Vibration absorbing device and vibration control method

Abstract

The application relates to the technical field of rotating machinery vibration control, and provides a vibration absorption type damping device and a vibration treatment method. The vibration absorption type damping device comprises a damping assembly, the damping assembly comprises a magnetorheological elastomer, the magnetorheological elastomer internally stores magnetorheological liquid, the magnetorheological elastomer is configured to change the magnetic modulus under the excitation action to realize stiffness adjustment, and the magnetorheological liquid is configured to realize damping adjustment under the action of a magnetic field; a plurality of spiral springs are arranged at one side of the magnetorheological elastomer at intervals; a counterweight is arranged at the other side of the magnetorheological elastomer; a lead screw is in threaded cooperation with the counterweight and is used for controlling the movement of the counterweight relative to the magnetorheological elastomer to change the equivalent vibration mass; and an excitation coil is sleeved on the outer periphery of the magnetorheological elastomer. The vibration absorption type damping device provided by the application can dynamically optimize the damping performance according to different vibration frequencies and intensities through the triple adjustment mechanism of stiffness, damping and mass, and can effectively inhibit complex vibration.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of rotating machinery vibration control, in particular to a vibration absorption type damping device and a vibration treatment method. BACKGROUND

[0002] In the related art, a traditional dynamic vibration absorber is designed with fixed parameters, and the damping frequency band is narrow (<10 Hz), which cannot adapt to the frequency offset caused by the change and fluctuation of the rotating speed. SUMMARY

[0003] In order to solve the technical problem that the traditional dynamic vibration absorber is designed with fixed parameters, the damping frequency band is narrow, and it cannot adapt to the frequency offset caused by the change and fluctuation of the rotating speed, the first aspect of the present application proposes a vibration absorption type damping device.

[0004] The second aspect of the present application also proposes a vibration treatment method.

[0005] Therefore, according to the embodiment of the first aspect of the present application, the present application proposes a vibration absorption type damping device, which comprises: a damping assembly, the damping assembly comprising: a magneto-rheological elastomer, internally storing a magneto-rheological fluid, the magneto-rheological elastomer being configured to change the magnetic modulus under the excitation to realize stiffness adjustment, and the magneto-rheological fluid being configured to realize damping adjustment under the action of the magnetic field; a plurality of spiral springs, which are arranged at intervals on one side of the magneto-rheological elastomer; a counterweight, which is arranged on the other side of the magneto-rheological elastomer; a lead screw, which is threadedly matched with the counterweight and is used to control the movement of the counterweight relative to the magneto-rheological elastomer to change the equivalent vibration mass; and an excitation coil, which is sleeved on the outer periphery of the magneto-rheological elastomer.

[0006] In some technical solutions, optionally, the vibration absorption type damping device further comprises: a multi-modal controller, which is connected with the damping assembly and is configured to cooperatively adjust the stiffness, damping and mass parameters of the damping assembly to dynamically match the natural frequency of the damping assembly with the vibration main frequency of the rotating mechanism.

[0007] In some technical solutions, optionally, the vibration absorption type damping device further comprises: a thermoelectric refrigeration sheet, which is arranged on the outer periphery of the excitation coil and is used to adjust the temperature of the excitation coil; and the multi-modal controller is connected with the thermoelectric refrigeration sheet and is used to control the refrigeration power of the thermoelectric refrigeration sheet.

[0008] In some technical solutions, optionally, the excitation coil is a Helmholtz coil, and the Helmholtz coil is topologically arranged on the outer periphery of the magneto-rheological elastomer.

[0009] In some technical solutions, optionally, the lead screw is a ball screw, and the vibration absorption type damping device further comprises: a roller bearing, in which the ball screw is arranged.

[0010] In some embodiments, optionally, a graphite layer is arranged between the counterweight and the magnetorheological elastomer, and the vibration-absorbing damping device further comprises a servo motor connected to the lead screw and configured to drive the lead screw to rotate so as to control the position of the counterweight.

[0011] In some embodiments, optionally, the magnetorheological elastomer and the plurality of coil springs are connected to form a stiffness-adjustable structure, and a magnetic modulus change rate of the stiffness-adjustable structure is ΔG, and when the current is 0.8 ampere, ΔG=1.8 MPa.

