Blade assembly and wind power generation device

Abstract

The present application provides a blade assembly and a wind power generation device. The blade assembly comprises a mounting shaft and a blade connected to the mounting shaft. The blade has opposite first and second surfaces along the circumferential direction of the mounting shaft. The first surface is recessed toward the second surface to form a force-bearing groove configured to bear wind impact, so that the blade assembly rotates. The torque of the blade Mθ=F0 × L=cos2 θFwind × L, where F0 is an equivalent resultant force applied to the blade, L is a moment arm, θ is a rotation angle, and Fwind is an equivalent wind force when θ is 0 degrees. The power of the blade P=Mθ × w=F0 × L × w, where w is an angular velocity. A discharge hole is provided at the bottom of the force-bearing groove, and is disposed near the mounting shaft and used for discharging air, so that the position of the equivalent resultant force is away from the mounting shaft, thereby lengthening the moment arm, increasing the torque, and improving the power.

Description

Blade assemblies and wind power generation devices

[0001] This application claims priority to Chinese patent application filed on June 19, 2024, with application number 202410791577.2 and entitled "Blade Assembly and Wind Power Generation Device", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of wind power generation technology, and in particular to a blade assembly and a wind power generation device. Background Technology

[0003] Wind energy is an inexhaustible natural resource. Using wind power will not lead to resource depletion, and the process of wind power generation does not produce greenhouse gas emissions, thus having a minimal impact on the environment. A wind power generation device is a device that converts wind energy into electrical energy. It uses wind power to drive blade assemblies to rotate, which in turn drives a generator to rotate, generating electricity through the principle of electromagnetic induction. Typically, a wind power generation device includes a generator and blade assemblies. The blade assemblies are rotatably connected to the generator. Wind acts on the blade assemblies, causing them to rotate relative to the generator, thereby generating electricity.

[0004] However, existing technologies for blade assembly design typically focus on the strength, stiffness, and weight of the blades themselves, with limited research on technical solutions for improving the torque provided by the blades, thereby increasing the power of the blade assembly.

[0005] Application content

[0006] This application provides a blade assembly and a wind power generation device that overcomes or at least partially solves the above-mentioned problems.

[0007] According to one aspect of the embodiments of this application, a blade assembly is provided, comprising: a mounting shaft rotatably connected to an external device; and a blade connected to the mounting shaft, the blade having a first surface and a second surface disposed opposite to each other along the circumference of the mounting shaft, the first surface being recessed toward the second surface, and a force-bearing groove being formed on the first surface, the force-bearing groove being used to withstand wind impact, causing the blade assembly to rotate relative to the external device; the torque provided by the blade satisfies: M θ =F0×L=cos 2 θF wind ×L; where M θ Let F0 be the torque acting on the blade, F0 be the equivalent resultant force acting on the blade, L be the lever arm of the equivalent resultant force, and θ be the rotation angle of the blade. wind When θ is 0 degrees, the equivalent wind force experienced by the blade is F. windThe plane perpendicular to the plane containing the groove of the force-bearing groove of the blade; the power provided by the blade satisfies: P = M θ ×w=F0×L×w=cos 2 θF wind ×L×w; where w is the angular velocity of the blade rotation; the bottom of the force groove is provided with a drain hole, which is located close to the mounting shaft. The drain hole is used to discharge air after it impacts the force groove, so that the position of the equivalent resultant force is far away from the mounting shaft.

[0008] In one alternative approach, the cross-sectional area of ​​the stress groove gradually decreases along the direction from the opening of the groove to the bottom of the groove.

[0009] In one alternative embodiment, along the radial direction of the mounting shaft, the bottom of the force-bearing groove has a first guide surface and a second guide surface disposed opposite to each other, the drain hole is disposed on the first guide surface, the first guide surface and the second guide surface are respectively inclined toward the center of the force-bearing groove, and both the first guide surface and the second guide surface are used to guide the airflow.

[0010] In one alternative approach, the number of drainage holes is multiple, and the multiple drainage holes are distributed on the first guide surface to form multiple stress zones on the first guide surface.

[0011] In one alternative embodiment, the distance between the bottom of the stress groove and the opening of the stress groove along the first guide surface is less than the distance between the bottom of the stress groove and the opening of the stress groove along the second guide surface.

[0012] In one alternative, the second guide surface is recessed toward the second surface to form a flow-gathering area, and the first guide surface protrudes toward the direction away from the second surface to form a flow-draining area.

[0013] In one alternative embodiment, the blade assembly further includes a mounting bracket connected to an external device; the mounting bracket is provided with a groove and an inlet communicating with the groove, the blade is disposed in the groove, the inlet is used to allow air to enter the groove and impact the stress groove; the mounting bracket is provided with a plurality of exhaust holes communicating with the groove, the plurality of exhaust holes being disposed near the inlet, the plurality of exhaust holes being used for air discharge.

[0014] In one alternative approach, the cross-sectional area of ​​the exhaust port gradually increases in the direction away from the inlet.

[0015] In one alternative approach, when viewed along the direction of the mounting axis, the mounting bracket is a circle with a notch, the notch corresponding to the inlet; when viewed along the direction of the mounting axis, the plurality of exhaust holes are arranged from the inlet along the circumference of the circle to form a first arc, the first arc having a first preset arc angle less than 45 degrees.

