WO2008047991A1 - Système de génération d'énergie éolienne comprenant une turbine à axe vertical équipée d'une roue à jet - Google Patents

Système de génération d'énergie éolienne comprenant une turbine à axe vertical équipée d'une roue à jet Download PDF

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Publication number
WO2008047991A1
WO2008047991A1 PCT/KR2007/002902 KR2007002902W WO2008047991A1 WO 2008047991 A1 WO2008047991 A1 WO 2008047991A1 KR 2007002902 W KR2007002902 W KR 2007002902W WO 2008047991 A1 WO2008047991 A1 WO 2008047991A1
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WO
WIPO (PCT)
Prior art keywords
guide vane
inlet guide
wind
power generating
impeller
Prior art date
Application number
PCT/KR2007/002902
Other languages
English (en)
Inventor
Seung-Bae Lee
Original Assignee
Aeronet Co., Inc.
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 Aeronet Co., Inc. filed Critical Aeronet Co., Inc.
Priority to US12/445,927 priority Critical patent/US20100296913A1/en
Publication of WO2008047991A1 publication Critical patent/WO2008047991A1/fr

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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
    • F03D—WIND MOTORS
    • F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor 
    • F03D3/02—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor  having a plurality of rotors
    • 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
    • F03D—WIND MOTORS
    • F03D13/00—Assembly, mounting or commissioning of wind motors; Arrangements specially adapted for transporting wind motor components
    • F03D13/10—Assembly of wind motors; Arrangements for erecting wind 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
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • 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
    • F03D—WIND MOTORS
    • F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor 
    • F03D3/04—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor  having stationary wind-guiding means, e.g. with shrouds or channels
    • 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
    • F03D—WIND MOTORS
    • F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor 
    • F03D3/04—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor  having stationary wind-guiding means, e.g. with shrouds or channels
    • F03D3/0409—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor  having stationary wind-guiding means, e.g. with shrouds or channels surrounding the 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
    • F05B2240/20—Rotors
    • F05B2240/21—Rotors for wind turbines
    • F05B2240/211—Rotors for wind turbines with vertical axis
    • F05B2240/213—Rotors for wind turbines with vertical axis of the Savonius type
    • 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
    • F05B2240/21—Rotors for wind turbines
    • F05B2240/211—Rotors for wind turbines with vertical axis
    • F05B2240/215—Rotors for wind turbines with vertical axis of the panemone or "vehicle ventilator" 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
    • Y02E10/70—Wind energy
    • Y02E10/74—Wind turbines with rotation axis perpendicular to the wind direction
    • 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
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin

