WO2012098362A1 - Rotor - Google Patents

Rotor Download PDF

Info

Publication number
WO2012098362A1
WO2012098362A1 PCT/GB2012/000055 GB2012000055W WO2012098362A1 WO 2012098362 A1 WO2012098362 A1 WO 2012098362A1 GB 2012000055 W GB2012000055 W GB 2012000055W WO 2012098362 A1 WO2012098362 A1 WO 2012098362A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
conic
radius
generators
helix
Prior art date
Application number
PCT/GB2012/000055
Other languages
English (en)
Inventor
Jason Dale
Aage Bjørn ANDERSEN
Original Assignee
Sea-Lix As
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sea-Lix As filed Critical Sea-Lix As
Publication of WO2012098362A1 publication Critical patent/WO2012098362A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/24—Non-positive-displacement machines or engines, e.g. steam turbines characterised by counter-rotating rotors subjected to same working fluid stream without intermediate stator blades or the like
    • F01D1/26—Non-positive-displacement machines or engines, e.g. steam turbines characterised by counter-rotating rotors subjected to same working fluid stream without intermediate stator blades or the like traversed by the working-fluid substantially axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/34—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes
    • F01D1/38—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes of the screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/10—Submerged units incorporating electric generators or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/12—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy
    • F03B13/26—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using tide energy
    • F03B13/264—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using tide energy using the horizontal flow of water resulting from tide movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B17/00—Other machines or engines
    • F03B17/06—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head"
    • F03B17/061—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head" with rotation axis substantially in flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/04—Machines or engines of reaction type; Parts or details peculiar thereto with substantially axial flow throughout rotors, e.g. propeller turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/12—Blades; Blade-carrying rotors
    • F03B3/121—Blades, their form or construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/12—Blades; Blade-carrying rotors
    • F03B3/126—Rotors for essentially axial flow, e.g. for propeller turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/40—Flow geometry or direction
    • F05B2210/404—Flow geometry or direction bidirectional, i.e. in opposite, alternating directions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F05B2240/13—Stators to collect or cause flow towards or away from turbines
    • F05B2240/133—Stators to collect or cause flow towards or away from turbines with a convergent-divergent guiding structure, e.g. a Venturi conduit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/40—Use of a multiplicity of similar components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/20—Geometry three-dimensional
    • F05B2250/23—Geometry three-dimensional prismatic
    • F05B2250/232—Geometry three-dimensional prismatic conical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/20—Geometry three-dimensional
    • F05B2250/25—Geometry three-dimensional helical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/30—Arrangement of components
    • F05B2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
    • F05B2250/311—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being in line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/501—Inlet
    • F05B2250/5011—Inlet augmenting, i.e. with intercepting fluid flow cross sectional area greater than the rest of the machine behind the inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • the invention relates to a rotor for extracting energy from a flowing liquid, for example a tidal flow.
  • a flowing fluid possesses kinetic energy due to its motion.
  • Naturally occurring fluid flows can be found in tidal currents, coastal or oceanic currents, river flows, thermal currents, air currents and elsewhere.
  • Fluid flows can also be generated by man directly or indirectly.
  • secondary fluid flows may be generated upstream or downstream of an obstacle placed in a naturally occurring fluid flow such as a dam in a river.
  • Fluid flows may be generated by the transport of a fluid in a pipeline or by a machine such as fluid flows in a fluid system installed on a train, on a ship or on an automobile.
  • Energy conversion from gas flows such as air currents, i.e. wind-power
  • Numerous specially designed turbines have been made for extracting energy from the wind.
  • the potential energy level is much larger in a liquid flow than in a gas flow because the fluid density is generally higher.
  • fluid speeds in excess of 5 m/s may be generated, although a more typical speed may lie in the range of 1 .5 - 2.5 m/s.
  • the energy density of tidal currents can typically be of the order of 4000 W/m 2 .
  • the density of air is around 1.2 kg/m 3 , therefore the energy density of wind at this speed is typically around 5 W/m 2 , this being around 800 times less than that available in a corresponding tidal current.
  • the invention provides a rotor comprising: at least one blade arranged to rotate about an axis of rotation, the blade being formed by a surface extending between inner and outer conic helixes; an inner surface and an outer rim enclosing the blade, the inner and outer surfaces following inner and outer generally conical surfaces of revolution corresponding to the paths of the conic helixes, wherein the conic helixes each have a pitch that decreases as the radius of the helix increases and wherein the blade extends between and is mounted to both the outer rim and the inner surface
  • a conic helix is a three dimensional curve formed on a surface of a generally conical body.
  • the surface of the generally conical body may be conical, frustoconical or any other shape formed as a surface of revolution that has a generally increasing or decreasing radius.
  • the surface is not specifically limited to a straight sided cone but could instead be a convex sided cone or frustocone such as a zone or ogive nose cone shape, or alternatively the cone could be a concave sided cone or frustocone.
  • each conic helix is formed with a radius that increases along an axis of the rotor and a pitch that decreases as the radius increases.
  • the inner and outer conic helixes preferably have the same decrease in pitch, although applications are possible where a different decrease in pitch for the inner and outer conic helix may be used.
  • inner and outer are used herein to refer to portions of the rotor that are at a smaller or greater radius from the axis of rotation of the rotor.
  • the rotor has one or more flow passages formed between front and back blade surfaces, the outer rim and the inner surface.
  • the flow passages effectively contain the flowing fluid and prevent energy being lost due to tip losses. Since the blade extends between and is mounted to both the outer rim and inner surface then the flow of fluid is fully contained and tip losses are minimised.
  • the rotor is for extracting kinetic energy from a liquid fluid flow or system of liquid fluid flows by converting the kinetic energy in the liquid fluid flow into a rotational force or torque, hence permitting onward conversion into a more convenient form of energy, such as electrical energy.
