New energy power generation device based on lever principle and dynamic balance system

Abstract

The invention discloses a new energy power generation device based on a lever principle and a dynamic balance system, and mainly solves the problems that traditional lever power generation is poor in rigidity and low in efficiency; 30%), the expansibility is insufficient, and the torque fluctuation is large. According to the core scheme, the bending rigidity of a 20-200 m ultra-long space truss lever is improved by 5-8 times compared with that of a solid lever, and flexural deformation is eliminated; 2) the gear-one-way bearing composite transmission mechanism converts the bidirectional swing of the lever into the one-way rotation of the generator, and the mechanical efficiency reaches 92%; (3) the hydraulic-PID dynamic balance system adjusts the balance weight in real time, and 85% torque fluctuation is restrained; and 4) the modular design supports infinite extension of the unit and linear increase of the generated power. Compared with the prior art, the single-machine efficiency of the device is improved by three times, the device can be expanded to the megawatt scale through multi-unit cooperation, high rigidity and operation stability are achieved, the technical bottleneck that rigidity, efficiency and expansibility are difficult to cooperate in the lever power generation field is broken through, and the device is suitable for large-scale power generation scenes such as wind power and tidal energy needing large-scale mechanical transmission.

Description

Technical Field

[0002] The present invention relates to the technical field of new energy power generation, and specifically to a power generation device that combines the lever principle with a dynamic balance system. It realizes efficient energy conversion by driving the main shaft of the generator through the reciprocating swing of a counterweight lever and is applicable to large-scale power generation scenarios. Background Art

[0004] Traditional power generation devices usually rely on fuel combustion or natural energy sources (such as wind energy, water energy) to drive generators, and there are problems such as strong energy dependence, low efficiency, or environmental limitations. Traditional lever-type power generation devices have problems such as low energy conversion efficiency, limited swing amplitude, and discontinuous torque transmission. The short lever-type structure adopted has defects such as limited swing amplitude, small output torque, and large mechanical vibration. In the prior art, patent application CN202211196241.9 improves the traction force through a labor-saving lever and a pulley system, but does not solve the problem of insufficient rigidity of the long lever; patent application CN202210477405.9 uses a one-way gear and a speed increaser to achieve torque transmission. Traditional lever-type power generation devices generally have the following defects:

[0005] · Insufficient structural rigidity: Long levers (>20 meters) are prone to flexural deformation during swinging, resulting in energy loss;

[0006] · Low energy conversion efficiency: It is difficult to efficiently convert the swinging kinetic energy into unidirectional rotational power;

[0007] · Lack of dynamic balance: There is a lack of a real-time torque compensation mechanism, and the system operation stability is poor;

[0008] · Insufficient scalability: The power generation of a single unit is limited, and it is difficult to control multiple units in coordination. In the prior art, patent application CN202211060878.5 proposed a pendulum rod-type power generation device, but its lever length is less than 15 meters and it relies on hydraulic drive, and the energy conversion efficiency is less than 30%. The present invention breaks through the technical bottleneck through the following innovations.

[0009] · Ultra-long truss lever (L 1 = 20 - 200 meters): Adopting a space truss structure, the flexural rigidity is increased to 5 - 8 times that of a traditional solid rod.

[0010] · Gear-one-way bearing composite drive: The mechanical conversion efficiency from bidirectional swing to unidirectional rotation reaches 92%.

[0011] · Real-time adjustment of dynamic counterweight: Combining hydraulic and PID control, the torque fluctuation suppression rate > 85%;

[0012] · Modular multi-unit coordination: Supports infinite expansion, and the total power generation is linearly related to the number of units.

[0013] · However, it lacks a multi-unit collaborative control mechanism.

[0014] Through the dynamic balance system, the cooperation of multi-phase lever groups, and the rigid reinforcement structure, the present invention comprehensively optimizes the power generation efficiency and stability. Summary of the Invention

[0016] 1. Core Structure

[0017] 1.1 Lever Mechanism Assembly

[0018] · Truss-type lever active end (17): The length L1 = 20 - 200 meters. Moving pulleys (8, 13) are installed on both sides of the end, and swing drive is achieved through traction ropes (7, 14).