[0016] According to another aspect of the embodiments of this application, a wind power generation device is provided, including a generator and the blade assembly described above, the blade assembly being connected to the generator.

[0017] The beneficial effects of this application embodiment are as follows: This application embodiment provides a blade assembly, including a mounting shaft rotatably connected to an external device; a blade connected to the mounting shaft, the blade having a first surface and a second surface disposed opposite to each other along the circumference of the mounting shaft, the first surface being recessed toward the second surface, and a force-bearing groove being formed on the first surface, the force-bearing groove being used to withstand wind impact, causing the blade assembly to rotate relative to the external device; the torque provided by the blade satisfies: M θ =F0×L=cos 2 θF wind ×L; where M θ Let F0 be the torque acting on the blade, F0 be the equivalent resultant force acting on the blade, L be the lever arm of the equivalent resultant force, and θ be the rotation angle of the blade. wind When θ is 0 degrees, the equivalent wind force experienced by the blade is F. wind The plane perpendicular to the plane containing the groove of the force-bearing groove of the blade; the power provided by the blade satisfies: P = M θ ×w=F0×L×w=cos 2 θF wind ×L×w; where w is the angular velocity of the blade rotation; a drain hole is provided at the bottom of the force-receiving groove, the drain hole is located close to the mounting shaft, and the drain hole is used to allow air to impact the force-receiving groove and then discharge, so that the position of the equivalent resultant force is far away from the mounting shaft. Through the above method, since the blade is provided with a drain hole, and the drain hole is located close to the mounting shaft, the position of the equivalent resultant force on the blade is far away from the mounting shaft, that is, the lever arm of the equivalent resultant force is lengthened. Since torque is the product of the equivalent resultant force and the lever arm, the torque on the blade is greater. Since power is the product of torque and angular velocity, under the premise of equal angular velocity, the power of the blade assembly provided in this application embodiment is improved. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the specific embodiments of this application or the prior art, the accompanying drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. In all the drawings, similar elements or parts are generally identified by similar reference numerals. In the drawings, the elements or parts are not necessarily drawn to scale.

[0019] Figure 1 is a schematic diagram of the blade assembly provided in an embodiment of this application;

[0020] Figure 2 is a schematic diagram of the forces acting on the blade provided in an embodiment of this application;

[0021] Figure 3 is a simplified schematic diagram of the forces acting on the blade provided in the embodiment of this application;

[0022] Figure 4 is a schematic diagram of the equivalent force on the blade provided in the embodiment of this application;

[0023] Figure 5 is a diagram showing the torque transformation of the blade provided in the embodiment of this application;

[0024] Figure 6 is a schematic diagram of the torque of the blade provided in the embodiment of this application;

[0025] Figure 7 is a force diagram of the blade after it rotates at a certain angle according to an embodiment of this application;

[0026] Figure 8 is another form of the force diagram of the blade after it rotates at a certain angle according to the embodiment of this application;

[0027] Figure 9 is a schematic diagram of the blades provided in the embodiment of this application without drainage holes;

[0028] Figure 10 is a schematic diagram of the blades with drainage holes provided in an embodiment of this application;

[0029] Figure 11 shows the power curve of the blade assembly;

[0030] Figure 12 is a partial cross-sectional view along QQ in Figure 1 provided in an embodiment of this application;

[0031] Figure 13 is a schematic diagram of the blade and mounting shaft in an exploded state according to an embodiment of this application;

[0032] Figure 14 is another schematic diagram of the blade and mounting shaft in an exploded state according to an embodiment of this application.

[0033] Figure 15 is an enlarged view of part A in Figure 14 provided in the embodiment of this application;

[0034] Figure 16 is a schematic diagram of the blades disposed on the mounting frame according to an embodiment of this application;

[0035] Figure 17 is a schematic diagram of the mounting bracket provided in the embodiment of this application without ventilation holes;

[0036] Figure 18 is a schematic diagram of the mounting bracket provided in the embodiment of this application having an exhaust opening;

[0037] Figure 19 is a schematic diagram of the mounting bracket provided in the embodiment of this application having an exhaust hole;

[0038] Figure 20 shows the torque curve of a single blade;

[0039] Figure 21 shows the torque curve of the mounting bracket provided in the embodiment of this application without an exhaust vent.

[0040] Figure 22 is a torque curve of the mounting bracket with exhaust holes provided in the embodiment of this application;

[0041] Figure 23 is a comparison of the torque curves of the blade assembly provided in the embodiments of this application;

[0042] Figure 24 is a schematic diagram of the torque standard deviation of the blade assembly;

[0043] Figure 25 is a schematic diagram of another perspective of Figure 19 provided in an embodiment of this application.

[0044] Figure label:

[0045] 100. Blade assembly;

[0046] 10. Blade; 10a. First surface; 10b. Second surface; 10c. Stress groove; 10d. First guide surface; 10e. Second guide surface; 10f. Drain hole; 10d1. Stress zone; 10d2. Drain zone; 10e1. Convergence zone; 10g. Through hole;

[0047] a1, first preset arc angle; a2, second preset arc angle;

[0048] 20. Mounting shaft; 201. Mounting part; 202. Connecting part; 20a. Step; 201a. Screw hole;

[0049] 30. Limiting component; 301. Straight part; 302. Bending part; 30a. Limiting groove.