Definitions

  • the present invention relates to a cross flow wind turbine with a vertical axis and a power generating system employing the same, and more particularly, to a cross flow wind turbine with a vertical axis and a power generating system employing the same with a higher power coefficient than turbines with horizontal axes, that do not cause noise pollution in the vicinity, that require a minimum of land, and which can be transported over land routes regardless of how large their capacities are.
  • Wind generators employ technology to convert movement of wind to electrical energy.
  • the generating capacity of the total number of wind generators installed across the globe amounted to 40,300MW, or the approximate equivalent to the capacity of 40 nuclear reactors, which is electricity that can power 2,300 homes.
  • wind generators were of comparatively small scale, with an impeller diameter of 15m and a capacity of 55KW; however, wind generators on the market today have increased in scale (with an impeller diameter of 50-10Om) and capacity (of 750-2,000KW).
  • Wind generators can largely be divided into vertical-axis and horizontal-axis generators.
  • Generators with vertical rotating axes include the widely known Darrieus-type generator, generators with an H-shaped blade, and Savonius impeller-type generators.
  • the advantage of such vertical shaft generators is that they do not require a yawing device required by generators with horizontal axes.
  • generators with vertical axes are generally less efficient at energy conversion compared to generators with horizontal axes, and are prone to vibration.
  • Mid to large-sized wind generators generally use inexpensive and sturdy induction-type generators which are directly connected to electrical power systems, and are designed to rotate at a constant speed according to the fixed frequency of the electrical power systems, regardless of constantly changing wind speeds.
  • the rotating speed of the impeller may be determined by a gear ratio of intermediate gears for altering speed.
  • the aerodynamic power coefficient (Cp) of a wind turbine is a ratio of shaft power generated by the turbine impeller to the wind power exerted on the impeller, and can be calculated using the following equation.
  • T torque (N -m)
  • ⁇ (rad/s) the angular speed
  • the speed coefficient ⁇ (also called the tip speed ratio) is a ratio of the tip speed ratio (Vt; p ) to the oncoming wind speed, and when the type of turbine is decided on, generally, the maximum power coefficient value can be calculated using Equation 2 below.
  • Equation 2 Equation 2
  • Equation 1 The performance of the wind turbine is determined by the power coefficient C p in Equation 1.
  • C p is the ratio of turbine output to the power of the oncoming air. In other words, it can be seen as the energy conversion efficiency.
  • the highest C p value attainable by a wind generator with a horizontal axis is 0.598
  • the highest power coefficient attainable by a Darrieus type vertical axis wind generator is 0.35.
  • these coefficients are theoretical, and coefficients achieved in practice fall short of these theoretical maximums.
  • FIG. 3 shows an oncoming wind speed of 5m/s, where the exiting wind of an inlet guide vane 20, despite it being at the mouth of a large inlet guide vane having an exit surface ratio of approximately 3.83, is unable to flow entirely into the entrance and flows to regions of low resistance, so that increase of streamlines corresponding to the surface area does not occur.
  • the present invention is directed to a jet wheel type vertical axis turbine that substantially obviates one or more problems due to limitations and disadvantages of the related art.
  • An object of the present invention is to provide a jet wheel type vertical axis turbine that blocks flow of air inside the impeller, so that a high speed jet pressure on the inlet guide vane is converted to a constant pressure between the blades disposed downstream of the flow which has passed through the inlet guide vane, thus generating a large amount of torque. Also, a large vortex is created around the region of the blades disposed downstream of the inlet guide vane that generate negative torque, so that negative torque is minimized.
  • a wind power generating system having a plurality of turbines installed coaxial Iy on a vertical axis on a support, and a generator driven by the plurality of turbines, the wind power generating system including: an impeller including an upper plate, a lower plate, and a plurality of arc-shaped blades sealed to prevent airflow therethrough; an arc-shaped inlet guide vane fixed to a frame connected through a separate bearing to an axis of the impeller, the inlet guide vane for accelerating a speed of wind blowing against the plurality of blades and converting the wind to a constant pressure between the blades and generating torque; a tail wing portion fixed to the frame, for controlling a position with respect to a direction of the wind; a gear assembly disposed between the axis of the impeller and the generator, for driving the impeller to uniformly maintain a vane rotating speed ratio to yield a high energy conversion efficiency, regardless
  • the wind power generating system may further include a side rear surface guide vane installed at a side of the frame, for using a collecting of main lines of flow in a rotating direction through rotation of the impeller, to increase efficiency of the wind power generating system.
