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WO2012159152A1 - Appareil de conversion d'énergie fluidique - Google Patents

Appareil de conversion d'énergie fluidique Download PDF

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Publication number
WO2012159152A1
WO2012159152A1 PCT/AU2012/000559 AU2012000559W WO2012159152A1 WO 2012159152 A1 WO2012159152 A1 WO 2012159152A1 AU 2012000559 W AU2012000559 W AU 2012000559W WO 2012159152 A1 WO2012159152 A1 WO 2012159152A1
Authority
WO
WIPO (PCT)
Prior art keywords
vanes
vane
energy conversion
conversion apparatus
fluid energy
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/AU2012/000559
Other languages
English (en)
Inventor
Ralph Tony Sarich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LINEAR TECHNOLOGIES Pty Ltd
Original Assignee
LINEAR TECHNOLOGIES Pty Ltd
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
Priority claimed from AU2011901987A external-priority patent/AU2011901987A0/en
Application filed by LINEAR TECHNOLOGIES Pty Ltd filed Critical LINEAR TECHNOLOGIES Pty Ltd
Publication of WO2012159152A1 publication Critical patent/WO2012159152A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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"
    • F03B17/062—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 at right angle to flow direction
    • F03B17/065—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 at right angle to flow direction the flow engaging parts having a cyclic movement relative to the rotor during its rotation
    • F03B17/067—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 at right angle to flow direction the flow engaging parts having a cyclic movement relative to the rotor during its rotation the cyclic relative movement being positively coupled to the movement of rotation
    • F03B17/068—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 at right angle to flow direction the flow engaging parts having a cyclic movement relative to the rotor during its rotation the cyclic relative movement being positively coupled to the movement of rotation and a rotor of the endless-chain type
    • 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

Definitions

  • the present invention relates to a fluid energy conversion apparatus. More particularly, but not exclusively, the invention relates to a linear apparatus for harnessing wind energy.
  • Examples of the invention seek to solve, or at least ameliorate, one or more disadvantages of previous fluid energy conversion apparatus.
  • a fluid energy conversion apparatus for extracting energy from a flowing fluid, comprising: a plurality of pivotably mounted vanes arranged for movement around an endless pathway having a primary transfer portion, a secondary transfer portion and transition portions therebetween, the apparatus configured so that in use vanes disposed on the primary transfer portion are generally upstream in the fluid flow of vanes disposed on the secondary transfer portion and the fluid flows sequentially past vanes on the primary transfer portion and secondary transfer portions respectively; a releasable brake operable in respect of each vane, each releasable brake being configured to fix the orientation of a respective vane when engaged; and vane adjustment means configured to release the brake and vary the orientation of a vane when the vane is in one of the transition portions to control the exposure of each vane to fluid incident upon that vane.
  • each endless drive means includes a pair of cables.
  • each endless drive means passes over a pair of spaced apart pulleys.
  • the apparatus further includes a drive disc disposed adjacent and coaxial with each respective pulley, the drive discs configured to engage the vanes as they pass through the transfer portions.
  • the drive disc includes a plurality of yokes extending therefrom, the yokes configured to engage respective vanes as they pass through the transfer portions.
  • the apparatus further includes a second pulley disposed adjacent each drive disc so that each drive disc is disposed between a pair of pulleys, each of which carries a single cable.
  • a plurality of connectors may be disposed along the cables to couple the vanes to the cables, the connectors configured to engage corresponding portions on each drive disc to transfer energy from the vanes to the drive disc.
  • one of the pair of spaced drive discs is coupled to an output shaft to drive a generator.
  • the vane adjustment means is coupled to each drive disc.
  • the vane adjustment means is driven by a cam disc disposed adjacent the drive disc, the cam disc being eccentrically movable relative to the drive disc.
  • the eccentricity of the cam disc is adjustable by a stepper motor.
  • the eccentricity of the cam disc can be varied in two dimensions.
  • each vane adjustment means includes a parallelogram four bar linkage, the coupler link of which is arranged to extend generally radially and is driven by a member extending from the cam disc and configured to engage the vanes to release the brake and vary their orientation.
  • the releasable brake includes a force conversion mechanism for receiving the vane adjustment means and acting to release the releasable brake, the force conversion mechanism having a transfer member disposed about an anchor point, the transfer member including first and second spaced apart annular bearing surfaces having different diameters, a smaller of said bearing surfaces being configured to extend loosely around the anchor point so that an input force urging the larger bearing surface toward the anchor point causes the transfer member to rotate, thereby advancing the smaller bearing surface along the anchor point to provide an output force in a direction generally perpendicular to the input force.
  • the releasable brake includes a force conversion mechanism for receiving the vane adjustment means and acting to release the releasable brake, the force conversion mechanism having: a plunger, the plunger including a sliding element at one end and a lateral member at an end opposite to the sliding element; a sleeve; and an insert, wherein the sliding element is slidably received in the sleeve and the lateral member is received in a recess formed in the insert, the insert and the sleeve being configured so that the sleeve can move laterally with respect to the insert thereby causing the lateral member to bear against an edge of the recess and pivot so that an end of the lateral member moves away from the sleeve in response to a lateral input force acting on the sleeve, thereby providing an output force which acts in a direction generally perpendicular to the input force.
  • the force conversion mechanism having: a plunger, the plunger including a sliding element at one end and a lateral
  • the vanes are fixed to the endless drive means with a connector for fixing a shaft to at least one endless cable that passes around a wheel
  • the connector comprising: a coupling element which is configured to surround at least a portion of the or each cable, the coupling element having extensions which extend along the cable on a side remote to said wheel; and a lug coupled to the coupling element, the lug being configured to accept the shaft, wherein the coupling element is arcuate between the extensions to prevent contact between the coupling element and the wheel.
