BG110070A - Wind energy converter - Google Patents

Abstract

The device is used for wind energy conversion. It consists of a base (1) in which a vertical rotor (2) rests with symmetrically and evenly arranged radial arms (3). Each of the ends of the arms is supplied with a vertical shaft (5), ending in its upper end by a vertical panel (6). Centrally in the rotor a vertical orienting shaft (7) is placed that ends with an orienting vane (8). Each of the shafts (5) is connected to the orienting shaft (7) by means of a respective mechanical transmission. During the rotation of the rotor, the mechanical transmission rotates the panels with a gear ratio with respect to the orienting shaft equal to 1:2 and 1:1, with a constant and inconstant angular speed, the angular speed of the rotor being constant. The mechanical transmission performs also just partial turns of the panels around one of their basic positions. In this way different planetary movements of the panels are ensured depending on the speed and nature of the wind, making the most of the wind power.

Description

TECHNICAL FIELD

The invention relates to a device with a vertical axis of rotation, which is used for the conversion of wind energy, which is used for the production of electricity, to drive water pumps and other wind power equipment.

BACKGROUND OF THE INVENTION

A wind energy conversion device (BG1049U1) is known, consisting of a fixedly fixed base in which a vertical hollow rotor is mounted, which at its bottom is fixedly connected to a drive shaft. At its upper end, the hollow rotor is shaped like a carousel with symmetrically and evenly spaced radial arms, the ends of which are fixed at one end vertically by a vertically oriented bearing sleeve. At each bearing sleeve, there is a corresponding vertical shaft, ending at the upper end with a corresponding vertical, symmetrically oriented shaft. Centrally, a vertical orientation shaft is mounted in the rotor, ending at the upper end with a rigidly oriented orientation indicator, whereby each shaft is connected to the orientation shaft by a 1: 2 mechanical transmission. The panels are fixed to the shafts and through their gears are pre-oriented to the shoulders so that one of the panels, which is mounted perpendicular to the wind direction arm, is oriented perpendicular to the wind direction guide, and each subsequent is rotated to the previous angle. (X = 360 / 2n, where η is the number of arms.

In the process of rotating this device, the panels realize planetary motions around the center of the device that do not use all the possibilities to increase the efficiency. on the device.

SUMMARY OF THE INVENTION

It is an object of the invention to make more efficient use of the capability of increasing the efficiency by creating a device providing for the realization of suitable planetary motions on the panels through which greater efficiency is achieved. on the device.

In order to explain the essence of the invention, and to describe the problem more easily and briefly, some of the device-characterizing parameters, such as:

O is the center of rotation of the rotor as well as of the device in question; 15.

Oi - Centers of rotation of the panels around their own axes FIG. 15. Indes i shows current positions.

Wind speed -U

Peripheral speed V _nep -lineynata speed of the geometric axes of the shaft terminating in a panel Fig. 15.

Active plane - a vertical plane perpendicular to the instantaneous wind direction and passing through the center O of the rotation of the device - FIG. 15, for the purposes of the explanation, the device is considered such that the wind influences it in a definite constant direction.

Rotation radius of the device R - the radius of the circle describing the centers of rotation of the panels about their own axes Oi relative to the center of rotation of the device O-fig. 15.

Impact radius - the segment through which a given force generates torque relative to a given center of rotation.

Item 1 -position 1 depends on the direction of rotation of the device selected, and represents the point where they intersect, the circle described by the axes Oi of the shafts ending in panels around the axis of the device O and the active plane, and at what point the direction of the peripheral speed V _nep and wind direction U coincide -Fig. 15.

Item 2 -position 2 depends on the direction of rotation of the device selected, and represents the point where they intersect, the circle described by the axes Oi of the shafts ending in panels around the axis of the device O and the active plane, and at which point the direction of the peripheral velocity V _nep and wind direction U are in opposite directions -fig. 15.

Angle (Xi - the current angle for a given arm defining the instantaneous rotation of a given arm compared to the active plane, where angle (Xi is viewed in the horizontal plane defined by the radius of rotation R and its starting arm lies on the intersection line between the horizontal plane and active plane, with its current arm being the considered arm of the rotor, to which the bearing panel is bearing, such as an angle (Xi is developed around the center of rotation O of the device. For the arm crossing Pos. 1 angle (X is zero degrees , as an angle (Xi changes from 0 ° o 360 ° of one revolution of the device, and then repeats the pin. 15.

Angle βί - the current angle for a panel defining the instantaneous direction of a given panel relative to the active plane, wherein angle βί is viewed in the same plane as the angle (Xi and its initial arm lies on the intersection between the horizontal plane and the active plane plane, its current arm being the direction of the panel. Angle βί develops about Pos.2 in the same direction that the angle develops (Xi and changes from 0 ° to 180 ° degrees for one revolution of the device, and then repeats -Fig. 15.

Angle δ - this is the angle locked between the axes of symmetry of two adjacent arms of a rotating structure and is equal to the result of a 360 ° division of the number of arms, wherein the angle δ is the same for all pairs of adjacent arms of the structure, so with the arms arranged symmetrically -Fig. 15.

The basic parameters for the device are also the dimensions of the panels, such as width (length) - I, height of the panel - h and thickness of the panel.

Resulting velocity U _{r - the} real wind velocity over the center of a particular panel, obtained as a result of the vector of wind velocity U and the vector of the momentary direction of peripheral velocity V _nep , for the considered arrangement of the panel as part of its circumference in the process FIG. 16-20.

Attack Angle - The angle between the direction of a particular panel and the direction of the resulting velocity U _r for a given panel location as the device rotates. For the sake of brevity, the angle of attack ψί is the angle between that direction of the panel and the direction and direction of the resultant velocity U _r , whereby lifting force is created on the panel with a torque-producing direction relative to the axis of the rotor, which helps rotate the rotor at the selected direction of rotation of the device - FIG. 16-20.

Angle (the angle between the direction of the resultant velocity U _r and the wind velocity i.fig. 16-20.

Angle <p _2i - the angle between the direction of the resultant velocity U _r and the peripheral speed V _ncp .fig. 16-20.

The object of the invention is solved by creating a wind energy conversion device-FIGS. 1 and 2, which consists of a fixedly fixed base in which a vertical hollow shaft is mounted, which is connected to a drive shaft by means of a mechanical gear consisting of a gear wheel fixed to the lower end of the hollow shaft associated with a gear wheel fixed to the drive shaft. At its upper end, the hollow shaft is shaped like a carousel with symmetrically and evenly spaced radial arms, at whose ends at equal distances from the center, it is fixedly fixed to one vertically oriented bearing bushing, in which a corresponding vertical shaft, ending at its upper end, is supported. corresponding rigidly fixed to the shaft panel. Centrally in the carousel there is a vertical orientation shaft, ending at the upper end with a rigidly oriented orientation indicator, with each shaft ending in a panel connected to the orientation shaft by means of a mechanical gear unit containing a separate module. The shafts ending in panels, through their gears, in the process of rotation of the device, realize their set directions from the gears to the orientation shaft, to the active plane, and to the resultant speed U _r . whereby they make corresponding planetary motions about the axis of the device.