[0019] · Structure: Regular triangular space truss, the chord members are Φ200×10mm Q345B steel pipes, the web members are Φ80×6mm, and the joints are connected by HS10.9 grade high-strength bolts.

[0020] · Length grading design (example): <![CDATA[L 1 (m)]]> Cross-sectional height (m) <![CDATA[Flexural rigidity EI (GN·m 2 )]]> Self-weight (t) 50 3.2 2.5 120 100 5.0 12.8 380 200 8.5 58.6 1500

[0021] · The mounting seats of the end moving pulleys (8, 13) are made of ZG270 - 500 cast steel, and the pin shafts are surface-hardened with chromium (thickness 50μm).

[0022] · Counterweight passive end (4): Symmetrically arranged at the lower end of the fulcrum shaft (40), satisfying the static balance equation: m counterweight · g · L counterweight centroid = m long rod · g · L long rod centroid m counterweight · g · L counterweight centroid = m long rod · g · L long rod centroid to ensure that the lever can hover at any position in the vertical plane.

[0023] The counterweight blocks (4) are of a layered combined structure, with a single-layer mass m = 10 tons (material: cast iron HT250), and the number of layers is adjusted by a hydraulic jacking mechanism (adjustment accuracy ±0.5 tons).

[0024] · Driving gear sets (32, 42): The pitch circle radius r = L2 (length of the passive end), converting the swing into a one-way rotation through one-way bearings (31, 43), and the module m of the driving gears (32, 42) = 20 - 50 (corresponding to L 1 grading), the tooth surfaces are carburized and quenched (hardness 58 - 62 HRC), and the pitch circle radius R = L 2 (length of the counterweight end).

[0025] · The forward driving gear (32) and the reverse driving gear (42) are respectively fixed on both sides of the fulcrum shaft (40) through keyways (H7 / k6 fit).

[0025] · The one-way bearings (31, 43) are of the CSK35-PP model, with a load-bearing capacity of 300 kN·m and a reverse free rotation angle < 0.1°.

[0027] · Gear meshing parameters (taking the module m = 20 as an example): Parameter Forward gear (32) Reverse gear (37) Driven gear (42) Number of teeth Z 60 60 30 Pressure angle α 20° 20° 20° |Helix angle β 15° right-handed 15° left-handed 15° right-handed

[0028] 1.2 Power input system

[0029] Traction force multiplication mechanism: The motor (3, 20) drives the speed reducer (2, 21) to drive the winch (1, 22), and the traction force is amplified through the fixed pulley (5, 16) and the movable pulley (8, 13), satisfying:

[0030] Assume a set of parameters:

[0031] Motor power P = 10 kW, speed n = 1500 rpm Reduction ratio i = 10, efficiency η = 90%, winch radius r = 0.1 m, number of rope segments of the pulley block n = 4,

[0032] Efficiency η = 85%

[0033] Substituting into the formula gives: F = 5733 x 4 x 0.85 ≈ 19,492 N

[0034] 1.3 Energy conversion system

[0035] · Dual-path transmission design:

[0036] · First path: The forward driving gear (42) of the fulcrum shaft (40) drives the driven shaft (50), and is transmitted to the power output shaft (53) through the belt sprockets (39, 56);

[0037] · Second path: The reverse driving gear (32) reverses the torque direction through the intermediate shaft (70) and the third shaft (57), and finally converges into the power output shaft (53);

[0038] · Speed increasing mechanism (25): Adopts a three-stage planetary gear (total speed increasing ratio i = 200 - 500:1) to increase the speed to 1500 rpm required by the generator (23).

