Vibration power generation device reversely utilizing buffeting suppression technology

Abstract

The invention relates to the field of power generation devices, in particular to a vibration power generation device reversely utilizing a buffeting suppression technology, which comprises a sleeve device and a plurality of improved blades, a plurality of improved blades are evenly distributed on the outer wall of the sleeve device, one end of each improved blade is connected with the outer wall of the sleeve device through an elastic base plate, piezoelectric ceramics are laid on the elastic base plate, and the improved blade is characterized in that the middle of each improved blade is bent, so that the section of each improved blade is in an arc shape. According to the device, the sections of the improved blades are arranged to be arc-shaped, and the arc-shaped openings are arranged outwards, so that more wind energy can be collected and utilized. Parameters such as wing chord length, thickness, maximum camber, camber position and the like of the improved blade are improved, and a buffeting suppression technology is reversely utilized, so that the blade can still generate more wind-induced mechanical energy under the blowing of small wind power and further convert the wind-induced mechanical energy into electric energy, and the collection efficiency and the utilization rate of wind energy are improved.

Description

Technical Field

[0001] The present invention relates to the field of power generation devices, and more specifically, to a vibration power generation device utilizing a reverse vibration suppression technology. Background Art

[0002] In the existing traditional vibration power generation field, the commonly used vibration power generation device mainly uses metal materials as a fixed elastic substrate, and multiple piezoelectric elements fixed on its elastic substrate, and a single-mass counterweight is configured at the end of the elastic substrate. Each piezoelectric element consists of a piezoelectric ceramic and two electrodes. When the device vibrates, the counterweight shakes and causes the elastic substrate to deform, which in turn causes the piezoelectric ceramic to generate voltage under pressure, thereby realizing electrical energy collection. This method of applying the piezoelectric effect has been widely accepted for its advantages such as simple structure and clear function. At present, this type of power generation equipment is usually deployed in mechanical equipment and transportation systems.

[0003] However, there are many sources of vibration in the environment. Among them, wind energy, as a common clean energy, produces almost no pollution during the power generation process, which can significantly reduce the negative impact on the environment and help improve the quality of the ecological environment. Compared with fossil fuels, wind energy does not produce greenhouse gases and pollutants such as carbon dioxide, and plays an important role in mitigating climate change and improving air quality. Wind energy is also a renewable energy source. It is formed by airflow caused by uneven heating of the earth's surface. It is an inexhaustible and inexhaustible energy source that will not be exhausted and will not cause resource depletion. In addition, wind energy resources are widely distributed around the world, especially in coastal areas, grasslands, deserts and other areas, which allows wind power generation to be implemented under different geographical conditions. The development of wind energy can reduce dependence on non-renewable energy, improve the diversity and stability of energy supply, and ensure national energy security. For remote areas with water shortage, fuel shortage and inconvenient transportation, wind power generation provides a stable and reliable power supply, which helps local economic development.

[0004] Although wind power generation has the above advantages, there are also some challenges. For example, the size, frequency and direction of wind will change over time. Therefore, the existing counterweight blocks that use wind energy for vibration power generation cannot adapt to the changes in wind energy in the environment and can only absorb a small part of the wind energy for vibration power generation, resulting in low power generation efficiency and low energy utilization efficiency. Summary of the invention

[0005] The present invention aims to overcome at least one defect of the above-mentioned prior art and provide a vibration power generation device that reversely utilizes the jitter suppression technology to solve the problem that the existing counterweight block that utilizes wind energy for vibration power generation cannot adapt to the changes in wind energy in the environment and can only absorb a small part of the wind energy for vibration power generation, resulting in low power generation efficiency and low energy utilization efficiency.

[0006] The technical solution adopted by the present invention is a vibration power generation device that reversely utilizes the jitter suppression technology, including a sleeve device and a plurality of improved blades, wherein the sleeve device is roughly cylindrical; the plurality of improved blades are evenly distributed on the outer wall of the sleeve device, one end of the improved blade is connected to the outer wall of the sleeve device through an elastic substrate, piezoelectric ceramics are laid on the elastic substrate, and the middle part of the improved blade is bent, so that the cross-section of the improved blade is arc-shaped.