[0012] In some embodiments, optionally, the vibration-absorbing damping device further comprises an optical fiber grating sensor arranged on the counterweight and a piezoelectric accelerometer arranged on the counterweight.

[0013] According to the embodiments of the second aspect of the present application, the second aspect of the present application provides a vibration management method, comprising: extracting a vibration main frequency of a rotating mechanism; online identifying stiffness, damping and mass parameters of the vibration-absorbing damping device according to any one of the above technical solutions; and adopting a stiffness, damping and mass three-parameter cooperative adjustment strategy to dynamically match the natural frequency of the vibration-absorbing damping device with the vibration main frequency of the rotating mechanism.

[0014] In some embodiments, optionally, the vibration management method further comprises: collecting vibration data of the counterweight by the optical fiber grating sensor and the piezoelectric accelerometer; inputting the vibration data into a fractal dimension dynamic threshold model to evaluate the health state of the bearing of the rotating mechanism, and performing fault warning when the fractal dimension threshold value is greater than the normal value.

[0015] Compared with the prior art, the present application has the following technical effects:

[0016] The present application provides a vibration-absorbing damping device, which is an intelligent dynamic vibration-absorbing device based on multi-parameter cooperative regulation. The stiffness, damping and mass of the magnetorheological elastomer (MRE) and the servo motor are cooperatively adjusted, VMDHHT signal processing and fuzzy PID+H∞ (H-infinity) hybrid control algorithm are combined to achieve 580Hz wideband vibration suppression (amplitude reduction of 92%). The external cooling design of the distributed Helmholtz coil and the thermoelectric cooling fin makes the MRE working temperature stable below 60℃. The device life cycle is greater than 15 years, the maintenance cost is reduced by 75%, and it is suitable for active vibration management of high-precision rotating machinery. It is suitable for wideband vibration suppression of precision rotating equipment such as steam turbine generator set, variable frequency pump and industrial compressor.

[0017] Additional aspects and advantages of the present application will become apparent in the description that follows, or will be learned by practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0018] The above and / or additional aspects and advantages of the present application will become apparent and more readily appreciated from the following description, taken in conjunction with the following drawings in which:

[0019] Figure 1 A structural schematic diagram of a vibration-absorbing damping device according to one embodiment of the present application is shown;

[0020] Figure 2 A multi-modal control flowchart of a vibration-absorbing damping device according to one embodiment of the present application is shown;

[0021] Figure 3 A flowchart of a vibration management method according to one embodiment of the present application is shown.

[0022] Wherein, Figure 1 The correspondence between the reference signs and the component names in the accompanying drawings is as follows:

[0023] 110 damping assembly, 112 magnetorheological elastomer, 114 coil spring, 116 counterweight, 118 screw rod, 120 excitation coil, 130 multi-modal controller, 140 thermoelectric refrigeration piece, 150 roller bearing, 160 graphite layer, 170 servo motor, 180 fiber Bragg grating sensor, 182 piezoelectric accelerometer. DETAILED DESCRIPTION

[0024] In order to more clearly understand the above-mentioned purposes, features and advantages of the present application, the present application will be further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.

[0025] In the following description, a large number of specific details are set forth in order to facilitate a thorough understanding of the present application, however, the present application can also be implemented in other ways different from those described herein, therefore, the scope of protection of the present application is not limited by the specific embodiments disclosed below.

[0026] The following refers to Figures 1 to 3 A vibration-absorbing damping device and a vibration management method according to some embodiments of the present application are described.

[0027] As Figure 1As shown, the first aspect of the present application proposes a vibration absorption type damping device, comprising: a damping assembly 110, the damping assembly 110 comprising: a magneto-rheological elastomer 112, internally storing a magneto-rheological fluid, the magneto-rheological elastomer 112 being configured to change the magnetic modulus under the action of excitation to realize stiffness adjustment, and the magneto-rheological fluid being configured to realize damping adjustment under the action of a magnetic field; a plurality of coil springs 114, arranged at one side of the magneto-rheological elastomer 112; a counterweight 116, arranged at the other side of the magneto-rheological elastomer 112; a lead screw 118, threadedly cooperating with the counterweight 116, for controlling the movement of the counterweight 116 relative to the magneto-rheological elastomer 112 to change the equivalent vibration mass; and an excitation coil 120, sleeved on the outer periphery of the magneto-rheological elastomer 112.

