Breeze power generation system

Abstract

The invention discloses a breeze power generation system. The invention relates to the technical field of wind power generation in renewable energy technologies. Comprising a wind energy-electric energy conversion assembly 3 installed on a frame body 1 and further comprises a wind energy assembly 2 responsible for transmitting wind energy to the wind energy-electric energy conversion assembly 3, and the wind energy assembly 2 comprises a plurality of fan blades 202 arranged in an annular array mode; the manifold surface of the fan blade 202 is of a fiber bundle type asymmetric topological configuration with an attack angle alpha and an airfoil profile curve beta as parameters; the symmetry constraint of the Euclidean group E (3) is converted into geometric transformation of a local coordinate system through topological mapping of the fiber bundles, so that the surface of the blade keeps continuous differentiability in a complex flow field environment, and the structural stability and aerodynamic performance are improved. The D4 symmetric group structure realizes periodic distribution of a flow field and a velocity field through quadruple rotational symmetry, so that wake vorticity is uniformly diffused in a rotational symmetry plane, a wake superposition effect of a traditional asymmetric layout is avoided, and mechanical vibration is reduced.

Description

Technical Field

[0001] This invention relates to the field of wind power generation technology in renewable energy technology, specifically to energy capture and efficient conversion in low wind speed environments (<3m / s), urban building integration, IoT sensor power supply, remote monitoring equipment and offshore / onshore wind farm technology, and particularly to micro-wind power generation systems. Background Technology

[0002] Micro-wind power generation systems, as a novel distributed energy technology, are primarily designed to meet energy capture needs in low-wind-speed environments (typically <3 m / s). They are widely used in scenarios such as urban building surfaces, IoT sensor nodes, and remote monitoring equipment, providing sustainable power support for low-power devices. [1] This technology is of strategic significance for promoting the widespread application of renewable energy and achieving my country's carbon neutrality and carbon peaking goals.

[0003] The configuration and spatial layout of the fan blade system are core factors determining energy conversion efficiency and operational stability. Current mainstream designs mostly employ multi-blade radially symmetrical layouts, with typical configurations including propeller-type, vertical-axis Darrieus-type, and biomimetic flapping-wing type. [2] For example, vertical axis Darius rotors (VAWTs) can effectively suppress boundary layer separation and improve the lift coefficient through variable pitch control, thereby optimizing start-up characteristics and energy capture efficiency under low Reynolds number conditions. [2] Radial symmetry layouts ensure system stability through torque balance characteristics. For example, the Savonius rotor, due to its simple structure, is widely used in small-scale power generation. However, its power coefficient is limited by suboptimal blade profile design. Performance can be improved through parametric profile optimization. [3] Optimization of key parameters such as the number of blades and tip speed ratio plays a decisive role in improving the performance of small wind turbines (SWTs). [4] .

[0004] However, it is difficult to achieve geometric compatibility between the blade manifold surface and the Euclidean group symmetry constraint layout, resulting in significant wake interference effects. [5] For example, traditional blade surfaces often use parametric smooth surfaces (such as NACA airfoils or Bézier surfaces). In periodic or rotationally symmetric layouts (such as triple symmetric configurations), each blade needs to achieve a strictly equidistant mapping through a three-dimensional rotation group SO(3). However, parametric surfaces often exhibit problems such as discontinuity in normal direction, abrupt curvature changes, or geodesic distance mismatch at splicing boundaries. For example, the NACA 0012 airfoil is prone to generating negative torque effects under nonlinear aerodynamic loads, reducing power efficiency. [5] .

[0005] Geometric incompatibility leads to non-uniform superposition of adjacent blade wakes in the plane of symmetry, inducing typical wake interference phenomena such as enhanced coherent vortex shedding, delayed pressure recovery, and aggravated downstream velocity deficit. [6-10] The wake effect, a key constraint in wind farm design, significantly reduces the power generation of downstream turbines and increases structural fatigue load by creating a low-speed, high-turbulence zone. [6] Studies of offshore wind farms have shown that turbulent channel flow in the wake of upstream turbines affects drag characteristics through Reynolds stress transfer. [7] When a free-surface turbulent flow passes through a square strip, the surface roughness and water surface deformation will alter the velocity fluctuations and shear stress distribution. [8] The wake not only manifests as a velocity deficit, but its additional turbulence also significantly increases the fatigue load on downstream units and shortens equipment lifespan. [9-10] .

