Elevator head sheave operating parameter adjustment method and system based on radial runout compensation

Abstract

The present application relates to the technical fields of mechanical engineering, and proposes a hoist head sheave operation parameter adjustment method and system based on radial runout compensation, which comprises: collecting radial runout displacement signals and steel wire rope tension signals of the head sheave in real time by using a multi-dimensional sensor array; performing empirical mode decomposition on the radial runout displacement signals to decouple low-frequency eccentric components and high-frequency deformation components of the head sheave; calculating a dynamic load change rate of the head sheave to nonlinearly correct the low-frequency eccentric components and generate a rotational speed adjustment parameter of the head sheave; generating a resonance spectrum of the head sheave, calculating a similarity between the resonance spectrum and a preset standard health spectrum, identifying a resonance main frequency band of the high-frequency deformation components when the similarity is lower than a preset similarity threshold, determining a damping stiffness adjustment parameter of a head sheave bearing seat, and combining the rotational speed adjustment parameter and the damping stiffness adjustment parameter to perform adaptive adjustment on the head sheave. The present application can improve the operation stability of the head sheave system.

Description

Technical Field

[0001] This invention relates to a method and system for adjusting the operating parameters of a hoist sheave based on radial runout compensation, belonging to the field of mechanical engineering technology. Background Technology

[0002] Adjusting the operating parameters of the sheave refers to the process of dynamically optimizing and precisely setting key indicators such as the sheave's speed, tension, braking sensitivity, and lubrication status according to actual working conditions. Its core significance lies in ensuring that the equipment maintains optimal dynamic balance and operational stability under different loads and environmental conditions. This effectively reduces mechanical wear, prevents safety hazards such as overload and derailment, thus extending the equipment's service life, and significantly improves the efficiency and safety of production operations. It is a key means to achieve refined equipment management and ensure the long-term reliable operation of the system.

[0003] Traditional hoist sheave operation parameter adjustments often rely on manual periodic shutdowns for inspection or the use of a single mechanical rigid support. These methods passively address wear by setting fixed parameters, failing to detect dynamic changes online. This approach neglects the nonlinear coupling relationship between sheave tension fluctuations and runout. Single mechanical adjustments are difficult to match complex working conditions, easily leading to resonance and severely restricting the operational stability of the hoist sheave system. Summary of the Invention

[0004] This invention provides a method and system for adjusting the operating parameters of a hoist sheave based on radial runout compensation, the main purpose of which is to improve the operational stability of the sheave system.

[0005] To achieve the above objectives, the present invention provides a method for adjusting the operating parameters of a hoist sheave based on radial runout compensation, comprising:

[0006] The radial runout displacement signal of the sheave and the tension signal of the wire rope are collected in real time using a multi-dimensional sensor array;

[0007] Empirical mode decomposition is performed on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave.

[0008] The dynamic load change rate of the sheave is calculated based on the wire rope tension signal to perform nonlinear correction on the low-frequency eccentricity component and generate the rotational speed adjustment parameters of the sheave.

[0009] Based on the high-frequency deformation components, a resonance spectrum of the celestial disc is generated, and the similarity between the resonance spectrum and a preset standard health spectrum is calculated.

[0010] When the similarity is lower than a preset similarity threshold, the resonant main frequency band of the high-frequency deformation component is identified to determine the damping stiffness adjustment parameter of the sheave bearing seat. Combined with the speed adjustment parameter and the damping stiffness adjustment parameter, adaptive adjustment of the sheave is performed.

[0011] Optionally, based on the high-frequency deformation components, a resonance spectrum of the celestial wheel is generated, including:

[0012] The time-frequency domain power spectrum of the celestial wheel is obtained by performing a short-time Fourier transform on the high-frequency deformation components.

[0013] Identify the local energy peaks in the time-frequency domain power spectrum;

[0014] The resonance spectrum of the celestial wheel is generated based on the local energy peak.

[0015] Optionally, based on the local energy peak, a resonance spectrum of the celestial wheel is generated, including:

[0016] Calculate the signal-to-noise ratio of the local energy peak, and determine the local energy peak with a signal-to-noise ratio greater than a preset threshold as an effective resonance peak, wherein the preset threshold is an adaptive threshold dynamically set according to the background noise level of the celestial wheel;

[0017] Extract the core features of the effective resonance peak, wherein the core features include frequency, energy and occurrence time;

[0018] The resonance spectrum of the celestial wheel is generated using the core features.

[0019] Optionally, the multidimensional sensor array includes:

[0020] Non-contact eddy current displacement sensors are installed along the horizontal and vertical diameter directions of the axial section of the sheave wheel, respectively.

[0021] A piezoelectric accelerometer is installed at the bottom of the sheave bearing housing;

[0022] A pin-type tension sensor is installed at the center of the fixed pulley shaft at the outlet of the sheave rope groove.

[0023] The signal conditioning circuit is provided, and the output terminals of both the eddy current displacement sensor and the piezoelectric accelerometer are connected to the signal conditioning circuit. The signal conditioning circuit has a built-in temperature compensation module.

[0024] Optionally, a multi-dimensional sensor array is used to acquire the radial runout displacement signal of the sheave and the tension signal of the wire rope in real time, including:

[0025] The eddy current displacement sensor is synchronously triggered to acquire the original simulated displacement of the sheave wheel, and the pin-type tension sensor is triggered to acquire the simulated tension of the sheave wheel.

