Vibration power generation device and method based on spring oscillator

Abstract

The application provides a vibration power generation device and method based on spring oscillators, which comprises a base, a guide mechanism, an inner spring oscillator system and an outer spring oscillator system. By setting the inner and outer double spring oscillator systems with different stiffness, the vibration energy of different frequencies can be efficiently absorbed and amplified, effectively solving the problem of narrow working frequency band of the traditional single spring oscillator system. Moreover, through the phase difference and amplitude superposition effect of the inner and outer oscillator vibrations, the small environmental vibration amplitude can be significantly amplified, thereby directly solving the bottleneck of the traditional electromagnetic power generation device, i.e. difficulty in driving and low output power under millimeter-level small amplitude vibration, so that the device can directly provide sufficient electric energy for the magneto-rheological damper and its sensor, and ultimately fundamentally solves the key problem of the magneto-rheological damping system, i.e. dependence on external power supply, complex wiring and limited application in high-speed trains and the like.

Description

Technical Field

[0001] This invention relates to the field of electromagnetic induction power generation technology, and specifically to a vibration power generation device and method based on a spring oscillator. Background Technology

[0002] As the operating speed of high-speed trucks continues to increase, their suspension systems face more complex and severe wheel-rail excitation, placing higher demands on vibration reduction performance. Magnetorheological dampers, due to their wide damping force adjustment range, fast response speed, and ease of intelligent control, have become an ideal choice for improving the performance of high-speed truck suspension systems. However, magnetorheological dampers and their control systems require a continuous and stable external power supply, which constitutes a significant limitation in practical applications. To solve this key problem, developing efficient and reliable self-powered technology by leveraging the abundant vibration energy generated during truck operation has become an important approach to promoting the large-scale application of magnetorheological damping systems on high-speed trucks.

[0003] Currently, vibration energy harvesting solutions for small devices mainly include piezoelectric and electromagnetic types. While piezoelectric devices are compact, their power output is typically only in the milliwatt range, insufficient to meet the power requirements of magnetorheological systems. Electromagnetic devices, although possessing greater power potential, often rely on large vibration amplitudes for efficient operation. However, the typical vibration amplitude at the installation location of a truck shock absorber is only a few millimeters, making it impossible to directly and effectively drive traditional electromagnetic power generation structures. Overall, existing technologies generally suffer from insufficient power output, high costs due to complex structures, and high efficiency only near narrow-band natural frequencies.

[0004] Therefore, there is an urgent need for a vibration power generation device and method based on a spring oscillator to solve the above-mentioned technical problems. Summary of the Invention

[0005] In view of the problems existing in the prior art, one of the objectives of the present invention is: In a first aspect, the present invention provides a vibration power generation device based on a spring oscillator, comprising: Base; A guiding mechanism, comprising an axially arranged guide tube, the bottom of which is fixed to the base, and an end cap provided on the top of which; An internal spring oscillator system, comprising a permanent magnet and a first spring, wherein one end of the first spring is fixedly connected to the end cap and the other end of the first spring is connected to the permanent magnet, and the permanent magnet is slidably disposed within the guide tube; An external spring oscillator system includes an induction coil, a coil support, and a second spring. The induction coil is sleeved on the outside of the guide tube. The coil support is used to fix the induction coil. One end of the second spring is fixedly connected to the base, and the other end of the second spring is connected to the coil support. The stiffness coefficient of the first spring is smaller than that of the second spring; When subjected to external vibration, the first spring and the second spring vibrate with different phases and amplitudes, and the permanent magnet and the induction coil generate an axial relative motion greater than the input amplitude of the external vibration, so that the permanent magnet generates a magnetic flux that passes through the induction coil, and an induced electromotive force is generated in the induction coil.

[0006] In one embodiment, the coil support includes an upper support and a lower support, which are respectively fixed at both ends of the axial direction of the induction coil. The lower support is connected to the second spring. The upper support and the lower support are provided with guide grooves on the side near the guide tube. The outer wall of the guide tube is provided with guide ribs arranged along the axial direction of the induction coil. The guide grooves and the guide ribs are slidably connected to restrict the axial movement of the induction coil.

