IT202100030845A1 - TURBINE FOR VERTICAL AXIS WIND GENERATOR - Google Patents

Description

Description of Patent for Industrial Invention having title:

?TURBINE FOR VERTICAL AXIS WIND GENERATOR?.

DESCRIPTION

The present invention refers to a vertical axis wind turbine.

As is known, wind generators are used to convert the kinetic energy of the wind into electrical energy. For this purpose, wind generators usually include a turbine equipped with a so-called rotor to which a plurality of turbines are associated. of shovels. The latter, in turn, is connected to an electric generator capable of transforming the rotation of the rotor into electrical energy.

In particular, vertical axis turbines are known in which the rotor rotates around a rotation axis arranged vertically, i.e. perpendicular to the ground and to the direction of the wind.

Vertical axis wind turbines are distinguished from horizontal axis ones as they allow you to exploit any wind direction, without the need for to orient the rotation axis of the rotor. Consequently, vertical axis turbines require less? of moving parts compared to those with a horizontal axis, which translates into greater durability and resistance to strong gusts of wind.

However, vertical axis wind turbines present problems related to the fact that the wind usually acts on the blades with a non-constant driving torque. That is, the blades, during rotation around the rotation axis, are usually found for a section in favor of the wind, generating a positive moment on the rotor, and for a section against the wind, generating a negative moment on the rotor which decreases the efficiency of the turbine.

To partially overcome these problems, two types of turbines are known, the so-called ?Savonius? turbines. and the so-called ?Darrieus?.

Savonius turbines are equipped with blades that have a semi-cylindrical shape capable of increasing wind resistance when are in favor of the wind and decrease it when, instead, they are against the wind. In particular, each blade has a concave internal surface to increase grip on the wind and a convex external surface to cut the wind. When the shovel? in a section in favor of the wind, the concave surface? downwind in order to increase the positive moment transmitted by the wind to the blade. When is the shovel? in a section against the wind, the convex surface is downwind to cut the wind and reduce the negative moment transmitted by the wind to the blade.

Darrieus turbines, on the other hand, are equipped with a large number of blades arranged vertically and equipped with a linear or curvilinear aerodynamic profile such as to be able to exploit the wind during the section in favor of the wind and cut it during the section against the wind.

Although these solutions partially reduce the aforementioned problems, they are not yet fully satisfactory as a strong wind resistance factor capable of reducing the performance of the turbine remains always present.

These turbines are therefore susceptible to further improvements aimed at improving their performance.

The main task of the present invention is? therefore that of devising a turbine for a vertical axis wind generator that allows the negative moment transmitted by the wind to the blades to be reduced to a minimum in order to maintain a substantially constant torque moment

Another purpose of the present invention? that of devising a vertical wind turbine capable of making the most of the kinetic energy of the wind, regardless of the direction of the wind. Other purpose of the present invention? that of devising a turbine for a vertical axis wind generator which allows the aforementioned drawbacks of the known art to be overcome within the context of a simple, rational solution that is easy and effective to use and has a low cost.

The purposes set out above are achieved by the present vertical axis wind turbine having the characteristics of claim 1.

Other characteristics and advantages of the present invention will be more evident from the description of a preferred, but not exclusive, embodiment of a vertical axis wind turbine, illustrated by way of example, but not by way of limitation, in the attached drawings in which:

- figure 1? a perspective view of a vertical axis wind turbine in accordance with the present invention, - Figure 2? a detailed view of the turbine adjustment means of figure 1,

- figure 3? a detailed view of the turbine positioning means of figure 1,

- figure 4? a view of the turbine base in figure 1,

- figure 5? a detailed view of the support element and the guide element,

- figures 6 and 7 are seen from above of the turbine in figure 1.

With particular reference to these figures, yes? indicated globally with 1 is a vertical axis wind turbine.

Turbine 1? can be positioned resting on the ground to be hit by a flow of wind in order to transform the kinetic energy of the latter into a rotary motion of a rotor 3. Furthermore, the turbine 1 is connected to an electric generator capable of transforming the rotary motion of rotor 3 into electrical energy.

As illustrated in figure 1, the turbine 1 includes at least one vertical support shaft 2. In particular, the support shaft 2 extends mainly along its own longitudinal direction. In use, the support shaft 2 is arranged in support of the ground and extends transversally to the latter.

In the context of this discussion, the terms ?superior? and ?bottom?, ?vertical? and "horizontal", used with reference to turbine 1, are intended to refer to the conditions of normal use of turbine 1, i.e. those in which it is placed resting on the ground.