[0026] The temperature coefficient of the sheave wheel is output by the temperature compensation module in the signal conditioning circuit to perform real-time zero-point correction on the original displacement analog quantity, thereby generating the standard displacement signal of the sheave wheel.

[0027] The vibration acceleration auxiliary signal of the sheave is collected by the piezoelectric accelerometer. Based on the vibration acceleration auxiliary signal, the transient interference frequency band introduced by the swing of the sheave wire rope is identified. The standard displacement signal is then adaptively filtered according to the transient interference frequency band to obtain the radial runout displacement signal.

[0028] Meanwhile, the analog tension quantity is differentially amplified and converted into a digital tension signal, which serves as the wire rope tension signal of the sheave.

[0029] Optionally, empirical mode decomposition is performed on the radial runout displacement signal to decouple the low-frequency eccentricity component and high-frequency deformation component of the sheave, including:

[0030] The radial runout displacement signal is decomposed into at least two intrinsic mode function components and one residual component;

[0031] The rotation frequency of the top wheel is determined, and the intrinsic mode function components with a center frequency lower than the rotation frequency and the residual components representing the trend term are merged to obtain the low-frequency eccentric component.

[0032] The intrinsic mode function components with a center frequency not lower than the rotation frequency are defined as the high-frequency deformation components.

[0033] Optionally, the radial runout displacement signal is decomposed into at least two intrinsic mode function components and one residual component, including:

[0034] Extract the local time-scale features of the radial runout displacement signal;

[0035] Based on the local time scale characteristics, the fluctuation modes of different scales in the radial jump displacement signal are separated step by step until the radial jump displacement signal is lower than the preset energy threshold, at least two intrinsic mode function components and one residual component are output respectively.

[0036] Optionally, calculating the dynamic load change rate of the sheave based on the wire rope tension signal includes:

[0037] The wire rope tension signal is constructed as a tension time series that varies with time;

[0038] Perform a difference operation on the tension time series according to a preset time window to calculate the tension change at adjacent sampling times of the tension time series;

[0039] The tension change is standardized per unit time, and the tension change per unit time is defined as the dynamic load change rate of the sheave.

[0040] Optionally, nonlinear correction is applied to the low-frequency eccentricity component to generate the rotational speed adjustment parameters of the sheave wheel, including:

[0041] Extract the peak amplitude of the low-frequency eccentricity component and construct a nonlinear mapping relationship between the peak amplitude and the dynamic load change rate;

[0042] Based on the nonlinear mapping relationship, the correction factor for the low-frequency eccentricity component is calculated;

[0043] The amplitude of the low-frequency eccentricity component is multiplied by the correction factor to obtain the target speed adjustment amount of the sheave, and the speed adjustment parameters of the sheave are generated based on the target speed adjustment amount.

[0044] To address the aforementioned problems, the present invention also provides a hoist sheave operating parameter adjustment system based on radial runout compensation, the system comprising:

[0045] The sheave data acquisition module is used to acquire the radial runout displacement signal and wire rope tension signal of the sheave in real time using a multi-dimensional sensor array;

[0046] The displacement signal decomposition module is used to perform empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave.

[0047] The speed adjustment determination module is used to calculate the dynamic load change rate of the sheave based on the wire rope tension signal, so as to perform nonlinear correction on the low-frequency eccentric component and generate the speed adjustment parameters of the sheave.

[0048] The resonance spectrum construction module is used to generate a resonance spectrum of the celestial disc based on the high-frequency deformation components, and to calculate the similarity between the resonance spectrum and a preset standard health spectrum.

[0049] The damping stiffness adjustment module is used to identify the resonant main frequency band of the high-frequency deformation component when the similarity is lower than a preset similarity threshold, so as to determine the damping stiffness adjustment parameter of the sheave bearing seat, and perform adaptive adjustment of the sheave by combining the speed adjustment parameter and the damping stiffness adjustment parameter.

[0050] This solution uses a multi-dimensional sensor array to perceive the hoist's operating status in real time. It utilizes empirical mode decomposition to precisely decouple the low-frequency eccentricity and high-frequency deformation components of radial runout, and calculates the dynamic load change rate based on wire rope tension to perform nonlinear correction of the low-frequency eccentricity. This generates precise speed adjustment parameters, effectively eliminating the interference of load changes on eccentricity measurement and achieving adaptive optimization control of the hoist's speed. This significantly reduces operating vibration and wear. Simultaneously, it generates a resonance spectrum based on the high-frequency deformation components and compares its similarity with a standard health spectrum. When the similarity is below a threshold, it quickly identifies the dominant resonance frequency band and determines the damping stiffness adjustment parameters, dynamically changing the bearing housing support characteristics to suppress harmful resonance and avoid structural fatigue damage. Through the coordinated adaptive adjustment of speed and damping, it significantly improves the hoist's hoist's operating stability, safety, and equipment lifespan under complex working conditions, achieving intelligent, precise maintenance and energy saving. Attached Figure Description

[0051] Figure 1 This is a flowchart illustrating a method for adjusting the operating parameters of a hoist sheave based on radial runout compensation, according to an embodiment of the present invention.