[0050] 40. Mounting bracket; 40a. Groove; 40b. Inlet; 40c. Exhaust hole; 40d. Exhaust opening; 40e. Exhaust vent. Detailed Implementation

[0051] To facilitate understanding of this application, a more detailed description is provided below with reference to the accompanying drawings and specific embodiments. It should be noted that when an element is described as "fixed to" another element, it can be directly on the other element, or one or more intermediate elements may exist between them. When an element is described as "connected" to another element, it can be directly connected to the other element, or one or more intermediate elements may exist between them. The terms "upper," "lower," "inner," "outer," "vertical," "horizontal," etc., used in this specification indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0052] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of the application. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0053] Furthermore, the technical features involved in the different embodiments of this application described below can be combined with each other as long as they do not conflict with each other.

[0054] Referring to Figure 1, this application provides a blade assembly 100, which includes blades 10 and a mounting shaft 20. The mounting shaft 20 is rotatably connected to an external device, such as a generator of a wind power generation device, and the blades 10 are connected to the mounting shaft 20. Wind acts on the blades 10 to convert the kinetic energy of the wind into the mechanical energy of the blade assembly 100, that is, the blade assembly 100 rotates relative to the external device.

[0055] Referring to Figure 1, the blade 10 has a first surface 10a and a second surface 10b arranged opposite each other along the circumference of the mounting shaft 20. The first surface 10a is recessed towards the second surface 10b, and a force-receiving groove 10c is formed on the first surface 10a. When wind impacts the wall of the force-receiving groove 10c, the wall of the force-receiving groove 10c bears the wind impact, causing the blade assembly 100 to rotate relative to the external equipment. On the one hand, the force-receiving groove 10c can increase the force-receiving area of ​​the wind; on the other hand, the force-receiving groove 10c can also capture the kinetic energy of the wind, improve the conversion rate of the wind's kinetic energy to mechanical energy, and further reduce the energy loss of the wind.

[0056] To facilitate the reader's understanding of the embodiments of this application, a theoretical analysis of the forces acting on the blade 10 provided in this embodiment is presented. The theoretical analysis employs the infinitesimal element analysis method. This method is a commonly used approach in analyzing and solving physical problems, and it represents a thought process that moves from the part to the whole. This method allows complex processes to be solved using familiar principles, simplifying the problem. When using the infinitesimal element method, the problem needs to be decomposed into multiple tiny "meta-processes," each following the same underlying principles. Thus, we only need to analyze these "meta-processes," and then apply necessary mathematical methods or physical concepts to them to solve the problem.

[0057] Please refer to Figure 2. In the stress analysis of the blade 10, the stressed blade 10 is divided into an infinite number of "meta-processes" along the circumference of the mounting axis 20. In a certain uniform wind field, the stress analysis is performed on a certain cross section of the blade 10 during the rotation process. The wind can be regarded as a uniform line load q acting on the actual stress curve S of the cross section of the blade 10.

[0058] To simplify the wind force experienced in this section, the actual force curve S is projected onto the direction perpendicular to the uniformly distributed line load q, and the length of the projected line segment is A, as shown in Figure 3.

[0059] The equivalent wind force F of a uniformly distributed line load q acting on the stress surface wind Let F0 be the wind force experienced at the cross section of blade 10. At this point, the equivalent net force F0 and the equivalent wind force F0 experienced by blade 10 within the cross section of blade 10 are... wind Equal, equivalent wind force F wind =qA, where q is the uniformly distributed line load on the blade within section 10, and A is the projection length A of the force curve S onto the direction perpendicular to the uniformly distributed line load q. Under the action of the uniformly distributed line load q, the equivalent wind force F wind The position is at the center of the entire force, that is, the lever arm L = 1 / 2A, as shown in Figure 4.

[0060] Please refer to Figures 5 and 6 for the equivalent wind force F. wind Equivalent substitution is performed to transform the planar force F wind Simplify the process by moving towards the center point O of the mounting shaft 20 (rotating shaft). Add a pair of elements at point O that are the same size as F. wind Equal but opposite balanced forces F1 and F2. It can be observed that F... wind F1 forms a couple, generating the first torque M. o (Principal moment), F2 is the force (principal vector) acting at point O. First torque M o A physical quantity used to represent the strength of the rotational effect produced by a couple, and it can change the angular momentum of an object. For the same object, the first torque M oThe larger the value, the easier it is to change the rotation state. This is because the equivalent resultant force F0 on the blade section 10 at this time is equal to the equivalent wind force F... wind If they are equal, then formula M o =F0×L=F wind ×L is used to calculate the magnitude of the first moment M0, where the equivalent resultant force F0 represents the force on the blade section 10, and the equivalent wind force F wind The force L represents the wind speed, and the lever arm L is the distance from point O to the equivalent wind force F. wind The vertical distance, the equivalent resultant force F0 and the equivalent wind force F wind When they are equal, the lever arm L is also the lever arm of the equivalent resultant force F0.

