A high-precision spindle performance testing method and system

Abstract

The present invention relates to the technical field of machine tool spindle performance testing, and in particular to a high-precision spindle performance testing method and system. The method comprises: initializing a mirror prototype of the spindle in a performance testing platform according to the main structure of the spindle shaft and the working environment constraints; establishing a load control instruction set based on the mirror prototype and the motion state of the spindle shaft in a composite performance testing scenario; performing dynamic perturbations on the spindle shaft according to the load control instruction set, and capturing the performance change characteristics of the shaft during the perturbation process; combining the performance change characteristics with the mirror prototype, performing self-organized calibration of the prototype parameters of the spindle shaft, and generating an enhanced mirror body with working condition adaptability; recalculating the load control instruction set based on the enhanced mirror body, triggering dynamic perturbations of multi-axis linkage, and outputting performance test results. Through the present invention, the real-time mismatch problem between spindle performance simulation and measured data under high-load conditions is effectively solved.

Description

Technical Field

[0001] The present invention relates to the technical field of machine tool spindle performance testing, and in particular to a high-precision spindle performance testing method and system. Background Art

[0002] As a core component of high-end CNC machine tools, dynamic performance testing of high-precision spindles is crucial to ensuring machining accuracy. Traditional testing methods rely primarily on the combination of finite element simulation models and physical testing platforms. These methods apply a preset load spectrum based on a simple geometric model to simulate actual operating conditions, and collect response data such as vibration and temperature rise to evaluate performance. However, with the prevalence of complex operating conditions such as high-speed cutting and heavy-load intermittent machining, existing technologies have revealed that static simulation models are difficult to adapt to the dynamic response evolution during continuously varying loads.

[0003] Specifically, because the material properties in the simulation model (such as elastic modulus and thermal expansion coefficient) usually use fixed empirical values ​​and the boundary conditions are set to an ideal constant state, when the spindle experiences dynamic disturbances such as speed jumps and load mutations, nonlinear factors such as the material's thermo-mechanical coupling effect and damping frequency-varying characteristics cause time-varying deviations between the theoretical response and the actual measured value. In particular, when the test duration exceeds the critical threshold, the cumulative error in thermal deformation and the mismatch in vibration harmonics will form a positive feedback loop, causing the simulation results to completely deviate from the actual physical behavior. At this time, the test must be interrupted, and the model parameters must be adjusted before re-running. This not only destroys the continuity of the dynamic test, but also fails to capture the true performance boundaries under transient mutation conditions.

[0004] The information disclosed in this background technology section is only intended to deepen the understanding of the overall background technology of the present disclosure and should not be regarded as an admission or any form of suggestion that the information constitutes the prior art known to those skilled in the art. Summary of the Invention

[0005] The present invention provides a high-precision spindle performance testing method and system, which can effectively solve the problems in the background technology.

[0006] In order to achieve the above object, the technical solution adopted by the present invention is:

[0007] A high-precision spindle performance testing method, the method comprising:

[0008] Initialize the spindle's mirror prototype in the performance test platform based on the spindle's main structure and working environment constraints;

[0009] Establishing a load control instruction set according to the mirror prototype and based on the motion state of the spindle shaft in a composite performance test scenario;

[0010] According to the load control instruction set, dynamic perturbation is performed on the main shaft body, and the performance change characteristics of the shaft body are captured during the perturbation process;

[0011] Combining the performance change characteristics with the mirror prototype, performing self-organized calibration of the prototype parameters of the main shaft body, and generating an enhanced mirror body with adaptability to working conditions;

[0012] The load control instruction set is recalculated based on the enhanced mirror body, the dynamic disturbance of the multi-axis linkage is triggered, and the performance detection result is output.

[0013] Furthermore, performing dynamic perturbation on the main shaft includes:

[0014] The load control instruction set is decomposed into a multi-axis linkage control signal group, wherein the control signal group includes:

[0015] A dynamic speed command of the spindle rotating shaft system, dynamically adjusting the speed gradient based on the predicted value of the thermal deformation of the spindle in the mirror prototype;

[0016] A broadband excitation waveform for a radially loaded shafting generates a vibration spectrum containing multi-order harmonic components according to the critical flutter frequency distribution of the enhanced mirror body;

[0017] A deformation compensation signal of the axially loaded shaft system, adjusting the loading phase according to the real-time strain data feedback in the performance change characteristics;

[0018] Among them, each axial control signal cooperates with the coupling control to execute the dynamic disturbance of the main shaft.

[0019] Furthermore, adjusting the loading phase according to the real-time strain data feedback in the performance change characteristics includes:

[0020] Capturing the real-time strain data by multi-dimensional partitioning, wherein the partitions are parallel mapped to the strain-sensitive areas of the mirror prototype;

[0021] Calculating the phase offset of the axially loaded shaft system based on the strain gradient of the partition and in association with the thermal expansion anisotropy weight in the enhanced mirror body;

[0022] generating a dynamic compensation parameter according to the phase offset, wherein the dynamic compensation parameter is inversely correlated with a material yield strength threshold of the mirror prototype;

[0023] The dynamic compensation coefficient is superimposed on the carrier frequency of the deformation compensation signal to generate an axial loading waveform with a phase pre-compensation characteristic.

[0024] Furthermore, dynamically adjusting the speed gradient based on the predicted value of thermal deformation of the spindle in the mirror prototype includes:

[0025] The thermal deformation prediction value is axially partitioned based on the material thermal conductivity anisotropy distribution map of the main axis in the mirror prototype;

[0026] Calculate the speed gradient change rate of the main shaft rotating shaft system according to the thermal deformation difference of the axial partition and in association with the thermal equilibrium time constant of the enhanced mirror body;

[0027] generating a stepped speed adjustment instruction based on the speed gradient change rate, wherein the step interval of the adjustment instruction is inversely correlated with the temperature rise mutation threshold in the performance detection result;

[0028] The step-shaped speed adjustment instruction is embedded in the transition interval of the dynamic speed instruction, so that the spindle speed approaches the target value in sections within a preset thermal deformation difference range.

[0029] Furthermore, generating a vibration spectrum containing multi-order harmonic components according to the critical flutter frequency distribution of the enhanced mirror body includes:

[0030] Dividing the critical flutter frequency distribution into a plurality of resonance sensitive areas according to frequency bands, and mapping the resonance sensitive areas to the structural modal parameters in the enhanced mirror body;

[0031] Obtaining an amplitude weight of a corresponding harmonic component according to the modal energy proportion of each resonance sensitive area, wherein the amplitude weight is associated with a vibration suppression threshold in the performance test result;

[0032] synthesizing a time series of multiple harmonics based on the amplitude weights, wherein the phase interval of the time series is inversely correlated with the damping ratio of the spindle material in the mirror prototype;

[0033] The time series is superimposed on the fundamental frequency component of the broadband excitation waveform to generate a target vibration spectrum with modal suppression characteristics.