[0039] 1.4 Dynamic balance system (Figure 4) Static balance condition: m 1 · g · L 1 = m 2 · g · R In the formula: · m 1 Equivalent mass at the driving end (including the self-weight of the structure and additional loads); · m 2Total mass of the counterweight

[0040] Dynamic adjustment mechanism

[0041] · Counterweight hydraulic adjustment system: Consists of a servo cylinder (stroke ±1.5 m), a proportional valve (response time <10 ms), and a pressure sensor (accuracy 0.1% FS);

[0042] · Control algorithm: Based on a hybrid strategy of PID and fuzzy control, it collects the torque signal of the fulcrum shaft in real time (sampling frequency 1 kHz) and outputs the counterweight displacement command Δx: where e(t) is the deviation between the set torque and the actual torque.

[0043] 1.5 Cooperative control of multi-phase lever groups

[0044] · Phase difference optimization: The phase difference θ between adjacent levers is θ = 360° / N (N is the number of levers). When N≥4 and θ≤90°, the output voltage fluctuation rate ΔV <5%.

[0045] · Speed smoothing mechanism: The angular velocity fluctuation rate after multi-unit superposition satisfies: Δω∝1NΔω∝N significantly improves the smoothness of the current sine curve.

[0046] 1.6 Rigidity strengthening system

[0047] · Cable-stayed cable system (73 - 80): Adopts 304 stainless steel cables (diameter ≥20 mm), pre-tightened in a triangular truss layout (pre-tightening force ≥10 kN), so that the deflection of the lever end is ≤L1 / 1000, and the bending stiffness is increased by 70%.

[0048] 2. Fulcrum shaft assembly:

[0049] 2.1. The fulcrum shaft (31) is forged from 42CrMo alloy steel, surface nitrided (hardness ≥60 HRC), with a diameter D = 200 - 800 mm (designed according to the L 1 length classification);

[0050] 2.2. The bearing adopts a double-row tapered roller bearing (model 3520XX, clearance 0.05 - 0.15 mm), with an internal temperature sensor (PT100) and a vibration monitoring module (sampling rate 10 kHz);

[0051] 2.3. The fulcrum seat (35) is a welded box structure, fixed to the concrete foundation through M64 anchor bolts (pre-tightening force 500 kN) at the bottom.

[0052] 3. Torque synthesis and speed-up transmission:

[0053] Single unit torque output: T 单组 = F eff · L 1 · sinθ · η 传动 where α is the lever swing angle (±30°), η 传动 = 92%

[0054] Multi-unit parallel connection ( Figure 3 ):

[0055] · The power output shaft (53) is connected to N groups of devices through drum tooth couplings (26, 71), and the total torque: T_total = NT_single group

[0055] The speed increasing mechanism (25) adopts a three-stage planetary gear, and the total speed ratio i = 300. The output speed:

[0056] Meets the synchronous speed requirement of the generator (23).

[0057] 4. Key innovation points

[0058] · Ultra-long truss lever anti-bending design:

[0059] Adopt variable cross-section space truss and double-sided stay cables to forcibly resist bending. The section moment of inertia I increases exponentially with L 1 increase:

[0060] where x is the distance from the fulcrum, ensuring that the maximum deflection δ_max < L 1 / 1500.

[0061] · Phase difference multi-unit coordination:

[0062] N groups of levers are arranged according to the swing angle phase difference (such as when there are 4 groups ), the total output torque volatility is reduced from ±35% of a single group to ±(35 / N)%.

[0063] · Install single-direction bearings (31, 43) in the forward and reverse reversing gears. Through gears (32, 42), the first-stage belt chain mechanism (39, 52, 56), the second-stage belt connection mechanism (62, 63, 64) and the coupling clutch (41, 60), the moment of the forward and reverse swing of the lever active end is converted into a single-direction positive torque and transmitted to the output shaft (52).

[0064] Composite material application:

[0065] The traction rope of the movable pulley adopts an ultra-high modulus polyethylene (UHMWPE)-steel wire composite cable (breaking strength ≥ 2500 MPa), reducing the weight by 40% compared with the traditional steel wire rope.