[0061] In practical applications, when blade 10 rotates, the torque M θ The force changes periodically with the rotation angle θ of blade 10. Please refer to Figure 7. When the rotation angle of blade 10 is θ, the actual force curve S is projected onto the direction perpendicular to the uniformly distributed line load q, and the length of the projected line segment is A1. At this time, the equivalent wind force F windθ =q×A1=q×A×cosθ=cosθF wind According to the formula, after rotating by an angle θ, the equivalent wind force F windθ Transform into cosθF wind , of which F wind This represents the equivalent wind force experienced by blade 10 when the rotation angle θ is 0 degrees. Please refer to Figure 8 for the equivalent wind force F after the rotation angle θ. windθ An angle is formed between the lever arm L and the torque M. Analysis shows that the magnitude of this angle is the aforementioned rotation angle θ. Therefore, when calculating the torque M... θ It is necessary to convert the equivalent wind force F windθ Projecting onto the direction perpendicular to the lever arm, we obtain the equivalent resultant force F0 = cosθF. windθ =cos 2 θF wind .

[0062] Then the torque M θ =F0×L=cos 2 θF wind ×L=cos 2 θM o Where L is the lever arm of the equivalent resultant force, and the first torque M o Let F be the torque when the rotation angle θ is 0 degrees. wind The equivalent wind force experienced by blade 10 when the rotation angle θ is 0 degrees is F. wind The plane perpendicular to the groove opening of the force groove 10c of the blade 10.

[0063] Additionally, referring to Figure 1, a drain hole 10f is provided at the bottom of the force-receiving groove 10c. The drain hole 10f is located close to the mounting shaft 20 and is used to allow air to discharge after impacting the force-receiving groove 10c, so that the position of the equivalent resultant force F0 is away from the mounting shaft 20. That is, when the air impacts the force-receiving groove 10c, part of it impacts the wall of the force-receiving groove 10c, and the other part is discharged from the drain hole 10f. Since the drain hole 10f is located close to the mounting shaft 20, the position of the equivalent resultant force F0 on the blade 10 is away from the mounting shaft 20, that is, the lever arm L of the equivalent resultant force F0 on the blade 10 is lengthened. Due to the torque M θ =F0×L, then the torque M on blade 10 θ Larger.

[0064] Specifically, please refer to Figures 9 and 10. In Figure 9, when the blade 10 is not equipped with the exhaust hole 10f, although the force-bearing area of ​​the blade 10 is large, a large amount of wind will escape from above, and the equivalent wind force F wind The lever arm length is L', that is, the lever arm length of the equivalent resultant force F0 is L'. In contrast, in the embodiment of this application, due to the setting of the exhaust hole 10f in Figure 10, the equivalent wind force F wind The position of the blade 10 is far from the mounting shaft 20, meaning the equivalent resultant force F0 on the blade 10 is far from the mounting shaft 20. Therefore, the lever arm length L of the equivalent resultant force F0 is greater than L'. Thus, the torque M on the blade 10 provided in this embodiment of the application... θ Larger.

[0065] Furthermore, the power provided by the blade 10 satisfies: P = M θ ×w=F0×L×w=cos 2 θF wind ×L×w; where w is the angular velocity of the blade 10. Since power P is the torque M... θ The product of the angular velocity w and the torque M experienced by the blade 10 provided in this embodiment, assuming the angular velocity w is equal, is... θ If the blade is increased, the power P provided by the blade 10 will be improved.

[0066] Please refer to Figure 11. Figure 11 shows the power curve of the blade assembly 100, with the horizontal axis representing the rotational speed of the blade 10. The test condition is a wind speed of 6 m / s. Specifically, P1 is the power curve of the blade 10 with the exhaust hole 10f provided in this embodiment (the blade assembly 100 does not include the mounting bracket 40); P2 is the power curve of the blade 10 with the exhaust hole 10f provided in this embodiment, and the blade assembly 100 includes the mounting bracket 40, which has an exhaust hole 40c, with the cross-sectional area of ​​the exhaust hole 40c gradually increasing in the direction away from the inlet 40b; P3 is the power curve of the blade 10 without the exhaust hole 10f provided (the blade assembly 100 does not include the mounting bracket 40); and P4 is the power curve of the blade 10 without the exhaust hole 10f provided in this embodiment, and the blade assembly 100 includes the mounting bracket 40, which does not have an exhaust hole 40c. By comparing P1 and P3, the power of the blade assembly 100 is significantly increased by setting the drain hole 10f in the blade 10.

[0067] In some embodiments, the number of blades 10 is multiple, and the multiple blades 10 are distributed circumferentially along the mounting shaft 20. Due to the arrangement of multiple blades 10, the torque M provided by the multiple blades 10 is... θ The power P provided by multiple blades 10 can be stacked, thereby increasing the overall power provided by the blade assembly 100.

[0068] Referring to Figure 1, the cross-sectional area of ​​the force-receiving groove 10c gradually decreases from its opening to its bottom, thus giving it excellent wind-catching and wind-catching capabilities. One specific implementation involves the force-receiving groove 10c having a first guide surface 10d and a second guide surface 10e positioned opposite each other at its bottom along the radial direction of the mounting shaft 20. Both guide surfaces 10d and 10e are inclined towards the center of the force-receiving groove 10c and are used to guide airflow.

[0069] In some embodiments, the first guide surface 10d is arc-shaped, and the second guide surface 10e is arc-shaped.

[0070] Specifically, the drain hole 10f is set on the first guide surface 10d. Since the drain hole 10f is set close to the mounting shaft 20, the first guide surface 10d is set closer to the mounting shaft 20 than the second guide surface 10e.