[0034] Furthermore, the mirror prototype of the spindle is initialized in the performance test platform, including:

[0035] Generate a parametric geometric model based on the three-dimensional structural topology data of the spindle shaft, wherein the parametric geometric model includes the moment of inertia distribution of each cross section of the spindle and the positioning parameters of the bearing support points;

[0036] Loading a material property set into the parameterized geometric model, the material property set including anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the spindle material;

[0037] Injecting boundary conditions according to the working environment constraints, the boundary conditions including temperature gradient field distribution and dynamic load spectrum;

[0038] performing coupled solution on the parameterized geometric model, the material property set, and the boundary conditions to generate an initial mirror prototype;

[0039] During the test process, the material property set of the initial mirror prototype is updated through real-time data assimilation according to the performance change characteristics to form the dynamically evolving mirror prototype.

[0040] Furthermore, performing coupled solution on the parameterized geometric model, the material property set, and the boundary condition includes:

[0041] Performing finite element solution on the parameterized geometric model to generate a structural grid model including a node stiffness matrix, and mapping the material property set in the structural grid model;

[0042] Performing transient heat transfer analysis based on the temperature gradient field distribution to calculate the nonlinear thermal deformation field of the spindle shaft under the action of thermal load;

[0043] The nonlinear thermal deformation field is used as an initial displacement condition and combined with the dynamic load spectrum to solve the dynamic stress distribution of the main shaft under the combined load;

[0044] Iteratively correcting the stiffness matrix of the corresponding node in the structural grid model according to the frequency domain response relationship between the dynamic stress distribution and the damping ratio frequency-varying characteristic;

[0045] When the residual norm of the modified node stiffness matrix is ​​less than a preset convergence threshold, the initial mirror prototype is output.

[0046] Furthermore, an enhanced mirror body with adaptability to working conditions is generated, including:

[0047] The performance change characteristics are compared with the theoretical response characteristics of the mirror prototype in multiple dimensions to extract three types of difference parameters: vibration amplitude-frequency characteristics, thermal deformation displacement deviation, and dynamic stress residual;

[0048] generating a frequency domain residual energy spectrum based on the difference parameters, and calculating a correction gradient of the main shaft material property set according to the amplitude envelope and phase offset angle of the energy spectrum;

[0049] Coordinately adjusting the anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-varying characteristics of the mirror prototype so that the correlation coefficient between the theoretical response characteristics of the mirror prototype and the performance variation characteristics reaches a preset matching threshold;

[0050] Verify the dynamic response accuracy of the adjusted mirror prototype to the multi-axis coupled load within the load mutation time window of the dynamic disturbance, and recalculate the correction gradient if the axial runout prediction error exceeds the tolerance range;

[0051] When the deviations between the predicted and measured contact stiffness tensors of the mirror prototype in at least three orthogonal directions are all less than a set tolerance, the material property set and boundary conditions of the current mirror prototype are locked to generate the enhanced mirror body.

[0052] A high-precision spindle performance testing system, comprising:

[0053] The mirror spindle module initializes the mirror prototype of the spindle in the performance test platform according to the main structure of the spindle body and the working environment constraints;

[0054] The instruction establishment module establishes a load control instruction set based on the mirror prototype and the motion state of the spindle in a composite performance test scenario;

[0055] The dynamic perturbation module performs dynamic perturbations on the main shaft according to the load control instruction set and captures the performance change characteristics of the shaft during the perturbation process;

[0056] The organization calibration module combines the performance change characteristics with the mirror prototype, performs self-organization calibration of the prototype parameters of the main axis body, and generates an enhanced mirror body with adaptability to working conditions;

[0057] The performance detection module recalculates the load control instruction set based on the enhanced mirror body, triggers the dynamic disturbance of multi-axis linkage, and outputs the performance detection results.

[0058] Furthermore, the mirror spindle module includes:

[0059] A geometric modeling unit generates a parametric geometric model based on the three-dimensional structural topology data of the spindle body. The parametric geometric model includes the moment of inertia distribution of each cross section of the spindle and the positioning parameters of the bearing support points;

[0060] A property loading unit is used to load a material property set into a parametric geometric model. The material property set includes the anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the spindle material.

[0061] Working condition constraint unit, which injects boundary conditions according to working condition environment constraints. The boundary conditions include temperature gradient field distribution and dynamic load spectrum;

[0062] A prototype generation unit performs coupled solution on the parameterized geometric model, material property set and boundary conditions to generate an initial mirror prototype;

[0063] During the test, the dynamic evolution unit performs real-time data assimilation and updates on the material property set of the initial mirror prototype according to the performance change characteristics to form a dynamically evolving mirror prototype.

[0064] The technical solution of the present invention can achieve the following technical effects:

[0065] Through the mirror prototype closed-loop calibration mechanism driven by dynamic disturbance characteristics, real-time self-optimization of simulation model parameters is achieved without interrupting testing, eliminating the defect of traditional static models that require interruption and intervention due to accumulated errors.

[0066] The above description is only an overview of the technical solution of the present application. In order to more clearly understand the technical means of the present application, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are listed below. BRIEF DESCRIPTION OF THE DRAWINGS

[0067] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments recorded in the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0068] Figure 1 The figure is a flow chart of a high-precision spindle performance testing method;

[0069] Figure 2 Schematic diagram of the process for executing dynamic perturbations;

[0070] Figure 3 A schematic diagram of the process for establishing a spindle mirror prototype;

[0071] Figure 4 Schematic diagram of the process of generating enhanced mirror body. DETAILED DESCRIPTION

[0072] The technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments.

[0073] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which this invention pertains. The terms used in this specification are for the purpose of describing specific embodiments only and are not intended to limit the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0074] Embodiment 1;

[0075] like Figure 1 As shown, the present application provides a high-precision spindle performance testing method, the method comprising:

[0076] S10: Initialize the mirror prototype of the spindle in the performance test platform according to the main structure of the spindle body and the working environment constraints;

[0077] S20: establishing a load control instruction set based on the mirror prototype and the motion state of the spindle in the composite performance test scenario;

[0078] S30: performing dynamic perturbations on the spindle body according to the load control instruction set, and capturing the performance change characteristics of the spindle body during the perturbation process;

[0079] S40: combining the performance change characteristics with the mirror prototype, performing self-organized calibration of the prototype parameters of the main shaft body, and generating an enhanced mirror body with adaptability to working conditions;

[0080] S50: Recalculate the load control instruction set based on the enhanced mirror body, trigger the dynamic disturbance of multi-axis linkage, and output the performance test results.

