RU2103545C1 - Wind-electric power plant (options) - Google Patents

Abstract

FIELD: windmills for driving electric generators, propellers of water transport, etc. SUBSTANCE: air stream used by windmill is shaped by force in wind tunnel so that speed of air stream running on propeller in narrow section of tunnel increases many times compared to its speed at inlet of wind tunnel. For obtaining maximal possible power from air stream, inlet and outlet sectional areas of wind tunnel should be equal and definite geometric relation should be maintained between diameters of air and water propellers. EFFECT: improved power taken off air stream. 10 cl, 2 dwg

Description

 The invention relates to wind engines for driving electric generators, propellers of water propellers of water vehicles, wind-driven water pumps for driving water pumps and other purposes.

 Known wind turbines with a freely rotating propeller or wind wheel (hereinafter referred to as "propeller" or simply "screw"), which are used as windmills, wind power plants, or to drive water pumps, etc.

The greatest power that a freely rotating screw can take from the power of the incoming flow in the jet formed by the screw will be when the flow rate decreases in front of the screw by 1/3 and behind the screw by another 1/3. The maximum power T _max and the stop force of the screw F corresponding to this power according to (1) will be equal to:
T _max = ρ • f • v ³ • 8/27 F = ρ • f • v ² • 4/9. ,
Here:
ρ = 0.125 kg (s) • c ² / m ⁴ - average air density at ground level;
fm ² is the value of the cross-sectional area swept by the screw;
V m / s is the speed of the incoming flow outside the zone of influence of the screw on the flow.

As you know, the total power flow T _p bounded by a cylinder with a cross-sectional area f will be equal to:
T = m • V ^2/2 = ρ • f • v ^3/2. .

Here:
m = ρ • f • v, is the second mass of air passing through section f. Therefore, the maximum possible power from the total power T _p is the value of T _max / T _p = 16/27 = 0.5928. This is the so-called the “ideal” maximum possible screw power with an efficiency of n = 1, when additional energy losses occurring at the jet boundary in the area of the screw’s active influence on the jet due to the unrestricted flow of high pressure air in front of the screw into the low pressure zone behind the screw, without plane of rotation of the screw. If we evaluate, taking into account the marked efficiency of the screw, n≤ => 0.7, then the real maximum possible mechanical power T _m , removed from the screw from the full power flow T _p will be already the value:
T _m / T _p = T _maxp / T _p ≤0.7 • 16/27 = 0.415
Thus, a freely rotating screw can convert into mechanical energy less than half the energy enclosed in the stream stream section f. Therefore, obtaining the required mechanical power in such wind turbines is achieved by increasing the area f swept by the screw, i.e. increasing the diameter of the screw to 30 m or more and lifting the screw to a considerable height of 60 m or more, where the speed of the incoming flow is slightly higher than that of the earth.

 An increase in the diameter of the propeller leads to a disproportionately large increase in its mass, complication and increase in the cost of manufacturing and installation of the propeller and the wind turbine as a whole, and a substantial increase in operating costs.

 Known wind turbines with the forced formation of the air flowing onto the screw, which is achieved by restricting the flow of the pipe and placing the screw inside the pipe.

The closest analogue of the wind turbine of the proposed wind power installation is a wind power installation (2), containing a propeller installed in the smallest section of a horizontal wind tunnel with open and equal in and exit sections, an orientation device for the direction of the wind and other auxiliary devices. An electric generator was used as the propeller load, the rotor of which is connected to the propeller shaft through a multiplier. The diameter of the propeller of the installation is d = 2.8 m, the area swept by the screw is f ₁ = 6.17 m ² . The value of the input section area f ₀ = 16 m ² . The ratio of the areas Δ ₁ = f ₀ / f ₁ , which can be determined as the concentration coefficient of the power density of the wind energy of a wind power installation, will be equal to:
Δ ₁ = f ₀ / f ₁ = 16 / 6.17 = 2.6,,
It is known to place such a wind power installation on a toroidal tethered balloon, the inner surface of the torus of which forms a wind tunnel and in a water vehicle, with mechanical transmission of propeller power to the propeller.

