Pressure compensation system and method for a high performance throttle valve

Abstract

The application belongs to the field of valve control, and discloses a pressure compensation system and method of a high-performance throttle valve; the method comprises the following steps: collecting system operation data in real time; the system operation data comprises pressure data, vibration data, position data and temperature data; based on the system operation data, a bipolar control system is designed through a primary pilot valve and a secondary pilot valve; when a nonlinear impact working condition occurs, the bipolar control system is controlled by a sliding mode control compensation strategy; the position data is calibrated and tested; and the control effect of the throttle valve under complex working conditions is effectively improved.

Description

TECHNICAL FIELD

[0001] The present application belongs to the field of valve control, and more particularly, relates to a pressure compensation system and method for a high-performance throttling valve. BACKGROUND

[0002] The existing Chinese patent application with publication number CN117570071A discloses a valve part and a hydraulic system with the valve part, the valve part at least comprising a first hydraulic port and a second hydraulic port for supplying hydraulic fluid to a hydraulic consumer, the valve part having a valve core, a pressure channel and a collection channel, wherein the pressure channel can be connected to a pump of the hydraulic system, the valve core selectively connecting the first hydraulic port to the pressure channel and the second hydraulic port to the collection channel, or connecting the first hydraulic port to the collection channel and the second hydraulic port to the pressure channel, an inlet pressure compensator being arranged between the pressure channel and the valve core, and an outlet pressure compensator being arranged between the valve core and the collection channel, the inlet pressure compensator and the outlet pressure compensator being controllable via a signal pressure device, and an external additional force depending on an operating state of the hydraulic system acting on the signal pressure device at the hydraulic port connected to the collection channel to block the inlet pressure compensator.

[0003] The existing technology still has the following problems:

[0004] When the conventional throttling valve encounters large load changes, high pressure differences or high-speed operation, it is easy to produce impact, vibration or even the phenomenon of being unable to respond in time due to insufficient response or control accuracy, which affects the effectiveness of the throttling valve.

[0005] In view of this, the present application proposes a pressure compensation system and method for a high-performance throttling valve to solve the above problems. SUMMARY

[0006] In order to overcome the above-mentioned defects of the prior art, in order to achieve the above-mentioned purpose, the present application provides the following technical scheme: a pressure compensation method for a high-performance throttling valve, comprising:

[0007] Real-time acquisition of system operation data; the system operation data includes pressure data, vibration data, position data and temperature data;

[0008] Based on the system operation data, a dual-pole control system is designed through a primary pilot valve and a secondary pilot valve;

[0009] When a nonlinear impact working condition occurs, a sliding mode control compensation strategy is used to supplement the control of the dual-pole control system;

[0010] Calibration testing is performed on the position data.

[0011] Further, the pressure data includes pre-valve pressure and post-valve pressure; the vibration data includes vibration amplitude and vibration frequency of the main valve core; the position data is the position of the main valve core; and the temperature data includes ambient temperature and oil temperature.

[0012] The design method of the bipolar control system comprises:

[0013] Step A1, set the control mode of the primary pilot valve through the preset control logic; the control mode includes standby mode, advance mode, enhancement mode and compensation mode;

[0014] Step A2, starting from the time stamp of starting to execute the control mode, continuously read the position of the main valve core at the end of n unit time after the starting point, calculate the position difference of adjacent time points to obtain the position difference value; if the position difference value is less than the preset difference threshold, increase the control power of the primary pilot valve by the preset gain amplitude; if there is a position difference value greater than or equal to the preset difference threshold, reduce the control power of the primary pilot valve; n is a positive integer;

[0015] Step A3, determine whether to start phase reverse fine tuning of the main valve core according to the vibration data;

[0016] Step A4, when increasing the control power of the primary pilot valve by the preset gain amplitude, evaluate whether to use the secondary pilot valve.

