MD660Z - Wind turbine - Google Patents

Abstract

The invention relates to wind-power engineering, namely to wind turbines designed for individual consumers.The wind turbine comprises a mast (8), on which is installed a rotor (1) with blades (2) with aerodynamic profile, placed in a gondola, mounted with the possibility of rotation around the mast (8) by means of tail-vane wheels (5), connected to a drive, formed of two worm gearings, an annular convergent diffuser (7), fixed to the blades (2) coaxially with the rotor (1), and a thermogenerator (9), mounted between the sections of the mast (8) and kinematically connected to the rotor (1) by means of a bevel gearing.

Description

The invention relates to wind energy, namely to wind turbines intended for individual consumers.

In the field of energy conversion systems of atmospheric currents directly into thermal energy, three directions of development have been configured.

The first direction refers to technical solutions, through which the available energy potential of the atmospheric currents is converted into electrical energy, and this is subsequently transformed into thermal energy. These systems for converting wind energy into useful energy are characterized by additional losses when transforming mechanical energy into electrical energy, then into thermal energy, and, respectively, by relatively increased costs.

The second direction refers to the systems for converting the energy of atmospheric currents directly into thermal energy, produced in special devices by the internal friction forces of the liquid, for example by injecting the liquid under pressure through small holes with the release of heat.

The disadvantages of these systems are the low reliability and high costs of high pressure hydraulic devices.

The third direction refers to the development of technical systems for converting wind energy directly into thermal energy, produced in thermal generators with eddy currents, which transform mechanical energy into thermal energy.

This direction of development is characterized by widening the possibilities of increasing the efficiency of the conversion of the available wind energy potential into useful energy for an extended range of air current speeds. It is considered ideal that the wind energy conversion system works efficiently in the entire range of air current speed variation in the location of the wind turbine installation, for example, from 3 to 20...25 m/s. At the same time, in wind turbines with power up to 30 kW, the nominal power corresponds to the wind speed of 10...12 m/s.

In this case, in wind turbines with three blades, at a wind speed of 20 m/s, the overload factor of the wind energy conversion system (with electric generators) should increase by 5...6 times.

In reality, conventional electric generators have an overload factor of 1.2...1.3.

It follows that for wind speeds higher than the nominal one of 10...12 m/s, we have to limit the mechanical power converted into electrical energy, a fact that leads to a sudden decrease in the efficiency of converting mechanical energy into electrical energy.

For the conversion of the kinetic energy of the atmospheric currents directly into thermal energy with relatively small wind turbines (up to 20...30 kW), technical solutions based on various devices for transforming mechanical energy into thermal energy are known.

A wind-driven heating system is known, which includes a tower, on which a bladed rotor is installed, located on a hub with the possibility of orienting it to the direction of the wind with the help of a vane, a volumetric hydraulic pump with gear wheels, the driving shaft of which is connected coaxially with the blade rotor shaft, a hydraulic system connected to the volumetric hydraulic gear pump and to an oil reservoir through the suction and discharge pipes, equipped with a damper with a small diameter orifice. The rotor with blades, under the action of the air currents, rotates the pump shaft with gears meshed together, so that the oil in the interdental space generates pressure in the discharge pipe. When the oil flows through the orifice damper with a pressure difference, heat is released with its discharge into the oil tank, and from the tank - into the residential heating system [1].

The disadvantage of this system is the reduced reliability of the components operated under high pressure. At the same time, the hydraulic system of considerable length (equal to the height of the tower), connected at one end with the gear pump and at the other end with the oil tank, rotates around the axis of the tower with the orientation of the bladed rotor to the changing direction of the wind , a fact that requires complex and expensive constructive solutions.