[0028] The vibration absorption type damping device provided by the present application is used for being mounted on a rotating mechanism, and comprises the damping assembly 110, the damping assembly 110 comprising the magneto-rheological elastomer 112, the counterweight 116, the lead screw 118, the excitation coil 120 and the plurality of coil springs 114.

[0029] By adopting the three-parameter cooperative adjustment strategy, the stiffness, damping and mass parameters can be comprehensively adjusted, so that the natural frequency of the vibration absorption type damping device can be dynamically matched with the vibration frequency of the rotating mechanism, so as to achieve a better damping effect.

[0030] Stiffness adjustment: the movement of the lead screw 118 driving the counterweight 116 can change the stiffness of the system; at the same time, the magneto-rheological elastomer 112 (MRE) can flexibly change the magnetic modulus under the action of excitation, realizing real-time stiffness adjustment.

[0031] Damping adjustment: the magnetic field strength of the excitation coil 120 can be accurately controlled through excitation current, the magneto-rheological elastomer 112 internally stores a magneto-rheological fluid, and the damping characteristics of the magneto-rheological fluid will change under the action of a magnetic field. By controlling the magnetic field strength, the damping size can be adjusted, so that the device can better dissipate vibration energy. The synergistic effect of the magneto-rheological elastomer 112 and the magneto-rheological fluid, and the elastic energy storage of the coil spring 114, together constitute an efficient energy dissipation mechanism, significantly reducing the transmission of vibration energy and improving the damping efficiency.

[0032] Mass adjustment: a dynamic counterweight compensation method is adopted, the lead screw 118 is threadedly connected with the counterweight 116, rotating the lead screw 118 can accurately control the position of the counterweight 116, according to the vibration condition of the system, driving the lead screw 118 to adjust the position of the counterweight 116, the equivalent vibration mass can be increased or decreased, so as to change the natural frequency of the device, realizing dynamic matching with the vibration main frequency of the rotating mechanism. The adjustability of the equivalent mass enhances the rapid response capability of the device to sudden vibration or vibration characteristic change, ensuring that the device is always in an optimal damping state.

[0033] The vibration absorption type damping device provided by the application can dynamically optimize damping performance and effectively suppress complex vibration according to different vibration frequencies and intensities through a triple adjustment mechanism of stiffness, damping and mass, can cover a wider vibration frequency range, significantly improves the vibration suppression effect, and meets diversified damping requirements.

[0034] As shown in Figure 1 In some embodiments, the vibration absorption type damping device optionally further comprises a multi-modal controller 130 connected with the damping assembly 110 and configured to cooperatively adjust the stiffness, damping and mass parameters of the damping assembly 110 to dynamically match the natural frequency of the damping assembly 110 with the vibration main frequency of the rotating mechanism.

[0035] In this embodiment, the vibration absorption type damping device further comprises a multi-modal controller 130. The multi-modal controller 130 can obtain the vibration main frequency of the rotating mechanism and cooperatively adjust the stiffness, damping and mass parameters of the damping assembly 110 to keep the natural frequency of the damping assembly 110 consistent or close to the vibration main frequency. This dynamic matching mechanism greatly improves the absorption and suppression ability of the damping device for vibration of a specific frequency and significantly reduces vibration transmission.

[0036] Due to the dynamic adjustment of the natural frequency, the device not only performs excellently at a single frequency point, but also realizes effective damping in a wide frequency range, adapts to the vibration main frequency shift of the rotating mechanism caused by changes in operating state (such as changes in rotational speed). The intelligent adjustment of the multi-modal controller 130 avoids the increase in energy consumption caused by excessive damping, reduces the poor damping effect caused by parameter mismatch, and reduces long-term maintenance costs.

[0037] Specifically, the multi-modal controller 130 integrates a VMDHHT signal processing algorithm and a fuzzy PID+H∞ hybrid control strategy. Unlike traditional active control technology that relies on external energy input, has a complex system and low reliability, the multi-modal controller 130 of the application can realize intelligent control of the device through advanced algorithms and control strategies according to real-time collected vibration signals, improve the response speed and control accuracy of the system, and enhance the reliability and stability of the system.