  • the inlet guide vane may have a distribution between a maximum value of a chord that is not covered by more than half of a radius of the impeller when the inlet guide vane is projected in a reverse flow direction, and a minimum value of the chord for minimizing loss through shortening an inlet passage, such that an accelerating result is generated in a chord of the inlet guide vane that is minimally long when a pitch of the blade is equal to an entire span of the inlet guide vane.
  • the inlet guide vane may have an outlet angle distribution formed by a relative speed vector of the blade inlet and the blade, of between at least -10° to +10° .
  • a pitch (p) between two of the inlet guide vane may be derived through designating an entire span pitch of the inlet guide vane as a multiple integer of a blade pitch, for generating torque of a cycle parallel to an inlet jet of the blade.
  • the wind power generating system may be modularized for utilizing minimal surface area of land and simultaneously having a highly efficient vertical axis turbine, through forming diameters of impellers at different levels in consideration of a generating power requirement of each module, after estimating wind speeds at a central point of each module within boundary layers thereof.
  • the controller may perform feedback control of the rotating axis of the inlet guide vane through the step motor to adjust an inlet angle between the wind direction and the entrance of the inlet guide vane, for preventing an overload of the generator through ensuring an outlet jet of the inlet guide vane does not exceed rated values according to a pre-inputted maximum speed (V c ) therefor and a pre-inputted operating vane speed ratio ( ⁇ m i n , ⁇ r aax ), and the controller secures a degree of efficiency of the wind generator system, regardless of wind speed, through adjusting the connected gear ratio of the generator differently according to a calculated value of the vane speed ratio from an rpm sensor of the impeller, and operates within an allowable operating vane speed ratio.
  • V c pre-inputted maximum speed
  • ⁇ m i n , ⁇ r aax pre-inputted operating vane speed ratio
  • the impeller, the inlet guide vane, and the frame may be supported by a horizontal axis, and a surface of the tail wing portion controlling the position according to the wind direction is installed vertically on a side opposite to the horizontal axis.
  • An advantage of the present invention is that by reducing the resistance within the inlet guide vane, feeding a flow of high speed wind toward the impeller blades at a suitable angle, optimizing the chord length of the inlet guide vane, the curvature of the inlet guide vane, and the exit angle of the inlet guide vane at an operating vane speed ratio for the pitch of one or many impeller blades, and by giving impellers at different levels diameters that are calculated based on a requirement to satisfy a generating power of each turbine module and wind speeds at a central point of each turbine module within boundary layers thereof, the land area used is minimized and a vertical axis turbine of high efficiency can be obtained.
  • FIG. 1 is a schematic view showing torque output of a Savonius drag- type vertical shaft turbine, according to the position of the impeller! ⁇ 38>
  • FIG. 2 is a view showing flow line distribution around a jet wheel type turbine impeller having a straight inlet guide vane! ⁇ 39>
  • FIG. 3 is a diagram showing an example of speed distribution
  • FIG. 4 is a schematic perspective view of a jet wheel type vertical axis wind turbine according to an embodiment of the present invention
  • FIG. 5 is a schematic perspective showing the gear assembly in FIG.
  • FIG. 6 is a two-dimensional diagram showing geometric variables of an inlet guide vane and rotor blade shown in FIG. 4; ⁇ 43>
  • FIG. 7 is a diagram showing a triangle formed by a speed vector at the outlet of the inlet guide vane in FIG. 4, the rotating speed vector at the tip of the rotor blade, and a relative speed vector of the rotor blade inlet ;
  • FIGS. 8 through 13 are diagrams showing various embodiments of a rotor according to changes in the inlet angles of rotor blades, of which the upper and lower surfaces are sealed; ⁇ 45> FIGS.
  • FIG. 14 through 19 are diagrams showing various embodiments of rotors according to changes in the inlet angles of the rotor blades, of which the upper and lower surfaces are sealed;
  • FIG. 20 is a diagram of a design embodiment of an impeller with an open upper and lower surface at a diameter Do of the opening of the rotor;
  • FIG. 21 is a graph comparing the respective performance characteristics of when both the upper plate and lower plate of a turbine to which an inlet guide vane of the present invention is installed are closed, when only one of the upper and lower plates are open, and when both the upper and lower plates are open; ⁇ 48> FIG.
  • FIG. 22 is a diagram showing design variables of a side rear guide vane of a jet wheel type vertical axis turbine according to the present invention
  • FIG. 23 is a graph comparing performance characteristics when an inlet guide vane (I.G.V.) and a side rear guide vane (S.G.V.) are installed and when they are not installed
  • FIG. 24 is diagram showing design variables of rotor size in stages for a wind generating system employing a jet wheel type vertical axis wind turbine according to the present invention!
  • FIG. 25 is a perspective view of an example of a module-type structure of a jet wheel type vertical axis wind turbine according to the present invention that is supported by a truss structure; ⁇ 52> FIG.
  • FIGS. 27 and 28 are diagrams showing formative sections of impeller wings and upper and lower plates by module of a jet wheel type vertical axis wind turbine according to the present invention