As the closest solution, a wind turbine is presented, which contains a tower, on which is installed a rotor with blades, located on a hub in a nacelle, installed with the possibility of rotation around the tower, as well as an electric generator, the shaft of which is connected with the blade rotor shaft. The turbine is equipped with two wind-wheels with blades with an aerodynamic profile, placed symmetrically on one side and the other of the nacelle, a hydraulic system is installed inside the nacelle, through which the nacelle has the possibility of tilting with respect to the axis of the tower. To increase the efficiency of the energy conversion of the air flow covered by the entire surface swept by the rotor blades, including the area adjacent to the hub, a central multi-blade turbine with a diameter d=(0.1...0.15) is coaxially located in the central area of the rotor from the diameter D of the rotor, consisting of a divergent inner diffuser, a convergent outer diffuser and a crown with blades, located in the upstream area between them, which have an aerodynamic profile and are inclined to the plane of the swept surface of the rotor at an angle in the same direction as well as the inclination of the rotor blades. The central multiblade turbine can be additionally equipped with a second row of blades, located downstream of the rotor [2].

The disadvantages of this turbine, in the case of using wind energy to produce thermal energy for heating residential spaces and other needs, consist of the following.

First of all, the problem related to the accumulation of useful energy produced and its use in periods when the speed of air currents V < 3 m/s is relevant, which in the case of thermal energy is technically solved more simply and with lower costs. For example, the ratio between the cost of an electric accumulator (in the case of wind turbines with electric generators) and a thermal accumulator of the same capacity (in the case of wind turbines with the conversion of wind energy directly into thermal energy) is 10 times higher, and the duration of operation of the thermal accumulator is higher than the electric one.

Secondly, the production of thermal energy from electricity with the use of electric accumulators or from the electricity produced directly by the electric generator of the wind turbine is characterized by higher costs and lower efficiency, determined by the double transformation of mechanical energy into thermal energy.

Thirdly, in wind turbines with electric generators, the bladed rotor is designed so that for the range of air current speeds between 3 m/s and 10...12 m/s, the available wind energy potential is converted into useful energy with maximum efficiency possible, and at air current speeds higher than 10...12 m/s the rotor converts the wind energy with a much lower efficiency, because the mechanical power must be limited by rotating the rotor at a certain angle from the wind direction or by changing the angle of attack of aerodynamic blades, braking, etc. Thus, at speeds up to 12 m/s, the conversion efficiency is determined by the aerodynamic profile of the blades with the performance coefficient Cp. The design of the aerodynamic rotors is carried out taking into account the Cp coefficient and the overload factor of the electric generator, which must not exceed 1.2...1.3 of the nominal load converted to air current speeds of 10...12 m/s. In this case, the shape of the aerodynamic profile of the blades must ensure self-braking at high speeds (V > 11...12 m/s), or the projection of the surface swept by the rotor blades on the plane perpendicular to the direction of the air current must be reduced, for example by tilting the rotor at a certain angle to the axis of the tower.

From these considerations, it follows that in wind turbines with electric generators, for speeds of air currents higher than the nominal one, the available wind power converted into useful energy must be limited, consequently the efficiency of the conversion of the wind energy potential into electricity decreases suddenly. At the same time, the efficiency of the transformation of electrical energy into thermal energy is reduced.

The problem that the invention solves consists in increasing the conversion efficiency of the available wind potential (at speeds higher than the nominal speed of 10...12 m/s) into thermal energy and reducing the cost of energy.

The problem is solved by the fact that the wind turbine contains a tower, on which a rotor with blades with an aerodynamic profile is installed, located in a gondola, mounted with the possibility of rotating it around the tower by means of wind-wheels, coupled to a mechanism of drive, consisting of two worm gears, a converging annular diffuser, fixed to the blades coaxial with the rotor, and an energy conversion device. A thermal generator is used as an energy transformation device, mounted between the sections of the tower and kinematically linked with the rotor through a bevel gear. Blades with an aerodynamic profile possess a minimum coefficient of aerodynamic performance greater than 0.1 at air flow speeds greater than 10...12 m/s. The shape of the aerodynamic profile of the blades is executed so that its power characteristic P(V) correlates with the power characteristic of the heat generator, and the twisting angle of the aerodynamic profile in sections along the entire length of the blades is 1...3°. The diameter of the suction mouth of the diffuser d1=(0.1...0.12)D, where D is the outside diameter of the rotor, and the axial width of the diffuser l=a1+c+a2, where:

a1=(0.05...0.1)d1;

c is the maximum height of the blade section in the direction of the axis of rotation of the rotor, located at a distance equal to the radius of the diffuser suction mouth;

a2 = (0.1...0.15)d1.