[0006] The cited references for this invention are as follows:

[0007] [1]Shankara Murthy HM, Hegde RN, Gaonkar RU, et al. A critical assessment of significant developments in wind turbine Performance [J]. International Journal of Ambient Energy, 2023, 45(1). [2]Gupta A, Abderrahmane HA, Janajreh I. Flow analysis and sensitivity study of Vertical-axis wind turbine under variable Pitching [J]. Applied Energy, 2024, 358: 122648. [3]Mohan M, Saha U K. Evolving a Novel Blade Shape of a Savonius WindRotor Using an Optimization Technique Coupled With Numerical Simulations andWind Tunnel Tests [J]. Journal of Energy Resources Technology, 2024, 146(4). [4]Yilmaz O. Low-speed, low induction multi-blade rotor for energyefficient small wind Turbines [J]. Energy, 2023, 282: 128607. [5]Junejo A R, Gilal N U, Doh J. Physics-informed optimization ofrobust control system to enhance power efficiency of renewable energy:Application to wind Turbine [J]. Energy, 2023, 263: 125667. [6]Umair M, Tardu S, Doche O. Reynolds stresses transport in aturbulent channel flow subjected to streamwise traveling Waves [J]. PhysicalReview Fluids, 2022, 7(5). [7]Jalalabadi R, Stoesser T. Large-eddy simulation of free-surfaceturbulent channel flow over square Bars [J]. International Journal of Heatand Fluid Flow, 2023, 103: 109187. [8]Ling Z, Zhao Z, Liu Y, et al. Multi-objective layout optimizationfor wind farms based on non-uniformly distributed turbulence and a new three-dimensional multiple wake Model [J]. Renewable Energy, 2024, 227: 120558. [9]Xu L, Zhou G, Guo Z. ART-LSTANet: An adaptive intelligent method for wind turbine wake Analysis [J]. Engineering Applications of ArtificialIntelligence, 2023, 126: 106809.

[10] Ali S, Park H, Lee D. Multi-Criteria Optimization of WindTurbines in an Offshore Wind Farm with Monopile Foundation Considering Structural Integrity and Energy Generation [J]. Journal of Marine Science andEngineering, 2024, 12(12): 2313. Summary of the Invention In view of this, the present invention aims to provide a micro-wind power generation system to solve or alleviate the technical problems existing in the prior art, namely, the difficulty in achieving geometric compatibility between the layout of the blade manifold surface and the Euclidean group symmetry constraint, and to at least provide a beneficial alternative; the technical solution of the present invention is implemented as follows: the micro-wind power generation system includes a wind energy to electricity conversion component 3 installed on a frame 1, and further includes, The wind energy is responsible for transferring wind energy to the wind energy-electricity conversion component 3 and then to the wind energy component 2. The wind energy component 2 includes a plurality of fan blades 202 arranged in a ring array. The manifold surface of fan blade 202 is a fiber bundle asymmetric topological configuration with parameters of angle of attack α and airfoil curve β. The wind group layout formed by each fan blade 202 is constrained by the symmetry of the Euclidean group. The overall topology of the wind group layout is a loop space formed based on the center point of the fundamental group π1. The relative positions between each fan blade 202 are parameterized by the rotation angle θ and the radial distance r.

[0008] The fan blade 202 is fixed to the frame 201, the frame 201 is rotatably fitted to the frame 1, the wind energy to electricity conversion component 3 is installed on the frame 1, and the frame 201 is connected to the input end of the wind energy to electricity conversion component 3 through a drive shaft.

[0009] Each fan blade 202 has a discrete hole system including several guide holes 203.

[0010] In one embodiment, the asymmetric topological configuration of the blade 202 includes a leading edge region that forms a high curvature gradient field, a trailing edge region that disperses wake vorticity, and a region constrained by homology group theory, whose relative position to the leading and trailing edge regions is in the middle region of the flow field stress concentration region with the blade chord length as the baseline.

[0011] In one embodiment, the leading edge region, trailing edge region, and intermediate region together form a chord length extension with a cubic polynomial distribution, and its twist angle is constrained by a fifth-order Bezier curve fitting.

[0012] In one embodiment, the wind array layout exhibits a rotationally symmetric topology under the constraint of minimum safety spacing. The rotationally symmetric topology forms geodesic paths through angle bisectors, and the layout satisfies the condition of minimizing geodesic curvature. The rotationally symmetric topology has a group effect with the center point as the fixed point, and the rotation angle θ of each fan blade satisfies the modulus 2π congruence relationship. The radial distance r satisfies the convex function constraint to avoid wake interference.

[0013] In one embodiment, the wind assembly layout forms a D4 symmetrical group structure, and the spacing between each fan blade 202 satisfies the constraint of 7 times the rotor diameter.

[0014] In one embodiment, the fiber-bundled asymmetric topology and wind array layout of the fan blade 202 are constrained by the following model: with the wind energy utilization coefficient Cp as the objective function, the constraints include the lift coefficient C. l / Drag coefficient C d Structural stress σ≤ yield stress σmax, wake velocity attenuation rate v∝1 / r 2 Asymmetric topological configurations optimize stress concentration regions using homology group theory; wind array layouts ensure rotational symmetry using the D4 symmetry group; geodesic paths are achieved through... r θ=0 ensures the shortest path.

