WO2009105848A2

WO2009105848A2 - Device for transformation of wind energy

Info

Publication number: WO2009105848A2
Application number: PCT/BG2009/000002
Authority: WO
Inventors: Valentin Notskov
Original assignee: Valentin Notskov
Priority date: 2008-02-26
Filing date: 2009-02-26
Publication date: 2009-09-03
Also published as: WO2009105848A3; BG110070A

Abstract

The device finds application in the transformation of wind energy. It comprises of a bearing base of a vertical rotor with symmetrically and equally set radial arms (3). At each of the arms' endings, is situated vertical spindle (5), finishing in its upper end with vertical panel (6). In the central part of the rotor, on bearing base is found directing spindle (7), ending with a wind pointer (8). Each spindle is connected with a directing spindle (7) by the relative mechanical gear. In rotation of the rotor mechanical gear registers rotations of panels with transferring ratio against the directing spindle at 1 :2 and 1 :1, with permanent and deviating rotation speed at permanent rotation speed of the rotor. The mechanical gear also transfers partial rotations of the panels around their initial positions. This secures different planetary motions of the panels depending on the speed and character of the wind.

Description

DEVICE FOR TRANSFORMATION OF WIND

ENERGY

AREA OF THE TECHNOLOGY

The invention regards to the mechanism with vertical rotating axis, used for the transformation of wind energy which is used for the creation of electricity, for powering water pumps and other mechanisms by wind force.

PRIOR CONDITION OF THE TECHNOLOGY

The popular mechanism for the transformation of wind energy (BG 1049U 1 ), which consists of a fixed base in which spins a vertical hollow rotor, which in the lowest part is connected with a lead away shaft. In the upper part the hollow rotor is formed like carousel with symmetrical and equilateral situated radiating arms, in which end at equal distances from the center is fixed a vertically oriented bearing sleeve. In every bearing sleeve rotates a vertical shaft, ending in its upper end with a vertical, symmetrical oriented in respect to the shaft panel. Centrally in the rotor is spun a vertically orienting shaft ending at its top end with a fixed orienting weather vane at which case each shaft is connected with the orienting shaft through mechanical gear with transmission ration of 1 :2. The panels are fixed to the shafts and through its gears are oriented in advance towards the arms so that one of the panels which is mounted perpendicularly to the directing weather vane arm, is oriented perpendicularly to the directing of the weather vane, and every next one is turned in respect to the prior to an angle cx=360/2n, where n is the number of the arms.

In the process of rotation of this mechanism the panels achieve planetary movement around the center of the device, and therefore do not use every possibility for increasing the coefficient of performance.

TECHNICAL ESSENCE OF THE INVENTION

The purpose of the invention is to utilize more efficiently the possibilities of increasing the coefficient of productivity by creating a device insuring the realization of appropriate planetary movement of the panels through which we derive a greater coefficient of productivity of the device.

To explain the essence of the invention, and for an easier and shorter description of the problem we are going to accept and label some characterizing parameters of the device in question as:

O - center of rotation of the rotor and of the described device- Fig. 15

Oi- center of rotation of the panels around its own axis-Fig. 15. The index i shows running configuration.

U- wind speed.

Vper- peripheral speed. Linear speed of the geometrical axis to the shaft ending with panels Fig.15.

Active plain- Vertical plain, perpendicular to the momentary position of the wind and passing through the center O of the device's rotation- Fig.15, as for the purpose of explanation the device is examined so that the wind acts on it with a given constant direction.

Radius of rotation of the device R - the radius of the circle which is described by the panels axis of rotation in respect of their own axis Oi, in respect to the center of rotation of the device O - Fig.15

Radius of coercion - segment through which a certain force creates a rotating moment in respect to a given center of rotation.

Pos. 1 - position 1 depends on the chosen direction of rotation of the device, and represents the point at which there is interception of, circumscribed circle by the axis Oi of the shaft ending with panels around the axis of the device O and the active plain, and in which point a precise direction of the peripheral speed Vper and the wind speed and direction U overlap- Fig.15

Pos.2 - position 2 depends on the chosen direction of rotation of the device and represents the point of interception, circumscribed circle by the axis Oi of the shaft ending with panels around the axis of the device O and the active plain, and in which point the direction of the peripheral speed Vper and the wind speed and direction U are with opposite directions - Fig.15

Angle (X/- the running angle for a given arm, determines the momentary turning of the given arm, compared with the active plain, where angle (X/ is viewed in the horizontal plain, described by the radius of rotation if, its initial arm is positioned in the interception line between the horizontal plain and the active plain, where the running arm is the viewed arm of the rotor, in respect to which rotates the given panel where angle (X/ developed around the center of rotation O of the device. For the arm crossing Pos. l angle (X is equal to zero degrees, where angle (X/ varies from zero to 360 degrees for one revolution of the device, after which it repeats- Fig.15

Angle βi- the running angle for a given panel, determines the momentary direction of a given panel in respect to the active plain, where angle βi is viewed in the same plain, in which we view angle (X/ and its initial arm is positioned on the interception line between the horizontal plain and the active plain and its running arm is the bearing of the panel. Angle βi develops around Pos.2 in the same direction in which angle (X develops and varies between zero to 180 degrees for one revolution of the device after which it is repeated-Fig.15.

Angle δ- this is the angle, locked between the axis of symmetry of the two adj acent arms of the rotating mechanism and it is equal to the result of the division of 360 degrees by the number of arms where angle δ is equal for all couples adj acent arms of the mechanism since the arms are situated symmetrically- Fig- 15. ^

Basic parameters for the device are the dimensions of the panels, where the width (length)- /, the hight of the panel- h, and the thickness of the panel.

The resultant speed Ur- the actual speed of wind coercion upon the center of a given panel, derived as a result from the vector of the wind speed U and the vector of momentary direction of the peripheral speed Vper, for the viewed location of the panel as a part of the circumscribed circle in the process of rotation of the device- Fig. 16-20.

Angle of action ψ/- the angle between the bearing of a given panel and the bearing of the resulting speed Ur for the given location of the panel in the process of rotation of the device. For simplicity of the presentation, the angle of action ψ* is considered the angle between this bearing of the panel and the bearing and the direction of the resulting speed Ur, where over the panel is created a lift force with direction creating a rotating moment in respect to the axis of the rotor, supporting the rotation of the rotor under the chosen direction of rotation of the device- Fig. 16-20. Angle φli- the angle between the bearing of the resultant speed Ur and the wind speed U- Fig.16-20.

Angle φ2i- the angle between the bearing of the resultant speed Ur and the peripheral speed Vper. Fig.16-20.

The task of the invention is solved, by creating a device for transforming wind energy- Fig. 1 & 2, which consists of a fixed base in which rotates a vertical hallow shaft, which is connected with lead away shaft by a mechanical gear, consisting of a fixed at the bottom end of the hollow shaft tooth gear. At its upper end the hollow shaft is shaped as a carousel with a symmetrically and equilateral placed radial arms, in which ends at equal distances from the center, is attached fixed vertically oriented bearing sleeve, in which is rotated a corresponding vertical shaft, concluding its upper end with a corresponding fixed to the shaft panel . Centrally in the carousel is rotated a vertical orienting shaft, concluding at its upper end with a fixed weather vane, where each shaft concluding with a panel is connected with orienting shaft through a mechanical gear, containing the differentiated module. The shafts concluding with panels through their own gears, in the process of rotation of the device, achieve their given from the gears running bearings in respect to the orienting shaft, in respect of the active plain, in respect also to the resultant speed Ur under which are completed corresponding planetary movements around the axis of the device.