 The closest analogue of the proposed wind power installation of a waterborne vehicle is a known device (3), the wind turbine of which with a propeller in a cylindrical tube operates on a propeller-propeller of a watercraft-yacht.

 A disadvantage of the known device is the need to use a large-diameter wind turbine propeller and the use of a pipe practically only as a guard for a rotating propeller.

 The closest analogue of the proposed wind power installation placed on a tethered toroidal balloon is the known device (4). The known device is a tethered toroidal balloon filled with light gas, the inner surface of the torus of which forms a wind tunnel with open inlet and outlet sections normal to the axis of the tube, in the smallest circular section of which is placed a wind turbine propeller with a generator. The input section of the pipe is less than the area of its output section, which is a disadvantage of the known device, because it leads to underutilization of all the cross-sectional area of the pipe to increase the power of the wind turbine.

 All these known devices form a flow running on the propeller, and devices (2) and (4) also concentrate wind energy from a larger inlet section into a smaller area swept by the screw.

In addition to the aforementioned, a common drawback of these and other known similar devices is the small value of the concentration coefficient of the wind power flux density per area swept by the screw Δ ₁ , which does not allow positive quantitative changes in the quality to overgrow. For example, an increase in the frequency of rotation of the propeller, as a result of the concentration of wind energy on the propeller, does not reach values at which it is possible to refuse to use the multiplier, if it is necessary to use relatively high-speed electric generators, etc. There is no energy concentration in the device according to (3), because the size of the inlet pipe section and the area swept by the screw are the same. In addition, for all these and other similar devices, the conditions for obtaining and the maximum possible power taken by the propeller from the incoming wind flow are not defined, and therefore, the means for maintaining the propeller load at the maximum possible power are not specified, i.e. no adaptation of the load to the maximum possible propeller power.

 All this not only reduces the efficiency of using wind energy, but, in some cases, does not allow to obtain a possible positive result. For example, in the device according to (3), the noted deficiencies will not allow the watercraft-windmill to travel directly against the wind, which means that a vessel with such a wind turbine will not have any fundamental advantages over a purely sailing vessel. This explains the fact that the idea of replacing the sail with a wind turbine operating on a water propeller of a windmill has not yet been realized, although the future in the use of wind energy in water transport vessels is, of course, behind a wind turbine with a propeller in a wind tunnel running on a water propeller .

 The objective of the invention is to increase to the maximum possible level of operational efficiency and the possibility of using wind power plants, reduce the cost of manufacturing, installation and operation by simplifying the design6 reduce metal and material consumption, reduce construction height.

 The invention is illustrated figure 1-2.

 Oriented in the direction of the external flow, opening on both sides of the wind tunnel 1 (Fig. 1) has a smoothly varying length, without jumps and kinks, the inner channel, in the smallest circular section of which is placed an air screw 2. The inlet and outlet of the pipe can have any not necessarily round sectional shape. The propeller shaft is connected either to the shaft of the electric generator 3 directly or through a reducer 4, when using a wind power installation as a wind power, or through two angular gears 5 and 6 with a shaft of a propeller-7 propeller, when using the proposed installation as a wind power water vehicle-wind-driven, or only through one angular gear 5 for driving a water screw-pump 8.

 Instead of a mechanical transmission to the propeller of the propulsor or pump, an electric transmission can be used - the so-called "synchronous electric shaft".

In the pipe, four sections are distinguished:
0 - input;
1 _I - closest to the plane of rotation of the screw from the input side;
1 _II - closest to the plane of rotation of the screw from the output side;
2 - day off.