[0015] Among them, the leaf element-momentum theory: ; ; Among them, power ; Among them, the tip speed ratio ; The bundle conditions for the asymmetric topological configuration include: Among them, the leading edge curvature gradient field Where s is the arc length parameter; Among them, the trailing edge fractal structure Where N is the number of fractal units and ε is the scale factor; Among them, the chord length is a cubic polynomial distribution. ; Among them, the fifth-order Bézier curve of twist angle ; The constraints of the wind array layout include: D4 symmetric group constraints: ; ; Among them, the radial distance convex constraint: ; Among them, the spacing constraint is: .

[0016] Compared with existing technologies, the mechanism by which this invention solves the problems of traditional technologies lies in: 1. Fiber bundle topology mapping: By parametric mapping of the manifold surface, the symmetry constraint of the Euclidean group E(3) is transformed into a geometric transformation of the local coordinate system, so that the blade surface can maintain continuous differentiability under any rotation angle.

[0017] II. Effect of D4 symmetry group: The periodic distribution of the velocity field of the flow field is achieved through four-fold rotational symmetry, so that the wake vorticity is uniformly diffused within the rotational symmetry plane, avoiding the wake superposition effect generated by traditional asymmetric layout.

[0018] III. Geodesic Motion Constraints: Through the hyperbolic geometry design of the guide rail, the fan blade 202 satisfies the following constraints during rotation. r The geodesic curvature condition of θ=0 enables natural path planning for mechanical motion, reducing energy loss in the transmission system.

[0019] Compared with the prior art, the beneficial effects of the present invention are: I. Manifold Surface Continuity: Fiber bundle topological mapping transforms the Euclidean group E(3) symmetry constraint into a geometric transformation of the local coordinate system, enabling the blade surface to maintain continuous differentiability under complex flow field conditions, thereby improving structural stability and aerodynamic performance. The D4 symmetry group structure achieves a periodic distribution of the flow field velocity field through quadruple rotational symmetry, allowing the wake vorticity to diffuse uniformly within the rotational symmetry plane, avoiding the wake superposition effect of traditional asymmetric layouts, and reducing mechanical vibration.

[0020] II. Motion Path Optimization: Geodesic Motion Constraint Design Ensures that Fan Blade 202 Satisfies the Requirement During Rotation r The geodesic curvature condition of θ=0 enables natural path planning of the transmission system, reducing energy loss and mechanical wear. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 This is a three-dimensional schematic diagram of the present invention; Figure 2 This is a three-dimensional schematic diagram from another perspective of the present invention; Figure 3 This is a three-dimensional schematic diagram of the wind power module of the present invention; Figure 4 This is a three-dimensional schematic diagram of the fan blade of the present invention; Figure 5 This is a schematic diagram of the fan blade surface of the present invention; Figure 6 This is a schematic diagram of the nonlinear coupling relationship in Embodiment 2 of the present invention; Figure 7 This is a schematic diagram of a finite element simulation of Embodiment 2 of the present invention; Figure 8 This is a schematic diagram of the nonlinear coupling relationship in Embodiment 3 of the present invention; Figure 9 This is a schematic diagram illustrating the nonlinear enhancement mechanism of fatigue strength by the cubic polynomial chord length distribution of the present invention. Figure 10 This is a schematic diagram of a finite element simulation of Embodiment 3 of the present invention; Figure 11 This is a schematic diagram of the nonlinear coupling mechanism of geodesic path, rotational angular modulus 2π congruence, and radial distance convex function constraint in Embodiment 4 of the present invention; Figure 12 This is a schematic diagram of the nonlinear coupling mechanism between the D4 symmetric group structure and the wake dynamics model in Embodiment 4 of the present invention. Figure 13 This is a schematic diagram of a finite element simulation of Embodiment 4 of the present invention; Figure 14 This is a schematic diagram illustrating the application results of the present invention. Detailed Implementation

[0023] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below; It should be noted that the various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since it corresponds to the method disclosed in the embodiments, the description is relatively simple, and relevant parts can be referred to the method section.

[0024] The following is an explanation of the terms used in the embodiments: (1) Angle of attack α: The angle between the chord line of blade 202 and the direction of incoming flow, which determines the lift and drag coefficient. The lift drops sharply when the critical angle of attack is exceeded.

[0025] (2) Airfoil curve β: The geometry of the 202 section of the blade affects the curvature and maximum thickness of the mid-arc.

[0026] (3) Fiber cluster asymmetric topology: In the design of the fan blade 202, the fiber space (e.g., vector field) is added at each point to achieve a non-uniform curvature distribution.

[0027] (4) Wind group layout: relative position configuration of multi-blade 202.

[0028] (5) Euclidean group: a transformation group that preserves the distance in Euclidean space (translation + rotation + reflection), with the dimension n determining the degree of freedom.

[0029] (6) Euclidean group symmetry constraint: The layout of the 202 fan blades must satisfy the E(n) group symmetry to avoid wake interference.

[0030] (7) Topological types: classification of topological space connectivity, genus and homotopy.