  • the rotor is a generator rotor for generation of electricity from tidal flows.
  • a preferred embodiment is therefore a generator comprising a rotor as discussed herein.
  • the rotor has an opening at the small diameter end of the rotor that is arranged for axial flow of fluid, preferably for solely axial flow.
  • the opening is perpendicular to the axis of rotation of the rotor and the blades are preferably formed to receive or expel fluid flowing in a generally axial direction and preferably without any (significant) radial flow.
  • the rotor has an opening at the large diameter end that is also perpendicular to the axis of rotation of the rotor.
  • the blades at the large diameter end are not arranged for solely axial flow, but instead may be adapted to receive or expel fluid flowing with a radial component to its movement.
  • a preferred embodiment does not permit flow of fluid through either opening of the rotor when the fluid flow has only a radial component and no axial component.
  • the inner and outer conic helix preferably start at the same longitudinal position along the axis of rotation of the rotor before extending along the direction of the axis of rotation of the rotor.
  • Preferably the inner and outer conic helix also extend for about the same axial length along the direction of the axis of rotation of the rotor.
  • the conic helix can be any suitable shape that allows for a three dimensional curve with an increasing radius and decreasing pitch as described above.
  • One preferred option is the use of an Archimedean spiral with a linear increase in radius, can be used to produce a rotor with a simple shape based on a straight sided frustocone.
  • the conic helix could alternatively be based on Euler, Fibonacci, Hyperbolic, Lituus, Logarithmic,
  • Theodorus or any other known spiral having varying radius r as a function of the polar coordinate ⁇ but also having a third variable, the length I, varying also as function of the polar coordinate ⁇ .
  • the inner and outer conic helix may be based on the same form of spiral or curve, with different initial and final radii. Alternatively, different forms of curve or spiral could be used for the inner and outer conic helix to produce a more complex shape for the blade.
  • the blade or blades are preferably formed as surfaces generated by straight lines between points on the inner and outer conic helixes at the same longitudinal distance along the direction of the axis of rotation of the rotor.
  • the blade surface may connect the pair of conic helixes in the radial direction.
  • the blades may be formed as surfaces generated by curves between points on the inner and outer conic helixes at the same longitudinal distance along the direction of the axis of rotation of the rotor. With this arrangement the blades surfaces may, for example, be concave when viewed from the large diameter end of the rotor.
  • the inner and outer conic helixes may both increase in radius at the same rate, such that the conic surfaces are generally parallel. However, it can be advantageous to adjust the performance of the rotor by having a different rate of increase in diameter for the inner and outer conic helixes.
  • the inner conic helix may increase in radius at a slower rate than the increase in radius of the outer conic helix in order to reduce or restrict the hydrodynamic reaction forces and torsional forces produced by the rotor.
  • the inner conic helix radius may increase at a faster rate than the outer conic helix radius in order to increase hydrodynamic reaction forces and torsional forces.
  • the rotor includes a housing located about the outer rim.
  • the housing may enclose the rotor and support bearings or shafts enabling rotation of the rotor.
  • the housing may include a convergent inlet and/or divergent outlet to condition the flow of fluid before it enters the rotor.
  • the rotor may be provided with one or more generators for converting the rotational movement of the rotor into electrical energy.
  • the outer rotating rim of the rotor may be arranged to act as the rotor in the electrical generator with a part of a stationary housing being the stator.
  • the inner peripheral surface may be arranged to act as the rotor with stationary parts along the axis of rotation of the rotor providing the stator.
  • the rotor and stator form an electrical generator set that is driven by the liquid flow and directly converts the motion of the rotor into electrical energy without the need to transfer the rotational force to an additional device.
  • Permanent or electro-magnets may be mounted on the outer rim of the rotor and on the inner of the rotor housing for this purpose.
  • the stator and the rotor formed may be configured in any suitable manner to produce alternating current (AC) or direct current (DC) in an efficient way.
  • Electronics and signal conditioning may be incorporated in the rotor housing or elsewhere to facilitate connection to an electrical network or a storage facility such as a battery installation.
  • magnets are not considered ideal for low speed applications. In low flow speed applications it is more efficient to have a large diameter rotor that is able to capture high levels of torque from the low speed fluid flow. This results in a relatively low speed of rotation of the rotor. A large number of magnets would be needed to directly generate the correct frequency for direct connection to a typical electrical grid. If a smaller number of magnets were used then additional electronic equipment would be required to condition the electrical signal to match the electrical grid.
  • the asynchronous generators can generate power that can then be fed directly to the grid at the correct frequency.
  • the rotor in this case may be a rotor with rotating peripheral inner and outer rims
  • large surface areas are available for connection to multiple high-speed, low torque generators.
  • Preferred embodiments therefore require the use of these generators, rather than a single generator connected to a central rotating shaft.
  • Several generators may be placed around the periphery of the rotating outer rim in order to extract the maximum power and/or be placed in the internal central space of the rotor and extract power from the rotating inner peripheral surface.
  • the connection between generator and either rim can be made with simple gearing or using a runner wheel.
  • the multiple generators may be arranged to be connected to the outer rim or inner peripheral surface at different diameters to thereby run at different rotational speeds relative to the speed of rotation of the rotor.
  • the outer rim and/or inner peripheral surface have a generally conical surface, and multiple generators may be moveably mounted parallel to a conical surface in order to permit variation of the input rotational speed to the generators by movement along the cone surface.
  • This arrangement operates in a similar fashion to some continuously variable transmission devices.
  • the generators may be moved along the surface by appropriate frame and stepper motors.
  • the generators may be mounted, for example, on the internal surface of the inner cone of the rotor, or on the external surface of the outer rim of the rotor.
  • multiple generators may be mounted to a stepped surface of the inner peripheral surface or outer rim, i.e. a surface comprised of multiple stacked cylinders of different diameters.
  • One or more rings of generators can preferably be engaged or disengaged at different speeds of rotation in order to generate electricity efficiently for the different speeds.