[0071] In some embodiments, the number of drainage holes 10f is multiple, and the multiple drainage holes 10f are distributed on the first guide surface 10d to form multiple force-bearing areas 10d1 on the first guide surface 10d. By setting the drainage holes 10f and the force-bearing areas 10d1, on the one hand, the force arm L of the equivalent resultant force F0 on the blade 10 can be lengthened due to the setting of the drainage holes 10f, and the torque M on the blade 10 can be increased.θ It is larger, and on the other hand, although it is equipped with an exhaust hole 10f, it can also withstand the impact of wind in the stress zone 10d1, thereby providing a portion of the torque M. θ Furthermore, when the wind escapes through the exhaust hole 10f, the forces on the blade 10 are more balanced, meaning that the rotational stability of the blade 10 is good.

[0072] In some embodiments, the drain hole 10f is an oblong hole, and the length direction of the drain hole 10f extends from the mounting shaft 20 toward the blade 10. That is, multiple drain holes 10f are arranged side by side on the first guide surface 10d.

[0073] In some embodiments, the distance between the bottom of the force-receiving groove 10c extending along the first guide surface 10d to the opening of the force-receiving groove 10c is less than the distance between the bottom of the force-receiving groove 10c extending along the second guide surface 10e to the opening of the force-receiving groove 10c. A drain hole 10f is disposed on the first guide surface 10d. This arrangement lengthens the lever arm L of the equivalent resultant force F0 experienced by the blade 10, thereby increasing the torque M experienced by the blade 10. θ It is larger, and also takes into account the impact of wind on the force-bearing groove 10c.

[0074] In some embodiments, referring to FIG12, the second guide surface 10e is recessed toward the second surface 10b to form a flow-gathering region 10e1, and the first guide surface 10d protrudes away from the second surface 10b to form a flow-draining region 10d2. The formation of the flow-gathering region 10e1 increases the wind-capturing capability of the force-receiving groove 10c. The formation of the flow-draining region 10d2 facilitates faster wind discharge from the drain hole 10f when wind impacts the force-receiving groove 10c.

[0075] Regarding the aforementioned mounting shaft 20, please refer to Figures 13 and 14. The mounting shaft 20 includes a mounting portion 201 and a connecting portion 202. The blade 10 is connected to the mounting portion 201, one end of the connecting portion 202 is connected to the mounting portion 201, and the other end of the connecting portion 202 is connected to an external device. Along the mounting portion 201 toward the connecting portion 202, the cross-section of the mounting portion 201 is larger than that of the connecting portion 202, so that a step 20a is formed between the mounting portion 201 and the connecting portion 202. The sidewall of the force-bearing groove 10c abuts against the step 20a. The step 20a has a limiting effect on the blade 10, reducing the offset of the blade 10 relative to the mounting shaft 20.

[0076] In some embodiments, there are two connecting portions 202, which are disposed opposite to each other on the mounting portion 201. The mounting portion 201 and the two connecting portions 202 form two steps 20a. A third guide surface abuts against one step 20a and a fourth guide surface abuts against the other step 20a.

[0077] In some embodiments, the mounting portion 201 is square in shape along the direction from the mounting portion 201 toward the connecting portion 202, and the number of blades 10 corresponds to the number of sides of the square, that is, one blade 10 is connected to the surface formed by any two adjacent sides of the square. For example, the number of blades 10 is four, the number of sides of the square is four, and the surface formed by any two adjacent sides of the square of one blade 10 is connected.

[0078] Regarding the connection between the blade 10 and the mounting shaft 20, the mounting part 201 is provided with a screw hole 201a, the blade 10 is provided with a through hole 10g, and the blade assembly 100 also includes a bolt. The bolt passes through the through hole 10g and is screwed into the screw hole 201a, thereby achieving a detachable connection between the blade 10 and the mounting shaft 20, facilitating transportation and maintenance. Optionally, the connection method between the blade 10 and the mounting shaft 20 can be riveting or welding, as long as it can fix the blade 10 to the mounting shaft 20.

[0079] In some embodiments, referring to FIG15, the blade assembly 100 further includes a limiting member 30, which is connected to the mounting shaft 20. The mounting shaft 20 and the limiting member 30 together form a limiting groove 30a. The blade 10 is inserted into the limiting groove 30a and is adapted to the limiting groove 30a. The limiting groove 30a is used to limit the blade 10. Specifically, the limiting member 30 includes a straight portion 301 and a bent portion 302. One end of the straight portion 301 is connected to the mounting shaft 20, and the other end of the straight portion 301 is connected to the bent portion 302. The bent portion 302 is disposed opposite to the mounting shaft 20. The straight portion 301, the bent portion 302, and the mounting shaft 20 together form the limiting groove 30a.

[0080] In some embodiments, referring to FIG16, the blade assembly 100 further includes a mounting bracket 40, which is connected to an external device, such as a generator of a wind power generation device. The mounting bracket 40 is provided with a trough 40a and an inlet 40b communicating with the trough 40a. The blade 10 is disposed in the trough 40a. The inlet 40b is used to supply air to enter the trough 40a and impact the stress groove 10c. The mounting bracket 40 is provided with a plurality of exhaust holes 40c communicating with the trough 40a. The plurality of exhaust holes 40c are disposed near the inlet 40b and are used for air discharge.