,
Сопротивление-упор трубы с винтом в целом будет равен:

,
Здесь:
f₀, f₂ - величина площади сечения на входе и выходе трубы.A loaded rotary screw creates resistance to the movement of the air flow inside the pipe so that at the entrance to the pipe in section 0 the flow velocity V _{0 is} always less than the flow velocity V outside the pipe, and the total air pressure p _{0 is} always greater than the static pressure p outside the pipe due to dynamic increase pressure of partially inhibited air flow in the pipe. At the outlet of the pipe in section 2, the flow rate in the pipe is V ₂ <V, and the total pressure is p ₂ <p, because an external stream moving at a higher speed in the same direction at the outlet creates additional rarefaction. Based on the foregoing, we will have full pressure in the section

,
The resistance-stop of the pipe with the screw as a whole will be equal to:

,
Here:
f ₀ , f ₂ - the value of the cross-sectional area at the inlet and outlet of the pipe.

,
Разность давлений p_1′-p_1″ , в сечениях 1_I - 1_II (скачек давления на винте) составит:
Δp₁= p_1′-p_1″= p₀-p₂+ρ•(v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ )=ρ(v²-v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ ) ,
Полное давление на обметаемую винтом площадь f₁, -сопротивление-упор P₁ собственно винта:
P₁= Δp_1′•f₁= ρ•f₁•(v²-v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ ) = ρ•f•(v²-v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ ) , Мощность на винте N будет равна:

,
Выражение для N имеет максимум при V₀=V/

, или v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ , =V²/3. Величина максимально возможной мощности на винте N_max, сила упора собственного винта P₁ и упор установки в целом P при этом будут равны:

,
Для концентрации плотности мощности потока на винте, величина f₁, ометаемой винтом площади в трубе должна быть в несколько раз меньше площади сечения трубы на входе: f₀=f₂ Δ₁•f₁ ,
Здесь:
Δ₁ = f₀/f₁= 4-9 и более, -коэффициент концентрации плотности мощности ветроустановки.The stop force at f ₀ = f ₂ , and taking into account the continuity condition (V ₀ • f ₀ = V ₂ • f ₂ ) and at V ₀ = V ₂ , will be equal to:
P = ρf ₀ (v ² -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ ) = ρ • f ₂ • (v ² -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ ),
Bernoulli equation for sections:

,
The pressure difference p _{1 ′} -p _{1 ″} , in sections 1 _I - 1 _II (pressure jump on the screw) will be:
Δp ₁ = p _{1 ′} -p _{1 ″} = p ₀ -p ₂ + ρ • (v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ ) = ρ (v ² -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ ),
The total pressure on the area f ₁ swept by the screw, is the resistance-stop P _{1 of} the screw itself:
P ₁ = Δp _{1 ′} • f ₁ = ρ • f ₁ • (v ² -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ ) = ρ • f • (v ² -v $\genfrac{}{}{0ex}{}{\text{2}}{\text{2}}$ ), Power on the screw N will be equal to:

,
The expression for N has a maximum at V ₀ = V /

, or v $\genfrac{}{}{0ex}{}{\text{2}}{\text{0}}$ , = V ^2/3. The value of the maximum possible power on the screw N _max , the stop force of the own screw P ₁ and the emphasis of the installation as a whole P will be equal to:

,
For concentration of the power density of the flow on the screw, the value of f ₁ swept by the screw of the area in the pipe should be several times smaller than the cross-sectional area of the pipe at the inlet: f ₀ = f ₂ Δ ₁ • f ₁ ,
Here:
Δ ₁ = f ₀ / f ₁ = 4-9 or more, is the concentration coefficient of the power density of the wind turbine.

,
И для Δ₁ =4-9 и более: N_max/T_max=(5,2-11,7) и более.Comparing N _max on the screw in the pipe with T _max free screw according to (1) we get:

,
And for Δ ₁ = 4-9 or more: N _max / T _max = (5.2-11.7) or more.

If we take the area f swept by a free screw equal to f = f ₀ = f ₂ = Δ ₁ • f ₁ , then in this case, N _max will be 1.299 times greater than T ^max .