Helpfully, the support shaft 2 is rotating around its own axis of revolution.

Preferably, the support shaft 2 has a substantially circular cross section.

Turbine 1? furthermore equipped with a base 4 intended to rest on the ground and capable of supporting the support shaft 2. Preferably, the base 4 includes a fifth wheel 5 capable of supporting the support shaft 2 in a rotary manner.

Conveniently, turbine 1? equipped with at least one rotor 3 associated with the support shaft 2 and rotating around a rotation axis X1.

Preferably, the rotation axis substantially parallel to the X2 axis of revolution of support shaft 2. Even more? preferably, the rotation axis substantially coinciding with the X2 axis of revolution. For this purpose, the rotor 3 has a substantially circular section and is arranged coaxially to the support shaft 2. In other words, the rotor 3 and the support shaft 2 are substantially concentric with each other.

Preferably, rotor 3? designed to rotate in a single predefined direction of rotation. Even more? preferably, this predefined direction of rotation ? counterclockwise.

The terms ?counterclockwise? and "clockwise", used with reference to the rotation of the support shaft 2 are to be understood with reference to the direction of rotation of the turbine 1 with respect to an observer looking at the turbine 1 from above.

Conveniently, turbine 1? operationally connected to an electric generator capable of transforming the rotary motion of rotor 3 into electric current. Preferably, the electric generator? positioned in correspondence with the base 4, facilitating assembly, maintenance and safety operations.

Usefully, the turbine 1 includes at least one blade 6 associated with the rotor 3 and comprising at least one gripping surface 7. The blade 6 is destined to be hit by a wind flow along a propagation direction V1 to rotate the rotor 3. In this case, the blade 6 is associated integral with the rotor 3 to rotate with the latter around the rotation axis X1. The wind flow, propagating along the propagation direction V1, intercepts the gripping surface 7 of the blade 6, transferring part of its kinetic energy to it so as to rotate the blade 6 and with it the rotor 3.

Advantageously, the turbine 1 includes means 8 for regulating the orientation of the gripping surface 7 as a function of the direction of propagation V1 of the wind flow. In particular, the adjustment means 8 are configured to increase or decrease the gripping surface 7 exposed to the wind depending on the positioning of the blade 6 with respect to the direction of propagation V1 of the wind.

For this purpose, the gripping surface 7? mobile, due to the thrust applied by the wind flow on the gripping surface 7, between:

- a gripping position in which the gripping surface 7? arranged substantially parallel to the X1 rotation axis; and - a release/recovery position in which the gripping surface 7? arranged substantially transversally to the X1 rotation axis.

In practice, with reference to the normal conditions of use of the turbine 1, in the gripping position, the gripping surface 7? arranged substantially vertically; instead, in the release/recovery position, the gripping surface 7? arranged substantially horizontally.

This arrangement allows the blade 6 to be placed in a gripping or release/recovery position depending on whether the blade 6 is rotating in favor of the wind or against the wind with respect to the direction of propagation of the wind flow in order to maximize the efficiency of the turbine 1.

The terms ?in favor of the wind? and ?against the wind? they refer to the direction of movement of the blade 6, during its rotation around the X1 rotation axis, with respect to the direction of wind propagation. In particular, ?in favor of the wind? indicates that blade 6? moved in the same direction as the direction of wind propagation. While, ?against the wind? indicates that blade 6? moved in a direction opposite to the direction of wind propagation.

In detail, blade 6? placed in a gripping position when ? in favor of the wind, while ? placed in the release/recovery position when ? against the wind.

Conveniently, in the gripping position the gripping surface 7? in the upwind position with respect to the direction of propagation V1 of the wind flow, and in the release position the gripping surface 7? in a downwind position with respect to the direction of propagation V1 of the wind flow.

With the terms ?windward? and ?downwind? it is intended to indicate the positioning of the gripping surface 7 with respect to the wind during its rotation around the rotation axis X1: the gripping surface 7? upwind when? facing the wind, i.e. facing the wind, while ? downwind when? hidden from the wind, that is, it is located against the wind.

To further specify the terms ?upwind? and ?downwind? it is considered that the blade 6 has a front surface 7a opposite the gripping surface 7. In particular, according to the direction of rotation of the blade 6, the front surface 7a? arranged in front of the gripping surface 7. The terms upwind and downwind refer to the position of the gripping surface 7 with respect to the front surface 7a.

