Long lead screw active resistance adjusting supporting device and long lead screw supporting damping control method

Abstract

The invention discloses a long lead screw active resistance adjusting supporting device and a long lead screw supporting damping control method, belongs to the field of lead screw equipment, and adopts the technical scheme that the long lead screw active resistance adjusting supporting device comprises a supporting block, two resistance adjusting assemblies, a plurality of excitation assemblies, a plurality of vibration sensors and a control module. The resistance adjusting assemblies are symmetrically arranged on the two sides of the supporting block and comprise corrugated pipes arranged in the axial direction of the lead screw, and shearing cavities filled with magnetorheological elastomers are formed in wave crests of the corrugated pipes. The excitation assemblies are evenly arranged in the axial direction, and the vibration sensors are arranged on the lead screw to collect vibration signals. The control module receives a sensor signal and adjusts the excitation intensity, stable axial rigidity support is provided through the corrugated pipe, the magnetorheological elastomer adjusts the radial rigidity in real time under the action of a magnetic field, and cooperative control over the axial rigidity and the radial rigidity is achieved. The device can effectively restrain multidirectional vibration of the lead screw, obviously improves dynamic stability of a system, and is particularly suitable for the field of high-speed precision transmission.

Description

Technical Field

[0001] This invention relates to the field of lead screw equipment, and in particular to a long lead screw active resistance adjustment support device and a long lead screw support damping control method. Background Technology

[0002] As a core component of precision transmission systems, the dynamic performance of long lead screws directly affects the overall accuracy and stability of the machine. When the lead screw's length-to-diameter ratio is ≥60 and the span exceeds 1.5m, the system rigidity decreases significantly, easily triggering multiple vibration modes under high-speed operation and complex load conditions. In particular, the amplitude of second-order bending vibration can reach ±5μm, severely restricting positioning accuracy. Furthermore, the thermal deformation and dynamic load changes generated during lead screw operation further exacerbate system instability. Therefore, modern high-end equipment places higher demands on lead screw support systems.

[0003] Currently, long lead screws mainly adopt two types of support methods: one is the traditional rigid bearing combination structure, which provides axial and radial constraints through angular contact ball bearings and thrust bearings. Although it can ensure high static stiffness, it lacks an effective damping mechanism. The other is a passive damping support that adds elastic elements such as rubber rings to the rigid support. It uses material deformation to dissipate vibration energy. Although it improves the damping characteristics to a certain extent, it is limited by the physical properties of the material, resulting in a narrow effective frequency band.

[0004] It is evident that the current support method has significant technical defects: First, traditional damping materials such as rubber have a narrow frequency band and are ineffective at suppressing high-frequency resonances above 500Hz; second, the decoupling design of axial and radial damping prevents vibration energy from being efficiently transmitted and dissipated in multiple dimensions; third, the passive support structure lacks dynamic adjustment capability and cannot adjust stiffness and damping characteristics in real time according to changes in operating conditions such as rotational speed and load, resulting in severe vibration response when the system passes the critical speed. Summary of the Invention

[0005] This invention addresses the problem that current passive support structures for lead screws cannot adjust their stiffness and damping characteristics in real time according to changes in operating conditions such as rotational speed and load. It provides an active resistance adjustment support device for long lead screws and a method for controlling the damping of long lead screw support.

[0006] To address the aforementioned problems, the present invention provides a long lead screw active resistance adjustment support device, comprising a support block and further comprising: two resistance adjustment components, each located on one side of the support block; each resistance adjustment component includes a bellows arranged along the axial direction of the supported lead screw, with its ends abutting against both ends of the support block; each corrugated peak of the bellows contains a shear cavity filled with a magnetorheological elastomer; multiple excitation components evenly arranged along the axial direction of the supported lead screw and close to the resistance adjustment components; multiple vibration sensors mounted on the supported lead screw and evenly arranged along its axial direction; and a control module electrically connected to both the vibration sensors and the excitation components, the control module receiving signals from the vibration sensors and adjusting the excitation intensity of the excitation components. This solution, by incorporating resistance adjustment components including bellows and a magnetorheological elastomer, achieves coordinated adjustment of axial and radial stiffness. The bellows provides stable axial stiffness support, while the magnetorheological elastomer can change its shear modulus in real time under the action of a magnetic field, thereby achieving precise control of radial stiffness. This composite structure design can effectively suppress multi-directional vibration of the lead screw during high-speed operation and significantly improve the dynamic stability of the system.