[0066] 2. Specific implementation of the technical solution

[0067] Example 1:

[0068] 50-meter single-unit power station

[0069] Parameter configuration:

[0070] Operation process:

[0071] Startup phase: The winch is driven synchronously by two motors, and the traction rope pulls the end of the lever at v = 0.2 m / s to achieve full swing of ±30° within 5 minutes;

[0072] Steady-state power generation: The output speed of the fulcrum shaft is n = 18 rpm, and after speed increase, it drives the generator to generate electricity at 1500 rpm;

[0073] Example 2:

[0074] 200-meter multi-unit power plant Parameter configuration:

[0075] Meet the grid connection standard IEEE 1547 series standards· Brief description of the drawings Figure 1 : of the overall structure 3 views; Figure 2 : Front view in the three views; Figure 3 : Side view in the three views; Figure 4 : Top view in the three views; Figure 5 : Figure 4 Enlarged view at B of; Figure 6 : Figure 4 Sectional view at A-A of; Figure 7 : Position diagram when the truss-type lever swings with the counterweight to the left extreme; Figure 8 : Position diagram when the truss-type lever swings with the counterweight to the right extreme; Figure 9 : Static balance diagram of the truss-type lever swinging with the counterweight on the fulcrum shaft; Figure 10 : Phase difference diagram of multiple levers swinging simultaneously; Δt i = Imsin(ωt + θ) In the figure: ω: Angular frequency (radian / second) Im: Current amplitude Initial phase angle Δt: Phase difference overlap density of multiple rods Explanation of drawing symbols: The first unit's single-group power generation device; II The second unit's single-group power generation device; III The first unit's single-group power generation device; IV The second unit's single-group power generation device; 1. Winch for winding ropes on the left side; 2. Reducer for winding ropes on the left side; 3. Motor for winding ropes on the left side; 4. Counterweight; 5. Fixed pulley for left-side support; 6. Fixing device for the left-side towing rope; 7. Left-side towing rope; 8. Movable pulley at the active end of the left-side lever; 9. Positioning shaft for the movable pulley at the active end of the left-side lever; 10. Positioning plate for the movable pulley at the active end of the lever; 11. Positioning shaft for the positioning plate of the movable pulley at the active end of the lever; 12. Positioning shaft for the movable pulley on the left side of the active end of the right-side lever; 13. Movable pulley at the active end of the right-side lever; 14. Right-side towing rope; 15. Fixing device for the right-side towing rope; 16. Fixed pulley for right-side support; 17. Active end of the truss-type lever; 18. Right-side support and fixing frame of the generator device; 19. Main power gear transmission and reversing mechanism; 20. Motor for winding ropes on the right side; 21. Reducer for winding ropes on the right side; 22. Winch for winding ropes on the right side; 23. Generator; 24. Generator coupling; 25. Speed-up box; 26. Coupling between the power system and the power generation system; 27. Positioning bearing for the counterweight support shaft of the lever; 28. Connecting key for the intermediate gear; 29. Intermediate gear; 30. Right-side driving gear; 31. One-way bearing for the right-side driving gear; 32. Right-side driving gear; 33. Shaft support plate; 34. Bearing; 35. Connecting key; 36. Passive shaft support; 37. Bearing; 38. Connecting key for the belt sprocket; 39. Left-side belt sprocket; 40. Fulcrum shaft of the truss-type lever; 41. Passive shaft coupling; 42. Left-side driving gear; 43. One-way bearing for the left-side driving gear; 44. Left-side support and fixing frame of the generator device; 45. Connecting key for the one-way bearing; 46. Positioning support bearing for the counterweight fulcrum shaft of the lever; 47. Driven gear; 48. Connecting key for the driven gear; 49. Support bearing for the passive shaft; 50. Passive shaft; 51. Passive output shaft; 52. Left-side transmission belt chain; 53. First-stage power output shaft; 54. Positioning bearing for supporting the power output shaft; 55. Connecting key for the left-side transmission sprocket; 56. Left-side transmission sprocket of the first-stage power output shaft; 57. Third shaft; 58. First-stage power output shaft; 59. Connecting key; 60. Right-side coupling; 61. Connecting key for the belt sprocket; 62. Right-side belt sprocket; 63. Right-side transmission belt chain; 64. Right-side transmission sprocket of the first-stage power output shaft; 65. Bearing; 66. Bearing; 67. Right-side support and fixing frame of the generator device; 68. Third shaft; 69. Bearing for the intermediate shaft; 70. Intermediate shaft; 71. Power output shaft of the first unit's single-group power generation device; 72. Power receiving shaft of the second unit's single-group power generation device.