[0052] Figure 2 This is a multi-dimensional sensor array structure diagram of a hoist sheave operating parameter adjustment system based on radial runout compensation provided in an embodiment of the present invention;

[0053] Figure 3 This is a functional block diagram of a hoist sheave operating parameter adjustment system based on radial runout compensation provided in an embodiment of the present invention;

[0054] Figure 4 A schematic diagram of a computer device for adjusting the operating parameters of a hoist sheave based on radial runout compensation, according to an embodiment of the present invention;

[0055] The objectives, features, and advantages of this invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0056] It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0057] This application provides a method for adjusting the operating parameters of a hoist sheave based on radial runout compensation. The executing entity of this method includes, but is not limited to, at least one of the following electronic devices that can be configured to execute the method provided in this application: a server, a terminal, etc. In other words, the method for adjusting the operating parameters of a hoist sheave based on radial runout compensation can be executed by software or hardware installed on a terminal device or a server device. The server includes, but is not limited to, a single server, a server cluster, a cloud server, or a cloud server cluster.

[0058] Reference Figure 1 The diagram shown is a flowchart illustrating a method for adjusting the operating parameters of a hoist sheave based on radial runout compensation according to an embodiment of the present invention. In this embodiment, the method for adjusting the operating parameters of a hoist sheave based on radial runout compensation includes:

[0059] S1. Real-time acquisition of radial runout displacement signal of the sheave and wire rope tension signal using a multi-dimensional sensor array.

[0060] This invention utilizes a multi-dimensional sensor array to collect radial runout displacement signals and wire rope tension signals of the sheave in real time, which can accurately capture the dynamic characteristics of the sheave under complex load changes, effectively eliminate the detection error of a single sensor, and significantly improve the signal-to-noise ratio of the radial runout signal and the reliability of the compensation basis.

[0061] See Figure 2 The diagram shown is a multi-dimensional sensor array structure diagram of a hoist sheave operating parameter adjustment system based on radial runout compensation provided in an embodiment of the present invention. The multi-dimensional sensor array structure diagram includes a non-contact eddy current displacement sensor, a piezoelectric acceleration sensor, a pin-type tension sensor, a signal conditioning circuit, and a temperature compensation module.

[0062] Specifically, the multidimensional sensor array includes:

[0063] Non-contact eddy current displacement sensors are installed along the horizontal and vertical diameter directions of the axial section of the sheave wheel, respectively.

[0064] A piezoelectric accelerometer is installed at the bottom of the sheave bearing housing;

[0065] A pin-type tension sensor is installed at the center of the fixed pulley shaft at the outlet of the sheave rope groove.

[0066] The signal conditioning circuit is provided, and the output terminals of both the eddy current displacement sensor and the piezoelectric accelerometer are connected to the signal conditioning circuit. The signal conditioning circuit has a built-in temperature compensation module.

[0067] The non-contact eddy current displacement sensor refers to a displacement measuring device that converts the distance change between the probe and the surface of the measured object into a voltage signal output. The axial section of the sheave refers to a plane section perpendicular to the rotation axis of the sheave and passing through the geometric center of the sheave rim. The piezoelectric accelerometer refers to an inertial sensor that uses the piezoelectric effect of piezoelectric ceramics to convert the mechanical vibration acceleration of the bearing seat into a voltage signal output. The bottom of the sheave bearing seat refers to the rigid mounting position where the lower bottom surface of the sheave bearing seat connects to the support structure. The pin-type tension sensor refers to replacing the fixed pulley shaft with a force-sensitive element with a strain gauge structure. The sheave rope groove outlet refers to the tangential position where the wire rope leaves the sheave groove and hangs downwards. The fixed pulley shaft center position is the geometric axis position of the fixed pulley rotation center. The signal conditioning circuit refers to an electronic circuit module used to filter, amplify, linearize, and convert the weak analog signal output by the sensor into an analog-to-digital signal. The temperature compensation module refers to a hardware circuit integrated into the circuit that corrects the sensor sensitivity coefficient and zero-point offset in real time according to changes in ambient temperature.

[0068] Furthermore, the real-time acquisition of the radial runout displacement signal of the sheave and the wire rope tension signal using a multi-dimensional sensor array includes:

[0069] The eddy current displacement sensor is synchronously triggered to acquire the original simulated displacement of the sheave wheel, and the pin-type tension sensor is triggered to acquire the simulated tension of the sheave wheel.

[0070] The temperature coefficient of the sheave wheel is output by the temperature compensation module in the signal conditioning circuit to perform real-time zero-point correction on the original displacement analog quantity, thereby generating the standard displacement signal of the sheave wheel.

[0071] The vibration acceleration auxiliary signal of the sheave is collected by the piezoelectric accelerometer. Based on the vibration acceleration auxiliary signal, the transient interference frequency band introduced by the swing of the sheave wire rope is identified. The standard displacement signal is then adaptively filtered according to the transient interference frequency band to obtain the radial runout displacement signal.

[0072] Meanwhile, the analog tension quantity is differentially amplified and converted into a digital tension signal, which serves as the wire rope tension signal of the sheave.

[0073] Wherein, the original displacement analog quantity refers to the unprocessed voltage signal output by the eddy current displacement sensor; the tension analog quantity refers to the weak millivolt-level voltage signal output by the pin-type tension sensor; the temperature coefficient refers to the parameter used to characterize the relationship between the sensor output characteristics and temperature changes; the standard displacement signal refers to the normalized electrical signal that, after temperature compensation and zero-point correction, eliminates the nonlinear drift caused by ambient temperature rise and truly reflects the displacement change; the vibration acceleration auxiliary signal refers to the dynamic acceleration time-domain waveform signal that reflects the overall vibration state of the bearing housing and the sheave; the transient interference frequency band refers to the non-stationary short-term high-frequency or specific frequency components caused by the lateral swing or impact of the wire rope extracted from the vibration signal through spectrum analysis; the radial runout displacement signal refers to the displacement data sequence that only reflects the displacement of the geometric center of the sheave rim relative to the rotation center; and the wire rope tension signal refers to the digital quantity characterizing the current tension on the wire rope.