[0007] The counterweight of the device is a blade with an improved structure. One end of the improved blade is connected to the sleeve device through an elastic substrate, and the other end is suspended in the air, so that it can vibrate under the action of wind, thereby driving the elastic substrate to vibrate. Piezoelectric ceramics are laid on the elastic substrate, and the vibration of the elastic substrate squeezes the piezoelectric ceramics to deform, thereby generating electrical energy. Multiple improved blades are evenly distributed on the outer wall of the sleeve device so that they can collect wind energy from multiple directions. Compared with straight blades, the improved blades with a curved middle part and an arc-shaped cross-section are more affected by wind force and collect more wind energy, thereby generating more wind-induced mechanical energy, which is converted into electrical energy and improves the utilization rate of wind energy.

[0008] Furthermore, the improved blade has an inner surface and an outer surface, the curvature of the inner surface is greater than the curvature of the outer surface, the outer surface of the improved blade faces the sleeve device, and the inner surface of the improved blade is away from the sleeve device.

[0009] The opening of the arc-shaped improved blade faces the inner surface. Setting the inner surface outward can collect more wind energy and receive greater wind force, thereby generating a larger amplitude. If the outer surface faces outward, the wind will blow to both sides along the curvature of the outer surface after acting on the outer surface. The improved blade is less affected by the wind force, and the vibration it generates is also small, so the utilization rate of wind energy is not high.

[0010] Furthermore, the cross-section of the improved blade is thicker in the middle and thinner at both ends, and the improved blade has a front end and a rear end, and the thickness of the front end of the improved blade is greater than the thickness of the rear end of the improved blade.

[0011] The thickness of the blade affects its stiffness and mass distribution. The profile of the improved blade is set to be thicker in the middle and thinner at both ends in order to reduce the mass of the blade, making it easier to vibrate, while ensuring that the improved blade has sufficient structural strength. The thickness of the front end of the improved blade is designed to be greater than the thickness of the rear end because the leading edge of the improved blade bears a larger aerodynamic load, so it is designed to be thicker to provide sufficient structural strength. The load on the trailing edge is relatively small, so it can be designed to be thinner.

[0012] Furthermore, the distance between the front end of the improved blade and the point where the curvature is the largest is greater than the distance between the rear end of the improved blade and the point where the curvature is the largest.

[0013] The position of the maximum curvature determines the airflow separation point of the blade. The improved blade is set so that the distance between the front end and the curvature position is greater than the distance between the rear end and the curvature position to ensure that the airflow separates in the rear half of the blade, thereby generating flutter.

[0014] Furthermore, the camber position p of the improved blade is 0.55 to 0.7 times the chord length.

[0015] The chord length refers to the straight-line distance from the leading edge to the trailing edge of the blade, and is the reference length of the blade section. The camber position p refers to the proportion of the chord length where the maximum camber is located, and is usually expressed as the percentage of the distance between the location of the maximum camber and the front end of the modified blade to the chord length. The camber position p of the improved blade is 0.55 to 0.7 times the chord length, that is, the distance between the maximum camber of the improved blade and the front end of the improved blade accounts for 55% to 70% of the chord length. Setting the camber position to 0.55 to 0.7 can optimize the position of airflow separation, making vortex shedding more likely to occur, thereby increasing the vibration amplitude of the blade.

[0016] Furthermore, the maximum curvature m of the improved blade is 0.05 to 0.15 times the chord length.

[0017] The maximum camber refers to the maximum bulge of the blade section in the direction perpendicular to the chord, usually expressed as a percentage of the chord length. The camber affects the aerodynamic characteristics of the blade. A larger camber can increase the lift of the blade, but it will also increase the drag. In a wind energy collector, appropriate camber can promote airflow separation and vortex shedding, thereby increasing the vibration amplitude. The smaller maximum camber value, i.e. 0.05 to 0.15, is selected to increase the flexibility of the blade without increasing too much structural complexity, making it easier to respond to wind vibrations.