[0081] Specifically, in the performance test platform, the mirror prototype of the spindle is first initialized based on the main structure of the spindle shaft and the working environment constraints. The mirror prototype refers to a virtual model similar to the spindle shaft, which can represent the dynamic behavior characteristics of the spindle under specific working conditions. The process of establishing this virtual model first requires the use of precise modeling software to digitally reproduce the geometric shape, material properties and working environment of the spindle. Then, a preliminary mirror prototype is built based on the virtual model. This prototype will serve as a reference benchmark for the spindle behavior in subsequent testing processes. Based on the spindle mirror prototype and combined with the motion state of the spindle shaft in a complex performance test scenario, a load control instruction set is constructed. The load control instruction set is an instruction set used to control the spindle to apply specific loads, speeds, vibrations and other external influences during the test. The generation of these instruction sets requires comprehensive consideration of the performance changes of the spindle under different loads and working conditions, especially the response characteristics of the shaft under complex working conditions. By comparing simulation calculations with actual test data, the load control instruction set can accurately simulate the motion behavior of the spindle shaft under specific working conditions. Under the guidance of the load control instruction set, dynamic disturbances are applied to the spindle shaft. Dynamic disturbances refer to the use of external forces or vibration sources to simulate sudden changes, shocks or vibrations that the spindle may encounter in the actual working process. For example, at high speeds, the spindle may be subject to vibration interference from the processing material or other mechanical components, thereby affecting its operating stability. By introducing a simulated disturbance signal into the platform, the spindle will undergo a series of dynamic changes. During this process, the performance change characteristics of the spindle (such as speed, temperature rise, vibration, etc.) will be accurately recorded. The capture of these performance change characteristics helps to identify the working status and potential faults of the spindle under specific loads. Based on the performance change characteristics captured during the dynamic disturbance process, combined with the initially established mirror prototype, a self-organizing calibration of the prototype parameters of the spindle axis body will be performed. The self-organizing calibration process gradually adjusts the parameters of the mirror prototype by comparing actual test data with the predicted results of the mirror prototype to make it more accurately reflect the performance of the spindle under real working conditions. This process involves multiple iterative calculations, and the various parameters in the mirror prototype are adjusted through optimization algorithms to ensure its strong adaptability to working conditions. The calibrated mirror prototype generates an enhanced mirror body with higher precision and accuracy, which can more realistically represent the performance of the spindle. The enhanced mirror body is used to re-solve the load control instruction set, triggering dynamic disturbances of multi-axis linkage, and further testing the performance of the spindle under complex working conditions. By comparing and analyzing the enhanced mirror image, the spindle's performance bottlenecks, potential failure points, and adaptability can be more clearly identified. After completing all disturbance tests, the performance testing platform will output complete performance test results based on the spindle's response and provide them to relevant engineers or operators for further analysis and optimization of the spindle design.

[0082] Through the technical solution of the present invention, a mirror prototype closed-loop calibration mechanism driven by dynamic disturbance characteristics is established, which realizes real-time self-optimization of simulation model parameters without interrupting testing, eliminating the defect of traditional static models that require interruption intervention due to accumulated errors.

[0083] Further, if Figure 2 As shown in the figure, dynamic perturbations are performed on the spindle body, including:

[0084] Decompose the load control instruction set into a multi-axis linkage control signal group, which includes:

[0085] The dynamic speed command of the spindle rotating axis system dynamically adjusts the speed gradient based on the predicted value of the thermal deformation of the spindle in the mirror prototype;

[0086] The broadband excitation waveform of the radially loaded shaft system generates a vibration spectrum containing multi-order harmonic components according to the critical flutter frequency distribution of the enhanced mirror body;

[0087] The deformation compensation signal of the axially loaded shaft system adjusts the loading phase according to the real-time strain data feedback in the performance change characteristics;

[0088] Among them, each axial control signal cooperates with the coupling control to execute the dynamic disturbance of the main shaft.

[0089] As a preferred embodiment of the above, according to the different axis systems and performance requirements of the spindle, the load control instruction set is first decomposed into control signal groups of multiple axis systems to ensure that the spindle can withstand the dynamic disturbance of multi-axis synergy at the same time during the test. These control signal groups include signals of the spindle rotating axis system, radial loading axis system and axial loading axis system. Each control signal group will provide independent and coordinated control signals according to the working characteristics and performance requirements of the spindle to ensure that the performance of the spindle under different load conditions is accurately evaluated; for the spindle rotating axis system, the dynamic speed instruction in the control signal group will be adjusted based on the predicted value of the thermal deformation of the spindle in the mirror prototype. During the operation of the spindle, the spindle shaft body High-speed rotation will generate heat, which will lead to thermal deformation. This deformation will affect the running accuracy of the spindle, especially under high load. Therefore, dynamically adjusting the speed gradient can effectively compensate for the impact caused by thermal deformation. In the implementation process, by establishing a numerical model of thermal deformation, the temperature and deformation of the spindle are monitored in real time, and then the speed gradient is dynamically adjusted to ensure the performance stability of the spindle in each working stage; the control signal group of the radially loaded shaft system adopts a broadband excitation waveform to simulate the multi-frequency vibration interference that the spindle may be subjected to in the actual working environment. The generation of this control signal depends on the critical flutter frequency distribution of the enhanced mirror body. Through this distribution, the response of the spindle at each frequency point is analyzed. The vibration spectrum containing multi-order harmonic components can be generated. This vibration spectrum can include the fundamental frequency and its high-order harmonics, which can accurately simulate the vibration response of the spindle at different operating frequencies. By adjusting these excitation waveforms, the tester can obtain the dynamic performance data of the spindle under different frequency interferences, and further analyze the resonance characteristics and structural stability of the spindle. During the test, the control signal group of the axially loaded shaft system also includes a deformation compensation signal, the purpose of which is to adjust the loading phase through real-time strain data feedback. Since the spindle may be subjected to axial force from the load during operation, causing its deformation, the deformation compensation signal can be fed back in time by installing a strain sensor and collecting the strain data of the shaft in real time. The current deformation condition of the spindle is calculated, and the loading phase is adjusted according to the data, so as to optimize the loading state of the spindle and ensure that the loading signal matches the actual deformation of the spindle shaft. This process can effectively avoid the test error caused by unbalanced loading; on the basis of the above-mentioned control signal groups, the rotation, radial and axial loading of the spindle are subjected to dynamic disturbance testing through the coordinated coupling control of multi-axis linkage. The axial control signals are synchronized and coordinated through a precise timing control system to ensure that the spindle can withstand dynamic disturbances from all directions at the same time during the test. This linkage control can simulate the actual stress conditions of the spindle in a complex working environment and provide accurate data for a comprehensive evaluation of the spindle performance.