The orienting weather vane always maintains the bearing of the orienting shaft, under which the direction of the orienting weather vane is perpendicular to the active plain. In a shift of the wind direction the orienting weather vane rotates the orienting shaft in such a way that it takes the same bearing in respect to the new wind direction and in respect to the now new active plain, as was previously the case. With this reorientation of the orienting shaft, the mechanical gear redirects the panels as well so that they take the same bearing in respect to the new active plain, which they had in respect to the previous.

According to the invention, the mechanical gear - Fig. 1 is made as a tooth gear, as over the orienting shaft is fixed an immovable leading tooth gear, with which for every arm and every shaft ending with a panel is engaged a driving tooth gear, where the driven tooth gears are fixed to one of the ends of the corresponding for the given arm, leading shaft of the mechanical gear, which spins on the fixed supports . With this to each shaft of a panel is fixed a following tooth gear with which is engaged a driving tooth gear, is established immovably over one of the ends of the corresponding for the given arm lead-away shaft of the mechanical gear, which rotates on a fixed supports . The lead-in shaft and the lead-away shaft are connected through a differentiated module permanently fixed to the given arm.

According to the invention, the differentiated module is designated to achieve a different transmitting ratios between the orienting shaft and the shafts ending with panels, with constant as well as variable angled speed of the transmitted motion, constituting in a constant or a variable angular speed of rotation of the shafts ending with panels, in a given areas of their orbit, under a constant angular speed of rotation of the rotor, and in the limits of one rotation of the rotor. Under this the panels create certain advancing of lagging variations in respect to the given transmission ratio, as in a given moment the panel has achieved larger angle of rotation, then the angle of rotation corresponding to the given transmission ratio, while in a certain following moment the panel is lagging under which creates smaller angle of rotation than the angle of rotation corresponding to the given transmission ratio. For the differentiated module is predicted to achieve and only partial rotations between the orienting shaft and the shafts ending with panels, which insures the rotations of the panels without complete rotations around their axis, and only partial rotation in one or other direction in respect to some base position of the panel. When the differentiated module achieves transmission ratio, then the differentiated module together with the remaining part of the gear, as a whole insure one way rotation of the connected shafts ending with panels and the orienting shaft one in relation to the other.

According to the invention, the differentiated module is made of a mechanism for shifting different transmission ratios, mechanism for engaging and disengaging of the motion between the orienting shaft and the shafts ending with panels, mechanism for developing irregularity of the transmitted motion, module for coercion of the mechanism for the creation of irregularity, as well as a system for accounting of the given position of the given arm in the process of rotation of the device, appropriate for shifting of another planetary movement, and system for controlling the differentiated module as a whole. When under the development of a given device is foretold the possibility for completion only for a part of the planetary motion of the panels, therefore in a differentiated module is completed only a part of its principles.

This way in the process of the rotation of the device, for more optimal use of the wind according to its speed and character the mechanical gear achieves different planetary movement of the panels.

According to the invention in the first planetary motion Fig.15, the bearings of the panels lock with the active plain βi equal to half angle OC/ which the corresponding arm locks with the active plain. The panels located in Pos. l take bearing, corresponding with the active plain and the panels located in Pos.2 take bearings perpendicular to the active plain.

So there is no overlapping of the panels in the process of rotation of the device in this planetary movement the panels are created with maximum theoretical possible width determined by the expression :

2.R.sin -

_/ _ 2 cos— 4

This planetary motion of the panels is applicable with peripheral speed Vper of the device less then the wind speed U, as maximal use of the wind power is used by the device at peripheral speed Vper, equal to one third of the wind speed U.

This planetary motion of the panels is most effective at the relation between angle at and angle βi equals to 2 : 1 .

This planetary motion of the panels achieve at the transmission ratio of the mechanical gear between the orienting shafts and the shafts ending with panels equal to 2 : 1 .

The device is characterized with a consistent coefficient of productivity since the forces are created through the drag of the panels, therefore it is vary appropriate for medium and high wind speeds . In part over the panels in Pos. 2 are created lift forces, which in the case create rotating moments around the axis of rotation of the rotor by means of small radii of coercion. In order to use these additional capabilities of the device the mechanical gear insures second planetary movement of the panels. The second planetary movement Fig.16 is also applicable with peripheral speed Vper of the device less then the wind speed, and is achieved with transmission ratio of the mechanical gear between the orienting shaft and the shafts ending with panels, equal to 2 : 1 , with consequent advancing and lagging rotations of the panels in regards to this transmission ratio.

Under the second planetary motion Fig.16 upon the rotation of the panels from Pos. l to point D l O the bearing of the panels lock angle βi equal to half from angle ai. Point DlO is a point in which the resultant speed Ur, coincides with the direction with the consequent arm of the rotor, which for the peripheral speed Vper equal to one third of the wind speed is achieved at angle ai equal to 70,53 degrees. In the sector around point D l O the panels achieve reorientation until reaching of optimal angle of action ψi. The reorientation is expressed in lagging deviation of the panel from its given transmission ratio .

From point DlO to DIl the orientation of the panels maintains optimal angle of action ψi. Where the panels produce reorientation, expressed in gradual advancing deviation of the panels, in regards to its assigned transmission ratio. This way in the viewed sector over the panels is achieved a substantial lift force creating a moment of rotation in regards to the rotors axis of rotation, through a large radius of coercion.

The point DIl is the point in which the panel maintaining an optimal angle of action ψi, at the same time achieves with the active plain angle βi, equal to half of angle ai.

From point DIl to point D 12 the bearings of the panels lock angle βi equal to half of angle ai. Point D12 is the point at which the panel maintaining with the active plain angle βi equal to half of angle ai, achieves an optimal angle of action ψi. From point D12 to D13 the bearings of the panels maintain an optimal angle of action ψi. Where as the panels achieve reorientation expressed in gradual advancing deviation of the panel, as a result of the given transmission ratio. In this sector over the panel is achieved substantial lift force creating a moment of rotation in regards to the rotors axis of rotation, through a large radius of coercion.

Point D13 is the point where the resultant speed Ur coincides in its bearing with the consequent arm of the rotor which for the peripheral speed of the device Vper equal to one third from the wind speed is achieved at angle ai equal to 289,47 degrees. In the section around point D13 the panel achieves reorientation until it reaches angle βi, equal to half of angle ai. The reorientation is expressed in a lagging deviation of the panel through the given transmission ratio.

From point D 13 to Pos. l the bearings of the panels lock angle βi equal to half of angle ai. This planetary movement is the most effective for use with comparatively low wind speeds up to around ten to twelve meters per second. At the panels situated behind the active plain the wind is already with turbulent character, which is typical for stronger winds. This way with the increase of the wind speed at a given moment the panels working through the creation of the lift force, turn out to be less ineffective in comparison with the case where it is used their resistance as result of the wind. This problem is solved with the third planetary movement.

The third planetary movement Fig.17 is also applicable at peripheral speeds Vper less than the wind speed and is achieved through transmission ratio of the mechanical gear, between the orienting shaft and the shafts ending with panels, equal to 2 : 1 , with the consequent advancing or lagging rotation of the panels for the given transmission ratio.