  • a first rotor as described above is provided in combination with a second rotor as described above, with the large diameter ends of the first and second rotors opposing one another, such that fluid exits the large diameter end of one rotor and then enters the large diameter end of the other rotor.
  • the rotors are both mounted for rotation about a single axis and are preferably arranged and mounted for contra-rotation, i.e. such that the first rotor rotates in the opposite direction about the axis to the second rotor.
  • the rotors may have blades that are formed from conic helixes that rotate in the same sense as the radius increases, i.e. both of the first and second rotors have blades that are formed clockwise as the conic helix radius increase, or alternatively both rotors have anti-clockwise blades. Further possible features of a preferred two-stage rotor arrangement are discussed below.
  • the invention provides a method comprising use of a rotor as described above for the production of rotational kinetic energy from flow of a fluid.
  • the method comprises use of the rotor to produce energy from a tidal flow, and more preferably use of the rotor to produce electrical energy from the tidal flow, for example in a generator.
  • the invention provides a method of manufacturing a rotor comprising at least one blade arranged to rotate about an axis of rotation, the method comprising: defining an inner conic helix and an outer conic helix, the conic helixes each having a pitch that decreases as the radius of the helix increases; and forming the blade(s) as a surface extending between inner and outer conic helixes.
  • the method may include providing features of the rotor and conic helixes as discussed above, including one or more of an outer rim, inner peripheral surface, shaft, starting position and length of conic helix, shape of conic helix, change of radius of conic helix, relative change of radius of inner and outer conic helixes, change of pitch of conic helix, number of blades, housing, generators, second rotor and so on.
  • the method comprises selecting the features of the rotor based on the desired characteristics of the rotor performance.
  • the method may comprise selecting the rate of change of radius of one conic helix or both conic helixes based on a desired torsional force output for a predetermined flow condition.
  • the predetermined flow condition might for example be the average tidal flow at an intended installation site, and the desired torsional force may be matched with optimal input torque for the intended output device, which might be a generator or multiple generators.
  • the method may comprise selecting the relative change of radius of inner and outer conic helix or selecting the change in pitch of one conic helix or both conic helixes based on a desired torsional force output for a predetermined flow condition.
  • the invention provides a rotor apparatus for extracting energy from bidirectional fluid flows, the rotor apparatus comprising a first rotor mounted for rotation about an axis of rotation in a first direction of rotation, the first rotor having at least one helical blade with a pitch that decreases in a direction along the axis of rotation; and a second rotor mounted for rotation about the same axis of rotation in an opposite direction of rotation and having at least one helical blade with a pitch that increases in the same direction along the axis of rotation, wherein fluid exiting the first rotor is passed to the second rotor.
  • each rotor Since the helical pitch of the helical blade is decreased in one direction each rotor possesses an optimum flow direction, which is from the larger pitch end to the smaller pitch end. Fluid entering parallel to the longitudinal axis and head-on to the larger helical pitch end would meet less of a resistance and would be gently guided into the rotor. As the fluid passes along the helical blade the decreasing pitch ensures efficient extraction of energy from the flow. Fluid could still flow parallel to the longitudinal axis and head-on in the non- preferred direction but power extraction would not be optimal since much energy would be lost in initially aligning the oncoming fluid flow to the angled rotor blades. Thus, conventionally rotors are designed with a preferred flow direction.
  • the rotor apparatus is a generator rotor, and hence a preferred embodiment comprises a generator including the rotor apparatus.
  • the above two-stage bidirectional rotor arrangement arises from the non-obvious realisation that when fluid exits a unidirectional helical bladed rotor the fluid will possess both a longitudinal and radial component and that this radial component will be well suited for entering the smaller helical pitch end of another unidirectional helical bladed rotor, when the two rotors have blades that turn in the same direction as the pitch decreases (i.e. both rotors having clockwise blades as the pitch decreases or both rotors having anticlockwise blades as the pitch decreases).
  • the fluid flow direction may enter from the smaller helical pitch end and flow towards the larger helical pitch end.
  • the two-stage rotor of this aspect enables energy to be extracted from flows in either direction along an axis without compromising the level of power production.
  • a preferred embodiment is a rotor apparatus for extracting energy from tidal flows, preferably by production of electricity, thereby the rotor apparatus functions as a tidal turbine.
  • a suitable bidirectional liquid flow might also be generated due to the regular back and forth or up and down movement of a ship or automobile.
  • first and/or second rotor(s) have an opening at the inlet or outlet end of the rotor apparatus that is arranged for axial flow of fluid.
  • the opening is perpendicular to the axis of rotation of the rotor apparatus and the blades are preferably formed to receive or expel fluid flowing in a generally axial direction, optionally in a solely axial direction.
  • the first and second rotors have openings at their opposed ends that are not arranged for solely axial flow, but instead may be adapted to receive or expel fluid flowing with a radial component to its movement.
  • a preferred embodiment does not permit flow of fluid through either opening of the rotor when the fluid flow has only a radial component and no axial component.
  • the first and second rotors have opposed ends that are of the same diameter.
  • the first rotor and/or second rotor may be a cylindrical rotor having a blade formed by a cylindrical helix.
  • the first rotor and/or second rotor have a blade or blades formed by a surface extending between inner and outer conic helixes, the conic helixes each having a pitch that decreases as the radius of the helix increases.
  • the rotors may have features as discussed above in relation to the first aspect of the invention, for example in relation to the shape and form of the conic helixes, the number of blades, the outer rim and inner peripheral surface, generator features and so on.
  • both the first rotor and the second rotor comprise a blade or blades formed between conic helixes
  • the two rotors have large diameter ends opposing one another and being of the same diameter.
  • the first and second rotors have ends opposing one another such that fluid flows from one rotor to the other.
  • the opposing ends are directly opposing, i.e. with a minimal gap in between the two rotors. This makes best used of the radial component of the flow exiting one rotor and entering the other.