Claims

1. A power generation device based on the lever principle: a device in which a counterweight lever swings back and forth to drive the main shaft of a generator to generate electricity, characterized in that include: -- A lever mechanism and a fulcrum shaft assembly, comprising a rotatably supported cylindrical swinging lattice-type lever fulcrum shaft (40), a lattice-type lever active end (17) (length L1>20-200 meters), a lever passive end (4) with a counterweight, and a driving gear (32, 42) rigidly connected to the fulcrum shaft (the radius of the driving gear pitch circle r=L2 is equal to the length of the lever passive end), wherein the length of the lattice-type lever active end (17) is equal to the length of the end movable pulley (8, 13) The length L1 from the center of the lever to the center of the fulcrum shaft (40), the length of the passive end lever is equal to the pitch circle radius of the driving gears (32, 42) mounted on the fulcrum shaft (40) and rigidly connected by a one-way bearing, the active end (17) of the lattice-type lever is rigidly connected to the fulcrum shaft (40) and vertically upward, the movable pulley assembly that pulls it to swing is vertically away from the fulcrum shaft (40), and the passive end (4) of the lever with a counterweight is at the lower end of the fulcrum shaft (40), and the layout is symmetrical; --A dynamic balancing system, comprising a passive end of a lever (4) provided with a counterweight, maintaining dynamic balance with the gravity moment of an active end of a lattice-type lever (17); under the support of a fulcrum shaft (40), the center of mass of the active end of the lever is balanced with the center of mass of the counterweight at the passive end of the lever, and can be suspended at any position on a vertical plane, conforming to the balance equation: m 配重 ·g·L 配重质心 =m 长杆 ·g·L 长杆质心 -- A power input system, comprising movable pulleys (8, 13) symmetrically arranged on both sides of the end of the active end (17) of the lattice-type lever, fixed pulleys (5, 16) mounted on a fixed frame, a capstan (1, 22) connected to the output shaft of the reducer, a reducer (2, 21), a driving motor (3, 20) at the input end of the reducer, and a traction rope (7, 14) wound around the capstan and passing through the fixed pulleys (5, 15), passing around the movable pulleys (8, 13) at the end of the lattice-type lever, and finally tied to the fixed frame. Taking one side as an example, the motor (3) is energized to drive the large speed ratio reducer (2) to rotate, and the speed of the motor (3) is reduced to meet the requirements of the swing frequency of the lever and increase the traction force, satisfying the formula T = 9.55N\cdotpm×i. The movable pulley (8) used at the end of the lattice-type lever doubles the traction force, satisfying the formula N 动滑轮 =F 杠杆摆动力 / 2; --Energy conversion system, a single energy conversion system is divided into a lever mounted on a fulcrum shaft (40), a counterweight, and a forward and reverse rotating active gear (32, 42) mounted with a one-way bearing, these components convert the swing kinetic energy of the lever into the forward and reverse rotation kinetic energy of the fulcrum shaft (40) around the support shaft positioning bearing (27, 46), the first group of transmission mechanisms cooperates with the passive shaft (50) and the passive gear (47) mounted on the passive shaft, the passive shaft coupling clutch (41), the passive shaft transmission belt sprocket (39), and the power output belt sprocket (56) to transmit the kinetic energy to the first unit single lever swing device power output shaft (53) through the transmission belt chain (52), the second group of transmission mechanisms is the torque of the fulcrum shaft (40) through the active gear The transition gear (29) installed on the transition shaft (70) meshed with the wheel (32) further meshes with the gear (59) installed on the third shaft (57) to transmit the reverse rotating torque to the power output shaft (53) through the coupling (60), belt sprocket (62), transmission belt chain (63), and belt sprocket (64) on the third shaft, and then transmits the transmitted torque to the input shaft of the speed-up mechanism (25) through the power output shaft coupling (26) connected to the power output shaft (53). After the speed is increased, the torque is used to drive the generator (23) to generate electricity. The torques of the single-group power generation devices of the second unit, the third unit, the fourth unit, etc. are respectively gathered into the same torque through their respective couplings (70) and transmitted to the generator (23) for power generation; --Multiple single lever swing devices I, II, III, IV, etc. respectively convert the reciprocating swing of the lever into continuous uniform rotation in the same direction. The power output shaft (53) is connected to the multiple single lever swing devices via the clutch (26, 71), and finally the power is transmitted to the generator (23) through the speed-up device for power generation. The number of single lever swing devices connected determines the user's demand for the total power and power generation quality. The more connected, the greater the power generation, and the smaller the phase difference angle θ of the swing of adjacent lattice-type levers (17). Since the angular velocity ω changes periodically with time, in the undamped simple harmonic oscillation, the angular velocity is at the equilibrium position (highest point) when it is the largest, and the direction changes alternately. The more the lattice-type levers (17) are, the smaller the phase angle θ set artificially between the rods, the smaller the speed change within the swing period α, the more stable the voltage emitted, and the smoother the current sine curve. --The lattice-type lever rigid lifting system, according to different uses, makes the lever exert the maximum force. Usually the length of the lever is designed to be very long (L≥20-200 meters), which will make the lever rigid insufficient. For this reason, a cable-stayed steel rope tensioning system (73, 74, 75, 76, 77, 78, 79, 80) is added to improve the rigidity of the lever.