At the third planetary movement Fig.17 from Pos. l through Pos.2 to point D12, the bearings of the panels lock angle βi equal to half of angle ai.

From point D 12 to point D 13 the bearings of the panels achieve optimal angle of action ψi. Where as the panels achieve reorientation which is expressed in the gradual advancing deviation of the panel, as a result to its given transmission ratio . At this sector over the panel is achieved substantial lift force creating a moment of rotation around the axis of the rotors rotation through large radius of coercion.

At the sector around point D13, the panel achieves reorientation until it reaches angle βi equal to half of angle ai. The reorientation is expressed in a lagging deviation of the panel from its given transmission ratio.

From point D13 to Pos. l , the bearings of the panels lock angle βi equal to half of angle ai. This planetary movement is used effectively at average wind speeds from around 8 to 10 to about 14 to 16 meters per second. At high wind speeds the wind is more turbulent, also the mutual influence of the adj acent panels situated in front of the active plain is now substantial.

Upon the streamlining of the panels from the wind flow, and the creation of the lift forces, for the given cases we get a complicated picture, as taken into account the panels rotation around their own axis of rotation connected with the rotation of the device as a whole. From the other point of view the faces of the panels move with different moment speed, as the faces of the panels situated behind the active plain move with a smaller speed than the faces of the panels situated in front of the active plain this presumes that the viewed optimal angle of action ψi, locked between the bearings of the panels and the bearings of the resulting speed Ur acting in respect to the center of the panels, for the panels behind and in front of the active plain on which centers act equal resulting speed Ur, in reality would have different optimal angles of action ψi, in regards to the direction of the resulting speed Ur. Because of the complicated picture the optimal angle of action ψi, can be determined only with calculations attached with the experimental data.

With the planetary movement, at which in the process of rotation of the device the panels achieve rotations around its axis as they orient according to the wind, in sequence with one of its sides and then the other, the panels are created symmetrically in respect to the shafts to which they are fixed.

The fourth planetary movement Fig.18 is used for protection of the device from overloading. It is achieved as the mechanical gear insures transmission ratio between the rotation of the orienting shaft and the shafts ending with panels equal to 1 : 1 .

At the fourth planetary movement Fig.18 the panels maintain bearings perpendicular to the active plain. So that we do not obtain overlapping of the panels in the process of rotations of the device at this planetary movement the panels are created with maximal theoretically possible width derived from the expression:

/ = 2.R.sin-

2

The fifth planetary movement Fig.19 is achieved as the mechanical gear insuring transmission ratio between the rotation of the orienting shaft and the shafts ending with panels equal to 1 : 1 , with consequent advancing and lagging deviation according to this transmission ratio . In Pos.l the panels obtain bearings perpendicular to the active plain.

From Pos.l to point Dl O the bearings of the panels maintain as a result of the resultant speed Ur certain angles of action ψi as the panels achieve gradual advancing rotation as a result of the given transmission ratio.

From point Dl O to Pos.2 the bearings of the panels maintain certain angles of action ψi, as the panels achieve gradual lagging rotation as a result of the given transmission ratio.

When Pos.2 is achieved the panels obtain bearings perpendicular to the active plain.

From Pos.2 to point D13 the bearings of the panels maintain certain angle of action ψi, as the panels achieve gradual lagging rotation as a result of its given transmission ratio.

From point D 13 to Pos. l the bearings of the panels maintain according to certain angles of action ψi, as the panels achieve gradual advancing rotation according to the given transmission ratio.

As Pos.l is achieved the panels once again achieve bearings parallel to the wind.

This planetary movement of panels is applicable at peripheral speeds Vper of the device less than the wind speed, as its use is possible at very large wind speeds. At this case the point is not to achieve an optimal angle of action ψi but achieving small angles of action ψi where we have a small coefficient of resistance, and this way the device would take the pressure of the wind. At the same time even with not so great coefficient of lift force as we take into account the large wind speed there would be achieved substantial lift forces. As this planetary movement can be used as well to maintain the device in process of rotation to insure the possibility for achieving the following shifting to the other movements.

The sixth planetary movement Fig.20 is applicable at peripheral speed Vper larger than the wind speed and is achieved as mechanical gear achieves the movement between the orienting shaft and the shafts ending with panels, expressed only with partial rotations of the panels in one or other direction, according to one base position. For the panels created as flat plates or as wing symmetrical profile the main position bearing coincides with the direction of the peripheral speed Vper of the device.

From Pos.l to point D14 the panels take up the base position. Point D14 is the point at which angle φ2i between the direction of the peripheral speed and the direction of the resultant speed Ur achieves value equal to the optimal angle of action ψi.

From point D14 to point D15 the bearings of the panels maintain optimal angle of action ψi as the panels achieve gradual rotation in the direction of the rotors rotation.

Point D15 is the point at which angle φ2i has reached maximal value which for the peripheral speed of Vper equal to three times the wind speed U which is achieved at angle ai equal to 70,53 degrees, and the angle φ2i itself is equal to 19,47 degrees.

From point D15 to point D 16 the bearings of the panels maintain optimal angle of action ψi as the panels achieve gradual rotation in the opposite direction of the rotor's rotation.

Point D16 is the point at which the angle φ2i obtains value equal to the optimal angle of action ψi as at this point the panel once again obtains its base position.

From point D 16 through Pos.2 to point D17 the panels obtain the base position. Point D17 is the point at which angle φ2i once again achieves value equal to the optimal angle of action ψi.

From Point D17 to Point D18 the bearings of the panels maintain optimal angle of action ψi as the panels achieve gradual rotation in the opposite direction of the rotors rotation.

Point D18 is the point at which angle φ2i has reached its maximal value which for the peripheral speed Vper equal to three times the wind speed U is achieved at angle ai equal to 360-70,53 degrees, and the angle φ2i itself is equal to 19,47 degrees .

From point D18 to point D 19 the bearings of the panels maintain optimal angle of action ψi, as the panels achieve gradual rotation in the direction of the rotors rotation.

Point D19 is the point at which angle φ2i obtains value equal to the optimal angle of action ψi, as at this point the panel once again obtains its base position.

From point D 19 to Pos. l the panels obtain base position.

At this planetary movement the panels are created symmetrically or asymmetrically in regards to the shaft to which they are fixed, according to how much this planetary movement is combined with others. It is characterized with achieved large lift forces creating rotating moment in respect to the rotor, through small radii of coercion.

As aforementioned for the possible way of exact determination of the optimal angle of action ψi is valid and for this planetary movement.

The appropriate moment for reorienting from a given variation of planetary movement in the process of rotation of the device to other is when a given panel is located in Pos.2, at which for all planetary movements, the panels obtain the same position. For the complete reorientation a period of time is necessary, at which the rotor can achieve at least one complete rotation which would allow all panels to pass through Pos. 2 and so is achieved their shift to the following planetary movement.

Those planetary movements are used in combination or only part of them are implemented. As the most simplified example for implementation of the device is when the mechanical gear achieves only partial rotations of the panels as the device functions only at larger peripheral speed Vper than the wind speed U.

The function of the device is monitored by automatic control system (AC S), which detects the factors influencing the function of the device, it makes decisions and regulates the shifting from one planetary movement to another. For this purpose the ACS receives data for the wind speed and direction from the sensors located in over or around the device. The AC S receives data also for the rotation moment of the device and for the appropriate moment for achieving the shift to a given planetary movement.