[0007] As a preferred embodiment of a long lead screw active resistance adjustment support device, constraint blocks are also provided at both ends of the support block, and the end of the bellows abuts against the constraint blocks. By setting the constraint blocks, excessive deformation of the bellows can be effectively limited, preventing permanent deformation damage caused by excessive displacement, while improving the stability and service life of the entire support device. The design of the constraint blocks also facilitates installation and positioning, ensuring that the bellows is always in optimal working condition.

[0008] On the other hand, the present invention also provides a long screw support damping control method, which uses the above-mentioned long screw active resistance adjustment support device, and the method includes the following steps: S1. Assemble the support device on the support position of the long lead screw; power on the control module, excitation component and vibration sensor, and connect to the host computer through the communication module to set the control parameters, including the vibration acceleration threshold, frequency-stiffness mapping relationship and maximum excitation current. S2. During the operation of the lead screw, the vibration signal of the lead screw is collected by the multiple vibration sensors to obtain a discrete time-domain vibration acceleration signal sequence, and the signal sequence is transmitted to the control module. S3. The control module performs real-time frequency domain analysis on the received discrete time domain vibration acceleration signal sequence and extracts the dominant frequency of the vibration and its corresponding amplitude as dynamic feature quantities. S4. Compare the dynamic feature quantities extracted in step S3 with the preset frequency-stiffness mapping relationship to determine the target magnetic field strength; based on the target magnetic field strength, calculate the target excitation current according to the pre-calibrated relationship between the magnetic field strength and the excitation current, and generate the corresponding digital control command. S5. The control module converts the digital control command into a pulse width modulation signal and outputs it to the excitation component. By adjusting the duty cycle of the pulse width modulation signal, the average excitation current of the excitation component is controlled to be equal to the target excitation current, thereby generating a magnetic field of target strength that acts on the magnetorheological elastic body, causing its macroscopic support stiffness to change. S6. After adjusting the support stiffness, return to step S2 and continue signal acquisition and analysis. Based on the newly obtained dynamic characteristic quantity, determine whether the amplitude corresponding to the vibration main frequency is less than or equal to the preset vibration acceleration threshold. If not, repeat steps S3 to S5 to correct the target excitation current and achieve adaptive adjustment.

[0009] This control method achieves real-time monitoring and active suppression of lead screw vibration. By establishing a complete perception-decision-execution closed-loop control system, the support stiffness can be dynamically adjusted according to the actual operating state of the lead screw, effectively suppressing vibrations at specific frequencies. Employing a control strategy based on frequency domain analysis and frequency-stiffness mapping, vibration characteristics can be accurately identified and responded to quickly, ensuring the system maintains excellent dynamic performance under various operating conditions.

[0010] As a preferred implementation of a long lead screw support damping control method, the process of obtaining the discrete-time vibration acceleration signal sequence in step S2 specifically involves: the analog voltage signal output by the vibration sensor is sampled by the analog-to-digital converter built into the control module at a sampling frequency of not less than 10 kHz to obtain a discrete voltage sequence; then, the discrete voltage sequence is multiplied by the calibration coefficient of the vibration sensor to convert it into a discrete-time vibration acceleration signal sequence. In step S1, the vibration sensor is a PVDF piezoelectric thin film sensor with a signal acquisition bandwidth of 0.5 to 5000 Hz; the control module is built on an FPGA. Using a PVDF piezoelectric thin film sensor in conjunction with a high sampling rate ADC conversion can accurately capture the vibration signal of the lead screw in a wide frequency range of 0.5-5000 Hz, providing a high-quality data foundation for subsequent frequency domain analysis. The FPGA-based control module ensures the real-time performance and reliability of signal processing, meeting the requirements of high-speed control.

[0011] As a preferred implementation of a long screw support damping control method, the FPGA-based control module is specifically constructed as follows: a parallel signal processing architecture is implemented within the FPGA using a hardware description language. This architecture integrates an FFT core for performing Fast Fourier Transform (FFT), a digital filter bank, and a pulse width modulation (PWM) generator. The FPGA parallel processing architecture can simultaneously perform multiple tasks such as signal acquisition, filtering analysis, and control output, significantly improving the system's response speed. The integrated FFT core and digital filter bank enable real-time frequency domain analysis, while the PWM generator precisely controls the excitation current, ensuring rapid and accurate adjustment of the magnetorheological elastomer's stiffness.

