Adjustment method and system for damper valve system

Abstract

The invention is applicable to the technical field of shock absorbers, and provides a method and a system for adjusting a shock absorber valve train, the method for adjusting the shock absorber valve train comprises the following steps: acquiring vibration data of the shock absorber valve train through a sensor assembly, and obtaining a frequency response function of the shock absorber valve train according to the vibration data; establishing a mathematical dynamic model of the damper valve system according to the vibration data, and describing a relationship between damper valve system parameters and a frequency response function; optimizing and adjusting the parameters of the valve system by using an optimization algorithm to obtain a minimum vibration amplitude; and verifying whether the adjusted damper valve system achieves an expected damping effect or not through an experiment. Through the automatic and intelligent adjustment process, the adjustment efficiency and precision of the shock absorber can be remarkably improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of shock absorbers, and particularly relates to a method and system for tuning a shock absorber valve system. Background Art

[0002] An automotive shock absorber is an automotive component that connects the vehicle chassis and the body to reduce body vibration. It is an important component in the suspension system and is related to the ride comfort and handling stability of the entire vehicle.

[0003] To improve the shock absorption effect of the shock absorber, it is usually necessary to tune the shock absorber. At present, the tuning method of traditional shock absorbers mainly relies on manual experience, that is, manually tuning each shock absorber one by one. However, this adjustment process is time-consuming and has limited accuracy.

[0004] With the increasing complexity of mechanical systems and the increasing requirements for shock absorption, there is an urgent need for a more efficient and accurate tuning method. Summary of the Invention

[0005] The present invention provides a method for tuning a shock absorber valve system, aiming to solve the problem that the existing method of manually tuning each shock absorber one by one results in a time-consuming adjustment process and limited accuracy.

[0006] The present invention is implemented as follows. A method for tuning a shock absorber valve system, the tuning method comprising:

[0007] Collecting vibration data of the shock absorber valve system through a sensor assembly, and obtaining a frequency response function of the shock absorber valve system according to the vibration data;

[0008] Establishing a mathematical dynamic model of the shock absorber valve system based on the vibration data, and describing the relationship between the parameters of the shock absorber valve system and the frequency response function;

[0009] Using an optimization algorithm to optimize and adjust the valve system parameters to obtain a minimized vibration amplitude;

[0010] Verifying through experiments whether the tuned shock absorber valve system achieves the expected shock absorption effect.

[0011] Optionally, the step of collecting vibration data of the shock absorber valve system through a sensor assembly and obtaining a frequency response function of the shock absorber valve system according to the vibration data includes:

[0012] Collecting a vibration input signal x(t) and a vibration output signal y(t) of the shock absorber valve system;

[0013] Performing a fast Fourier transform on the vibration input signal x(t) and the vibration output signal y(t) to obtain corresponding frequency domain representations X(f) and Y(f);

[0014] Based on the corresponding frequency-domain representations X(f) and Y(f), the frequency response function H(ω) = Y(f) / X(f) is obtained.

[0015] Optionally, when the vibrator valve train is a single-degree-of-freedom system, the frequency response function is:

[0016] H(ω) = 1 / (k - mω² + jcω),

[0017] where: m is the mass, c is the damping coefficient, k is the stiffness, ω = 2πf is the angular frequency, and j is the imaginary unit, defined to represent the phase and amplitude relationship in frequency analysis.

[0018] Optionally, if the vibration output signal y(t) is an acceleration response signal, the frequency response function is:

[0019] H(ω) = -ω² / (k - mω² + jcω),

[0020] where: m is the mass, c is the damping coefficient, k is the stiffness, ω = 2πf is the angular frequency, and j is the imaginary unit, defined to represent the phase and amplitude relationship in frequency analysis.

[0021] Optionally, a mathematical dynamic model of the shock absorber valve train is established based on vibration data, including establishing a single-degree-of-freedom system model and a multi-degree-of-freedom system model respectively, where

[0022] the equation of motion of the single-degree-of-freedom system model is where m is the mass, c is the damping coefficient, k is the stiffness, x(t) is the displacement response, and F(t) is the external excitation force;

[0023] the equation of motion of the multi-degree-of-freedom system model is where M is the mass matrix, C is the damping matrix, K is the stiffness matrix, X(t) is the displacement vector, and F(t) is the external excitation force vector.