According to the invention the orienting shaft could be propelled from a electro motor controlled by the ACS.

According to the invention the mechanical gear could be substituted so that for the propulsion of every panel is anticipated independent electro motor controlled by the AC S .

According to the invention the panels could be framed with a stretched sail within the frame. This execution would bring about increase of the absorbed from the device torque, since as the forces are absorbed through the friction of the panels, as the sail is stretched the area of the panel would increase, as upon the achievement of the lift force the panel would turn into an arched surface which always self orientates in an appropriate way.

According to the invention in order to lower the separation of the air flow as the lift forces achieve on the sides along the vertical edges of the panels could be attached elements for creation of turbulence at the peripheral layer.

According to the invention in order to limit the inductive friction a horizontal surface could be attached to the bottom and the top end of the panels .

If there is a need the arms could be insured against torsion as all couples of adj acent arms are connected in between them at their ends with insuring rods, which are fixed to the corresponding arms. If there is a large number of arms some of them do not have to be executed. In this case the insuring rods could be executed as circular sectors with radius equal to the radius of the devices rotation. The bearing sleeves for the missing arms are attached over the circular sectors, as they assume positions which they would have assumed in the case that these arms are executed. In the cases that the circular insuring rods substitute the missing arms, then the mechanic gear connecting the panels with the orienting shaft are attached over the adj acent arms and the corresponding circular implemented rod.

According to the invention to the bottom end of the arms could be attached vertical surfaces, which in the process of rotation of the device would increase the obtained torque. For this purpose, in this semicircle from the perimeter of the arms, which is located towards the side of Pos. l , these surfaces assume bearing parallel to the arm to which they are attached, and therefore in the other semicircle from the perimeter of the arm, which is located towards the side of Pos.2, these surfaces assume bearing parallel to the wind direction. These surfaces are applicable with devices functioning at peripheral speed Vper less than the wind speed, as besides the created additional torque they maintain the device in continual rotation with the existence of the wind which allows for consequent shifting.

According to the invention the device could be implemented with two rotors rotating in opposite directions.

According to the invention the base could be executed with the possibility for movement, as the obtained from the rotation of the device torque could be used for moving the base.

CLARIFICATIONS TO THE ATTACHED FIGURES

Fig. l . Vertical section through the device powered and oriented only from the wind speed and direction.

Fig.2. Top view of the device shown in Fig. l .

Fig.3. Diagram of an option of the differentiated module with illustrated diagram of the mechanism for the shifting of different transmission ratios, mechanism for creating of irregularity of the transmitted movement, and module for influence over the mechanism for creation of irregularity.

Fig.4. Diagram of the mechanism for engaging and disengaging of the transmitted movement.

Fig.5. Diagram for the creation of pendulum like motion of the swinging axis and diagram of the influential arm.

Fig.6. System for control of the differentiated module as a whole.

Fig.7. Diagram for partial case of execution of the differentiated module, where the module for influence over the mechanism for irregularity of the movement is executed with independent propulsion.

Fig.8. Diagram for partial case of execution of the differentiated module, for achieving of planetary movement only with partial rotation of the panels.

Fig.9. Option of the device, where the orienting shaft is powered by electro motor.

Fig.10. Option of the device, where every shaft of a panel is powered from an independent electro motor.

Fig.11. Example for creating of turbulent peripheral layer.

Fig.12. Diagram of the additionally attached surfaces under the arms of the device.

Fig.13. Option of the device executed from two rotors rotating in opposite directions.

Fig.14. Option of the device executed with movable base.

Fig.15. Schematic view of the device illustrating geometrical and mechanical parameters of the device.

Fig.16. The planetary movement of the panels with a combined creation of driving forces.

Fig.17. The planetary movement of the panels with a combined creation of driving forces.

Fig.18. Planetary movement of the panels at the overload defensive option.

Fig.19. Planetary movement of the panels only for the creation of lift forces.

Fig.20. Planetary movement of the panels achieved only with partial rotation of the panels.

EXAMPLARY IMPLEMENTATION OF THE INVENTION

The device for transformation of wind energy is implemented Fig. l , as in the fixed base 1 , rotates a vertical hollow rotor 2. In its bottom part the rotor 2 is connected with a lead-away shaft 18, through a fixed to its bottom end tooth gear 19, connected with a fixed lead-away shaft 18, tooth gear 20. At its upper end rotor 2 is shaped as carousel with four symmetrical and equilateral located radial arms 3.

In the ends of the arms 3 , at equal distances from the center is fixed a vertical orienting bearing sleeve 4, in which rotates corresponding vertical shaft 5 , ending in its upper end with a corresponding fixed to the shaft 5 , panel 6. Centrally in the rotor is spun a vertical orienting shaft 7 ending in its upper end with a fixed orienting weather vane 8.

Every shaft 5 is connected with the orienting shaft 7 through a mechanical gear M, which is executed as a tooth gearing. Over the orienting shaft 7 is fixed one leading cone shaped tooth gear 9, with which for each arm 3 is meshed a leading cone shaped tooth gear 10 a piece, which are fixed to one end with the corresponding for the given arm 3 , lead-in shaft 1 1 of the mechanical gear M, spun in the immovable supports 12. On each shaft 5 is fixed a led cone shaped tooth gear 13 , as each one of them is meshed with a propelling cone shaped tooth gear 14, fixed to one end of the corresponding for the given arm 3 lead-away shaft 15 of the mechanical gear M, which rotates on supports 16.

The lead-in shaft 1 1 and the lead-away shaft 15 are connected through a differentiated module 17, permanently established to the given arm 3. The differentiated module 17 is made of mechanism 33 for shifting of the different transmission ratios, mechanism 34 for engaging and disengaging of the movement between the orienting shaft 7 and shafts 5 ending with panels 6, mechanism 35 for creating of irregularity of the translated motion, module for influence 36 over the mechanism for the creation of irregularity, as well as a system for accounting of a certain rotation of the given arm 3 in the process of rotation of the device, and system for control Fig.6 of the differentiated module 17 as a whole.

The mechanical gear M together with the differentiated module 17 as a whole insures one way rotation of the connected orienting shaft 7 and shaft 5 ending with panel 6, one in accord with the other.

The process of rotation of the device is monitored from an automatic control system ACS 21 , where over the rotor, to the orienting shaft 7 for each arm 3 is attached a sensor 22, monitoring the given moment of rotation between the orienting shaft 7 and the rotor, as the sensor 22 is connected with the AC S 2 1 . Over the orienting weather vane 8 is attached sensor 23 monitoring the wind speed and direction as sensor 23 is connected with ACS 2 1 .

The mechanism 33 for shifting of the different transmission ratios Fig.3 designated for the transmission ratios 2 : 1 and 1 : 1 , between the orienting shaft 7 and the shafts 5 , is executed from two parallel shafts . The first shaft is the driving shaft 38 which coincides with the lead-in shaft 1 1 of the mechanical gear M. The second shaft is the driven shaft 40, which rotates on the supports 4 1 and coincides with the constantly rotating shaft 5 1 , from the mechanism 34 for engaging and disengaging of the motion.

To the driving shaft 38 are fixed two tooth gears 42 and 43 , which are constantly meshed in couples with two other tooth gears 44 and 45 , freely rotating over the driving shaft 40. The freely rotating tooth gears 44 and 45 are executed with steps 46 and 47 which are turned one against the other, as for each step 46 and 47 is formed a corresponding opening (slot) 48 and 49. Between the steps 46 and 47 of the freely rotating tooth gears 44 and 45 , over the driving shaft 40 with capability for actual axial rotation of the shaft but without overturning in respect to the shaft is established a grooved sleeve 50.