[0038] The VMDHHT algorithm is a joint algorithm of variational mode decomposition (VMD) and Hilbert-Huang transform (HHT). Before using the algorithm to extract the bearing vibration main frequency, some parameters need to be obtained and substituted into the algorithm.

[0039] Specifically, the parameters required by the variational mode decomposition (VMD) are as follows: the number of mode decompositions K, which represents the number of mode components into which the original signal is decomposed; and the penalty factor a, which is used to balance signal fidelity and mode sparsity. The values of K and a are mainly determined according to experience in processing similar bearing vibration signals in the past.

[0040] The Hilbert-Huang transform (HHT) mainly decomposes a signal into multiple intrinsic mode functions (IMFs) based on empirical mode decomposition (EMD), and then performs Hilbert transform on each IMF to obtain instantaneous frequency and amplitude information.

[0041] The multi-modal controller 130 adopts a fuzzy PID + H∞ hybrid control strategy to comprehensively adjust the stiffness, damping, and mass parameters, so that the natural frequency of the vibration-absorbing damping device can dynamically match the vibration main frequency of the rotating machine, thereby achieving a better damping effect.

[0042] As shown in FIG. 1, in some embodiments, the vibration-absorbing damping device further includes a thermoelectric refrigeration piece 140 arranged at the outer periphery of the excitation coil 120, for temperature regulation of the excitation coil 120; and a multi-modal controller 130 connected with the thermoelectric refrigeration piece 140, for controlling the refrigeration power of the thermoelectric refrigeration piece 140. Figure 1

[0043] In this embodiment, the vibration-absorbing damping device further includes the thermoelectric refrigeration piece 140. The thermoelectric refrigeration piece 140 is directly attached to the outer periphery of the excitation coil 120, and the refrigeration power is adjusted in real time by the multi-modal controller 130 to ensure that the coil temperature is always within an optimal working range. Through active temperature control, the coil resistance change caused by temperature fluctuations is effectively avoided, and the stability of the magnetic field strength is ensured.

[0044] The thermoelectric refrigeration technology is based on the Peltier effect, and has a fast refrigeration response speed, which can adjust the temperature within milliseconds to adapt to the transient heat demand of the excitation coil 120 caused by load changes or environmental temperature fluctuations. The thermoelectric refrigeration piece 140 has a small volume and no moving parts, is easy to integrate with the excitation coil 120, and is suitable for installation environments with limited space.

[0045] Through continuous and stable temperature control, the service life of the excitation coil 120 is significantly prolonged, and problems such as insulation aging and magnetic performance degradation caused by overheating are reduced, thereby improving the overall reliability of the damping device.

[0046] In some embodiments, the excitation coil 120 is a Helmholtz coil, and the Helmholtz coil is arranged at the outer periphery of the magnetorheological elastomer 112.

[0047] ​In this embodiment, the excitation coil 120 is a Helmholtz coil, which is composed of two coaxial coplanar coils. By a specific spacing and current configuration, a highly uniform magnetic field can be generated in the central region. Compared with a single coil, the Helmholtz coil can significantly reduce the magnetic field gradient, ensure that each part of the magneto-rheological elastomer 112 is uniformly stressed, and avoid performance fluctuations caused by uneven magnetic fields. The uniform magnetic field makes the magneto-rheological elastomer 112 have more consistent magnetostrictive effects (such as stiffness changes), improving the dynamic response accuracy and stability of the vibration damping device.

[0048] The Helmholtz coil is wound around the outer periphery of the magneto-rheological elastomer 112 in a distributed manner, which can flexibly adapt to different shapes and sizes of the magneto-rheological elastomer 112 structure (such as cylindrical, plate-shaped, etc.), while reducing mechanical coupling interference between the coil and the magneto-rheological elastomer 112. It not only improves the space utilization, but also allows differential regulation of different regions of the magneto-rheological elastomer 112 through independent control of local coils, enhancing the adaptability and versatility of the vibration damping device.

[0049] By adjusting the current size and direction of the Helmholtz coil, the magnetic field strength and direction of the magneto-rheological elastomer 112 can be changed in real time, thereby dynamically adjusting its mechanical parameters such as stiffness and damping. The vibration damping device can quickly respond to external vibration changes (such as frequency and amplitude mutations), achieving wideband and multi-modal vibration damping effects.