  • the releasable brake includes a hydrostatic locking mechanism.
  • Figure 1 is a perspective view of a fluid energy conversion apparatus of one embodiment of the invention.
  • Figure 2 is a partial close perspective view of the apparatus
  • Figure 3 is another partial close perspective view of the apparatus
  • Figure 4 is another partial close perspective view of the apparatus
  • Figure 5 is a close inner side view of a pulley of the apparatus in one condition of use
  • Figure 6 is a close inner side view of a pulley of the apparatus in another condition of use
  • Figure 7 is a close front perspective view of an example of a vane adjustment brake mechanism for use with the apparatus
  • Figure 8 is a close rear perspective view of an example of a vane adjustment brake mechanism for use with the apparatus
  • Figure 9 is a close perspective view of an example of a vane adjustment brake mechanism for use with the apparatus.
  • Figure 10 is a plan view of the brake mechanism
  • Figure 1 1 is a close perspective view of the brake mechanism fitted to a vane
  • Figure 12 is another close perspective view of the brake mechanism fitted to a vane
  • Figures 13A to 13C are respective sectioned side, side and plan views of a mechanism for fixing and releasing the vanes, the mechanism shown in one condition of use;
  • Figures 14A to 14C are respective sectioned side, side and plan views of the mechanism of Figure 13 A, the mechanism shown in another condition of use;
  • Figures 15A and 15B are sectioned views of an alternative mechanism for fixing and releasing the vanes, the mechanisms shown in first and second conditions of use respectively;
  • Figures 16A and 16B are sectioned views of the mechanism of Figure 15 A, the mechanism shown in communication with an actuator;
  • Figure 17 is a side view of an alternative mechanism for adjusting the orientation of the vanes
  • FIGS 18 and 19 are partial side views of an alternative mechanism for locking and unlocking the vanes
  • Figures 20 and 21 are partial end views of the mechanism of Figures 18 and 19;
  • Figures 22 and 23 are side views of an alternative mechanism for adjusting the orientation of the vanes;
  • Figure 24 is a schematic diagram of alternative mechanism for adjusting the orientation of the vanes
  • Figure 25 is a schematic diagram of a mechanism for use with the mechanism shown in Figure 24;
  • Figure 26 is a side view of a swash plate mechanism which can be used as an alternative mechanism for adjusting the orientation of the vanes;
  • Figure 27 is a side view of another alternative mechanism for adjusting the orientation of the vanes
  • Figure 28 is an upper perspective view of a connector used to couple a shaft of the vanes to a drive cable
  • Figure 29 is a lower perspective view of a connector used to couple a shaft of the vanes to a drive cable
  • Figure 30 is an end view of a drive disc and pulleys of an alternatively configured apparatus
  • Figure 31 is a perspective view of the arrangement of Figure 23.
  • Figure 32 is a side view of the apparatus. DETAILED DESCRIPTION
  • a fluid energy conversion apparatus 10 for extracting energy from a flowing fluid.
  • the apparatus 10 comprises a plurality of pivotably mounted vanes 12 arranged for movement around an endless pathway having a primary transfer portion 16, a secondary transfer portion 18 and transition portions 20a,20b therebetween.
  • the apparatus 10 is configured so that in use vanes 12 disposed on the primary transfer portion 16 are generally upstream in the fluid flow of vanes 12 disposed on the secondary transfer portion 18 and the fluid flows sequentially past vanes on the primary transfer portion 16 and secondary transfer portion 18 respectively.
  • the apparatus 10 includes a releasable brake 50 which is operable in respect of each vane 12. Each releasable brake 50 is configured to fix the orientation of a respective vane 12 when engaged. As illustrated in Figure 3, the apparatus 10 also includes a vane adjustment means 38 which is configured to release the brake 50 and vary the orientation of a vane 12 when the vane 12 is in one of the transition portions to control the exposure of each vane 12 to fluid incident upon that vane 12. A determined orientation to the fluid flow of each vane 12 is fixed whilst in the primary transfer 16 and the secondary transfer portion 18.
  • the vanes 12 extend between a pair of endless drive means, each of which in this example includes a pair of steel cables 14.
  • a pair of cables 14 is used to improve stability and rigidity of the endless drive means.
  • the endless drive means may comprise cables made of other materials or a single cable, a belt, chain or other suitable flexible element.
  • Vanes 12 are pivotably connected at either end to the cables 14 and are arranged to rotate about their centre of mass.
  • the cables 14 pass around a pair of spaced apart pulleys 24 and are capable of reversal in their direction of travel.
  • Cables are used as they can easily be made to an appropriate length and readily sourced. If a cable is chosen correctly, it will not stretch appreciably during use.
  • the function of the cables 14 is to carry the weight of the vanes 12 or aerofoil structure and also the load associated with the wind.
  • the pulleys 24 are free-wheeling and power is transmitted from the vanes 12 through cables 14 and directly through a drive disc 26.
  • One advantage of using cables in this manner is that it enables the cable to not be necessarily in significant tension which reduces the loading on the bearings and consequential losses of the apparatus.
  • the flow of a fluid through the apparatus 10 can also be seen in Figure 1.
  • the fluid is air moving under the influence of wind, the direction of which is labelled as A.
  • the vanes 12 travelling in the primary transfer portion 16 travel in direction B which is opposite to direction C, the direction which vanes 12 travel in the secondary transfer portion 18.
  • each vane 12 always faces toward the wind when the vane is in the primary or secondary transfer portion.
  • the angle of vanes relative to the cables 14 when the vanes are in the primary transfer portion is different than the angle of the vanes in the secondary transfer portion as the direction of wind travelling through the apparatus 10 changes as the wind passes over vanes in the primary transfer portion.
