Performance enhanced configurable multi-purpose cross-flow wind turbine

Abstract

A wind turbine rotor includes a shaft, a plurality of primary blades disposed at regular intervals about the shaft, and a plurality of secondary blades disposed about the shaft between the primary blades of the plurality of primary blades. Each secondary blade of the plurality of secondary blades is smaller than each primary blade of the plurality of primary blades.

Description

[0001] Cross-references to related applications

[0002] This application claims the benefit of U.S. Provisional Application No. 63 / 063,955, filed August 10, 2020, which is incorporated herein by reference in its entirety. Technical Field

[0003] This disclosure relates to the field of renewable energy, and more specifically, to wind turbines designed for crossflow or transverse axial flow applications. Background Technology

[0004] Wind turbines can be easily deployed in specific locations where the electricity generated can be used directly at the deployment site, fed directly into the grid, or stored in an energy storage system. Wind turbines can also serve local microgrids, supporting multiple facilities. Therefore, wind power is an ideal alternative energy source in many situations.

[0005] However, conventional wind turbines suffer from inefficiency and low power output. In particular, conventional drag-based wind turbines are inefficient when wind impacts the return blades. These conventional traction-based wind turbines are also known to have self-starting problems.

[0006] Therefore, improved wind turbines are needed. Attached Figure Description

[0007] A better understanding of this disclosure can be achieved by referring to the accompanying drawings, which will clearly reveal many features and advantages of this disclosure to those skilled in the art. It should be noted that these drawings are provided to aid in understanding the invention and are not intended to limit the scope of the invention to the specific content shown in each drawing. The invention can be used in various configurations utilizing the same operating principles as described herein.

[0008] Figure 1 This is a partial cross-sectional view showing an example wind turbine.

[0009] Figure 2 This is a cross-sectional view showing an example configuration of a wind turbine rotor.

[0010] Figure 3 This is a cross-sectional view of an example wind turbine rotor assembly.

[0011] Figure 4 This is a cross-sectional view of an example wind turbine rotor assembly.

[0012] Figure 5 This is an isometric three-dimensional view of an example wind turbine rotor configuration shown relative to the axis.

[0013] Figure 6This is a cross-sectional view of an example wind turbine rotor.

[0014] Figure 7 This is a cross-sectional view of an example wind turbine rotor using four main blades and four secondary blades.

[0015] Figure 8 This is a cross-sectional view of an example wind turbine rotor using four main blades and eight secondary blades.

[0016] Figure 9 , Figure 10 and Figure 11 Includes illustrations of example wind turbine systems.

[0017] Figure 12 , Figure 13 , Figure 14 , Figure 15 , Figure 16 , Figure 17 , Figure 18 , Figure 19 , Figure 20 and Figure 21 An illustration of an example wind turbine system including enhancement devices.

[0018] The same reference symbols are used in different diagrams to represent similar or identical items. Detailed Implementation

[0019] In one example, the wind turbine uses interacting primary and secondary blades to enhance its performance during rotation. This enhanced performance is achieved by positioning the secondary blades within the primary blades to further concentrate and convert the wind force flowing over the convex and concave surfaces of the primary and secondary blades into usable energy.

[0020] A drag-based crossflow configuration is described, in which an example rotor design is used to enhance the performance (or power output) of a wind turbine. This is achieved by configuring a rotor with multiple main blades (or scoops) around an axis defined, for example, by a rotational shaft, and then further positioning an additional set of secondary blades between the main blades. The position and shape (or configuration) of the secondary blades increase the direct capture of additional energy from the wind, while also redirecting additional wind force to the main blade group.

[0021] In this specification, the terms "blade" and "scoop" are used interchangeably. Generally, the part of a wind turbine that directly interacts with the wind is called a blade. Typical utility-scale wind turbine blades are based on foil or lift designs. Drag-based wind turbine blades are often more scoop-shaped, but can also generally be referred to as blades. The term "rotor" refers to a complete set of blades around an axis and, optionally, connected to a central shaft or shaft defining that axis.

[0022] The term "configuration" can be used to describe the overall shape, size, curvature, depth, and angle of a single primary or secondary blade. The same configuration term can also be used to describe a complete rotor, where the rotor configuration describes the complete rotor, including individual primary and secondary blade groups, each with its own configuration, surrounding or connected to a central shaft or axis.

[0023] Figure 1 This shows a partial cross-section of an example wind turbine. A partial cross-sectional view is provided to illustrate the operating principle of the wind turbine. The wind turbine can be positioned vertically or horizontally. Figure 1 The image shows a partial cross-section, with the wind direction horizontally from the right towards the partial cross-section. Figure 1 Other indicators show the wind path that occurs when wind interacts with and causes the wind turbine to rotate. For clarity, the interaction of the wind is represented by dashed lines, as is the direction of rotation.

[0024] In the view, at the angle, the main blade 101A is shown on the concave surface primarily facing the wind and bearing the wind force to rotate the shaft 103. In this view, the direction of rotation of the shaft is counterclockwise.

[0025] Another main blade 101B is positioned relative to the axis at the point of rotation. When in this position, the main blade 101B is shown acting on the main blade 101C by redirecting the airflow passing through the main blade 101A to the main blade 101A.

[0026] The second-stage blade 102A adds extra wind capture surface area to the rotor and interacts with the main blades (101A, 101B) to improve efficiency.

[0027] As wind passes over the top of the main blade 101B, it is partially directed into the secondary blade 102A, which increases the rotational torque, and is also directed into the main blade 101A, further increasing the rotational torque. In this method, by concentrating wind energy into adjacent blades while still allowing a portion of the airflow through the rotor, the bypass air flowing around each blade is used to produce a positive effect.

[0028] The second-stage blade 102A contributes further by its positioning and configuration (or shape and angle relative to the shaft) because it is able to accelerate the airflow based on the incoming wind, causing it to be redirected and slightly compressed between the rotor's main and second-stage blades.

[0029] During rotation, the primary and secondary blades act alternately in transmitting the total torque to the shaft via direct wind force and by redirecting it to other blades. This effect is known as "continuous cycle," as seen when using auxiliary blades. Figure 2 Further detailed description.

[0030] Figure 2 A cross-sectional view of an example rotor is shown. Again, airflow is shown entering from the right, and a rotor with three main blades 201A, 201B, 201C and three secondary blades 202A, 202B, 202C is shown.

[0031] During rotation, this rotor configuration creates a continuous cycle of wind interaction, offering several benefits. As previously mentioned, both the primary and secondary blades are used to provide rotational torque to the axis while also concentrating airflow into blades adjacent to or nearly adjacent to them.