2. The power generation device according to claim 1, characterized in that: The torque transmission mechanism comprises a fulcrum shaft (40), an active lattice-type lever (17), a passive end counterweight (4), a positive driving gear (42) symmetrically embedded with positive one-way bearings (43) on both sides of the lever, and a reverse driving gear (32) embedded with reverse one-way bearings (31), wherein the rotation direction of the one-way bearings and the rotation direction of the fulcrum shaft (40) form a positive and reverse layout, that is, when the active gear (42) rotates in the reverse direction, the passive gear (47) rotates in the forward direction, and the torque of the fulcrum shaft (40) is directly transmitted to the passive output shaft (51) through the coupling (41) through the connecting keys (45, 48), and the coupling (41) has the function of automatic connection and separation. At this time, the clutch (41) is closed, and the torque is transmitted to the power output shaft (53) through the belt sprocket (39), the transmission belt chain (52), and the belt sprocket (56) on the output shaft (51). At this time, the one-way bearing (31) in the other active gear (32) does not rotate and does not transmit torque; --When the lattice lever (17) swings forward around the lever fulcrum axis (40), the movable gear (32) rotates forward, driving the transition gear (29) on the transition shaft (70) to rotate in the opposite direction, and the meshing transmission gear (59) installed on the third shaft (57) rotates forward. When the clutch (60) is closed, the torque is transmitted to the other side shaft (68) of the third shaft, driving the conveyor sprocket (62) to be transmitted to the sprocket (64) via the conveyor chain (63), and the positive torque is transmitted to the output shaft (53) to rotate, so that the output shaft (53) rotates; --When the driving gear (42) meshes with the driven gear (47) and the related clutch (41), the sprocket (39, 56) and the conveyor belt chain (52) to transmit torque to rotate the power output shaft (53), the sprocket (64) will also be forced to rotate in the reverse direction, and the conveyor belt chain (63) connected thereto will drive the conveyor belt sprocket (62) to rotate together. At this time, the clutch (60) is in a disengaged state, so that the torque will not be transmitted in the reverse direction to the third shaft (57) or even affect the movement of the fulcrum shaft (40) through a series of transmissions. On the contrary, when the sprocket (64) outputs torque, the sprocket (56, 39) and the conveyor belt chain (52) will also rotate. However, the clutch (41) is in an open state, and the power will not be transmitted back in the reverse direction. The two clutches (41) and the clutch (60) are alternately opened and closed during operation; --The transmission mechanism is divided into several groups according to the power generation demand of the system, and each group transmits its own torque to the power output shaft (53). In this way, the more groups there are, the greater the torque transmitted to the generator (23) through the speed increase box (25). --The force applied by the end point of the active end (17) of the lattice-type lever and the force generated on the pitch circle of the active gear (32, 42) conform to the lever law: F1×L1=F2×L2 Where: F1=2N 主动 is the external force applied to the top of the grid-type lever; L1 is the distance from the active end point to the fulcrum axis O; F2 is the force on the tooth profile on the pitch circle of the driving gear; L2 is the distance from the gear pitch circle to the fulcrum axis O; N=1 / 2F1 N is the external force applied to the grid lever through the movable pulley.