[0090] Furthermore, the loading phase is adjusted based on the real-time strain data feedback in the performance change characteristics, including:

[0091] Real-time strain data is captured by multi-dimensional partitioning, and the partitions are mapped in parallel with the strain-sensitive areas of the mirror prototype;

[0092] Based on the strain gradient of the partition, the phase offset of the axially loaded shaft system is calculated by correlating the thermal expansion anisotropy weight in the enhanced mirror body.

[0093] generating a dynamic compensation parameter according to the phase offset, wherein the dynamic compensation parameter is inversely correlated with a material yield strength threshold of the mirror prototype;

[0094] The dynamic compensation coefficient is added to the carrier frequency of the deformation compensation signal to generate an axial loading waveform with phase pre-compensation characteristics.

[0095] As a preferred embodiment of the above, in order to accurately capture the real-time strain data of the spindle, the strain data is first captured by multi-dimensional partitioning. The partitioning process divides and monitors the strain data in multiple dimensions based on the geometric characteristics of the spindle, the workload, and the structural characteristics of the mirror prototype. These partitions are parallel mapped to the strain-sensitive areas in the mirror prototype. These areas usually include high-strain areas of the spindle, such as the connection parts of the spindle, key load points, and areas with large temperature changes. In this way, the strain data of these areas can be accurately obtained, thereby providing accurate basic data for the subsequent phase offset calculation; based on the strain data of the above partitions Based on the data, the strain gradient of each partition is further calculated. The strain gradient reflects the degree of deformation of the spindle in each area due to external loading. Combined with the thermal expansion anisotropy in the mirror prototype, the thermal expansion characteristics of the spindle under different working conditions and their influence are calculated. On this basis, the corresponding loading phase offset of each partition is determined by establishing the thermal expansion anisotropy weight. Thermal expansion anisotropy means that different areas have different responses to thermal deformation. Especially under high-speed operation, the temperature distribution of the spindle may be uneven, resulting in different expansion rates and deformation directions in different areas. By calculating these anisotropy weights, the loading phase can be accurately adjusted to avoid Test error caused by thermal deformation; based on the calculated phase offset, dynamic compensation parameters are further generated. The dynamic compensation parameters are used to adjust the axial loading signal in real time to ensure the loading accuracy of the spindle under different working conditions. When generating dynamic compensation parameters, reverse correlation is performed based on the yield strength threshold of the material in the mirror prototype. The yield strength of the material refers to the critical point where the material undergoes permanent deformation under external force. Under high load, the spindle material may fatigue or fail due to excessive deformation. The reverse correlation process will ensure that the material's bearing range will not be exceeded during the loading process through analysis of the yield strength threshold, thereby avoiding damage to the spindle. Recoverable damage; finally, the dynamic compensation coefficient is superimposed on the carrier frequency of the deformation compensation signal to generate an axial loading waveform with phase pre-compensation characteristics. This loading waveform can accurately compensate for the deformation caused by the thermal expansion of the spindle, material properties and external loads, thereby optimizing the loading process and ensuring that the strain response of the spindle shaft matches the test conditions. By dynamically adjusting the loading waveform, fine regulation of each spindle axis can be achieved to ensure high accuracy and reliability of the test data. During the implementation process, the adjustment of the loading waveform not only takes into account the conventional axial force changes, but also performs real-time correction according to the real-time monitored strain data to minimize errors.

[0096] Furthermore, the speed gradient is dynamically adjusted based on the predicted value of the thermal deformation of the spindle in the mirror prototype, including:

[0097] The thermal deformation prediction value is based on the axial partitioning of the material heat conduction anisotropy distribution map of the principal axis in the mirror prototype;

[0098] According to the thermal deformation difference of the axial partition, the speed gradient change rate of the main shaft rotating shaft system is calculated by correlating the thermal equilibrium time constant of the enhanced mirror body;

[0099] Generate a stepped speed adjustment command based on the speed gradient change rate, and the step interval of the adjustment command is inversely correlated with the temperature rise mutation threshold in the performance test result;

[0100] The step-shaped speed adjustment command is embedded in the transition interval of the dynamic speed command, so that the spindle speed approaches the target value in sections within the preset thermal deformation difference range.

[0101] As a preferred embodiment of the above, first, the spindle is divided into multiple thermally sensitive areas in the axial direction according to the anisotropic distribution data of the heat conduction of the spindle material in the mirror prototype. During the operation of the spindle, due to the different heat conduction properties of different materials and different axial regions, the generated thermal deformation rates will also be different. The thermal deformation prediction value of the spindle is obtained through finite element simulation or experimental methods, and the spindle is partitioned in the axial direction according to these thermal deformation differences. This partitioning process can accurately identify the temperature and thermal stress distribution of each region of the spindle during high-speed operation, thereby providing a basis for subsequent speed adjustment. After determining the thermally sensitive area of ​​the spindle, the speed gradient change rate of the spindle rotating shaft system is calculated according to the thermal deformation differences in different regions, further combined with the thermal equilibrium time constant of the enhanced mirror body in the mirror prototype. The thermal equilibrium time constant represents the time required for the spindle to reach thermal stability when it is affected by an external heat load. In the area with large temperature changes, the thermal equilibrium time constant is large, indicating that the area responds slowly to temperature changes. By analyzing the thermal equilibrium time constant, the speed gradient change rate of the spindle rotating shaft system is calculated according to the thermal deformation differences in different regions. The correlation between the time constant and the thermal deformation difference in each region can determine the adjustment rate of the speed gradient in each region; based on the calculated speed gradient change rate, a stepped speed adjustment instruction is generated. The stepped adjustment method divides the speed change into multiple stages, and the speed change amplitude of each stage gradually increases or decreases to avoid drastic changes in the speed adjustment process. The interval between each step is inversely correlated with the temperature rise mutation threshold in the spindle performance test results. That is, when the temperature rise mutation threshold is low, the step interval of the speed adjustment is small; when the temperature rise change is relatively stable, a larger adjustment amplitude and a larger step interval can be used; finally, the generated stepped speed adjustment instruction is embedded in the dynamic speed instruction transition interval of the spindle. The transition interval refers to the process of the spindle adjusting from the initial steady-state speed to the target test speed. By embedding the stepped adjustment instruction in the transition interval, the spindle speed change can gradually approach the target value within the thermal deformation difference range, without causing unnecessary thermal shock or thermal stress concentration due to excessively drastic speed changes.