[0031] (8) Basic group π1: The group structure of closed homotopy classes in topological space, reflecting connectivity.

[0032] (9) The center point of the basic group π1: the fixed point in the basic group, corresponding to the layout base point.

[0033] (10) Loop space: a set of closed homotopy classes, and the group operation is path connection.

[0034] (11) Rotation angle θ: The angle at which the fan blade 202 rotates around the center, which determines the symmetry of the layout.

[0035] (12) Radial distance r: The distance from the blade 202 to the center of the frame 201, which affects the wind energy capture efficiency.

[0036] (13) High curvature gradient field: the region where the curvature of the leading edge of the 202 blade changes sharply, which enhances wind energy capture.

[0037] (14) Wake vorticity: The intensity of the vortex generated at the trailing edge of blade 202 affects downstream wind energy.

[0038] (15) Homology group theory: a topological theory that uses the algebraic representation of the connectivity of topological space to identify the critical point along the chord length of the fan blade 202, eliminate stress concentration, and improve structural strength to optimize stress distribution.

[0039] (16) Flow field stress concentration area: The area where the airflow exerts a concentrated force on the fan blade 202, which requires structural reinforcement.

[0040] (17) chord length of blade 202: The straight distance from the leading edge to the trailing edge of blade 202 determines the aerodynamic performance.

[0041] (18) Cubic polynomial distribution of chord length along the blade: The chord length varies along the blade 202 according to a cubic function to optimize the lift distribution. Combined with Bézier curve fitting, a smooth transition from the blade root to the blade tip is achieved, reducing stress abrupt changes.

[0042] (19) Fifth-order Bézier curve fitting constraint: The twist angle varies along the span according to the fifth-order Bézier curve to ensure a smooth transition. This avoids the aerodynamic performance degradation caused by abrupt changes in the twist angle and improves wind energy capture efficiency.

[0043] (20) Angle bisector shape: The geometric shape of the angle bisector in the fan blade 202 layout determines the geodesic path.

[0044] (21) Geodesic path: the shortest path on the curved surface, used to optimize the wind group layout path.

[0045] (22) 2π congruence relation: The rotation angle θ satisfies modulo 2π congruence, ensuring the periodic symmetry of the layout.

[0046] (23) Convex function constraint: The radial distance r satisfies the convex function to avoid local extrema leading to layout failure.

[0047] (24) Rotor diameter: The rotation diameter of the fan blade 202 in motion, which determines the range of wind energy capture.

[0048] (25) Straight line connection angle: The angle between the lines connecting the centers of the two blades 202 determines the compactness of the layout.

[0049] (26) Center angle: The angle between the center of fan blade 202 and the center of rotation determines the symmetry of the layout.

[0050] The following embodiments define the relevant symbols:

[0051] Example 1: As Figures 1-5 As shown, this embodiment discloses a micro-wind power generation system. The frame 1 serves as a basic support platform, on which the wind energy to electricity conversion component 3 is fixedly installed. The wind energy component 2 adopts a structure of fan blades 202 arranged in a ring array. Specifically, N fan blade units (N≥3) are arranged at equal intervals along the circumference on the frame 201 with the center point as the base point. The manifold surface of each fan blade 202 is constructed into a fiber bundle asymmetric topology by parameterizing the angle of attack α (0°≤α≤30°) and the airfoil curve β.

[0052] Specifically, the frame 201 is rotatably coupled to the frame body 1 via rolling bearings, and the drive shaft uses a spline connection to transmit rotational kinetic energy to the generator input end of the wind energy to electricity conversion component 3. The fan blade 202 has a discrete hole system on its surface, including guide holes 203 with a diameter of 5-20mm.

[0053] Understandably, this design is based on the symmetry constraints of the Euclidean group E(3), using the center point of the fundamental group π1 as the topological base point to construct the loop space and achieve geometric compatibility of the wind pack layout. The fiber-bundle asymmetric topological configuration achieves active control of flow field boundary layer separation under low Reynolds number conditions through the parameterized coupling of the angle of attack α and the airfoil curve β. The parameterized design of the rotation angle θ (θ=2π / N) and the radial distance r (r=k·R, k is a proportionality coefficient) ensures that each blade 202 satisfies the condition of minimizing geodesic curvature during rotation, avoiding wake superposition effects.

[0054] Example 2: Based on the aforementioned examples, this example further discloses an asymmetric topological configuration for the fan blade 202. In implementing the asymmetric topological configuration of the fan blade 202, the leading edge region is formed using a five-axis CNC machining center to achieve a high curvature gradient field, with the radius of curvature decreasing exponentially from the blade root to the blade tip (R0). c =R0e ky k=0.05mm - ¹) Discrete guide holes 203 with a diameter of 0.5-1.0 mm are created in the trailing edge region using laser micro-hole processing technology to form a fractal topology to disperse wake vorticity. The relative position of the middle region to the leading / trailing edge regions is determined by finite element topology optimization based on homology group theory. The chord length baseline is smoothly transitioned using cubic spline interpolation to ensure that the stress concentration area of ​​the flow field is located in the range of 30%-70% of the blade chord length.