  • the wind path 36 through the apparatus 10 is thus generally 'S' shaped. Accordingly, to maximise energy transfer from the wind to vanes in the secondary transfer portion 18, the orientation of vanes 12 in the secondary transfer portion 18 needs to be varied.
  • vanes 12 Any convenient number of vanes 12 may be employed in the apparatus 10, the number preferably being consistent with good mechanical design practice taking into consideration issues of mechanical balance of rotating components and achieving the required vane area to optimise energy transfer from the flowing fluid.
  • the apparatus 10 includes a drive disc 26 disposed adjacent and coaxial with each respective pulley 24.
  • the drive discs 26 are configured to engage the vanes 12 (shown in broken lines in Figure 2) as they pass through the transition portions 20a, 20b and are provided for the purpose of transferring power from the vanes 12 to an output shaft 28.
  • Each drive disc 26 includes a plurality of yokes 27 extending radially outward therefrom. In the described example, there are three equally separated yokes 27 disposed around the drive disc 26 at an angle of 120 degrees apart so that at least one yoke 27 is engaged at all times. It is this engagement of the yokes 27 and the vanes 12 that provides drive from the vanes 12.
  • the yokes 27 are configured to engage a shaft 41 of respective vanes 12 as they pass through the transfer portions 20a, 20b.
  • Resilient material surrounds the shaft 41 in a region where the yokes 27 are intended to engage the shaft 41 to absorb impact and reduce noise.
  • Only one of the pair of spaced drive discs is coupled to an output shaft 28 to drive a generator 30 to generate electricity.
  • the output shaft 28 is directly coupled to the generator 30.
  • the generator 30 may be any commercially available generator of any convenient configuration and output voltage.
  • An idler shaft 32 is disposed at an end of the apparatus which is opposite from the end where the output shaft 28 is disposed.
  • the distance between shafts 28 and 32 is fixed via a frame, which also acts .to spatially fix the location of the generator 30 relative to the idler shaft 32 and the output shaft 28.
  • the apparatus 10 illustrated in Figure 3 includes a plurality of vane adjustment means 38 to vary the angle or orientation of the vanes 12.
  • Each vane adjustment means 38 is configured to engage a release mechanism (not shown) on a respective vane. Engagement of the release mechanism releases a brake (item 50 in broken lines in Figure 2) acting on each vane 12, allowing it to be rotated to a new orientation.
  • the vane adjustment means 38 includes a parallelogram four bar linkage, the coupler link 40 of which is arranged to extend generally radially outward of the drive disc 26 to act as a push rod.
  • An end 42 of the coupler link 40 has a flat surface configured to actuate the release mechanism. Due to the configuration of the parallelogram four bar linkage mechanism, the end 42 travels through a curved path, thereby assisting in the engagement and operation of the release mechanism as it passes through the transition portions 20a, 20b.
  • the coupler link 40 is driven by a member 44 which extends from a cam disc 29.
  • the cam disc 29 is eccentrically movable relative to the drive disc 26 so as to vary the amount of travel of the vane adjustment means 38, thereby controlling the magnitude of the orientation change of the vanes 12.
  • the cam disc 29 is generally free wheeling and not coupled to the generator 30, though is acted upon and caused to rotate by a trailing arm 31 linking the drive disc 26 and the cam disc 29 so that they rotate together. Such a configuration is necessary so as to maintain a link between the drive disc 26 and the cam disc 29 to that they rotate together, though to accommodate the eccentric movement of the cam disc 29 relative to the drive disc 26.
  • the cam disc 29 is mounted about a nylon arbour bearing 46 which has a slotted inner region that fits over the drive shaft 28.
  • the arbour bearing 46 is movable along rods 48 under the action of an electronically controlled motor, which in the described example is a stepper motor 49, . to achieve eccentric movement of the cam disc 29 relative to the drive disc 26.
  • the stepper motor 49 rotates a slotted arm in which a pin moves to effect movement of the arbour bearing 46.
  • the offset will be set in the range of 0mm to 50mm. However, 'negative' values of, offset may be used under certain circumstances. Although the described example utilises a stepper motor to achieve the desired eccentric offset, it will be appreciated that other means of achieving this offset may be used.
  • cam disc 29 is movable in one dimension.
  • cam disc 29 is mounted so as to be movable in two dimensions which are generally perpendicular to each other.
  • the inventors have found that movement of the cam disc 29 in two dimensions is necessary to be able to set the blade departure angle correctly and also to allow a more accurate acceptance of the incoming blade angle without inadvertently setting a steep departure angle. By providing adjustment in two dimensions, the blade departure angle can more accurately be set.
  • Figures 5 and 6 show the cam disc 29 at opposing extremes of travel. As can be seen, the eccentric rotation of the cam disc 29 causes a reciprocal motion of the member 44 relative to the vane adjustment means 38, thereby driving the vane adjustment means 38 to vary the orientation of the vanes 12.
  • FIGs 7 and 8 illustrate an example brake 131 which is used to fix the orientation of the vanes 12.
  • the brake 131 is in the form of a releasable hydrostatic lock formed by a hydraulic cylinder acting on the vanes 12 that allows the orientation of a respective vane to be varied.
  • a shaft 41 extends from vane 12 and is rigidly mounted thereto in a coaxial manner to allow the vane 12 to rotate.
  • a release mechanism in the form of two cone drivers 56 (refer Figures 13A to 16B), is provided.
  • One cone driver is provided for engagement of vanes exiting the primary transfer portion 16 and another for vanes exiting the secondary transfer portion 18. Engagement of a respective cone driver 56 with the end 42 of the coupler link 40 initiates release the mechanism 131.