By placing the gripping surface 7 in the gripping position when ? upwind and in the release/recovery position when ? downwind, ? It is possible to transmit a maximum positive moment and a minimum negative moment to the rotor 3. This precaution allows the effective efficiency of turbine 1 to be maximized, given by the subtraction of the negative moment from the positive moment.

As can be seen from figures 6 and 7, the blade 6, rotating around the rotation axis X1, defines a work trajectory 9, substantially circular, comprising:

- a section of opening 9a in which the blade 6? moved from the release/recovery position to the grip position;

- an outward section 9b in which blade 6? in the gripping position, and the gripping surface 7 being in an upwind position with respect to the direction of propagation V1;

- a closing section 9c in which the blade 6? moved from the grip position to the release/recovery position; And

- a return section 9d in which the blade 6? kept in the release/recovery position, and the gripping surface 7 being in a downwind position with respect to the direction of propagation V1.

Usefully, the opening section 9a has an angular extension between 50? and 80?, preferably 60?. The forward section 9b has an angular extension between 50? and 80?, preferably 60?. The closing section 9c has an angular extension between 50? and 80?, preferably 60?. The return section 9d has an angular extension between 120? and 210?, preferably 180?.

With the term ?angular extension? it is intended to indicate the angular distance between two points of a circular trajectory, such as the work trajectory 9.

This angular distance? measured by the width of the non-concave angle formed by the two rays of the trajectory having as their ends the two points of the circular trajectory. Preferably, this angular distance ? expressed in sexagesimal degrees.

Conveniently, blade 6? hinged to the rotor 3 to rotate around a hinge axis X3 between the gripping position and the release/recovery position. Helpfully, the X3 hinge axis is substantially transverse to the X1 rotation axis.

In particular, the blade 6 has at least one pin element 10 which is hinged to the rotor 3.

Preferably, the pin element 10 has a substantially cylindrical configuration and is coupled to the rotor 3 by means of a rotary pair.

Preferably, the hinge axis substantially parallel to the gripping surface 7. Even more? preferably, the hinge axis X3 is passing through a midline of the gripping surface 7.

Shovel 6? what? rotatable by substantially 90? to move the gripping surface 7 between the gripping position, in which ? arranged substantially parallel to the X1 rotation axis, and the release position, in which it is arranged transversally to the rotation axis.

As mentioned above, the adjustment means 8 are configured to rotate the blade 6 around the hinge axis X3 between the gripping position and the release/recovery position. In particular, the adjustment means 8 are configured to arrange the blade 6 in the gripping position when the gripping surface 7 is in the upwind position, and in the release/recovery position when the gripping surface 7? in a leeward position.

The adjustment means 8 are placed between the support shaft 2 and the rotor 3. In particular, the adjustment means 8 are supported by the support shaft 2 and, during the rotation of the blade 6 and the rotor 3 around the rotation axis X1, act on the blade 6 to rotate it between the gripping position and the release/recovery position.

As can be seen from figure 2, the adjustment means 8 comprise at least one guide element 11 associated with the support shaft 2, and at least one trolley element 12 associated with the blade 6 and coupled to the guide element 11. The element cart 12, in use, ? configured to slide along the guide element 11 due to the rotation of the rotor 3.

Preferably, the trolley element 12 includes at least one bearing 13 capable of sliding along the guide element 11. Even more? preferably, the trolley element 12 includes a pair of bearings 13 arranged one below and one above the guide element 11.

Usefully, the guide element 11 has a substantially circular ring shape. The guide element 11? arranged substantially concentrically to the rotor 3 and/or to the support shaft 2. In particular, the guide element 11 is arranged on a plane transverse to the X1 rotation axis, or on a substantially horizontal plane. As visible from figure 5, the guide element 11 has a shaped profile 14 configured to allow the passage of the blade 6 from the gripping position to the release position. In this case, the trolley element 12 is capable of sliding along at least the shaped profile 14. During this sliding, the shape of the shaped profile 14 allows the trolley element 12 to be moved along an operating direction. In particular, the driving direction? substantially parallel to the X1 rotation axis, that is? substantially vertical. In other words, the shaped profile 14? shaped to move the trolley element 12 towards/away from the blade 6.

As described in detail in the following description, the adjustment means 8 are suitable for rotating the blade 6 following the movement of the trolley element 12 along the driving direction.