[0102] Furthermore, a vibration spectrum containing multi-order harmonic components is generated according to the critical flutter frequency distribution of the enhanced mirror body, including:

[0103] The critical flutter frequency distribution is divided into multiple resonance sensitive areas according to the frequency band, and the resonance sensitive areas are mapped to the structural modal parameters in the enhanced mirror body;

[0104] According to the modal energy proportion of each resonance sensitive area, the amplitude weight of the corresponding harmonic component is obtained, and the amplitude weight is associated with the vibration suppression threshold in the performance test result;

[0105] The time series of multi-order harmonics is synthesized based on amplitude weights, and the phase interval of the time series is inversely correlated with the damping ratio of the spindle material in the mirror prototype;

[0106] The time series is superimposed on the fundamental frequency component of the broadband excitation waveform to generate a target vibration spectrum with modal suppression characteristics.

[0107] As a preferred embodiment of the above, first, the critical flutter frequencies that may occur during the operation of the spindle are obtained, and these frequencies are divided into multiple resonance sensitive areas according to frequency bands. The frequency range of each frequency band represents the area where the spindle is prone to flutter under specific working conditions. These areas are mapped with the structural modal parameters of the enhanced mirror body. The enhanced mirror body is a model that optimizes and improves the dynamic behavior of the spindle model under different working conditions. It contains detailed structural modal parameters, such as natural frequency, modal shape and damping ratio. Through the mapping of these modal parameters, each resonance sensitive area and the corresponding modal information in the enhanced mirror body can be accurately identified, thereby more accurately reflecting the The vibration characteristics of the main shaft are obtained; after delineating each resonance sensitive area, it is necessary to obtain the amplitude weight of the corresponding harmonic component according to the modal energy ratio of each resonance sensitive area. The modal energy ratio reflects the contribution of each mode of the main shaft to the overall vibration in a specific resonance frequency band. Through simulation or experimental testing, the energy distribution of the modes in different frequency ranges is obtained, and combined with the vibration suppression thresholds in the performance test results, these thresholds usually indicate the maximum vibration amplitude that the main shaft can withstand under different vibration intensities, and then the amplitude weight of the harmonic component is adjusted in reverse. This process ensures that the amplitude of each harmonic component in the vibration spectrum is consistent with its corresponding modal energy and vibration suppression threshold. association, thereby optimizing the vibration control strategy; according to the amplitude weights obtained by the above calculation, the time series of multi-order harmonics is synthesized. Multi-order harmonics refer to composite vibration signals containing multiple frequency components. Their frequencies are determined based on the critical flutter frequency of the main shaft and its modal characteristics. By synthesizing harmonics of different orders, a complete vibration spectrum is formed. In addition, when generating the time series, it is also necessary to consider that the phase interval of each order harmonic is inversely correlated with the damping ratio of the main shaft material in the enhanced mirror body. The higher the damping ratio, the stronger the main shaft's ability to absorb vibration energy, so the amplitude of its vibration response will be reduced. Therefore, when generating the time series, the change in the damping ratio will inversely affect The phase interval between the resonant harmonics is adjusted to ensure that the generated vibration spectrum can reasonably reflect the actual dynamic characteristics of the spindle; finally, the synthesized multi-order harmonic time series is superimposed on the fundamental frequency component of the broadband excitation waveform to form a target vibration spectrum with modal suppression characteristics. The fundamental frequency component of the broadband excitation waveform refers to the initial excitation signal applied to the spindle during the test. It contains multiple frequency components and can stimulate the vibration response of the spindle in different frequency ranges. By superimposing the synthesized harmonics on this fundamental frequency signal, the vibration of each resonance-sensitive area of ​​the spindle can be suppressed, avoiding excessive chatter during the test, thereby improving the test accuracy and the stability of the spindle.

[0108] Further, if Figure 3 As shown, the mirror prototype of the spindle is initialized in the performance test platform, including:

[0109] Generate a parametric geometric model based on the three-dimensional structural topology data of the spindle body. The parametric geometric model includes the moment of inertia distribution of each cross section of the spindle and the positioning parameters of the bearing support points.

[0110] Loading a material property set into the parametric geometric model, the material property set includes anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the spindle material;

[0111] Inject boundary conditions according to the working environment constraints, including temperature gradient field distribution and dynamic load spectrum;

[0112] Perform coupled solution on the parameterized geometric model, material property set and boundary conditions to generate the initial mirror prototype;

[0113] During the test, the material property set of the initial mirror prototype is updated through real-time data assimilation based on the performance change characteristics to form a dynamically evolving mirror prototype.

[0114] As a preferred embodiment of the above, first, based on the three-dimensional structural topological data of the main shaft body, a parametric geometric model of the main shaft is generated. The model is constructed through high-precision three-dimensional modeling technology, covering the shape and size of each cross section of the main shaft, including the size, cross-sectional shape, geometric features, etc. of each axial segment. The model includes not only the geometric shape of the main shaft, but also the moment of inertia distribution of the main shaft and the position parameters of the bearing support points. The moment of inertia distribution reflects the mass distribution of each part of the main shaft during the rotation process. The mass distribution and shape of key parts such as the two ends and the middle of the main shaft will affect the dynamic and static performance of the main shaft. Therefore, the geometric model must be described in detail. ; In the generated parametric geometric model, the material property set of the spindle is further loaded. The material property set includes the anisotropic elastic modulus, thermal expansion coefficient gradient and damping ratio frequency-varying characteristics of the spindle material. The anisotropic elastic modulus is used to describe the elastic performance of the spindle material in different directions, the thermal expansion coefficient gradient takes into account the expansion characteristics of the spindle material at different temperatures, and the damping ratio frequency-varying characteristics reflect the energy absorption capacity of the material at different frequencies, which is crucial for the vibration control of the spindle. These physical properties of the material are usually obtained through experimental data or standard values ​​in the material database, combined with the specific working environment and Conditions are adapted; next, according to the working conditions of the spindle under actual working conditions, corresponding boundary conditions are injected. The boundary conditions include temperature gradient field distribution and dynamic load spectrum. The temperature gradient field distribution takes into account the temperature changes caused by friction, conduction, radiation and other factors during the operation of the spindle, and maps them to various areas of the spindle, especially the bearing contact parts and the spindle load-bearing parts. The dynamic load spectrum simulates the time series of dynamic loads according to external interference such as vibration and load of the spindle during operation. These boundary conditions will affect the thermal deformation of the spindle, material stress distribution, etc., so they need to be adjusted according to the specific requirements of the working environment; After completing the above steps, the generated parameterized geometric model, material property set, and boundary conditions are jointly solved using a coupled solution method to generate an initial mirror prototype. Coupled solution refers to integrating the geometric model, material properties, and external working environment conditions into a multi-physics, multi-dimensional computational problem. The dynamic behavior of the spindle under actual working conditions is solved through numerical calculation methods. This process can simulate the operation of the spindle under different load, temperature, speed, and other conditions, including the spindle's stress, deformation, vibration and other physical characteristics. In this way, the resulting initial mirror prototype can highly restore the performance of the spindle in a real environment.During performance testing, the initial mirror prototype's material property set is updated through real-time data assimilation based on the performance change characteristics collected in real time. This process rapidly processes and provides feedback on the data collected during testing, adjusting the material property parameters in the mirror prototype to ensure consistency with the actual operating state of the spindle. The data assimilation and update process utilizes a dynamic adjustment algorithm to continuously correct errors in material properties through optimized estimation. This real-time update enables the mirror prototype to continuously adapt to changes in the spindle during different operating stages, forming a dynamically evolving mirror prototype.