The wind turbine with a high coefficient of performance provides the following advantages.

The wind turbine ensures the efficient conversion of the available wind potential at air current speeds between 10 and 20 m/s, thanks to the shape of the aerodynamic profile of the rotor blades, characterized by a minimum coefficient of performance greater than 0.1, and the power correlation mechanical ones developed with the eddy current thermal generator overload coefficient between 2 and 3, without reducing the area swept by the rotor blades, for example by rotating the rotor at some angle from 0 to 45° around the tower axis, or by varying the angle of attack of the blades, or by aerodynamic braking provided in the design of rotors with blades.

This, as well as the specifics of the construction of the blades with an angle of twisting of the aerodynamic profile in sections along the entire length of the blades of 1...3°, allow increasing the conversion efficiency of the available wind potential into useful energy, for example thermal. At the same time, equipping the rotor with the converging annular diffuser with the diameter of the suction mouth d1 = (0.1...0.12)D and the axial width l=a1+c+a2, located coaxially with the rotor, stops the flow of air currents in the longitudinal direction of blades, a fact that essentially reduces the separation of the boundary layer at the blade-fluid interaction (at high speeds V = 10...20 m/s) and, respectively, the negative influence of the turbulence in the area adjacent to the blades. Consequently, it increases the efficiency of converting wind energy into useful energy, increases the amount of energy produced annually and lowers its cost.

The invention is explained by the drawings in fig. 1-13, which represent:

- fig. 1, general view of the wind turbine with high aerodynamic performance coefficient;

- fig. 2, sectional view of the wind turbine;

- fig. 3, general view of the wind turbine with the axial section of the tower;

- fig. 4, the general view of the wind turbine with the location of the wind-wheels in the area downstream of the rotor;

- fig. 5, rotor with converging annular diffuser in section (a) and in 3D (b);

- fig. 6, the available power of the wind and the power obtained by the turbine;

- fig. 7, the performance coefficient as a function of the specific speed λ;

- fig. 8, the family of characteristics n depending on (λ, V∞ - parameter);

- fig. 9, the family of characteristics P (V∞, λ - parameter);

- fig. 10, the family of characteristics P (n, V∞ - parameter);

- fig. 11, the power characteristics P(V) of the turbine with different aerodynamic profiles;

- fig. 12, the Weibull distribution of the wind speed in the turbine location;

- fig. 13, the power characteristics P(V) of the eddy current thermal generator turbine and the electric generator turbine.

The wind turbine (fig. 1) contains a tower 8, on which is installed a rotor 1 with blades 2 with an aerodynamic profile, a nacelle consisting of bodies 3 and 4 assembled demountably, two wind rose wheels 5 mounted on an axis 6, located symmetrically on either side of the gondola. A converging annular diffuser 7 is attached to the blades 2 coaxial with the rotor 1. Between the sections of the tower 8, a thermal generator 9 with eddy currents is mounted.

The main shaft 10 (fig. 2) of the rotor 1 is installed in bearings in the nacelle body and is equipped at the end opposite the rotor 1 with a bevel gear 11. The nacelle body 4 is a spatial construction, which includes a bushing 12 with an axis that intersects perpendicularly with the common axis of the bodies 3 and 4 of the nacelle and a bushing 13 with the axis located perpendicular to the axis of the bushing 12. Inside the bushing 12 of the body 4 in the bearings is placed a hollow shaft 14, immovably fixed to the tower 8. On the hollow shaft 14, a worm wheel 15 is located, meshed with the worm of the shaft 16, on the end of which is mounted a worm wheel 17, meshed with the worm 18 of the common shaft 19 of the flywheels 5.