[0018] Furthermore, the thickness t of the improved blade is 0.15 to 0.3 times the chord length.

[0019] Thickness refers to the maximum thickness of the modified blade section in the direction perpendicular to the chord, usually expressed as a percentage of the chord length. Thickness affects the stiffness and mass distribution of the blade. Appropriate thickness can ensure that the blade can produce sufficient vibration under the action of wind while ensuring the structural strength of the improved blade. The relatively thin thickness of 0.15 to 0.3 is selected to reduce the mass of the blade, making it easier to vibrate, while ensuring that the improved blade has sufficient structural strength. Thinner blades are more likely to bend and vibrate under the action of wind, which helps to increase the contact area with the wind and the energy conversion efficiency.

[0020] Furthermore, the number of the improved leaves is 6 to 10.

[0021] More improved blades can collect more wind energy. The improved blades are evenly distributed on the outer wall of the sleeve device, so that different improved blades face different directions, thereby collecting wind from different directions. However, too many improved blades will make the distance between the blades too small, so that they appear dense and affect the vibration of the improved blades. Therefore, the number of improved blades is set to 6 to 10, so that it can collect wind from different directions without affecting its vibration due to too many improved blades.

[0022] Furthermore, the elastic substrate is connected to the outer wall of the sleeve device through a ball joint device, the ball joint device is fixed on the outer wall of the sleeve device, the ball joint device has a rotating shaft, the rotating shaft is rotatable, and the elastic substrate is connected to the rotating shaft of the ball joint device.

[0023] The improved blade is connected to the sleeve device through a rotatable ball joint device. When the improved blade is acted upon by wind, it can rotate through the ball joint device to adjust its windward angle so that it can collect more wind energy and improve the utilization rate of wind energy.

[0024] Furthermore, the net distance between two adjacent improved blades is 0.6-1.2 m.

[0025] The smaller the net distance between two adjacent improved blades, the more wind energy can be collected. However, too small a net distance will affect the vibration of the improved blades and the adjustment of their windward angles. Therefore, the net distance between two adjacent improved blades is set to 0.6 to 1.2 m.

[0026] Compared with the prior art, the beneficial effects of the present invention are as follows: by combining the improved blade with the piezoelectric ceramic, the improved blade vibrates under the action of wind, thereby driving the piezoelectric ceramic to deform and generate electric energy for power generation, replacing the vibration of traditional mechanical equipment as a vibration source for power generation, realizing the utilization of clean energy, reducing the cost of power generation, and improving economic benefits. The improved blade is set in an arc shape, and its opening is set outward, so that it can collect more wind energy for utilization. By setting the thickness of the improved blade, it can generate sufficient vibration under the action of wind while ensuring the structural strength. By setting the curvature position of the improved blade, the position of airflow separation is optimized, making it easier for vortex shedding to occur, thereby increasing the vibration amplitude of the blade. By setting the maximum curvature of the improved blade, the flexibility of the blade is increased without increasing too much structural complexity, making it easier to respond to wind vibration. The vibrating piezoelectric device reversely utilizes the flutter suppression technology, so that the improved blade can still generate more wind-induced mechanical energy under the blowing of a small wind force, and then convert it into electric energy, thereby improving the collection efficiency and utilization rate of wind energy. The device is also equipped with a rotatable ball joint device, so that the improved blades can adjust the windward angle, realize 360° wind energy collection without dead angles, and improve vibration mechanical energy. The device has 6 to 10 improved blades, which are evenly arranged on the outer wall of the sleeve device to ensure that there is a certain distance between two adjacent improved blades, so that it can collect wind energy in any direction without affecting the vibration and angle adjustment between each other. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 It is a structural diagram of the present invention.

[0028] Figure 2 It is an enlarged view of the connection between the elastic base and the ball joint of the present invention.

[0029] Figure 3 This is an enlarged view of the lower end of the improved blade of the present invention.