[0115] Furthermore, coupled solutions are performed on parameterized geometry, material property sets, and boundary conditions, including:

[0116] The parameterized geometric model is solved by finite element method to generate a structural mesh model including a node stiffness matrix, and a material property set is mapped into the structural mesh model;

[0117] Perform transient heat transfer analysis based on the temperature gradient field distribution to calculate the nonlinear thermal deformation field of the spindle under thermal load;

[0118] The nonlinear thermal deformation field is used as the initial displacement condition and combined with the dynamic load spectrum to solve the dynamic stress distribution of the main shaft under the combined load.

[0119] According to the frequency domain response relationship between dynamic stress distribution and frequency-varying characteristics of damping ratio, the stiffness matrix of the corresponding nodes in the structural mesh model is iteratively modified;

[0120] When the residual norm of the modified node stiffness matrix is ​​less than the preset convergence threshold, the initial mirror prototype is output.

[0121] As a preferred embodiment of the above, a parametric geometric model is first constructed based on the geometric parameters of the spindle structure. The model preferably adopts a three-dimensional solid modeling method, which can accurately express the structural characteristics and dimensional changes of the spindle shaft under various working conditions. Subsequently, the geometric model is imported into the finite element modeling environment, and the grid density is divided based on the importance of the various parts of the spindle structure. The key parts such as the shoulder, the connection part and the bearing seat area are divided into encrypted grids to improve the analysis accuracy. Then, in the generated structural grid model, the material property set is mapped. The material property set includes parameters such as thermal expansion coefficient, Young's modulus, Poisson's ratio, thermal conductivity, etc., and the area is divided and the parameters are assigned according to the different materials of the various components of the spindle to ensure the physical reality of the thermal structure coupling. In the simulation of the thermal load condition, the typical heat source in the working process of the spindle is modeled to form a multi-source coupled temperature gradient field distribution, and then a transient heat transfer analysis is performed. The analysis adopts a time-step integration method to obtain the temperature distribution data inside the spindle shaft at different time points, and further calculates the nonlinear thermal deformation field of the spindle under the action of the thermal load. Preferably, the nonlinear thermal deformation field is obtained by node The point displacement form covers the entire shaft structure to fully reflect the non-uniform deformation effect caused by heat. After obtaining the nonlinear thermal deformation field, it is used as the initial displacement boundary condition and combined with the preset dynamic load spectrum to perform structural dynamic response analysis. The dynamic load spectrum can be obtained from the measured working conditions or standard test loads, including the change sequence of three types of loads: axial, radial and rotational. In the dynamic analysis process, the time-varying characteristics of the load and the influence of the main shaft's own moment of inertia and damping are considered to solve the dynamic stress distribution of the main shaft under the composite load. The dynamic stress field helps to reveal the main shaft in actual working conditions. Possible fatigue concentration areas and structural weak parts; in order to further improve the accuracy of model prediction, the obtained dynamic stress distribution is coupled with the pre-established damping ratio frequency characteristic relationship curve for analysis, and the stiffness matrix of the key nodes in the structural grid model is adjusted according to the damping change trend of the main shaft under different frequency responses. The correction is performed in an iterative manner. After each round of iterative update, the residual norm of the node stiffness matrix is ​​calculated and compared with the preset convergence threshold. If the residual norm is lower than the threshold, the model is considered to have converged, and the corresponding initial mirror prototype is output.

[0122] Further, if Figure 4 As shown in the figure, an enhanced mirror body with adaptability to working conditions is generated, including:

[0123] The performance change characteristics are compared with the theoretical response characteristics of the mirror prototype in multiple dimensions, and three types of difference parameters are extracted: vibration amplitude-frequency characteristics, thermal deformation displacement deviation, and dynamic stress residual.

[0124] Generate a frequency domain residual energy spectrum based on the difference parameters, and calculate the correction gradient of the main shaft material property set according to the amplitude envelope and phase offset angle of the energy spectrum;

[0125] The anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the mirror prototype are adjusted in a coordinated manner so that the correlation coefficient between the theoretical response characteristics and the performance variation characteristics of the mirror prototype reaches a preset matching threshold;

[0126] Within the load mutation time window of dynamic disturbance, verify the dynamic response accuracy of the adjusted mirror prototype to multi-axis coupled loads. If the axial runout prediction error exceeds the tolerance range, recalculate the correction gradient.

[0127] When the deviation between the predicted and measured contact stiffness tensors of the mirror prototype in at least three orthogonal directions is less than the set tolerance, the material property set and boundary conditions of the current mirror prototype are locked to generate an enhanced mirror body.