[0055] It should be noted that the configuration design of this embodiment follows the following underlying logic: the high curvature gradient field at the leading edge accelerates the flow field through the Cauchy momentum equation, improving the dynamic pressure conversion efficiency at low Reynolds numbers; the fractal structure at the trailing edge is based on the turbulent boundary layer theory, and changes the wake vorticity distribution through the micro-jet generated by the guide hole 203, reducing the turbulence intensity; the homology group constraint in the middle region achieves the coordination of the stress tensor field through the Hodge decomposition theorem, ensuring that the stress distribution of the blade is uniform during rotation and avoiding local stress concentration.

[0056] like Figure 6 As shown in the left panel (Cp-λ-v relationship), Cp exhibits a parabolic trend of first increasing and then decreasing with λ, reaching a peak of 0.48 near λ=7, consistent with the prediction of the leaf element-momentum theory. The influence of wind speed v manifests as a nonlinear modulation effect—when the wind speed increases from 2 m / s to 12 m / s, the peak region of Cp shifts by approximately 15% towards higher λ, revealing the dynamic balance mechanism between low-wind-speed initiation and high-wind-speed operation.

[0057] like Figure 6 As shown in the middle panel (σ-θ-r relationship), the stress distribution exhibits significant anisotropy: in the θ=30°-60° range, stress concentration zones (σ>250MPa) appear in the r=2-4m region, while when θ>70°, the stress decreases exponentially with increasing r. This distribution verifies the stress dispersion effect achieved by the fiber bundle topology through hyperboloid transition design, which conforms to Saint-Venant's principle in mechanics of materials.

[0058] like Figure 6 As shown in the right panel (εv-r relationship), the measured data points (solid red line) have a good fit of 0.98 with the theoretical model (εv∝1 / r²), which verifies the accuracy of the wake dynamics model.

[0059] It should be pointed out that, such as Figure 7 As shown, the high curvature design at the leading edge reduces the starting wind speed to 2.1 m / s, the fractal structure at the trailing edge reduces the turbulence intensity of the downstream unit by 25% through wake vortex dispersion, and the coherence constraint in the middle region reduces the maximum stress value of the blade by 30%, meeting the fatigue load requirements in the IEC 61400-2 standard.

[0060] Example 3: Based on the previous examples, this example further discloses the constraint scheme of the asymmetric topological configuration of the fan blade 202.

[0061] The chord lengths of the leading, trailing, and intermediate regions are parametrically controlled using a cubic polynomial distribution, where y represents the spanwise coordinate. Twist angle... (y) Control points are determined by fitting a fifth-order Bézier curve. i is dynamically adjusted based on the angle of attack α (α=5) 25), the parameter t∈[0,1] is normalized by spanwise position. This implementation achieves precise forming of the blade profile through a five-axis linkage machining center, ensuring chord length tolerance ≤±0.1mm and torsion angle tolerance ≤±0.2°.

[0062] Specifically, the cubic polynomial chord length distribution is approximately optimized using Taylor expansion to optimize the flow field pressure gradient, reducing the risk of boundary layer separation and increasing the lift coefficient C at low Reynolds numbers. l The fifth-order Bézier curve fitting utilizes the piecewise smoothness of the Bernstein basis functions to achieve a continuous change in the torsion angle, avoiding the stress abrupt changes caused by traditional linear interpolation. According to the Navier-Stokes equations, this configuration makes the flow field velocity gradient... The uniform distribution of v along the chord length reduces turbulent dissipation. At the same time, the parameterized coupling of the chord length and the torsion angle satisfies the symmetry constraint of the Euclidean group E(3), ensuring the geometric compatibility of the wind array layout.

[0063] like Figure 8 The upper left panel (chord length coefficient-Reynolds number relationship) shows the cubic polynomial chord length coefficients (a0-a3) as a function of the Reynolds number Re (10). 4 -10 6 The nonlinear evolution of a0 shows that a0 exhibits sinusoidal modulation characteristics (amplitude 0.1), reflecting the optimization effect of Taylor expansion on the pressure gradient of the flow field; a1 exhibits cosine decay characteristics (period 10). 5 The boundary layer separation risk suppression mechanism was verified; a2-a3 showed exponential decay and linear growth characteristics, respectively, which met the optimization requirements of the lift coefficient Cl at low Reynolds number.

[0064] like Figure 8 The distribution characteristics of the torsion angle φ(y) of the fifth-order Bézier curve fitting shown in the upper right panel (Bézier curve torsion angle distribution) are as follows: φ(y) presents a C² continuous smooth transition in the t∈[0,1] interval, avoiding the stress abrupt change caused by traditional linear interpolation.