[0007] In one embodiment, the system further includes an outer shell, which is fixedly connected to the base. The outer shell and the base enclose a cavity, and the guide mechanism, the inner spring oscillator system, and the outer spring oscillator system are located within the cavity.

[0008] In one embodiment, the device further includes an installation mechanism, the installation mechanism comprising: A connecting base, one side of which is fixedly connected to the base; Mounting components, which are used to connect to the vehicle body structure; The connecting base and the mounting component are detachably connected, and the clamping or fitting surface of the mounting component can be adapted to the surface shape of the vehicle body structure.

[0009] In one embodiment, a limiting mechanism is further included, which is disposed inside the guide tube and located at one end of the guide tube near the base. The limiting mechanism is used to absorb impact and prevent the permanent magnet from colliding with the base.

[0010] In one embodiment, a fixing mechanism is further included, which includes a fixing ring and a fixing post. The bottom of the fixing post is fixedly connected to the base, and the top of the fixing post is connected to the fixing ring. The fixing ring is located above the coil support and is sleeved on the guide tube.

[0011] In one embodiment, the fixing post is located on the side of the coil support away from the guide tube, and the fixing post is used to limit the relative position of the coil support along the radial direction of the guide tube.

[0012] In one embodiment, the system further includes a power management module disposed on the base and electrically connected to the induction coil. The power management module is used to process the electrical energy generated by the induction coil, and the output terminal of the power management module is provided with a standard power interface.

[0013] In one embodiment, the stiffness coefficient of the first spring is in the range of 300 N / m to 600 N / m, and the stiffness coefficient of the second spring is in the range of 3000 N / m to 7000 N / m.

[0014] Secondly, the present invention also provides a vibration power generation method based on a spring oscillator, employing the aforementioned vibration power generation device based on a spring oscillator, comprising the following steps: External vibrations are received by the inner spring oscillator system and the outer spring oscillator system, respectively. By using the different stiffness parameters of the first spring and the second spring, the inner spring oscillator system and the outer spring oscillator system vibrate with different natural frequencies and phases; The permanent magnet and the induction coil vibrate under the action of their respective spring oscillator systems. The phase difference and amplitude superposition effect between the two vibrations of the permanent magnet and the induction coil are used to amplify the relative motion amplitude between the permanent magnet and the induction coil. The amplified relative motion between the permanent magnet and the induction coil changes the magnetic flux passing through the induction coil, thereby generating an induced electromotive force and realizing the conversion of vibrational mechanical energy into electrical energy.

[0015] Compared with the prior art, the advantages of the present invention are that the embodiments of this application provide a vibration power generation device and method based on a spring oscillator. The vibration power generation device based on a spring oscillator includes a base, a guide mechanism, an inner spring oscillator system and an outer spring oscillator system. By setting inner and outer double spring oscillator systems with different stiffnesses, the efficient absorption and amplification of vibration energy at different frequencies can be achieved, effectively solving the problem of narrow operating frequency band of traditional single spring oscillator systems. Furthermore, through the phase difference and amplitude superposition effect of the vibration of the inner and outer oscillators, the amplitude of small environmental vibrations is significantly amplified, thereby directly solving the bottleneck of traditional electromagnetic power generation devices being difficult to drive and having low output power under millimeter-level small-amplitude vibrations. This allows the device to directly provide sufficient power to magnetorheological vibration dampers and their sensors, ultimately fundamentally solving the key problems of magnetorheological vibration damping systems relying on external power supply, complex wiring, and limited application in high-speed trains and other applications. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the structure of a vibration power generation device based on a spring oscillator, provided for some embodiments of this application.

[0017] Figure 2 This application provides an induced current meter for a spring-oscillator-based vibration power generation device under different amplitudes in some embodiments.

[0018] Figure 3 The induced voltage and induced current of the permanent magnet vibration-type power generation device provided in some embodiments of this application.

[0019] Figure 4 The induced voltage and induced current of the induction coil vibration type power generation device provided in some embodiments of this application.

[0020] Figure 5 The induced voltage and induced current of the dual-spring oscillator resonant power generation device provided in some embodiments of this application.