If we go to the real mechanical power that can be removed from the screw and take into account a significant increase in the efficiency of the screw in the pipe, the value of which can be taken n ₁ ≥0.85, and for the free screw n≤0.7, then the ratio of real mechanical powers in this case will be: N _m / T _m = N _max • n ₁ / T _maxn ≥ 1.299 • 0.85 / 0.7 = 1.58. Since the task of providing T _max for a freely rotating screw is still unsolved, the practical gain in the mechanical power of the proposed installation will be even more significant.

,
для свободного винта:
δ_т= F/T_max= (4ρf•v²/9)/(8•ρ•f•v³/27) = 3/2•v, .About some other, practical, important indicators of the proposed wind power installation, compared with the installation with a free screw:
Axial emphasis per unit of power:
For screw in pipe

,
for free screw:
δ _{t = F / T max = (4ρf} • v ^2/9) / (8 • ρ • f • v ^3/27) = ^3/2 • v,.

.Axial thrust ratio: for the same power:

.

And for Δ ₁ = 4-9 or more δ = (0.289-0.128) or less,
The power on the screw N according to (1) is proportional to (≡) the product of the diameter d to the fifth power and the cube of the screw speed n N ≡ d ⁵ n ³ ,
For the screw in the pipe N ₁ = d $\genfrac{}{}{0ex}{}{\text{5}}{\text{1}}$ • n $\genfrac{}{}{0ex}{}{\text{3}}{\text{1}}$ = f $\genfrac{}{}{0ex}{}{\text{5/2}}{\text{one'}}$ n ³ ,.

.For a free screw: T = d ⁵ • n ³ = f ^5/2 • n ³
Power Ratio:

.

From here:
The ratio of rotational speeds n ₁ / n = (1,299 ^1/8 • Δ $\genfrac{}{}{0ex}{}{\text{5/2}}{\text{1}}$ ) = 1,091 • Δ $\genfrac{}{}{0ex}{}{\text{5/6}}{\text{1}}$ .

And for Δ ₁ = 4-9 or more, n ₁ / n = (3.48-6.81) or more.

All other, practically significant performance indicators of the proposed wind turbine depend on the value of the power density concentration coefficient
Δ ₁ = f _0/1. So compared with the performance of a wind turbine with a free screw, when changing the value of the coefficient of concentration of power density Δ ₁ = f ₀ / f ₁ = 4-9 or more, similar indicators of the proposed wind turbine change:
- screw mass - up to 0.289-0.128 or less;
- gyroscopic moment - up to 0.018-0.0128 or less;
- internal stresses in the screw material - 3-5.15 times or more;
- centrifugal force of unbalanced screw mass - up to 0.187-0.064 or less;
- the greatest deflection of the end of the blade - up to 0.866-0.578 or less;
- the critical rotational speed of the screw shaft is 2-3 times or more.

Some conclusions from comparative indicators of the operation of a wind turbine with a screw in the pipe and with a freely rotating screw, the swept area of which is equal to the area of the pipe inlet section:
- reducing axial emphasis facilitates the working conditions of the support node, simplifies its design and reduces cost;
- increasing the speed will allow in most cases to abandon the multipliers that increase the rotational speed of the screw to the required, which greatly simplifies and reduces the cost of manufacturing and operation of the wind turbine. In addition, a several-fold increase in the rotational speed reduces the amount of drive torque developed by the rotor by the same amount;
- reducing the mass of the screw further reduces the cost of its manufacture and operation;
- a decrease in the gyroscopic moment provides a proportional decrease in the load of the mechanism of rotation of the plane of rotation of the screw when changing the direction of the wind;
- an increase in internal stresses is the only considered parameter for a screw in a pipe worse than a free screw. However, the internal stresses of the material of the propeller of the wind turbine are an order of magnitude lower than the internal stresses of the material of the propeller when it is operated on an aircraft, so the indicated increase in internal stresses does not exceed the permissible level. In addition, there are several ways to reduce the internal stresses that occur during operation of the screw.