[0065] like Figure 8 The flow field velocity gradient is shown in the lower left panel (three-dimensional velocity gradient distribution). The nonlinear distribution characteristics of v with respect to spanwise position y and Reynolds number Re are shown. v reaches its maximum value of 1.8s at y=0.5. - ¹, It exhibits an exponential growth trend with increasing Re (exponential 0.3).

[0066] like Figure 8 The lower right panel (vector field flow field distribution) shows the two-dimensional distribution characteristics of the flow field velocity. The velocity vector exhibits a spiral distribution pattern, reaching a maximum value of 1.2 m / s at x=0.5, y=0.5.

[0067] Among them, the cubic polynomial chord length distribution makes the spanwise load distribution of the blade more uniform, and the fatigue strength is increased by 40%, meeting the GL 2010 wind power certification standard. like Figure 9 The upper left panel (three-dimensional fatigue strength distribution) shows the fatigue strength as a function of wind speed (2-12 m / s) and Reynolds number (10). 4 -10 6 The nonlinear evolution law of fatigue strength at wind speeds of 4-8 m / s and Reynolds numbers of 3 × 10⁻⁶ m / s: 4 -8×10 4 The interval showed a significant enhancement effect (peak value 48%).

[0068] like Figure 10 The upper right panel (evolution of chord length coefficient a0) shows the nonlinear variation characteristics of the a0 coefficient with Reynolds number: a0 at a Reynolds number of 10... 4 -10 5 The interval exhibits sinusoidal modulation characteristics (amplitude 0.15), and at 10... 5 -10 6 The interval exhibits an exponential decay characteristic (decay constant 0.002), verifying the optimization effect of Taylor expansion on the flow field pressure gradient.

[0069] like Figure 10 The spanwise load heatmap shown in the lower left panel shows that the load has a maximum value of 12 N / m in the middle of the chord (y=0.5) and shows a linear increasing trend with increasing wind speed (slope 0.8 N / m²).

[0070] like Figure 10 The bottom right panel (temperature-fatigue strength contour line) shows the combined effect of temperature (-20~40℃) and wind speed on fatigue strength: fatigue strength reaches its maximum value of 50% at a temperature of 20℃ and a wind speed of 6m / s, and exhibits a linear decay characteristic as the temperature increases (decay rate 0.5% / ℃).

[0071] Furthermore, such as Figure 10 As shown, the torsion angle control achieved by fitting the fifth-order Bézier curve maintains the optimal angle of attack α of blade 202 within a wide wind speed range (2-12 m / s), and the wind energy utilization coefficient C p Increased to 0.52; and parametric design supports rapid prototyping iteration by adjusting the coefficient α. i and i It can be adapted to different installation scenarios (such as urban rooftops and offshore platforms).

[0072] Example 4: This example further discloses a specific implementation method for the wind turbine layout based on the previous examples. Under the constraint of minimum safety distance, the wind turbine layout adopts a D4 symmetry group structure to achieve rotational symmetry topology. Specifically, with the center point of frame 1 as the fixed point, a geodesic path is constructed through the angle bisector, and the path equation satisfies... s The geodesic curvature minimization condition for θ=0. The rotation angle θ of each blade is configured according to the modulus 2π congruence (θ... i =2πi / N+Δθ, i=1,2,...,N), the radial distance r is a quadratic convex function r(y=ky). 2 The +my+b (k>0) constraint ensures that the spacing Δr between adjacent fan blades 202 is ≥7Drotor.

[0073] Specifically, such as Figure 11 As shown, the geodesic path achieves torque-free rotation through the Levi-Civita connection, reducing mechanical losses; the modulus 2π congruence of the rotation angle θ ensures that each blade 202 achieves equidistant mapping under the action of the three-dimensional rotation group SO(3), satisfying the symmetry constraint of the Euclidean group E(3). The convex function constraint of the radial distance r ensures the monotonically decreasing characteristic of the wake velocity deficit Δu∝1 / r2 through Jensen's inequality, effectively suppressing wake interference. (1) The upper left panel (three-dimensional mechanical loss distribution) shows the nonlinear evolution of mechanical loss with rotation angle θ (0-2π rad) and radial distance r (1-10 m). Mechanical loss shows a significant reduction effect (valley value 0.3 W) in the range of θ=π / 2-3π / 2 and r=5-7 m, which verifies the optimized design of Levi-Civita connection for torque-free rotation.

[0074] (2) The upper right panel (wake velocity loss heatmap) shows the distribution characteristics of the wake velocity loss Δu with radial distance r (1-10m) and wind speed v (2-12m / s). Δu exhibits a 1 / r² attenuation characteristic in the r=1-3m range (peak value 1.2m / s), which is consistent with the prediction of Jensen's inequality for convex function constraints.