[0024] Optionally, describe the relationship between the shock absorber valve train parameters and the frequency response function, including: the relationship between stiffness and mass and the natural frequency, the relationship between the damping coefficient and vibration attenuation, and the relationship between the resonance amplitude and the damping coefficient, where

[0025] the expression of the relationship between stiffness and mass and the natural frequency is as the stiffness k increases, the natural frequency increases, and as the mass m increases, the natural frequency decreases;

[0026] the expression of the relationship between the damping coefficient and vibration attenuation is as the damping c increases, the damping ratio increases, the resonance peak amplitude decreases, and the vibration attenuates faster;

[0027] The relational expression between the resonance amplitude and the damping coefficient is Near the resonance frequency, the resonance amplitude is inversely proportional to the damping coefficient. The smaller the damping, the larger the resonance amplitude.

[0028] Optionally, an optimization algorithm is used to optimize and adjust the valve train parameters, including:[[]]

[0029] Obtain the coefficients of each part of the shock absorber valve train, and substitute each coefficient into the optimization algorithm for iterative update;

[0030] Adjust the valve train parameters to minimize the error between the system response and the target performance, so as to optimize and obtain the minimum vibration amplitude; the optimization algorithm is:

[0031]

[0032] Among them,

[0033] ω is the inertia weight (controlling the tendency of the particle to maintain its original velocity);

[0034] c1 and c2 are acceleration coefficients (usually c1 = c2 = 2);

[0035] r1 and r2 are random numbers within [0, 1];

[0036] P best is the historical optimal position of each particle, and g best is the global optimal position of all particles in the particle swarm;

[0037] The position of the i-th particle is x i , xi = [x i1 , x i2 ,..., x iD , and D is the dimension;

[0038] The velocity of the i-th particle is v i , vi = [v i1 , v i2 ,..., v iD , and D is the dimension; the particle is each parameter combination of the vibrator valve train to be optimized. If the stiffness of the vibrator valve train to be optimized is k, the damping coefficient is c, and the pre-tightening force is F0, then the position vector of the particle is P = [k, c, F0].[[]]

[0039] Optionally, to check whether the shock absorber valve train after experimental calibration reaches the expected shock absorption effect, it includes:[[]]

[0040] Under a predetermined stroke and frequency, make the shock absorber perform simple harmonic motion through a bench test;

[0041] Record the damping force and displacement changes of the shock absorber and draw the corresponding curve indicator diagram;

[0042] Identify the opening point of the shock absorber valve system according to the mutation point of the curve indicator diagram;

[0043] Record the damping force and speed changes of the shock absorber and plot the corresponding relationship curve;

[0044] Determine whether the tuned shock absorber valve system achieves the expected shock absorption effect according to the opening point and the relationship curve.

[0045] The present invention further provides a tuning system for a shock absorber valve system for tuning the shock absorber valve system, including an electro-hydraulic servo universal testing machine, a shock absorber to be tuned, and a sensor assembly. The shock absorber to be tuned is used to perform corresponding tests and tuning on the electro-hydraulic servo universal testing machine. Among them,

[0046] A shock absorber test bench is provided on the electro-hydraulic servo universal testing machine, and the shock absorber to be tuned is used to be placed on the shock absorber test bench;

[0047] The sensor assembly is arranged on the shock absorber and is used to detect the vibration signal of the shock absorber.

[0048] Optionally, the tuning system further includes:

[0049] A data acquisition component, arranged inside the electro-hydraulic servo universal testing machine, is used to obtain and collect the vibration signals of the sensor assembly;

[0050] A controller component, used to be connected to the data acquisition component, is used to receive the digital signals of the vibration signals, and control and tune the shock absorber valve system according to the vibration data.

[0051] Optionally, the sensor assembly includes: a force sensor, a displacement sensor, and an accelerometer. The force sensor, the displacement sensor, and the accelerometer are all fixed on the shock absorber and are respectively used to detect the force signal, displacement signal, and acceleration signal of the shock absorber, facilitating the tuning of the shock absorber valve system.

[0052] Optionally, the data acquisition component includes a data acquisition card and a signal conditioning circuit. Among them,

[0053] The data acquisition card is respectively communicatively connected to each sensor of the sensor assembly and is used to collect the relevant signals of each sensor;

[0054] The input end of the signal conditioning circuit is connected to the data acquisition card, the output end of the signal conditioning circuit is connected to the controller component, and the signal conditioning circuit is used to amplify and filter the sensor signals.

[0055] Optionally, the controller component includes a control cabinet and a servo controller and a PLC controller installed in the control cabinet.

