.pdf

01035-kolnp-2006 form-1.pdf

01035-kolnp-2006 international search authority report.pdf

01035-kolnp-2006 pct form.pdf

01035-kolnp-2006-assignment.pdf

01035-kolnp-2006-correspondence others-1.1.pdf

01035-kolnp-2006-form-3-1.1.pdf

1035-KOLNP-2006-FORM-27.pdf

1035-kolnp-2006-granted-abstract.pdf

1035-kolnp-2006-granted-assignment.pdf

1035-kolnp-2006-granted-claims.pdf

1035-kolnp-2006-granted-correspondence.pdf

1035-kolnp-2006-granted-description (complete).pdf

1035-kolnp-2006-granted-drawings.pdf

1035-kolnp-2006-granted-examination report.pdf

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1035-kolnp-2006-granted-reply to examination report.pdf

1035-kolnp-2006-granted-specification.pdf

1035-kolnp-2006-REPLY TO EXAMINATION REPORT.pdf

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Patent Number 240348
Indian Patent Application Number 1035/KOLNP/2006
PG Journal Number 19/2010
Publication Date 07-May-2010
Grant Date 05-May-2010
Date of Filing 21-Apr-2006
Name of Patentee WAVE STAR ENERGY APS
Applicant Address MAGLEMOSEVEJ 61, DK-2920 CHARLOTTENLUND
Inventors:
# Inventor's Name Inventor's Address
1 RESEN STEENSTRUP PER MAGLEMOSEVEJ 61, DK-2920 CHARLOTTENLUND
2 HANSEN KELD HOVEDGADEN 63, DK-6621 GESTEN
3 ARPE HANSEN NIELS GRONLANDSPARKEN 88C, DK-6715 ESBJERG N
PCT International Classification Number F03B 13/18, 11/06
PCT International Application Number PCT/DK2004/000704
PCT International Filing date 2004-10-14
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 PCT/DK2003/00693 2003-10-14 IB