  • the gap in between the two rotors may be increased to reduce the chopping effect between rotors. Then aquatic life may pass through the device unharmed by being carried along by the swirling flow.
  • first rotor and the second rotor have a blade or blades of the same shape formed by similar conic helixes. This ensures maximum bidirectionality since an identical fluid flow can enter the two-stage rotor apparatus from either end with the same resulting power take off.
  • the rotor apparatus may comprise a housing about the first and second rotors.
  • the housing preferably supports the rotors for rotation about the axis of rotation.
  • the rotor housing may be designed to perform various functions.
  • the rotor housing may be designed purely to house the rotors and provide support by way of mechanical bearings, magnetic bearings or some other type of active or passive bearing system which allows the rotors to freely rotate with low friction.
  • a sealing arrangement such as lip seals, labyrinth seals or some other type of sealing arrangement may also be in place to prevent the liquid flow from reaching the bearings or electrical components in the rotor housing. Or, some of the liquid flow may be directed towards the bearings and heat exchangers of electrical components and used as coolant in demanding applications.
  • the housing may also enclose generator parts, control systems and suchlike. Any suitable shape of housing may be used.
  • the rotor housing has an inlet section and an outlet section.
  • the rotor housing may be used to enhance the performance of the rotors.
  • the inlet geometry of the rotor housing may be designed to increase the linear velocity of the liquid flow as it enters the rotor entrance through use of a convergent section or some other geometry. Since the power available from the liquid flow is proportional to the cube of the liquid flow velocity, this provides an effective means of increasing the amount of available energy.
  • the outlet of the rotor housing may also be designed to slow down the liquid flow in a controlled manner through the use of a divergent section or specially designed outlet geometry so that viscous and turbulence losses are minimised and the fluid is gently returned to the main bulk of fluid flow with minimal disturbance.
  • the invention provides a method comprising use of a two-stage rotor apparatus as described above for the production of rotational kinetic energy from flow of a fluid.
  • the method comprises use of the two-stage rotor apparatus to produce energy from a tidal flow, and more preferably use of the rotor to produce electrical energy from the tidal flow.
  • the invention provides a method of manufacturing a two-stage rotor apparatus comprising: mounting a first rotor for rotation about an axis of rotation, the first rotor having at least one helical blade with a pitch that decreases in a direction along the axis of rotation; and mounting a second rotor for rotation about the same axis of rotation in an opposite direction of rotation, the second rotor having at least one helical blade with a pitch that increases in the same direction along the axis of rotation.
  • the method may include providing features of the rotor apparatus as discussed above in relation to the fourth aspect.
  • the shape and form of the rotor may be selected as discussed above in relation to the method of the third aspect.
  • the invention provides a rotor for generation of electrical power from a fluid flow, the rotor comprising a surface having a diameter that varies along the length of the rotor, wherein multiple generators are mounted to receive rotational force from movement of the surface at varying diameters thereof.
  • the surface may be a generally conical surface or a stepped surface, as described above.
  • the term generally conical is intended to refer to not only perfect right cones but also truncated cones, convex cones and concave cones as discussed above.
  • the generators may be low torque, high speed, high efficiency generators such as asynchronous generators as discussed above.
  • Several generators may be placed around the periphery of a rotating outer rim in order to extract the maximum power and/or be placed in an internal central space of the rotor and extract power from the rotating inner rim.
  • the connection between generator and either rim can be made with simple gearing or using a runner wheel or some other means.
  • the rotor may have features as discussed above in relation to the rotor and two-stage rotor apparatus.
  • the generators may be moveably mounted parallel to a generally conical surface in order to permit variation of the input rotational speed to the generators by movement along the cone surface as discussed above.
  • the invention also encompasses use of the rotor described above for the production of electricity from fluid flows.
  • Figures 2A and 2B show the rotor of Figure 1 with the outer peripheral rim partially cut-away so that more detail of the rotor design is visible
  • Figures 3A and 3B are perspective views of the rotor of Figures 1 and 2 with the outer rim partially and fully omitted,
  • Figures 4A and 4B show an alternative embodiment of a rotor where the inner conic helix radius increases at a lesser rate than the outer conic helix radius
  • Figures 5A and 5B show a further alternative where the inner conic helix radius increases at a greater rate than the outer conic helix radius
  • Figures 6A and 6B show an alternative embodiment where the helical pitch is decreased at a lesser rate than the rotor of Figures 1 and 2 ,
  • Figures 7A and 7B show an alternative embodiment where the helical pitch is decreased at a greater rate than the rotor of Figures 1 and 2,
  • Figures 8A and 8B illustrate an embodiment of a two-stage rotor apparatus arrangement in side view and end view with the outer rim partially omitted
  • Figures 9A and 9B are perspective views of the two-stage rotor apparatus of Figure 8 with the outer rim partially and fully omitted,
  • Figure 10 shows a two-stage rotor apparatus installed in a housing with generators on the outer rotor surface
  • Figure 1 1 shows a two-stage rotor apparatus installed in a housing with generators on an inner conical rotor surface
  • Figure 12 shows an alternative arrangement with generators on a stepped inner rotor surface
  • Figure 13 illustrates an arrangement with a pair of two-stage rotor apparatus installed on a tower type of structure for use on the sea bed
  • Figure 14 is a graph showing the variation in torsional forces generated by a two stage rotor apparatus as the ratio of the minimum radius do and maximum radius Do of the conic helix is changed
  • Figure 15 is a graph showing the variation in torsional forces generated by a two stage rotor apparatus with modification to the rate at which the inner conic helix radius increases compared to the outer conic helix radius, and
  • Figure 16 is a graph showing the variation in torsional forces generated by a two stage rotor apparatus when the rate of decrease of the helical pitch is adjusted by altering the rate of increase of helical frequency.
  • Figures 1 A and 1 B depict an embodiment of a rotor including an outer peripheral rim 1 , blades 2 and inner peripheral surface 3.
  • the rotor can be used to turn the flow of a liquid into rotational movement that can then be used to generate electricity.
  • the rotor is used in a turbine for generating electricity from tidal flows.
  • the blades 2 extend between the inner peripheral surface 3 and the outer rim 1 and hence form enclosed flow paths.