[0017] Further, the sliding mode control compensation strategy specifically comprises:

[0018] Step D1, when the pressure difference is greater than the corresponding preset maximum threshold, the system is marked to enter the sliding mode control compensation area; in the sliding mode control compensation area, the sliding mode control branch logic is executed, and the pressure control signal of the main valve core is corrected by the sliding mode control compensation strategy;

[0019] Step D2, establish a sliding surface and set a state variable; the sliding surface is the weighted sum of the position difference value and the change rate of the position difference value of the main valve core;

[0020] Step D3, preset equivalent control parameters; the equivalent control parameters are continuous control amounts that keep the sliding surface equal to 0;

[0021] Step D4, switch the system through the sat() smoothing function to calculate and obtain switching control parameters;

[0022] Step D5, add the equivalent control parameters and the switching control parameters to synthesize the sliding mode compensation control amount, and compensate the original driving signal of the main valve core with the sliding mode compensation control amount.

[0023] Further, the judgment method of whether to start phase reverse fine tuning comprises:

[0024] If the vibration amplitude and the vibration frequency of the main valve core both exceed the corresponding preset threshold values, the phase reversal fine adjustment is started; otherwise, the phase reversal fine adjustment is not started.

[0025] Further, the pre-act mode is to enable the primary pilot valve according to a first gain; the enhanced mode is to enable the primary pilot valve according to a second gain; the first gain and the second gain are both preset gain powers, and the second gain power is greater than the first gain power; and the compensation mode includes:

[0026] When the ambient temperature or the oil temperature is greater than the corresponding preset maximum threshold value, the gain of the primary pilot valve is reduced by a preset amplitude;

[0027] When the ambient temperature or the oil temperature is less than the corresponding preset maximum threshold value, the output pressure of the primary pilot valve is increased by a preset amplitude.

[0028] Further, the evaluation method of whether to use the secondary pilot valve includes:

[0029] If, after m unit times of increasing the control power of the primary pilot valve by a preset gain amplitude, the position of the main valve core does not reach a preset target position, the secondary pilot amplification mode is entered, and the secondary pilot valve is started, i.e., the secondary pilot valve is switched from a standby state to a high-power output state; otherwise, the standby state of the secondary pilot valve is maintained; m is a positive integer;

[0030] If the position of the main valve core is less than a preset distance from the preset target position, the secondary pilot valve is switched from the high-power output state to the standby state.

[0031] Further, the preset control logic specifically includes:

[0032] Step B1, subtract the pressure before the valve from the pressure after the valve to obtain a pressure difference;

[0033] Step B2, if the pressure difference is less than a preset pressure difference threshold value and the temperature data is within a preset interval range, the control mode is adjusted to the pre-act mode; if the pressure difference is greater than or equal to the preset pressure difference threshold value and the temperature data is within the preset interval range, the control mode is adjusted to the enhanced mode; if the temperature data is not within the preset interval range, the control mode is adjusted to the compensation mode.

[0034] Further, the method steps of the calibration test include:

[0035] Step E1, move the main valve core to a mechanical limit position, and record the actual reading of the position sensor at this time;

[0036] Step E2, if the error between the actual reading and the theoretical position reading is greater than a threshold value, record the error in the controller for correction of the main valve core position reading.

[0037] Further, the pressure data is acquired by a pressure sensor; the vibration data is acquired by a vibration sensor; the position data is acquired by a magnetostrictive sensor; and the temperature data is acquired by a temperature sensor.

[0038] A pressure compensation system of a high-performance throttling valve, implementing a pressure compensation method of the high-performance throttling valve, comprising:

[0039] A data acquisition module is configured to acquire system operation data in real time; the system operation data comprises pressure data, vibration data, position data and temperature data.

[0040] A dual-pole control module is configured to design a dual-pole control system through a primary pilot valve and a secondary pilot valve based on the system operation data.

[0041] A sliding mode control module is configured to perform supplementary control on the dual-pole control system through a sliding mode control compensation strategy when a nonlinear impact working condition occurs.

[0042] An automatic calibration module is configured to calibrate and test the position data.