  • FIGS. 29 and 30 are flowcharts showing control algorithms employed by a jet wheel type vertical axis wind turbine according to the present invention.
  • FIG. 4 is a schematic perspective view of a jet wheel type vertical axis wind turbine according to an embodiment of the present invention
  • FIG. 5 is a schematic perspective showing the gear assembly in FIG. 4.
  • a jet wheel type vertical axis turbine and a wind generator system employing the same includes a pair of turbines 1 co-axial Iy disposed one above the other, a speed sensor 23, a gear assembly 44, a generator 45, a plurality of turbine supports 60, and a controller 70.
  • a turbine 1 includes an impeller 10, inlet guide vanes 20 and 21, an inlet guide vane rotating shaft 22, a side rear surface guide vane 30, and a tail wing portion 50.
  • the impeller 10 blocks wind flow with a circular arc shaped blade 11 and top and bottom plates.
  • the inlet guide vanes 20 and 21 are fixed to a frame 12 connected to a bearing 41 that is separate from that of an impeller shaft 10a, so that wind blowing toward the wings is accelerated and a constant pressure can be maintained between the blades 11 to generate torque.
  • the side rear surface guide vane 30 and the tail wing portion 50 are respectively fixed at sides of the frame 12, and the tail wing portion 50 especially adjusts the incoming direction of wind.
  • the gear assembly 44 is disposed between the impeller shaft 10a and the generator 45, and uses a generator torque controlling method that maintains a high level of energy efficiency, regardless of constantly fluctuating wind speeds with respect to a fixed frequency of the electrical power system, and a constant rotating speed of the vanes.
  • the gear assembly 44 may be a multi-speed assembly with two or more helical or bevel gears, in order to attain a gear ratio of 1:100 or higher.
  • the controller 70 feeds back the speed signal of the jet to control the received direction of the wind and the angle of the inlet between the inlet guide vanes 20 and 21 through controlling the rotation of the inlet guide vane rotating shaft 22 of the inlet guide vane 20 through a step motor, in order to maintain a uniform rotating speed of the turbine.
  • Elements not described in FIGS. 4 and 5 include an inlet guide vane case shaft thrust bearing 41, an impeller shaft thrust bearing 42, a drive shaft gear 43, and a generator support 46.
  • FIG. 6 is a two-dimensional diagram showing geometric variables of an inlet guide vane and rotor blade shown in FIG. 4, and FIG. 7 is a diagram showing a triangle formed by a speed vector at the outlet of the inlet guide vane in FIG. 4, the rotating speed vector at the tip of the rotor blade, and a speed vector of a relative speed vector of the rotor blade inlet.
  • the forming factors of the inlet guide vanes 20 and 21 that affect the increase in performance of the above-described turbine 1 may be defined as the cord length (C) of the inlet guide vanes, a ratio (pitch-chord ratio) of the pitch (p) of the inlet guide vanes to the chord length (C) thereof, a curvature of the inlet guide vanes, and an outlet angle ( ⁇ ) of the inlet guide vanes.
  • an optimum outlet angle of the inlet guide vane 20 is given by altering the pitch of one or many impeller blade(s) to correspond to the given rotating speed ratio.
  • FIG. 6 is a two-dimensional plan view showing geometrical variables of the inlet guide vane 21 and the impeller blade 11.
  • the outlet angle ( ⁇ ) of the inlet guide vane 21 and the inlet angle ( ⁇ ib) of the impeller blade 11 are respectively the angles formed between the outlet tangent of the inlet guide vane 21 and the inlet tangent of the blade 11 with the rotating direction at the end of the blade 11.
  • FIG. 7 shows a triangular speed vector shape of the speed vector Ci of the inlet guide vane 20, the rotating speed vector Ui of the end of the blade 11, and the relative speed vector W 2 of the blade 11 inlet.
  • Equation 3 the inlet angle of attack (i) is defined as ⁇ itr ⁇ i-
  • Z 3 and Z r are the number of inlet guide vanes 20 and 21 and blades 11, and when ⁇ 0 is defined as the angle between the blades 11, the minimum and maximum values for the distribution of chord lengths (C) of the inlet guide vane 20 can be derived using Equation 3 below. ⁇ 70> [Equation 3]
  • D is the diameter of the impeller 10
  • n number of chord lengths of the inlet guide vane have values from Ci - C n
  • m is an overall pitch of the inlet guide vane 20 that is, a whole number value of (Z 3 -Dp divided by the blade pitch.
  • the angle of attack ( ⁇ i b - ⁇ i) formed by the blade inlet relative speed vector (Wi) and the blade is between -10° and
  • Equation 4 can be used to obtain the outlet angle ( ⁇ ) of the inlet guide vane from the given B 2b and the range of the angle of attack function. ⁇ 73> [Equation 4]
  • the distance between the rows of the inlet guide vane 20 that is also the pitch (p) is made to be the entire pitch of the inlet guide vane - that is, so that (Z s -l)p becomes a multiple integer of the blade pitch (m) and allow the blade intake jets to have parallel torque pulses.
  • ⁇ is the design tolerance between the blade 11 and the inlet guide vane 20.
  • FIGS. 8 through 12 various embodiments of the inlet guide vane 20 according to the present invention will be described using Equations 3 through 5. Of the embodiments, those in which the length of the inlet passage is minimized is preferable, in order to reduce loss in the passage and attain turbine efficiency.