[0056] The beneficial effects achieved by the present invention are due to a shock absorber valve system calibration method provided herein, which includes: collecting vibration data of the shock absorber valve system via a sensor assembly, and obtaining a frequency response function of the shock absorber valve system based on the vibration data; establishing a mathematical dynamic model of the shock absorber valve system based on the vibration data, and describing the relationship between the shock absorber valve system parameters and the frequency response function; optimizing and adjusting the valve system parameters using an optimization algorithm to minimize the vibration amplitude; and experimentally verifying whether the adjusted shock absorber valve system achieves the expected vibration reduction effect. This automated and intelligent calibration process can significantly improve the efficiency and accuracy of shock absorber calibration. BRIEF DESCRIPTION OF THE DRAWINGS

[0057] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0058] 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, for ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative labor.

[0059] Figure 1 This is a flowchart of a method for adjusting a shock absorber valve system provided in this application.

[0060] Figure 2 This is a flowchart of another method for adjusting a shock absorber valve system provided in this application.

[0061] Figure 3 This is an FV curve diagram of a shock absorber valve system adjustment method provided in this application.

[0062] Figure 4 This is a structural block diagram of a shock absorber valve system adjustment system provided in this application.

[0063] Figure 5 This is a structural block diagram of another shock absorber valve system adjustment system provided in this application. DETAILED DESCRIPTION

[0064] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0065] In order to effectively illustrate the embodiments of the present invention, the embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0066] The present invention provides a method for tuning a shock absorber valve system. Refer to the appendix Figures 1 to 3 The following are the specific steps disclosed in the embodiments of the present invention:

[0067] Step S101: Collect vibration data of the shock absorber valve system through a sensor assembly, and obtain the frequency response function of the shock absorber valve system according to the vibration data;

[0068] In the specific implementation process, the vibration data may include input signals and output information. The time-domain data of the input (excitation signal, such as force) and output (response signal, such as acceleration, velocity or displacement) can be detected simultaneously. Usually, a force sensor and an accelerometer are used to collect the input signal and the output signal respectively. That is, this step further includes:

[0069] Collect the vibration input signal x(t) and the vibration output signal y(t) of the shock absorber valve system;

[0070] Perform a fast Fourier transform on the vibration input signal x(t) and the vibration output signal y(t) to obtain the corresponding frequency-domain representations X(f) and Y(f) respectively;

[0071] According to the corresponding frequency-domain representations X(f) and Y(f), obtain the frequency response function H(w) = Y(f) / X(f). Among them, the frequency response function H(w) is usually a complex function, including vibration amplitude and phase information. For a linear time-invariant system, its theoretical expression is related to the system dynamic parameters.

[0072] Taking the vibrator valve system as a single-degree-of-freedom system as an example for illustration, the frequency response function is:

[0073] H(w) = 1 / (k - mw^2 + jcw), where: m is the mass, c is the damping coefficient, k is the stiffness, w = 2πf is the angular frequency, j is the imaginary unit, and the definition is the core component of the complex number, used to represent the phase and amplitude relationship in frequency analysis.

[0074] If the measured output signal is an acceleration response signal, the frequency response function should be:

[0075] H(w) = -w^2 / (k - mw^2 + jcw),

[0076] where: m is the mass, c is the damping coefficient, k is the stiffness, w = 2πf is the angular frequency, j is the imaginary unit, and the definition is used to represent the phase and amplitude relationship in frequency analysis.

[0077] Step S102: Establish a mathematical dynamic model of the shock absorber valve system according to the vibration data, and describe the relationship between the parameters of the shock absorber valve system and the frequency response function;

[0078] Establishing a mathematical dynamic model includes establishing a single-degree-of-freedom system model and a multi-degree-of-freedom system model respectively. In this application, it is illustrated by taking the damper valve system mainly composed of mass, spring and damper as an example. Among them,

[0079] The motion equation of the single-degree-of-freedom system model is where m is the mass (kg), c is the damping coefficient (N·s / m), k is the stiffness (N / m), x(t) is the displacement response (m), and F(t) is the external excitation force (N);

[0080] The motion equation of the multi-degree-of-freedom system model is where M is the mass matrix, C is the damping matrix, K is the stiffness matrix, X(t) is the displacement vector, and F(t) is the external excitation force vector.