[0032] The airflow entering the rotor is both captured by each individual blade (primary and secondary blades) to transmit direct torque to the shaft, and redirected to adjacent blades. This effect further increases the amount of torque exerted by each blade on the shaft within the rotor.

[0033] Although Figure 2 A rotor at a specific angle relative to a particular wind direction is shown, but the advantages of said rotor are not limited to any particular rotation angle or wind direction, for example, as Figure 4 This is further illustrated in the text.

[0034] Another benefit of the example rotor configuration described in this article is that it reduces what is commonly referred to as "return drag" when the number of blades in a crossflow wind turbine is increased.

[0035] like Figure 3 As shown, the exemplary rotor configuration provides additional benefits beyond the continuous cycle of wind concentration acting on the blades of the shaft during rotation. The exemplary rotor configuration provides a shielding effect that reduces the return drag of the portion of the crossflow wind turbine rotor that returns to the wind during rotation. The return drag effect in conventional crossflow wind turbines is a well-known limiting factor in the performance characteristics of such wind turbines.

[0036] To better understand the benefits of reduced return drag, it may be helpful to briefly describe some issues related to increasing the number of blades in a Savonius-type wind turbine. It has been found that increasing the number of blades in a Savonius wind turbine reduces performance. While this may seem counterintuitive, it is easily explained. If the number of main blades increases, for example from three to six, the inner point of the blade (the point closest to the axis) will be more directly oriented towards the axis to accommodate the space required for additional blades. In this case, for various reasons, any expected performance improvement may be reduced or offset despite the addition of more blades. For example, the incoming wind may be substantially blocked at each blade by the next blade in front of it, relative to the direction of the incoming wind. Furthermore, the return drag on the rotor may increase disproportionately compared to any positive effects expected from adding more blades of the same configuration. Additionally, the effective conversion of useful rotational torque in the crosswind direction is reduced as the wind is directed more inward towards the central axis point.

[0037] This embodiment of the wind turbine and rotor provides a solution that allows more blades to be added to a crossflow wind turbine rotor, thereby providing a beneficial performance improvement while reducing the negative impact of return drag. The aforementioned problem can be transformed into a beneficial effect by using an alternating blade profile configuration around the shaft. Figure 3 The rotor configuration using six blades (three main blades and three second-stage blades) is shown. The main blade groups and second-stage blade groups are configured differently to improve performance.

[0038] Figure 3 The interaction between the turbine rotor and the inlet air on the return side of the rotating return air is particularly noted, especially for the second-stage blade 302B, the main blade 301C, and the second-stage blade 302C. The inlet air direction view of the rotor is represented by a dashed line pointing directly to the center point of the rotor shaft. Figure 3 The diagram also shows additional indicators for “rotating wind direction” and “counter-rotating wind direction”, indicated by dashed lines, to illustrate the airflow entering the rotor at points above and below the center point of the wind directly facing the axis.

[0039] In the view, the second-stage blade 302B faces and rotates most directly towards the incoming wind. The wind direction moves approximately in front of the second-stage blade 302B relative to the incoming wind. The displacement wind pattern is shown in the dashed arrows above and below the text indicating "displacement wind." The second-stage blade 302B displaces a portion of the wind to flow upwards into the wind turbine rotor, most directly into the main blade 301B, where a portion of the exhaust air from the main blade 301A acts on the main blade 301A, further contributing to the rotational torque. As further shown, the second-stage blade 302B displaces another portion of the wind outwards from the center of rotation. This rotor configuration effectively provides shielding for the main blade 301C, which follows the second-stage blade 302B around the axis of rotation. Furthermore, at the position relative to the indicated wind direction angle, the second-stage blade 302C, following the main blade 301C, is completely shielded by the main blade 301C.

[0040] As the wind turbine rotor continues to rotate around its axis of rotation, each of the main blades and second-stage blades has the function of transmitting torque to the axis, reinforcing adjacent blades, and protecting subsequent blades.

[0041] To further illustrate the main functions and advantages of the embodiments, the following are provided: Figure 4 ,in Figure 3 The rotor configuration shown rotates 60 degrees counterclockwise about a central axis (e.g., shaft (303 or 403)), relative to... Figure 3 The angle mentioned.

[0042] exist Figure 4 In the middle, the wind basically comes from Figure 3 The direction shown on the right is towards the wind turbine rotor. Figure 4 In the rotor rotation angle shown, the second-stage blades now move relative to the wind and shaft (303, 403) to the position of the main blades, as... Figure 3 As shown.

[0043] like Figure 4 As shown, during the stated rotation angle, the favorable wind concentration effect continues to occur. When viewed at this angle, the second-stage blade 402B faces the incoming wind most directly. As the wind flows over the top of the second-stage blade 402B, it is concentrated into the main blade 401B. When the wind flows below the second-stage blade 402B, at this position, additional wind is concentrated upwards and enters the concave surface of the second-stage blade 402A, aided by the displacement wind indicated from the adjacent main blade 401C. In this configuration, at this position, another portion of the wind passing through blades 402B and 401C will be discharged through the rotor shaft and generate a downward force on the main blade 401A. This... Figure 4 The middle part is indicated by the dashed arrow line above the main blade 401A and the "exhaust" label.

[0044] Another benefit is the useful use of exhaust gas. Figure 4 The rotor configuration shown allows some exhaust air to flow out of the wind turbine rotor on the side opposite to the incoming air in such a way that the exhaust air further contributes to the downward force.

[0045] Figure 1-4 The angles, curvatures, relative dimensions, and positioning of the main and second-stage blades shown are intended to aid in understanding the basic operating principles and benefits of the turbine and rotor embodiments. The angles, curvatures, shapes, relative dimensions, and positioning of the main and second-stage blades can be modified for various rotor configurations to achieve the same benefits.

[0046] When Figure 4 and Figure 3 Another advantage is obvious when making comparisons. From Figure 4 The alternative angles shown clearly demonstrate that, during rotation, the wind force distribution driving the shaft remains relatively consistent in each rotation due to the continuous cycle of contributions from the main and second-stage blades to the overall and combined forces transmitted to the shaft. Using main and second-stage blades on a wind turbine rotor allows for more stable torque transmission to the shaft than a typical crossflow wind turbine rotor.

[0047] For example, two- or three-bladed, drag-based wind turbine rotors, such as in a typical Savonius configuration, may experience uneven or intermittent torque pulses transmitted from the rotor to the shaft during operation. These uneven torques can lead to vibration and noise, limiting the potential applications or deployment locations of such designs. These forces also cause mechanical fatigue on the rotor and related components, and when coupled to a charge controller or grid-connected inverter, they can also lead to inefficiencies because the torque applied to the connected generator or alternator fluctuates as the effective surface area of ​​the rotor facing the wind increases and decreases during the rotational period. This is particularly pronounced in two-bladed, drag-based Savonius wind turbine rotors.