  • the underlying spiral that forms the shape of the blades 2 is based upon an Archimedean spiral where there is a linear increase in radius r with the polar coordinate ⁇ .
  • the resulting rotor therefore has the shape of a frustum of a cone.
  • Three rotor blades 2 can be seen within the rotor and also the inner peripheral surface 3.
  • the longitudinal axis of the rotor 4 is shown by a centre line.
  • the maximum outer diameter of the rotor is denoted by Do and the minimum outer diameter by do.
  • the length of the rotor is denoted by L and the local length I is measured from the end of the rotor having the minimum outer diameter do.
  • FIGS 2A and 2B depict the rotor of Figures 1 A and 18 with outer peripheral rim 1 partially hidden for clarity.
  • the inner peripheral rim 3 is also highlighted.
  • the three rotor blades 2 have a shape formed by a pair of conic helixes.
  • Outer conic helix 5 is a helix formed on the internal surface of the outer rim 1 and forms a varying outer radius ro of the blade 2.
  • Inner conic helix 6 is a helix formed on the outside of the inner cone 3 and forms a varying inner radius ri of the blade.
  • Both of the helixes have an increasing radius and a decreasing helical pitch along the longitudinal axis 4.
  • the blades 2 have a decreasing helical pitch resulting from an increasing helical frequency.
  • the pair of conic helixes 5 and 6 are generated in a clockwise direction and have different initial radii which increase at an equal rate to form a pair of parallel conic helixes
  • Figures 3A and 3B show perspective views of the rotor of Figures 1 and 2 in which further detail of the shape of the blades 2 can be seen.
  • Figures 4A and 4B show a variation of the rotor.
  • the pair of conic helixes 5 and 6 are generated in a clockwise direction and form the shape of the blades 2 in the manner discussed above.
  • the radius ri of the inner conic helix 6 increases at a lesser rate than the radius ro of the outer conic helix 5 to thereby form a pair of non-parallel conic helixes that are spaced further apart at the large diameter end of the rotor than at the small diameter end of the rotor.
  • Figures 5A and 5B show a further variation in which the radius ri of the inner conic helix 6 increases at a greater rate than the radius ro of the outer conic helix 5 to thereby form a pair of non-para!!e! conic helixes that are spaced closer together at the large diameter end of the rotor than at the small diameter end of the rotor.
  • Figures 6A and SB show a further variation which has parallel inner and outer cones as in Figures 1 and 2 , but in which the helical pitch decreases at a slower rate than the previously described embodiments. This results in a slower rate of increase of the helical frequency.
  • Figures 7A and 7B show the opposite variant in which the helical pitch decreases at a greater rate resulting in a faster rate of increase of the helical frequency.
  • Figures 8A, 8B, 9A and 9B show a pair of rotors in a two-stage rotor apparatus that may function as a tidal turbine.
  • Figures 8A and 8B are side and end views with the outer rim 1 partially omitted.
  • Figures 9A and 9B are perspective views of the same rotor pair with the outer rim 1 partially and fully omitted.
  • the two rotors are mounted end to end on a common axis of rotation 4. In use, the rotors with counter- rotate as described above.
  • the rotors shown in the Figures are similar to the rotors illustrated in Figures 1 , 2 and 3 herein, but it will be appreciated that the two-stage rotor apparatus could comprise any pair of rotors with the required helical blade shape, such as any of the alternative embodiments and variations of rotors described herein.
  • Figure 10 shows an embodiment of a two-stage rotor apparatus that may function as a tidal turbine with a pair of counter-rotating rotors 7, 8 installed in a housing 9 along a common longitudinal axis 4.
  • the housing 9 is shown in cross-section and the rotors 7, 8 are shown in partial cross-section.
  • the rotors 7 and 8 rotate about a common fixed shaft 1 1 that is secured to the housing 9 and supported by bearings 10.
  • labyrinth seals 15 are placed at either end of the rotors 7, 8 between an inner surface of the housing 9 and outer surface of the rims 1 of each rotor 7, 8.
  • the two ends of the housing 9 have a convergent divergent geometry 16 designed to increase/decrease the fluid velocity and enhance the
  • the two-stage rotor apparatus is used to accommodate a unidirectional flow and also a reversible or cyclic flow by the combination of two of the rotors.
  • the first stage rotor receives the approaching liquid fluid flow possessing a longitudinal component and extracts a proportion of the kinetic energy by converting it into rotational force or torque that causes the first stage rotor to rotate.
  • the second stage rotor has a geometry constructed in the same way as the first stage rotor and rotates around the same longitudinal axis as the first stage rotor but it is turned through 180° relative to the first stage rotor. It therefore rotates in the opposite direction about the axis.
  • the fluid possesses both a longitudinal and radial component.
  • the second stage rotor extracts a further proportion of the kinetic energy from the liquid flow.
  • the fluid exits the second stage rotor it ideally possesses a longitudinal component only and can be returned to the main flow with minimal interference.
  • the housing 9 is designed to provide a mounting area for multiple low torque, high speed, high efficiency generators 13 placed outside of the rotors 7, 8.
  • the generators 13 are driven by the movement of the external rotating rim 1 of the rotors 7, 8 by appropriate gearing.
  • Figure 1 1 shows a cross-section of an alternative embodiment of a two-stage rotor apparatus installed in a housing 9.
  • the generators 13 are placed within the inner cone instead of outside the outer cone.
  • Fixed mounting blocks 12 are attached to the fixed shaft 1 1 within the rotors 7 and 8. These provide a mounting area for multiple low torque, high speed, high efficiency generators 13.
  • the generators 13 are driven by the internal surface of the inner cone 3 of the rotors 7, 8 by appropriate gearing.
  • the rotor itself forms the shape similar to the frustum of a cone.
  • a feature of this shape is that the linear velocity of the rim 3 varies along the longitudinal axis 4 due to a varying outer radius. Since the generators 13 in this embodiment are mounted on a block 12 with a surface parallel to the inner surface of the inner cone 3 the generators 13 can be moved along the surface by appropriate frame and stepper motors 14.
  • the generators 13 can be secured to a common movable frame assembly or be separately moved along the frustum surface by stepper motors triggered by hard wired or wireless monitoring equipment and/or CPU so that the two-stage rotor apparatus is able to respond to changes in the rotational speed of the rotors 7, 8 and adjust the longitudinal position of the generators along the frustum.
  • This enables the generators 13 to be moved within the rotors 7, 8 to respond to changes in the rotational speed of the rotors 7, 8.
  • a relatively constant generator speed within the variable range of the generators 13 can be achieved through a range of fluid flows.
  • the generator connection point can be made at the higher linear velocity end, this being at the larger diameter end of the rotor.
  • the generator connection point can be repositioned at the lower linear velocity end, this being the smaller diameter end of the rotor.