In this case, the shaped profile 14 includes at least one activation portion 15 on which the trolley element 12 slides along an activation direction, the activation portion 15 being configured to allow the blade 6 to perform a 90° rotation. Furthermore, the shaped profile 14 includes a return portion 16 on which the trolley element 12 slides along a return direction, the return portion 16 being configured to allow the blade 6 to perform a further 90° rotation.

Specifically, the trolley element 12 is moved, due to the thrust applied by the wind flow on the blade 6, along the shaped profile 14 according to a predefined direction of rotation. During this movement, the trolley element 12 travels along the activation portion 15 according to an activation direction and the return portion 16 according to a return direction. The conformation of the activation portion 15 and the return portion 16? such as to move the trolley element 12 along the direction of operation.

For this purpose, the activation portion 15 consecutively comprises at least a first inclined section 15a and at least a first linear section 15b.

The first inclined section 15a allows the trolley element 12 to be moved along the direction of operation in order to rotate the blade 6 by substantially 90? to place it in the gripping position. The first linear section 15b instead? shaped to keep the trolley element 12 in the gripping position.

Similarly, the return portion 16 consecutively comprises at least a second inclined section 16a and at least a second linear section 16b.

The second inclined section 16a allows the trolley element 12 to be moved along the operating direction in order to rotate the blade 6 by substantially 90? to place it in the release/recovery position. The second linear section 16b instead? shaped to keep the trolley element 12 in the release/recovery position.

In practice, the inclined sections 15a, 16a allow the trolley element 12 to be brought closer/further away with respect to the blade 6. Instead, the linear sections 15b, 16b allow the trolley element 12 to be kept at a substantially fixed distance.

For this purpose, the linear sections 15b, 16b extend substantially transversally to the rotation axis X1. In other words, the linear sections 15b, 16b lie on a respective substantially horizontal plane.

Furthermore, the linear sections 15b, 16b are arranged substantially staggered from each other, that is, one is arranged closer and the other further away with respect to the blade 6.

Usefully, the sliding of the trolley element 12 along the first inclined section 15a, the first linear section 15b, the second inclined section 16a and the second linear section 16b corresponds, respectively, to the movement of the blade 6 along the opening section 9a, the outward section 9b, the closing section 9c and the return section 9d.

Preferably, the guide element 11 is arranged underneath the blade 6. Preferably, the first linear section 15b is arranged close to the blade 6 and the second linear section 16b? placed away from the blade 6.

As visible from figure 5, the first inclined section 15a? interposed between the first linear section 15b and the second linear section 16b, while the second inclined section 16a is interposed between the second linear section 16b and the first linear section 15b. Preferably, the activation portion 15 and the return portion 16 are consecutive to each other.

Conveniently, the adjustment means 8 comprise at least one assembly for transmitting the motion 17 of the trolley element 12 to the blade 6. In particular, the assembly for transmitting the motion 17? interposed between the trolley element 12 and the blade 6. In this case, the motion transmission group 17 is coupled to the blade 6 and to the trolley element 12 to rotate with the latter around the rotation axis X1.

The motion transmission group 17 ? configured to rotate the blade 6 following the sliding of the trolley element 12 on the activation portion 15 and on the return portion 16. In this case, the motion transmission group 17 is configured to rotate the blade 6 following the movement of the trolley element 12 along the driving direction. In other words, the motion transmission unit 17? configured to transform, through a specific kinematic mechanism, the movement of the trolley element 12 along the direction of operation into a rotation of the blade 6 around the hinge axis X3.

For this purpose, advantageously, the motion transmission assembly 17 includes at least one gear 18, 19 capable of transforming the motion of the trolley element 12 along the driving direction into a rotary motion of the blade 6 around the hinging axis X3 . In detail, the motion transmission assembly 17 includes at least one toothed wheel 18 coupled to the blade 6, and at least one rack rod 19 meshing with the toothed wheel 18. The rack rod 19 is designed to slide vertically in an alternating manner as a result of the sliding of the trolley element 12 on the shaped profile 14. Following this vertical sliding, the rack rod 19 rotates the toothed wheel 18 and with it the blade 6.

In this case, the trolley element 12, sliding on the shaped profile 14, moves the rack rod 19 alternately along the direction of operation. In particular, during the transition of the trolley element 12 along one of the inclined sections 15a, 16a, the trolley element 12 varies its distance with respect to the blade 6, moving the rack rod 19 along the direction of operation. In turn, the rack rod 19 meshes with the toothed wheel 18, rotating it around the hinge axis X3.