[0012] As a preferred implementation of a long screw support damping control method, in step S3, the real-time frequency domain analysis specifically involves performing a Fast Fourier Transform (FFT) on the discrete time-domain vibration acceleration signal sequence to obtain the frequency-domain acceleration components; the dominant vibration frequency and its corresponding amplitude are obtained by calculating the maximum value of the magnitude of the frequency-domain acceleration components. Converting the time-domain signal to a frequency-domain signal using the FFT clearly identifies the main frequency components and their amplitudes of the screw vibration, providing an accurate basis for subsequent stiffness adjustment. This method can effectively distinguish vibrations of different natures and achieve targeted suppression.

[0013] As a preferred implementation of a long screw support damping control method, in step S3, before the frequency domain analysis, the discrete-time vibration acceleration signal sequence is filtered using the digital filter bank. The operation is based on a finite impulse response (FIR) filter, and the filtered vibration acceleration signal sequence is obtained by weighted summation of the input signal sequence. The dynamic feature quantity is extracted based on the filtered vibration acceleration signal sequence. Preprocessing the original signal using an FIR digital filter effectively removes noise interference and improves the accuracy of vibration feature extraction. The FIR filter has linear phase characteristics, which can maintain the waveform of the signal without distortion, ensuring the reliability of subsequent analysis.

[0014] As a preferred implementation of a long screw support damping control method, in step S4, the frequency-stiffness mapping relationship is a data table pre-stored in the control module, which uses the dominant vibration frequency as an index to map the corresponding optimal target magnetic field strength; the pre-calibrated magnetic field strength and excitation current relationship is a linear or nonlinear function characterizing the correspondence between magnetic field strength and excitation current. Through the pre-stored frequency-stiffness mapping relationship table, the control system can quickly query the optimal control parameters for a specific vibration frequency, greatly improving the response speed. The pre-calibrated magnetic field strength and excitation current relationship ensures the accuracy of control, making the stiffness adjustment of the magnetorheological elastomer more accurate and reliable.

[0015] As a preferred implementation of a long screw support damping control method, in step S5, the digital control command is a digital quantity representing the target duty cycle, the pulse width modulation signal is generated according to the target duty cycle, and the average excitation current is proportional to the target duty cycle. By adjusting the target excitation current, the excitation component generates a magnetic field with continuously adjustable field strength within the range of 0-0.8T. Using PWM control technology, precise and continuous adjustment of the excitation current can be achieved, thereby realizing stepless control of the magnetic field strength. This control method has the advantages of fast response, high precision, and strong anti-interference capability, and can meet the fine adjustment requirements of magnetorheological elastomers for magnetic field strength.

[0016] As a preferred implementation of a long screw support damping control method, the method further includes: S7. Temperature Monitoring and Compensation: The temperature of the support device is monitored in real time by a built-in thermocouple, which is located inside or on the surface of the support block. If the temperature exceeds a preset range, the control module corrects the target excitation current determined in step S4 based on a pre-stored temperature-current compensation coefficient to obtain a compensated target current, or activates the phase change material for thermal management. The phase change material is filled in the annular cavity between the constraint block and the support block. The temperature monitoring and compensation function effectively solves the temperature rise problem caused by the lead screw during long-term high-speed operation. By monitoring the temperature in real time with thermocouples and combining the heat storage and release characteristics of the phase change material, the support device can be maintained within a suitable operating temperature range, avoiding performance degradation due to temperature changes and ensuring stable operation of the system under various working conditions.

[0017] This invention achieves coordinated adjustment of axial and radial stiffness through a resistance adjustment assembly comprising a bellows and a magnetorheological elastomer. The bellows provides stable axial support, while the magnetorheological elastomer can adjust radial stiffness in real time under the influence of a magnetic field, effectively suppressing multi-directional vibrations during high-speed operation. The constraint block limits excessive deformation of the bellows, improving the stability and service life of the device. Regarding the control method, a complete perception-decision-execution closed-loop control system is established. Vibration sensors collect signals in real time, and a parallel processing architecture based on FPGA performs fast Fourier transform and digital filtering to accurately extract vibration characteristics. A pre-stored frequency-stiffness mapping relationship is used to quickly determine the target magnetic field strength, and PWM regulation is used to achieve precise control of the excitation current, enabling adaptive adjustment of the support stiffness to suppress vibrations at specific frequencies. Furthermore, temperature monitoring and phase change material thermal management effectively control the operating temperature rise, ensuring the system's stability under various operating conditions. The overall solution has the advantages of wideband vibration suppression, fast dynamic response, and high control precision, significantly improving the dynamic stability and positioning accuracy of the long screw system. Attached Figure Description

[0018] To more clearly illustrate the technical solution of this patent, the drawings used in the description will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this patent. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention.