[0075] Example 5: This example further discloses a constraint scheme for the wind turbine layout based on the previous examples. The wind turbine layout adopts a D4 symmetry group structure to achieve fourfold rotational symmetry. Specifically, with the center point of frame 1 as the center of symmetry, the rotationally symmetrical configuration of each fan blade 202 is achieved. The spacing Δd between adjacent fan blades 202 strictly satisfies Δd≥7Drotor (Drotor is the rotor diameter). This is monitored in real time by a laser rangefinder and fed back to the dynamic yaw control system to ensure that the spacing deviation is ≤±1% during operation. This layout achieves precise positioning of the fan blades 202 through a five-axis linkage machining center.

[0076] Furthermore, such as Figure 12 As shown, the underlying logic of the D4 symmetric group structure is based on the coupled optimization of group theory and fluid mechanics: the quadruple rotational symmetry realizes the periodic distribution of the flow velocity field through group representation theory, reducing turbulent mixing losses; the 7Drotor spacing constraint is based on the wake dynamics model to ensure the wake velocity deficit Δu∝1 / r of the upstream fan blade 202. 2 The downstream fan blade 202 attenuates the current to below the safe threshold to avoid wake superposition effects. (1) The upper left panel (three-dimensional flow field velocity field distribution) shows the nonlinear evolution of the flow field velocity field with rotation angle θ (0-2πrad) and radial distance r (1-10m). The velocity field exhibits sinusoidal modulation characteristics (amplitude 1.5m / s) in the range of θ=π / 2-3π / 2 and r=5-7m, which verifies the optimized design of the periodic distribution of the flow field by the D4 symmetry group.

[0077] (2) The upper right panel (wake velocity loss heatmap) shows the distribution characteristics of wake velocity loss Δu with radial distance r (1-10m) and wind speed v (2-12m / s). Δu exhibits a 1 / r² attenuation characteristic in the range of r=1-3m (peak value 1.2m / s), which is consistent with the wake dynamics model's prediction of the safety threshold.

[0078] (3) The left panel (D4 symmetry group parameter relationship) shows the modulus 2π congruence relationship between the rotation angle θ and the center angle γ. γ is constant at 7π / 15 (84°), and θ exhibits periodic remapping characteristics (period 2π), which verifies the optimization of the periodic distribution of the flow velocity field by the quadruple rotational symmetry.

[0079] Furthermore, such as Figure 13 As shown, according to the Navier-Stokes equations, the overall arrangement of each fan blade 202 causes the Reynolds stress τ in the flow field to... ij The blades are evenly distributed within the rotational symmetry plane, which improves energy conversion efficiency. At the same time, the D4 symmetry of the overall layout of each blade 202 satisfies the subgroup constraint of the Euclidean group E(3), thus ensuring the geometric compatibility of the wind group layout.

[0080] Preferably, the angle between any two blades 202 connected by a straight line is 84°, and the included angle to the center is 168°.

[0081] Application Example. This example simulates a wind farm in the eastern coastal region of China, where the average annual wind speed is 8 m / s, the temperature range is -5 to 35℃, and the humidity is 70-90%. The system adopts a D4 symmetrical group structure layout and is equipped with blade groups constrained by 7Drotor spacing, aiming to achieve efficient and stable power generation in low wind speed environments.

[0082] (a) Environmental parameters: Baseline wind speed: 8 m / s (turbulence intensity 15%); Temperature: 20℃ (standard operating conditions); Humidity: 70%; Atmospheric density: 1.225 kg / m³; (ii) Simulation parameters: Rotation angle θ: π / 3 (60°); Radial distance r: 5m (compliant with 7Drotor constraints); Wake velocity deficit Δu: 0.5 m / s (below the safety threshold); Blade material: CFRTP reinforced composite material (tensile strength 500 MPa); (III) Specific working conditions: like Figure 14 As shown: (1) Flow field optimization verification: At a wind speed of 8 m / s, the global velocity field vector diagram shows that the flow field exhibits a fourfold rotational symmetry distribution, with uniform vortex diffusion in the wake region at the blade tail and a 20% reduction in turbulence intensity. The D4 symmetry group structure reduces the velocity gradient in the flow field. The v is uniformly distributed along the chord length, reducing turbulent dissipation by 30%.

[0083] (2) Structural stress analysis: The von Mises stress distribution diagram of the blade shows that the maximum stress point of 42.5 MPa is located at the blade root, which meets the GL 2010 wind power certification standard (safety factor 2.5). The stress concentration in the leading edge region was optimized by cubic polynomial chord length distribution, which reduced the stress gradient by 30% and extended the fatigue life to 25 years.

[0084] (3) Wake control verification: The wake vortex diffusion slice shows that at the 7-rotor spacing (r=5m), the wake velocity deficit Δu=0.5m / s, which conforms to the 1 / r² decay law. The vortex diffusion at the downstream fan blades is uniform, avoiding the wake superposition effect, and the power generation of the downstream units is increased by 20%.

[0085] (4) Dynamic performance evaluation: The performance parameter-time relationship graph shows that the peak value of the system torque periodic fluctuation is 180 Nm and the average efficiency is 60%. In the wind speed range of 6-10 m / s, the efficiency fluctuation is ≤ ±3%, which meets the requirements of IEC 61400-2 standard.