For this purpose, the toothed wheel 18? rigidly connected to blade 6 to rotate with the latter. In this case, the toothed wheel 18? integral with the pin element 10 of the blade 6. Preferably, the toothed wheel 18 is coaxial with the pin element 10.

Preferably, the rack rod 19 has a substantially elongated shape which extends along its own longitudinal direction substantially parallel to the drive direction V.

The trolley element 12 is rigidly connected to the rack rod 19. Preferably, the bearings 13 of the trolley element 12 are hinged directly to the rack rod 19.

As visible from figure 2, the motion transmission assembly 17 has at least one support element 20 configured to slideably support the rack rod 19 along the operating direction. Preferably, the support element 20 is associated with rotor 3 to rotate with the latter. Furthermore, the support element 20? arranged in correspondence with blade 6.

Usefully, the support element 20 defines a groove in which the rack rod can be inserted smoothly. The groove extends along a direction substantially parallel to the driving direction. Furthermore, the groove has a cross section of a shape complementary to the cross section of the rack rod.

As mentioned above, the support shaft 2 is rotatable around the X2 axis of revolution in order to vary its angular position.

Conveniently, the turbine 1 includes positioning means 22 associated with the support shaft 2 and configured to rotate the support shaft 2 according to the direction of propagation V1 in order to arrange the support shaft 2 with a predefined angular position.

In detail, at the predefined angular position, the positioning means 22 are positioned so as to arrange the gripping surface 7 in the gripping position when ? upwind and in the release/recovery position when ? leeward.

In this case, as mentioned above, the guide element 11 is integral with the support shaft 2 to rotate with the latter. The positioning means 22 are suitable for rotating the support shaft 2 in order to arrange the activation direction in favor of the wind and the return direction against the wind, with respect to the direction of propagation V1 of the wind flow.

In other words, when the support shaft 2 is in the predefined angular position, the activation portion 15 and the return portion 16 are arranged so that the movement of the trolley element 12 along the activation direction and along the return direction is, respectively, in favor of the wind and against the wind .

In this way, by varying the angular position of the support shaft depending on the direction of propagation, the adjustment means 8 can act on the blade 6 so as to place it in the gripping position when the gripping surface 7 is upwind, and in the release/recovery position when ? leeward.

Furthermore, the positioning means 22, by rotating the support shaft 2, can position the activation portion 15 in correspondence with the opening and forward section, and the return portion 16 in correspondence with the closing and return section. Even more? specifically, when the support tree 2 is arranged in correspondence with the predefined angular position, the first inclined section 15a is arranged in correspondence with the opening section 9a, the first linear section 15b is arranged in correspondence with the forward section 9b, the second inclined section 16a is arranged in correspondence with the closing section 9c and the second linear section 16b? arranged in correspondence with the return section 9d.

As illustrated in figure 3, the positioning means 22 comprise at least one sail element 23 associated with the support shaft 2 and mobile in rotation around the rotation axis X1. In this case, the sail element 23 rotates together with the support shaft 2 around the rotation axis X1 in order to vary its angular position.

As mentioned above, the support shaft 2 rotates freely around the rotation axis X1.

The sail element 23 is configured to rotate according to the direction of propagation V1, placing the support shaft 2 in the predefined angular position.

For this purpose, the sail element 23 is equipped with a pair of gripping faces 24a, 24b opposed to each other and designed to grip the wind flow. Preferably, the grip faces 24a, 24b are arranged substantially parallel to each other. Furthermore, the grip faces 24a, 24b are arranged substantially parallel to the rotation axis X1.

The wind flow, hitting the grip faces 24a, 24b, exerts on the sail element 23, and therefore on the support shaft 2, a moment capable of rotating it until placing the sail element 23 in an equilibrium position in which the moment exerted by the wind is? null. In particular, in the equilibrium position, the grip faces 24a, 24b are substantially parallel to the direction of wind propagation.

Usefully, the equilibrium position of the sail element 23 corresponds to the predefined angular position of the support shaft 2.

In this case, the gripping faces 24a, 24b lie on a substantially vertical plane passing through the rotation axis X1. This plane cuts the turbine 1 in two, defining a first and a second side. When the sail element 23 is in the equilibrium position, the blade 6, rotating along the predefined direction of rotation, moves on the first side in favor of the wind and on the second side against the wind.

Usefully, when blade 6 passes through the first side? arranged in a gripping position, i.e. in a windward position, while when it passes through the second side? arranged in the release/recovery position, i.e. in the leeward position.