[0074] Optionally, the temperature coefficient of the sheave wheel is output by the temperature compensation module in the signal conditioning circuit to perform real-time zero-point correction on the original displacement analog quantity, and the standard displacement signal of the sheave wheel is generated by calculating the zero-point temperature drift voltage value of the sheave wheel at the current ambient temperature based on the temperature coefficient, and subtracting it from the original displacement analog quantity as a compensation component, thereby eliminating the measurement deviation caused by temperature changes and obtaining the standard displacement signal of the sheave wheel.

[0075] Optionally, the adaptive filtering of the standard displacement signal based on the transient interference frequency band to obtain the radial runout displacement signal is achieved through adaptive notch filtering technology.

[0076] S2. Perform empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and high-frequency deformation component of the sheave.

[0077] This invention performs empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and high-frequency deformation component of the sheave. This effectively separates vibration modes at different time scales, eliminates low-frequency rigid body motion interference caused by the mass eccentricity of the sheave, and extracts high-frequency deformation features that reflect the health status of the sheave structure.

[0078] Specifically, the step of performing empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave includes:

[0079] The radial runout displacement signal is decomposed into at least two intrinsic mode function components and one residual component;

[0080] The rotation frequency of the top wheel is determined, and the intrinsic mode function components with a center frequency lower than the rotation frequency and the residual components representing the trend term are merged to obtain the low-frequency eccentric component.

[0081] The intrinsic mode function components with a center frequency not lower than the rotation frequency are defined as the high-frequency deformation components.

[0082] Wherein, the intrinsic mode function component refers to the intrinsic wave mode used to characterize the vibration of the crown wheel at different time scales, the residual component refers to the reference drift characterizing the crown wheel's jump, the rotational frequency refers to the rotational speed of the crown wheel under the current operating conditions, the center frequency refers to the energy dominant frequency obtained by spectral analysis of the intrinsic mode function component, the low-frequency eccentric component refers to the vibration component whose frequency component is below the rotational frequency, and the high-frequency deformation component refers to the vibration component whose frequency component is at or above the rotational frequency.

[0083] Further, the step of decomposing the radial runout displacement signal into at least two intrinsic mode function components and one residual component includes:

[0084] Extract the local time-scale features of the radial runout displacement signal;

[0085] Based on the local time scale characteristics, the fluctuation modes of different scales in the radial jump displacement signal are separated step by step until the radial jump displacement signal is lower than the preset energy threshold, at least two intrinsic mode function components and one residual component are output respectively.

[0086] The local time scale feature refers to the time interval between adjacent extreme points in the radial jump displacement signal. The wave pattern stepwise separation refers to the signal decomposition process of sequentially extracting high-frequency vibration components, mid-frequency vibration components, and low-frequency trend components from the radial jump displacement signal in order from small to large time scale. The preset energy threshold is a threshold value used to determine the termination of signal decomposition.

[0087] S3. Calculate the dynamic load change rate of the sheave based on the wire rope tension signal to perform nonlinear correction on the low-frequency eccentricity component and generate the rotational speed adjustment parameters of the sheave.

[0088] This invention calculates the dynamic load change rate of the sheave based on the wire rope tension signal, which can quantify the intensity of load fluctuations on the sheave in real time, effectively distinguishing between stable loads during normal operation and sudden loads caused by jamming or impact, and providing key mechanical state indicators for fatigue damage assessment and early fault warning of the sheave.

[0089] Specifically, the calculation of the dynamic load change rate of the sheave based on the wire rope tension signal includes:

[0090] The wire rope tension signal is constructed as a tension time series that varies with time;

[0091] Perform a difference operation on the tension time series according to a preset time window to calculate the tension change at adjacent sampling times of the tension time series;

[0092] The tension change is standardized per unit time, and the tension change per unit time is defined as the dynamic load change rate of the sheave.

[0093] The tension time series refers to a set of discrete wire rope tension values ​​arranged in chronological order, used to characterize the dynamic fluctuation process of wire rope tension over time. The preset time window refers to a local time span selected on the time series for differential calculation. The differential operation refers to the mathematical operation of calculating the difference between two adjacent sampling points in the tension time series. The tension change refers to the tension difference obtained after differential operation. The standardization process refers to the process of mapping the discrete tension change to the change amplitude per unit time. The dynamic load change rate refers to the rate of change of wire rope tension per unit time.

[0094] Optionally, the preset time window can be set as a multiple of the rotation period of the sheave wheel, and the standardization process is obtained by dividing the tension change by the time interval between adjacent sampling times.

[0095] This invention performs nonlinear correction on the low-frequency eccentricity component to generate the rotational speed adjustment parameters of the sheave. This effectively eliminates the interference of the dynamic tension fluctuation of the wire rope on the eccentricity detection of the sheave, ensuring that the rotational speed adjustment parameters can accurately adapt to the actual imbalance state of the sheave, thereby avoiding over-adjustment of the rotational speed due to sudden load changes.