  • a hydraulic valve 133 is provided at a rear of each cone driver so that activation of a respective cone driver 56 causes the valve 133 to be opened.
  • the valve 133 is in fluid communication with a hydraulic accumulator 135 and a hydraulic cylinder 137. Operation of the valve 133 allows piston 139 of the hydraulic cylinder 137 to move, thereby releasing the vane 12 and allowing it to rotate.
  • brake 131 Due to the positive operating characteristics of a hydraulic system, brake 131 provides a hydrostatic locking system that acts to positively maintain a desired vane orientation. In the described example, air is used as a working fluid, though it will be appreciated that other fluids may similarly be used.
  • FIG 9 illustrates an alternative example brake 50 which is used to fix the orientation of the vanes 12.
  • a shaft 41 extends from vane 12 and is rigidly mounted thereto in a coaxial manner.
  • the brake 50 includes a floating brake disc 52 which is disposed between two slotted plates 54a, 54b which are fixed by bar 55 and which also engage a slot in the brake disc 52 at diametrically opposite points. This mounts the brake disc 52 in such a way that it is free to move transversely and its ultimate position when clamped by the brake 50 is determined by brake pads. This ensures clean operation and in particular release of the brake. If the disc is fixed then the pads do not contact the disc necessarily with the surfaces parallel and this result in imperfect brake operation and variability in release.
  • brake 50 includes an arm 58 which can be activated to clamp the brake disc 52.
  • the arm 58 is activated in response to movement of plunger 60.
  • the plunger 60 extends through the brake 50 and forms part of the release mechanism, which in the example shown is a cone driver 56 (refer Figures 13A to 16B).
  • the plunger is connected to 2:1 mechanical lever arrangement.
  • An actuating wire extends from that lever around the shaft 41 to another lever arrangement which moves a roller to act on the arm 58 of the disc brake 52.
  • the mechanical advantage of the second lever is around 14:1 which in combination with the lever action of the brake arm itself gives an overall mechanical advantage of the order of 30:1.
  • tension springs 51 act upon arm 58 to provide a clamping force of about 20kg.
  • the roller that engages the arm 58 that actuates the brake pad moves in an arcuate path and is adjusted such that it is operating at the end of the arc. That is, a small movement of the roller provides a high degree of travel of the arm 58. Adjustment of the position is by way of the mounting of the axis on which the actuating arm pivots. The screw extends through for adjustment of the axis position and hence the arm.
  • Leaf type springs 61 are fitted to initiate movement of the cone drivers 56 because the small movement of the roller against the arm 58 requires additional force to initiate movement as the restoring springs on the brake mechanism (which acts on the lever mounted roller) do not provide a very large force at that high degree of movement on that portion of travel.
  • a pair of cone drivers 56 one for engagement of vanes exiting the primary transfer portion 16 and another for vanes exiting the secondary transfer portion 18, is coupled to the shaft 41 and is configured to operate in connection with the brake 50.
  • Activation of each cone driver 56 is through contact with the end 42 of the coupler link 40.
  • Activation of the cone driver 56 disengages the brake 50, thereby allowing the vane 12 to be rotated so that its orientation can be varied.
  • Movement of the coupler link 40 is generally constant and during initial contact of the end 42 of the coupler link 40 with the cone driver 56, the brake 50 is disengaged. Further movement of the coupler link 40 results in the orientation of the vane 12 being varied. As the end 42 of the coupler link 40 becomes disengaged from the cone driver 56, the cone driver 56 returns to a neutral state and the brake 50 returns to an engaged condition of use which fixes the orientation of the vane 12.
  • Each cone driver 56 includes a conical element 58 that, in connection with housing 60, operates to convert the action of the end 42 of the coupler link 40 of the vane adjustment means 38 perpendicularly so as to activate a plunger 60 ( Figure 9). As illustrated in Figures 11 and 12, a pair of leaf springs 61 are provided so as to urge the release mechanism to a neutral position when not activated. Figures 13A to 13C and 14A to 14C further describe the action of each cone driver 56.
  • the cone driver 56 includes a transfer member in the form of a conical element 58 which is disposed about an anchor point, which in the described example is a sleeve 68.
  • the conical element 58 is a hollow truncated cone or frustoconical element.
  • the conical element 58 has first and second spaced apart annular bearing surfaces 125 and 127 respectively which have different diameters. Each of the bearing surfaces are configured so that a force bears against it so that the force may be converted using the conical element 58.
  • a smaller of said surfaces which in the described example is the first bearing surface 125, is configured to extend loosely around the sleeve 68 so that an input force urging the larger surface 127 toward the sleeve 68 causes the conical element 58 to rotate or tilt, thereby advancing the smaller bearing surface 125 along the sleeve 68 to provide an output force in a direction generally perpendicular to the input force.
  • the conical element 58 is disposed within a housing 62 which is in the form of a cylinder with one end closed and other open. In a resting state a lower surface of the conical element 58 rests squarely on an internal surface of the closed end of the housing 62.
  • a circular cam head 64 Disposed adjacent the open end of the housing 62 is a circular cam head 64.
  • the cam head 64 forms an upper part of plunger 60, a shaft 66 of which is restrained for linear movement within a fixed sleeve 68.
  • Fixed sleeve 68 is fixed to ground plate 63 and the housing 62 is free to move laterally with respect to the sleeve until the conical element 58 has rotated a predetermined amount and locks.
  • An open upper end of the conical element 58 is arranged to fit loosely around the sleeve 68.
  • the open upper end of the conical element 58 is disposed proximal to the open end of the housing 62.
  • the plunger 60 and the housing 62 together define an expandable chamber.