[0043] The pressure compensation system and method of the high-performance throttling valve have the following technical effects and advantages:

[0044] The dual-pole control system (primary pilot valve + secondary pilot valve) is constructed to enable the main valve core to be smoothly fine-tuned at a small load and quickly amplified to drive force at a large load; then the sliding mode control compensation strategy is used to perform supplementary control on the dual-pole control system for fine correction, so that the position of the main valve core can be quickly and accurately adjusted under high pressure difference and nonlinear impact, overshoot and oscillation are reduced, and the control effect of the throttling valve under complex working conditions is effectively improved.

[0045] Four control modes (standby mode, advance mode, enhanced mode and compensation mode) are provided; when the temperature is high, the system automatically reduces the gain to avoid impact caused by excessive sensitivity of the valve core; when the temperature is low or the viscosity rises, the output pressure of the pilot valve is moderately increased to overcome the viscous resistance; in this way, the control effect can be kept relatively stable regardless of the temperature.

[0046] The automatic calibration module provides the position correction capability of the system after long-term use, overcomes the deviation accumulation caused by mechanical wear, sensor drift, thermal expansion and cold contraction, significantly reduces the maintenance time, and improves the economic benefit of the throttling valve. BRIEF DESCRIPTION OF DRAWINGS

[0047] Figure 1 FIG. 1 is a schematic diagram of a pressure compensation system of a high-performance throttling valve according to Embodiment 1 of the present application;

[0048] Figure 2A flow chart of a pressure compensation method for a high-performance throttle valve of embodiment 2 of the present application;

[0049] Figure 3 A flow chart of a design method for a dual-pole control system of embodiment 1 of the present application;

[0050] Figure 4 A flow chart of a sliding mode control compensation strategy of embodiment 1 of the present application. DETAILED DESCRIPTION

[0051] The technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by a person of ordinary skill in the art without creative work fall within the scope of protection of the present application.

[0052] Embodiment 1

[0053] Please refer to Figure 1 As shown in the figure, the pressure compensation system of the high-performance throttle valve described in the present embodiment comprises a data acquisition module, a dual-pole control module, a sliding mode control module and an automatic calibration module, and each module is connected through wired and / or wireless connection.

[0054] The data acquisition module is used for acquiring system running data in real time; the system running data comprises pressure data, vibration data, position data and temperature data;

[0055] The pressure data comprises pre-valve pressure and post-valve pressure; the vibration data comprises vibration amplitude and vibration frequency of the main valve core; the position data is the position of the main valve core; and the temperature data comprises ambient temperature and oil temperature. In a hydraulic system, pressure directly reflects the load size, oil line resistance and fluid environment borne by the valve port. By acquiring pressure data, the subsequent dual-pole pilot valve sensing system can perceive the current pressure, so as to adaptively adjust the thrust size of the main valve core. For example, when the pre-valve pressure rises and the post-valve pressure drops, the pilot valve needs to adjust the output pressure in time to avoid over-shooting of the main valve core. At the same time, by acquiring pressure data, the subsequent dual-pole control module and sliding mode control module can obtain the deviation between the current pressure data and the pressure target value, so as to execute different instructions (dual-pole control system and sliding mode control compensation strategy) and avoid compensation in a blind state.

[0056] By acquiring the main valve core position, it is helpful to judge the difference between the set position and the actual position in the subsequent bipolar control module; in high-performance throttle valves, the main valve core often needs to act under high speed and frequent conditions, which may produce vibration, impact or flutter; excessive vibration not only causes the valve core to be positioned inaccurately and noise to increase, but also accelerates the mechanical wear of the valve core and valve sleeve, and even destroys the system stability; by acquiring the vibration amplitude and frequency of the main valve core, it is helpful for the system to identify whether flutter, resonance or other unsafe impact fluctuations occur, so as to make corresponding phase-reversing compensation.