[0081] Describing the relationship between the damper valve system parameters and the frequency response function mainly includes: the relationship between stiffness and mass and the natural frequency, the relationship between the damping coefficient and vibration attenuation, and the relationship between the resonance amplitude and the damping coefficient. Among them,

[0082] The relationship expression between stiffness and mass and the natural frequency is When the stiffness k increases, the natural frequency increases; when the mass m increases, the natural frequency decreases;

[0083] The relationship expression between the damping coefficient and vibration attenuation is When the damping c increases, the damping ratio increases, the resonance peak amplitude decreases, and the vibration attenuates faster;

[0084] The relationship expression between the resonance amplitude and the damping coefficient is Near the resonance frequency, the resonance amplitude is inversely proportional to the damping coefficient. The smaller the damping, the larger the resonance amplitude.

[0085] That is, the stiffness k is used to dominate the natural frequency, the damping c controls the resonance amplitude and the attenuation speed, and the mass m affects the inertial force and the natural frequency.

[0086] Step S103: Use an optimization algorithm to optimize and adjust the valve system parameters to obtain the minimum vibration amplitude;

[0087] In the specific implementation process, this optimization algorithm adopts the particle swarm algorithm. Through the particle swarm algorithm, the valve system parameters (such as the stiffness k, damping coefficient c, mass m, etc. of the damper) are optimized. By adjusting the valve system parameters (such as k, c, m), the error between the system response (such as vibration amplitude, frequency response function, etc.) and the target performance (such as the minimum resonance amplitude, specific frequency band attenuation) is minimized. The specific steps are as follows:

[0088] Obtain the coefficients of the damper valve system and substitute each coefficient into the optimization algorithm for iterative update;

[0089] Adjust the valve train parameters to minimize the error between the system response and the target performance, so as to optimize and obtain the minimum vibration amplitude; the optimization algorithm is as follows:

[0090]

[0091] Among them,

[0092] ω is the inertia weight (controlling the tendency of the particle to maintain its original velocity);

[0093] c1 and c2 are acceleration coefficients (usually c1 = c2 = 2);

[0094] r1 and r2 are random numbers within [0, 1];

[0095] P best is the historical optimal position of a single (single particle or single data), and g best is the global optimal position of the population (all particles or all data in the entire particle swarm);

[0096] The position of the i-th particle is x i , xi = [x i1 , x i2 ,..., x iD , and D is the dimension;

[0097] The velocity of the i-th particle is v i , vi = [v i1 , v i2 ,..., v iD , and D is the dimension.

[0098] In the specific implementation process, the particles are the parameter combinations of each vibration valve system to be optimized. If the stiffness of the vibration valve system to be optimized is k, the damping coefficient is c, and the pre-tightening force is F0, then the position vector of the particle is P = [k, c, F0]. The particle swarm algorithm adjusts these parameter values to find the optimal combination that minimizes the objective function (such as minimizing the vibration amplitude).

[0099] In the specific implementation process, through the particle swarm algorithm, the optimal combination of valve train parameters can be efficiently searched, so as to improve the vibration reduction performance or meet specific dynamic requirements. Specifically, in order to obtain the minimum vibration amplitude, the following steps usually need to be implemented:

[0100] Step 1: Define the fitness function. Specifically, this fitness function is directly related to the optimization objective. For example, this fitness function is:

[0101] Among them,

[0102] The input signal is the current parameters of the vibrator valve system, with stiffness k, damping coefficient c, and pre-tightening force F0; the output signal is the mean square error of the vibration amplitude (the smaller the value, the better the performance); through the simulation model or experimental test, input the current parameters and measure the vibration response.

[0103] Step 2: The PSO iteration process. Specifically, it can be achieved by initializing the particle swarm, iteratively updating, and outputting the optimal result to obtain the minimized vibration amplitude. The details are as follows:

[0104] 1. Initialize the particle swarm

[0105] Randomly generate multiple groups of parameter combinations (i.e., particles), for example:

[0106] Particle 1: [k = 1000, c = 50, F0 = 10]

[0107] Particle 2: [k = 1500, c = 80, F0 = 15]

[0108] …

[0109] Each particle corresponds to an initial fitness value, which is calculated through simulation or experiment and will not be elaborated in detail here.

[0110] 2. Iterative update and convergence

[0111] In each iteration, based on P best and g best update the velocity and position of each particle respectively, and then recalculate the fitness value to update the individual optimal P best and the global optimal g best .

[0112] Termination condition: Usually, when the maximum number of iterations is reached, or the change in the fitness value is less than the threshold (such as ∣f new -f old ∣ < 10-6∣f new -f old ∣ < 10 -6 ), it means that the iteration is completed and the minimized vibration amplitude is calculated.