From both sides of the grooved sleeve 50 are formed teeth 5 1 with rounded tips and cross-dimensions corresponding to the dimensions of the channels (the grooves) 48 and 49. The length of the so formed dual tooth 5 1 and the distance between steps 46 and 47 are coordinated so that upon the movement of the grooved sleeve 50 and meshing of tooth 5 1 with channel 49 of one of the steps 47, then in the moment of meshing, the other tooth to have not mashed completely from channel 50 of the other step 46. The couples constantly meshed teeth gears in combination with the rest of the mechanical gear, when meshing with the grooved sleeve 50 with one or the other available rotating tooth gears 44 and 45 , achieve transmission ratio between the orienting shafts 7 and shafts 5 equal to 2 : 1 and 1 : 1 .

On the outside of the grooved sleeve 50 is formed step 150 which rotates in shifting lever 52 for the grooved sleeve, which is propelled by the control system Fig.6 of the differentiated module 17 as a whole .

Mechanism 34 for engaging and disengaging of the movement Fig.4 between the orienting shaft 7 and shafts 5 , consists of two coaxial shafts . One of the shafts is the constantly rotating shaft 53 , which coincides with the driven shaft 40 from the mechanism 33 for engaging and disengaging the transmission ratios. The other shaft is the not constantly rotating shaft 54 which rotates in the supports 56 and 57 as to its end is fixed receiving cone shaped tooth gear 55 , from the mechanism 35 for creation of the irregularity of the motion. With their close ends the two shafts rotate amongst each other as the end of one of the shafts is executed as step 58, which rotates in the slot 59, formed in the end of the other shaft.

In their close ends the shafts are executed with the same number and dimension of the outside grooved channels 60 in which with the possibility for axial movement is meshed a feathered sleeve 61 . The feathered sleeve 61 consists of a sleeve to which from the side and in its depth are build up keys 62 with rounded ends 63 and corresponding by number and dimension the grooved channels 60, as the outside dimension of the keys 62 is larger than the diameters of the shafts 53 and 54.

On the closer to the feathered sleeve 61 support 56, are formed inside grooved channels 64 - The length of the keys 62 and the distance from the support 56 to the end of the not constantly rotating shaft 54, are coordinated so that in the moment of meshing of one end of the grooves 62 with the keys 64 of the support 56, where it is achieved blocking of the not constantly rotating shaft 54, from the other end of the keys 62 so that it has not meshed completely from the grooved channels 60 of the constantly rotating shaft 53.

The mechanical gear M in combination with the differentiated module 17 are meshed so that the grooved channels of both shafts 53 and 54 and of the support 56 coincides with angle ai of the arm 3 , equal to 180 degrees .

On the outside of the feathered sleeve 61 is formed step 65 , which rotates in a shifting lever 66 for the feathered sleeve, driven by the control system Fig.6 of the differentiated module 17 as a whole.

Mechanism 35 for creating of irregularity of the transmitted movement Fig.5 between the orienting shaft 7 and shafts 5 , consists of incoming 55 and outgoing 67 cone shaped geared tooth gears, which are coaxial with the same parameters and are located at certain distances, facing one against the other. The incoming 55 cone shaped tooth gear is attached to the not constantly rotating shaft 54, from the mechanism 34 for engaging and disengaging of the movement. The outgoing 35 cone shaped tooth gear is fixed to the outgoing shaft 15 of the mechanical gear M.

Simultaneously with the two cone shaped tooth gears 55 and 67 is meshed third swinging cone shaped tooth gear 68, as the axis of the three mutually meshed cone shaped tooth gears 55 , 68 and

67 intercept in one point Dl . The swinging cone shaped tooth gear

68 is fixed over the swinging axis 69 with the possibility for pendulum like movement around point Dl .

The swinging axis 69 is implemented as passing through the swinging cone shaped tooth gear 68 and in one of its ends rotates in holder 70, located between the incoming and outgoing tooth gears 55 and 67 and attached with a socket-joint to the immovable support 71 , as the geometrical axis of the socket-j oint 72 coincides with the axis of the incoming 55 and the outgoing 67 cone shaped tooth gears. The swinging axis 69 is powered from the arm for influence 73 , of -the module 36 for influence over the mechanism 35 for creation of irregularity.

At the immovably established incoming cone shaped tooth gear 55 , by the pendulum like movements of the swinging axis 69, the swinging cone shaped tooth gear 68 turns on the incoming tooth gear 55 , as with this brings about in motion the outgoing cone shaped tooth gear 67 expressed in partial rotations in one direction or other, in respect to one base position of the swinging axis 69. By the rotating incoming tooth gear 55 the motion which creates the swinging tooth gear 68 compounds or lessens the transmitted movement, expressed in faster or slower rotations of the outgoing tooth gear 67, compared with a given transmission ratio. The base position of the swinging axis 69 corresponds to the position which is taken by the panels in Pos.2.

The module 36 for influence over the mechanism for creation of irregularity 35 , implemented for achieving of three planetary movements consists of, receiving shaft 74, which rotates on supports 75. The receiving shaft 74 is connected with mechanical gear M, as for the incoming shaft 1 1 of the mechanical gear M is fixed cone shaped tooth gear 27, which is meshed with other cone shaped tooth gear 28, fixed to one end of the parasite shaft 29, which rotates in support 30. To the other end of the parasite shaft 29 is fixed cone shaped tooth gear 31 , which is meshed with another cone shaped tooth gear 32 fixed to one of the ends of the receiving shaft 74. Or the receiving shaft 74 is connected directly with the orienting shaft 7, through a mechanical gear, as the gears in both cases insures transmission ratio between the orienting shaft 7 and the receiving shaft 74 equal to 1 : 1 .

Over the receiving shaft 74 are fixed three cylindrically shaped humps 76. Immediately next to shaft 74 and with the possibility for movement coaxially of shaft 74, in fixed supports 77 is implemented slider 78. Over the slider 78 coaxially to shaft 74, against each hump 76 are formed directing slots 24, in which with possibility for movement against the humps are implemented engaging levers 79, with rounded from the side of the humps end.

From the opposite of the receiving shaft 74 of the slider 78, the engaging levers 79 are executed with heel 80, as between the heels 80 and the slider 78 over every engaging lever 79 threaded an elastic element 8 1 , exercising force in the opposite of the shaft 74 direction. From this end of the engaging levers 79 are limited by the positioning lever 84, which moves on fixed supports 83 in direction coaxial of the receiving shaft 74, at which in this end the engaging lever 79 are executed with rolls 82.

The hump channels are executed so that at least in one moment of the rotation of the receiving shaft 74, the distances between the hump channels in their part located against the engaging lever 79, corresponds to the distances between the engaging levers 79. This moment coincides with the moment at which a given arm has rotated to angle ai equal to 180 degrees . The positioning lever 84 is executed with three steps 26, which upon the movement of the positioning lever 84 pressure a given engaging lever 79 to the corresponding humped channel 25 , as they release the rest of the engaging levers 79. The dimensions of the engaging levers 79 and the dimensions between the steps 26 of the positioning lever 84 are considered so that upon one shifting movement of the engaging lever 84, to be achieved engagement only of one engaging lever 79 to the corresponding humped channel 25. The height of the steps 26 and the forming of the path between them are considered so that in the moment of engagement of a given engaging lever 79 to the corresponding humped channel 25 , from the corresponding engaging lever 79 which disengages, so that it does not mash completely from the corresponding humped channel 25.