  • the outlet angle ( ⁇ ) of the incoming air in each of the channels against the rotors may be made the same.
  • the high speed dynamic pressure from the inlet guide vanes 20 and 21 between the plurality of blades 11 juxtaposed to the inlet guide vanes 20 and 21 is maintained at a constant pressure or maintains consistency of positive pressure and negative pressure against either side of the blades in order to generate torque. Therefore, the impeller's performance varies according to the number of rotations of the impeller ( ⁇ ), the diameter of the impeller (D), the diameter of the impeller hub (Dh), the diameter of the opening of the upper and lower plates (D 0 ), the number of blades (Z 1 -), and the inlet angles (J3 ib ) of the blades.
  • the torque output of a Savonius vertical axis type turbine fluctuates widely according to its rotation, so that it is preferable to determine the number of wings (Z r ) based on the above Equation 5.
  • the wing inlet angles ( ⁇ ib) are determined according to the rated vane speed ratio ( ⁇ r ), and is generally a value between 10° and 70° .
  • FIGS. 14 through 19 are diagrams showing various embodiments of rotors according to changes in the inlet angles of the rotor blades 11, of which the upper and lower surfaces are sealed
  • FIG. 20 is a diagram of a design embodiment of an impeller with an open upper and lower surface at a diameter Do of the opening of the rotor.
  • FIG. 21 shows the measured performance characteristics of the turbine when both the upper and lower plates, between which the inlet guide vanes are installed, are sealed, when one of the plates is opened, and when both the upper and lower plates are opened. The results show that in a large-sized turbine, the highest level of efficiency is derived when both the upper and lower plates are open.
  • FIG. 22 is a diagram showing design variables of side rear guide vane of a jet wheel type vertical axis turbine according to the present invention.
  • ⁇ i and ⁇ 2 are the respective inlet and outlet installed angles of the side rear surface guide vanes
  • ⁇ 3 and ⁇ 4 are respective angles formed by the rotating direction of the rotor blades and an inlet tangent of a side rear surface guide vane, and the rotating direction of the rotor blades and an outlet tangent of a side rear surface guide vane
  • P is shows the position of a central pivot axis of the side rear surface guide vane.
  • the side rear surface guide vane allows the finely spaced lines to the right of the rotating rotor in FIG.
  • FIG. 23 is a graph comparing performance characteristics when an inlet guide vane (I.G.V.) and a side rear guide vane (S.G.V.) are installed and when they are not installed.
  • I.G.V. inlet guide vane
  • S.G.V. side rear guide vane
  • C p maximum operating coefficient
  • a turbine module with two or more vertical axis jet wheel turbines may be used, as shown in FIG. 4.
  • the impeller diameter from end to end is designed keeping in mind changes in wind speed according to altitude (atmospheric boundary layers). That is, using Equation 6 below, after the wind speeds in the atmospheric boundary layers at the center of the turbine module are estimated, the impeller diameters at each level are calculated to satisfy the generating requirements for each module.
  • the coefficient showing the speed distribution has a value of approximately 1/0.16, and Z g shows the thickness of a boundary layer.
  • FIG. 24 is diagram showing design variables of rotor size in stages for a wind generating system employing a jet wheel type vertical axis wind turbine according to the present invention.
  • the power for each module is:
  • Equation 6 the estimated wind speed (Coo) at the center of the module using Equation 6 and an efficiency value C p estimated using the vane speed ratio derived through Equation 2 are used to repeat the calculations of the diameters D for the turbines of the module.
  • a is the ratio of the height to the diameter of the impeller 10
  • Q n is the efficiency of the generator motor.
  • the ratio of the impeller height to its diameter may be different for each turbine module.
  • FIG. 25 is a perspective view of an example of a large-scale module- type structure of a jet wheel type vertical axis wind turbine according to the present invention with a fixing axis 40 is supported by a truss structure 80.
  • FIG. 26 shows a large-scale module type jet wheel vertical axis wind turbine with a fixing axis 40 installed on a bed on a ground surface, and a rail structure 90 supporting a roller bearing, installed below the rotor blades and guide vanes to distribute the weight of the axis, to move over a rail above the bed on the ground.
  • the impeller 10 blades and the upper and lower plates for each module are configured in a frame structure (as shown in FIG. 27), a truss structure (as shown in FIG. 28), or a membrane structure (not shown) formed over a truss.
  • FIGS. 29 and 30 are flowcharts showing control algorithms employed by a jet wheel type vertical axis wind turbine according to the present invention.
  • the inlet guide vane 20 is installed to not only increase the speed of oncoming wind, but also control the rotation of the impellers according to a measured wind speed against the impellers using controlling algorithms as shown in FIGS. 29 and 30, in order to overcome the drawback of conventional large-scale drag-type turbines in their high degree of efficiency fluctuation.
  • a step motor or a hydraulic motor is used to control (through feedback) the rotating shaft 22 of the inlet guide vanes 20 and 21, so that wind direction and the blown angle between the entrances of the inlet guide vanes can be controlled.