  • Figure 12 shows a cross-section of an alternative embodiment of a two-stage rotor apparatus installed in a housing 9.
  • the generators 13 are mounted on a fixed motor mount 16 instead of outside the outer cone.
  • the fixed motor mounts 12 are attached to the fixed shaft 1 1 within the rotors 7 and 8. This provides a mounting area for multiple low torque, high speed, high efficiency generators 13.
  • the generators 13 are driven by the internal revolving surface of the inner cone 3 of the rotors 7, 8 by appropriate gearing.
  • the rotor itself forms the shape similar to the frustum of a cone.
  • a feature of this shape is that the linear velocity of the rim 3 varies along the longitudinal axis 4 due to a varying outer radius. Since the generators 13 in this embodiment are mounted on a fixed motor mount 16 the generators 13 can be installed as rings of generators that can be engaged or disengaged as required at different locations along the longitudinal axis 4.
  • the rings of generators 13 can be engaged or disengaged by stepper motors triggered by hard wired or wireless monitoring equipment and/or CPU so that the two-stage rotor apparatus is able to respond to changes in the rotational speed of the rotors 7, 8 and adjust the number of rings of generators 13 in use at any given time.
  • rings of generators 13 can be engaged at the higher linear velocity end, this being at the larger diameter end of the rotor.
  • the rings of generators can be engaged at the lower linear velocity end, this being the smaller diameter end of the rotor.
  • the engagement of multiple rings is also possible, for example, engaging two or more rings of generators at the lower linear velocity end or two or more rings of generators at the higher linear velocity end.
  • the two stage rotor apparatus may be effectively applied to horizontal as well as to vertical liquid fluid flow directions and to those in-between by varying the orientation of the inlet and outlet and the orientation of the rotors.
  • the rotor housing also functions to direct the liquid flow into the rotor to correct minor cross-flow deviations.
  • the rotor housing may have a steering and suspension system and include fins, gearing and buoyancy control devices in order for it to adjust its position within a flow field in order to optimise performance or to surface for maintenance purposes if submerged in a l/quid stream.
  • the steering and suspension system provides a certain self-adjusting capability with regards to changes in flow direction.
  • the two-stage rotor apparatus may be supported on a floor, e.g. the seabed or it may be suspended in a liquid flow by means of a tethering or anchoring arrangement to the seabed or a floating raft. Or it may sit on a tower installed on the seabed so that it can be recovered from the sea for
  • the two stage turbine arrangement may be raised to the surface or lowered to the seabed.
  • the entire turbine arrangement may be configured so that only a smaller part of the arrangement would need to be recovered for maintenance.
  • a sub unit of the arrangement containing the rotor and electrical components only could be separated from the main installed structure leaving the main installed structure in place. This provides a simpler maintenance operation.
  • FIG 13 shows one possible utilisation of the two-stage rotor apparatus as a tidal turbine.
  • Rotors 7,8 in two housings 9 as shown in Figures 10, 11 or 12 are installed on a tower structure that can be installed on the sea bed.
  • the multiple rotor housings may be aligned with the primary flow direction to allow effective operation in a reversible or cyclic flow such as a tidal current system. Since the two-stage rotor apparatus is capable of efficient operation with flow in either direction it is not necessary to provide a mechanism for rotation of the tower when the tidal flow changes direction.
  • An alternative arrangement would be to mount the two-stage rotor apparatus in a housing within a pipe where fluid flows. Fluid flow in either direction would be efficiently converted into rotational movement and, in accordance with the preferred embodiment of the rotor, converted into electrical power by generators.
  • the pipe could be installed within the waterways of a dam or a hydropower station or a tidal barrage.
  • liquid current system consisting of two liquid reservoirs connected in such a way that the transfer of liquid from one reservoir to the other is allowed.
  • a liquid flow may be induced between the two reservoirs as a consequence of externally applied natural or man-made forces. Such an external force may be
  • rotors as described herein are utilised in preferred embodiments in a two- stage rotor apparatus installed in a rotor housing.
  • the two-stage rotor apparatus is subjected to a variety of liquid fluid flow scenarios, such as tidal flows, the rotors extract the kinetic energy from the liquid fluid flow and convert it into a rotational force or torque which causes the pair of specially shaped rotors to rotate.
  • the torque is applied to drive electrical generators as set out above.
  • the torque may be used to drive a pump, a compressor or any other device requiring a rotational force or torque to be applied.
  • the geometry of the rotors facilitates the conversion of the kinetic energy in the liquid fluid flow to rotational force or torque.
  • the geometry of the rotors is based on pair of conic helixes 5, 6 that have an increase in radius r with a polar coordinate ⁇ along the longitudinal axis 4, each helix 5, 6 possessing a different initial radius.
  • the pair of conic helixes 5, 6 also have a pitch that decreases with the polar coordinate ⁇ as the radius increases.
  • the decreasing helical pitch provides an increasing helical frequency.
  • This type of conic helix may be defined as a three dimensional spiral having varying radius r as a function of the polar coordinate ⁇ but also having a third variable, the length I, varying also as function of the polar coordinate ⁇ .
  • the pair of conic helixes may be generated in a clockwise or anticlockwise direction and as shown in Figures 6A to 7B the rate of decrease of the helical pitch resulting in an increase in helical frequency may be varied to obtain an optimum decrease of helical pitch per unit of length.
  • Other variables that have a direct effect on the power extracted are the initial and final radii of the pair of conic helixes (and thus the minimum and maximum inner and outer diameters of the rotor) and the overall length of the rotor. These may also be optimised for a given flow situation.
  • a rotor having a relatively small minimum and maximum outer diameters may be preferred, for example 1 m and 2m diameter respectively.
  • a longer rotor may be beneficial which then allows room to extend the pair of conic helixes to optimise the power output.
  • space may not be an issue and large diameters, for example 10m and 20m respectively can be utilised to greatly enhance the power output.
  • a shorter rotor can then be used to reduce installation and footprint costs.
  • the rotor blade surfaces of the rotor are formed when the pair of conic helixes are connected together in the radial direction.
  • three identical rotor blades 2 are present. There could alternatively be less or more identical rotor blades 2 spaced equally around the rotor.
  • the rotor blades 2 extend between the inner peripheral surface 3 and the outer rim 1 and are fixed to either the inner peripheral surface 3 or the outer rim 1 for rotation therewith.
  • a hydrodynamic reaction force is created on a solid surface when a body of fluid flowing over the solid surface experiences a change of momentum.