[0030] Figure 4 This is a cross-sectional view of the improved blade of the present invention. DETAILED DESCRIPTION

[0031] The drawings of the present invention are only for illustrative purposes and should not be construed as limiting the present invention. In order to better illustrate the following embodiments, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of the actual product; it is understandable to those skilled in the art that some well-known structures and their descriptions in the drawings may be omitted.

[0032] In the description of the present invention, it should be understood that the terms "upper", "lower", "middle", "inside", "outside" and the like indicating directions or positional relationships are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the components or elements referred to must have a specific direction, be constructed and operated in a specific direction, and therefore should not be understood as limiting the present invention.

[0033] like Figures 1 to 3 As shown, a vibration power generation device using the vibration suppression technology in reverse comprises a sleeve device 1, an elastic substrate 2 and an improved blade 3. The overall appearance of the sleeve device 1 is roughly cylindrical, and a plurality of ball joint devices 4 are evenly distributed on its outer wall, and the ball joint device 4 is fixedly connected to the sleeve device 1. The ball joint device 4 has a rotating shaft 41, and a fixing block 42 is arranged on the rotating shaft 41. The number of the improved blades 3 and the elastic substrate 2 is the same as the number of the ball joint devices 4. Preferably, the number of the improved blades 3 is 6 to 10. As the most preferred, the number of the improved blades 3 is 8, and the angle between two adjacent improved blades is 45 degrees, and the net distance between the two is 0.6 to 1.2 m. A connecting slot 31 is arranged at the lower end of each improved blade 3, and one end of the elastic substrate 2 is connected to the connecting slot 31 by special glue, and the other end is connected to the fixing block 42 by a bolt 5. The side of the elastic substrate 2 is also paved with a piezoelectric ceramic 6. When the improved blade 3 is blown by wind, the improved blade 3 will shake greatly, thereby driving the elastic substrate 2 to vibrate, and then squeezing the piezoelectric ceramic 6 to deform and generate electrical energy.

[0034] Specifically, Figure 1 , Figure 4 As shown, the improved blade 3 is thicker in the middle and thinner at both ends, and has a front end 32 and a rear end 33, and the thickness of the front end 32 is greater than the thickness of the rear end 33, which reduces the mass of the blade while ensuring that the improved blade 3 has sufficient structural strength, making it easier to vibrate. The middle part of the improved blade 3 is curved, and its cross-section is arc-shaped. The improved blade 3 has an inner surface 34 and an outer surface 35, wherein the curvature of the inner surface 34 is greater than the curvature of the outer surface 35. The inner surface 34 of the arc-shaped improved blade 3 is set outward so that more wind energy can be collected. The cross-sectional shape of the improved blade 3 is also designed by reversely utilizing the buffeting suppression technology, so that it can still generate more wind-induced mechanical energy under the blowing of a small wind force.

[0035] Flutter is an irregular, violent vibration caused by flow separation. It occurs when the boundary layer on the wing surface transitions to a turbulent state, causing the airflow to separate from the wing surface and form vortices. This airflow separation and vortex shedding will produce pressure fluctuations on the wing, causing flutter. In order to eliminate the negative impact of flutter on aircraft performance, designers often take measures such as changing the wing shape, using leading edge slats and flaps, and using vortex generators.

[0036] The present invention adopts a strategy opposite to that of aircraft buffeting suppression, and improves the cross-sectional shape of the blade so that it can still generate greater vibration under a smaller wind force, thereby increasing energy output.