Abstract

L'invention concerne un système de génération d'énergie éolienne qui constitue une technologie permettant de convertir de l'énergie éolienne en énergie électrique. Le système bloque l'écoulement d'air à l'intérieur de la roue, de façon qu'une pression de jet haute vitesse sur une IGV (aube directrice d'entrée) soit convertie en pression constante entre les aubes disposées en aval de l'écoulement qui est passé dans l'aube directrice d'entrée, ce qui permet de générer une quantité importante de couple.
PCT/KR2007/002902 2006-10-18 2007-06-15 Système de génération d'énergie éolienne comprenant une turbine à axe vertical équipée d'une roue à jet WO2008047991A1 (fr)

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US12/445,927 US20100296913A1 (en) 2006-10-18 2007-06-15 Wind power generating system with vertical axis jet wheel turbine

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KR20060101180 2006-10-18
KR10-2006-0101180 2006-10-18

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN112145341A (zh) * 2019-06-28 2020-12-29 泓星科技有限公司 垂直轴式风力发电机

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US5463257A (en) * 1993-11-23 1995-10-31 Yea; Ton A. Wind power machine
KR200163686Y1 (ko) * 1999-06-25 2000-02-15 박광한 풍력이용률이향상되는풍차
EP1079104A1 (fr) * 1999-02-03 2001-02-28 Fredy P. Paciello Generateur hydraulique et/ou eolien ameliore
KR20060052694A (ko) * 2003-06-05 2006-05-19 인텍 파워 시스템스 리미티드 발전기

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5463257A (en) * 1993-11-23 1995-10-31 Yea; Ton A. Wind power machine
EP1079104A1 (fr) * 1999-02-03 2001-02-28 Fredy P. Paciello Generateur hydraulique et/ou eolien ameliore
KR200163686Y1 (ko) * 1999-06-25 2000-02-15 박광한 풍력이용률이향상되는풍차
KR20060052694A (ko) * 2003-06-05 2006-05-19 인텍 파워 시스템스 리미티드 발전기

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CN112145341A (zh) * 2019-06-28 2020-12-29 泓星科技有限公司 垂直轴式风力发电机

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