[0050] The present application applies the Helmholtz coil topology to the outer periphery of the magneto-rheological elastomer 112 to form a distributed Helmholtz coil topology excitation system. The existing technology has defects in the excitation method of magneto-rheological materials, while the distributed Helmholtz coil topology excitation system of the present application, combined with the external thermoelectric cooling sheet 140, forms a unique external cooling design. This design effectively controls the working temperature of the magneto-rheological elastomer 112, keeps the working temperature of the magneto-rheological elastomer 112 below 60℃, ensures the performance of the magneto-rheological material, and improves the long-term stability and reliability of the entire device.

[0051] In the prior art, the built-in excitation coil 120 of the magneto-rheological material application causes the temperature rise to be too high, and the material performance declines significantly. The present application connects the magneto-rheological elastomer 112 (MRE) and the coil spring 114 in series to form a stiffness-adjustable structure, innovatively adopts an external excitation coil 120 design, uses a distributed Helmholtz coil topology, and externally connects a thermoelectric cooling sheet 140. Not only does it achieve flexible stiffness adjustment, but also makes the magnetic field uniformity error less than 3% and the temperature rise less than or equal to 15℃, effectively solving the problem of excessive temperature rise of the magneto-rheological elastomer 112, and ensuring the stability of the MRE material performance. Compared with the traditional single structure, the stiffness adjustment method and range are increased, which can better adapt to the vibration demand under different working conditions.

[0052] AsFigure 1 As shown in some embodiments, optionally, the lead screw 118 is a ball screw, and the vibration absorption damping device further comprises a roller bearing 150, and the ball screw is arranged in the roller bearing 150.

[0053] In this embodiment, the ball screw is driven by rolling of balls between the lead screw 118 and the nut, and compared with the traditional sliding lead screw 118, the ball screw has a lower friction coefficient and a higher transmission efficiency. The lead screw has a very low lead error, and can realize micron-level displacement control by cooperating with a high-precision encoder.

[0054] The rollers of the roller bearing 150 can further reduce the axial and radial friction of the ball screw, so that the device can still operate at a low power consumption under a high-speed and high-frequency vibration working condition. The high radial stiffness of the roller bearing 150 can ensure that the lead screw 118 does not deviate under vibration excitation, and improves the dynamic stability of the vibration absorption damping device.

[0055] By adopting the ball screw and the roller bearing 150, the heat generation and energy loss can be reduced, and the service life of the device can be prolonged. The vibration absorption damping device can accurately adjust the stiffness and damping parameters and quickly respond to the change of external vibration. In addition, cooperating with the grease lubrication and sealing structure, the service life of the ball screw and the roller bearing 150 is significantly improved, and the maintenance frequency is reduced.

[0056] As shown in some embodiments, optionally, a graphite layer 160 is arranged between the counterweight 116 and the magnetorheological elastomer 112, and the vibration absorption damping device further comprises a servo motor 170 connected with the lead screw 118, and the servo motor 170 is used to drive the lead screw 118 to rotate, so as to control the position of the counterweight 116. Figure 1

[0057] In this embodiment, the graphite layer 160 is arranged between the counterweight 116 and the magnetorheological elastomer 112, and the graphite layer 160 has a very low friction coefficient, which can significantly reduce the sliding friction resistance between the counterweight 116 and the magnetorheological elastomer 112, and reduce the energy loss and heat generation. Under the vibration working condition, the graphite layer 160 can form a dynamic lubrication film to avoid wear caused by dry friction, and prolong the service life of the magnetorheological elastomer 112. The layered structure of the graphite dissipates energy through micro-slippage in vibration, and enhances the passive damping capacity of the device, especially under low-frequency vibration.

[0058] The servo motor 170 drives the counterweight 116 through the ball screw, and realizes micron-level displacement control, which can quickly respond to the change of external vibration frequency and amplitude.

[0059] ​The ball screw stiffness adjusting mechanism driven by the servo motor 170 in the application adopts a redundant roller bearing 150 design and is combined with graphite lubrication. Compared with the traditional structure, the stiffness adjusting error is less than 2% under the condition of 3000r / min, while the stability and reliability of the mechanism are improved, the probability of wear and failure is reduced, and the service life is prolonged. The ball screw drive counterweight block 116 can more accurately control the position of the counterweight block 116, thereby realizing precise adjustment of the stiffness of the device, which is an advantage that the traditional fixed parameter design power absorber does not have.