For this purpose, the first linear section 15b and the second linear section 16b have an angular distance from the sail element 23 substantially equal to 90?.

Furthermore, at least the first linear section 15b? arranged on the first side and at least the second linear section 16b? placed on the second side.

In this case, the first inclined section 15a, the first linear section 15b and the second inclined section 16a are arranged on the first side, while the second linear section 16b? placed on the second side. Even more? specifically, the beginning of the first linear section 15b and the end of the second linear section 16b are substantially on the plane defined by the gripping faces 24a, 24b of the sail element 23.

As visible from figure 5, the positioning means 22 include at least one support element 25 placed between the sail element 23 and the support shaft 2. In particular, the support element 25 is connected to one?end? top of the support shaft 2.

Furthermore, the support element 25 is arranged transversely to the support shaft 2. In particular, the support element 25 has an elongated shape which extends mainly along its own longitudinal direction. The longitudinal direction of the support element 25 is transverse to the X2 axis of revolution.

As visible from figure 3, the support element 25 extends between a head portion 25a and a tail portion 25b. The head portion 25a ? associated with the support tree 2, while the tail portion 25b is associated with the sail element 23.

Preferably, the head portion 25a has a cross section of a larger size than the cross section of the tail portion 25b.

Helpfully, the support shaft 2 is equipped with a modular structure in which a plurality is identified? of modular portions 27 that can be associated with each other in a removable manner. In particular, the modular portions 27 can be associated with each other to create the support shaft 2. This arrangement facilitates the transport and assembly of the turbine 1.

Preferably, the modular portions 27 can be coupled together by means of at least one junction 28. In this case, the modular structure 26 includes three modular portions 27. In particular, the modular structure 26 includes a base modular portion associated with the base, a terminal modular portion and a central modular portion interposed between the base and terminal modular portions.

Preferably, the modular portions 27 have a tubular shape with a substantially circular section.

As visible from figure 5, the rotor 3? coupled to the support shaft 2 by interposition of a support ring 29. In particular, the support ring 29 is associated integrally with the support shaft 2. The rotor 3 is slidably coupled to the support ring 29 to rotate around the rotation axis X1.

For this purpose, the support element 20 has a guiding surface 30 with a substantially circular profile. The driving surface 30 ? arranged on a plane transverse to the X1 rotation axis. Rotor 3? coupled to the support element by the interposition of a bearing element capable of sliding along the guide surface 30.

As visible from figure 1, the rotor 3? equipped with a tree structure 31 which extends substantially parallel to the support shaft 2. Conveniently, the tree structure 31 has a tubular shape and contains within itself at least partially the support shaft 2. In this case, the tree structure shaft 31 and the support shaft 2 are substantially coaxial with each other.

The tree structure 31 ? also supported in a rotoidal manner by the fifth wheel 5 of the base 4.

As mentioned previously, the blade 6 has a gripping surface 7, such as a sail. Preferably, the gripping surface 7 of the blade 6? made at least partly in Kevlar fabric.

Usefully, the blade 6 has a reinforcing structure 32 designed to keep the gripping surface 7 in tension.

Preferably, the reinforcing structure 32? associated with the pin element 10.

The reinforcing structure 32 has at least one boom element 33 associated with the gripping surface 7. The boom element 33 is associated with the pin element 10 and ? arranged transversally to the latter.

The boom element 33 defines a housing suitable for at least partially receiving the gripping surface 7. Preferably, the housing is a through opening in which there is part of the gripping surface 7 is inserted. The boom element 33 is inserted. also gifted? of at least one tensor 34 capable of hooking onto the gripping surface 7 to tension it. Preferably, the boom element 33 is equipped with a pair of tensors, each arranged at one end? of the boom element 33.

Furthermore, the reinforcing structure 32? also equipped? of at least one reinforcement rod 35 associated with the boom element 33 and on which there is gripping surface 7 mounted.

The reinforcement rod 35 ? arranged transversally to the boom element 33. In particular, the boom element 33 and the reinforcement rod 35 are arranged, respectively, transversally and substantially parallel to the hinging axis X3.

Preferably, the reinforcing rod 35 extends along a midline of the gripping surface 7.

Furthermore, the reinforcing structure 32 comprises one or more stiffening slats, not shown in the figures, arranged around the perimeter of the gripping surface 7, preferably inserted inside pockets made on the gripping surface 7.