A shaft 20 is mounted in the inner cavity of the hollow shaft 14 in the bearings, on one end of which a bevel gear 21 is mounted, and on the opposite end a toothed coupling with an internal cylindrical gear 22 is mounted (fig. 3). The driving shaft of the thermal generator 9, by means of another toothed coupling, with internal cylindrical gear 23, of a torsion shaft 24 with the coupling 22, is kinematically linked with the shaft 20 (fig. 2), and by means of bevel gears 11 and 21 and of the main shaft 10 - with the rotor 1 of the wind turbine.

The wind turbine works in the following way.

At a wind speed greater than 2.5...3 m/s, the air currents, interacting with the blades 2 with an aerodynamic profile (fig. 3), drive the rotor 1 and the main shaft 10 (fig. 2) in a movement of rotation with the angular speed ωr, and by means of the bevel gears 11 and 21, of the shaft 20, the torsion shaft 24 with the toothed couplings with internal gear 22 and 23, the rotational movement and the torque are transmitted to the driving shaft of the thermal generator 9 with currents whirlwinds.

The wind turbine with blades with an aerodynamic profile, equipped with a convergent diffuser 7, fixed to the blades 2, stops the flow of the fluid in the longitudinal direction of the blades, which leads to the essential reduction of the separation of the boundary layer at the blade-fluid interaction and, respectively, to the efficiency converting the kinetic energy of air currents into useful energy at high wind speeds.

The orientation of the rotor 1 with blades 2 in the direction of the air currents is carried out by means of the wind-wheels 5, connected with the rotor by a kinematic chain.

If the wind direction is perpendicular to the swept surface of the rotor 1 with the blades 2, the wind-wheels 5 (fig. 4) having asymmetric profiles (mirror) do not rotate under the action of the air flow. The wind-wheels 5 start to rotate in one direction or another only if the wind direction (V1, V2) changes and forms some angle θ(t) with the axis of rotation of the rotor 1.

The blades of the wind-wheels 5 with an aerodynamic profile are placed so that when the wind direction changes (for example V1) under a certain angle θ(t), the aerodynamic forces developed by the blades impose on the wind-wheels 5 a rotational movement with the angular speed ωV1 in the direction of movement clock hands. The rotation movement from the wind-wheels 5, by means of the worm gears (fig. 2) with both left or both right-hand screws, is transmitted to the body 4 of the nacelle, which together with the rotor 1 (fig. 4) will rotate around the axis of the tower with the angular velocity ωg = ωV1/i1·i2 in the opposite direction of the clockwise movement. The rotation of the rotor 1 (counter-clockwise) around the axis of the tower will last until the plane of rotation of the wind-wheels 5 coincides with the direction of the wind V1, and the plane of rotation of the rotor 1 will be positioned perpendicular to the direction of the wind.

The vanes of the wind-wheels 5 are placed so that when the direction of the air flow V2 (fig. 4) is changed, the aerodynamic forces impose on the wind-wheels 5 a rotational movement in the opposite direction of the clockwise movement, and on the rotor 1 - a rotational movement around the axis of the tower clockwise, thus orienting it to the direction of the air flow V2 (or in the opposite direction in relation to the case of the direction of the air flow with V1).

According to the measurements during one year, it was found that wind gusts in a time period t of up to 10 s change their direction on extremes from 0° to 28° (for the speed at the rotor axis V = 25 m/s) .