The orienting wind indicator always maintains such a direction of the orientation shaft, in which the guide of the orienting wind indicator is perpendicular to the active plane. As the wind direction changes, the orientation windmill rotates the orientation shaft to take the same direction relative to the new wind direction and to the new active plane that it had with the previous ones. With this reorientation of the orientation shaft, the mechanical gearbox reorients the panels to occupy the same directions with respect to the new active plane that they had with the previous one.

According to the invention, the mechanical gearbox of FIG. 1 is designed as a gear, with a guide gear stationary being fixed on the orientation shaft, by which a drive gear is engaged for each arm and each shaft ending with a panel, and the driven gears are fixed at one end of the respective gear. for a given arm, an input shaft of the mechanical gearing, which rests in fixed supports. In this case, each shaft of the panel is fixed on one guide gear wheel, with which it is engaged on one drive gear, fixed on one end of the corresponding shaft of the gearbox for bearing for the given arm, which camps in fixed supports. The inlet shaft and the outlet shaft are connected by means of a separate module fixed to the given arm.

According to the invention, the separate module is intended to realize different gear ratios between the orientation shaft and the shafts ending in panels, both with a constant and variable angular velocity of the transmitted movement, expressed in a constant or variable angular velocity of rotation of the shafts ending with the panels, in certain sections of their circumference, at a constant angular velocity of rotation of the rotor, and within one revolution of the rotor. In this case, the panels make certain forward or delay deviations with respect to the given gear ratio, at which time the panel realized a larger rotation angle, from the rotation angle corresponding to the given gear ratio, while at a certain next moment the panel lagged behind, which already realizes - smaller rotation angle than the rotation angle corresponding to the specified gear ratio. The detached module is intended to realize only partial rotations between the orientation shaft and the shafts ending in panels, which provides the panels with no full rotation about their axes, and only partial rotations in one direction or the other with respect to some basic position of the panel. When the detachment implements a gear ratio, the detachment module, together with the rest of the gear, generally provide one-way rotation of the coupled, panel-ending shafts and the orientation shaft relative to each other.

According to the invention, the separate module consists of a mechanism for switching different gear ratios, a mechanism for switching on and interrupting the movement between the orientation shaft and the shafts ending in panels, a mechanism for creating irregularity of the transmitted movement, a module for influencing the mechanism for creating irregularity , as well as a system for detecting a particular position of a given arm in the process of rotating a device suitable for switching to other planetary motion, and a steering system we of the module as a whole. When the implementation of a device provides for the possibility of realizing only part of the planetary motion of the panels, respectively, in a separate module only part of its nodes are executed.

Thus, in the process of operation of the device, to optimize the use of wind, depending on its speed and nature, the mechanical gear realizes various planetary movements of the panels.

According to the invention, in the first planetary motion, FIG. 15, the directions of the panels conclude with the active plane an angle βί equal to half the angle (Xi, which concludes the respective arm with the active plane. The panels in Pos. 1 occupy a direction coinciding with the active plane, and the panels located in Pos. 2 occupy directions perpendicular to the active plane.

In order to avoid overlapping of the panels in the process of rotation of the device, in this planetary motion the panels are filled with the maximum theoretically possible width determined by the dependence:

· ⁵

2.R.sin- ι = _______ r.

δ cos4

This planetary motion of the panels is applicable at a peripheral velocity V _nep of the device less than the wind speed U, and the maximum utilization of the wind power is achieved by the device at a peripheral velocity V _nep equal to one third of the wind speed U.

V = -and trans.

This planetary motion of the panels is most effective at a ratio of angle (Xi and angle βί equal to 2: 1.

This planetary motion of the panels is realized by the gear ratio of the mechanical gearing between the orientation shaft and the shafts ending in panels equal to 2: 1.

Characterized by constant efficiency, because forces are obtained by the resistance of the panels, making it particularly suitable for medium and high wind speeds. In particular, lifting forces are created on the panels around Pos. 2, which in this case exert torques relative to the axis of rotation of the rotor, by means of small radii of influence. To take advantage of these additional features of the device, the mechanical gearbox provides a second planetary movement of the panels.

The second planetary motion of FIG. 16 is also applicable at peripheral velocities V _ncp of the device less than the wind velocity, and is realized at the gear ratio of the mechanical gear between the orienting shaft and the shafts ending in panels equal to 2: 1, with corresponding forward and delay rotations of panels in relation to this gear ratio.

In the second planetary motion of FIG. 16 at the circumference of the panels from Pos. 1 to point D, the directions of the panels conclude an angle βΐ equal to half the angle (Xi. Point D10 is the point at which the resultant velocity U _r coincides in the direction with the corresponding rotor arm, which for peripheral velocity V _nep equal to one-third of the wind speed is realized at an angle (Xi equal to 70.53 degrees. In the area about tJ, the panels realize a reorientation until the optimum angle of attack is reached ψί. The reorientation is expressed in a delayed (lagging) deviation. panel, from the preset affective attitude.

From TJ to T11, the panel directions maintain an optimal angle of attack ψί. In this case, the panels make a reorientation, which is a gradual pre-emptive deviation of the panel relative to the given gear ratio. Thus, in the section under consideration, considerable lifting force is exerted on the panel, generating torque against the axis of rotation of the rotor, by means of a large radius of action.

Point E11 is the point at which the panel, maintaining the optimum angle of attack ψί, at the same time realizes with the active plane an angle βί equal to half the angle (Xi.

From E11 to E12, the directions of the panels conclude an angle βί equal to half the angle (Xi. Point E12 is the point at which the panel maintains with the active plane an angle βΐ equal to half the angle (Xi, at the same time realizes an optimal angle of attack ψί.

From d12 to dj, the panel directions maintain an optimal angle of attack ψί. In this case, the panels make a reorientation, which is a gradual pre-emptive deviation of the panel relative to the given gear ratio. In this section, considerable lifting force is also exerted on the panel, generating torque relative to the axis of rotation of the rotor, by means of a large radius of impact.

T.13 point is a point where the resultant velocity U _r coincides in direction with the respective side of the rotor, a circumferential speed of the device V _nep equal to one third of the wind speed is realized at an angle (Xi equal to 289.47 degrees. In the section about d13, the panel realizes a reorientation to reach an angle βί equal to half of the angle (Xi. The reorientation is expressed in the delayed (lagging) deviation of the panel from its predetermined gear ratio.

From point E13 to Pos. 1, the directions of the panels conclude with an angle βί equal to half the angle (Xi.

This planetary movement is most effective for use at relatively low wind speeds of up to about 10 - 12 meters per second. In the panels behind the active plane, the wind is already turbulent, which is more pronounced with stronger wind. Thus, with increasing wind speed, at some point these panels working by creating a lifting force prove to be more effective than when they use wind resistance. This problem is solved with the third planetary movement.

The third planetary motion of FIG. 17 is also applicable at peripheral speeds V _ne p less than the wind speed, and is realized at the gear ratio of the mechanical gearbox, between the orientation shaft and the shafts ending in panels equal to 2: 1, with corresponding forward and delayed rotations of panels against this gear ratio.