[0021] Figure label: 1. End cap; 2. Guide tube; 3. First spring; 4. Permanent magnet; 5. Upper bracket; 6. Induction coil; 7. Lower bracket; 8. Second spring; 9. Base. Detailed Implementation

[0022] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are 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 this application. However, this application can be implemented 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 this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0023] In the description of this application, it should be understood that if terms such as "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" appear, these terms indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0024] Furthermore, where the terms "first" and "second" appear, these terms are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, where the term "multiple" appears, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0025] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or a joint; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0026] In this application, unless otherwise expressly specified and limited, the use of descriptions such as "above" or "below" the second feature indicates that the first and second features are in direct contact or indirect contact via an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. Similarly, "below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0027] It should be noted that if an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. If an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. If so, the terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this application are for illustrative purposes only and do not represent the only possible implementation.

[0028] The invention will now be further described with reference to the accompanying drawings.

[0029] Firstly, see Figure 1 This application provides an embodiment of a spring-based vibration power generation device, which includes a base 9, a guide mechanism, an inner spring oscillator system, and an outer spring oscillator system. The guide mechanism includes an axially arranged guide tube 2, the bottom of which is fixed to the base 9, and an end cap 1 on the top of which is provided. The inner spring oscillator system includes a permanent magnet 4 and a first spring 3. One end of the first spring 3 is fixedly connected to the end cap 1, and the other end is connected to the permanent magnet 4. The permanent magnet 4 is slidably disposed inside the guide tube 2. The outer spring oscillator system includes an induction coil 6 and a coil... A bracket and a second spring 8 are provided. The induction coil 6 is sleeved on the outside of the guide tube 2. The coil bracket is used to fix the induction coil 6. One end of the second spring 8 is fixedly connected to the base 9, and the other end of the second spring 8 is connected to the coil bracket. The stiffness coefficient of the first spring 3 is smaller than that of the second spring 8. When subjected to external vibration, the first spring 3 and the second spring 8 vibrate with different phases and amplitudes. The permanent magnet 4 and the induction coil 6 generate an axial relative motion greater than the input amplitude of the external vibration, so that the permanent magnet 4 generates a magnetic flux that passes through the induction coil 6, thereby generating an induced electromotive force in the induction coil 6.

[0030] The vibration power generation device based on spring oscillators provided in this application embodiment achieves efficient absorption and amplification of vibration energy at different frequencies by setting up an inner and outer double spring oscillator system with different stiffnesses. This effectively solves the problem of narrow operating bandwidth of traditional single spring oscillator systems. Furthermore, through the phase difference and amplitude superposition effect of the inner and outer oscillator vibrations, the amplitude of minute environmental vibrations is significantly amplified. This directly solves the bottleneck of traditional electromagnetic power generation devices, which are difficult to drive and have low output power under millimeter-level small-amplitude vibrations. This allows the device to directly provide sufficient power to magnetorheological vibration dampers and their sensors, ultimately fundamentally solving the key problems of magnetorheological vibration damping systems relying on external power supply, complex wiring, and limited application in high-speed trains and other applications.

[0031] In this embodiment, the permanent magnet 4 is an N52 neodymium magnet. The induction coil 6 in the device is an enamel-coated aluminum coil with an internal diameter of 40 mm, a thickness of 5 mm, and 2000 turns. Of course, in other embodiments, operators can use different permanent magnets 4 and induction coils 6 according to specific needs.

[0032] like Figure 1 As shown, in some embodiments, the coil support includes an upper support 5 and a lower support 7, which are respectively fixed at both ends of the axial direction of the induction coil 6. The lower support 7 is connected to the second spring 8. The upper support 5 and the lower support 7 are provided with guide grooves on the side near the guide tube 2. The outer wall of the guide tube 2 is provided with guide ribs arranged along the axial direction of the induction coil 6. The guide groove and the guide ribs are slidably connected to restrict the movement of the induction coil 6 along the axial direction.

[0033] The coil support is designed to reliably fix and elastically support the mass of the external spring oscillator system by fixing the upper support 5 and the lower support 7 to both ends of the induction coil 6, and connecting the second spring 8 through the lower support 7. Simultaneously, guide grooves are provided on the upper support 5 and the lower support 7, which slide in cooperation with the guide ribs on the outer wall of the guide tube 2. This effectively restricts the induction coil 6 to move only along a preset axial direction, preventing radial offset or rotation during vibration. This ensures that the relative motion between the permanent magnet 4 and the induction coil 6 always remains on the optimal magnetic flux change path, significantly improving the efficiency and stability of converting vibration energy into electrical energy.