The remaining indicators indicate a significant relief of the vibration mode that occurs when the wind turbine:
- a decrease in the centrifugal force of a statically unbalanced mass reduces the level of vibration;
- reducing the deflection of the end of the blade while reducing its mass and size reduces the additional dynamic imbalance of the rotating screw;
- an increase in the rotational speed increases the frequency of the resulting vibrations to a greater extent than the critical rotational speed of the rotor shaft increases.

 All this facilitates the creation of highly effective vibration isolation and makes possible the mastless use of the proposed wind turbine on the roofs of individual buildings and structures, not only industrial but also domestic.

The ratio of the rotational speeds of the propeller p ₁ and load p _n

 For a wind turbine with an electric generator.

The best option: n ₁ = n _n - allows direct connection of the propeller shaft and the rotor of the generator.

Acceptable option: n ₁ > n _n - requires a gearbox that reduces the rotational speed of the screw.

The worst case scenario is n ₁ <n _n - it requires a multiplier that increases the rotational speed of the screw.

For a wind turbine with a load on the propeller or water pump:
In this case, in principle, a transmission cannot be dispensed with. As the best option for mechanical transmission, n ₁ ≥n _n
The power given by the water screw to the water flow will be equal to N _in = N ₁ • η _in • η ₁ , or N _in / N ₁ = η _in • η ₁ .

Here:
p ₁ and p _in - the efficiency of the propeller and propeller, including energy loss in the transmission elements.

Since the power of any screw is N = ρ • d ⁵ • n ³ , then:
N _in / N ₁ = ρ _in • d $\genfrac{}{}{0ex}{}{\text{5}}{\text{in}}$ • n $\genfrac{}{}{0ex}{}{\text{3}}{\text{in}}$ / ρ • d $\genfrac{}{}{0ex}{}{\text{5}}{\text{1}}$ n $\genfrac{}{}{0ex}{}{\text{3}}{\text{1}}$ = η ₁ • η _century From here
d _in = d ₁ [η ₁ • η _in • (ρ / ρ _in )] ^0.2 (n ₁ / n _in ) ^0.6 .

Since n ₁ / n _in = i is the gear ratio of transmission from air to propeller. Therefore, we will finally have the value of the diameter d _in - of the propeller, adapted to the maximum possible power of the propeller:
d _in = d ₁ • [η ₁ • η _in (ρ / ρ _in )] ^0.2 • i ^0.6 .

.The largest value of the diameter of the propeller will be at the largest value (η ₁ • η _in ) _max , which will be with a mechanical transmission to drive the propeller. For single-stage bevel gears from the propeller shaft to the transmission shaft and from the transmission shaft to the propeller shaft with an efficiency of each 0.98 and an upper value of the propeller and propeller efficiency of 0.85, the value (П ₁ • П _в ) $\genfrac{}{}{0ex}{}{\text{0.2}}{\text{max}}$ = (0.98 • 0.85 • 0.98 • 0.85) ^0.2 = 0.93. Given the value of ρ _in = 102 kg (s) with ² / m ⁴ and p = 0,125 kg (s) with ² / m ^{4 the} upper diameter value of the adapted propeller will be equal to:
d _max = d ₁ • 0.93 • (0.125 / 102) ^0.2 i ^0.6 = 0.243 • d ₁ • i ^0.6
The lower diameter of the adapted propeller will be lower when using an electric transmission that gives the smallest value (η ₁ • η _c ) _min . If we take the smallest efficiency of the electric generator and electric motor of such a transmission as 0.8 and the smallest value of the efficiency of the propeller and propeller, as 0.75, then the lower diameter of the adapted screw will be equal to:
d _min = d ₁ • (0.8 • 0.75 • 0.8 • 0.75) ^0.2 •• (0.125 / 102) ^0.2 • i ^0.6 = 0.213 • d ¹ • i ^{0, 6} /
Thus, the diameter of the propeller load, adapted to the maximum possible power of the propeller, in any modes of its operation should be within:
d _in = (0.213-0.243) • d ₁ • i ^0.6
When the freely rotating water screw operates in place, its thrust-thrust according to (1) will be equal to: P _in = 2 • m • v = 2 2 • ρ _in • f _in • v ² , and the power transmitted by the water screw to the flow
N _a = N _{1 'η 1} • η _in = m • v ^2/2 = ρ _a • f • v _in ^3/2. Hence v = (2 • N ₁ • η ₁ • η _in / ρ _in • f _in ) ^1/3 and the propeller thrust in this case will be equal to: P _in = 2 • ρ _in • f _in • v ² = 2 • ρ _in f _in • (2N • η ₁ • η _in / ρ _in • f _c ) ^1/3 . Given that the resistance-emphasis wind turbine as a whole is equal to P = 2 • p • f • V ₀ ^2/3, then the relative magnitude of water abutment screw will be:

.

But: f _in / f ₀ = (f _in / f ₁ ) / (f ₁ / f ₀ ) = = (f ₀ / f ₁ ) / Δ ₁ , and f _in / f ₁ = (d _in / d ₁ ) ² = (0.243 •• i ^0.6 ) ² . And, for example, for i = 1 (f _in / f ₁ ) -0.243 ² = 0.059 and f _in / f ₀ = (f _in / f ₁ ) / Δ ₁ = 0.059 / Δ ₁ , therefore:
P _in / P = 18.46 • (f _in / f ₀ ) ^1/3 = 18.46 0.059 ^1/3 / Δ $\genfrac{}{}{0ex}{}{\text{1/3}}{\text{1}}$ = 7.19 • Δ $\genfrac{}{}{0ex}{}{\text{-1/3}}{\text{1}}$ . And for Δ ₁ = 4-9 P _in / P = 4,53-3,45. The thrust of the propeller when it is in place is several times higher than the resistance-stop of the wind turbine itself, which shows the possibility of the movement of such a windbreaker vessel directly against the wind.

 The operation of the water screw in the nozzle, especially with a variable output section, can increase this ratio by a factor of 2 or more.

 Calculations showed that such a windbreaker can move at any rate with respect to the true direction of the wind with almost the same speed, which is approximately 0.34-0.38 of the absolute wind speed.

 It can therefore be argued that the use of a wind turbine in a wind tunnel instead of sails on a water vehicle-wind turbine with a high concentration of wind flow power density on a propeller operating in the maximum possible propeller power mode will allow the vessel to move not only in sharp wind directions the courses - a “cool bedevindt”, but also directly against the wind - with the “leventik” course, which is fundamentally inaccessible to any purely sailing vessel, and in many cases the speed against the wind is th vessel will be the largest. In addition, a calculated comparison of the efficiency of creating thrust by sails or a water screw operating from such a wind turbine showed that with a relative size of the input section of the wind turbine pipe, which is only 0.125 part of the area of all sails of a purely sailing vessel at all courses, except for “backstop”, propeller thrust exceeds the total thrust of all sails. On the course “bakstag” the same value of propeller thrust with sails provides the area of the inlet section of the wind turbine pipe equal to 0.19-0.3 of the total area of the sails.

 Setting up and controlling the sails of a sailing vessel requires a lot of knowledge, skill and physical strength, often fraught with inconvenience, especially in inclement weather, so even experienced sailors do not use all the opportunities provided by the wind.

 The control of a ship-sailing ship with the proposed wind power installation is reduced to orienting the wind turbine in the direction of the so-called pennant wind, i.e. in the direction of the wind relative to the vessel, which is equivalent to orienting the fixed installation to the true direction of the wind and maintaining the flow velocity at the inlet or outlet of the pipe at 1/3 of the value of the wind pressure outside the pipe, which, as was shown, is automatically ensured by the use of a water screw adapted to the maximum possible power of the propeller, the diameter of which must correspond to the above ratio.

 As a special case of application, it is provided to use a variable pitch propeller (VIS) without limiting its diameter, as well as its operation in nozzles with an unregulated and adjustable output section.