In the third planetary motion of FIG. 17 from Pos.1 through Pos.2 to E12, the directions of the panels conclude an angle βί equal to half the angle (Xi.

From item 12 to item 13, the panel directions realize the optimum angle of attack ψΐ. In this case, the panels make a reorientation, which is a gradual pre-emptive deviation of the panel relative to the given gear ratio. In this section, considerable lifting force is exerted on the panel, generating torque relative to the axis of rotation of the rotor by means of a large radius of impact.

In the section about tD13, the panel realizes a reorientation to reach an angle βί equal to half the angle (Xi. The reorientation is expressed in the delayed (lagging) deviation of the panel from its predetermined gear ratio.

From point E13 to Pos. 1, the directions of the panels conclude with an angle βί equal to half the angle (Xi.

This planetary motion is effective for use at average wind speeds of about 8-10 to about 14-16 meters per second. At high wind speeds, it is more turbulent, and the interplay between adjacent panels in front of the active plane is already significant.

When the panels flow from the air stream, when the lift forces are created, the complex picture is obtained for the considered cases, taking into account the rotation of the panels around their own rotation axes, which is related to the rotation of the device as a whole. On the other hand, the faces of the panels move at different instantaneous speeds, with the faces of the panels behind the active plane moving at lower speeds than the faces of the panels facing the active plane. This implies that the optimum angles of attack ψΐ thus locked between the directions of the panels and the directions of the resultant velocities U _r acting against the centers of the panels, behind the panels behind and in front of the active plane, whose centers are affected by the equal resultant velocities U _r , are in reality will have different optimal angles of attack ψί, relative to the directions of these resultant velocities U _r . Due to the complex picture, the optimal angles of attack ψί can only be determined by calculations supported by experimental data.

In planetary motions where, in the process of rotating the device, the panels rotate about their axis by orienting themselves to the wind, alternately with one side and the other, the panels are symmetrically executed with the shafts to which they are attached.

The fourth planetary motion FIG. 18, serves to protect the device from overload. It is implemented as a mechanical gearbox providing a gear ratio between the rotation of the orientation shaft and the shafts ending in panels equal to 1: 1.

In the fourth planetary motion, FIG. The 18 panels maintain directions perpendicular to the active plane.

In order to avoid overlapping of the panels in the process of rotation of the device, in this planetary motion the panels are filled with the maximum theoretically possible width determined by the dependence:

I = 2.R.sin—

Fifth Planetary Movement FIG. 19 is realized, the mechanical gearing providing a gear ratio between the rotation of the steering shaft and the shafts ending in panels equal to 1: 1, with corresponding forward and delay deviations relative to that gear ratio.

In Pos. 1, the panels occupy directions perpendicular to the active plane.

From Pos. 1 to D.J., the directions of the panels maintain, according to the resultant velocity U _r, certain angles of attack ψί, with the panels realizing a progressively faster spin relative to the predetermined gear ratio.

From TJ to Pos.2, the panel directions support certain angles of attack ψί, with the panels realizing a gradual lag behind the set gear ratio.

Upon reaching Pos. 2, the panels occupy directions perpendicular to the active plane.

From Pos. 2 to D.D. 13, the panel directions support certain angles of attack ψί, with the panels realizing a gradual lag behind the set gear ratio.

From point E13 to Pos. 1, the directions of the panels support at certain angles of attack пане, with the panels realizing a progressively faster spin relative to the given gear ratio.

Upon reaching Pos. 1, the panels again take a direction parallel to the wind.

This planetary motion of the panels is applicable at peripheral velocities V _nep of the device less than the wind speed, and can be used at very high wind speeds. In this case, the goal is not to achieve optimal angles of attack ψί, but to realize small angles of attack ψί at which we have a small coefficient of resistance, so the device will absorb the wind pressure. At the same time, even with slightly higher lift factors, given the high wind speed, significant lift forces will be realized. Such planetary motion can only be used to support the device in the process of rotation to allow subsequent switching to other movements.

The sixth planetary motion of Fig. 20 is applicable at peripheral velocities V _ne p greater than wind speed, and is realized, with the mechanical gear moving between the orienting shaft and the shafts ending in panels, expressed only by partial rotations of the panels in one and the other direction towards one basic position. For panels made as flat plates or as a symmetrical wing profile, the basic position in the direction coincides with the direction of the peripheral velocity V _nep of the device.

From Pos.1 to Vol.14, the panels occupy a basic position. Point E14 is the point at which the angle φ2ΐ between the direction of the peripheral velocity V _nep and the direction of the resultant velocity U _r acquires a value equal to the optimal angle of attack ψί,

From points D14 to D15, the directions of the panels maintain an optimum angle of attack ψί, with the panels realizing a gradual rotation in the direction of rotation of the rotor.

Item D15 is a point where the corner φ2ί has reached a maximum value, a peripheral speed of V _nep equal to three times the wind speed U is realized at an angle <Xi equal to 70.53 degrees, while the angle φ ₂ is equal ΐ 19.47 degrees,

From tD15 to tD16, the directions of the panels maintain the optimum angle of attack ψί, with the panels realizing a gradual rotation in the opposite direction of rotation of the rotor.

Point D16 is the point at which the angle φ _2ί acquires a value equal to the optimum angle of attack ψί, at which point the panel again occupies a basic position.

From item 16 through item 2 to item 17 the panels occupy a basic position.

Point E17 is the point at which the angle φ _2ί regains a value equal to the optimum angle of attack ψμ

From eD17 to eD18, the directions of the panels maintain an optimum angle of attack ψ, as the panels realize a gradual rotation in the opposite direction of rotation of the rotor.

T.18 point is a point where the angle φ _2ί has reached a maximum value, a circumferential speed V _nep equal to three times the wind speed U is realized at an angle (Xi equal to 360 to 70.53 degrees, while the angle φ _2ί is equal to 19.47 degrees,

From TG18 to TG19, the directions of the panels maintain an optimum angle of attack панеι, with the panels realizing a gradual rotation in the direction of rotation of the rotor.

Point E19 is the point at which the angle φ ₂ ί acquires a value equal to the optimum angle of attack ψι, at which point the panel again occupies a basic position.

From item 19 to Item 1, the panels occupy a basic position.

In this planetary motion, the panels are symmetrically or asymmetrically arranged relative to the shaft to which they are attached, depending on how well this planetary motion is combined with others. It is characterized by the realization of large lifting forces, generating torques against the rotor, through small radii of influence.

What has been said about the possible way of accurately determining the optimum angle of attack ψί also applies to this planetary motion.

The right moment to reorient from a particular movement of the panels in the process of rotating the device to another is when a panel is located in Pos.2, in which in all planetary movements, the panels occupy the same position. A complete reorientation requires a period of time during which the rotor realizes at least one full rotation in order for all panels to pass through Pos.2 and to switch them to the next planetary motion.

These planetary movements are used in combination, or only part of them are performed. As the simplest embodiment of the device, the mechanical gear unit realizes only partial rotations of the panels, with the device operating only at a higher peripheral speed V _nep than the wind speed U.