[0048] Furthermore, self-starting issues may arise in a two-blade rotor configuration. If the two-blade crossflow rotor is positioned at rest relative to the future inlet wind angle, which is substantially parallel to the inlet wind, a larger airflow may be required to force the rotor to reach rotational speed to provide any useful energy or work, which further contributes to the overall loss of efficiency during operation.

[0049] As mentioned above, the common approach of adding more blades to the same configuration can negatively impact performance because the increased windward drag is greater than the increased effective drag when the blades rotate the shaft under the influence of wind.

[0050] In this embodiment of the rotor and blades, by utilizing the aerodynamic benefits provided by adding secondary blades with different configurations, the negative (or harmful) effects of adding more primary blades with the same configuration are reduced.

[0051] To date, two-dimensional cross-sectional diagrams of the center point of one possible configuration of the primary and secondary wind turbine blades have been used to describe the utility and benefits of the primary and secondary wind turbine blades, including the wind turbine rotor, which have beneficial aerodynamic effects. In another example, in Figure 5 A three-dimensional view of the rotor configuration using the advantageous method described is provided.

[0052] Figure 5 A three-dimensional view of one embodiment is shown, in which three main blades (501A, 501B, 501C) and three secondary blades (502A, 502B, 502C) are positioned relative to an axis or axis 503.

[0053] The blades, including primary blades (501A, 501B, 501C) and secondary blades (502A, 502B, 502C), can be fixed together or fixed to a shaft for rotation about the shaft in fixed relative positions. For example, the blades can be fixed to an end cap on the shaft. In another example, the blades can be fixed to each other using structural rods, struts, trusses, etc. In yet another example, the blades can be fixed to the shaft using a hub and optional rods, struts, trusses, etc.

[0054] While the diagram shows specific dimensional relationships between the blades, rotor, and shaft, the particular configuration is not limited to any specific size or configuration. More than one rotor can be connected to a longer shaft or axle, where each connected rotor contributes to the shaft's total power output potential.

[0055] Provided Figure 2 , Figure 3 , Figure 4 and Figure 5 The specific rotor configuration shown and its individual possible blade configurations, where the relationship between alternating primary and secondary blades enables more efficient utilization of available wind energy compared to similar designs in practice.

[0056] The enhanced performance comes partly from utilizing the two surfaces of the main and secondary blades to directly transfer wind energy to the shaft and redirect wind energy that is not directly captured (or overflow / exhaust) to adjacent blades.

[0057] As previously Figure 4As described and illustrated herein, additional performance and efficiency benefits can be achieved through the configuration and positioning of the primary and secondary blades, wherein exhaust gas from the rotor provides a further beneficial effect on the total torque transmitted from the rotor to the shaft. The beneficial effects of the continuous circulation method described herein are not limited to... Figures 1 to 5 The specific rotor and blade configuration shown indicates that the method utilizes both primary and secondary blades in a favorable wind turbine rotor configuration.

[0058] Many variations of wind turbine rotors are envisioned. In the example embodiment shown, a rotor configuration using three main blades and three second-stage blades is used. The exemplary rotor configuration shown is not intended to be construed as limiting any particular number of blades, rotor size, or specific blade size or geometry to achieve the performance enhancement benefits. For example, a wind turbine rotor using two main blades and two second-stage blades can significantly improve the performance of a drag-based crossflow wind turbine using only two main blades. Therefore, a wind turbine rotor using two main blades and two or more second-stage blades between the main blades can provide further benefits. In another example, a wind turbine rotor using four main blades and four second-stage blades may also be used.

[0059] Multiple secondary blades can be used within a given set of primary blades. For example, a rotor with four primary blades can include two or more secondary blades spaced apart between the primary blades, and achieve these benefits. Thus, for example, a rotor with three primary blades and nine secondary blades (where the three secondary blades are located between each primary blade) can also be used.

[0060] In another example, a rotor with five, six, or seven or more main blades and interacting secondary blades can also be used in an advantageous configuration.

[0061] The embodiments provide improved performance for lateral axial or lateral flow wind turbine applications, particularly drag-based wind turbines. The embodiments can be advantageously used in horizontal or vertical axis applications. The embodiments include highly configurable wind turbine rotors well-suited for a variety of applications.

[0062] supply Figure 6 To illustrate the configurable nature of the wind turbine rotor, an example rotor with three main blades and three second-stage blades is used. Each of the three main blades is indicated as 601. Each second-stage blade is indicated as 611. Additional indicators show the geometric points defining the example embodiment of the rotor design to illustrate the configurable nature of the rotor design. Because the example design provides three main blades and three second-stage blades, the geometric indicators are triangular. Designs including more than three main blades or second-stage blades will result in other polygonal geometric indicators.

[0063] The outer circumference point of the main blade 601 is located at the vertex of the dashed triangle 602. The inner circumference point of the main blade 601 is located at the vertex of the dashed triangle 603. The outer circumference point of the secondary blade 611 is located at the vertex of the dashed triangle 612. The inner circumference point of the secondary blade 611 is located at the vertex of the dashed triangle 613.

[0064] Vertices can define the shape and curvature of each set of primary and secondary blades. In this embodiment, the vertices of the primary blade 601 are shown at the vertices of hash triangle 604. In this embodiment, the vertices of the secondary blade 611 are shown at the vertices of hash triangle 614.

[0065] By changing the dimensions or angles of the indicated circumferential points 602, 603, 612, 613 and vertices 604 and 614, the rotor configuration can be adjusted to achieve different performance characteristics that are advantageous for adapting to the specific wind conditions of the deployment type or location. For example, if deployed in a transverse axial flow horizontal axis configuration on a building roof facing the prevailing wind direction, the rotor configuration can be designed to take advantage of the concentrated and accelerated airflow on the building roof. In this type of deployment, multiple rotors can be advantageously used along a common axis, and each rotor can receive concentrated wind from the upward direction, a natural consequence of wind flowing over the top of the structure.

[0066] In a vertical axis (or Vawt) configuration, multiple rotors can also be used along a common axis or axial path. These advantages are available in both vertical and horizontal deployments of wind turbine rotors. As already discussed, the curvature, size, length, width, depth, and relative angle of each blade or scoop can be varied to achieve the desired effect.