3. The power generation device according to claim 1, characterized in that: The adjustable counterweight (4) and the active end (17) of the lattice-type lever are rigidly fixed on the fulcrum shaft (40) and maintain static balance. The balance condition satisfies: W 配重 ·L 配重 =W 杠杆 ·L 杠杆 Bring in m 配重 g 配重 =m 杠杆 g 杠杆 The swing angle of the active lattice lever (17) around the fulcrum axis (40) is exactly the same as the swing angle of the adjustable counterweight (4), but in the opposite direction. The lattice lever (4) and the counterweight (4) have a considerable weight, and therefore the kinetic energy of the swing on the fulcrum shaft (40) is relatively large: It can also be expressed as Where I is the moment of inertia of the rigid body relative to a certain axis, m i =W For a lattice lever with multiple mass systems, the moment of inertia can also be expressed by summing: I=∫ρR 2 dV=∫R 2 dm Where: ρ is the density, R is the distance from the particle to the axis of rotation; When the active end (17) of the lattice-type lever and the counterweight (4) reciprocate around the fulcrum axis at an angle α to the turning point, the impact on the system is the greatest. The dynamic characteristics and formula of the turning point conform to the relationship between kinetic energy and angular velocity. Turning point characteristics: when the swing reaches the maximum angle, the angular velocity ω=0, and the kinetic energy E k =0, all converted into gravitational potential energy.

4. The power generation device according to claim 1, characterized in that: A driving gear (32) and a driving gear (42) are respectively mounted and fixed on both sides of the active end (17) of the lattice-type lever fixed on the fulcrum shaft (40). The two gears rotate in a positive and negative direction alternately under the support of the one-way bearing (31) and the one-way bearing (43). That is, when one rotates forward, the other does not rotate. After the reversal, when one rotates reversely, the other does not rotate. In this way, the active end (17) of the lattice-type lever will transmit the generated strong torque to the power output shaft (53) through the driving gears (32, 42) and other transmission components regardless of whether it swings forward or reverse.