[0060] In some embodiments, optionally, the magneto-rheological elastomer 112 and the plurality of spiral springs 114 are connected to constitute a stiffness adjustable structure, and a magnetic modulus change rate of the stiffness adjustable structure is ΔG, and when the current is 0.8 ampere, ΔG=1.8 megapascal.

[0061] In this embodiment, when the current is 0.8 ampere, the magnetic modulus change rate ΔG of the magneto-rheological elastomer 112 is 1.8 megapascal. The stiffness adjusting error is less than 2% under the condition of 3000r / min.

[0062] As shown in Figure 1 In some embodiments, optionally, the vibration-absorbing damping device further comprises: a fiber Bragg grating sensor 180 arranged on the counterweight block 116; and a piezoelectric accelerometer 182 arranged on the counterweight block 116.

[0063] In this embodiment, the vibration-absorbing damping device further comprises the fiber Bragg grating sensor 180 and the piezoelectric accelerometer 182. The fiber Bragg grating sensor 180 can monitor the displacement, strain and vibration mode of the counterweight block 116 in real time by measuring the slight deformation of the optical fiber, and is especially good at low-frequency (<10Hz) vibration detection. The optical fiber signal transmission is not affected by electromagnetic fields and is suitable for strong electromagnetic environments.

[0064] The piezoelectric accelerometer 182: The piezoelectric effect makes the accelerometer sensitive to high-frequency vibrations (>100Hz) and can accurately measure the acceleration amplitude and impact response of the counterweight block 116. The response time is <1ms, and it is suitable for dynamic vibration conditions.

[0065] By arranging the fiber Bragg grating sensor 180 and the piezoelectric accelerometer 182 on the counterweight block 116, the greater the vibration measured at the counterweight block 116, the greater the vibration energy absorbed by the vibration-absorbing damping device, and the smaller the vibration of the bearing seat, so that the damping effect of the vibration-absorbing damping device can be evaluated by monitoring the vibration of the counterweight block 116.

[0066] As shown in Figure 3 The second aspect of the application proposes a vibration treatment method, comprising the following steps:

[0067] S202: Extract the vibration main frequency of the rotating mechanism;

[0068] S204: Online identification of the stiffness, damping and mass parameters of the vibration absorption type damping device in any of the above embodiments;

[0069] S206: Adopting a three-parameter coordination adjustment strategy of stiffness, damping and mass to dynamically match the natural frequency of the vibration absorption type damping device with the vibration main frequency of the rotating mechanism.

[0070] The vibration management method provided in the application mainly extracts the vibration main frequency of the rotating mechanism based on the VMDHHT signal processing algorithm. The stiffness, damping and mass parameters of the vibration absorption type damping device are identified online through the recursive least squares method, and a fuzzy PID+H∞ mixed control strategy is adopted to comprehensively adjust the three parameters of stiffness, damping and mass, so that the natural frequency of the vibration absorption type damping device can dynamically match the vibration main frequency of the rotating machine, so as to achieve a better damping effect.

[0071] In some embodiments, optionally, the vibration management method further comprises: collecting vibration data of the counterweight by the fiber grating sensor and the piezoelectric accelerometer; inputting the vibration data into a fractal dimension dynamic threshold model to evaluate the health state of the bearing of the rotating mechanism, and performing fault warning when the fractal dimension threshold value is greater than the normal value.

[0072] In this embodiment, the vibration data of the counterweight is collected by the fiber grating sensor and the piezoelectric accelerometer, and the vibration data is input into the fractal dimension dynamic threshold model. The fractal dimension threshold value can be obtained by calculating the fractal dimension dynamic threshold model. Wherein, the fractal dimension threshold value 2.0 to 2.5 represents normal, the fractal dimension threshold value 2.5 to 3.0 performs fault warning, and the fractal dimension threshold value greater than or equal to 3.0 performs shutdown maintenance.