[0020] Explanation of main figure symbols 00. Lead screw, 1. Support block, 2. Bellows, 3. Shearing cavity, 4. Magnetorheological elastomer, 5. Excitation assembly, 6. Vibration sensor, 7. Constraint block. Detailed Implementation

[0021] To make the objectives, features, and advantages of this patent more apparent and understandable, the technical solutions of this patent will be clearly and completely described below with reference to the accompanying drawings of the specific embodiments. Obviously, the embodiments described below are only some embodiments of this patent, and not all embodiments. Based on the embodiments of this patent, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this patent.

[0022] Example 1 like Figure 1 As shown, a long lead screw active resistance adjustment support device includes a support block 1, and further includes: Two resistance adjustment components are respectively located on both sides of the support block 1. Each resistance adjustment component includes a bellows 2, which is arranged along the axial direction of the supported lead screw 00, and the end of the bellows 2 abuts against the two ends of the support block 1. Each crest of the bellows 2 is provided with a shear cavity 3, which is filled with a magnetorheological elastomer 4. The two ends of the support block 1 are also provided with constraint blocks 7, and the end of the bellows 2 abuts against the constraint blocks 7. Multiple excitation components 5 are evenly arranged along the axial direction of the supported lead screw 00 and close to the resistance adjustment component. Multiple vibration sensors 6 are provided, and the multiple vibration sensors 6 can be disposed on the supported lead screw and evenly arranged along the axial direction of the supported lead screw. The control module is electrically connected to both the vibration sensor 6 and the excitation component 5. The control module can receive signals from the vibration sensor 6 and adjust the excitation intensity of the excitation component 5.

[0023] Example 2 This embodiment further provides a long lead screw support damping control method, which uses the long lead screw active resistance adjustment support device described in Embodiment 1. The method includes the following steps: S1. Assemble the support device on the support position of the long lead screw; power on the control module, excitation component 5 and vibration sensor 6, and connect to the host computer through the communication module to set the control parameters, including the vibration acceleration threshold, frequency-stiffness mapping relationship and maximum excitation current. S2. During the operation of the lead screw, the vibration signals of the lead screw are collected by the multiple vibration sensors 6 to obtain a discrete time-domain vibration acceleration signal sequence, and the signal sequence is transmitted to the control module: The process of obtaining the discrete-time vibration acceleration signal sequence is as follows: the analog voltage signal output by the vibration sensor 6 is sampled by the analog-to-digital converter built into the control module at a sampling frequency of not less than 10 kHz to obtain a discrete voltage sequence. Then, the discrete voltage sequence is multiplied by the calibration coefficient of the vibration sensor to convert it into a discrete-time vibration acceleration signal sequence. In step S1, the vibration sensor 6 is a PVDF piezoelectric thin film sensor with a signal acquisition bandwidth of 0.5 to 5000 Hz. The control module is built on an FPGA. Specifically, the FPGA-based control module is constructed by programming a parallel signal processing architecture within the FPGA using a hardware description language. This architecture integrates an FFT core for performing Fast Fourier Transform, a digital filter bank, and a pulse width modulation generator. S3. The control module performs real-time frequency domain analysis on the received discrete time-domain vibration acceleration signal sequence, and extracts the dominant frequency of the vibration and its corresponding amplitude as dynamic feature quantities: The real-time frequency domain analysis specifically involves performing a Fast Fourier Transform on the discrete-time vibration acceleration signal sequence to obtain the frequency domain acceleration components; the dominant vibration frequency and its corresponding amplitude are obtained by calculating the maximum value of the magnitude of the frequency domain acceleration components. Prior to the frequency domain analysis, the discrete-time vibration acceleration signal sequence is filtered using the digital filter bank. The operation is implemented based on a finite impulse response filter, and the filtered vibration acceleration signal sequence is obtained by weighted summation of the input signal sequence; the dynamic feature quantities are extracted based on the filtered vibration acceleration signal sequence.

[0024] S4. Compare the dynamic feature quantities extracted in step S3 with the preset frequency-stiffness mapping relationship to determine the target magnetic field strength; based on the target magnetic field strength, calculate the target excitation current according to the pre-calibrated relationship between the magnetic field strength and the excitation current, and generate the corresponding digital control commands: The frequency-stiffness mapping relationship is a data table pre-stored in the control module, which uses the dominant vibration frequency as an index to map the corresponding optimal target magnetic field strength; the pre-calibrated magnetic field strength and excitation current relationship is a linear or nonlinear function characterizing the correspondence between magnetic field strength and excitation current.