[0113] 3. Output the optimal result

[0114] Final data: The parameter combination g best = [k*, c*, F0*] corresponding to the global optimal position, and the minimum vibration amplitude f min = f(k*, c*, F0 * ).

[0115] Verification: Substitute the optimized parameters into simulation or actual tests to verify whether the vibration amplitude is significantly reduced, and find the parameter combination and its performance indicators that minimize the vibration amplitude through iteration.

[0116] Step S104: Check through experiments whether the tuned shock absorber valve system achieves the expected shock absorption effect.

[0117] In the specific implementation process, a dynamometer characteristic test and a speed characteristic test can be carried out on the shock absorber valve system. Specifically, this step S104 further includes:

[0118] Step S201: Make the shock absorber perform simple harmonic motion through a bench test at a predetermined stroke and frequency;

[0119] Specifically, a bench test can be carried out under the conditions of a stroke of 100 mm and a frequency of 1.67 HZ.

[0120] Step S202: Record the damping force and displacement changes of the shock absorber and draw the corresponding curve dynamometer diagram;

[0121] In the specific implementation process, record the data of the damping force F and displacement S of the shock absorber respectively, so as to draw the curve corresponding to the damping force F and displacement S, which is recorded as the curve dynamometer diagram. The mutation point can be clearly identified through the curve dynamometer diagram, and this mutation point is used as the opening point of the shock absorber valve system. By this method, the valve system parameters (such as spring stiffness, valve plate clearance) can be optimized to ensure that the opening point is consistent with the design target.

[0122] Step S203: Identify the opening point of the shock absorber valve system according to the mutation point of the curve dynamometer diagram;

[0123] Step S204: Record the damping force and speed changes of the shock absorber and draw the corresponding relationship curve;

[0124] In the specific implementation process, test the relationship curve (F-V diagram, for example, as shown) between the damping force F and speed V at multiple speed levels (such as 0.05 m / s to 1.0 m / s), so as to analyze the response of the shock absorber valve system in the low-speed compression / rebound stage and the high-flow rate stage according to this relationship curve, and thus verify whether the linear or non-linear damping characteristics of the tuned valve system meet the design requirements. Figure 3 shown) to analyze the response of the shock absorber valve system in the low-speed compression / recovery stage and the high-flow rate stage according to this relationship curve, so as to verify whether the linear or non-linear damping characteristics of the tuned valve system meet the design requirements.

[0125] Step S205: Determine whether the tuned shock absorber valve system achieves the expected shock absorption effect according to the opening point and the relationship curve.

[0126] Specifically, compare the opening point of the curve dynamometer diagram obtained from the test and the relationship curve with the theoretical model or simulation effect to identify whether the deviation is within the preset range. If it is within the preset range, it indicates that the tuned shock absorber valve system can achieve the expected shock absorption effect; otherwise, it cannot achieve the expected shock absorption effect.

[0127] Of course, in the specific implementation process, it also includes dynamic characteristic tests, durability tests, temperature characteristic tests, automatic test system integration tests, etc. initiated for the shock absorber. By comparing the results of different dynamic characteristic tests, durability tests, temperature characteristic tests, and automatic test system integration tests with the theoretical model or simulation results, the deviations are identified and the valve train parameters (such as valve plate thickness, pre-tightening force) are adjusted, so as to achieve the expected shock absorption effect.

[0128] In the specific implementation process, the basic tuning of the shock absorber can be achieved through methods such as curve dynamometer diagrams and the relationship curve diagrams of damping force F and speed V, so as to meet the basic characteristics of the shock absorber. In the specific implementation process, it can also be further tuned through dynamic characteristic tests (covering the vehicle body vibration frequency band of 0.1 - 30 Hz), durability tests (simulating 100,000 km road tests), and temperature characteristic tests (verifying from -40°C to 120°C), etc., so as to achieve an effective tuning process for the shock absorber by superimposing corresponding tests according to different application scenarios, thereby improving the performance of the shock absorber.

[0129] Of course, in the specific implementation process, the comparison between the theoretical model or simulation results is to obtain the corresponding curves or structures through the simulation model, and then compare them with the test results to determine whether the requirements can be met. Details are not elaborated here specifically.