[0034] like Figure 1 As shown, in some embodiments, it also includes an outer shell, which is fixedly connected to the base 9. The outer shell and the base 9 enclose a cavity, and the guide mechanism, the inner spring oscillator system and the outer spring oscillator system are located in the cavity.

[0035] By setting up an outer shell that is fixedly connected to the base 9, the outer shell and the base 9 together form a sealed cavity structure, which can completely house the guide mechanism, the inner spring oscillator system and the outer spring oscillator system within the cavity. This effectively isolates the intrusion of external dust, moisture and foreign objects, significantly improving the long-term operational reliability of the device in complex vibration environments such as high-speed trains, and providing a stable working space for the internal moving parts, thus avoiding the influence of external interference on the vibration transmission and energy conversion process.

[0036] like Figure 1 As shown, in some embodiments, an installation mechanism is also included. The installation mechanism includes a connecting base and an installation component. One side of the connecting base is fixedly connected to the base 9. The installation component is used to connect with the vehicle body structure. The connecting base and the installation component are detachably connected. The clamping surface or contact surface of the installation component can be adapted to the surface shape of the vehicle body structure.

[0037] The mounting mechanism connects the base and the mounting components in a detachable manner, allowing the clamping or contact surfaces of the mounting components to flexibly adapt to the surface shapes of different vehicle structures. This significantly improves the adaptability and ease of installation of the power generation device in narrow or irregular installation spaces such as high-speed trains. At the same time, reliable mechanical connections ensure the structural stability of the device under complex vibration conditions, providing a solid installation foundation for the efficient collection of vibration energy.

[0038] like Figure 1 As shown, in some embodiments, a limiting mechanism is also included. The limiting mechanism is disposed inside the guide tube 2 and is located at one end of the guide tube 2 near the base 9. The limiting mechanism is used to absorb impact and prevent the permanent magnet 4 from colliding with the base 9.

[0039] The limiting mechanism, located at one end of the guide tube 2 near the base 9, can effectively absorb the impact energy of the permanent magnet 4 during vibration, preventing it from rigidly colliding with the base 9. This significantly improves the reliability and service life of the device under severe vibration conditions, reduces vibration energy loss caused by collisions, and ensures the continuous and stable operation of the power generation process.

[0040] like Figure 1 As shown, in some embodiments, a fixing mechanism is also included, which includes a fixing ring and a fixing post. The bottom of the fixing post is fixedly connected to the base 9, and the top of the fixing post is connected to the fixing ring. The fixing ring is located above the coil support and is sleeved on the outside of the guide tube 2.

[0041] The fixing mechanism supports the top fixing ring through the fixing column extending from the base 9, so that the fixing ring is fitted on the outside of the guide tube 2, limiting the guide tube 2 and forming a constraint above the coil support. This design provides effective motion limitation and structural protection for the coil support in the axial direction, preventing it from overshooting or becoming unstable during severe vibration, thereby enhancing the guidance of the movement of the external spring oscillator system and the reliability of the overall structure, and ensuring the smooth operation of the energy conversion process.

[0042] like Figure 1 As shown, in some embodiments, the fixing post is located on the side of the coil support away from the guide tube 2, and the fixing post is used to limit the relative position of the coil support in the radial direction of the guide tube 2.

[0043] By setting the fixed column on the side of the coil support away from the guide tube 2, the relative displacement of the coil support along the radial direction of the guide tube 2 can be effectively restricted, thereby ensuring that the induction coil 6 always maintains a coaxial relationship with the guide tube 2 during vibration, avoiding magnetic circuit inhomogeneity and power generation efficiency reduction caused by radial offset, and significantly improving the stability and reliability of vibration energy harvesting.

[0044] like Figure 1As shown, in some embodiments, a power management module is also included. The power management module is disposed on the base 9 and is electrically connected to the induction coil 6. The power management module is used to process the electrical energy generated by the induction coil 6, and the output end of the power management module is provided with a standard power interface.