The operation of the device is monitored by an automated control system (ACS), which, taking into account the factors affecting the operation of the device, makes decisions and regulates the transition from a planetary planetary movement to another. For this purpose, the ACS receives wind direction and speed information from sensors located in, above, or around the device. The ACS receives information on both the instantaneous rotation of the device and the appropriate moment to realize the transition to a planetary movement.

According to the invention, the steering shaft can be driven by an electric motor controlled by an ACS.

According to the invention, the mechanical gearbox can be replaced by providing a separate electric motor controlled by the control unit to drive each panel.

According to the invention, the panels can be made of a frame structure with a web stretched therein. This implementation will also increase the power absorbed by the device, as when the forces are obtained by the resistance of the panels, when stretching the canvas will increase the surface of the panel, and upon realization of the lifting force, the panel will become an arc plate, which is always self-oriented in an appropriate manner.

According to the invention, in order to reduce the flow of airflow in the lifting force, elements may be attached laterally to the vertical edges of the panels to create a turbulent boundary layer.

According to the invention, in order to limit the inductive resistance, horizontal panels are attached to the lower and upper edges of the panels.

If necessary, the arms are secured against torsion, with all pairs of adjacent arms at the end connecting to each other with securing beams that are firmly attached to the respective arms. With a large number of shoulders, some of them may not be filled. In this case, the beams are designed as circular sectors with a radius equal to the radius of rotation of the device. The missing sleeve bearing sleeves are secured to the circular sectors, occupying the positions they would occupy if these arms were met. In case the circular safety beams replace the missing arms, the mechanical gears connecting the panels to the orientation shaft are secured to the adjacent arms and the corresponding circular beam.

According to the invention, vertical panels can be attached to the underside of the arms, which in the process of rotation of the device increase the power obtained. For this purpose, in this semicircle from the circumference of the arms extending toward the side of Pos. 1, these panels occupy a direction parallel to the arm to which they are attached, whereby in the other semicircle of the circumference of the arms extending toward the side of Pos. .2, these planes occupy a direction parallel to the wind direction. These panels are applicable to devices operating at peripheral velocities V _nep less than the wind speed, and in addition to creating additional power, they keep the device in constant rotation in the presence of wind allowing subsequent switching.

According to the invention, the device can be provided with two rotating rotors.

According to the invention, the base may be movable, using the power absorbed by the device to drive the base.

EXPLANATIONS OF THE FIGURES Attached

Figure 1. Vertical section of the device, driven and oriented only by the force and direction of the wind.

Figure 2. The device view shown in Figure 1, top.

FIG. Schematic diagram of a separate module with schematics of a mechanism for switching different gear ratios, a mechanism for creating unevenness of the transmitted movement and a module for influencing the mechanism for creating irregularities,

4. Scheme of mechanism for switching on and interrupting the transmitted movement.

FIG. 5. Scheme for creating the pendulum motion of the swinging axis and the scheme of the impact arm.

6. Management system for the module as a whole.

7. Scheme of a separate case of execution of a separate module, wherein the module for influencing the movement unevenness mechanism is self-propelled.

FIG. 8. Schematic diagram of a particular case of execution of a separate module for the realization of planetary motion, with only partial rotations of the panels.

9. A variant of the device in which the steering shaft is driven by an electric motor.

FIG. 10. A device variant in which each panel shaft is driven by a separate electric motor.

11. An example of creating a turbulent boundary layer.

FIG. 12. Scheme of additional attached areas under the arms of the device.

FIG. 13. A variant of the device made of two rotating rotors.

FIG. 14. Variant of the device with a movable base.

FIG. 15. Schematic view of a device representing the geometrical and mechanical parameters of the device.

FIG. 16. Planetary motion of the panels with the combined creation of the driving forces.

FIG. 17. Planetary motion of the panels with the combined creation of the driving forces.

FIG. 18. Planetary motion of the panels in the protective version.

FIG. 19. Planetary motion of panels for creation of lifting forces only.

20. Planetary motion of the panels, realized with only partial rotations of the panels.

EXAMPLE IMPLEMENTATION OF THE INVENTION

The wind energy conversion device is shown in FIG. 1, with a vertically hollow rotor 2 supported in a fixedly fixed base 1. In its lower part, the rotor 2 is connected to a drive shaft 18 by means of a gear wheel 19 firmly attached to its lower end. firmly attached to the drive shaft 18, gear 20. In its upper part, the rotor 2 is shaped like a carousel with four symmetrically and evenly spaced radial arms 3.

At the edges of the arms 3, at an equal distance from the center, a vertically oriented bearing bushing 4 is fixed, in which a corresponding vertical shaft 5, terminating at its upper end with a corresponding, firmly attached to the shaft 5, panel 6, is mounted. is a vertical orientation shaft 7, terminating at its upper end with a rigidly oriented orientation indicator 8.

Each shaft 5 is connected to the orientation shaft 7 by means of a mechanical gear M, which is designed as a gear. A guide conical gear 9 is firmly attached to the orientation shaft 7, by which one driven conical gear 10 is secured to each arm 3, which are rigidly secured to one end of the mechanical gear input shaft 11 corresponding to a given shaft 3. M, bearing in stationary supports 12. Each shaft 5 is rigidly fixed to one driven conical gear 13, each of which is engaged to one driven conical gear wheel 14, firmly attached to one end of the corresponding outlet 3 for the given arm. mechanical shaft shaft 15 M, bearing in supports 16.

The input shaft 11 and the output shaft 15 are connected by means of a detachable module 17, fixedly fixed to a given arm 3. The detached module 17 consists of a mechanism 33 for switching different gear ratios, a mechanism 34 for switching on and interrupting the movement between the orientation shaft 7 and the shafts. 5 ending with panels 6, mechanism for creating uneven movement of the transmitted movement, module of influence 36 on the mechanism for creating irregularity, as well as a system for reporting a certain rotation of a given arm 3 in the process and the rotation of the drive and control system of Figure 6 separate module 17 as a whole.

The mechanical gearbox M together with the separate module 17 generally provide a one-way rotation of the connected, orientation shaft 7 and shaft 5 terminating with the panel 6 relative to each other.

The process of rotation of the device is monitored by an automatic control system ACS 21, whereby on the rotor to the orientation shaft 7, a sensor 22 is attached to each arm 3, recognizing a certain torque between the orientation shaft 7 and the rotor, with the sensor 22 being connected to the ACS 21. Above the orienting wind indicator 8 is a sensor 23 that detects the direction and speed of the wind, and the sensor 23 is connected to the ACS 21.

The mechanism for switching different gear ratios Fig. 3, designed for gear ratios 2: 1 and 1: 1, between the orientation shaft 7 and the shafts 5, is made of two parallel shafts. The first shaft is a drive shaft 3 8 that coincides with the input shaft 11 of the mechanical gearbox M. The second shaft is a driven shaft 40, which rests on supports 41 and coincides with a rotating shaft 51, of the mechanism 34 for switching on and interrupting movement.