[0067] For example, in one embodiment, the rotational diameter of a single rotor may be specified as one meter. Using Figure 6 As an example, and particularly as described in the diagram, each inner circumferential point of the set of main blades 601 does not directly point to the shaft. In one example, the inner circumferential point is located at a point within a range of 5% to 50% of the rotor radius from the rotor center. For example, the inner circumferential point could be located at a point within a range of 10% to 40% or 20% to 30% of the outer diameter from the rotor center along the rotor radius. In one example, the inner circumferential point of the main blade 601 could be positioned along the radius at approximately 25% of the axis of rotation. The inner circumferential point of each main blade 601 is guided (when projected along the tangent of the main blade at the inner circumferential point) away from the shaft and toward another main blade, such as... Figure 6 The inner circumference point 603 is shown in the middle.

[0068] like Figure 6As shown, the length of each main blade 601 ranges from 40% to 80% of the rotor diameter, wherein the length is determined by the distance extending along the main blade 601 between the outer circumferential point 602 and the inner circumferential point 603. For example, the length ranges from 45% to 75% or 50% to 60% of the rotor diameter. Using the provided example, the length of the main blade can be approximately 55% of the total diameter.

[0069] The curvature depth of each main blade is defined as the shortest distance from vertex 604 to a straight line extending between the outer circumference point 602 and the inner circumference point 603, ranging from 10% to 60% of the main blade length. For example, the curvature depth can range from 15% to 40% or 20% to 35% of the main blade length. The curvature depth can be approximately 25% of the length of each main blade.

[0070] With this configuration of the main blade 601, a portion of the wind passing through the concave and convex surfaces of the main blade 601 is directed into the next main blade, wherein the point of rotation of the outer edge 602 of the main blade 601 is substantially facing the wind.

[0071] The redirection of wind from one main blade 601 to the next main blade 601 (receiving main blade) occurs at a point entering the receiving main blade 601, which is located within a range of 5% to 65% of the distance from the inner circumference point of each main blade relative to the blade length. For example, relative to the blade length, the point may be within a range of 15% to 45%, or 20% or 40% of the distance from the inner circumference point of each main blade. The redirection of wind from one main blade to another may occur at approximately 33% or approximately one-third of the distance from the inner circumference point of the receiving blade.

[0072] exist Figure 6 In the example shown, when measured from the inner circumference point 603 of the main blade, the vertex 604 of the main blade 601 is located at 20% to 80% of the main blade length. For example, the range is 45% to 75% of the length, such as 50% to 70%, or approximately 66%. Such a vertex can form a complex radius curvature. In another example, the vertex 603 can be centered along the length of the main blade 601 and can form an arcuate or curved blade profile or cross-section. For example, the arc or curve can be a parabola, a circle, an ellipse, a hyperbola, an involute curve, or a complex curve. As previously mentioned, the depth of the main blade can also be adjusted by moving the vertex 604 outward from the length point of each main blade 601, the length point being defined by the distance between the outer circumference point 602 and the inner circumference point 603.

[0073] As described herein, a second-stage blade 611 is added. The second-stage blade 611 is placed between the main blades 601 and is configured to use curvature, size, length, and angle that enhance rotor performance.

[0074] exist Figure 6 In the example shown, the length of the second-stage blade 611 (measured from the inner circumference point 613 to the outer circumference point 612) ranges from 10% to 55% of the total rotor diameter. For example, the length can range from 20% to 50% of the total rotor diameter, or from 30% to 45% of the total rotor diameter. In one example, the second-stage blade can have a length of 40% or approximately two-fifths of the total rotor diameter. The apex 614 of the second-stage blade can be positioned at a location starting from its inner circumference point within a range of 40% to 90% of the blade length. For example, the apex can be positioned at a location within a range of 45% to 75% or 50% to 60% of the blade length, starting from the inner circumference point of the blade. The apex can be at 50% of the blade length or approximately at the center. The length of the second-stage blade can be from 20% to 85% of the main blade length. For example, the length of the second-stage blade can range from 40% to 80% or 50% to 75% of the main blade length. In one example, the length of the second-stage blade relative to the length of the main blade can be 70%. The inner circumferential point of the second-stage blade can be positioned at a location ranging from 45% to 85% of the radius from the shaft to the outer diameter. For example, the inner circumferential point can be positioned at a location of 50% to 75% or 55% to 70% of the radius from the shaft to the outer diameter. In one example, the inner circumferential point of the second-stage blade can be positioned at 65% of the distance between the rotor radius and the center of rotation. The inner circumferential point of the second-stage blade is positioned much further from the shaft than the inner circumferential point of the main blade.

[0075] exist Figure 6 In the example shown, air passing through the convex and concave surfaces of the secondary blade 611 is also guided into the adjacent primary blade, wherein, when measured from the outer peripheral point 602 of the adjacent primary blade 601, the secondary blade guides bypass air into the adjacent primary blade 602 at a point ranging from 15% to 50% of the length of the adjacent primary blade. For example, when measured from the outer peripheral point 602 of the primary blade 601, the point may be in the range of 20% to 45% or 30% to 40%. When measured from the outer peripheral point 602 of the primary blade 601, the point may be 33% or approximately one-third of the length of the primary blade 601.

[0076] Relative to the inner circumference point 613 and inner circumference of the second-stage blade 611, the space between the concave surface of the second-stage blade 611 and the convex surface of the main blade 601 is slightly reduced from the point between the outer circumference point 612 of the second-stage blade 611 and the outer circumference point 602 of the main blade 602 to point 603 of the main blade 601. The air passing between the main blade 601 and the second-stage blade 611 is accelerated and guided into the concave surface of the adjacent main blade 601.

[0077] The "inlet point" is located near the outer circumference point 612 of the second-stage blade 611 and the apex of the main blade 602. The "outlet point" is approximately located between the inner circumference point 613 of the second-stage blade 611 and the inner circumference point 602 of the main blade 601. The cross-sectional area of ​​the outlet point is 65% to 95% of the cross-sectional area of ​​the inlet point. For example, the area of ​​the outlet point can be in the range of 70% to 90% or 75% to 85% of the area of ​​the inlet point. In one example, the area of ​​the outlet point relative to the area of ​​the inlet point can be 80%.

[0078] Figure 7 The rotor configuration shown uses four main blades and four secondary blades, all of which have an arcuate cross-sectional profile. Figure 7 The embodiments provided the benefits of continuous cyclic effects, demonstrating the configurable nature of wind turbine rotors. Figure 7 The image shows the positioning of four main blades (701, 702, 703, 704) and four secondary blades (711, 712, 713, 714) relative to the axis of rotation.