[0130] For example: In the dynamic characteristic test, a sine sweep signal is mainly applied through an exciter to measure the response amplitude of the shock absorber at different frequencies, and the resonance frequency and damping ratio are identified. Combining an acceleration sensor and a dynamic acquisition system, the vibration mode of the shock absorber structure is analyzed to verify the influence of the valve train on the system dynamics. In this durability test, the actual working conditions (such as cyclic loading tens of thousands of times) are mainly simulated on a test bench to test the damping force attenuation, sealability change, and fatigue characteristics of the tuned valve train. This temperature characteristic test is mainly to evaluate the performance stability of the valve train in different temperature environments. For example, in the range of -40°C to 120°C, the change curve of the damping force with temperature is tested, and the influence of the change in oil viscosity on the opening and closing characteristics of the valve train is analyzed; in this automatic test system integration test, a high-precision data acquisition card (such as PCIE - 1816H) and a displacement sensor are mainly used to capture the damping force and displacement signals in real time, evaluate the dynamic response of the valve train through spectrum analysis, and automatically generate a test report in combination with software, so as to facilitate improving the test efficiency, reducing human errors, and being applicable to batch verification of the tuned valve train.

[0131] Of course, in the specific implementation process, the present application also discloses a calibration system for a shock absorber valve system, which is used for calibrating the shock absorber valve system. The calibration system includes an electro-hydraulic servo universal testing machine and a shock absorber to be calibrated. The shock absorber to be calibrated is used to perform corresponding tests and calibrations on the electro-hydraulic servo universal testing machine. Among them, a shock absorber test bench is provided on the electro-hydraulic servo universal testing machine, and the shock absorber to be calibrated is used to be placed on the shock absorber test bench.

[0132] Specifically, as Figure 4 shown, the calibration system further includes a sensor assembly, a data acquisition assembly, and a controller assembly. Specifically, the sensor assembly, the data acquisition assembly, and the controller assembly are also all provided on the electro-hydraulic servo universal testing machine. Specifically, the sensor assembly is provided on the shock absorber to detect the vibration signal of the shock absorber. Among them, the sensor assembly may include a force sensor, a displacement sensor, and an accelerometer. The force sensor, the displacement sensor, and the accelerometer are all fixed on the shock absorber and are respectively used to detect the force signal, the displacement signal, and the acceleration signal of the shock absorber, which is convenient for calibrating the shock absorber valve system. The data acquisition assembly is used to communicate with the above-mentioned force sensor, displacement sensor, and accelerometer, so as to collect the force signal, the displacement signal, the acceleration signal, etc., and then send the relevant vibration signals to the controller assembly. The controller assembly executes the relevant steps of the calibration method as described above according to the relevant signals, which will not be elaborated in detail here. The controller assembly is connected to the data acquisition assembly and is used to receive the digital signal of the vibration signal and control and calibrate the shock absorber valve system according to the vibration data. For the specific calibration method, reference can be made to the relevant description in the above embodiments, which will not be elaborated in detail here.

[0133] Of course, in the specific implementation process, the data acquisition assembly includes a data acquisition card and a signal conditioning circuit. Among them, the data acquisition card is respectively communicatively connected to each sensor of the sensor assembly to collect the relevant signals of each sensor. The input end of the signal conditioning circuit is connected to the data acquisition card, and the output end of the signal conditioning circuit is connected to the controller assembly. And the signal conditioning circuit is used to amplify and filter the sensor signals. Specifically, the data acquisition card and the signal conditioning circuit can be integrated and used, such as a data acquisition system of PXIe-4330. For the specific reference, reference can be made to the relevant description of the prior art, which will not be elaborated in detail here.

[0134] Of course, in the specific implementation process, the electro-hydraulic servo universal testing machine in the application can be PWS-10, which is mainly a device for dynamic characteristic tests of materials and structures. Its main structure can be described in detail in combination with the above content:

[0135] 1. Electro-hydraulic servo system

[0136] The electro-hydraulic servo system includes a servo valve (such as the MOOG D631 series), a hydraulic cylinder, and a pump source. The servo valve is used to precisely control the flow direction and flow rate of hydraulic oil to achieve closed-loop control of force and displacement. The hydraulic cylinder, as an actuator, is used to apply dynamic loads or displacements. The pump source can adopt the Coburg CB series, which is used to provide hydraulic power and usually includes a main pump and an auxiliary pump to maintain the system pressure.

[0137] 2. Loading Frame MTS

[0138] The loading frame MTS generally includes a test bench frame and a loading arm. The loading arm mainly provides rigid support for installing specimens and loading devices. The loading arm is mainly used to apply loads and is usually connected to the hydraulic cylinder, enabling tensile, compressive, or bending loading.