[0025] S5. The control module converts the digital control command into a pulse width modulation signal and outputs it to the excitation component 5. By adjusting the duty cycle of the pulse width modulation signal, the average excitation current of the excitation component 5 is controlled to be equal to the target excitation current, thereby generating a magnetic field of target strength that acts on the magnetorheological elastic body 4, causing a change in its macroscopic support stiffness. The digital control command is a digital quantity representing the target duty cycle, the pulse width modulation signal is generated according to the target duty cycle, and the average excitation current is proportional to the target duty cycle. By adjusting the target excitation current, the excitation component 5 generates a magnetic field with a continuously adjustable field strength in the range of 0-0.8T.

[0026] S6. After adjusting the support stiffness, return to step S2 and continue signal acquisition and analysis. Based on the newly obtained dynamic characteristic quantity, determine whether the amplitude corresponding to the vibration main frequency is less than or equal to the preset vibration acceleration threshold. If not, repeat steps S3 to S5 to correct the target excitation current and achieve adaptive adjustment. S7. Temperature monitoring and compensation: The temperature value of the support device is monitored in real time by a built-in thermocouple, which is set inside or on the surface of the support block 1. If the temperature value exceeds the preset range, the control module corrects the target excitation current determined in step S4 according to the pre-stored temperature-current compensation coefficient to obtain the compensated target current, or activates the phase change material for thermal management, which is filled in the annular cavity between the constraint block and the support block 1.

[0027] As can be seen from the above embodiments, the beneficial effects of the present invention are as follows: This solution achieves coordinated adjustment of axial and radial stiffness through a resistance adjustment component comprising a bellows and a magnetorheological elastomer. The bellows provides stable axial support, while the magnetorheological elastomer can adjust radial stiffness in real time under the action of a magnetic field, effectively suppressing multi-directional vibration during high-speed operation. The constraint block limits excessive deformation of the bellows, improving the stability and service life of the device. Regarding the control method, a complete perception-decision-execution closed-loop control system is established. Vibration sensors collect signals in real time, and a parallel processing architecture based on FPGA performs fast Fourier transform and digital filtering to accurately extract vibration characteristics. A pre-stored frequency-stiffness mapping relationship is used to quickly determine the target magnetic field strength, and PWM regulation is used to achieve precise control of the excitation current, enabling adaptive adjustment of the support stiffness to suppress vibrations at specific frequencies. Furthermore, temperature monitoring and phase change material thermal management effectively control the operating temperature rise, ensuring the system's stable performance under various operating conditions. The overall solution has the advantages of wideband vibration suppression, fast dynamic response, and high control precision, significantly improving the dynamic stability and positioning accuracy of the long screw system.

[0028] The above description of the disclosed embodiments enables those skilled in the art to implement or use this patent. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this patent. Therefore, this patent is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A long lead screw active resistance adjustment support device, comprising a support block (1), characterized in that, Also includes: Two resistance adjustment components are located on both sides of the support block (1). Each resistance adjustment component includes a bellows (2), which is arranged along the axial direction of the supported lead screw (00). The end of the bellows (2) abuts against both ends of the support block (1). Each crest of the bellows (2) is provided with a shear cavity (3), which is filled with a magnetorheological elastomer (4). Multiple excitation components (5) are evenly arranged along the axial direction of the supported lead screw and close to the resistance adjustment component; Multiple vibration sensors (6) are provided on the supported lead screw (00) and are evenly arranged along the axial direction of the lead screw (00). The control module is electrically connected to both the vibration sensor (6) and the excitation component (5). The control module can receive the signal from the vibration sensor (6) and adjust the excitation intensity of the excitation component (5).

2. The long lead screw active resistance adjustment support device according to claim 1, characterized in that, The support block (1) is further provided with constraint blocks (7) at both ends, and the end of the bellows (2) abuts against the constraint blocks (7).