According to one or more? versions, the turbine 1 includes at least one group of blades 6 equipped with a plurality? of blades 6 associated with the rotor 3. Preferably, the blades 6 of the group of blades 6 are arranged symmetrically along the rotor 3.

The blades 6 of the group of blades 6 are substantially similar to each other and the adjustment means 8 are configured to move each blade 6 between the yield position and the release/recovery position as previously described.

Preferably, the adjustment means 8 comprise a single guide element 11 associated with the group of blades 6. Furthermore, the adjustment means 8 comprise at least one trolley element 12 and at least one motion transmission assembly 17 associated with each blade 6 of the plurality? of blades 6.

Preferably, the turbine 1 comprises at least one group of blades 6 equipped with three blades 6. Even more? preferably, the three blades 6 are equidistant from each other. In particular, the blades 6 are spaced apart from each other by an angular distance between 100? and 150?, preferably 120?. However, it cannot be excluded that the turbine 1 may comprise a greater or lesser number of blades 6.

According to one or more? versions, turbine 1 includes a plurality? of rotors 3 and a plurality? of groups of blades 6, each group of blades 6 being associated with a rotor 3. Furthermore, the turbine 1 comprises a plurality? of 8 adjustment means, each of which ? associated with a group of blades 6.

Preferably, the turbine 1 comprises three rotors 3 and three groups of blades 6. As visible from figure 1, the shaft structures 31 of the rotors 3 are associated with each other to create a single shaft structure mounted on the base 4.

Object of the present invention? else? a vertical axis wind generator comprising a turbine 1 as previously described.

Furthermore, the wind generator ? equipped with an electric generator operationally connected to the rotor 3 of the turbine 1. The electric generator is configured to transform the rotary motion of rotor 3 into electrical energy.

Preferably, the electric generator? arranged in correspondence with the base 4 of the turbine 1.

As illustrated in figure 4, conveniently, the wind generator includes at least one speed multiplier 36 interposed between the electric generator and the rotor 3. The speed multiplier 36? configured to apply a variable resistance to rotor 3 depending on the speed? of rotation of the latter in order to maintain the speed? of rotation of the rotor 3 substantially constant, while at the same time increasing the electrical power generated by the electric generator.

In particular, the 36 rpm multiplier? designed to prevent rotor 3 from exceeding a speed? of pre-established maximum rotation.

By means of the speed multiplier 36 ? Is it possible to decrease the speed? rotation of rotor 3, increasing or maintaining constant the electrical power generated by the electric generator.

In other words, the spin multiplier 36 ? designed to keep the speed constant? of rotation of rotor 3, even if the speed varies? of the wind flow, without affecting the electrical power obtainable from the wind flow. In this case, the speed multiplier 36 has a pinion 39 connected to the rotor 3 to rotate with the latter. Furthermore, the speed multiplier includes at least a brushless motor 37 equipped with a gear 38 meshing with the pinion 39. The brushless motor? designed to act on the pinion 39 by applying a braking resistance which decreases the rotation of the rotor 3, while at the same time increasing the electrical power supplied.

Preferably, the rev multiplier 36 ? mounted on the base 4.

Preferably, the speed multiplier 36 has a plurality? of brushless motors 37 arranged perimetrically to the rotor 3.

Yes ? in practice it has been noted that the invention described achieves the proposed purposes and in particular it is underlined that the turbine for vertical axis wind generators allows the negative moment transmitted by the wind to the blades to be reduced to a minimum in order to maintain a torque moment substantially constant, thus making the most of the kinetic energy of the wind, regardless of the direction of the wind.

Claims (21)