[0057] The oil viscosity is closely related to the temperature, the higher the oil temperature, the lower the oil viscosity, and the flow resistance and valve core friction will be reduced; the metal material (such as valve core, valve body) will also expand and contract with the external environmental temperature and internal oil temperature, causing the fitting gap to change slightly; when the oil temperature is detected to be high, the viscosity is low, the valve core is often more flexible, and the control gain needs to be reduced to prevent overshoot; and when the temperature is low, the viscosity is high, the valve core is more difficult to move, and the gain or pilot valve pressure needs to be moderately increased to overcome the viscous resistance.

[0058] The pressure data is acquired by a pressure sensor; one installation port is arranged on the pipeline near the valve body inlet and the pipeline downstream of the valve body, and the sensor is fixed at the installation port to detect and acquire the pressure data.

[0059] The vibration data is acquired by a vibration sensor; the position data is acquired by a magnetostrictive sensor; and the temperature data is acquired by a temperature sensor.

[0060] The bipolar control module is based on system operation data, and a bipolar control system is designed through a primary pilot valve and a secondary pilot valve to realize automatic adjustment of the main valve core.

[0061] The primary pilot valve is used to perform preliminary sensing and small-range adjustment of the system pressure, and provides a moderate and gentle driving force for the main valve core; the secondary pilot valve is used to increase the control force of the main valve core when the system detects a large flow or high pressure difference demand, so that the main valve core can quickly reach the target position in a short time; through the two-stage structure, the system can not only avoid impact and lag caused by large flow or pressure change, but also quickly respond under extreme conditions to maintain the required throttling effect and pressure compensation performance.

[0062] Referring to Figure 3 The design method of the bipolar control system includes:

[0063] Step A1, set the control mode of the primary pilot valve through the preset control logic; the control mode includes standby mode, advance mode, enhancement mode and compensation mode; the advance mode is to smoothly enable the primary pilot valve according to a first-stage gain; the enhancement mode is to quickly enable the primary pilot valve according to a second-stage gain, so as to prepare for subsequent secondary amplification of the main valve core; the first-stage gain and the second-stage gain are both preset gain powers, and the second-stage gain power is greater than the first-stage gain power;

[0064] The compensation mode specifically includes:

[0065] When the ambient temperature or the oil temperature is greater than the corresponding preset maximum threshold value, the oil viscosity decreases, the valve core may become too flexible, leading to too fast response, which may cause overshoot or instability; the system reduces the primary pilot valve gain by a preset amplitude to reduce the output pressure, so as to avoid rapid overshoot;

[0066] When the ambient temperature or the oil temperature is less than the corresponding preset maximum threshold value, the oil viscosity increases, the valve core movement becomes slow; the system increases the output pressure of the primary pilot valve by a preset amplitude to ensure that the valve core can still respond quickly in a high-viscosity environment, and also helps to ensure that the main valve core moves smoothly.

[0067] The preset control logic specifically includes:

[0068] Step B1, subtract the pressure before the valve from the pressure after the valve to obtain a pressure difference;

[0069] Step B2, if the pressure difference is less than a preset pressure difference threshold value and the temperature data is within a preset interval range, the control mode is adjusted to the advance mode; if the pressure difference is greater than or equal to the preset pressure difference threshold value and the temperature data is within the preset interval range, the control mode is adjusted to the enhancement mode; if the temperature data is not within the preset interval range, the control mode is adjusted to the compensation mode.

[0070] Step A2, starting from the time stamp of starting to execute the control mode, continuously read the main valve core positions at the end of n unit times after the starting point, calculate the main valve core position differences at adjacent time points, and obtain the position difference values; if all the position difference values are less than a preset difference threshold value, it indicates that the main valve core has not moved or moves slowly, reflecting that the power of the primary pilot valve is not enough, so the control power of the primary pilot valve is increased by a preset gain amplitude; if there is a position difference value greater than or equal to the preset difference threshold value, it indicates that the main valve core has obviously moved and is close to the set opening, so the control power of the primary pilot valve is reduced to reduce the pressure output and prevent overshoot; n is a positive integer;

[0071] Step A3, determine whether to start phase reverse fine adjustment of the main valve core according to the vibration data; the method for determining whether to start phase reverse fine adjustment includes:

[0072] If the vibration amplitude and the vibration frequency of the main valve core both exceed the corresponding preset threshold values, it indicates that the main valve core is started too violently, and the phase reverse fine adjustment is started; otherwise, the phase reverse fine adjustment is not started.