 The use of the proposed wind power installation as an electric power supply for power supply of electric networks, for ensuring the propeller operation in the maximum possible power mode, will require regulation of the power given by the generator according to the regime of preservation of the high-pressure head of the flow at the inlet to the pipe at 1/3 of the high-speed wind pressure outside the pipe, i.e., it will require a device for adapting the load to the maximum possible propeller power.

 The proposed wind power installation, placed on a balloon (Fig. 2), contains a tethered toroidal balloon lighter than air 1, the inner surface of the torus of which forms a wind tunnel 2, forming an air flow. In the smallest circular section of the pipe there is an air screw 3 and a rotor of the generator 5 connected directly to it or via a gearbox 4. The aerostat is connected via a cable 6 to a cable 7 and an electric cable 8 to service systems located on the ground or floating vessel. The balloon is filled with light gas with some overpressure, which ensures the stability of the balloon shape under dynamic wind effects. The leash system always orientates the axis of the aerostat in the wind with the front section of the entrance section.

 As a special case of application in versions of wind power plants, it is planned to use an asynchronous generator and a synchronous compensator with starting, regulating and protective equipment according to (5) during autonomous operation of a wind power installation or only one asynchronous generator when the unit is operating on a centralized power supply system.

 As a special case of application, it is envisaged to use a variable pitch propeller and use a jet-slotted blade in the propeller according to (6).

 Sources of information.

 1. Yuryev B.N. Propellers. Gosmashmetizdat, 1933, Moscow.

 2. EPO application N 0045202 F 03 D 1/04, 1982.

 3. EPO application N 0045202 F 03 D 1/04, 1982.

 4. FR application N 2092851 B 63 H 13/00, 1972.

 5. Application N 93-053617 / 07 (053494). The decision on the grant of patent 02 2 HOUSE 10.11.95 077519. Patent RU (11) 2073310 (13) C1 6 H 02 P 9/42, 1997.

 6. Application N 93050451/11 (050571). The decision on the grant of a patent 01 2 HOUSE 01.01.96. 11 26 02.

Claims (10)

1. A wind power installation comprising a rotary tube mounted on a water vehicle with an open inlet and outlet section, inside of which there is a propeller with power transmission to the propeller, characterized in that the rotary tube is made in the form of a Venturi wind tunnel, the inlet and outlet section of which equally, the propeller is mounted in a narrow section of the venturi, and the diameter of the propeller is determined from the following relationship:
d _in (0.213 0.243) • d • i ^0.6 ,
where i is the gear ratio from the propeller to the propeller;
d propeller diameter.  2. Installation according to claim 1, characterized in that the water screw is made with a variable pitch.  3. Installation according to claims 1 and 2, characterized in that the water screw is equipped with a nozzle.  4. Installation according to claims 1 to 3, characterized in that the nozzle is made with a variable output section.  5. Wind power installation containing a horizontally mounted wind tunnel with a confuser-diffuser channel, a propeller located in the smallest section of the channel, a device for orienting the axis of the pipe in the direction of wind speed, characterized in that the area of the inlet section of the pipe is equal to the area of the outlet section of the pipe, and the frequency the rotation of the rotor of the generator is 0.5 1 of the rotational speed of the propeller.  6. A wind power installation containing a wind tunnel mounted on a tethered balloon with open inlet and outlet sections normal to the axis of the tube, in the smallest circular section of which there is a propeller with a generator connected to ground systems, and the wind tunnel is formed by the inner surface of the toroidal balloon, different the fact that the area of the inlet section of the pipe is equal to the area of the outlet section, and the rotational speed of the rotor of the generator is 0.5 1 rotational speed of the propeller.  7. Installation according to PP.5 and 6, characterized in that the electric generator is made asynchronous.  8. Installation according to PP.5 to 7, characterized in that the installation contains a synchronous compensator, trigger synchronizing regulatory and protective equipment.  9. Installation according to claims 5 and 6, characterized in that the propeller is made with a variable pitch.  10. Installation according to PP.5, 6 and 9, characterized in that the propeller blade is made jet.

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