[0081] Please refer to Figure 17. Figure 17 is a schematic diagram of the mounting bracket 40 without the exhaust port 40c. When the blade 10 rotates, the wind in the groove 40a creates resistance to the blade 10, affecting its rotation. Specifically, because the blade 10 is resisted by the wind in the groove 40a, the force of the wind entering from the inlet 40b impacting the force groove 10c is canceled out. Therefore, the equivalent net force F0 on the blade 10 decreases, and the torque M on the blade 10 decreases. θ The power P of the blade assembly 100 decreases, affecting the efficiency of wind power conversion.

[0082] Please refer to Figure 18, which is a schematic diagram of the mounting bracket 40 with an exhaust opening 40d. That is, the area of ​​the mounting bracket 40 near the inlet 40b is open. Therefore, although the resistance of the blades 10 to the wind within the groove 40a will be reduced, the wind entering from the inlet 40b will also escape significantly from the exhaust opening 40d. Thus, the equivalent wind force F provided by the wind... wind The force decreases because the equivalent net force on blade 10 is F0 = cosθF. windθ =cos 2 θF wind Then the equivalent net force F0 on blade 10 will also decrease, and the torque M on blade 10 will also decrease. θ The power P of the blade assembly 100 decreases, affecting the efficiency of wind power conversion.

[0083] Please refer to Figure 19. Figure 19 is a schematic diagram of the mounting bracket 40 with an exhaust port 40c. This reduces the resistance of the blade 10 to the wind in the groove 40a, while also taking into account the impact of the wind entering from the inlet 40b on the blade 10. This ensures that the blade 10 receives the optimal equivalent resultant force F0, and guarantees that the torque M on the blade 10 is within the optimal range. θ To ensure optimal power P of the blade assembly 100, the best wind power conversion efficiency is achieved.

[0084] In some embodiments, referring to Figure 19, the cross-sectional area of ​​the exhaust port 40c gradually increases in the direction away from the inlet 40b, thereby increasing the optimal torque M experienced by the blade 10. θ The duration of the wind power conversion is increased to improve the efficiency of wind power conversion.

[0085] Specifically, since the equivalent resultant force F0 = cosθF windθ =cos 2 θF wind Then the torque M can be obtained. θ =F0×L=cos 2 θF wind ×L=cos 2 θM o Where L is the lever arm of the equivalent resultant force, and the first torque M o Let F be the torque when the rotation angle θ is 0 degrees. wind The equivalent wind force experienced by blade 10 when the rotation angle θ is 0 degrees is F. wind The plane perpendicular to the groove opening of the force-bearing groove 10c of the blade 10. Therefore, it can be seen that when the rotation angle θ is 0 degrees, it can provide the maximum torque M. θ That is, the first torque M o Once the rotation angle increases, the torque M will increase. θThe attenuation. When the rotation angle θ is small, cos... 2 θ approaches 1, at which point formula M θ =F0×L=cos 2 θF wind ×L, then the equivalent wind force F wind With respect to torque M θ The impact is significant. A smaller exhaust vent 40c is opened here to provide wind compensation and prolong the duration of the optimal torque, i.e., the first torque M. o Or close to the first torque M o The duration of the rotation increases, improving the efficiency of wind power conversion. As the rotation angle θ increases, cos... 2 The value of θ affects the torque M θ The impact is gradually increasing, and the equivalent wind force F wind With respect to torque M θ As the influence gradually weakens, opening a larger exhaust hole 40c at this time can ensure the balance of the rotation of the blade 10 and improve the operational stability of the blade assembly 100.

[0086] Please refer to Figure 20. M1 is a torque curve showing that the blade 10 of this application is provided with an exhaust hole 10f, and the blade assembly 100 includes a mounting frame 40 with an exhaust hole 40c. Along the direction away from the inlet 40b, the cross-sectional area of ​​the exhaust hole 40c gradually increases. M2 is a torque curve showing that the blade 10 is provided with an exhaust hole 10f, and the blade assembly 100 includes a mounting frame 40, but the mounting frame 40 is not provided with an exhaust hole 40c. Comparing M1 and M2, by providing an exhaust hole 10f on the blade 10 and an exhaust hole 40c on the mounting frame 40, the torque M can be extended. θ When the wind is at a high level, the efficiency of wind power conversion is improved.

[0087] Please refer to Figure 21. M01 is the torque curve of a blade 10 with an exhaust port 10f, and the blade assembly 100 includes a mounting bracket 40, but the mounting bracket 40 does not have an exhaust port 40c. M02 is the torque curve of another blade 10 with an exhaust port 10f, and the blade assembly 100 includes a mounting bracket 40, but the mounting bracket 40 does not have an exhaust port 40c. M00 is the curve resulting from the combination of M01 and M02.

[0088] Please refer to Figure 22. M11 is a moment curve showing a blade 10 with an exhaust hole 10f, and the blade assembly 100 includes a mounting bracket 40 with an exhaust hole 40c. The cross-sectional area of ​​the exhaust hole 40c gradually increases in the direction away from the inlet 40b. M12 is another moment curve showing a blade 10 with an exhaust hole 10f, and the mounting bracket 40 with an exhaust hole 40c. The cross-sectional area of ​​the exhaust hole 40c gradually increases in the direction away from the inlet 40b. M10 is a curve combining M11 and M12.