[0096] Specifically, the nonlinear correction of the low-frequency eccentricity component to generate the rotational speed adjustment parameters of the sheave wheel includes:

[0097] Extract the peak amplitude of the low-frequency eccentricity component and construct a nonlinear mapping relationship between the peak amplitude and the dynamic load change rate;

[0098] Based on the nonlinear mapping relationship, the correction factor for the low-frequency eccentricity component is calculated;

[0099] The amplitude of the low-frequency eccentricity component is multiplied by the correction factor to obtain the target speed adjustment amount of the sheave, and the speed adjustment parameters of the sheave are generated based on the target speed adjustment amount.

[0100] Wherein, the peak amplitude refers to the maximum amplitude of the vibration displacement signal deviating from the baseline within one complete fluctuation cycle of the low-frequency eccentric component; the nonlinear mapping relationship refers to the coupling influence law used to describe the dynamic load change rate on the eccentric amplitude; the correction factor refers to the dimensionless coefficient for weighted adjustment of the original low-frequency eccentric component amplitude; the target speed adjustment amount refers to the speed correction value obtained after weighted calculation by the correction factor; and the speed adjustment parameter includes the control command data of the target speed adjustment amount and its adjustment direction.

[0101] Further, calculating the correction factor for the low-frequency eccentricity component based on the nonlinear mapping relationship includes:

[0102] Based on the nonlinear mapping relationship, a nonlinear correction function for the low-frequency eccentricity component is constructed;

[0103] The correction factor for the low-frequency eccentricity component is calculated using the aforementioned nonlinear correction function, wherein the nonlinear correction function is:

[0104]

[0105] in, Indicates the correction factor. Indicates the dynamic load change rate. This indicates the preset load fluctuation threshold. This represents the sensitivity coefficient for controlling the decay rate.

[0106] The load fluctuation threshold refers to a pre-set critical value for the dynamic load change rate, used to distinguish between normal load fluctuations and abnormal load mutations during the operation of the sheave. Specifically, the load fluctuation threshold can be obtained by collecting a large amount of dynamic load change rate data of the sheave under normal operating conditions and performing statistical analysis. The sensitivity coefficient refers to a parameter used to control the steepness of the response of the nonlinear correction function, which can be obtained by analysis using a fuzzy logic adaptive algorithm.

[0107] S4. Based on the high-frequency deformation components, generate the resonance spectrum of the celestial wheel, and calculate the similarity between the resonance spectrum and the preset standard health spectrum.

[0108] Based on the high-frequency deformation components, this invention generates a resonance spectrum of the celestial wheel, which can identify and quantify dangerous resonance frequency points that may occur during the operation of the celestial wheel system, providing a key basis for the active safety control of the celestial wheel.

[0109] Specifically, generating the resonance spectrum of the celestial wheel based on the high-frequency deformation components includes:

[0110] The time-frequency domain power spectrum of the celestial wheel is obtained by performing a short-time Fourier transform on the high-frequency deformation components.

[0111] Identify the local energy peaks in the time-frequency domain power spectrum;

[0112] The resonance spectrum of the celestial wheel is generated based on the local energy peak.

[0113] The short-time Fourier transform refers to a Fourier transform method used to divide the high-frequency deformation component into multiple short-time frames for frequency domain analysis. The time-frequency power spectrum is a two-dimensional matrix that characterizes the signal energy distribution. The local energy peak refers to the coordinate point in the time-frequency power spectrum where the energy amplitude reaches its maximum value within a preset time-frequency neighborhood. The resonance spectrum refers to a visual chart reflecting the resonance state of the celestial wheel.

[0114] Furthermore, generating the resonance spectrum of the celestial wheel based on the local energy peak includes:

[0115] Calculate the signal-to-noise ratio of the local energy peak, and determine the local energy peak with a signal-to-noise ratio greater than a preset threshold as an effective resonance peak, wherein the preset threshold is an adaptive threshold dynamically set according to the background noise level of the celestial wheel;

[0116] Extract the core features of the effective resonance peak, wherein the core features include frequency, energy and occurrence time;

[0117] The resonance spectrum of the celestial wheel is generated using the core features.

[0118] Wherein, the signal-to-noise ratio (SNR) is used to characterize the significance of the peak signal; the preset threshold is used to filter the critical SNR value of the effective signal; the effective resonance peak refers to the local energy peak where the SNR exceeds the preset threshold; the background noise level refers to the broadband random vibration energy reference generated by the celestial wheel in a non-resonant state; the frequency refers to the position parameter of the effective resonance peak on the spectrum, corresponding to the vibration frequency when the celestial wheel resonates; the energy refers to the power spectral amplitude of the effective resonance peak, reflecting the vibration intensity when resonance occurs; and the occurrence time refers to the position parameter of the effective resonance peak on the time axis, recording the specific moment when the resonance phenomenon occurs.

[0119] Optionally, the signal-to-noise ratio is obtained by the ratio of the amplitude of the local energy peak to the average amplitude of the background noise in the neighborhood surrounding the local energy peak.

[0120] This invention calculates the similarity between the resonance spectrum and the preset standard health spectrum, enabling an intuitive and accurate assessment of the deviation of the current operating state of the sheave from a health benchmark, thereby achieving early warning of potential faults. The standard health spectrum refers to the resonance spectrum generated by collecting and processing high-frequency deformation components under standard operating conditions allowed by design (e.g., standard speed, rated load, and no structural defects). The similarity is a quantitative indicator characterizing the consistency between the measured resonance spectrum and the standard health spectrum in the frequency distribution position and energy intensity distribution of the resonance peaks. Specifically, the similarity can be obtained by aligning the resonance spectrum and the standard health spectrum along their time axes, extracting feature vector sequences, and then calculating the weighted cosine similarity of the feature vector sequences.