3. A method for controlling the damping of a long lead screw support, characterized in that, The method using the long lead screw active resistance adjustment support device as described in claim 1 or 2 includes the following steps: S1. Assemble the support device on the support position of the long screw; power on the control module, excitation component (5) and vibration sensor (6), and connect to the host computer through the communication module to set the control parameters, which include the vibration acceleration threshold, frequency-stiffness mapping relationship and maximum excitation current. S2. During the operation of the lead screw, the vibration signal of the lead screw is collected by the multiple vibration sensors (6) to obtain a discrete time-domain vibration acceleration signal sequence, and the signal sequence is transmitted to the control module. S3. The control module performs real-time frequency domain analysis on the received discrete time domain vibration acceleration signal sequence and extracts the dominant frequency of the vibration and its corresponding amplitude as dynamic feature quantities. S4. Compare the dynamic feature quantities extracted in step S3 with the preset frequency-stiffness mapping relationship to determine the target magnetic field strength; based on the target magnetic field strength, calculate the target excitation current according to the pre-calibrated relationship between the magnetic field strength and the excitation current, and generate the corresponding digital control command. S5. The control module converts the digital control command into a pulse width modulation signal and outputs it to the excitation component (5). By adjusting the duty cycle of the pulse width modulation signal, the average excitation current of the excitation component (5) is controlled so that it is equal to the target excitation current, thereby generating a magnetic field of target strength that acts on the magnetorheological elastic body (4) and causes its macroscopic support stiffness to change. S6. After adjusting the support stiffness, return to step S2 and continue signal acquisition and analysis. Based on the newly obtained dynamic characteristic quantity, determine whether the amplitude corresponding to the vibration main frequency is less than or equal to the preset vibration acceleration threshold. If not, repeat steps S3 to S5 to correct the target excitation current and achieve adaptive adjustment.

4. The method for controlling the damping of a long lead screw support according to claim 3, characterized in that, In step S2, the process of obtaining the discrete time-domain vibration acceleration signal sequence is as follows: the analog voltage signal output by the vibration sensor (6) is sampled by the analog-to-digital converter built into the control module at a sampling frequency of not less than 10 kHz to obtain a discrete voltage sequence, and then the discrete voltage sequence is multiplied by the calibration coefficient of the vibration sensor to convert it into a discrete time-domain vibration acceleration signal sequence; in step S1, the vibration sensor (6) is a PVDF piezoelectric thin film sensor with a signal acquisition bandwidth of 0.5 to 5000 Hz; the control module is built based on FPGA.

5. The method for controlling the damping of a long lead screw support according to claim 4, characterized in that, The control module based on FPGA is specifically constructed as follows: a parallel signal processing architecture is implemented inside the FPGA through hardware description language programming. This architecture integrates an FFT core for performing fast Fourier transform, a digital filter bank, and a pulse width modulation generator.

6. The method for controlling the damping of a long lead screw support according to claim 5, characterized in that, In step S3, the real-time frequency domain analysis specifically involves performing a fast Fourier transform on the discrete time-domain vibration acceleration signal sequence to obtain the frequency domain acceleration components; and calculating the maximum value of the magnitude of the frequency domain acceleration components to obtain the vibration dominant frequency and its corresponding amplitude.

7. The method for controlling the damping of a long lead screw support according to claim 6, characterized in that, In step S3, before the frequency domain analysis, the discrete time domain vibration acceleration signal sequence is filtered using the digital filter bank. The operation is based on the finite impulse response filter. The filtered vibration acceleration signal sequence is obtained by weighted summation of the input signal sequence. The dynamic feature quantity is extracted based on the filtered vibration acceleration signal sequence.

8. The method for controlling the damping of a long lead screw support according to claim 3, characterized in that, In step S4, the frequency-stiffness mapping relationship is a data table pre-stored in the control module, which uses the vibration dominant frequency as an index to map the corresponding optimal target magnetic field strength; the pre-calibrated magnetic field strength and excitation current relationship is a linear or nonlinear function characterizing the correspondence between magnetic field strength and excitation current.

9. The method for controlling the damping of a long lead screw support according to claim 3, characterized in that, In step S5, the digital control command is a digital quantity representing the target duty cycle, the pulse width modulation signal is generated according to the target duty cycle, and the average excitation current is proportional to the target duty cycle; by adjusting the target excitation current, the excitation component (5) generates a magnetic field with a field strength that is continuously adjustable in the range of 0-0.8T.

10. The method for controlling the damping of a long lead screw support according to claim 3, characterized in that, The method further includes: S7. Temperature monitoring and compensation: The temperature value of the support device is monitored in real time by the built-in thermocouple, which is set inside or on the surface of the support block (1); if the temperature value exceeds the preset range, the control module corrects the target excitation current determined in step S4 according to the pre-stored temperature-current compensation coefficient to obtain the compensated target current, or activates the phase change material for thermal management, which is filled in the annular cavity between the constraint block and the support block (1).

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