[0128] As a preferred embodiment of the above, firstly, based on the initial mirror prototype constructed in the above steps, a theoretical response characteristic analysis is carried out, and a multi-dimensional comparison is made with the performance change characteristics collected under actual operating conditions. The performance change characteristics are preferably the vibration response, thermal deformation displacement trajectory and stress sensing data recorded by the online sensing system. Through Fourier transform and sliding time window processing technology, the dynamic characteristic evolution trend of the main shaft response in different frequency ranges can be obtained. In this comparison process, three types of key difference parameters are extracted: the difference in vibration amplitude-frequency characteristics (such as resonance peak offset, frequency band response amplitude anomaly, etc.), the measured and predicted deviation of thermal deformation displacement, and the residual in the dynamic stress field. Differential stress amplitude distribution; for the extracted difference parameters, the frequency domain residual energy spectrum is constructed to further analyze its frequency energy distribution and phase difference, and the signal envelope analysis and short-time spectrum reconstruction method are used to extract the amplitude envelope of the energy spectrum and its phase offset angle to calculate the material property correction gradient for model adjustment. The correction gradient reflects the need for non-uniformity correction of the material under different frequency responses, and is then used to guide the adjustment strategy of the relationship between the anisotropic elastic modulus, thermal expansion coefficient gradient and damping ratio with frequency; in the model parameter adjustment stage, the above three key material parameters are collaboratively corrected through an iterative optimization algorithm. The goal of the correction is to make the correlation coefficient between the response characteristics of the mirror prototype in the theoretical simulation and the actual performance change characteristics collected reach a preset matching threshold, so as to ensure that the enhanced mirror body has a highly consistent physical response capability. On this basis, a typical working condition disturbance window is selected for simulation verification. This window includes transient working conditions such as load mutation and high-speed variable frequency startup. The spindle axial runout is predicted through simulation and the error is compared with the measured data. If the prediction error exceeds the set tolerance, the above-mentioned correction gradient needs to be recalculated and iteratively adjusted. In the final step, the adjusted mirror prototype is subjected to a three-axis verification of the contact stiffness tensor. The contact stiffness tensor is analyzed in the orthogonal directions of the spindle and the fixture, bearing, and structural connection area. The sensor measured data is compared with the finite element simulation results. When the deviation between the predicted stiffness values ​​and the measured values ​​in the three directions is less than the set tolerance, it indicates that the mirror prototype has a stable response capability under a multi-working condition and multi-physics coupling environment, and then its material property set and boundary conditions are locked, and the enhanced mirror body with working condition adaptability is formally generated.

[0129] Embodiment 2;

[0130] Based on the same inventive concept as the high-precision spindle performance testing method in the aforementioned embodiment, the present invention further provides a high-precision spindle performance testing system, the system comprising:

[0131] The mirror spindle module initializes the mirror prototype of the spindle in the performance test platform according to the main structure of the spindle body and the working environment constraints;

[0132] The instruction establishment module establishes a load control instruction set based on the mirror prototype and the motion state of the spindle in a composite performance test scenario;

[0133] The dynamic perturbation module performs dynamic perturbations on the main shaft according to the load control instruction set and captures the performance change characteristics of the shaft during the perturbation process;

[0134] The organization calibration module combines the performance change characteristics with the mirror prototype, performs self-organization calibration of the prototype parameters of the main axis body, and generates an enhanced mirror body with adaptability to working conditions;

[0135] The performance detection module recalculates the load control instruction set based on the enhanced mirror body, triggers the dynamic disturbance of multi-axis linkage, and outputs the performance detection results.

[0136] The above-mentioned adjustment system in the present invention can effectively realize a high-precision spindle performance testing method, and the technical effects that can be achieved are as described in the above-mentioned embodiments and will not be repeated here.

[0137] More specifically, the mirror spindle module includes:

[0138] A geometric modeling unit generates a parametric geometric model based on the three-dimensional structural topology data of the spindle body. The parametric geometric model includes the moment of inertia distribution of each cross section of the spindle and the positioning parameters of the bearing support points;

[0139] A property loading unit is used to load a material property set into a parametric geometric model. The material property set includes the anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the spindle material.

[0140] Working condition constraint unit, which injects boundary conditions according to working condition environment constraints. The boundary conditions include temperature gradient field distribution and dynamic load spectrum;

[0141] A prototype generation unit performs coupled solution on the parameterized geometric model, material property set and boundary conditions to generate an initial mirror prototype;

[0142] During the test, the dynamic evolution unit performs real-time data assimilation and updates on the material property set of the initial mirror prototype according to the performance change characteristics to form a dynamically evolving mirror prototype.

[0143] Similarly, the above-mentioned optimization schemes for the system can also respectively achieve the corresponding optimization effects of the method in Example 1, which will not be repeated here.

[0144] Although the present application has been described with reference to specific features and embodiments thereof, it is apparent that various modifications and combinations may be made thereto without departing from the spirit and scope of the present application. Accordingly, this specification and drawings are merely illustrative of the present application as defined herein and are deemed to cover any and all modifications, variations, combinations or equivalents within the scope of the present application. Obviously, those skilled in the art may make various modifications and variations to the present application without departing from the scope of the present application. Thus, the present application is intended to include such modifications and variations as fall within the scope of the present application and its equivalents.

Claims

1. A high-precision spindle performance testing method, characterized in that: The method comprises: Initialize the spindle's mirror prototype in the performance test platform based on the spindle's main structure and working environment constraints; Establishing a load control instruction set according to the mirror prototype and based on the motion state of the spindle shaft in a composite performance test scenario; According to the load control instruction set, dynamic perturbation is performed on the main shaft body, and the performance change characteristics of the shaft body are captured during the perturbation process; The performance change characteristics are combined with the mirror prototype to perform self-organized calibration of the prototype parameters of the main shaft body to generate an enhanced mirror body with adaptability to working conditions. The enhanced mirror body with adaptability to working conditions is generated, including: The performance change characteristics are compared with the theoretical response characteristics of the mirror prototype in multiple dimensions to extract three types of difference parameters: vibration amplitude-frequency characteristics, thermal deformation displacement deviation, and dynamic stress residual; generating a frequency domain residual energy spectrum based on the difference parameters, and calculating a correction gradient of the main shaft material property set according to the amplitude envelope and phase offset angle of the energy spectrum; Coordinately adjusting the anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-varying characteristics of the mirror prototype so that the correlation coefficient between the theoretical response characteristics of the mirror prototype and the performance variation characteristics reaches a preset matching threshold; Verify the dynamic response accuracy of the adjusted mirror prototype to the multi-axis coupled load within the load mutation time window of the dynamic disturbance, and recalculate the correction gradient if the axial runout prediction error exceeds the tolerance range; When the deviations between the predicted and measured contact stiffness tensors of the mirror prototype in at least three orthogonal directions are all less than a set tolerance, the material property set and boundary conditions of the current mirror prototype are locked to generate the enhanced mirror body; The load control instruction set is recalculated based on the enhanced mirror body, the dynamic disturbance of the multi-axis linkage is triggered, and the performance detection result is output.