[0079] The main outer blade frame 705, main inner blade frame 706, and main blade apex frame 707 illustrate the length, depth, and curvature of the main blade. Similarly, the auxiliary outer blade frame 715, auxiliary inner blade frame 716, and secondary blade apex frame 717 illustrate the length, depth, and curvature of the secondary blade. The main blade and secondary blade can have [specific features related to...]. Figure 6 The descriptions of those similar lengths, dimensions, curvatures, and positions.

[0080] The wind vector is approximately pointed towards the dashed line of the wind turbine rotor, where the wind originates from the right relative to the direction of the diagram. In the view, the wind vector line represents the general path or airflow as the wind passes over the convex surface of the main blade 702 and below the concave surface of the second-stage blade 711.

[0081] The "entry point" is located near the outer frame point of the second-stage blade 711 and the apex of the main blade 702. The "exit point" is roughly located between the inner frame point of the second-stage blade 711 and the inner frame point of the main blade 702. Figure 7 In the examples used, the cross-sectional area at the exit point is 65% to 95% of the cross-sectional area at the inlet point. For example, the area of ​​the exit point can be in the range of 70% to 90% or 75% to 85% of the area of ​​the inlet point. In one example, the area of ​​the "exit point" relative to the area of ​​the inlet point can be 80%.

[0082] As shown in the figure, wind passing beneath the convex surface of the main blade 702 and the concave surface of the secondary blade 711 is guided to the concave surface of the main blade 701. This configuration increases the amount of wind force guided into the main blade 701.

[0083] Such as about Figure 1 As mentioned above, in Figure 7 In the middle, the secondary blades 711, 712, 713 and 714 can be configured in shape, angle and position to produce an acceleration effect when wind enters the indicated inlet point of the main blade 702 and the secondary blade 711 and the indicated outlet point between the main blade 702 and the secondary blade 711.

[0084] The inlet point can be approximately 10% larger than the outlet point. The length of the secondary blade, or its distance from the outer frame point and the inner frame point, is approximately 50% of the length of the primary blade.

[0085] The relative size and position of the primary and secondary blades can vary due to a number of factors. These factors include the rotor diameter, the number of primary and secondary blades, the deployment type (horizontal or vertical), and whether external shielding or reinforcement is used during deployment.

[0086] Although the term "framework" is used to define Figure 7 and Figure 6 The inner and outer points of each primary and secondary blade are specified, but this does not imply any specific construction method that restricts the blades around the rotor. Figure 6 The triangular indicators shown as the main blade inner frame, main blade outer frame, secondary blade inner frame, and secondary blade outer frame are intended to illustrate the relational geometry of each blade in one possible embodiment, wherein the wind turbine rotor includes three main blades and three secondary blades about a central axis of rotation. Figure 6 Triangular indicators marking the vertices of the primary and secondary blades are provided to show the deepest point of each blade.

[0087] Similarly, Figure 7 The labels provided, particularly 705, 706, 707, 715, 716, and 717, are also intended to aid in understanding the geometry of this embodiment using a rotor configuration comprising four main blades and four secondary blades. While using interior and exterior points on each of the main and secondary blades for the structural frame may be advantageous, other structural frame methods are conceivable. Various methods exist for connecting or securing wind turbine blades to the central shaft or hub.

[0088] Figure 8 Another example of a rotor configuration is shown, where the rotor uses four main blades and eight additional blades (e.g., four second-stage and four third-stage blades). The four main blades are designated 801A, 801B, 801C, and 801D. A set of second-stage blades is designated 811A, 811B, 811C, and 811D. A set of third-stage blades is designated 821A, 821B, 821C, and 821D. In order to... Figure 8For clarity in the description, the group of three-stage blades can be described as "boosting blades". In the rotor configuration, each main blade has as described above regarding... Figure 6 The length mentioned above may be approximately 60% of the rotor diameter, and the blade depth at the center of the arcuate blade may be as described above. Figure 6 As described above, or it could be approximately 30% of the length of each primary blade. The secondary blades each have as described above regarding... Figure 6 The length mentioned above, or approximately 30% of the rotor diameter, and having the characteristics described above relative to... Figure 6 The depth described may be approximately 20% of the length of each secondary blade.

[0089] The size of the third-stage blade can be smaller than that of the first-stage blade or the second-stage blade. For example, the relative length of the third-stage blade (along the blade from the inner circumference point to the outer circumference point) compared to the entire rotor diameter can be in the range of 10% to 25%. In one example, the relative length can be in the range of 12% to 18% or 14% to 16% of the rotor diameter. In one example, the relative length of the third-stage blade can be 15%. The location of the inner circumference point of the third-stage blade is farther from the rotor's central axis 803 than that of the first- and second-stage blades. For example, the inner circumference point can be set at 70% to 90% of the radius from the shaft or center point to the outer diameter, for example, at 80% to 95% of the radius. The depth of the third-stage blade can be in the range of 5% to 25% of the blade length. For example, the depth can be in the range of 8% to 22% or 10% to 20% of the blade length. In one example, the depth can be 15% of the blade length.

[0090] exist Figure 8 In the diagram, relative to the drawing direction, the wind direction toward the wind turbine rotor is generally from the right. There are three indicators marked as wind vectors, near the dashed line pointing inwards towards the interior of the second-stage blade 801A. A wind vector line is shown passing between the main blade 801B and the second-stage blade 811B. A second wind vector line is shown passing between the second-stage blade 811B and the booster blade 821B. A third wind vector line is shown passing through the booster blade 821B and entering the main blade 801A.

[0091] The "concentrated wind zone" is located within the concave area of ​​the main blade 801A, where the dashed wind vector line essentially points towards the area of ​​the rotor. In this embodiment, the wind turbine rotor can apply more torque to the shaft or axis as a result of the concentrated airflow that may enter the main blade from the second-stage blade.

[0092] The "deflecting wind" flows into a portion of the wind turbine, which is deflected back into the wind during rotation. The rotation direction shown in the illustration is counterclockwise. In the rotation position shown, the booster blade 821C deflects a portion of the wind upward into the concave region of the main blade 801B and deflects a portion of the wind downward into the partially exposed region of the convex surface of the second-stage blade 811C.

[0093] As further shown, the second-stage blade 811C will also essentially reduce the wind relative to... Figure 8 The direction of the wind deflects downwards. "Downwards" is intended to aid understanding of the diagram. The downwards direction can also be described as an outwards direction, where the wind deflects away from the center of rotation.

[0094] Due to the wind deflection generated by the booster blade 821C, the main blade 801C is essentially blocked in the incoming wind and then further deflected by the second-stage blade 811C. As a result, the back pressure received by the main blade 801C when returning to the wind is lower than when implemented on the rotor without the use of the second or third-stage blades.