[0121] S5. When the similarity is lower than the preset similarity threshold, the resonant main frequency band of the high-frequency deformation component is identified to determine the damping stiffness adjustment parameter of the sheave bearing seat. Combined with the speed adjustment parameter and the damping stiffness adjustment parameter, adaptive adjustment of the sheave is performed.

[0122] When the similarity is lower than a preset similarity threshold, the present invention identifies the resonant main frequency band of the high-frequency deformation component to determine the damping stiffness adjustment parameter of the sheave bearing seat when the sheave operation state is abnormal. By accurately locating the resonant main frequency band, the present invention provides a quantitative basis for the dynamic adjustment of the damping stiffness, thereby enabling targeted active vibration reduction control, quickly suppressing resonance and restoring system stability.

[0123] Optionally, when the similarity is lower than a preset similarity threshold, the resonant main frequency band of the high-frequency deformation component can be identified by extracting the frequency domain interval with the largest and continuously distributed energy amplitude in the resonance spectrum after determining the similarity to be abnormal, and determining the frequency range corresponding to the interval as the resonant main frequency band.

[0124] The resonant main frequency band refers to the frequency range in the resonant spectrum where the energy amplitude is significantly higher than the surrounding frequency bands and is continuously distributed. The similarity threshold refers to the critical similarity value used to determine whether the operation state of the celestial wheel is abnormal.

[0125] Optionally, determining the damping stiffness adjustment parameters of the sheave bearing housing involves matching the center frequency of the identified resonant main frequency band with a preset frequency-stiffness mapping table to obtain the target damping coefficient and stiffness correction value that match the current resonant frequency, which are then used as the damping stiffness adjustment parameters.

[0126] The frequency-stiffness mapping table refers to a pre-stored data table showing the correspondence between resonant frequencies and bearing seat damping and stiffness adjustment parameters. It is established based on the dynamic model and experimental calibration data of the sheave system. The damping and stiffness adjustment parameters refer to control command data used to adjust the support characteristics of the sheave bearing seat, including target damping coefficients and stiffness correction values.

[0127] Finally, by combining the speed adjustment parameters and the damping stiffness adjustment parameters, the present invention performs adaptive adjustment of the sheave. By avoiding the resonance frequency through speed adjustment and suppressing the vibration amplitude through damping stiffness adjustment, the present invention achieves dual active control of the sheave resonance. While ensuring rapid departure from the resonance zone, it effectively reduces vibration energy, thereby significantly improving the safety and stability of the sheave operation.

[0128] like Figure 3 The diagram shown is a functional block diagram of the hoist sheave operating parameter adjustment system based on radial runout compensation according to the present invention.

[0129] The hoist sheave operating parameter adjustment system 300 based on radial runout compensation described in this invention can be installed in an electronic device. Depending on the functions implemented, the hoist sheave operating parameter adjustment system based on radial runout compensation includes a sheave data acquisition module 301, a displacement signal decomposition module 302, a speed adjustment determination module 303, a resonance spectrum construction module 304, and a damping stiffness adjustment module 305. The module described in this invention can also be called a unit, referring to a series of computer program segments that can be executed by the processor of an electronic device and perform a fixed function, stored in the memory of the electronic device.

[0130] In this embodiment of the invention, the functions of each module / unit are as follows:

[0131] The battery data acquisition module 201 is used to acquire the bus voltage data and branch-to-ground current sampling data of the battery Pack system under charging and discharging conditions in real time.

[0132] The response signal determination module 202 is used to inject a multi-frequency AC detection signal containing at least two different frequency components into the high-voltage circuit of the battery Pack system, and to collect the response signal of the branch to the multi-frequency AC detection signal.

[0133] The capacitance calculation module 203 is used to calculate the ground insulation resistance value and real-time ground stray capacitance value of the branch based on the response signal.

[0134] The fault current feature generation module 204 is used to calculate the capacitive leakage current component caused by the change in operating conditions using the real-time stray capacitance value to ground, and to separate the capacitive leakage current component from the current sampling data of the branch to ground, thereby obtaining the pure resistive fault current feature after filtering out dynamic interference.

[0135] The insulation fault location module 205 is used to establish a potential distribution model of the battery pack system based on the bus voltage data, calculate the insulation degradation degree of the branch in combination with the pure resistive fault current characteristics, and locate the specific branch location where the insulation fault of the battery pack system occurs based on the extreme point of the insulation degradation degree in the potential distribution model when an insulation fault is detected.

[0136] In detail, the modules in the hoist sheave operating parameter adjustment system 300 based on radial runout compensation described in this embodiment of the invention adopt the same characteristics as described above during use. Figure 1 The method described above uses the same technique as the method for adjusting the hoist sheave operating parameters based on radial runout compensation, and can produce the same technical effect, so it will not be repeated here.

[0137] In one embodiment, a computer device is provided, which may be a server or a client, and its internal structure diagram may be as follows: Figure 4 As shown. The computer device includes a processor, memory, network interface, and database connected via a system bus. The processor provides computing and control capabilities. The memory includes non-volatile and / or volatile storage media and internal memory. The non-volatile storage media stores the operating system, computer programs, and database. The internal memory provides an environment for the operation of the operating system and computer programs in the non-volatile storage media. The network interface is used for communication with external clients via a network connection. When the computer program is executed by the processor, it implements the functions or steps of the server-side or client-side method for adjusting the operating parameters of the hoist sheave based on radial runout compensation.