[0086] (iv) Demonstration of technical effectiveness: The 3D velocity field vector diagram verifies that the D4 symmetry group achieves a periodic flow field distribution, reducing turbulent mixing losses by 15% and increasing the wind energy utilization coefficient Cp to 0.52. A close-up of the blade stress distribution shows a maximum stress of 42.5 MPa, meeting material strength requirements. The effectiveness of the radial distance convex function constraint is verified using Jensen's inequality.

[0087] The wake eddy diffusion slice confirms that the 7Drotor spacing constraint causes Δu to attenuate below the safe threshold at the downstream blades, avoiding wake superposition effects and improving overall power generation efficiency by 12%. The torque-efficiency time relationship curve shows that the system maintains stable operation under variable wind speed conditions, with efficiency fluctuations ≤±3%, meeting the requirements of distributed power generation systems.

[0088] (V) Conclusion: This application example fully verifies the nonlinear coupling mechanism between the D4 symmetric group structure and the wake dynamics model through finite element simulation, providing a visual basis for the efficient and stable operation of micro-wind power generation systems in low wind speed environments.

[0089] All the above embodiments merely illustrate implementation methods for relevant practical applications of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. A micro-wind power generation system, characterized in that, Including wind-to-electricity conversion components (3), and also including, The wind energy component (2) is responsible for transmitting wind energy to the wind energy-electricity conversion component (3), and the wind energy component (2) includes a plurality of fan blades (203). The manifold surface of the fan blade (203) is a fiber bundle asymmetric topological configuration with parameters of angle of attack α and airfoil curve β. The wind group layout formed by each of the fan blades (203) is constrained by the symmetry of the Euclidean group, and the overall topology of the wind group layout is a loop space formed based on the center point of the basic group π1.

2. The micro-wind power generation system according to claim 1, characterized in that: The asymmetric topological configuration of the fan blade (203) includes: A leading edge region that forms a high curvature gradient field; The trailing edge region that disperses wake vorticity; Constrained by the homology group theory, its relative position with the leading edge region and the trailing edge region is in the middle region of the flow field stress concentration region with the blade chord length as the baseline.

3. The micro-wind power generation system according to claim 2, characterized in that: The leading edge region, the trailing edge region, and the intermediate region together form a chord length extension with a cubic polynomial distribution, and its twist angle is constrained by a fifth-order Bezier curve fitting.

4. The micro-wind power generation system according to claim 1, characterized in that: The wind array layout exhibits a rotationally symmetric topology; the rotationally symmetric topology forms geodesic paths through angle bisectors. The rotationally symmetric topology has a group action with the center point as the fixed point. The rotation angle θ of each fan blade (203) satisfies the modulo 2π congruence relation, and the radial distance r satisfies the convex function constraint to avoid wake interference.

5. The micro-wind power generation system according to claim 4, characterized in that: The overall layout of the wind group forms a D4 symmetrical group structure, and the spacing between each fan blade (203) satisfies the constraint of 7 times the rotor diameter.

6. The micro-wind power generation system according to claim 5, characterized in that: The angle between any two of the aforementioned fan blades (203) is 84° and the included angle to the center is 168°.

7. The micro-wind power generation system according to claim 1, 2 or 4, characterized in that: Each of the fan blades (203) is provided with a discrete hole system including a plurality of guide holes (203).

8. The micro-wind power generation system according to claim 1, 2 or 4, characterized in that: The fiber-bundle asymmetric topology of the fan blades (203) and the wind array layout are constrained by the following model: The objective function is to maximize the wind energy utilization coefficient Cp, with constraints including the lift coefficient C. l / Drag coefficient C d Structural stress σ≤ yield stress σmax, wake velocity attenuation rate v∝1 / r 2 ; The asymmetric topological configuration optimizes the stress concentration region through homology group theory. The wind group layout ensures rotational symmetry through the D4 symmetry group; Geodesic path passes through r θ=0 ensures the shortest path.

9. The micro-wind power generation system according to claim 8, characterized in that: The model includes: Leaf element-momentum theory: ； ； power ; Tip speed ratio ; The bundle conditions for the asymmetric topological configuration include: Leading edge curvature gradient field Where s is the arc length parameter; trailing edge fractal structure Where N is the number of fractal units and ε is the scale factor; String length cubic polynomial distribution ; Fifth-order Bézier curve of twist angle ; The constraints of the wind array layout include: D4 symmetric group constraints: ； ； Radial distance convex constraint: ; Spacing constraints: .

10. The micro-wind power generation system according to claim 1, 2 or 4, characterized in that: The fan blade (203) is fixed to the frame (201), the frame (201) is rotatably fitted to the frame body (1), the wind energy to electricity conversion component (3) is installed on the frame body (1), and the frame (201) is connected to the input end of the wind energy to electricity conversion component (3) through a drive shaft.

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