[0089] Please refer to Figure 23 and compare the torque curves M00 and M10. M00 is at a high level for approximately 1 / 3 of the cycle, while M10 is at a high level for approximately 2 / 3 of the cycle. This indicates that by providing an exhaust hole 10f on the blade 10 and an exhaust hole 40c on the mounting bracket 40, the cross-section of the exhaust hole 40c gradually increases along the direction away from the inlet 40b, which can increase the torque M experienced by the blade 10. θ The longer the wind power is maintained at a high level, the higher the efficiency of wind power conversion. In addition, the fluctuation of curve M10 is significantly smaller than that of curve M00, indicating that the blade assembly 100 provided in this application embodiment has good operational stability.

[0090] Please refer to Figure 24, which shows the torque standard deviation of blade assembly 100. Torque standard deviation is a statistical parameter that measures the degree of fluctuation in torque measurement or torque output. In engineering and physics, torque stability is crucial for ensuring the performance and reliability of mechanical systems. In short, the smaller the torque standard deviation, the more stable the system operation. In Figure 24, δ1 is the standard deviation of the torque of the blade 10 with the exhaust hole 10f provided in the embodiment of this application (the blade assembly 100 does not include the mounting bracket 40); δ2 is the standard deviation of the torque of the blade 10 with the exhaust hole 10f provided in the embodiment of this application, and the blade assembly 100 includes the mounting bracket 40, the mounting bracket 40 is provided with the exhaust hole 40c, and the cross-section of the exhaust hole 40c gradually increases in the direction away from the inlet 40b; δ3 is the standard deviation of the torque of the blade 10 without the exhaust hole 10f provided (the blade assembly 100 does not include the mounting bracket 40); δ4 is the standard deviation of the torque of the blade 10 without the exhaust hole 10f provided in the embodiment of this application, and the blade assembly 100 includes the mounting bracket 40, the mounting bracket 40 is not provided with the exhaust hole 40c.

[0091] Please refer to Figures 11 and 24 together and compare the power curves P1 and P3. By setting the exhaust hole 10f on the blade 10, the power of the blade assembly 100 is significantly improved. By comprehensively comparing the power curves P1, P2, and P3, as well as the torque standard deviations δ1, δ2, and δ3, the optimal combination of power curve P2 and torque standard deviation δ2 is obtained. That is, the technical solution provided in this application embodiment, which sets the exhaust hole 10f on the blade 10 and the blade assembly 100 includes a mounting frame 40, which is provided with an exhaust hole 40c. The cross-sectional area of ​​the exhaust hole 40c gradually increases in the direction away from the inlet 40b. This solution can simultaneously take into account the power of the blade assembly 100 and the operational stability of the blade assembly 100.

[0092] In some embodiments, referring to Figure 25, viewed along the direction of the mounting axis 20, the mounting bracket 40 is a circle with a notch, the notch corresponding to the inlet 40b; viewed along the direction of the mounting axis 20, multiple exhaust holes 40c are arranged from the inlet 40b along the circumference of the circle to form a first arc (not shown), the first arc having a first preset arc angle α1, which is less than 45 degrees. This limits the position of the exhaust holes 40c on the mounting bracket 40, ensuring the torque M experienced by the blade 10. θ Optimal, and to ensure that the blade 10 experiences the optimal torque M. θ Duration.

[0093] In some embodiments, the notch is fan-shaped, and the included angle of the fan-shaped notch is 90 degrees.

[0094] In some embodiments, the mounting bracket 40 is provided with an exhaust port 40e communicating with the roller groove 40a; viewed along the direction of the mounting shaft 20, a second arc (not shown) is formed along the circumference of the circle from the inlet 40b to the exhaust port 40e, the second arc having a second preset arc angle a2, the second preset arc angle a2 being greater than the first preset arc angle a1 and less than 90 degrees. Because the blade 10 experiences a torque M when rotating. θ There is attenuation. By setting the exhaust port 40e, the resistance on the blade 10 is greatly reduced, preventing the blade 10 from stopping due to resistance, and improving the stability of the blade 10 rotation.

[0095] In this embodiment, the blade assembly 100 includes a mounting shaft 20 and blades 10. The mounting shaft 20 is rotatably connected to an external device, and the blades 10 are connected to the mounting shaft 20. The blades 10 have a first surface 10a and a second surface 10b disposed opposite each other along the circumference of the mounting shaft 20. The first surface 10a is recessed towards the second surface 10b, and a force-bearing groove 10c is formed on the first surface 10a. The force-bearing groove 10c is used to withstand wind impact, causing the blade assembly 100 to rotate relative to the external device. The torque M provided by the blades 10... θ Satisfy: M θ =F0×L=cos 2 θF wind ×L; where M θ Let F0 be the torque acting on the blade, F0 be the equivalent resultant force acting on the blade, L be the lever arm of the equivalent resultant force, and θ be the rotation angle of the blade. wind When θ is 0 degrees, the equivalent wind force experienced by the blade is F. wind The plane perpendicular to the opening of the force-receiving groove 10c of the blade 10; the power provided by the blade 10 satisfies: P = M θ ×w=F0×L×w=cos 2 θF wind×L×w; where w is the angular velocity of the blade rotation; the bottom of the force groove 10c is provided with a drain hole 10f, which is located close to the mounting shaft 20. The drain hole 10f is used to allow wind to impact the force groove 10c and then discharge, so that the position of the equivalent resultant force F0 is far away from the mounting shaft 20. That is, when the wind impacts the force groove 10c, part of it impacts the wall of the force groove 10c, and the other part is discharged from the drain hole 10f. Since the drain hole 10f is located close to the mounting shaft 20, the position of the equivalent resultant force F0 provided by the blade 10 is far away from the mounting shaft 20, that is, the lever arm L of the equivalent resultant force F0 provided by the blade 10 is lengthened. Since the torque M θ If the equivalent resultant force F0 is the product of the lever arm L, then the torque M acting on blade 10 is... θ Larger. Because power P is torque M θ The power P of the blade assembly 100 provided in this application embodiment is increased by multiplying the angular velocity w by the angular velocity w, provided that the angular velocity w is equal.