[0045] The power management module is directly mounted on the base 9 and electrically connected to the induction coil 6. It realizes the rectification, filtering and voltage regulation of the electrical energy generated by vibration. Its standard power interface at the output end provides a stable and reliable power supply for external electrical equipment, thereby effectively converting irregular vibration energy into a standard power output that can be directly used, which significantly improves the practicality and integration level of the device.

[0046] like Figure 1 As shown, in some embodiments, the stiffness coefficient of the first spring 3 ranges from 300 N / m to 600 N / m, and the stiffness coefficient of the second spring 8 ranges from 3000 N / m to 7000 N / m.

[0047] By setting the stiffness coefficients of the first spring 3 and the second spring 8 within significantly different ranges, the inner and outer spring oscillator systems have distinctly different natural frequencies, thus forming a wideband, high-efficiency energy harvesting system. This design ensures that the device maintains high power generation efficiency over a wide range of vibration frequencies, successfully solving the problems of narrow operating bandwidth and frequency sensitivity of energy harvesting efficiency in traditional single oscillator systems. In the embodiments of this application, the load energy is mainly distributed at several dominant frequencies, particularly 1.95 Hz, 7.81 Hz, 11.72 Hz, and 14.65 Hz.

[0048] First spring: responsible for matching lower frequency bands (such as 1.95Hz, 7.81Hz), wire diameter 1.0 mm, free length 35 mm, effective number of turns 6.

[0049] Second spring: responsible for matching higher frequency bands (such as 11.72Hz, 14.65Hz), wire diameter 2.0 mm, free length 45 mm, effective number of turns 5.

[0050] The first and second springs are made of piano wire. Of course, the materials and specifications mentioned above can be replaced according to actual needs.

[0051] The formula for calculating the natural frequency is: ; in: It is the spring stiffness coefficient (N / m); It is the mass (kg) of the oscillator.

[0052] The mass of a permanent magnet, based on a common N52 neodymium iron boron cylindrical magnet with a diameter of 30 mm and a height of 20 mm, is 0.2–0.3 kg.

[0053] The mass of the induction coil and coil support is 0.5–0.8 kg.

[0054] The target frequency of the first spring is set between 5-8Hz to cover the main frequency of 7.81Hz.

[0055] .

[0056] Therefore, the stiffness of the first spring is in the range of 300-600 N / m.

[0057] In addition, the target frequency of the second spring is set between 10-15Hz to cover the main frequencies of 11.72Hz and 14.65Hz.

[0058] .

[0059] Therefore, the stiffness of the second spring is in the range of 3000-6000 N / m.

[0060] The stiffness ratio of the two springs is 10, which ensures a sufficiently large separation of the natural frequencies of the inner and outer oscillator systems, thereby generating a significant phase difference within the target frequency band (6-14 Hz).

[0061] When the stiffness is too low (e.g., the stiffness of the first spring is less than 300 N / m), the amplitude of the inner oscillator is too large, which may exceed the travel of the guide tube and cause a collision.

[0062] When the stiffness is too high (e.g., the stiffness of the second spring is greater than 6000 N / m), the response amplitude of the external oscillator is too small, which is not conducive to energy harvesting.

[0063] An oscillator with too little mass has low inertia and is easily affected by frictional damping, air damping, and electromagnetic damping, which may lead to ineffective excitation or unstable motion under non-ideal conditions. Furthermore, permanent magnets require a certain volume to provide a sufficiently strong magnetic field, and coils require a certain number of turns and volume to provide sufficient output voltage and power. Their physical dimensions determine the lower limit of their mass; pursuing extremely small mass will result in a weak magnetic field or insufficient coil turns, failing to meet power generation requirements. Therefore, the choice of mass is a balance between effectively absorbing energy and being effectively driven by the spring, taking a value that is above average within the achievable range.

[0064] The first spring targets a frequency of 5-8 Hz, not the lowest 1.95 Hz, but rather the vicinity of 7.81 Hz, where energy is more concentrated and more controllable from an engineering perspective. This allows for effective energy harvesting in this frequency band while keeping the spring stiffness within a reasonable, reliable, and amplitude-controllable range (300-600 N / m).