  • Sleeve 68 is truncated so that as the open upper end of the conical element 58 moves upward, it passes over the end of sleeve 68, allowing it to rotate further.
  • the open upper end may be configured so that, after a predetermined amount of rotation, it locks onto Shaft 66 to limit the amount of movement of the cam head 64.
  • the open upper end may be configured so as to allow full rotation of the conical element 58, as shown in Figure 14A.
  • a conical element 58 is used, though it will be appreciated that this element may be replaced with a rigid part having two rings fixed together with a coupling element. It will also be appreciated that two rigid forks, each of which pass around the shaft, also fixed together with a coupling element, may be alternatively be used.
  • Friction reducing coatings may be used to address these issues or ball bearings may be incorporated into the housing 61.
  • a return spring may be required to ensure that the cone driver 56 returns to a neutral position. If a constant load is applied to the plunger 60, the mechanism may return to its neutral state without the need for a return spring.
  • a return spring may be fixed to the ground plate 63 and pass around at least a portion of the circumference of the housing 61 so that movement of the housing 61 relative to the ground plate 63 encounters some resistance, thereby causing the mechanism to return to its neutral position.
  • a leaf spring fixed to the ground plate 63 may act upon the housing 61 to urge it to a neutral position.
  • FIG 15A illustrates an alternative to the cone driver mechanism 56.
  • This mechanism 43 comprises a plunger 45 which includes a circular head 47, a stem 65 and a slider, which is shown in the form of a ball 67.
  • the ball 67 is slidably received in sleeve 69.
  • Use of a ball 67 for the slider allows the shaft to pivot with respect to a longitudinal axis of the sleeve 69.
  • the mechanism 43 includes a ring 85 and an insert 87.
  • the insert 87 is generally annular and an outermost surface is configured to fit inside the ring 85.
  • the insert 87 may be held fixed to an inside surface of the ring 85 using a fastener such as a grub screw for example.
  • the insert 87 has in inner recess 89 which is configured to receive head 47.
  • the head 47 is in the form of a planar circular disc, though other shapes are also possible if the recess 89 in the insert 87 is configured to match the shape of the head 47.
  • the ring 85 is fixed to the insert 87 in such a manner so as to maintain a gap 91 in which a flange 93 of the sleeve 69 can be received.
  • the diameter of the flange 93 is larger that aperture 95 of the ring 85 so that the sleeve 69 is coupled to the ring 85 and the insert 87, though lateral movement between the ring 85/insert 87 and the sleeve 69 is still possible.
  • a return spring may be required to ensure that the mechanism returns to a neutral position. If a constant load is applied to the head 47, the mechanism may return to its neutral state without the need for a return spring.
  • a return compression spring may be fitted between the ball 67 and the insert 87 to urge the ball 67 to a resting position.
  • a return spring may be fitted between the sleeve 69 and the ring 85 to urge these parts to a neutral position relative to each other.
  • a circular head 47 is used, though it will be appreciated that this may be replaced with an elongate member which is configured to pivot with respect to the insert 87.
  • Figures 16A and 16B illustrate an example of the mechanism 43 in use.
  • the mechanism 43 is fixed to an actuator 99 having a platform 101 which is required to be lifted along direction B.
  • Input force A is available though acts in a direction generally perpendicular to direction B and is required to be converted so that it can be utilised.
  • Installing mechanism 43 in communication with force A and actuator 99 provides the required force conversion.
  • the sleeve 69 When the sleeve 69 is acted upon by the force A, the sleeve moves laterally with respect to the ring 85 and the insert 87.
  • the movement of the sleeve 69 is restrained so as to be only in a lateral direction.
  • the movement of the sleeve 69 causes the head 47 of the plunger 45 to rotate, thereby lifting tip 97 and platform 101.
  • Figure 17 illustrates another method of controlling the orientation of the vanes 12 by way of gears.
  • An actuating gear 70 is arranged in communication with the drive disc 26 and the cam disc 29 so as to be actuated by the eccentric movement of the cam disc 29 in a manner similar to that of the vane adjustment means 38.
  • the actuating gear 70 is configured to operate in response to a pull rod, as opposed to a push rod as previously described in relation to member 40.
  • the actuating gear 70 is arranged to engage gear segment 72 fixed to the vane 12. Radial movement of the member 44 causes lever 73 to pivot, thereby moving the actuating gear 70 through arc R. Once the actuating gear 70 and the gear segment 72 are engaged, movement of the actuating gear 70 in this manner causes the vane 12 to rotate, thereby changing its orientation.
  • Figures 18 to 21 illustrate a method of locking and releasing the vanes 12 so that their orientation may be varied by way of a geared system, such as that shown in Figure 17.
  • the vane locking system 71 is mounted to vane shaft 41 and includes an actuator 74 which can move radially on the vane shaft 41. As the actuating gear 70 and the gear segment 72 come into contact, the actuator 74 moves radially along direction F, thereby acting upon cone 75 and in turn lever 76. Rotation of lever 76 causes cable 77 to be retracted.
  • the cable 77 is connected to a wedge 78 disposed between a pair of bearings 79. Movement of the wedge 78 into and out of contact of the bearings 79 acts to expand a channel formed in the end of member 81.
  • the channel in member 81 is disposed between the gear segment 72 and the vane 12. Expansion of the channel causes the gear segment and the vane 12 to become locked or unlocked.
  • the vane becomes unlocked and driven under the action of the movement between the actuating gear 70 and the gear segment 72 to change the orientation of the vanes.
  • the vane lock is no longer released and the vanes are fixed in their orientation.
  • Figures 22 and 23 illustrate another method of controlling the orientation of the vanes 12 using a hydraulic system 80.