[0096] This application also provides an embodiment of a wind power generation device, which includes a generator and the blade assembly 100 described above. The blade assembly 100 is connected to the generator. For the specific structure and function of the blade assembly 100, please refer to the above embodiments, which will not be repeated here.

[0097] The above description is merely an embodiment of this application and does not limit the patent scope of this application. Any equivalent structural or procedural transformations made using the content of this application's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this application.

Claims

1. A blade assembly, characterized in that, include: Mounting shaft, rotatably connected to external equipment; The blade is connected to the mounting shaft. The blade has a first surface and a second surface that are disposed opposite to each other along the circumference of the mounting shaft. The first surface is recessed toward the second surface. A force-bearing groove is formed on the first surface. The force-bearing groove is used to withstand wind impact, so that the blade assembly rotates relative to the external equipment. The torque provided by the blade satisfies: M θ =F0×L=cos 2 θF wind ×L Among them, M θ Let F0 be the torque acting on the blade, F0 be the equivalent resultant force acting on the blade, L be the lever arm of the equivalent resultant force, and θ be the rotation angle of the blade. wind When θ is 0 degrees, the equivalent wind force experienced by the blade is F. wind The plane perpendicular to the opening of the force-receiving groove of the blade; The power provided by the blades satisfies: P=M θ ×w=F0×L×w=cos 2 θF wind ×L×w Where w is the angular velocity of the blade rotation; The bottom of the force-bearing groove is provided with a drain hole, which is located close to the mounting shaft. The drain hole is used to allow air to impact the force-bearing groove and then discharge, so that the position of the equivalent resultant force is far away from the mounting shaft. Along the direction from the opening of the stress groove to the bottom of the groove, the cross-sectional area of ​​the stress groove gradually decreases; Along the radial direction of the mounting shaft, the bottom of the force-receiving groove has a first guide surface and a second guide surface that are arranged opposite to each other. The drain hole is disposed on the first guide surface. The first guide surface and the second guide surface are respectively inclined toward the center of the force-receiving groove. Both the first guide surface and the second guide surface are used to guide the airflow. The number of drainage holes is multiple, and the multiple drainage holes are distributed on the first guide surface to form multiple force-bearing zones on the first guide surface; The distance between the bottom of the stress groove and the opening of the stress groove along the first guide surface is less than the distance between the bottom of the stress groove and the opening of the stress groove along the second guide surface.

2. The blade assembly according to claim 1, characterized in that, The second guide surface is recessed toward the second surface to form a flow-gathering area, and the first guide surface protrudes toward the direction away from the second surface to form a flow-draining area.

3. The blade assembly according to claim 1, characterized in that, The number of blades is multiple, and the multiple blades are distributed circumferentially along the mounting axis.

4. The blade assembly according to claim 1, characterized in that, The drain hole is a waist-shaped hole, and the length of the drain hole extends from the mounting shaft toward the blade.

5. The blade assembly according to any one of claims 1-4, characterized in that, The blade assembly also includes a mounting bracket, which is connected to an external device; The mounting frame is provided with a groove and an inlet that connects to the groove. The blades are disposed in the groove, and the inlet is used to supply air to enter the groove and impact the force groove. The mounting bracket is provided with multiple exhaust holes that communicate with the roller groove. The multiple exhaust holes are located near the inlet and are used for air discharge.

6. The blade assembly according to claim 5, characterized in that, Along the direction away from the air inlet, the cross-section of the exhaust hole gradually increases.

7. The blade assembly according to claim 6, characterized in that, Viewed along the direction of the mounting axis, the mounting bracket is a circle with a notch, and the notch corresponds to the inlet. Viewed along the direction of the mounting axis, the plurality of exhaust holes are arranged from the inlet along the circumference of the circle to form a first arc, the first arc having a first preset arc angle, which is less than 45 degrees.

8. The blade assembly according to claim 7, characterized in that, The mounting bracket is provided with an exhaust port that connects to the roller groove; viewed along the direction of the mounting axis, a second arc is formed along the circumference of the circle from the inlet to the exhaust port, the second arc having a second preset arc angle, the second preset arc angle being greater than the first preset arc angle and less than 90 degrees.

9. The blade assembly according to claim 7, characterized in that, The notch is fan-shaped, and the included angle of the fan-shaped notch is 90 degrees.

10. A wind power generation device, characterized in that, It includes a generator and a blade assembly as described in any one of claims 1-9, the blade assembly being connected to the generator.

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