[0065] The target frequencies for the second spring are 11.72Hz and 14.65Hz, which have higher energy. Similarly, if the target frequency is set too low in order to cover all frequencies starting from 8Hz, its stiffness will be too close to that of the first spring, failing to generate a sufficient phase difference and thus losing the core advantage of the dual-oscillator superposition amplification.

[0066] The displacement and phase formulas for a spring oscillator system under simple harmonic excitation are shown below: .

[0067] The formula for resonant frequency is: .

[0068] Resonant vibration refers to the periodic motion of an object under the action of force. This motion is proportional to the force and displacement and always points towards equilibrium. The vibration of a spring oscillating system with a single degree of freedom is resonant vibration P0. Considering that the structure consists of two independent spring oscillating systems with a relative vibration relationship between them, the vibration between the permanent magnet 4 and the induction coil 6 is considered as superposition. This concept is simplified to the vibration generated by the permanent magnet 4 relative to the induction coil 6. Assuming that the vibration of the permanent magnet 4 and the vibration of the induction coil 6 are both sinusoidal functions, i.e., y1 is the vibration function of the inner permanent magnet and y2 is the vibration function of the coil, the expressions are as follows: ; The formula for y² can be transformed into the following formula: ; Substituting the formulas for y1 and y2 (after transformation) into the untransformed formula for y2, we obtain the following formula: ; Based on the auxiliary angle equation, the superposition result of the two vibration equations is obtained as follows: .

[0069] Therefore, it can be seen that the superposition of two harmonic vibrations with the same frequency leads to a significant increase in amplitude, even though the vibration frequency remains unchanged.

[0070] In addition, preliminary tests revealed the following natural frequencies and actual resonant frequencies for each test device: .

[0071] Based on the test data of the resonant frequency formula and the results in the table above, the damping ratio of the permanent magnet is 0.552 and the damping ratio of the induction coil is 0.485.

[0072] .

[0073] Based on the above formula, the phase difference between the permanent magnet and the induction coil is calculated to be 7.72.

[0074] Assuming the initial phase of the moving iron assembly is 0, the amplitude is 5mm, and the frequency matches the actual resonant frequency of 5Hz, then the vibration equation of the moving iron assembly is: .

[0075] Because the six sets of induction coils have relatively high spring stiffness, their initial phase is set to 7.72 degrees, the amplitude to 3 mm, and the frequency to be consistent with the moving iron group at 5 Hz. The vibration equation of the induction coil is: .

[0076] After simulation analysis, the maximum induced current of permanent magnet 4 and induction coil 6 reached 0.008A and 0.006A, respectively.

[0077] The vibration equations of permanent magnet 4 and induction coil 6 are superimposed to derive the vibration equation of permanent magnet 4 relative to induction coil 6, as follows: .

[0078] like Figure 2 As shown, the maximum induced current of the toroidal resonant circuit is approximately 0.023A. Compared to permanent magnet 4, this value is increased by approximately 65%. Furthermore, compared to the induction coil, it is increased by approximately 74%. Therefore, the power generation efficiency of the toroidal resonant circuit is significantly improved.

[0079] A sinusoidal vibration comparison test was conducted to measure the power generation capacity of the test prototype at the vibration frequency of the anti-yawing vibration damper using a sinusoidal signal, and a comparative analysis was performed. Based on the actual working stroke of the anti-yawing vibration damper, the vibration amplitude was 2 mm.

[0080] from Figures 3-5As can be seen, since the low-frequency vibration energy is mainly absorbed by the internal permanent magnet 4-spring oscillator, and the forced vibration response of the low-stiffness spring oscillator system is more significant, the output power of the power generation device will fluctuate greatly at low frequencies. Higher-frequency vibration energy is absorbed by the coil spring oscillator, and the power generation process gradually stabilizes. By organizing and analyzing the test data, the effective values ​​of induced voltage, current, and power for each test group at different vibration frequencies were obtained. The percentage increase in power generation of the ring iron resonance group relative to the moving iron group and the moving ring group was calculated, as shown in the table below.

[0081]

[0082] The device generates power ranging from 2.80 watts to 20.18 watts within the main frequency band of the anti-yaw damper. This is sufficient to meet the power supply requirements of the magnetorheological equipment during high-speed train operation. Its maximum power generation capacity is 98% higher than the previous level.