In order for the wind vane wheels 5 to be positioned in the downstream area under the action of the air flow and to ensure the operative orientation of the wind turbine rotor to the direction of the wind, it is necessary that when the wind direction changes in a certain time interval the "wind vane" kinematic chain - worm-turn gears" to satisfy the following kinematic requirements:

1. The wind-wheels 5 to develop a frequency of revolutions nV, necessary to orient the rotor 1 with the blades 2 to the direction of the wind for up to 10 s with some inertia (delay), to exclude dynamic effects (caused by the change speed of the wind direction), according to the relationship:

, (1)

where: k - the coefficient to ensure the inertia of the turbine orientation to the direction of the wind (k > 1);

no - rotation frequency of the rotor with aerodynamic blades in the direction of the wind, min-1;

i1, i2 - transmission ratios of worm gears;

θ (t) - the angle between the extremes of change in the direction of the wind gust, angular degrees;

t - duration of change of wind gust direction, s.

2. The wind-wheels 5 to develop a torsion moment Tν, necessary to overcome the reactive moment Tr (at the tubular shaft 14, fig. 2, around which the gondola rotates), developed during the interaction of wind gusts with the rotating rotor, determined from the relationship:

(2)

where: Tr - the reactive moment (at the tubular shaft 14, fig. 2, around which the gondola rotates), developed during the interaction of wind gusts with the rotating rotor;

i1, i2 - transmission ratios of worm gears;

ηΣ - the summary mechanical efficiency of the kinematic chain (worm gears, pairs of bearings).

According to research, when the fluid interacts with the airfoil blade, the fluid, interacting with the hub of the rotor 1, flows in the longitudinal direction of the blades 2 depending on the speed of the fluid. The flow in this area is characterized by turbulence and the appearance of eddies favoring the separation of the boundary layer, phenomena that negatively influence the efficiency of its kinetic energy conversion. The negative influence of these phenomena amplifies with the increase of the fluid speed. To reduce the negative influence of these effects on the conversion efficiency, the rotor 1 (fig. 5) is equipped with the converging annular diffuser 7.

The purpose of the invention is to increase the energy conversion efficiency by increasing the amount of useful energy obtained from the available wind potential, determined by the formula:

Pw = 0.5ρAV3, (3)

where: ρ is the air density, kg/m3;

A - the surface swept by the rotor blades, m2;

V - wind speed, m/s.

The power obtained from the available wind potential of an ideal wind turbine is limited by the Betz limit and depends on the coefficient of performance Cp of the airfoil rotor. In fig. 6 shows the power obtained by an ideal wind turbine, estimated according to the formula P = 0.5Cp ρAV3, from the available wind potential calculated at different wind speeds according to formula (3).

To argue the achievement of the purpose of the invention through the proposed technical solutions, we analyze the power characteristics P(V) of an aerodynamic rotor with a diameter of 8 m.

To this end:

1. We perform the comparative analysis for two sets of blades with two airfoils with different performance coefficients Cp(λ), where λ is the specific speed determined by the formula

(4)

where: ω is the angular speed of rotation of the rotor, s -1;

R - rotor radius, m;

V - wind speed, m/s.

The numerical values Cp(λ) of the compared aerodynamic profiles are shown in table 1, and the graphic interpretation - in fig. 7.

Table 1

λ 2 4 6 8 10 12 14 16 18 Cp Profile 1 0.050 0.180 0.340 0.350 0.345 0.32 0.275 0.212 0.125 Profile 2 0.050 0.180 0.340 0.350 0.325 0.28 0 .215 0.140 0.050

2. According to the definition in the specialized literature, the characteristic Cp(λ) is described as the variation of the mechanical power developed by the turbine depending on the speed of rotation of the aerodynamic rotor, provided that the wind speed is constant. Considering that ω = πn/30, from (4) we obtain the rotation speed n:

. (5)

3. From formula (5) we calculate the family of characteristics n = F(λ, V) (for airfoil 1), in which the wind speed is considered as a parameter, with the presentation of the results in fig. 8.

4. For the same values of the specific speed λ from fig. 7 and with the formula P = 0.5Cp(λ)ρπR2V3 we calculate the mechanical power depending on the wind speed, the specific speed λ and the performance coefficient Cp, which is considered a parameter. The results are presented in fig. 9.