[0037] like Figure 4 As shown, the profile design parameters of the improved blade 3 include chord length c, camber position p, thickness t and maximum camber m. The chord length c refers to the straight-line distance from the front end to the rear end of the blade, which is the reference length of the blade profile. The chord length c determines the size of the blade and affects the surface area and wind resistance of the blade. A longer chord length c can increase the contact area between the blade and the wind, thereby improving the energy collection efficiency. The maximum camber m refers to the maximum convexity of the blade profile in the direction perpendicular to the chord, usually expressed as a percentage of the chord length c. The camber affects the aerodynamic characteristics of the blade. A larger camber can increase the lift of the blade, but it will also increase the resistance. In a wind energy collector, an appropriate camber can promote airflow separation and vortex shedding, thereby increasing the vibration amplitude. The camber position p refers to the proportion of the chord length c where the maximum camber is located, usually expressed as a percentage of the distance between the maximum camber location and the front end 31 of the improved blade to the chord length c. The camber position determines the airflow separation point of the blade. The appropriate camber position can optimize the position of airflow separation, making vortex shedding more likely to occur, thereby increasing the vibration amplitude of the blade. The thickness t refers to the maximum thickness of the blade section in the direction perpendicular to the chord, usually expressed as a percentage of the chord length c. The thickness affects the stiffness and mass distribution of the blade. The appropriate thickness can ensure that the blade can generate sufficient vibration under the action of wind while maintaining structural strength.

[0038] In this solution, the maximum camber value m is 0.05 to 0.15 times the chord length. The smaller maximum camber value is selected to increase the flexibility of the blade without increasing the complexity of the structure too much, so that it is easier to respond to wind vibration. Preferably, the maximum camber value m is 0.1 times the chord length. The camber position p is 0.55 to 0.7 times the chord length, which is selected based on the vortex shedding theory to ensure that the airflow separates in the rear half of the blade, thereby generating flutter. Preferably, the camber position p is 0.6 times the chord length, that is, the maximum camber is designed at 60% of the chord length. The thickness t is 0.15 to 0.3 times the chord length. The relatively thin thickness is selected to reduce the mass of the blade, making it easier to vibrate while maintaining sufficient structural strength. Thinner blades are more likely to bend and vibrate under the action of wind, which helps to increase the contact area with the wind and the energy conversion efficiency. Preferably, the thickness t is 0.24 times the chord length.

[0039] Based on the design of the above profile parameters, the blades can be fluttered under wind, generating more wind-induced mechanical energy, which can be converted into more electrical energy. At the same time, combined with the Kaimal wind spectrum, adjusting the cross-sectional parameters of the improved blades can further increase the vibration mechanical energy. The following is an example of adjusting the cross-sectional parameters of the improved blades combined with the Kaimal wind spectrum, taking Zhuhai and Shanghai as examples.

[0040] 1. Calculate the peak frequency of local winds in Zhuhai and Shanghai.

[0041] When the equipment was used in Zhuhai, statistics were collected on the local wind speed in Zhuhai over the past five years, and the average wind speed was found to be 3.88m / s. Combined with the kamial spectrum, the frequency peak was found to be 8.0HZ.

[0042] 2. Calculate the cross-sectional parameters.

[0043] Knowing the natural frequency of wind, in order to infer the cross-sectional parameters and weight of the beam, the principles of structural dynamics need to be applied. First of all, the natural frequency of wind actually refers to the vibration frequency of the beam under the action of wind, which is related to the natural frequency of the beam itself.

[0044] When designing this product, the improved blade is vertically upward, one end is connected to the sleeve device, and the other end is suspended, so it can be treated as a cantilever beam. In order to make the improved blade resonate with the wind under the action of wind, the natural frequency of the beam should be consistent with the peak wind frequency obtained from local statistics. The natural frequency of the beam can be calculated according to the following four formulas:

[0045]

[0046]

[0047]

[0048] m=ρV (4)

[0049] Where f is the natural frequency of the beam (HZ), k is the stiffness of the cantilever beam (N / m 2 ), I is the moment of inertia (mm 4 ), E is the elastic modulus (Pa), and m is the weight of the cantilever beam.

[0050] According to the material used for the cantilever beam, check its material density and elastic modulus. Here, take a certain steel as an example. After checking, its material density ρ=7800kg / m 3, elastic modulus E = 200GPa. It can be calculated that when the horizontal projection length of the cantilever beam is L = 1m, the width b = 0.01m, and the height h = 0.02m, the natural frequency f of the beam is 8.06, which is closest to the frequency peak of the wind speed in Zhuhai in the past five years. That is, when the horizontal projection length of the cantilever beam is L = 1m, the width b = 0.01m, and the height h = 0.02m, resonance can occur with maximum efficiency.