To the slider 78 is fixed an influencing arm 73 , which drives the swinging axis 69 from the mechanism 35 for the creation of irregularity. The influencing arm 73 is executed from two parts, as in its end it ends with a fork 1 18, which wraps around the swinging axis 69 the fork 1 18 rotates to the rest of the arm 120 through a formed step 1 19 of the fork 1 18 and formed opening 121 to the rest of the arm 120.

The system 37 for accounting of a given position of the given arm 3 in the process of rotation of the device, consists of sensor 22, which gives signal to ACS 21 , when a certain arm 3 achieves angle of rotation equal to 180 degree.

The system of control of Fig.6 of the differentiated module 17 as a whole, for achieving the three planetary motions of the panels, and is executed with one common propulsion element, consists of a slate 91 , which slides on fixed supports 92, and to which are fixed the shifting lever for the grooved sleeve 52, and the shifting lever for the feathered sleeve 66. To the side of slate 91 in a fixed support 93 , with possibility for rotation around it rotates angled segment 94, as one of the arms of segment 94 is meshed in the rotating to the slate heel 95 with possibility for sliding in the heel 95 , and the other arm of segment 94 is meshed in the rotating towards positioning lever 84 heel 96, with possibility for sliding within it.

The slate 91 is powered from an electro motor 100 through a fixed to the slate 91 arm 97 on which is created a cut out 98 meshed to the driving pin 99 of the electro motor 100. To the electro motor 100 is attached a sensor 101 , against which are fixed three sensors 102, one for each functioning positions of the slate 91 , as the sensors 102 are placed on necessary angular shift in respect to the electro motor 100, and are connected to the ACS 21 .

As an exemplary implementation of the differentiated module 17 is executed with a possibility for accomplishing three planetary movements of the panels from which the first planetary movement, is the case where the panels 6 achieve only partial deviation from the given base position. The grooved sleeve 50 is meshed to the bigger freely rotating tooth gear 44, in which case between the orienting shaft 7 and the shafts of the panels 6 is achieved transmission ration 2 : 1 . The feathered sleeve 61 is meshed to the fixed support 56 as the movement to mechanism 35 for a irregularity is disengaged. The humped channel 25 to which in the moment is meshed the engaging lever 79 is created with the corresponding humped profile, as the movement of the slider 79 is achieved, as well as the deviation of the swinging axis 69.

For achieving of the second planetary movement, under which the directions of the panels 6 maintain angles βi in respect to the active plain equal to one half angle ai with corresponding advancing and lagging rotations of the panels, thus achieving the later shifting for each arm 3 , passing through Pos.2 limited by one revolution of the rotor 2. The feathered sleeve 61 disengages from the unmovable support 56 and meshes the constantly rotating shaft 53 and the not constantly rotating shaft 54 one to the other, thus achieving transmission of the rotation motion to the panels . The humped channel 25 to which in the moment of meshing with engaging lever 79 is created with the corresponding humped profile, and achieves shifting of slider 78, as well as deviation from the swinging axis 69. The length of the teeth 5 1 of the grooved sleeve 50 and the depth of the cut out 50 of the step 46 of a larger freely rotating tooth gear 44, are coordinated so that with this shift of the grooved sleeve 50 meshing is not achieved, from the bigger freely rotating tooth gear 44, and the meshing to the smaller freely rotating tooth gear 45 , where the transmission ratio between the orienting shaft 7 and shafts 5 , continues to be equal to 2 : 1 . For achieving of the third planetary movement of the panels 6, which is the overload defensive option, where the panels 6 maintain directions, perpendicular to the active plain, for the consequent for each arm 3 shift, the grooved sleeve 50 disengages from the large freely rotating tooth gear 44 and meshes to the smaller 45 , thus between the orienting shaft 7 and the shafts 5 , is achieved transmission ratio 1 : 1 . The humped channels 25 to which in this moment is meshed shifting lever 79 is created as a symmetrical cylindrical channel, and does not achieve shifting of the slider 78, and deviations of the swinging axis 69.

As an example of the execution of Fig.8, the differentiated module 17 is created with possibility for achieving, only of planetary movement of the panels, where the panels 6 achieve only partial deviations from the given base position. The receiving shaft 74 from the mechanism 36 for influence and the incoming shaft 1 1 of the mechanical gear M are executed as one common shaft, over which is fixed one cylindrical hump 76. The incoming cone shaped tooth gear 55 from the mechanism 35 for creating of irregularity is established to the immovable support 90, as the swinging axis 68 is meshed directly with the humped channel 25.

As an example of execution Fig.7, the differentiated module 17 is executed, as a constant rotating shaft 53 from the mechanism for engaging and disengaging 34 and the incoming shaft 1 1 of the mechanical gear M, are executed as one common shaft. The receiving cone shaped tooth gear 55 is fixed over the not constantly rotating shaft 54. Mechanism 36 for influence is executed, as the influential arm 73 , is fixed to the axis of the immovably placed electro motor 37.

As an example of execution of the device Fig. 9 the orienting shaft 7 is driven from the electro motor 1 13 connected with the ACS . Where the orienting shaft 7 is executed as a hollow shaft 207, as to its upper end is fixed a leading cone shaped tooth gear 9. At the lower end of the orienting shaft 7 is fixed a tooth gear 1 1 1 , which is meshed with another tooth gear 1 12, fixed to the axis of the electro motor 1 13. In the orienting shaft 207 rotates weather vane rod 1 14 established immovably, as to the upper end of the weather vane rod 1 14, is established sensor 23 , measuring the wind speed and direction, and connected with AC S 21 .

As an example of execution of the device Fig.10, shafts 5 are driven by independent for each arm 3 electro motors 1 1 5 connected with ACS 2 1 . On each arm 3 is established to each one electro motor 1 15 immovably. To the axis of each electro motor 1 1 5 is fixed a tooth gear 1 16 meshed with a fixed to the corresponding shaft 5 tooth gear 1 17. In rotor 2 rotates the weather vane rod 1 14.

As an example of execution Fig.11 panels 6 could be created from an immobile established to shaft 5 framed structure 125 , in which is attached sail 126.

In order to create a turbulent border layer Fig.11 is used circular segment 13 1 , which is in essence a vertical body, established in length of the vertical edge of the panel 6, and is fixed immovably to panel 6 by supports 137. In vertical section the circumference like segment is formed by the interception of two circumferences 132 and 133 , as the centers of the circumferences lays on the line determining the direction of the panel 134, at some distance one from another. The center of the circle forming the inside part 133 of the segment 13 1 is with a smaller radius and is placed closer to the face 135 of the panel 6. The so formed edges 136 of the segment 13 1 overlap a given part of panel 6.

This way with the streamlining of panel 6, at point D2 is created larger pressure and the air enters through this zone in segment 13 1 , as upon exit through the zone at point D3 , it is very turbulent and it creates turbulence at the border layer at the face of the panel.