  • hydrodynamic force acting on the body of fluid in a particular direction is equal to the rate of change of momentum of the body of fluid in that direction as dictated by Newton's Second law.
  • an equal and opposite hydrodynamic reaction force acts on the so/id surface bounding the body of fluid. Examples of such hydrodynamic reaction forces are those found when a jet of water strikes a wall, or the force felt in a pipe system when the fluid is forced to turn a bend or the force felt on a solid body when placed in a flowing fluid forcing the fluid to flow around it.
  • a solid surface bounding the body of flowing fluid is formed by the front and rear of a pair of rotor blades and the inner and outer rims of the rotor.
  • the hydrodynamic reaction force acts in the opposite direction and since the centre of the hydrodynamic reaction force is displaced at a radial distance from the longitudinal axis, a torsional force is generated that acts around the longitudinal axis of the rotor and tends to turn the rotor.
  • the underlying mathematical spiral of the conic helix can be based on
  • the underlying spiral is based upon an Archimedean spiral when there is a linear increase in radius r with the polar coordinate ⁇ .
  • the use of a Archimedean spiral with linear increase in the radii r with the polar coordinate ⁇ provides a conic helix formed about a straight sided frustocone as shown in the Figures.
  • a non-linear increase in the inner and outer radii r with the polar coordinate ⁇ would provide a different shape, for example the external and internal conic surfaces may be curved.
  • the pair of conic helixes are chosen to have a linear increase in radii r with the polar coordinate ⁇ along the longitudinal axis, each possessing a different initial radius.
  • the increasing radius of either conic helix may increase at greater or lesser rates to form a pair of non-parallel conic helixes.
  • they may increase at the same rate to form a pair of parallel conic helixes.
  • the helical pitch is also decreased by way of varying I as a function of ⁇ continuously or in discrete steps along the longitudinal axis 4.
  • the rate of decrease of helical pitch or the rate of increase of helical frequency in the embodiments of the Figures is linear. It may alternatively be non-linear.
  • the helix shape, radius increase and pitch decrease combine to provide the overall hydrodynamic reaction force on the rotor and thus the torque and power output. These parameters may be optimised to maximise the power extraction from a given fluid flow or to limit the power extraction from a given fluid flow if required.
  • the following set of equations consider the hydrodynamic reaction forces and torques generated.
  • Equation [1] the mass flow w into the rotor is constant.
  • the hydrodynamic reaction forces F x , F y and F s are necessarily produced due to the continuously decreasing helical pitch or in other words, due to a continuous change in the direction of the fluid flow and thus a change in the velocity components w , v and w of the fluid between the velocity components at first and second arbitrary cross sections in the rotor, the first and second arbitrary cross sections being at different distances along the rotor length. This results in a rate of change of momentum and the hydrodynamic reaction forces as expressed by Equation [2.1] to [2.3].
  • the distance from the longitudinal axis at which the hydrodynamic reaction forces act is continuously increased or decreased by the change in radius of the pair of conic helixes. For each complicated flow passage a separate set of torsional forces result, the total torsional force around the longitudinal axis of the rotor being the sum of all torsional forces acting around the longitudinal axis of the rotor.
  • magnification of the torsional force and power output is only dependent on the rate at which the radius of the pair of conic helixes increases.
  • connection between the pair of conic helixes is not limited to being straight.
  • the connection may be curved, for example, a concave surface may be used to increase the surface area along the surface of the specially shaped rotor blade in order to spread the resulting hydrodynamic forces over a larger area and reduce internal stresses.
  • the pair of conic helixes are generally axially aligned for simplicity but may be slightly misaligned in order to change the surface characteristics of the conic helixes in a beneficial way.
  • Figure 14 is a graph illustrating the effect of varying the ratio of the outer maximum diameter Do of the rotor to the minimum outer diameter do.
  • the radii of the pair of conic helixes are increased at the same rate to form a pair of parallel conic helixes.
  • the increasing diameter results in an increase in the distance from the longitudinal axis at which the hydrodynamic reaction forces act and thus provides a magnification of the torsional force.
  • the magnification of the torsional force is dependent on the rate at which the radii of the pair of conic helixes increase.
  • Figure 14 uses an arrangement with no change in diameter, i.e. where the ratio of maximum and minimum radii [Do/do] is one.
  • This is a rotor where the radii of the pair of conic helixes does not increase i.e. this is a rotor based upon a cylindrical helix and not a conic helix.
  • the rotors described herein, which are based on blades formed by conic helixes, have a ratio of greater than one and this provides a torque multiplication and an increase in efficiency as shown in the Figure.
  • Figure 15 is a graph illustrating the effect of increasing or decreasing the relative radii of the pair of conic helixes to form a pair of non- parallel conic helixes.
  • the inner conic helix increases in radius at a slower rate than the increase in radius of the outer conic helix (i.e. [Anll]/[Aro/l] ⁇ 1 )
  • arbitrary cross sectional areas at first and second longitudinal distances along the rotor increase at a faster rate. This has the effect of reducing the changes in the velocity components and since the mass flow is constant, the hydrodynamic reaction forces and torsional forces produced are lower.
  • Figure 16 is a graph illustrating the effect of changes in the rate of decrease of the helical pitch that results in a change in the rate of increase of helical frequency ⁇ f.
  • a change of this nature will result in an increase or decrease in the torsional forces and thus power output.
  • a decrease in torsional force is achieved by a slower rate of decrease of helical pitch or a slower rate of increase of helical frequency and an increase in torsional force is achieved by a faster rate of decrease of helical pitch or a faster rate of increase in helical frequency.
  • the preferred embodiments described herein provide a compact low complexity two-stage rotor apparatus that is ideal for generation of electricity from tidal flow.
  • the two-stage rotor apparatus can however be effectively applied to any liquid flow system which may have single, reversible or cyclic liquid current characteristics.
  • the design of the rotors and blades can be tuned to a particular application through variation of parameters as described above.
  • the parameters are not limited to the values and combinations of values set out herein. Instead the parameters can be varied alone or in combination as required to achieve desired performance characteristics.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Oceanography (AREA)
  • Power Engineering (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Hydraulic Turbines (AREA)