[0139] 3. Sensor System

[0140] In the specific implementation process, the sensor system usually includes a force sensor, a displacement sensor, an acceleration sensor, a strain gauge, or a strain indicator. The force sensor can adopt the 9257B series sensors, which are mainly used to measure the applied force or load. The displacement sensor can adopt the edis series sensors, which are mainly used to measure the displacement or deformation of the specimen. The acceleration sensor can adopt the 8707A series sensors, which are mainly used to measure the acceleration response of the specimen. The strain gauge or strain indicator can adopt the YZ series strain gauges, which are mainly used to measure the strain of the specimen.

[0141] 4. Data Acquisition System

[0142] The data acquisition system can adopt the PXIe-4330 system, which generally includes a data acquisition card and a signal conditioning module. The data acquisition card is used to acquire sensor signals. The signal conditioning module is mainly used to amplify, filter, and process sensor signals. Of course, the relevant structures can all be realized in the prior art and will not be elaborated in detail here.

[0143] 5. Control System

[0144] The control system includes a control cabinet, a servo controller, and a software system. The control cabinet generally contains a control panel, a PLC (programmable logic controller), or a computer control system; the servo controller is mainly used to control the servo valve to achieve precise control of force and displacement. The software system is mainly used to set test parameters, control the test process, and acquire and analyze data.

[0145] 6. Specimen Installation Device MTS

[0146] The specimen installation device includes furniture and a centering device. Among them, the fixture is mainly used to fix the specimen to ensure its stability during the test. The centering device is mainly used to adjust the centering of the specimen to reduce the influence of eccentric loading.

[0147] 7. Auxiliary System

[0148] In the specific implementation process, the auxiliary system generally includes a hydraulic oil cooling system, a hydraulic oil filtration system, and a gas source system. Among them, the hydraulic oil cooling system is mainly used to cool the hydraulic oil to maintain the stability of the system temperature. The hydraulic oil filtration system is mainly used to filter impurities in the hydraulic oil to ensure the cleanliness of the system. The gas source system is mainly used to provide pneumatic control or auxiliary functions.

[0149] Of course, in the embodiments of the present application, the structural composition and description of the electro-hydraulic servo universal testing machine are not limited to the above embodiments. It may also include other related dynamic characteristic testing equipment such as exciters (such as LDS V455) and dynamic signal analyzers (such as NI PXIe-4499), which will not be elaborated in detail here. The relevant structures and function descriptions can also refer to the descriptions of electro-hydraulic servo universal testing machines disclosed in the prior art, and will not be repeated here.

[0150] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A tuning method for a shock absorber valve system, characterized in that, The calibration method includes: Collecting vibration data of the shock absorber valve system through a sensor component, and obtaining the frequency response function of the shock absorber valve system according to the vibration data; Establishing a mathematical dynamic model of the shock absorber valve system based on the vibration data, and describing the relationship between the parameters of the shock absorber valve system and the frequency response function; Using an optimization algorithm to optimize and adjust the valve system parameters to obtain a minimized vibration amplitude; Verifying through experiments whether the calibrated shock absorber valve system achieves the expected shock absorption effect.

2. The tuning method of the shock absorber valve system according to claim 1, characterized in that The step of collecting vibration data of the shock absorber valve system through a sensor component and obtaining the frequency response function of the shock absorber valve system according to the vibration data includes: Collecting the vibration input signal x(t) and the vibration output signal y(t) of the shock absorber valve system; Performing a fast Fourier transform on the vibration input signal x(t) and the vibration output signal y(t) to obtain the corresponding frequency domain representations X(f) and Y(f) respectively; According to the corresponding frequency domain representations X(f) and Y(f), obtaining the frequency response function H(w) = Y(f) / X(f).

3. The calibration method of the shock absorber valve system according to claim 2, characterized in that, When the shock absorber valve system is a single-degree-of-freedom system, the frequency response function is: H(w) = 1 / (k - mw^2 + jcw), where m is the mass, c is the damping coefficient, k is the stiffness, w = 2πf is the angular frequency, j is the imaginary unit, and is defined to represent the phase and amplitude relationship in frequency analysis.

4. The calibration method of the shock absorber valve system according to claim 3, characterized in that, If the vibration output signal y(t) is an acceleration response signal, the frequency response function is: H(w) = -w^2 / (k - mw^2 + jcw), where: m is the mass, c is the damping coefficient, k is the stiffness, w = 2πf is the angular frequency, j is the imaginary unit, and is defined to represent the phase and amplitude relationship in frequency analysis.