1) Turbine (1) for vertical axis wind generator, including: - at least one vertical support shaft (2); - at least one rotor (3) associated with said support shaft (2) and rotating around a rotation axis (X1); - at least one blade (6) associated with said rotor (3) and comprising at least one gripping surface (7), said blade (6) being intended to be hit by a wind flow along a propagation direction (V1) to rotate said rotor (3); characterized in that it includes means for regulating (8) the orientation of said gripping surface (7) as a function of the direction of propagation (V1) of said wind flow. 2) Turbine (1) according to claim 1, characterized in that said support shaft (2) is rotating around its own axis of revolution (X2) substantially parallel to said axis of rotation (X1). 3) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said gripping surface (7) is? mobile, due to the thrust applied by said wind flow on said gripping surface (7), between: - a gripping position in which said gripping surface (7) is arranged substantially parallel to said rotation axis (X1); And - a release/recovery position in which said grip surface (7) is arranged substantially transversally to said rotation axis (X1). 4) Turbine (1) according to one or more? of the previous claims, characterized in that in said gripping position said gripping surface (7) is? in an upwind position with respect to the direction of propagation (V1) of said wind flow and in said release position said gripping surface (7) ? in a downwind position with respect to said direction of propagation (V1) of said wind flow. 5) Turbine (1) according to the previous claims, characterized in that said blade (6) is hinged to said rotor (3) to rotate around a hinging axis (X3) between said gripping position and said release/recovery position, said hinging axis (X3) being substantially transverse to said rotation axis (X1). 6) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said adjustment means (8) are placed between said support shaft (2) and said rotor (3). 7) Turbine (1) according to one or more? of the previous claims, characterized in that said adjustment means (8) comprise: - at least one guide element (11) associated with said support shaft (2) - at least one trolley element (12) associated with said blade (6) and coupled to said guide element (11), said trolley element (12), in use, being configured to slide along said guide element (11) due to the rotation of said rotor (3). 8) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said guide element (11) has a shaped profile configured to allow the passage of said blade (6) from said gripping position to said release/recovery position. 9) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said shaped profile (14) includes at least: - an activation portion (15) on which said trolley element (12) slides along an activation direction, said activation portion (15) being configured to allow said blade (6) to perform a rotation of 90?, e - a return portion (16) on which said trolley element (12) slides along a return direction, said return portion (16) being configured to allow said blade (6) to perform a further rotation of 90? . 10) Turbine (1) according to one or more? of the previous claims, characterized in that said activation portion (15) consecutively includes at least a first inclined section (15a) and at least a first linear section (15b), and said return portion (16) consecutively includes at least a second inclined section (16a) and at least a second linear section (16b), said first inclined section (15a) and said second inclined section (16a) being adjacent to said first linear section (15b). 11) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said adjustment means (8) comprise at least one motion transmission assembly (17) of said trolley element (12) to said blade (6), said motion transmission assembly (17) being configured to rotate said blade (6) following the sliding of said trolley element (12) on said activation portion (15) and said return portion (16). 12) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said motion transmission assembly (17) includes: - at least one toothed wheel (18) coupled to said blade (6), e - at least one rack rod (19) meshing with said toothed wheel (18), said rack rod (19) being able to slide vertically in an alternating manner due to the sliding of said trolley element (12) on said shaped profile (14). 13) Turbine (1) according to one or more? of the previous claims, characterized by the fact that it includes at least three blades (6) equidistant from each other. 14) Turbine (1) according to one or more? of the previous claims, characterized in that it includes positioning means (22) associated with said support shaft (2) and configured to rotate said support shaft (2) according to said propagation direction (V1) in order to arrange said support shaft (2) with a predefined angular position. 15) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said guide element (11) is integral with said support shaft (2) to rotate with the latter, said positioning means (22) being capable of rotating said support shaft (2) in order to arrange said activation direction in favor of the wind and said direction of return against the wind with respect to said direction of propagation (V1). 16) Turbine (1) according to one or more? of the previous claims, characterized in that said positioning means (22) comprise at least one sail element (23) associated with said support shaft (2) and movable in rotation around said rotation axis (X1). 17) Turbine (1) according to one or more? of the previous claims, characterized by the fact that said first linear section (15b) and said second linear section (16b) have an angular distance from said sail element (23) substantially equal to 90?. 18) Vertical axis wind generator including a turbine (1) according to one or more? of the previous claims and an electric generator operatively connected to said rotor (3), said electric generator being configured to transform the rotary motion of said rotor (3) into electrical energy. 19) Vertical axis wind generator according to the previous claim, characterized by the fact that said turbine (1) includes at least one base (4) arranged, in use, resting on the ground, said electric generator being arranged in correspondence with said base (4 ). 20) Vertical axis wind generator according to one or more? between claims 18 and 19, characterized in that it includes a speed multiplier (36) interposed between said electric generator and said rotor (3), said speed multiplier (36) being configured to apply a resistance to said rotor (3) variable depending on the speed? of rotation of the latter in order to maintain the speed? of rotation of said rotor (3) substantially constant, while at the same time increasing the electrical power generated by the electric generator. 21) Vertical axis wind generator according to one or more? between claims 18 to 20, characterized in that said speed multiplier (36) comprises: - at least one pinion (39) connected to said rotor (3) to rotate with the latter, e - at least one brushless motor (37) equipped with a gear (38) meshing with said pinion (39).