For the creation of turbulent border layer as well as improvement of the clinging of the flow to the back of the panel 6, internally of the segment 13 1 opposite of faces 135 of panels 6 are mounted wedge shaped feathers 140. Internally for the segment 13 1 and symmetrically in regards to it are established vertical axis 139, to which with possibility for rotation around the axis 139, are fixed wedge shaped feathers 140. The wedge shaped feathers 140 are connected with the inner part of the segment with elastic elements 141 , which exert force in direction towards the wedge shaped feathers in such a way that support the wedge shaped feathers attached to the edges 136 of the segment 13 1 . The distance from the vertical axis 139 to the face 135 of the panel 6 is considered in such a way that it insures the overturning of the wedge shaped feathers 140 around the vertical axis 139.

This way with the streamlining of panel 6 the created in point D2 greater pressure pushes against and opens the consequent wedge shaped feather 140 and the air enters through this zone into segment 13 1 through a larger opening as on its exiting from the segment through the zone at point D3 it creates even more turbulence which creates more turbulence in the border layer where as it clings to the edge 136 of segment 13 1 , with its own contour wedge shaped feather 140 continues the outer contour 132 of segment 13 1 , to a greater proximity of the contour of the panel, as it prevents the separation of the airflow at its beginning at the streamlining of the very segment 13 1 .

As an example of execution of the device Fig. l , to the upper and lower end of the panels 6 are attached horizontal plains 142, for decreasing of the inductive resistance.

As an example of execution of the device Fig.12, under the arms 3 of the device are attached additional surfaces which are composed of immovably positioned to the lower end of the arms 3 vertical supports 128 to which with possibility for rotation around the supports 128 are positioned vertically oriented plains 129. For every vertical plain 129 under the given arm 3 of the rotor is immovably attached a controller of the closing 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 plain 129. In vertical position the controller of closing 130 overlaps the upper end of the vertical plain 129.

As for example of execution Fig.13 the device is executed with two rotating one against the other rotors where in the orienting shaft 207 is rotated a vertical hollow rotor 202, which is connected with the lead-away shaft 218 through a fixed to its lower end tooth gear 219, connected with a fixed to the lead-away shaft 21 8, tooth gear 220. In its upper part the rotor 202 is shaped like a carousel with symmetrical and at the same distances established radial arms 203 , in which end at equal distances from the center is attached immovably one for each vertical oriented bearing sleeve 204, in which rotates the consequent vertical shaft 205, ending in its upper end with the consequent, fixed to the shaft 205 panel 206. Centrally in the rotor 202 is rotated a vertical orienting shaft 227, ending in its upper end with a fixed orienting weather vane 8. Every shaft 205 of panel 206 is connected with a orienting shaft 227 through mechanical gear M.

Towards the lower end of the orienting shaft 227, is fixed tooth gear 23 1 . On the lower end of the orienting shaft 207, is fixed a tooth gear 230. The tooth gear 23 1 and tooth gear 230, are connected through a mechanical chain 232, which achieves transmission ratio between the orienting shaft 227 and the hollow orienting shaft 207, equal to 1 : 1 and one way rotation of the connected shafts one in respect to the other.

As an example for execution of the device Fig. 14 the base 1 is executed with a possibility for movement, which as it is established over four moving wheels 240. The moving wheels 240 are connected in pairs with axis 241 , which rotates on supports 242 formed in the base 1 . The axis 240 of one pair of moving wheels 240 is connected with the rotor 2 through a mechanical gear, which at the bottom end of the rotor 2 is fixed to a cone shaped tooth gear 243 , which is connected with the fixed to the axis 241 , cone shaped tooth gear 244.

FUNCTION OF THE DEVICE

Under the influence of the wind, the orienting weather vane together with the orienting shaft, to which it is mounted, rotates and it orients in the direction of the wind, as with each change of the wind, the orienting weather vane and the orienting shaft, reorient and take this new direction in respect to the new direction of the wind, as it was in respect to the previous direction.

In the process of rotation of the device, the panels achieve given planetary movements around the axis of the rotor, given to them from the mechanical gear, connecting them with the orienting shaft, as with that maintains a given direction in respect to the wind direction. Upon the change of the direction of the wind, the reorienting of the orienting shaft, through mechanical gear, is passed on to the panels, upon which they take the same bearings in respect to the new direction of the wind, as they head in respect to the previous.

The planetary movements and their characteristics are explained in the technical essence of the invention. The mechanism for creating of the planetary movements, is explained in the examples for executing of the device.

The rotation movement of the rotor, through the lead-away shaft is passed to the device after the next for the transformation of wind energy.

Claims

PATENT CLAIM

1. The device for transformation of wind energy, consisting of base ( 1 ), in which rotates hollow rotor (2), which in its upper end is executed as carousel with symmetrical and equal distances radial arms (3), in which ends at equal distances from the center is mounted immovably one vertical oriented bearing sleeve (4), in which rotates corresponding vertical shaft (5), ending at its upper end with corresponding fixed to the shaft (5) panel (6), characterized with centrally in rotor (2) is rotated vertical orienting shaft (7) ending at its upper end with fixed orienting weather vane (8), or the orienting shaft (7), is connected with electro motor ( 1 13), where as the panels (6) are executed symmetrically or unsymmetrically in respect to the shafts (5), as each shaft (5) is connected with the orienting shaft (7) through a gear, or every shaft (5) is connected with electro motor ( 1 15), where as the base ( 1 ) is immovably established, as rotor (2) is connected with lead-away shaft ( 18), through a fixed to the lower end of the rotor (2) tooth gear ( 19), connected with the fixed to the lead-away shaft ( 18), tooth gear (20) where the function of the device is monitored from the automatic control system ACS (21 ), where along the vertical edges ( 135) of the panels (6) are attached elements ( 13 1 ), for creation of turbulent border layer, in which case in the upper and lower end of the panels (6), are attached immovably plains ( 142), for decreasing of the inductive resistance where to the lower end of the arms (3), are attached additional surfaces ( 129).

2. The device for transformation of wind energy according to claim 1 , characterized by the fact that the gear is executed as a mechanical gear M, containing differentiated module ( 17), as over the orienting shaft (5) is attached immovably a leading tooth gear (9), with which for each arm (3), is connected a driven tooth gear ( 10), fixed to one of the ends of the placed over each arm (3) incoming shaft ( 1 1 ) of the mechanical gear (M), which rotates on unmovable supports ( 12), with this on each shaft (5) ending with panel (6) is fixed a driven tooth gear ( 13), with which is connected a driving tooth gear ( 14), attached immovably to one end of the place over each arm (3), outgoing shaft ( 15) of the mechanical gear M, rotating on immovable supports ( 16) where the incoming shaft ( 1 1 ) and the outgoing shaft ( 15) are connected through differentiated module ( 17), immovably established to the given arm (3), and is intended to achieve different transmission ratios between the orienting shaft (7) and shafts (5) ending with panels (6), with constant or variable angular speed of the transmitted movement, limited to one revolution of the rotor (2), and at a constant angular speed of the rotor (2), or the differentiated module ( 17) is intended to disengage the movement between the orienting shaft (7) and shafts (5) ending with panels (6), thus achieving partial rotations of shafts (5) ending with panels (6), in respect to a given base position, where the mechanical gear M contains the differentiated module ( 17), as a whole insures one way rotation of the connected, orienting shaft (7) and shafts (5) ending with panels (6), one in respect to the other.