[0083] Based on the testing of the experimental prototype, such as Figure 3-5 Based on the data in the table above, under vibration at 8 Hz: When only the internal spring oscillator system is operational: permanent magnet 4 vibrates significantly, while induction coil 6 remains essentially stationary. The effective value of the system output voltage is approximately 12.20 V, and the effective value of the current is approximately 0.59 A. This state primarily reflects the response amplitude of the internal spring oscillator system.

[0084] When only the external spring oscillator system is operational: induction coil 6 vibrates significantly, while permanent magnet 4 remains essentially stationary. The effective value of the system output voltage is approximately 5.54 V, and the effective value of the current is approximately 0.08 A. This state primarily reflects the response amplitude of the external spring oscillator system, whose output amplitude (voltage and current) differs significantly from that of the internal spring oscillator system.

[0085] The dual internal spring oscillator system works in tandem: both the permanent magnet 4 and the induction coil 6 vibrate. The effective value of the system output voltage is approximately 25.23 V, and the effective value of the current is approximately 0.80 A. The output is much greater than the output of the two single modes mentioned above, and it is not a simple sum of the two.

[0086] Because the responses of the two oscillators differ in both amplitude and phase, their relative motion is amplified when they work together, ultimately making the power generation of the double inner spring oscillator system (20.18 W) 2.8 times that of the inner spring oscillator system alone (7.19 W), rather than simply 1+1=2.

[0087] Furthermore, the embodiments of this application are designed to address the self-powered problem of high-speed train vibration dampers. The design is based on the actual train load spectrum (dominant frequencies: 1.95Hz, 7.81Hz, 11.72Hz, 14.65Hz). The operating frequency band of the device (6-14Hz) is optimized and determined around these dominant frequencies, directly solving the engineering bottleneck of requiring external wiring power supply for magnetorheological vibration dampers. This significant stiffness ratio is key to creating an effective phase difference and achieving the amplification effect of "ring iron resonance," rather than any combination of two springs. It integrates two electromagnetic power generation modes, namely "inner spring oscillator system permanent magnet" and "outer spring oscillator system induction coil," into one system through the shared magnetic field of the permanent magnet and the mechanically coupled double spring guiding system. The two oscillator permanent magnets and coils are nested in space, relative in motion, and coordinated electrically, thus producing a power generation effect of "1+1>2."

[0088] Secondly, an embodiment of this application provides a vibration power generation method based on a spring oscillator, employing the aforementioned vibration power generation device based on a spring oscillator, comprising the following steps: External vibrations are received by the inner spring oscillator system and the outer spring oscillator system, respectively. By using the different stiffness parameters of the first spring 3 and the second spring 8, the inner spring oscillator system and the outer spring oscillator system vibrate with different natural frequencies and phases. By generating vibrations under the action of their respective spring oscillator systems, the phase difference and amplitude superposition effect between the two vibrations of permanent magnet 4 and induction coil 6 are utilized to amplify the relative motion amplitude between permanent magnet 4 and induction coil 6. The amplified relative motion between the permanent magnet 4 and the induction coil 6 changes the magnetic flux passing through the induction coil 6, thereby generating an induced electromotive force and realizing the conversion of vibration mechanical energy into electrical energy.

[0089] The vibration power generation method provided in this application embodiment sets up inner and outer spring oscillator systems with significant stiffness differences, so that the two can respond with different natural frequencies and phases when receiving external vibrations. Furthermore, by utilizing the vibration superposition effect caused by the phase difference between the two oscillator systems, the limited vibration amplitude in the environment is converted into a large-amplitude axial relative motion between the permanent magnet 4 and the induction coil 6, which effectively enhances the rate of change of magnetic flux through the induction coil 6, thereby significantly improving the output intensity of the induced electromotive force and the power generation, and realizing the efficient and stable collection and conversion of mechanical energy in a wide-bandwidth, small-amplitude vibration environment.