To the drive shaft 38 are fixed two gears 42 and 43, which are permanently engaged in pairs with the other two gears 44 and 45, freely bearing on the drive shaft 40. The freely bearing gears 44 and 45 are filled with steps and 47, which are facing each other, as in each step 46 and a corresponding slot (socket) 48 and 49 is formed. Between the steps 46 and 47 of the freely bearing gears 44 and 45, on the driven shaft 40, with the possibility of axial movement on the shaft , but no slotted sleeve 50 is fitted without scrolling.

On both sides of the slot sleeve 50, teeth 51 are formed with rounded tips and transverse dimensions corresponding to the dimensions of the grooves (sockets) 48 and 49. The length of the double-sided tooth 51 and the distance between steps 46 and 47 are combined such that at moving the slotted sleeve 50 and engaging one tooth 51 with the groove 49 in one step 47, then, at the time of engagement, the other tooth does not completely disengage from the groove 50 in the other step 46. The pairs of permanently engaged gear wheels in combination with the rest part of the mechanical gearbox, nd engagement of the spline nut 50 with one or other free bearing gears 44 and 45 realize a gear ratio between the orientation shaft 7 and the shaft 5, equal to 2: 1 or 1: 1.

Outside of the slot sleeve 50, a step (board) 150 is formed, which rests in a switch lever 52 for the slot sleeve, which is actuated by the control system of Fig. 6 of the detached module 17 as a whole.

The movement and interruption mechanism 34 of Fig. 4 between the orientation shaft 7 and the shafts 5 consists of two coaxial shafts. One shaft is a continuously rotating shaft 53, which coincides with the drive shaft 40 of the mechanism 33 to engage different gear ratios. The other shaft is a non-rotating shaft 54, bearing in supports 56 and 57, with an end conical gear 55, firmly attached to its end, by the mechanism 35 for creating uneven movement. With their near ends, the two shafts bear with each other, the end of one shaft being made as a step 58, which rests in a socket 59 formed at the end of the other shaft.

At their near ends, the shafts are provided with the same number and size of outer grooves 60, in which the keyway 61 is fastened with axial movement. The keyway 61 is a bushing to which laterally and in depth, keyways 62 are provided with rounded ends 63 and corresponding to the number and dimensions of the grooves 60, with the outer size of the keyways 62 having a diameter greater than the diameters of the shafts 53 and 54.

At the closest to the keyway 61, the support 56 is formed by internal grooves 64. The length of the keyways 62 and the distance from the support 56 to the end of the non-rotating shaft 54 are combined such that at the moment of engagement of one end of the keyways. 62 with the slots 64 of the support 56, thereby locking the non-rotating shaft 54, the other end of the dowels 62 may not be completely detached from the grooves 60 of the continuously rotating shaft 53.

The mechanical gearing M, in combination with the separate module 17, are engaged so that the grooves of the two shafts 53 and 54 and of the support 56 coincide at an angle (Xi of the arm 3 equal to 180 degrees.

Outside of the keyway 61, a step (board) 65 is formed which camps in a switching lever 66 for the keyway driven by the system of FIG. 6 for controlling the module 17 as a whole.

FIG. 35 for creating uneven movement of the transmitted movement. FIG. 5 between the orientation shaft 7 and the shafts 5, it consists of an inlet 55 and an outlet 67 conical gear wheels, which are coaxial, with the same parameters and spaced at a certain distance, facing each other. The inlet 55 conical gear wheel is secured to the non-rotating shaft 54 of the actuation and interruption mechanism 34. The outlet 35 conical gear wheel is firmly attached to the outlet shaft 15 of the mechanical gearbox M.

Along with the two conical gears 55 is 67, a third swinging conical gear wheel 68 is engaged, the axes of the three mutually engaged conical gears 55.68 and 67 intersect at one point D1. The swinging conical gear wheel 68 is fixed to the swinging axis 69 with the possibility of pendulum-like movements around point D1.

The swinging axis 69 is made through a swinging through the swinging conical gear wheel 68 and, with one end, it rests in a retainer 70, located between the inlet and outlet gears 55 and 67, and pivotally secured to the fixed support 71, the geometrical axis of the hinge 72 coinciding with the axes of the inlet 55 and the outlet 67 conical gears. The swinging axis 69 is driven by an impact arm 73, of the module 36 for influencing the mechanism 35 for creating irregularities.

In a fixed inlet conical gear 55, in the pendulum-like motions of the swinging axis 69, the swinging conical gear 68 is rotated over the inlet gear 55, thereby driving the outgoing conical gear 67, which is expressed in parts one and the other direction, relative to one basic position of the swinging axis 69. With a rotary inlet gear 55, the motion generated by the swinging gear wheel 68 is superimposed or subtracted from the transmitted movement, resulting in faster and slower speeds. gear wheel output 67, compared to a specific gear ratio. The basic position of the swinging axis 69 corresponds to the position occupied by the panels in Pos.2.

Module 36 for affecting the non-uniformity mechanism 35, configured to effect three planetary motions, consists of a receiving shaft 74 which supports bearings 75. The receiving shaft 74 is connected to the mechanical gear M, such as the input shaft 11 of the mechanical gear M is a rigidly conical gear wheel 27 which is engaged with another conical gear wheel 28 firmly secured to one end of the spurious shaft 29, which rests on a support 30. To the other end of the spurious shaft 29 is a rigidly splined gear wheel 31, which is involved with another o a conical gear 32 firmly attached to one end of the receiving shaft 74. Or the receiving shaft 74 is connected directly to the orientation shaft 7 by means of a mechanical gear, the gears in both cases providing a gear ratio between the orientation shaft 7 and the receiving shaft 74, equal to at 1: 1.

On the receiving shaft 74 are fixed three cylindrical cams 76. In the immediate vicinity of the shaft 74 and with the possibility of movement coaxially to the shaft 74, a slider 78 is mounted in the fixed supports 77. On the slider 7 coaxially with the shaft 74, opposite each cam 76 guide holes 24 are formed, in which inclining levers 79 are arranged transversely to the humps, with a rounded end to the humps.

From the opposite side to the receiving shaft 74, the side of the slider 78, the engagement levers 79 are made with heels 80, and between each heel 80 and the slider 78, an elastic member 81 is exerted on each of the engagement levers 81, exerting force in an opposite direction to the shaft 74. On this side, the engagement levers 79 are limited by a positioning lever 84 which moves in fixed supports 83 in a direction coaxial with the receiving shaft 74, wherein at that end the engagement levers 79 are filled with rollers 82.

The cam channels are arranged such that at least at one point of rotation of the receiving shaft 74, the distances between the cam channels, in the part opposite the engagement levers 79, correspond to the distances between the engagement levers 79. This moment coincides with the moment when the arm rotates at an angle of ai equal to 180 degrees. The positioning lever 84 is made up of three steps 26 which, when moving the positioning lever 84, press a particular engaging lever 79 to the corresponding cam channel 25, releasing the remaining engaging levers 79. The dimensions of the engaging levers 79 and the dimensions between the steps 26 of the positioning lever 84 are adapted in such a way that, in the case of a switching movement of the switch lever 84, it is realized that only one switch lever 79 is connected to the corresponding humeral channel 25. The height of the steps 26 and the design of the transitions between them are adapted us so that, at the moment of engaging a lever 79 into the corresponding cam channel 25, then the respective disconnect lever 79 which is being disengaged does not completely disengage from the corresponding cam channel 25.