3. The device for transformation of wind energy according to claim 2, characterized by differentiated module ( 17) which consists from mechanism (33) for shifting of different transmission ratios, mechanism (34) for engaging and disengaging of the movement between the orienting shaft (7) and shafts (5 ) ending with panel (6), mechanism (35 ) for creation of irregularity of the transmitted movement, influencing module (36) over the mechanism for creation of irregularity, as well as a system for accounting of certain position, in the process of rotation of the device, of a given arm (3 ), and system for control Fig.6 of the differentiated module as a whole or only part of the connections of the differentiated module ( 17) are executed.

4. The device for transforming of wind energy according to claim 1 characterized with the fact that the panels (6) are executed from a fixed to the shaft (5) framed structure ( 125 ), in which is stretched sail ( 126) .

5. The device for transforming of wind energy according to claim 1 , which is characterized with that, the device is executed from two rotors spinning in opposite directions one in respect to the other.

6. The device for transforming of wind energy according to claim 1 , which is characterized with that the base ( 1 ) is executed with possibility for movement.

7. Method for the use of the device for the transformation of wind energy, exhibited in that in the process of rotation of the device, the panels (6) achieve planetary movement around the axis of the device, characterized by the planetary movement of the panels (6), expressed in advancing and lagging deviations, of the rotations of the panels (6), from the given transmission ratio in respect the rotors rotation limited by one rotation of the rotor, or only in partial rotations of the panels (6) in respect to a given base position of the panels (6), limited by one rotation of the rotor.

8. Method for the use of the device for transformation of wind energy, according to claim 7, characterized with that upon the planetary movement, that the bearings of panels (6) lock with the active plain angle βi, equal to half of angle ai of the rotation of the corresponding arm (3), where the panels (6) are created with theoretically possible maximal width determined by the expression:

where / is the width of the given panel (6), R is radius of rotation of the device, angle δ is the angle between the axis of symmetry of two adjacent arms (3) of the device at which this planetary movement of the panels (6) is applied at peripheral speed Vper of the device, smaller than the wind speed U, as the maximal use of the torque of the wind, the device achieves at peripheral speed Vper equal to one third of the wind speed U, at relation between angle ai and βi, equal to 2 : 1.

9. The method for using of the device for transforming of wind energy, according to claim 7, characterizes with that, upon a planetary movement from Pos. 1 to point D l O, the bearing of the panels (6) lock with the active plain angle βi, equal to half of angle ai of rotation of the corresponding arm (3), as point D l O is the point at which the resultant speed Ur coincides in bearing with the corresponding arm (3), where in the sector around point D l O, the panels (6) achieve reorientation until they reach the optimal angle of action ψi, in respect to the bearing of the resultant speed Ur, where from point D l O to point D I l , the bearing of the panels (6) maintain optimal angle of action ψi, as point D I l is the point at which the bearing of the panels (6) maintain optimal angle of action ψi, and at the same time achieves angle βi, equal to half of angle ai, at which from point D I l to point D 12 the bearing of the panels (6) lock angle βi, equal to half of angle ai, as point D 12 is the point at which the bearing of the panels (6) maintains angle βi, equal to half of angle ai, and at the same time achieves optimal angle of action ψi, where as from point D 12 to point D 13 , the bearing of the panels maintain an optimal angle of action ψi, as point D 13 is the point at which the resultant speed Ur coincides in bearing with the consequent arm (3 ), at which in the segment around point D 13 , the panels (6) achieve reorientation until reaching of angle βi, equal to half of angle ai, as from point D 13 to Pos. l , the bearings of the panels (6) lock angle βi, equal to half of angle ai, at which this planetary movement of the panels is applicable at peripheral speed Vper of the device, smaller than the wind speed.

10. Method for the use of the device for transforming of wind energy according to claim 7, characterized with that, upon planetary movement, from Pos. l to point D 12, the bearing of the panels (6) lock with the active plain angle βi, equal to half of angle ai, of rotation of the consequent arm (3), as point D 12 is the point at which the bearing of the panels (6) maintain angle βi, equal to half of angle ai, and at the same time achieves an optimal angle of action ψi, in respect to the bearing of the resultant speed Ur, at which from point D 12 to point D 13 , the bearing of the panels maintain optimal angle of action ψi, as point D 13 is the point at which the resultant speed Ur coincides in bearing with the consequent arm (3 ), at which in the sector around point D 13 , the panels (6) achieve reorientation until reaching angle βi, equal to half of angle ai, as from point D 13 to Pos. l , the bearings of the panels (6) lock angle βi, equal to half of angle ai, at which this planetary movement of the panels is applicable at peripheral speeds Vper of the device, smaller than the wind speed.

1 1 . Method for the use of the device for transformation of wind energy, according to claim 7, characterized with that upon a planetary movement, the panels maintain bearings perpendicular to the active plain, where as the panels (6) are created with theoretically maximal width, determined by the expression:

/ = 2.R.sin-

where / is the width of the given panel (6), R is the radius of rotation of the device, angle δ is the angle between the axis of symmetry of the two adj acent arms (3) of the device.

12. Method for the use of the device for transformation of wind energy, according to claim 7, characterized with that, upon a planetary movement, in Pos. l and Pos.2 the panels (6) obtain bearings, perpendicular to the active plain, as in the rest of the orbit, the bearings of the panels lock with the bearings of the resultant speed Ur, a given angle of action ψi, at which planetary movement of the panels, is applicable at peripheral speed Vper of the device, smaller than the wind speed.

13. Method for the use of the device for transformation of wind energy, according to claim 7, characterized with that upon the planetary movement the panels (6) achieve partial rotation around one base position, perpendicular to the consequent arm, at which from Pos. l to point D 14, the panels obtain base position, as point D 14 is the point at which angle φ2i between the bearing of the peripheral speed Vper and the bearing of the resultant speed Ur obtains value, equal to the optimal angle of action ψi, where as from point D 14 to point D 15, the bearing of the panels maintain an optimal angle of action ψi, achieving gradual rotation in the direction of the rotors rotation, as point D 15 is the point at which angle φ2i has reached maximal value, where as from point D l 5 to point D 16, the bearing of the panels maintain an optimal angle of action ψi, achieving gradual rotation in the opposite direction of the rotors rotation, as point D 16 is the point at which angle φn obtains value, equal to an optimal angle of action ψi, and at this point the panel once again obtains base position, at which from point D 16 to point D 17, the panels obtain base position, as point D 17 is the point at which angle φ2i once again obtains value, equal to the optimal angle of action ψi, at which from point D 17 to point D 18, the bearing of the panels maintain optimal angle of action ψi, achieving gradual rotation in the opposite direction of the rotors rotation, as point D l 8 is the point at which angle φ2i has reached maximal value, at which from point D 18 to point D 19 the bearing of the panels maintain optimal angle of action ψi, achieving gradual rotation in the direction of the rotors rotation, as point D 19 is the point at which angle φ2i obtains value, equal to the optimal angle of action ψi, and in this point the panel once again obtains base position, at which from point D 19 to Pos. l , the panels obtain base position, at which this planetary movement of the panels (6) is applicable at peripheral speed Vper of the device larger than the wind speed.

14. Method for the use of the device for transformation of wind energy, characterized with that, the torque achieved at the rotation of the device, is used as driving torque, for movement of the base of the device.

15. Mechanism for creation of irregularity of the transmitted circular motion, characterized with that, it consists of mechanism for creation of irregularity of the transmitted movement (35) and module for influence (36) over the mechanism for creation of irregularity of the transmitted motion.