  • a pair of cone drivers 56 are used to act upon a transfer lever 82 which is mounted to the vane shaft 41 via a transfer bush 84.
  • Activation of the transfer lever 82 causes a thrust disc 86 to urge against a transfer lever 88 which is in communication with a primary lever 90.
  • the primary lever 90 and a secondary lever 92 are both rotatably mounted to reaction arm 94. Operation of the primary lever 90 in turn operates the secondary lever 92, thereby causing the hydraulic cylinder 96 to lock or unlock so that the orientation of the vanes 12 can be controlled by movement of the piston 98.
  • FIGS 24 and 25 illustrate another method of varying the orientation of the vanes 12.
  • a chain 103 which is disposed adjacent the drive disc 26.
  • the chain 103 is one of three chains which are disposed adjacent to each other in a side by side relationship.
  • Each chain drives a single drive sprocket 11 1 which is coupled to a driver gear (not shown) via a shaft (not shown) that is configured to engage a gear segment 107 on a vane 12 at a point in the transition portion 20a, 20b.
  • Three chains are provided so that three drive sprockets 11 1 may be about the drive disc 26 and offset from the other drive sprockets by 120 degrees.
  • the engagement between a drive sprocket 111 and the vane 12 can occur at three positions which are 120 degrees apart.
  • a pair of idler pulleys 1 13 are provided so that chain 103 can be routed in such a manner as to pass over both a central sprocket 105 and the drive sprocket 111 to provide rotation in a desired direction.
  • Rotation of the central sprocket 105 causes rotation of the drive sprocket 111 so that a desired angle of the drive sprocket 11 1 can be set.
  • Each chain 103 passes around a central sprocket 105 that is controlled independently of the other central sprockets so that each chain 103 is controlled independently of the other chains.
  • the orientation of each vane can be controlled independently of the other vanes.
  • the arrangement shown in Figure 25 is suitable for varying the orientation of the vanes at an end of the apparatus which drives an output shaft. It will be appreciated that at an opposite end of the apparatus, the vanes will need to be rotated in a direction which is opposite to that shown in Figure 25.
  • pulleys 113 and the chain 103 may instead merely pass around the central sprocket 105 and the drive sprocket 1 11 so that the drive sprocket 11 1 rotates in an opposite direction at this end.
  • each drive sprocket 111 may be connected to a piston so as to function as a crank mechanism so that a reciprocal motion is provided by the piston which acts as a pushrod to engage the vanes and vary their Orientation as they pass through the transition portions.
  • Such mechanisms may be configured for use at either end of the apparatus.
  • each central sprocket 105 may be controlled by the cam disc 29 or by another mechanism such as a swash plate, such as that shown in Figure 25, which is driven by the output shaft 28.
  • Figure 26 illustrates another method of controlling the orientation of the vanes 12 using a swash plate mechanism.
  • the mechanism includes a shaft 160 for connection to a stepper motor.
  • the shaft 160 drives gear 162 which rotates a screw driven pitch adjuster 164.
  • a slot 166 allows linear movement of the pitch adjustor 164 on shaft 28 without rotation.
  • Mounted to shaft 33 is a toothed pulley or sprocket 169 which is driven so as to rotate at the same speed as the drive disc 26.
  • the sprocket 169 may be fixed to the same shaft as the drive disc 26.
  • the sprocket 169 may be coupled to the drive disc 26 in another manner, such as a coupler linkage for example, so that the two components rotate together.
  • Swash plate 168 is fixed to and rotates with shaft 28, thereby moving pitch control rods 170. It can be seen that the movement of the pitch control rods 170 is not in a direction consistent with the coupler link of the previously described parallelogram mechanism.
  • a simple mechanical mechanism can be used to convert the basic reciprocating movement generated by the swash plate to movement in a direction suitable for driving a pushrod to vary the orientation of a vane.
  • the angle of the swash plate 168 is varied under the action of link 172 which is in communication with the pitch adjustor 164.
  • Figure 27 illustrates another method of controlling the orientation of the vanes 12 using an alternative swash plate mechanism 100.
  • the mechanism 100 includes arms 102 which are coupled to the push rods by links 104.
  • the mechanism 100 is mounted on the output shaft 28 by a static bush 106.
  • Housing 108 is pivotally mounted to the static bush 106 so that adjustment of degree of movement of the swash mechanism 100 may be achieved by movement of link 1 10.
  • a bearing 1 17 is mounted between ring 109 and the housing 108 so that rotation of the shaft 28 causes the housing 109 to rotate, thereby inducing reciprocal motion of the pushrods through links 104.
  • the connector 140 comprises a coupling element, in the form of a pair of sleeves 142a, 142b, which is configured to surround at least a portion of each cable 14a, 14b.
  • Each of the sleeves 142a, 142b have extensions 144a, 144b which extend along the cable on a side 146b of the sleeve which is remote to the pulleys 24 around which the cables 14a, 14b extend.
  • Each sleeve 142a, 142b is arcuate between the extensions 144a, 144b to prevent contact between the sleeve 142a, 142b and the pulleys.
  • a lug 144 is coupled to the sleeves 142a, 142b.
  • the lug 144 is configured to accept the shaft 41 in such a manner so that the shaft 41 is free to rotate with respect to the connector 140.
  • Each sleeve 142 is arcuate or curved in a central portion 147 which is between the extensions 144a, 144b.
  • the amount of curvature of the curved portion 147 is slight and proportional to a radius of the pulleys 24.
  • the radius of the arc takes into consideration the bend radius of the cable and is just enough to ensure that there is no contact between the sleeve 142 and the pulleys 24.
  • the radius of the arc is smaller than a radius of the pulleys so that the sleeve 142 does not contact the pulleys as the connector 140 moves over them.