5. For different constant wind speeds V and the range of variation of the specific speed λ from fig. 8 we determine the corresponding values of the rotation speed n, and from fig. 9 - the mechanical power P, thus we obtain the family of characteristics P(n, V), shown in fig. 10.

6. Based on the data obtained from the functions presented in fig. 10 and fig. 8 we construct the power characteristic P(V) for profile 1, shown in fig. 11. For example: for V = 4 m/s and λ = 4 from fig. 8 we get n = 38.2 rev/min. From fig. 10, for V = 4 m/s and n = 38.2 rev/min we obtain P = 0.35 kW. Analogously: for V = 8 m/s and λ = 8 from fig. 8 we get n = 153 rev/min. From fig. 10, for V = 8 m/s and n = 153 rev/min we obtain P = 5.53 kW and so on. Analogously, the power characteristic P(V) is determined for profile 2, shown in fig. 11 with dashed line.

In fig. 11, the surface between the two curves represents the additional mechanical power obtained from the wind potential with blades with aerodynamic profile 1 with increased performance coefficient, shown in fig. 7.

Increasing the obtained energy and, respectively, the conversion efficiency is achieved by reducing the twisting angle of the aerodynamic profiles within the limits of φ = (1...3)° (fig. 4) in relation to the plane of rotation of the rotor blades. The obtained mechanical energy is converted into useful energy, for example thermal, with the help of the eddy current thermal generator, which has an overload coefficient between 2 and 3. The technical-economic effect of the implementation of the invention is presented by calculating the thermal energy, which can be produced during a year:

1. Under the same wind conditions, using wind turbine with airfoil 1 and an eddy current heat generator compared to wind turbine with airfoil 2.

2. Under the same wind conditions, using wind turbine with airfoil 1 and an eddy current thermal generator compared to the energy produced using wind turbine with airfoil 2 and an electric generator.

For the calculation of the annual thermal energy production, the following initial data are required: the power characteristics of the wind turbine P(V) with different profiles, fig. 11 and the Weibull distribution of the wind speed, measured in the respective locality over a period of 12 months, fig. 12.

The difference between the P(V) characteristics occurs for wind speeds higher than the nominal speed, in the given case, higher than 10 m/s. The Weibull distribution of the wind speed was obtained as a result of the data processing, obtained over a period of 12 months and presents the probability density function of the wind speed over the entire period of measurements. From fig. 11 and 12 show that the range of profitable wind speeds is between 3 and 18 m/s. This range of speeds is divided into intervals, for example equal to 1 m/s, and for each interval the weight (probability density function) of the respective speed is determined for the entire measurement period, in our case - 8760 hours. For example, the speed weight of 8 m/s is equal to 0.118 or 0.118x8760=1033.7 h/year.

Table 2

Numerical values of the wind speed probability density function, F(V), for 12 months

Wind speed, m/s 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 Function, F(V) 0.065 0.098 0.117 0.128 0.128 0.118 0.095 0.070 0.045 0.028 0.016 0 .012 0.007 0.005 0.003 0.00

For both profiles, the amount of thermal energy that could be produced over a period of one year under identical wind conditions was calculated. Formulas for calculating thermal energy production

for profile 1 and

for profile 2, where the P1(V) values correspond to the characteristic of profile 1, and P2(V) - to profile 2 from fig. 11. Thus, the wind turbine with airfoil 1 will produce 9.4% more energy.

In the case of electricity production, the P2(V) characteristic differs from that shown in fig. 11. The overload coefficient of the electric generator is 1.2...1.3. For wind speeds higher than the nominal one, measures must be taken to limit the power developed by the turbine. The turbine rotor is moved out of the wind direction or the angle of attack of the blade is changed. As an example, in fig. 13 shows the power coefficient of the turbine with aerodynamic profile 2 with a power of 10 kW and equipped with an electric generator (the characteristic is provided by the manufacturer).