[0073] It should be noted that the purpose of determining whether to start the phase reverse fine adjustment is to enable the main valve core to smoothly leave the static state or to only maintain small amplitude adjustment through the primary pilot valve under low load working conditions without generating obvious impact.

[0074] Step A4: When the control power of the primary pilot valve is increased by the preset gain amplitude, it is further evaluated whether to use the secondary pilot valve to achieve greater driving to ensure that the main valve core can still respond quickly under high load or large flow conditions; the evaluation method of whether to use the secondary pilot valve includes:

[0075] If the main valve core position does not reach the preset target position after m unit times after the control power of the primary pilot valve is increased by the preset gain amplitude, it indicates that the power of the primary pilot valve is still insufficient, and then the secondary pilot amplification mode is entered, and the secondary pilot valve is started, i.e., the secondary pilot valve is switched from the standby state to the high-power output state, so that the secondary pilot valve exerts greater oil pressure on the main valve core in a short time; otherwise, the standby state of the secondary pilot valve is maintained; m is a positive integer;

[0076] When the main valve core position is less than the preset distance from the preset target position, the secondary pilot valve is switched from the high-power output state to the standby state.

[0077] The sliding mode control module supplements the control of the bipolar control system through a sliding mode control compensation strategy when a nonlinear impact working condition occurs, thereby reducing the overshoot and oscillation of the main valve core; the nonlinear impact working condition is that the pressure difference is greater than the corresponding preset maximum threshold value;

[0078] Please refer to Figure 4 The sliding mode control compensation strategy specifically includes:

[0079] Step D1: When the pressure difference is greater than the corresponding preset maximum threshold value, the system immediately marks that it enters the sliding mode control compensation zone to prevent the bipolar control system from being insufficient to suppress large amplitude oscillation; the sliding mode control branch logic is executed in the sliding mode control compensation zone, so that the pressure control signal of the main valve core is corrected by the sliding mode control compensation strategy;

[0080] Step D2: A sliding surface is established and a state variable is set; the sliding surface is a weighted sum of the position difference of the main valve core and the change rate of the position difference; when the sliding surface is equal to 0, it indicates that the system is on the sliding surface; the purpose of the sliding mode control is to enable the system state to approach and remain on the sliding surface where the sliding surface is equal to 0;

[0081] It should be noted that the position deviation rate is: the position difference corresponding to the current time minus the position difference corresponding to the last time, and then divided by the position difference corresponding to the last time.

[0082] It should be noted that the sliding surface is a quantitative data of the deviation degree of the ideal state of the system, and the sliding surface equal to 0 indicates that the oscillation is effectively suppressed.

[0083] Step D3, preset an equivalent control parameter, which is a continuous control amount for keeping the sliding surface equal to 0 when the system approaches the sliding surface;

[0084] Step D4, the system is adjusted by a sat() smoothing function to calculate a switching control parameter; the purpose is to provide a corresponding compensation force when the sliding surface is not 0, so that the sliding surface returns to 0;

[0085] Step D5, add the equivalent control parameter and the switching control parameter to synthesize a sliding compensation control amount, and compensate the original driving signal of the main valve core with the sliding compensation control amount, so that in the case of nonlinear impact of large pressure difference, the main valve core will not have a serious overshoot or oscillation by relying on the conventional control, but will realize smooth transition through the rapid correction of the sliding compensation control amount.

[0086] An automatic calibration module is used to calibrate the position data, reduce the cumulative error after long-term work, and improve the accuracy of the bipolar control system and the sliding mode control compensation strategy.

[0087] Under high frequency and long period of use, the signal of the sensor may drift, and the valve core positioning may change slightly due to wear or thermal expansion and contraction; through the automatic calibration module, these errors are periodically confirmed and corrected to ensure control accuracy.