  • the curvature of the central portion 147 may be constant or vary in a regular or irregular manner.
  • the curvature of the central portion 147 prevents contact between the sleeve and the pulleys by pushing the sleeve away from the pulleys, thus reducing the amount of. disturbance inflicted on the pulleys as the connector 140 passes over it, thereby reducing unwanted noise and vibrations.
  • a thickness of leading and trailing edges 148a, 148b respectively of each sleeve 142a, 142b is also tapered to further prevent contact between the sleeve 142a, 142b and the pulleys to. reduce the amount of disturbance inflicted on the pulleys as the connector 140 passes over them.
  • This tapering is generally in a region 146a of the sleeve 142 which is innermost during use.
  • a V-shaped groove is provided in the pulleys 24 to receive the cable 14. It will be appreciated that sides of sleeves 142 have a potential to contact the pulleys 24 and cause noise. Tapering of the connector around the leading and trailing edges prevents this contact occurring.
  • the extensions 144a, 144b also urge the cables 14a, 14b into an arc so as to raise each sleeve 142a, 142b away from the pulleys.
  • the extensions 144a, 144b also act to cushion any contact between a sleeve and the pulleys.
  • the curvature of the central portion 147 also contributes a small amount of force to acts to fix the connector 140 to each cable 14 so as to transfer power from the shaft 41 to the cable 14 and, in turn, the drive member about which the cable 14 extends.
  • the extensions 144a, 144b of the sleeve 142 urge the cable 14 into an arc, as the connector 140 becomes loaded the tension in the cable 14 will act to a straighten the cable and the sleeve 142, thus imparting force from the cable 14 on the sleeve 142 which acts to affix the two components together.
  • the sleeves 142a, 142b are required to be coupled together.
  • the sleeves 142a, 142b are coupled by a coupling member 150 from which the lug 144 extends.
  • a support member 152 also extends between the sleeves 142a, 142b and adjacent the coupling member 150.
  • the support member 152 is fixed to the coupling member 150 and has two passages extending through it in which grub screws can be received to form a connection between the sleeve 142a, 142b and the cables 14a, 14b.
  • Each sleeve 142 is sized so that an internal diameter of the sleeve 142 is slightly larger than an external diameter of the cable 14 so that connector may be easily installed on the cable 14 by threading the cable 14 through the sleeve 142.
  • the curvature of sleeve 142 is formed prior to the insertion of the cable 14.
  • An upper portion of each sleeve 142 is configured to accept the grub screw that extends through the support member 152 and through the upper portion of the sleeve to engage the cable and fix the connector to the cable.
  • Each grub screw acts to fix the connector 140 to the cable 14 so as to transfer power from the shaft 12 to the cable 14 and, in turn, the pulleys or drive member about which the cable 14 extends.
  • Lug 144 has a central hole through which the shaft 41 can be received.
  • a screw 154 is used to fix a collar 156 to the shaft 41, though it will be appreciated that other forms of connection may be used to couple the shaft 41 to the lug 144.
  • a single cable or more than 2 cables, for example 3 or 4 may be used.
  • a single coupling element or sleeve may surround each cable or a number of cables.
  • Each of the illustrated sleeves is shown as being circular in cross section, though it will be appreciated that the sleeve may take other forms which are not circular.
  • a sleeve may be configured to surround more than one cable and thus would be appropriately shaped so as to engage each of those cables.
  • An advantage of using a connector such as connector 140 is that some degree of synchronisation between the cables 14 and the drive disc 26, which would otherwise not be ' possible because there is no registration or indexing possible with a cable, can be achieved. It will be noted that this synchronisation can only be achieved while a vane is received through the connector 140. This is because it is the vane shaft 41 which engages the drive disc 26. Because the connector allows some synchronisation to be provided, the manufacture of the endless drive means is simplified and the importance of each cable being of exactly the same length is reduced. It will be appreciated though that, whilst generous, a tolerance on cable length will exist and once this tolerance has been exceed difficulties may be encountered. Accordingly, a vane 12 may become transversely angled with respect to the cables 12 without causing much difficulty as the vanes are brought back into alignment when passing through the transition portions 20a, 20b.
  • Figures 30 and 31 illustrate an alternative drive disc, pulley and cable arrangement to address this issue.
  • a drive disc 120 is disposed between two free-wheeling pulleys 122.
  • a cable 14 extends around each of the pulleys 122 and the pulleys support the weight of the cables.
  • Each vane 12 is connected to the cables 14 with an arcuate connector 124 ( Figure 31) which is configured to engage corresponding portions on each drive disc to transfer energy from the vanes to the drive disc the drive disc 120.
  • a further disc 126 is provided adjacent the innermost pulley 122 and is locked to shaft 28 so as to rotate with the drive disc 120.
  • the vane adjustment means 38 as . previously described, is fixed to disc 126 and acts to engage and vary the orientation of the vanes 12 as they pass through the transition portions 20a, 20b.
  • the drive disc 120 has slots 128, which may also be notches, indentations or extensions, formed around its periphery so as to engage the connector 124 and transfer power from the vanes 12 to the output shaft 28. It can be seen that slots 128 are configured to engage a bridge 130 of the connector 124 so as to bring the vanes into engagement with the drive disc 120.
  • the bridge 130 is a hollow tube so that the shaft 41 of the vanes 12 can pass through and become rotatably fixed to the connector 124. Because it is the connector 124 which engages the drive disc 120, and not the shaft of the vanes, it is possible to remove a vane from the apparatus without upsetting the synchronisation of the apparatus.
  • Each connector 124 includes a pair of arcuate arms 129 and is configured to attach to each cable 14 using a pair of dogs 132 rotatably fixed to each arm 129 at ends thereof.