[0095] Another significant advantage is that when the main blade 801C is in the illustrated rotating position, it almost completely blocks the return drag of the subsequent booster blade 821D and second-stage blade 811D. This demonstrates the aforementioned advantage, where additional blades can be added to a drag-based crossflow wind turbine rotor, which can increase wind capture and enhance the performance of the wind turbine rotor without adding additional return drag.

[0096] Rotor blades can be interconnected or connected to a shaft (shaft / axle) via various structures. For example, blades can be attached to end caps, which in turn are attached to a shaft. In another example, blades can be connected to a shaft or axle using separate hubs and struts or rods.

[0097] For example, such as Figure 9 As shown, rotor blades 904 can be connected to end caps 906, which are connected to shaft 902. Blades 904 are held in a fixed position relative to other blades 904 via end caps 906. Although one rotor including a set of blades connected to the end cap is shown, more than one rotor can be connected to shaft 902. Optionally, shaft 902 can be directly connected to generator 908, such as an axial flux generator, or alternatively, it can be indirectly connected to the generator via other mechanisms. For example, shaft 902 can be connected to the generator using mechanical transmission methods such as chains and sprockets, gears, pulley systems, friction drives, fluid drives, continuously variable transmissions (CVTs), or other transmission methods.

[0098] exist Figure 10In another example shown, blades 1004 or 1006 are connected to shaft 1002 via hub 1008. Blades 1004 or 1006 can be connected to the hub directly or via brackets, struts, or trusses. For example, blades 1004 of a rotor assembly can each be attached to shaft 1002, while rotors 1006 of another rotor assembly can each be connected to shaft 1002. In one example, shaft 1002 can be connected to generator 1012 via chain and sprocket 1014, pulley system, or another gear ratio drive mechanism.

[0099] exist Figure 11 In another example shown, the blades 1104 of the rotor assembly may be connected to the generator housing 1006. The generator housing 1106 rotates and has a shaft 1108 that remains stationary. The shaft 1108 is connected to the top of the tower 1102.

[0100] In another example, one or more enhancement devices may be positioned around the rotor. Enhancement devices can collect wind from a larger area, concentrate wind, or partially block wind. In one example, the enhancement device is fixed relative to one or more rotors. The enhancement device may be fixed relative to the axis or shaft as the rotor blades rotate about it. For example, the number of enhancement devices may range from 1 to 12, such as a range of 4 to 10 or 6 to 10 areas.

[0101] For example, the length of the reinforcing device can be measured from the point closest to the rotor to the farthest point along the reinforcing device. In one example, the length of the reinforcing device can be in the range of 0.1 to 10 times the rotor diameter. For example, the length of the reinforcing device can be in the range of 0.5 to 5 times the rotor diameter, such as 0.5 to 2 times the rotor diameter.

[0102] Furthermore, the reinforcing device can be positioned at an angle relative to the radial direction extending from or from the shaft. In the example, the angle can be in the range of 10° to 90°, such as the range of 15° to 70°, 15° to 60°, or 25° to 50°.

[0103] In another example, the enhancement device can have a shape such as a straight line or a curve. In this example, the curve shape can be a parabola, a circle, an ellipse, a hyperbola, an involute curve, or a complex curve. For example, the curve can be an involute curve or a complex curve. In another example, the curve can be a parabola. In yet another example, the shape can be straight.

[0104] For example, Figure 12 and Figure 13A reinforcing device 1204 is shown distributed around the rotor 1202. The length of the reinforcing device 1204 is greater than the diameter of the rotor 1202, for example, 1.2 to 2 times the diameter of the rotor 1202. The reinforcing device 1204 is arranged at an angle of 45° relative to the radial direction extending from the shaft 1203. As shown, the reinforcing devices 1204 are arranged in fixed positions evenly distributed around the rotor. For example, four reinforcing devices 1204 are distributed around the rotor 1202 at a 90° offset. Figure 12 In the image, air 1206 is shown entering from a direction relative to the fixed reinforcing device 1204. Most of the air is concentrated in the rotor. Figure 13 The diagram illustrates wind 1306 entering from different directions relative to a fixed position relative to the enhancement device 1204. Some of the wind 1306 is concentrated by the enhancement device 1204, while some is deflected by it. A small portion of the wind 1306 may impact the rotor at the point where the blades return. Compared to conventional designs, the rotor design described above is advantageously less sensitive to such impacts and more capable of deflecting them.

[0105] Figure 14 and Figure 15 A reinforcing device 1404 is shown distributed around the rotor 1402. The length of the reinforcing device 1404 is less than the diameter of the rotor 1402. For example, the length can be in the range of 0.5 to 0.95 times the diameter of the rotor 1402. The reinforcing device 1404 is arranged at an angle of 45° relative to the radial direction extending from the axis of the rotor 1402. Figure 14 As shown, most of the airflow 1406 is concentrated in the rotor 1402. When the airflow 1506 enters from a different direction relative to the enhancement device 1404, for example, as Figure 15 As shown, more of the wind 1506 can be deflected or concentrated by a different set of enhancement devices 1404. Here, a small portion of the wind 1506 can impact the rotor at the location where the blades return. Compared to conventional designs, the rotor design described above is advantageously less sensitive to such impacts and more capable of deflecting them.

[0106] Figure 16 and Figure 17 The use of linear enhancement devices, such as enhancement devices 1604 or 1704, is shown. Figure 16 As shown, reinforcement devices 1604, with a length smaller than the diameter of rotor 1602, are uniformly distributed around rotor 1602. For example, eight reinforcement devices 1604 are distributed around rotor 1604, and gather more airflow 1606 than a single rotor 1602, concentrating some airflow 1606 into rotor 1602. In another example, Figure 17 A larger linear reinforcement device 1704 is shown distributed around the rotor 1702. In one example, the length of the reinforcement device 1704 may be greater than the diameter of the rotor 1702.

[0107] In a further example, Figure 18 and Figure 19 This includes eight curved reinforcing devices 1804 distributed around the rotor 1802. (The text abruptly ends here.) Figure 18 The wind 1806 in the direction shown is concentrated or deflected. Similarly, as... Figure 19 As shown, winds 1906 entering from different directions are concentrated or deflected away from rotor 1802 by different enhancement devices 1804.

[0108] In another example, a single reinforcement or retaining wall of a building can be used to partially block wind. For example, such as Figure 20 As shown, a reinforcement device or guardrail 2004 can be installed to partially block wind approaching the horizontal rotor 2002 located on the horizontal surface 2006. The wind can be blocked by impacting the second-stage rotor blades, which are moving back to their receiving position.