5. The power generation device according to claim 1, characterized in that: In order to reduce the weight, the active end (17) of each single group of levers is designed as a lattice structure and light materials are selected. In addition, inclined cables (73, 74, 75, 76, 77, 78, 79, 80) are specially added on both sides of the lever. The strength and rigidity are enhanced by tightening the steel cables. The lever is used in an upright position. In this way, when the lever swings at a constant speed around the fulcrum axis (30), the weight of the active end of the lever, the counterweight, the inclined cable system and its auxiliary parts all fall on the fulcrum axis (40). In addition, with the balancing effect of the counterweight block (4), the lever plus the counterweight can be suspended at any position in the vertical plane and maintain a static equilibrium state. When swinging, during the entire swinging process, especially at the turning point, the linear momentum, angular momentum, kinetic energy, momentum and angular velocity all change periodically with time, which is determined by the moment of inertia, external force and counterweight setting. The reasonable design of the counterweight optimizes the dynamic response of the system and reduces vibration. Its mathematical expression is: -Linear momentum: Linear momentum of the active end point p = m1v, where velocity v = L1ω, Therefore ρ=m1L1ω Since the magnitude and direction of ω change periodically during the swing process, the momentum also changes accordingly. The system achieves static balance (m1L1=m2L2) through the counterweight, and the system bus momentum is zero because the momentum at both ends is opposite in direction and equal in magnitude. - Angular velocity changes: When the system swings, the angular velocity ω changes periodically with time. In undamped simple harmonic oscillation, the angular velocity is at its maximum at the equilibrium position (highest point) and is zero at its lowest point, with alternating directions. Its motion follows the laws of a physical pendulum and is affected by the moment of inertia and restoring torque. -Calculation formula Moment of Inertia: Equations of motion: The total torque includes the external torque and gravity torque: Angular velocity and angular acceleration: -Equilibrium condition When m1L1=m2L2, the gravity moments cancel each other out and the system is in static equilibrium. At this time, the equation of motion is: Angular acceleration is directly determined by the external torque and the moment of inertia. Momentum and angular velocity change periodically over time, which is determined by the moment of inertia, external force and counterweight setting. Reasonable design of counterweight optimizes the dynamic response of the system and reduces vibration.

6. The power generation device according to claim 1, characterized in that: The reciprocating swing of the active end (17) of the lever in a single group is realized by the movable pulleys (8, 13), traction ropes (7, 14), fixed pulleys (5, 16), rope fixed ends (6, 16), winches (1, 22), reducers (2, 21), and motors (3, 20) at both ends of the lever. When the motor on one side is working, the other side is in a free state, and the active end (17) of the lever is pulled toward the side of the working motor. Conversely, the active end (17) of the lever is pulled toward the other side. During this process, the high-speed torque of the motor is rapidly increased after being decelerated by the large-reduction-ratio reducer. In addition, the small-diameter winch and movable pulley have the characteristic of halving the traction force, so that the lever system can be swung with only a very small-power motor, and a force amplified by (20-200) times is generated at the passive end of the lever. The pulling force generated by the traction rope (7, 14) after passing through the motor (3, 20), reducer (2, 21), and winch (1, 22) system meets the pulling force formula: Tmotor: motor torque (unit: N·m) i: reduction ratio η: Mechanical efficiency r: Winch radius (unit: m) F: Final output pulling force (unit: N).

7. The power generation device according to claim 1, characterized in that: The gear set of the speed increaser (25) comprises a three-stage planetary gear speed increase mechanism, and the speed increase ratio i satisfies: Among them, Z2 and Z3 are the number of teeth on the first-stage sun gear and ring gear, Z5 and Z6 are the number of teeth on the second stage, and Z8 and Z9 are the number of teeth on the third stage.

8. The power generation device according to claim 1, characterized in that: The movable pulley (9, 13) is provided with an anti-slip groove structure, the diameter D of the movable pulley and the diameter d of the traction rope (7, 14) satisfy D≥20d, and a polyurethane friction layer is provided on the surface of the pulley.

9. The power generation device according to claim 1, characterized in that: The fulcrum shaft (40) is supported by double-row tapered roller bearings (27, 46); the bearing seat is provided with a lubricating oil channel and a temperature sensor; and the bearing preload can be adjusted within a range of 0.05-0.15 mm.

10. The power generation device according to claim 1, characterized in that: The length ratio of the lattice-type long rod section (17) and the short rod section-driving gear (32, 42) (1 / 2 driving gear radius) is L1 / L2 (driving gear radius) ≥ (20 meters-200 meters): 1 = (20 meters-200 meters). The long rod section adopts a lattice-type steel structure (17), a counterweight adjustment block (4) is provided at the end thereof, and a piezoelectric power generation film layer is laid on the entire rod body surface.

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