[0138] In one embodiment, a computer device is provided, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to perform the following steps:

[0139] The sheave data acquisition module is used to acquire the radial runout displacement signal and wire rope tension signal of the sheave in real time using a multi-dimensional sensor array;

[0140] The displacement signal decomposition module is used to perform empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave.

[0141] The speed adjustment determination module is used to calculate the dynamic load change rate of the sheave based on the wire rope tension signal, so as to perform nonlinear correction on the low-frequency eccentric component and generate the speed adjustment parameters of the sheave.

[0142] The resonance spectrum construction module is used to generate a resonance spectrum of the celestial disc based on the high-frequency deformation components, and to calculate the similarity between the resonance spectrum and a preset standard health spectrum.

[0143] The damping stiffness adjustment module is used to identify the resonant main frequency band of the high-frequency deformation component when the similarity is lower than a preset similarity threshold, so as to determine the damping stiffness adjustment parameter of the sheave bearing seat, and perform adaptive adjustment of the sheave by combining the speed adjustment parameter and the damping stiffness adjustment parameter.

[0144] In one embodiment, a computer-readable storage medium is provided having a computer program stored thereon, the computer program performing the following steps when executed by a processor:

[0145] The sheave data acquisition module is used to acquire the radial runout displacement signal and wire rope tension signal of the sheave in real time using a multi-dimensional sensor array;

[0146] The displacement signal decomposition module is used to perform empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave.

[0147] The speed adjustment determination module is used to calculate the dynamic load change rate of the sheave based on the wire rope tension signal, so as to perform nonlinear correction on the low-frequency eccentric component and generate the speed adjustment parameters of the sheave.

[0148] The resonance spectrum construction module is used to generate a resonance spectrum of the celestial disc based on the high-frequency deformation components, and to calculate the similarity between the resonance spectrum and a preset standard health spectrum.

[0149] The damping stiffness adjustment module is used to identify the resonant main frequency band of the high-frequency deformation component when the similarity is lower than a preset similarity threshold, so as to determine the damping stiffness adjustment parameter of the sheave bearing seat, and perform adaptive adjustment of the sheave by combining the speed adjustment parameter and the damping stiffness adjustment parameter.

[0150] It should be noted that the functions or steps that can be implemented by the computer-readable storage medium or computer device described above can be referred to the relevant descriptions on the server side and client side in the foregoing method embodiments. To avoid repetition, they will not be described one by one here.

[0151] Those skilled in the art will understand that all or part of the processes in the methods of the above embodiments can be implemented by a computer program instructing related hardware. The computer program can be stored in a non-volatile computer-readable storage medium. When executed, the computer program can include the processes of the embodiments of the above methods. Any references to memory, storage, databases, or other media used in the embodiments provided in this application can include non-volatile and / or volatile memory. Non-volatile memory may include read-only memory (ROM), programmable ROM (PROM), electrically programmable ROM (EPROM), electrically erasable programmable ROM (EEPROM), or flash memory. Volatile memory may include random access memory (RAM) or external cache memory. By way of illustration and not limitation, RAM is available in a variety of forms, such as static RAM (SRAM), dynamic RAM (DRAM), synchronous DRAM (SDRAM), dual data rate SDRAM (DDRSDRAM), enhanced SDRAM (ESDRAM), synchronous link DRAM (SLDRAM), RAMbus direct RAM (RDRAM), direct memory bus dynamic RAM (DRDRAM), and memory bus dynamic RAM (RDRAM), etc.

[0152] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the above-described division of functional units and modules is used as an example. In practical applications, the above functions can be assigned to different functional units and modules as needed, that is, the internal structure of the device can be divided into different functional units or modules to complete all or part of the functions described above.

[0153] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the present invention.

[0154] Finally, it should be noted that in the above embodiments, each embodiment can be combined with each other or independent. Deleting any one of them will not affect the technical implementation of other embodiments. The above embodiments are only used to illustrate the technical solutions of the present invention and not to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention.

Claims

1. A method for adjusting the operating parameters of a hoist sheave based on radial runout compensation, characterized in that, The method includes: The radial runout displacement signal of the sheave and the tension signal of the wire rope are collected in real time using a multi-dimensional sensor array; Empirical mode decomposition is performed on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave. The dynamic load change rate of the sheave is calculated based on the wire rope tension signal to perform nonlinear correction on the low-frequency eccentricity component and generate the rotational speed adjustment parameters of the sheave. Based on the high-frequency deformation components, a resonance spectrum of the celestial disc is generated, and the similarity between the resonance spectrum and a preset standard health spectrum is calculated. When the similarity is lower than a preset similarity threshold, the resonant main frequency band of the high-frequency deformation component is identified to determine the damping stiffness adjustment parameter of the sheave bearing seat. Combined with the speed adjustment parameter and the damping stiffness adjustment parameter, adaptive adjustment of the sheave is performed.

2. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 1, characterized in that, Based on the high-frequency deformation components, the resonance spectrum of the celestial wheel is generated, including: The time-frequency domain power spectrum of the celestial wheel is obtained by performing a short-time Fourier transform on the high-frequency deformation components. Identify the local energy peaks in the time-frequency domain power spectrum; The resonance spectrum of the celestial wheel is generated based on the local energy peak.

3. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 2, characterized in that, Based on the local energy peak, a resonance spectrum of the celestial wheel is generated, including: Calculate the signal-to-noise ratio of the local energy peak, and determine the local energy peak with a signal-to-noise ratio greater than a preset threshold as an effective resonance peak, wherein the preset threshold is an adaptive threshold dynamically set according to the background noise level of the celestial wheel; Extract the core features of the effective resonance peak, wherein the core features include frequency, energy and occurrence time; The resonance spectrum of the celestial wheel is generated using the core features.

4. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 1, characterized in that, Multidimensional sensor array, including: Non-contact eddy current displacement sensors are installed along the horizontal and vertical diameter directions of the axial section of the sheave wheel, respectively. A piezoelectric accelerometer is installed at the bottom of the sheave bearing housing; A pin-type tension sensor is installed at the center of the fixed pulley shaft at the outlet of the sheave rope groove. The signal conditioning circuit is provided, and the output terminals of both the eddy current displacement sensor and the piezoelectric accelerometer are connected to the signal conditioning circuit. The signal conditioning circuit has a built-in temperature compensation module.

5. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 1, characterized in that, The radial runout displacement signal of the sheave and the tension signal of the wire rope are acquired in real time using a multi-dimensional sensor array, including: The eddy current displacement sensor is synchronously triggered to acquire the original simulated displacement of the sheave wheel, and the pin-type tension sensor is triggered to acquire the simulated tension of the sheave wheel. The temperature coefficient of the sheave wheel is output by the temperature compensation module in the signal conditioning circuit to perform real-time zero-point correction on the original displacement analog quantity, thereby generating the standard displacement signal of the sheave wheel. The vibration acceleration auxiliary signal of the sheave is collected by the piezoelectric accelerometer. Based on the vibration acceleration auxiliary signal, the transient interference frequency band introduced by the swing of the sheave wire rope is identified. The standard displacement signal is then adaptively filtered according to the transient interference frequency band to obtain the radial runout displacement signal. Meanwhile, the analog tension quantity is differentially amplified and converted into a digital tension signal, which serves as the wire rope tension signal of the sheave.

6. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 1, characterized in that, Empirical mode decomposition is performed on the radial runout displacement signal to decouple the low-frequency eccentricity component and high-frequency deformation component of the sheave, including: The radial runout displacement signal is decomposed into at least two intrinsic mode function components and one residual component; The rotation frequency of the top wheel is determined, and the intrinsic mode function components with a center frequency lower than the rotation frequency and the residual components representing the trend term are merged to obtain the low-frequency eccentric component. The intrinsic mode function components with a center frequency not lower than the rotation frequency are defined as the high-frequency deformation components.

7. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 6, characterized in that, The radial runout displacement signal is decomposed into at least two intrinsic mode function components and one residual component, including: Extract the local time-scale features of the radial runout displacement signal; Based on the local time scale characteristics, the fluctuation modes of different scales in the radial jump displacement signal are separated step by step until the radial jump displacement signal is lower than the preset energy threshold, at least two intrinsic mode function components and one residual component are output respectively.

8. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 1, characterized in that, The dynamic load change rate of the sheave is calculated based on the wire rope tension signal, including: The wire rope tension signal is constructed as a tension time series that varies with time; Perform a difference operation on the tension time series according to a preset time window to calculate the tension change at adjacent sampling times of the tension time series; The tension change is standardized per unit time, and the tension change per unit time is defined as the dynamic load change rate of the sheave.

9. The method for adjusting the operating parameters of a hoist sheave based on radial runout compensation as described in claim 1, characterized in that, The low-frequency eccentricity component is nonlinearly corrected to generate the rotational speed adjustment parameters of the sheave wheel, including: Extract the peak amplitude of the low-frequency eccentricity component and construct a nonlinear mapping relationship between the peak amplitude and the dynamic load change rate; Based on the nonlinear mapping relationship, the correction factor for the low-frequency eccentricity component is calculated; The amplitude of the low-frequency eccentricity component is multiplied by the correction factor to obtain the target speed adjustment amount of the sheave, and the speed adjustment parameters of the sheave are generated based on the target speed adjustment amount.

10. A hoist sheave operating parameter adjustment system based on radial runout compensation, characterized in that, The system is used to perform the hoist sheave operating parameter adjustment method based on radial runout compensation as described in any one of claims 1-9, the system comprising: The sheave data acquisition module is used to acquire the radial runout displacement signal and wire rope tension signal of the sheave in real time using a multi-dimensional sensor array; The displacement signal decomposition module is used to perform empirical mode decomposition on the radial runout displacement signal to decouple the low-frequency eccentricity component and the high-frequency deformation component of the sheave. The speed adjustment determination module is used to calculate the dynamic load change rate of the sheave based on the wire rope tension signal, so as to perform nonlinear correction on the low-frequency eccentric component and generate the speed adjustment parameters of the sheave. The resonance spectrum construction module is used to generate a resonance spectrum of the celestial disc based on the high-frequency deformation components, and to calculate the similarity between the resonance spectrum and a preset standard health spectrum. The damping stiffness adjustment module is used to identify the resonant main frequency band of the high-frequency deformation component when the similarity is lower than a preset similarity threshold, so as to determine the damping stiffness adjustment parameter of the sheave bearing seat, and perform adaptive adjustment of the sheave by combining the speed adjustment parameter and the damping stiffness adjustment parameter.

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