[0109] In another example, a single reinforcement device or retaining wall can be tilted to direct wind into the rotor while preventing wind from impacting the return side. For example, Figure 21 An angled amplification device 2104 is shown, which directs airflow into a rotor 2102, which is horizontally positioned on a surface 2104, such as the roof of a building. The amplification device 2104 is arranged at an angle relative to the surface, for example, within the range of 15° to 80°, 25° to 70°, or 35° to 60°.

[0110] The examples provide various improvements to the design of drag-based crossflow wind turbine rotors. A key advantage is the improved performance achieved by using different configurations of main and second-stage blades within the rotor.

[0111] When using this wind turbine rotor design, there can be many variations. For example, when used in a transverse axial (or crossflow) horizontal axis configuration, the rotor configuration can be adjusted to take advantage of the concentrated wind force and direction if external reinforcements are added to one or both of the upper and lower regions around the wind turbine rotor assembly to further concentrate the wind into the rotor.

[0112] When used in vertical axis wind turbine applications, the rotor can be specifically configured for the wind conditions at the deployment site. In stand-alone vertical axis deployments, the advantages and benefits of the continuous circulation method described herein can be realized from all wind angles.

[0113] Various configurations of wind turbine rotors are available to suit low, medium, or strong wind conditions and can be fine-tuned. For example, the embodiments of the wind turbine rotor designs presented are not limited to any particular size. In one embodiment, the components for the finished rotor assembly can be designed to allow the transport of one or more rotors on a standard transport pallet. In some cases, larger or smaller rotor assemblies may be required.

[0114] The rotor can be made of a variety of materials. For example, materials such as fiberglass, plastic or aluminum, steel, alloys, textiles or other materials, or any combination of these materials, can be used in the construction of the rotor and its blades.

[0115] Various configurations or geometries of the rotor and its individual blades can be used. For example, the cross-sectional view shown in the figures is a specific aerodynamically improved embodiment using blade curvature along a single axis for each blade. The surface of each individual blade can have curvature or geometry that varies across multiple axes. For example, if the surface of each blade is curved along the X and Y axes, using a generally rectangular shape, the blade can resemble a rectangular parabolic disc. If the blade surface is curved along a single axis, such as... Figure 5 As shown, sidewalls or end caps can be added to span the region from the outer diameter point to the inner diameter point on either side of the blade, as well as the region that fully reaches the blade curvature. The geometry of the sidewalls can also be changed.

[0116] Wind turbines can be connected to various mechanical or electrical systems to transfer mechanical energy to other devices. For example, a wind turbine can be connected to a generator to produce electricity using the mechanical energy harvested from the wind. In another example, a wind turbine can be connected to a mechanical system such as a pump or momentum storage system.

[0117] In a first embodiment, the wind turbine rotor includes a shaft, a plurality of main blades arranged at regular intervals around the shaft, and a plurality of second-stage blades arranged around the shaft between the main blades. Each of the plurality of second-stage blades is smaller than each of the plurality of main blades.

[0118] In the example of the first embodiment, the length of each second-stage blade is in the range of 20% to 50% of the diameter of the wind turbine rotor.

[0119] In the first embodiment and another example of the above embodiments, the vertex of each secondary blade is from 40% to 90% of the length of each secondary blade along the inner circumference point of each secondary blade.

[0120] In the first embodiment and another example of the above examples, the length of each secondary blade is 20% to 85% of the length of each primary blade.

[0121] In the first embodiment and the additional examples described above, the inner circumference point of each secondary blade is 45% to 85% of the radius extending from the shaft to the outer diameter.

[0122] In the first embodiment and another example of the above examples, the inner circumference point of each secondary blade is farther from the axis than the inner circumference point of each primary blade.

[0123] In the first embodiment and another example of the above examples, the area at the exit point between each secondary blade and each primary blade is smaller than the area at the inlet point between each secondary blade and each primary blade.

[0124] In the first embodiment and another example of the above examples, the area at the exit point between each secondary blade and each primary blade is between 65% and 90% of the area at the inlet point between each secondary blade and each primary blade.

[0125] In the first embodiment and another example of the above examples, the inner circumference point of each main blade is 5% to 50% of the radius from the shaft to the outer diameter.

[0126] In the first embodiment and another example of the above examples, the length of each main blade is 40% to 90% of the diameter of the wind turbine rotor.

[0127] In the first embodiment and the additional examples of the above examples, the curvature depth of each main blade is 10% to 60% of the length of each main blade.

[0128] In another example of the first embodiment and the above examples, the wind turbine rotor further includes a plurality of tertiary blades disposed between a plurality of primary blades and a plurality of secondary blades. For example, each of the plurality of tertiary blades is smaller than each of the plurality of secondary blades. In another example, each of the plurality of tertiary blades has a relative length of 10% to 25% of the wind turbine rotor diameter. In another example, each of the plurality of tertiary blades has a curvature depth of 8% to 22% of the length of each tertiary blade.

[0129] In the first embodiment and another example of the above examples, the shaft of the wind turbine rotor is arranged vertically.

[0130] In the first embodiment and the additional examples described above, the wind turbine rotor shaft is arranged horizontally.

[0131] In a second embodiment, the wind turbine system for power generation includes a generator and a wind turbine rotor. The wind turbine includes a shaft mechanically coupled to the generator, a plurality of main blades arranged at regular intervals around the shaft, and a plurality of second-stage blades arranged around the shaft among the main blades. Each of the plurality of second-stage blades is smaller than each of the plurality of main blades.

[0132] In the example of the second embodiment, the shafts are directly mechanically connected.

[0133] In another example of the second embodiment and the examples described above, the shaft is mechanically connected using chains and sprockets, gears, pulley systems, friction drives, fluid drives, or continuously variable transmissions (CVTs).

[0134] In the second embodiment and another example of the above examples, the wind turbine system further includes a plurality of reinforcement devices arranged at fixed locations around the wind turbine rotor. For example, one of the reinforcement devices is straight. In another example, one of the reinforcement devices is curved. In yet another example, the curved reinforcement device has a shape including parabolic, circular, elliptical, hyperbolic, involute, or complex curves. In yet another example, one of the reinforcement devices is positioned at an angle of 10° to 90° relative to a radial direction extending from the axle. In yet another example, the length of the reinforcement device is in the range of 0.1 to 10 times the diameter of the wind turbine rotor. For example, the length is 0.5 to 5 times the diameter of the wind turbine rotor.

[0135] In the example of the second embodiment, the length of each second-stage blade is in the range of 20% to 50% of the diameter of the wind turbine rotor.

[0136] In another example of the second embodiment and the example above, the vertex of each secondary blade is from 40% to 90% of the length of each secondary blade along the inner circumference point of each secondary blade.