5. The calibration method of the shock absorber valve system according to claim 4, characterized in that Establishing a mathematical dynamic model of the shock absorber valve system based on the vibration data includes respectively establishing a single-degree-of-freedom system model and a multi-degree-of-freedom system model, where The motion equation of the single-degree-of-freedom system model is where m is the mass, c is the damping coefficient, k is the stiffness, x(t) is the displacement response, and F(t) is the external excitation force; The motion equation of the multi-degree-of-freedom system model is where M is the mass matrix, C is the damping matrix, K is the stiffness matrix, X(t) is the displacement vector, and F(t) is the external excitation force vector.

6. The tuning method of the shock absorber valve system according to claim 5, characterized in that, Describing the relationship between the parameters of the shock absorber valve system and the frequency response function includes: the relationship between stiffness and mass and the natural frequency, the relationship between the damping coefficient and vibration attenuation, and the relationship between the resonance amplitude and the damping coefficient, where The relationship expressions between stiffness, mass and natural frequency are That is, when the stiffness k increases, the natural frequency increases; when the mass m increases, the natural frequency decreases. The relational expression between the damping coefficient and the vibration attenuation is That is, when the damping c increases, the damping ratio increases, the resonance amplitude decreases, and the vibration attenuates faster; The relational expression of the resonance amplitude and the damping coefficient is Near the resonance frequency, the resonance amplitude is inversely proportional to the damping coefficient. The smaller the damping, the larger the resonance amplitude.

7. The calibration method of the shock absorber valve system according to claim 6, characterized in that, Using an optimization algorithm to optimize and adjust the valve system parameters includes: Obtaining the coefficients of the shock absorber valve system and substituting the coefficients into the optimization algorithm for iterative update; Adjusting the valve system parameters to minimize the error between the system response and the target performance, thereby optimizing to obtain a minimized vibration amplitude; the optimization algorithm is: Where ω is the inertia weight; c1, c2 are acceleration coefficients, c1 = c2 = 2; r1, r2 are random numbers within [0, 1]; P best is the historical optimal position of each particle, g best is the global optimal position of all particles in the particle swarm; The position of the i-th particle is x i , xi = [x i1 , x i2 ,..., x iD , where D is the dimension; The velocity of the i-th particle is v i , vi = [v i1 , v i2 , ..., v iD , where D is the dimension; the particle is each parameter combination of the vibrator valve system to be optimized. If the stiffness, damping coefficient, and pre-tightening force of the vibrator valve system to be optimized are k, c, and F0 respectively, then the position vector of the particle is P = [k, c, F0].

8. The calibration method of the shock absorber valve system according to claim 1, characterized in that The step of verifying through experiments whether the calibrated shock absorber valve system achieves the expected shock absorption effect includes: Making the shock absorber perform simple harmonic motion through a bench test at a predetermined stroke and frequency; Recording the damping force and displacement changes of the shock absorber and drawing the corresponding curve dynamometer diagram; Identifying the opening point of the shock absorber valve system according to the mutation point of the curve dynamometer diagram; Recording the damping force and speed changes of the shock absorber and drawing the corresponding relationship curve; Determining whether the calibrated shock absorber valve system achieves the expected shock absorption effect according to the opening point and the relationship curve.

9. A calibration system for a shock absorber valve system, used for calibrating the shock absorber valve system, characterized in that, It includes an electro-hydraulic servo universal testing machine, a shock absorber to be calibrated, a sensor component, a data acquisition component, and a controller component. The shock absorber to be calibrated is used to perform corresponding tests and calibrations on the electro-hydraulic servo universal testing machine, where A shock absorber test bench is provided on the electro-hydraulic servo universal testing machine, and the shock absorber to be calibrated is used to be placed on the shock absorber test bench; The sensor component is arranged on the shock absorber and is used to detect the vibration signal of the shock absorber; The data acquisition component is arranged inside the electro-hydraulic servo universal testing machine and is used to obtain and collect the vibration signals of the sensor component; The controller component is connected to the data acquisition component and is used to receive the digital signals of the vibration signals and control and calibrate the shock absorber valve system according to the vibration data.

10. The calibration system for the shock absorber valve train according to claim 1, characterized in that, The sensor component includes: a force sensor, a displacement sensor and an accelerometer. The force sensor, the displacement sensor and the accelerometer are all fixed on the shock absorber and are respectively used to detect the force signal, the displacement signal and the acceleration signal of the shock absorber, so as to facilitate the calibration of the shock absorber valve system.

Images