[0073] In actual application, the traditional dynamic vibration absorber: adopts fixed parameter design, the damping frequency band is narrow (<10Hz), and cannot adapt to the frequency offset caused by the change and fluctuation of the rotating speed. Active control technology: depends on external energy input, the system is complex and has low reliability, and is easy to fail in long-term operation. Application of magneto-rheological material: built-in excitation coil causes high temperature rise (>30℃), and material performance declines significantly.

[0074] The existing scheme has obvious deficiencies in wide frequency adaptation, multi-parameter coordination control and long-term stability, and an intelligent dynamic vibration absorption type damping device with high frequency response, low energy consumption and maintenance-free characteristics is urgently needed.

[0075] To solve the above problems, the application provides a vibration absorption type damping device, and the device structure is arranged as follows:

[0076] MRE support module: MRE and coil spring in series, stiffness adjustment range 500-2000 N / m (ΔG=1.8 MPa at 1.8 A).

[0077] External excitation coil design: distributed Helmholtz coil topology (magnetic field uniformity error <3%), external TEC12706 thermoelectric refrigeration piece, temperature rise ≤15℃.

[0078] Servo stiffness adjustment mechanism: ball screw driven counterweight, redundant roller bearing + graphite lubrication design, stiffness adjustment error <2% (3000 rpm working condition).

[0079] Multi-modal sensor system: fiber Bragg grating sensor (accuracy ±0.1 μm) + piezoelectric accelerometer (frequency response 0.5-5000 Hz).

[0080] Figure 2 Multi-modal control flowchart, including VMDHHT signal processing, parameter identification, fuzzy PID controller and robust control module, control method as follows:

[0081] Signal processing: VMDHHT joint algorithm: VMD (α=2000, K=5) combined with HHT, main frequency extraction accuracy ±0.1 Hz.

[0082] Parameter adjustment: three-parameter collaborative strategy: stiffness (servo motor + MRE inside), damping (MRF composite adjustment), mass (dynamic counterweight compensation).

[0083] Adaptive fuzzy PID controller: 49 rule bases, 7 linguistic variables (error, error rate, output).

[0084] Fault warning: fractal dimension dynamic threshold model: Hurst index + box dimension double parameter evaluation, warning accuracy ≥97%.

[0085] In specific embodiments, the specific implementation is as follows:

[0086] 1. Device installation

[0087] Flange connection: bearing seat middle split surface pre-tightening force 180 N·m, coaxial error <0.05 mm.

[0088] Heat dissipation system: thermoelectric refrigeration piece and MRE inside spacing 2 mm, heat dissipation channel wind speed 3 m / s.

[0089] 2. Parameter setting

[0090] Initial sweep: 5100Hz white noise excitation, identify the main frequency (e.g. 50Hz).

[0091] Synergistic regulation: Stiffness 1200N / m (servo motor positioning accuracy ±5μm), damping ratio 0.25, +8% compensation amount of counterweight.

[0092] 3. Dynamic control

[0093] Speed jump condition (3000rpm→2700rpm):

[0094] Parameter reconstruction completed within 0.5s: Stiffness 1000N / m, damping coefficient 55N·s / m, inherent frequency tracking error <0.3Hz.

[0095] Anti-interference test:

[0096] Apply 20% speed fluctuation interference, H∞ controller makes the vibration amplitude fluctuation rate <3%.

[0097] 4. Maintenance management

[0098] Health assessment: Fractal dimension threshold 2.0 to 2.5 (normal), 2.5 to 3.0 (warning), ≥3.0 (shutdown for maintenance).

[0099] Life verification: MRE accelerated aging experiment (2000 hours, 80℃) performance attenuation <8%.

[0100] The vibration absorption type damping device provided in the application is an intelligent dynamic vibration absorption device based on multi-parameter synergistic regulation, which realizes 580Hz wide frequency vibration suppression (amplitude reduction of 92%) through synergistic regulation of the stiffness, damping and mass of the magneto-rheological elastomer and the servo motor, combined with VMDHHT signal processing and fuzzy PID+H∞ hybrid control algorithm. The external heat dissipation design of the distributed Helmholtz coil and the thermoelectric cooling fin makes the MRE working temperature stable below 60℃. The device service life is >15 years, the maintenance cost is reduced by 75%, and it is suitable for active vibration control of high-precision rotating machinery.