[0051] When the equipment was used in Shanghai, statistics were collected on the local wind speed in Shanghai over the past five years, and the average wind speed was found to be 2.84m / s. Combined with the kamial spectrum, the frequency peak was found to be 5.9HZ.

[0052] From the above formula, we can know that the natural frequency f of the beam is proportional to the stiffness k and inversely proportional to the mass m. Both the stiffness k and the mass m are related to the cross-sectional parameters b, h, and L. Therefore, it can be adjusted by increasing L and reducing b and h. When the width b = 0.008m, the height h = 0.018m, and the length L = 1.1m, the natural frequency f = 5.98HZ, which is closest to the frequency peak value of 5.9HZ, and is consistent with the statistically obtained Shanghai wind frequency, so resonance can occur with maximum efficiency.

[0053] From the above, we can infer that when the wind frequency is inconsistent in different places, the natural frequency of the beam can be changed by adjusting the cross-sectional parameters b, h, and L. When the wind frequency is large, b and h can be appropriately increased and L can be reduced; when the wind frequency is small, b and h can be appropriately reduced and L can be increased. When it is close to the local statistical wind frequency amplitude, the resonance effect can occur under the blowing of the wind.

[0054] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the technical solution of the present invention, and are not intended to limit the specific implementation methods of the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the claims of the present invention shall be included in the protection scope of the claims of the present invention.

Claims

1. A vibration power generation device using reverse vibration suppression technology, comprising a sleeve device and a plurality of improved blades, wherein the sleeve device is roughly cylindrical; the plurality of improved blades are evenly distributed on the outer wall of the sleeve device, one end of the improved blade is connected to the outer wall of the sleeve device through an elastic substrate, and piezoelectric ceramics are laid on the elastic substrate, characterized in that: The middle portion of the improved blade is bent, so that the cross section of the improved blade is arc-shaped.

2. A vibration power generation device using reverse chattering suppression technology according to claim 1, characterized in that: The improved blade has an inner surface and an outer surface, the curvature of the inner surface is greater than that of the outer surface, the outer surface of the improved blade faces the sleeve device, and the inner surface of the improved blade is away from the sleeve device.

3. A vibration power generation device using reverse chattering suppression technology according to claim 1, characterized in that: The cross section of the improved blade is thicker in the middle and thinner at both ends, and the improved blade has a front end and a rear end, and the thickness of the front end of the improved blade is greater than the thickness of the rear end of the improved blade.

4. A vibration power generation device using reverse chattering suppression technology according to claim 3, characterized in that: The distance between the front end of the improved blade and the curvature position is greater than the distance between the rear end of the improved blade and the curvature position.

5. A vibration power generation device using reverse chattering suppression technology according to claim 4, characterized in that: The distance p between the front end of the improved blade and the curvature position is 0.55 to 0.7 times the chord length.

6. A vibration power generation device according to any one of claims 1 to 5, characterized in that: The maximum curvature m of the improved blade is 0.05 to 0.15 times the chord length.

7. A vibration power generation device using reverse chattering suppression technology according to claim 6, characterized in that: The thickness t of the improved blade is 0.15 to 0.3 times the chord length.

8. The vibration power generation device according to claim 6, characterized in that: The number of the improved leaves is 6 to 10.

9. The vibration power generation device according to claim 6, characterized in that: The elastic base is connected to the outer wall of the sleeve device through a ball joint device, the ball joint device is fixed on the outer wall of the sleeve device, the ball joint device has a rotating shaft, the rotating shaft is rotatable, and the elastic base is connected to the rotating shaft of the ball joint device.

10. A vibration power generation device using reverse chattering suppression technology according to claim 9, characterized in that: The net distance between two adjacent improved blades is 0.6-1.2 m.

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