[0090] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A vibration power generation device based on a spring oscillator, characterized in that, include: Base; A guiding mechanism, comprising an axially arranged guide tube, the bottom of which is fixed to the base, and an end cap provided on the top of which; An internal spring oscillator system, comprising a permanent magnet and a first spring, wherein one end of the first spring is fixedly connected to the end cap and the other end of the first spring is connected to the permanent magnet, and the permanent magnet is slidably disposed within the guide tube; An external spring oscillator system includes an induction coil, a coil support, and a second spring. The induction coil is sleeved on the outside of the guide tube. The coil support is used to fix the induction coil. One end of the second spring is fixedly connected to the base, and the other end of the second spring is connected to the coil support. The stiffness coefficient of the first spring is smaller than that of the second spring; When subjected to external vibration, the first spring and the second spring vibrate with different phases and amplitudes, and the permanent magnet and the induction coil generate an axial relative motion greater than the input amplitude of the external vibration, so that the permanent magnet generates a magnetic flux that passes through the induction coil, and an induced electromotive force is generated in the induction coil.

2. The vibration power generation device based on a spring oscillator according to claim 1, characterized in that, The coil support includes an upper support and a lower support, which are respectively fixed at both ends of the axial direction of the induction coil. The lower support is connected to the second spring. The upper support and the lower support are provided with guide grooves on the side near the guide tube. The outer wall of the guide tube is provided with guide ribs arranged along the axial direction of the induction coil. The guide grooves and the guide ribs are slidably connected to restrict the axial movement of the induction coil.

3. The vibration power generation device based on a spring oscillator according to claim 1, characterized in that, It also includes an outer shell, which is fixedly connected to the base. The outer shell and the base enclose a cavity, and the guide mechanism, the inner spring oscillator system and the outer spring oscillator system are located in the cavity.

4. The vibration power generation device based on a spring oscillator according to claim 3, characterized in that, It also includes an installation mechanism, which comprises: A connecting base, one side of which is fixedly connected to the base; Mounting components, which are used to connect to the vehicle body structure; The connecting base and the mounting component are detachably connected, and the clamping or fitting surface of the mounting component can be adapted to the surface shape of the vehicle body structure.

5. The vibration power generation device based on a spring oscillator according to claim 1, characterized in that, It also includes a limiting mechanism, which is disposed inside the guide tube and located at one end of the guide tube near the base. The limiting mechanism is used to absorb impact and prevent the permanent magnet from colliding with the base.

6. The vibration power generation device based on a spring oscillator according to claim 1, characterized in that, It also includes a fixing mechanism, which includes a fixing ring and a fixing post. The bottom of the fixing post is fixedly connected to the base, and the top of the fixing post is connected to the fixing ring. The fixing ring is located above the coil support and is sleeved on the outside of the guide tube.

7. The vibration power generation device based on a spring oscillator according to claim 6, characterized in that, The fixing post is located on the side of the coil support away from the guide tube, and the fixing post is used to limit the relative position of the coil support along the radial direction of the guide tube.

8. The vibration power generation device based on a spring oscillator according to claim 1, characterized in that, It also includes a power management module, which is mounted on the base and electrically connected to the induction coil. The power management module is used to process the electrical energy generated by the induction coil, and the output end of the power management module is provided with a standard power interface.

9. The vibration power generation device based on a spring oscillator according to claim 1, characterized in that, The stiffness coefficient of the first spring ranges from 300 N / m to 600 N / m, and the stiffness coefficient of the second spring ranges from 3000 N / m to 7000 N / m.

10. A vibration-based power generation method based on a spring oscillator, characterized in that, The vibration power generation device based on a spring oscillator as described in any one of claims 1-9 includes the following steps: External vibrations are received by the inner spring oscillator system and the outer spring oscillator system, respectively. By using the different stiffness parameters of the first spring and the second spring, the inner spring oscillator system and the outer spring oscillator system vibrate with different natural frequencies and phases; The permanent magnet and the induction coil vibrate under the action of their respective spring oscillator systems. The phase difference and amplitude superposition effect between the two vibrations of the permanent magnet and the induction coil are used to amplify the relative motion amplitude between the permanent magnet and the induction coil. The amplified relative motion between the permanent magnet and the induction coil changes the magnetic flux passing through the induction coil, thereby generating an induced electromotive force and realizing the conversion of vibrational mechanical energy into electrical energy.

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