2. The high-precision spindle performance testing method according to claim 1, characterized in that: Performing dynamic perturbations on the spindle shaft includes: The load control instruction set is decomposed into a multi-axis linkage control signal group, wherein the control signal group includes: A dynamic speed command of the spindle rotating shaft system, dynamically adjusting the speed gradient based on the predicted value of the thermal deformation of the spindle in the mirror prototype; A broadband excitation waveform for a radially loaded shafting generates a vibration spectrum containing multi-order harmonic components according to the critical flutter frequency distribution of the enhanced mirror body; A deformation compensation signal of the axially loaded shaft system, adjusting the loading phase according to the real-time strain data feedback in the performance change characteristics; Among them, each axial control signal cooperates with the coupling control to execute the dynamic disturbance of the main shaft.

3. The high-precision spindle performance testing method according to claim 2, characterized in that: Adjusting the loading phase according to the real-time strain data feedback in the performance change characteristics includes: Capturing the real-time strain data by multi-dimensional partitioning, wherein the partitions are parallel mapped to the strain-sensitive areas of the mirror prototype; Calculating the phase offset of the axially loaded shaft system based on the strain gradient of the partition and in association with the thermal expansion anisotropy weight in the enhanced mirror body; generating a dynamic compensation parameter according to the phase offset, wherein the dynamic compensation parameter is inversely correlated with a material yield strength threshold of the mirror prototype; The dynamic compensation coefficient is superimposed on the carrier frequency of the deformation compensation signal to generate an axial loading waveform with a phase pre-compensation characteristic.

4. The high-precision spindle performance testing method according to claim 2, characterized in that: Dynamically adjusting the speed gradient based on the predicted value of thermal deformation of the spindle in the mirror prototype includes: The thermal deformation prediction value is axially partitioned based on the material thermal conductivity anisotropy distribution map of the main axis in the mirror prototype; Calculate the speed gradient change rate of the main shaft rotating shaft system according to the thermal deformation difference of the axial partition and in association with the thermal equilibrium time constant of the enhanced mirror body; generating a stepped speed adjustment instruction based on the speed gradient change rate, wherein the step interval of the adjustment instruction is inversely correlated with the temperature rise mutation threshold in the performance detection result; The step-shaped speed adjustment instruction is embedded in the transition interval of the dynamic speed instruction, so that the spindle speed approaches the target value in sections within a preset thermal deformation difference range.

5. The high-precision spindle performance testing method according to claim 2, characterized in that: Generating a vibration spectrum containing multi-order harmonic components according to the critical flutter frequency distribution of the enhanced mirror body, including: Dividing the critical flutter frequency distribution into a plurality of resonance sensitive areas according to frequency bands, and mapping the resonance sensitive areas to the structural modal parameters in the enhanced mirror body; Obtaining an amplitude weight of a corresponding harmonic component according to the modal energy proportion of each resonance sensitive area, wherein the amplitude weight is associated with a vibration suppression threshold in the performance test result; synthesizing a time series of multiple harmonics based on the amplitude weights, wherein the phase interval of the time series is inversely correlated with the damping ratio of the spindle material in the mirror prototype; The time series is superimposed on the fundamental frequency component of the broadband excitation waveform to generate a target vibration spectrum with modal suppression characteristics.

6. The high-precision spindle performance testing method according to claim 1, characterized in that: Initialize the mirror prototype of the spindle in the performance test platform, including: Generate a parametric geometric model based on the three-dimensional structural topology data of the spindle shaft, wherein the parametric geometric model includes the moment of inertia distribution of each cross section of the spindle and the positioning parameters of the bearing support points; Loading a material property set into the parameterized geometric model, the material property set including anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the spindle material; Injecting boundary conditions according to the working environment constraints, the boundary conditions including temperature gradient field distribution and dynamic load spectrum; performing coupled solution on the parameterized geometric model, the material property set, and the boundary conditions to generate an initial mirror prototype; During the test process, the material property set of the initial mirror prototype is updated through real-time data assimilation according to the performance change characteristics to form the dynamically evolving mirror prototype.

7. The high-precision spindle performance testing method according to claim 6, characterized in that: Performing a coupled solution on the parameterized geometric model, the material property set, and the boundary condition, including: Performing finite element solution on the parameterized geometric model to generate a structural grid model including a node stiffness matrix, and mapping the material property set in the structural grid model; Performing transient heat transfer analysis based on the temperature gradient field distribution to calculate the nonlinear thermal deformation field of the spindle shaft under the action of thermal load; The nonlinear thermal deformation field is used as an initial displacement condition and combined with the dynamic load spectrum to solve the dynamic stress distribution of the main shaft under the combined load; Iteratively correcting the stiffness matrix of the corresponding node in the structural grid model according to the frequency domain response relationship between the dynamic stress distribution and the damping ratio frequency-varying characteristic; When the residual norm of the modified node stiffness matrix is ​​less than a preset convergence threshold, the initial mirror prototype is output.

8. A high-precision spindle performance testing system, characterized in that: Using the high-precision spindle performance testing method according to claim 1, the system includes: The mirror spindle module initializes the mirror prototype of the spindle in the performance test platform according to the main structure of the spindle body and the working environment constraints; The instruction establishment module establishes a load control instruction set based on the mirror prototype and the motion state of the spindle in a composite performance test scenario; The dynamic perturbation module performs dynamic perturbations on the main shaft according to the load control instruction set and captures the performance change characteristics of the shaft during the perturbation process; The organization calibration module combines the performance change characteristics with the mirror prototype, performs self-organization calibration of the prototype parameters of the main axis body, and generates an enhanced mirror body with adaptability to working conditions; The performance detection module recalculates the load control instruction set based on the enhanced mirror body, triggers the dynamic disturbance of multi-axis linkage, and outputs the performance detection results.

9. The high-precision spindle performance testing system according to claim 8, characterized in that: The mirror spindle module comprises: A geometric modeling unit generates a parametric geometric model based on the three-dimensional structural topology data of the spindle body. The parametric geometric model includes the moment of inertia distribution of each cross section of the spindle and the positioning parameters of the bearing support points; A property loading unit is used to load a material property set into a parametric geometric model. The material property set includes the anisotropic elastic modulus, thermal expansion coefficient gradient, and damping ratio frequency-dependent characteristics of the spindle material. Working condition constraint unit, which injects boundary conditions according to working condition environment constraints. The boundary conditions include temperature gradient field distribution and dynamic load spectrum; A prototype generation unit performs coupled solution on the parameterized geometric model, material property set and boundary conditions to generate an initial mirror prototype; During the test, the dynamic evolution unit performs real-time data assimilation and updates on the material property set of the initial mirror prototype according to the performance change characteristics to form a dynamically evolving mirror prototype.

Images