[0137] In the second embodiment and another example of the above examples, the length of each secondary blade is 20% to 85% of the length of each primary blade.

[0138] In the second embodiment and the additional examples of the above examples, the inner circumference point of each secondary blade is 45% to 85% of the radius extending from the shaft to the outer diameter.

[0139] In the second embodiment and another example of the above examples, the inner circumference point of each secondary blade is farther from the axis than the inner circumference point of each primary blade.

[0140] In the second embodiment and another example of the above examples, the area at the exit point between each secondary blade and each primary blade is smaller than the area at the inlet point between each secondary blade and each primary blade.

[0141] In the second embodiment and the additional examples of the above examples, the area at the exit point between each secondary blade and each primary blade is between 65% and 90% of the area at the inlet point between each secondary blade and each primary blade.

[0142] In another example of the second embodiment and the example described above, the inner circumference point of each main blade is 5% to 50% of the radius from the shaft to the outer diameter.

[0143] In the second embodiment and another example of the above examples, the length of each main blade is 40% to 90% of the diameter of the wind turbine rotor.

[0144] In the second embodiment and the additional examples of the above examples, the curvature depth of each main blade is 10% to 60% of the length of each main blade.

[0145] In the second embodiment and another example of the above examples, the wind turbine rotor further includes a plurality of tertiary blades disposed between a plurality of primary blades and a plurality of secondary blades. For example, each of the plurality of tertiary blades is smaller than each of the plurality of secondary blades. In another example, each of the plurality of tertiary blades has a relative length of 10% to 25% of the wind turbine rotor diameter. In another example, each of the plurality of tertiary blades has a curvature depth of 8% to 22% of the length of each tertiary blade.

[0146] In the second embodiment and another example of the above examples, the shaft of the wind turbine rotor is arranged vertically.

[0147] In the second embodiment and the additional examples of the above examples, the shaft of the wind turbine rotor is arranged horizontally.

[0148] In a third embodiment, a power generation method includes installing a wind turbine system in a wind path. The wind turbine system includes a generator and a wind turbine rotor. The wind turbine rotor includes a shaft mechanically connected to the generator, a plurality of main blades arranged at regular intervals around the shaft, and a plurality of second-stage blades arranged around the shaft between the main blades. Each of the plurality of second-stage blades is smaller than each of the plurality of main blades.

[0149] In the foregoing specification, the concepts have been described with reference to specific embodiments. However, those skilled in the art will recognize that various modifications and changes can be made without departing from the scope of the invention as set forth in the following claims. Therefore, the specification and drawings should be considered illustrative rather than restrictive, and all such modifications should be included within the scope of the invention.

[0150] As used herein, the terms “comprising,” “including,” “having,” or any other variations thereof are intended to cover non-exclusive inclusion. For example, a process, method, article, or apparatus that includes a list of features is not necessarily limited to those features, but may include other features not expressly listed or inherent to such a process, method, article, or apparatus. Furthermore, unless explicitly stated otherwise, “or” refers to an inclusive or, not an exclusive, or. For example, condition A or B satisfies either: A is true (or exists), B is false (or does not exist); A is false (or does not exist) and B is true (or exists); and both A and B are true (exist).

[0151] Furthermore, the term "a / an" is used to describe the elements and components described herein. This is done merely for convenience and to give a general meaning to the scope of the invention. This specification should be understood to include one or at least one, and the singular includes the plural, unless it is obvious otherwise.

[0152] The benefits, other advantages, and solutions to problems have been described above with reference to specific embodiments. However, the benefits, advantages, solutions to problems, and any features that may lead to or make more apparent any benefit, advantage, or solution shall not be construed as key, essential, or fundamental features of any or all claims.

[0153] Upon reading this specification, those skilled in the art will recognize that, for clarity, certain features described herein in the context of individual embodiments may also be provided in combination in a single embodiment. Conversely, for brevity, the various features described in the context of a single embodiment may also be provided individually or in any sub-combination. Furthermore, references to values ​​within the scope include every value within the scope.

Claims

1. A wind turbine system driven by a wind turbine, the wind turbine comprising: Multiple main blades arranged at regular intervals around the axis; and Multiple secondary blades are arranged around the axis such that each secondary blade is located between a pair of consecutive adjacent main blades among the multiple main blades. The size of each secondary blade is smaller than that of each main blade among the multiple main blades. The position and orientation of each secondary blade are configured to block the wind from the adjacent subsequent main blades among the multiple main blades in the direction of rotation of the axis. as well as Multiple tertiary blades are arranged around the axis. In the direction of rotation of the axis, each tertiary blade is located between the concave surface of the immediately preceding adjacent primary blade and the convex surface of the immediately following adjacent secondary blade. The size of each tertiary blade is smaller than that of each secondary blade. The primary and secondary blades alternately contribute to the torque transmitted to the axis by redirecting the crossflow. The crossflow simultaneously applies wind force to the convex surfaces of the primary and secondary blades that return to the crossflow during rotation, and to the concave surfaces of the primary and secondary blades that move away from the crossflow during rotation.

2. The wind turbine system according to claim 1, characterized in that, The relative length of each of the plurality of third-stage blades is 10% to 25% of the outer diameter of the wind turbine.

3. The wind turbine system according to claim 1, characterized in that, The plurality of main blades further includes three main blades, and the plurality of secondary blades further includes three secondary blades.

4. The wind turbine system according to claim 1, characterized in that, The plurality of main blades further includes at least four main blades.

5. The wind turbine system of claim 1, further comprising at least one reinforcement device disposed around the shaft, wherein the position of the at least one reinforcement device remains fixed such that rotation of the shaft and / or rotation of the turbine rotor disposed around the shaft does not affect the fixed position of the at least one reinforcement device.

6. The wind turbine system according to claim 5, characterized in that, The at least one reinforcement device further includes a plurality of reinforcement devices distributed around the axis.

7. The wind turbine system according to claim 5, characterized in that, The at least one reinforcing device further includes at least one bending reinforcing device.

8. The wind turbine system according to claim 5, characterized in that, The at least one enhancement device further includes at least one direct enhancement device.

9. The wind turbine system of claim 1, further comprising a generator connected to the shaft of the wind turbine.

10. The wind turbine system of claim 9, wherein the shaft is directly mechanically connected to the generator.

11. The wind turbine system of claim 9, wherein the shaft is indirectly mechanically connected to the generator.

12. The wind turbine system of claim 11, wherein the shaft is indirectly mechanically connected to the generator by one of the following methods: chain and sprocket, gear, belt and pulley system, friction drive, fluid drive, and continuously variable transmission (CVT).

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