[0088] The method steps of the calibration test include:

[0089] Step E1, slowly move the main valve core to the mechanical limit position, and record the actual reading of the position sensor at this time;

[0090] Step E2, if the error between the actual reading and the theoretical position reading is greater than a threshold value, record the error in the controller for correction of the main valve core position reading.

[0091] Embodiment 2

[0092] Please refer to Figure 2 The embodiment provides a pressure compensation method for a high-performance throttle valve, which comprises:

[0093] Real-time acquisition of system operation data; the system operation data includes pressure data, vibration data, position data and temperature data;

[0094] Based on system operation data, a bipolar control system is designed through a primary pilot valve and a secondary pilot valve;

[0095] When a nonlinear impact working condition occurs, a supplementary control is performed on the bipolar control system through a sliding mode control compensation strategy.

[0096] The position data is calibrated and tested.

[0097] Embodiment 3

[0098] In order to further improve the automation and adaptive ability of the sliding mode control, the application further provides a pressure compensation method of a high-performance throttle valve; by training a sliding mode control model, the original sliding mode control compensation strategy is replaced, a large amount of historical data can be further utilized to improve the response in a nonlinear scene, and a "sliding mode surface" does not need to be manually designed; the training method of the sliding mode control model comprises:

[0099] z groups of sliding mode data sets are obtained, the sliding mode data set comprises a pressure difference, a position difference value, a position difference value change rate and a corresponding sliding mode compensation control amount; the sliding mode data set is taken as a sample set, the sample set is divided into a training set and a test set; an RNN classifier is constructed, the pressure difference, the position difference value and the position difference value change rate in the training set are taken as inputs of the sliding mode control model, the corresponding sliding mode compensation control amount in the training set is taken as a target output, the classifier is iteratively trained to obtain a preliminary control model; the preliminary control model is tested by using the test set, if the accuracy of the preliminary control model meets a preset accuracy, the preliminary control model is taken as the sliding mode control model; the preliminary control model is an RNN neural network model; z is a positive integer greater than 1.

[0100] In actual operation, when the system detects that the "pressure difference is greater than a preset maximum threshold value", the trained sliding mode control model can be directly called to adaptively handle the nonlinear working condition, and the adaptive ability of the system is further enhanced, and the stability of the throttle valve during operation is improved.

[0101] The above-described embodiments are only used to illustrate the technical solutions of the present application, and not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that the technical solutions recorded in the foregoing embodiments can be modified, or some technical features can be replaced by equivalents; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present application, and should be included in the protection scope of the present application.

Claims

1. A pressure compensation method for a high-performance throttle valve, characterized in that, include: The system collects operational data in real time; the operational data includes pressure data, vibration data, position data, and temperature data; the pressure data includes inlet and outlet pressures; the vibration data includes the vibration amplitude and frequency of the main valve core; the position data includes the position of the main valve core; and the temperature data includes ambient temperature and oil temperature. Based on system operation data, a bipolar control system is designed using a primary pilot valve and a secondary pilot valve. The design method for the bipolar control system includes: Step A1: Set the control mode of the primary pilot valve through preset control logic; the control mode includes standby mode, pilot mode, enhancement mode and compensation mode; Step A2: Starting from the timestamp of the start of the control mode, continuously read the main valve core position at the end of n unit time points after the start point, calculate the difference in main valve core position between adjacent time points, and obtain the position difference value; if the position difference value is less than the preset difference threshold, increase the control power of the primary pilot valve by the preset gain amplitude; if there is a position difference value greater than or equal to the preset difference threshold, decrease the control power of the primary pilot valve; where n is a positive integer. Step A3: Based on the vibration data, determine whether to initiate phase reverse fine-tuning of the main valve core; Step A4: When increasing the control power of the primary pilot valve by the preset gain amplitude, evaluate whether to use the secondary pilot valve; When nonlinear impact conditions occur, a sliding mode control compensation strategy is used to supplement the bipolar control system. The location data was calibrated and tested.

2. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The sliding mode control compensation strategy specifically includes: Step D1: When the pressure difference is greater than the corresponding preset maximum threshold, the system marks the entry into the sliding mode control compensation zone; in the sliding mode control compensation zone, the sliding mode control branch logic is executed, and the pressure control signal of the main valve core is corrected by the sliding mode control compensation strategy. Step D2: Establish the sliding surface and set the state variables. The sliding surface is the weighted sum of the position difference of the main valve core and the rate of change of the position difference. Step D3: Preset equivalent control parameters, wherein the equivalent control parameters are continuous control quantities that keep the sliding surface equal to 0 in the system; Step D4: Perform on / off regulation of the system using the SAT smoothing function and calculate and obtain the switching control parameters; Step D5: Add the equivalent control parameters and the switching control parameters to synthesize the sliding mode compensation control quantity, and use the sliding mode compensation control quantity to compensate the original drive signal of the main valve core.

3. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The method for determining whether to initiate phase reversal fine-tuning includes: If the vibration amplitude and vibration frequency of the main valve core both exceed the corresponding preset threshold, phase reverse fine adjustment will be initiated; otherwise, phase reverse fine adjustment will not be initiated.

4. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The pilot mode is to activate the primary pilot valve according to the first-level gain. The enhancement mode is to activate the primary pilot valve according to the secondary gain; Both the primary gain and the secondary gain are preset gain powers, with the secondary gain power being greater than the primary gain power. The compensation mode includes: When the ambient temperature or oil temperature exceeds the corresponding preset maximum threshold, the gain of the primary pilot valve is reduced by a preset amount. When the ambient temperature or oil temperature is lower than the corresponding preset maximum threshold, the output pressure of the primary pilot valve is increased by a preset amount.

5. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The evaluation method for whether to use a secondary pilot valve includes: If, after increasing the control power of the primary pilot valve by the preset gain amplitude for m unit time intervals, the main valve core position has not reached the preset target position, then the secondary pilot amplification mode is entered, and the secondary pilot valve is activated, that is, the secondary pilot valve is switched from the standby state to the high power output state; otherwise, the standby state of the secondary pilot valve is maintained; m is a positive integer. If the main valve core position is less than the preset target position by a preset distance, the secondary pilot valve will switch from high power output state to standby state.

6. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The preset control logic specifically includes: Step B1: Subtract the inlet pressure from the outlet pressure to obtain the pressure difference; Step B2: If the pressure difference is less than the preset pressure difference threshold and the temperature data is within the preset range, the control mode is adjusted to the pre-emptive mode; if the pressure difference is greater than or equal to the preset pressure difference threshold and the temperature data is within the preset range, the control mode is adjusted to the enhanced mode; if the temperature data is not within the preset range, the control mode is adjusted to the compensation mode.

7. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The calibration test method includes the following steps: Step E1: Move the main valve core to the mechanical limit position and record the actual reading of the position sensor at this time; Step E2: If the error between the actual reading and the theoretical position reading is greater than the threshold, the error is recorded in the controller for correction of the main valve core position reading.

8. The pressure compensation method for a high-performance throttle valve according to claim 1, characterized in that, The pressure data is acquired through a pressure sensor; the vibration data is acquired through a vibration sensor; the position data is acquired through a magnetostrictive sensor; and the temperature data is acquired through a temperature sensor.

9. A pressure compensation system for a high-performance throttle valve, implementing the pressure compensation method for a high-performance throttle valve according to any one of claims 1-8, characterized in that, include: The data acquisition module is used to collect system operation data in real time. The system operating data includes pressure data, vibration data, position data, and temperature data; A bipolar control module is designed based on system operation data, using a primary pilot valve and a secondary pilot valve to create a bipolar control system. The sliding mode control module supplements the bipolar control system with a sliding mode control compensation strategy when nonlinear impact conditions occur. The automatic calibration module performs calibration tests on the location data.

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