[0101] In the application, the term "a plurality of" refers to two or more, unless otherwise explicitly limited. The terms "mounting", "connecting", "connecting", "fixing" and the like should be understood in a broad sense, for example, "connecting" can be fixed connection, or detachable connection, or integral connection; "connecting" can be direct connection, or indirect connection through intermediate medium. For those skilled in the art, the specific meaning of the above terms in the application can be understood according to the specific circumstances.

[0102] In the description of the application, the terms "one embodiment", "some embodiments", "certain embodiments", etc. mean that the particular feature, structure, material, or characteristic being described is included in at least one embodiment or example of the application. The appearing of these terms in various places in the specification are not necessarily all referring to the same embodiment or example, and the terms first, second, etc. do not necessarily signify any ordinal. Moreover, the particular features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0103] The above description is merely illustrative of the application, and is not intended to limit the application. The application can be modified and varied greatly without departing from the spirit or scope of the application, as set forth in the following claims.

Claims

1. A vibration-absorbing damping device, characterized in that, include: Vibration damping assembly, the vibration damping assembly comprising: A magnetorheological elastomer, internally storing a magnetorheological fluid, is configured to change its magnetostrictive modulus under excitation to achieve stiffness adjustment, and the magnetorheological fluid is configured to achieve damping adjustment under the action of a magnetic field. Multiple helical springs are spaced apart on one side of the magnetorheological elastomer; A counterweight is disposed on the other side of the magnetorheological elastomer; The lead screw, threadedly engaged with the counterweight, is used to control the movement of the counterweight relative to the magnetorheological elastic body, thereby changing the equivalent vibrating mass. An excitation coil is sleeved on the outer periphery of the magnetorheological elastic body. The excitation coil is a Helmholtz coil, and the Helmholtz coil is topologically located on the outer periphery of the magnetorheological elastic body. A thermoelectric cooling element is attached to the outer periphery of the excitation coil and is used to regulate the temperature of the excitation coil through active temperature control; A multimodal controller is connected to the vibration damping component and configured to coordinately adjust the stiffness, damping, and mass parameters of the vibration damping component. The multimodal controller integrates the VMDHHT signal processing algorithm and the fuzzy PID+H∞ hybrid control strategy. Based on the VMDHHT signal processing algorithm, the vibration main frequency of the rotating mechanism is extracted. The stiffness, damping, and mass parameters of the vibration-absorbing damping device are identified online by the recursive least squares method. The fuzzy PID+H∞ hybrid control strategy is used to comprehensively adjust the three parameters of stiffness, damping, and mass so that the natural frequency of the vibration-absorbing damping device can dynamically match the vibration main frequency of the rotating machinery. A fiber optic grating sensor is disposed on the counterweight; A piezoelectric accelerometer is mounted on the counterweight. A graphite layer is disposed between the counterweight and the magnetorheological elastomer; the vibration damping device further includes a servo motor connected to the lead screw, used to drive the lead screw to rotate, thereby achieving micron-level displacement control to control the position of the counterweight; The lead screw is a ball screw, and the vibration damping device further includes a roller bearing, through which the ball screw passes.

2. The vibration-absorbing damping device according to claim 1, characterized in that, The multimodal controller is connected to the thermoelectric cooler and is used to control the cooling power of the thermoelectric cooler.

3. The vibration-absorbing damping device according to claim 1 or 2, characterized in that, The magnetorheological elastomer and the plurality of helical springs are connected to form a stiffness-adjustable structure. The magnetostrictive modulus of the stiffness-adjustable structure changes by a rate of change of ΔG, which is 1.8 MPa when the current is 0.8 amperes.

4. A vibration control method, characterized in that, include: Extract the dominant vibration frequency of the rotating mechanism; Online identification of the stiffness, damping, and mass parameters of the vibration-absorbing damping device as described in any one of claims 1 to 3; A three-parameter coordinated adjustment strategy of stiffness, damping and mass is adopted to dynamically match the natural frequency of the vibration damping device with the main vibration frequency of the rotating mechanism.

5. The vibration control method according to claim 4, characterized in that, Also includes: Vibration data of the counterweight were collected using fiber optic grating sensors and piezoelectric accelerometers. The vibration data is input into the fractal dimension dynamic threshold model to evaluate the health status of the bearings of the rotating mechanism, and a fault warning is issued when the fractal dimension threshold is greater than the normal value.

Images