Abstract

L'invention concerne un rotor comprenant au moins une pale (2) conçue pour tourner autour d'un axe de rotation (4), la pale (2) étant formée d'une surface s'étendant entre des hélices coniques intérieure et extérieure (5, 6); une surface intérieure (3) et une couronne extérieure (1) entourant la pale (2), les surfaces intérieure et extérieure (3,1) suivant les surfaces de révolution généralement coniques intérieure et extérieure correspondant aux trajets des hélices coniques (5, 6), les hélices coniques (5, 6) présentant chacune un pas qui diminue à mesure que le rayon de l'hélice augmente et la pale (2) s'étendant entre et étant montée sur la couronne extérieure (1) et la surface intérieure (3).
PCT/GB2012/000055 2011-01-20 2012-01-20 Rotor WO2012098362A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1101009.7 2011-01-20
GB1101009.7A GB2487403A (en) 2011-01-20 2011-01-20 Conical helical rotor

Publications (1)

Publication Number Publication Date
WO2012098362A1 true WO2012098362A1 (fr) 2012-07-26

Family

ID=43769364

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2012/000055 WO2012098362A1 (fr) 2011-01-20 2012-01-20 Rotor

Country Status (2)

Country Link
GB (1) GB2487403A (fr)
WO (1) WO2012098362A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013110140A1 (fr) * 2012-01-24 2013-08-01 Aquaglobe Pty Ltd Génératrice à sortie variable et turbine à eau
US8777555B1 (en) 2013-02-21 2014-07-15 Lockheed Martin Corporation Yaw drive tidal turbine system and method
AT515256A1 (de) * 2014-01-09 2015-07-15 Valentin Dragaschnig Energiewandler
CN107939583A (zh) * 2017-12-30 2018-04-20 长沙紫宸科技开发有限公司 一种便携式涵道水流发电器
CN112360672A (zh) * 2020-11-16 2021-02-12 太仓治誓机械设备科技有限公司 一种海洋洋流发电装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20130219A1 (it) * 2013-02-18 2014-08-19 Gledis Cinque Rotore idraulico realizzato con parti in materiale flessibile
CN105697224B (zh) * 2016-02-02 2016-09-28 河海大学 一种利用潮流能发电的斐波那契螺旋形水轮机
DE102016107574A1 (de) * 2016-04-24 2017-10-26 Aquakin Gmbh Wirbelwasserkraftwerk
CN106870244B (zh) * 2016-12-29 2018-11-27 河海大学 一种带圆弧螺旋形叶片的冷却塔用双转轮水轮机

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4722665A (en) * 1984-11-07 1988-02-02 Tyson Warren N Turbine
WO1998025027A1 (fr) * 1996-12-02 1998-06-11 Northern Research & Engineering Corporation Turbine hydraulique a pales helicoidales
WO2004113717A1 (fr) * 2003-06-25 2004-12-29 Sinvent As Turbine hydraulique et pompe a liquide
DE102008032411A1 (de) * 2008-07-10 2010-01-14 INSTI-EV-Sachsen e.V. c/o IREG mbH Strömungswandler

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE377829B (fr) * 1974-09-16 1975-07-28 Karlstad Mekaniska Ab
WO2001007787A1 (fr) * 1999-07-26 2001-02-01 Impsa International Inc. Pompe rotative a courant continu
CN201461213U (zh) * 2009-05-08 2010-05-12 单运秋 螺旋式水轮机

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4722665A (en) * 1984-11-07 1988-02-02 Tyson Warren N Turbine
WO1998025027A1 (fr) * 1996-12-02 1998-06-11 Northern Research & Engineering Corporation Turbine hydraulique a pales helicoidales
WO2004113717A1 (fr) * 2003-06-25 2004-12-29 Sinvent As Turbine hydraulique et pompe a liquide
DE102008032411A1 (de) * 2008-07-10 2010-01-14 INSTI-EV-Sachsen e.V. c/o IREG mbH Strömungswandler

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013110140A1 (fr) * 2012-01-24 2013-08-01 Aquaglobe Pty Ltd Génératrice à sortie variable et turbine à eau
AU2013212537B2 (en) * 2012-01-24 2017-06-01 Aquaglobe Pty Ltd A variable output generator and water turbine
US8777555B1 (en) 2013-02-21 2014-07-15 Lockheed Martin Corporation Yaw drive tidal turbine system and method
AT515256A1 (de) * 2014-01-09 2015-07-15 Valentin Dragaschnig Energiewandler
AT515256B1 (de) * 2014-01-09 2017-10-15 Dragaschnig Valentin Energiewandler
CN107939583A (zh) * 2017-12-30 2018-04-20 长沙紫宸科技开发有限公司 一种便携式涵道水流发电器
CN112360672A (zh) * 2020-11-16 2021-02-12 太仓治誓机械设备科技有限公司 一种海洋洋流发电装置

Also Published As

Publication number Publication date
GB2487403A (en) 2012-07-25
GB201101009D0 (en) 2011-03-09

Similar Documents

Publication Publication Date Title
US9599090B2 (en) Rotor apparatus
WO2012098362A1 (fr) Rotor
US4960363A (en) Fluid flow driven engine
EP2205833B1 (fr) Ensemble turbine
US9086047B2 (en) Renewable energy extraction device
US20180195582A1 (en) Control apparatus and method for variable renewable energy
WO2010109169A2 (fr) Turbine sans aube, et générateur électrique
US20190331088A1 (en) Dolphin-Blade, Fluid Flow, Reciprocal Motor
EP3613980A1 (fr) Turbine à axe vertical
CN104976031A (zh) 高压外传螺旋凹槽发电系统
NO20200281A1 (en) Hydrokinetic turbine having helical tanks
WO2013110140A1 (fr) Génératrice à sortie variable et turbine à eau
Uzakov et al. Study of constructive dimensions of Kaplan hydro turbine in variable water flows
CN104976062A (zh) 高压外传螺旋凹壁发电系统
GB2376508A (en) Turbine
KR101838901B1 (ko) 유속 가중화 수차 발전 시스템
Gheorghe-Marius et al. ENERGY CAPTURE IN THE GRAVITATIONAL VORTEX WATER FLOW.
US20210348595A1 (en) Fluid turbine
Oo Design of 50 kw kaplan turbine for micro hydro power plant
CN103380276B (zh) 转子装置
CN105041550A (zh) 高速外传螺旋环驱动发电系统
KR20210053944A (ko) 전방향 발전 장치
GB2508814A (en) Concentric turbine arrangement
RU2532823C2 (ru) Гидроэнергетическая установка
Stefano Innovative Fluid Machine that Can Operate both as a Turbine and as a Pump

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12701363

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12701363

Country of ref document: EP

Kind code of ref document: A1