An impact arm 73 is firmly attached to the slider 78, which drives the swinging axis 69 of the mechanism 35 to create irregularities. The impact arm 73 is made of two parts, ending at the end with a fork 118 that encloses the swinging axis 69, the fork 118 rests against the rest of the arm 120 via a shaped step 119 of the fork 118 and a shaped opening 121 to the rest of the arm 120.

The system 37 for detecting a particular position of a given arm 3 in the process of rotating the device consists of a sensor 22 that signals to the ACS 21 when a particular arm 3 realizes a rotation angle of 180 degrees.

The control system of Fig. 6 of the separate module 17 as a whole, for realizing three planetary movements of the panels, and filled with one common actuator, consists of a sled 91 which slides into the fixed supports 92, and to which they are rigidly fastening the switch lever for the slot sleeve 52, and the switch lever for the key sleeve 66. Sideways from the carriage 91 to a fixed support 93, with the possibility of rotating around it an angular segment 94, with one arm of the segment 94 is engaged in the bearing 95 to with sliding ability in ne s 95, and the other arm segment 94 is engaged in the bearing to the positioning lever 84 heel 96 slidably therein.

The carriage 91 is driven by the motor 100 by means of a rigidly attached to the carriage 91 arm 97, on which a slot 98 is attached to the drive finger 99 of the motor 100. A sensor 101 is attached to the motor 100, against which three sensors 102 are mounted, one for each each working position of the carriage 91, the sensors 102 being disposed at the necessary angular displacement relative to the motor 100, and connected to the ACS 21.

As an example embodiment, the detached module 17 is configured to realize three planetary motions of the panels, of which the first planetary motion is the case in which the panels 6 realize only partial deviations from a given basic position. The slot sleeve 50 is engaged to the larger freewheel gear wheel 44, with a 2: 1 gear ratio between the orientation shaft 7 and the shafts of the panels 6. The keyway 61 is secured to the fixed support 56 and the movement to the non-uniform mechanism 35 is interrupted. The cam channel 25 to which the locking lever 79 is currently engaged is provided with a corresponding cam profile, displacements of the slider 78 are realized, as well as deviations of the swinging axis 69.

For the realization of the second planetary motion, in which the angles of the panels 6 support angles βί with respect to the active plane equal to half the angle αί, with corresponding forward and lagging rotations of the panels, subsequent switches are realized for each arm 3 passing through Pos.2 , within one revolution of the rotor 2. The key bushing 61 is detached from the fixed support 56 and engages the rotating shaft 53 and the non-rotating shaft 54 mutually, thereby transmitting rotational motion to the panels. The cam channel 25 to which the engaging lever 79 is currently engaged is provided with a corresponding cam profile, and displacements of the slider 78 are realized, as well as deviations of the swinging axis 69. The length of the teeth 51 of the slotted sleeve 50 and the depth of the slit 50 of the step 46 of the larger free bearing gear 44 are combined such that the displacement of the slot sleeve 50 does not result in cleavage and, from the large free bearing gear 44, and the engagement of the small free bearing gear 45, at which before The ratio of the steering shaft 7 to the shaft 5 remains equal to 2: 1.

For realizing the third planetary movement of the panels 6, which is the protective variant, in which the panels 6 maintain directions perpendicular to the active plane, at the subsequent switching for each arm 3, the slot sleeve 50 is detached from the large free bearing gear 44 and engaged. to the small 45, whereby a gear ratio of 1: 1 is realized between the orientation shaft 7 and the shafts 5. The hump channel 25 to which the engaging lever 79 is currently engaged is designed as a symmetrical cylindrical channel, and no displacements of the slider 78 and displacement of the swinging axis 69 are realized.

As an embodiment of FIG. 8, the detached module 17 is configured to realize only planetary motion of the panels, wherein the panels 6 realize only partial deviations from a given basic position. The receiving shaft 74 of the impact mechanism 36 and the inlet shaft 11 of the mechanical gearbox M are designed as one common shaft, on which a cylindrical cam 76 is firmly fixed. The inlet conical gear 55 of the uneven creation mechanism 35 is fixed to a fixed support. 90, the swinging axis 68 being secured directly into the hump channel 25.

As an exemplary embodiment of FIG. 7, the detached module 17 is configured, with the continuously rotating shaft 53 of the on / off mechanism 34 and the inlet shaft 11 of the mechanical drive M being constructed as one common shaft. The inlet conical gear 55 is rigidly fixed to the non-rotating shaft 54. The impact mechanism 36 is configured and the impact arm 73 is rigidly fixed to the axis of a stationary motor 37.

As an exemplary embodiment of the apparatus of Fig. 9, the orientation shaft 7 is driven by an motor 113 coupled to an ACS. In this case, the orientation shaft 7 is designed as a hollow shaft 207, with its leading end firmly attached to the leading conical gear wheel 9. At the lower end of the orientation shaft 207 there is a rigidly mounted gear wheel 111, which is engaged with another gear wheel 112, rigidly secured to the axis of the motor 113. In the orientation shaft 207, the windshield rod 114 is mounted stationary, and a sensor 23 for speed and wind direction and associated with the ACS 21 is mounted at the upper end of the windshield rod 114.

As an exemplary embodiment of the apparatus, FIG. 10, the shafts 5 are driven by single motors 115 for each arm 3 connected to the control unit 21. One motor 11 is fixed on each arm 3. Each axle 115 is rigidly secured to the axle of the gear wheel 116, secured by a firmly fastened to the corresponding shaft 5, gear wheel 117. In the rotor 2, the windshield rod 114 is supported.

As an embodiment, FIG. 11, the panels 6 may be made of a frame structure 125 fixed to the shaft 5, in which a web 126 is fastened.

To create a turbulent boundary layer FIG. 11 uses a circular segment 131, which is a vertical body located along the vertical edge of the panel 6, and is fixed to the panel 6 by means of supports 137. In a vertical section, the circular segment is formed by the intersection of two circles 132 and 133, such as the centers of the circles lie on the line defining the direction of the panel 134 at some distance from each other. The center of the circle forming the inner portion 133 of segment 131 is of smaller radius and is located closer to the face 135 of panel 6. Thus, the formed edges 136 of segment 131 overlap a portion of panel 6.

Thus, at the flow of panel 6, a greater pressure is created at point D2 and air enters through this zone in segment 131, and when it exits through the zone at point D, it is highly turbulent and turbulates and the boundary layer is still at the front of the panel.

To create a turbulent boundary layer as well as to improve the adhesion of the flow to the back of the panel 6, wedge-shaped feathers 140 are mounted internally to the segment 131 against the foreheads 135 of the panels 6. to which, with the possibility of rotation about the axes 139, wedge-shaped feathers 140 are mounted. The wedge-shaped feathers 140 are connected to the inside of the segment by elastic elements 141, which exert force in the direction of the wedge-shaped feathers 140 so as to hold the wedge-shaped ones. the feathers 140 attached to the edges 136 of the segment 131. The distance from the vertical axes 139 to the forehead 135 of the panel 6 is adapted to allow the wedge feathers 140 to rotate about the vertical axes 139.