For comparison, we present the power characteristic of the turbine with airfoil 1 and equipped with an eddy current heat generator, which has an overload coefficient higher than 2. We find that for wind speeds higher than 10 m/s (nominal speed) to limit the power by turning the rotor away from the wind. Power is limited to 12.5 kW (the overload factor is equal to 25%). If the wind speed continues to increase and exceeds 16 m/s, the rotor plane will be parallel to the wind speed vector and the developed power will be zero. Thus, electrical and mechanical overloads of the electrical generator are excluded.

In the case of using profile 1 and the eddy current thermal generator, it is not necessary to limit the power, because the latter has an overload coefficient between 2 and 3. The rotor plane is maintained perpendicular to the wind speed vector. As the wind speed increases, the power developed by the turbine will also increase and, for the profile in question, the power will reach the maximum value equal to 26 kW, then it will decrease due to aerodynamic braking.

With the help of the characteristics in fig. 13 and the formulas above, the quantities of thermal and electrical energy, which could be produced over the period of one year, were calculated:

Thermal energy ETP1 = 45814.8 kWh or 164.9 GJ,

Electric energy EEP2 = 38351.3 kWh or 138.1 GJ.

In the case of using the turbine with aerodynamic profile 1 and the thermal generator with eddy currents, the amount of energy is 19.4% higher than in the case of using the turbine with aerodynamic profile 2 and the electric generator.

So, a wind turbine with an aerodynamic profile with a high coefficient of aerodynamic performance Cp(λ) (realized by the technical solutions proposed in the invention), intended to transform the available energy of the wind potential into thermal energy produced by an eddy current thermal generator, compared to a wind turbine with an electric generator and an aerodynamic profile compatible with it for reasons of limiting the developed power, generates useful energy for the period of one year with 7463 kWh and, respectively, with 26.8 GJ more.

At the same time, in the wind turbine, according to the invention, the electronic system for orienting the tripartite rotor to the variable direction of the air flow is replaced by a mechanical system equipped with aerodynamic wind-wheels. This solution leads to the reduction of the production cost by (25...30)% and ensures the increase of reliability in operation. It should also be mentioned that the thermal generator with eddy currents, compared to the electric generator, is constructively simpler, the production cost is lower, and the reliability increases due to the overload coefficient equal to 2...3 (1,2...1, 3 - for the electric generator).

1. US 4366779 A 1983.01.04

2. MD 4213 B1 2013.03.31

Claims (1)

Wind turbine, which contains a tower (8), on which is installed a rotor (1) with blades (2) with an aerodynamic profile, located in a nacelle, mounted with the possibility of rotating it around the tower (8) by means of wheels -windrose (5), coupled to an actuation mechanism, consisting of two worm gears, a converging annular diffuser (7), fixed to blades (2) coaxial with the rotor (1), and an energy conversion device, characterized in that a thermal generator (9) is used as an energy conversion device, mounted between the sections of the tower (8) and kinematically linked with the rotor (1) through a bevel gear (11) and (21); the blades (2) with an aerodynamic profile have a minimum coefficient of aerodynamic performance greater than 0.1 at air flow speeds greater than 10...12 m/s, at the same time the shape of the aerodynamic profile of the blades (2) is executed so that its characteristic of power correlates with the power characteristic of the thermal generator (9), and the twist angle of the aerodynamic profile in sections along the entire length of the blades (2) is 1...3°; the diameter of the suction mouth of the diffuser (7) is d1=(0.1...0.12)D, where D is the outer diameter of the rotor (1), and the axial width of the diffuser (7) is equal to l=a1+c +a2, where: a1=(0.05...0.1)d1; c is the maximum height of the blade section in the direction of the axis of rotation of the rotor (1), located at a distance equal to the radius of the suction mouth of the diffuser (7); a2 = (0.1...0.15)d1.