  • Each dog 132 includes a screw for gripping the cable 14 so as to fix the connector 124 to the cable 14.
  • the arms 129 are elongate so as to provide a longer reaction arm to support the connector and reduce any tendency of the connector to kink the cable.
  • FIG 32 illustrates a stator 180 which may be used in conjunction with the apparatus 10 to improve the efficiency of the apparatus 10.
  • the stator 180 includes a plurality of guide vanes 181 which form three stages of guide vanes: a first stage 182, a second stage 184 and a third stage 186.
  • Each of the guide vanes 181 may be made of from a metallic or a cloth material.
  • Each of the guide vanes 181 may also have a slightly curved profile.
  • the vanes 181 are used to guide the wind 183 so that the air flow through the apparatus 10 is relatively straight. Reducing the wake turbulence caused by the apparatus 10 increases the efficiency of the apparatus.
  • the vanes 12 are moving in direction D and the orientation of the guide vanes 181 is configured accordingly.
  • the first stage of guide vanes 182 directs the air flow upwards and onto the vanes 12 in the primary transfer portion 16.
  • the second stage of vanes 184 guides the airflow through the apparatus 10 and onto the vanes 12 passing through the secondary transfer portion 18.
  • the third stage of vanes 186 assists in smoothing out the airflow as it exits the apparatus 10 so that it is generally at a similar height to which it entered the apparatus 10.
  • the stator 180 may be in the form of an array, or separate arrays, of guide vanes which are fixed together, though adjustable so that all of the vanes move together in a fixed relationship.
  • the described examples each have a single series of vanes disposed between two cables.
  • a further cable extending around another set of pulleys may be provided and a second series of vanes adjacent the first series of vanes 12 provided which extend between the second cable and the additional cable.
  • a common output shaft may be used.
  • the described examples also feature an endless drive means which comprises a pair of cables disposed adjacent each other.
  • multiple cables may be used to accommodate apparatus having a large number of vanes or which is subject to a high wind loading.
  • three or more cables may be used and the number of cables used is not necessarily required to be even.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Wind Motors (AREA)

Abstract

L'invention concerne un appareil de conversion d'énergie fluidique permettant d'extraire de l'énergie d'un fluide en écoulement et comprenant : une pluralité de pales montées pivotantes et agencées pour effectuer un mouvement autour d'un itinéraire continu présentant un tronçon de transfert primaire, un tronçon de transfert secondaire, et des tronçons de transition entre ces derniers, l'appareil étant configuré de telle manière que lorsqu'il fonctionne, les pales agencées sur le tronçon de transfert primaire se trouvent en général dans le sens de l'écoulement du fluide en amont des pales agencées sur le tronçon de transfert secondaire, et le fluide s'écoule séquentiellement en passant respectivement par les pales du tronçon de transfert primaire et du tronçon de transfert secondaire ; un frein desserrable utilisable pour chaque pale, chaque frein desserrable étant configuré pour bloquer l'orientation de la pale concernée lorsqu'il est engagé ; et un moyen d'ajustement configuré pour desserrer le frein et modifier l'orientation d'une pale lorsque la pale est sur un des tronçons de transition de manière à réguler l'exposition de chaque pale au fluide incident sur ladite pale.
PCT/AU2012/000559 2011-05-20 2012-05-18 Appareil de conversion d'énergie fluidique Ceased WO2012159152A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2011901987 2011-05-20
AU2011901987A AU2011901987A0 (en) 2011-05-20 Fluid Energy Conversion Apparatus

Publications (1)

Publication Number Publication Date
WO2012159152A1 true WO2012159152A1 (fr) 2012-11-29

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014089630A1 (fr) * 2012-12-13 2014-06-19 University Of Wollongong Appareil de conversion de l'énergie éolienne
WO2019012233A1 (fr) * 2017-07-12 2019-01-17 Institut Polytechnique De Grenoble Centrale hydroelectrique
JP2020526708A (ja) * 2017-07-13 2020-08-31 チョウ、ヨン−スCHO, Yong−Soo 潮力発電装置
DE202022102557U1 (de) 2022-05-11 2023-08-17 Tim Brocks Windkraftanlage

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB859007A (en) * 1957-07-23 1961-01-18 Winfred Matthewman Improvements in or relating to thrust and/or lift producing devices for use in a fluid medium
WO2001027470A1 (fr) * 1999-10-08 2001-04-19 Ingvald Lie Machine eolienne
US6435827B1 (en) * 2000-10-27 2002-08-20 James Steiner Apparatus for generating a fluid flow
WO2010030895A2 (fr) * 2008-09-11 2010-03-18 Levi Avraham Y Aérogénérateur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB859007A (en) * 1957-07-23 1961-01-18 Winfred Matthewman Improvements in or relating to thrust and/or lift producing devices for use in a fluid medium
WO2001027470A1 (fr) * 1999-10-08 2001-04-19 Ingvald Lie Machine eolienne
US6435827B1 (en) * 2000-10-27 2002-08-20 James Steiner Apparatus for generating a fluid flow
WO2010030895A2 (fr) * 2008-09-11 2010-03-18 Levi Avraham Y Aérogénérateur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014089630A1 (fr) * 2012-12-13 2014-06-19 University Of Wollongong Appareil de conversion de l'énergie éolienne
WO2019012233A1 (fr) * 2017-07-12 2019-01-17 Institut Polytechnique De Grenoble Centrale hydroelectrique
JP2020526708A (ja) * 2017-07-13 2020-08-31 チョウ、ヨン−スCHO, Yong−Soo 潮力発電装置
DE202022102557U1 (de) 2022-05-11 2023-08-17 Tim Brocks Windkraftanlage

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