Thus, at the flow of panel 6, the high pressure created at point D2 presses and opens the corresponding wedge-shaped pen 140 and the air enters through this zone into the segment 131 through a larger opening, and when it exits the segment through the zone at point D, it is still the boundary layer is also more turbulent and turbulent, whereby when adhering to the edge 136 of the segment 131, with its own contour, the wedge-shaped pen 140 extends the outer contour 132 of the segment 131 to close proximity to the outline of the panel, t flow at the beginning, when the segment 131 itself flows.

As an exemplary embodiment of the apparatus, FIG. 1, horizontal panels 142 are attached to the upper and lower ends of the panels 6 to reduce the inductive resistance.

As an exemplary embodiment of the apparatus, FIG. 12, additional areas are secured below the arms 3 of the device, which consist of the vertically fixed supports 128, which are fixed to the lower edge of the arms, to which vertically oriented plates 129. With respect to each vertical plane 129, sub the corresponding arm 3 of the rotor is a fixed retainer of closure 130, which is located on the line connecting the vertical supports 128 and the center of the device, and is at a distance from the vertical support 128 less than the width of the vertical and plane 129. In the vertical direction, the closure limiter 130 overlaps the upper edge of the vertical plane 129.

As an embodiment, FIG. 13, the device is provided with two rotating rotors relative to each other, wherein a vertical hollow rotor 202 is mounted in the orientation shaft 207, which is connected to a drive shaft 218 by means of a rigidly fixed gear wheel 219 connected to a rigidly fixed end thereof. to the drive shaft 218, gear wheel 220. In its upper part, the rotor 202 is shaped like a carousel with symmetrically and evenly spaced radial arms 203, at whose ends at equal distances from the center, a vertically oriented bearing sleeve is fixed.

204, in which the corresponding vertical shaft 205, terminating at the upper end with a corresponding rigidly fixed to the shaft 205 panel 206., is mounted centrally in the rotor 202 is a vertical orientation shaft 227, terminating at its upper end with a rigidly oriented orientating wind indicator 8. Each the shaft 205 of the panel 206 is connected to the orientation shaft 227 through the mechanical gearing M.

A gear wheel 231 is rigidly attached to the lower end of the orientation shaft 227. The gear wheel 230 is rigidly fixed to the lower end of the orientation shaft 207. The gear wheel 231 and the gear wheel 230 are connected by a mechanical chain 232 which implements a transmission relationship between the orientation shaft 227 and the hollow orientation shaft 207 equal to 1: 1 and the unidirectional rotation of the connected shafts relative to each other

As an exemplary embodiment of the apparatus, FIG. 14, the base 1 is configured to be movable by being mounted on four drive wheels 240. The drive wheels 240 are coupled in pairs with axles 241, which support bearings 242 formed at the base 1. The axis 241 of one pair of drive wheels 240 is connected with the rotor 2 by means of a mechanical gear, with a conical gear wheel 243 firmly attached to the lower end of the rotor 2, which is connected to a rigidly conical gear 244 fixed to the axis 241.

DEVICE ACTION

Under the influence of the wind, the orienting windmill, together with the orienting shaft to which it is attached, rotates and orientates in the wind direction, and with each change of wind, the orienting windmill and the orienting shaft, reorient and take that direction to the new wind direction. which they had compared to the previous direction.

In the process of rotating the device, the panels make certain planetary motions about the axis of the rotor, set by the mechanical gear connecting them to the orientation shaft, while maintaining certain directions in the direction of the wind.When changing the direction of the wind, reorienting the orientation the shaft, through the mechanical gear, is also transmitted to the panels, in which they take the same directions in relation to the new wind direction that they had with the previous one.

The planetary motions and their characteristics are explained in the technical nature of the invention. The mechanism for creating planetary motions is explained in the embodiments of the invention.

The rotational motion of the rotor is transmitted through a drive shaft to a subsequent wind energy conversion device.

Claims (15)

Patent Claims A wind energy conversion device comprising a base (1) in which a hollow rotor (2) is mounted, which at its upper part is designed as a carousel with symmetrically and evenly spaced radial arms (3) at the ends of which Equally spaced from the center, a vertically oriented bearing sleeve (4) is fixed to it, in which a corresponding vertical shaft (5) ends, terminating at its upper end with a corresponding, rigidly fixed to the shaft (5) panel (6), characterized by the fact that a vertical orientation shaft (7) is mounted centrally in the rotor (2), ending at its upper end with a rigidly oriented orientation indicator (8), or the orientation shaft (7) is connected to an electric motor (113), wherein the panels (6) are symmetrically or asymmetrically arranged relative to the shafts (5), with each shaft (5) ) is connected to the orientation shaft (7) by means of a gear, or each shaft (5) is connected to an electric motor (115), whereby the base (1) is fixed, the rotor (2) is connected to a driving shaft (18), by means of a gear wheel (19) rigidly secured to the lower end of the rotor (2) connected to a rigidly secured shaft (18) , a gear wheel (20), wherein the operation of the device is monitored by an automated control system (21), whereby elements (131) are attached to the vertical edges (135) of the panels (6) to create a turbulent boundary layer , in which panels (142) are fixed at the upper and lower edges of the panels (6) to reduce the inductive resistance, while additional areas (129) are attached to the lower side of the arms (3). A wind energy conversion device according to claim 1, characterized in that the gear unit is configured as a mechanical gear unit M, comprising a separate module (17), and a guide gear (9) is fixed to the orientation shaft (5). , to which for each arm (3) is connected one driven gear (10), firmly fixed to one end located on each arm (3) of the input shaft (11) of the mechanical gear (M), which is stationary in stationary supports (12), with each shaft (5) ending in panel (6) being rigidly fixed to but a guide gear (13) to which a drive sprocket (14) is fixed, fixed to one end located on each arm (3), an output shaft (15) of the mechanical gearbox M, which is stationary ( 16), wherein the inlet shaft (11) and the outlet shaft (15) are connected by means of a separate module (17), fixedly fixed to a given arm (3), and intended to realize different transmission relations between the orienting shaft (7) and the shafts (7). 5) ending with panels (6), with constant or variable angular velocity of transmitted motion ation, within a single rotation of the rotor (2), and at a constant angular velocity of the rotor (2), or the detached module (17) is designed to interrupt the movement between the orientation shaft (7) and the shafts (5) ending in panels ( 6), whereby it realizes only hourly rotations of the shafts (5) ending in panels (6), relative to a certain basic position thereof, wherein the mechanical gearbox M containing the detached module (17) generally provides a unidirectional rotation of the connected, orienting shaft (6). 7) and shafts (5) terminating with panels (6) relative to each other. 3. Wind energy conversion device according to claim 2, characterized in that the detached module (17) consists of a mechanism (33) for switching different gear ratios, a mechanism (34) for switching on and interrupting the movement between the orientation shaft. (7) and shafts (5) ending in panels (6), mechanism (35) for creating irregularities of the transmitted movement, module of influence (36) on the mechanism for creating irregularities, as well as a system for reading a certain position, in the process of rotating a device th, a certain arm (3) and a control system (Figure 6) of the separate module as a whole, or meeting only some of the nodes of the separate unit (17). A wind energy conversion device according to claim 1, characterized in that the panels (6) are made of a frame structure (125) fixed to the shaft (5), in which a web (126) is attached. A wind energy conversion device according to claim 1, characterized in that the device is made up of two rotating rotors relative to each other. A wind energy conversion device according to claim 1, characterized in that the base (1) is movable. 7. A method of using a wind energy conversion device, wherein in the process of rotating the device, the panels (6) make planetary motions about the axis of the device, characterized in that the planetary motion of the panels (6 ), are expressed in anticipatory and delayed deviations, of the rotations of the panels (6), of the given gear ratio relative to the rotation of the rotor, within one rotation of the rotor, or only in partial rotations of the panels (6), relative to a certain basic position on the panel lite (6), within one rotation of the rotor, Method for using a wind energy conversion device according to claim 7, characterized in that in planetary motion, the directions of the panels (6) conclude with the active plane an angle βί equal to half the angle (Xi of rotation of the wind). the corresponding arm (3), wherein the panels (6) are provided with a theoretically possible maximum width determined by the dependence 2.R.sin1 = _______ 2 δ cos— 4 where, I is the width of a panel (6), R is the radius of rotation of the device, and the angle δ is the angle between the axes of symmetry of two adjacent arms (3) of the device, whereby this planetary motion of the panels (6) applicable at a peripheral speed V _nep of the device less than the wind velocity U, such as maximum utilization of the power of wind, the device realized at the peripheral speed V _nep equal to one third of the wind velocity U, and with a ratio between the angle αί and an angle βί equal to 2: 1. A method for using a wind energy conversion device according to claim 7, characterized in that in the planetary motion, from Pos. 1 to E10, the directions of the panels (6) conclude with an active plane with an angle βί equal to half of the angle αί of rotation of the respective arm (3), with point D10 being the point at which the resulting velocity U _r coincides in the direction with the corresponding arm (3), whereby in the region around point D10 the panels (6) reorient to reaching the optimum angle of attack спрямо with respect to the direction of p the resultant velocity U _r , wherein from point D10 to point D11, the directions of the panels (6) maintain an optimal angle of attack ψί, with point D11 being the point at which the direction of the panels (6) maintains an optimal angle of attack ψι, and in at the same time realizes an angle βί equal to half of the angle αί, where from point E11 to point E12, the directions of the panels (6) conclude an angle βί equal to half of the angle αί, where point E12 is the point at which the direction of the panels (6) maintains an angle βί equal to half of the angle αί and at the same time realizes an optimal angle of attack ψ>, where from point E12 to point E13, the directions of the panels maintain an optimum angle of attack ψ ,, as point E13 is a point at which the resulting velocity U _r coincides in the direction with the corresponding arm (3), whereby in the section around point D13, panels (6) reorient to an angle βΐ equal to half the angle (Xi, and from point D13 to Pos.1, the directions of the panels (6) conclude an angle βί equal to half of angle (Xi , where this planetary motion of the panels is applicable at peripheral velocities V _nep of the device, less wind speed A method for using a wind energy conversion device according to claim 7, characterized in that in the planetary motion from Pos. 1 to E12, the directions of the panels (6) conclude with an active plane an angle βΐ equal to half angle (Xi, rotating the corresponding arm (3), point E12 being the point at which the direction of the panels (6) maintains angle βί equal to half angle (Xi, and at the same time realizes the optimum angle of attack ψ ,, relative to a direction of the resultant velocity U _r, at which point D12 to a point T.13, apravleniyata the panels maintain an optimum angle of attack ψι, as an T.13 is a point where the resultant velocity U _r coincides in direction with the respective arm (3), wherein in the area around the point T.13, the panels (6) realize a shift until the angle βί equal to half an angle (Xi, such as from point E13 to Pos. 1, the directions of the panels (6) conclude an angle βί equal to half an angle (Xi, whereby this planetary motion of the panels is applicable at peripheral velocities V device's _nep less than wind speed A method of using a wind energy conversion device according to claim 7, characterized in that in planetary motion, the panels maintain directions perpendicular to the active plane, wherein the panels (6) are theoretically maximum width determined by dependency I = 2.R.sin - where, 1 is the width of a panel (6), R is the radius of rotation of the device, and the angle δ is the angle between the axes of symmetry of two adjacent arms (3) of the device. 12. A method of using a wind energy conversion device according to claim 7, characterized in that, in planetary motion, in Poss. 1 and Pos. 2, the panels (6) occupy directions perpendicular to the active plane, as in the rest. part of the circumference, the directions of the panels conclude with the directions of the resultant velocity U _r , a certain angle of attack ψί, whereby this planetary motion of the panels is applicable at a peripheral velocity V _nep of the device less than the wind speed 13. The method of using a wind energy conversion device according to claim 7, characterized in that, in planetary motion, the panels (6) realize partial rotations about one basic position perpendicular to the respective arm, from Zone 1 to point E14. , the panels occupy a basic position, point E14 being a point at which an angle φ _2ί between the direction of the peripheral velocity V _nep and the direction of the resultant velocity U _r acquires a value equal to the optimal angle of attack ψί, from point E14 to point E15 , on ravleniyata the panels maintain an optimum angle of attack ψί, realizing a gradual swing in the direction of rotation of the rotor, as a point D15 is a point where the angle φ _2ί has reached a maximum value, at which point D15 to the dot D16, the directions of the panels maintain optimum Attack angle ψί, realizing a gradual rotation in the opposite direction of rotation of the rotor, point D16 being a point at which angle φ ₂ ί acquires a value equal to the optimum angle of attack ψί, and at that point the panel again occupies a basic position at which from points D16 D17 to a point, the panels occupy a basic position, as a point D17 is a point where the angle <ρ ₂ ί again acquires a value equal to the optimum angle of attack ψΐ, wherein from t.D17 to t.D18, the directions of the panels maintained optimum angle of attack ,ί, realizing a gradual rotation in the opposite direction of rotation of the rotor, with point D18 being the point at which angle φ ₂ ί has reached a maximum value, where from point D18 to point D19, the directions of the panels maintain an optimal angle of rotation. attack ψί, realizing a gradual turn in the direction of artene rotor, as a point D19 is a point where the angle φ ₂ ί acquires a value equal to the optimum angle of attack ψί, and at this point the panel again occupies a central position, at which point D19 to position 1, the panels occupy mainly a position where this planetary motion of the panels (6) is applicable at peripheral velocities V _nep of the device greater than the wind speed. 14. A method of using a wind energy conversion device, characterized in that the power generated by the rotation of the device is used as motor power to move the base of the device. 15. Mechanism for generating irregularity of the transmitted circular motion, characterized in that it consists of a mechanism for creating irregularity of the transmitted movement (35) and an impact module (36) on the mechanism for creating irregularity of the transmitted movement.