Large-flow oil supply dynamic pressure control and instantaneous flow compensation method and system

Abstract

The invention discloses a high-flow oil supply dynamic pressure control and instantaneous flow compensation method and system, and relates to the technical field of automatic control. The problems of effectively realizing flow regulation and pressure stability control in a large-flow servo system are solved. The method comprises the following steps: constructing a mathematical model of the large-flow energy accumulator group; a large-flow cartridge valve pressure control model is built according to the large-flow energy accumulator set mathematical model; constructing an advanced controller; the cartridge valve is adjusted according to the advanced controller, the control quantity output by the energy accumulator is controlled through the cartridge valve, and flow compensation is achieved. The method is applied to the field of ultra-large test piece analogue simulation.

Description

Technical Field

[0001] The invention relates to the field of automatic control technology, and in particular to a large-flow oil supply dynamic pressure control and instantaneous flow compensation method. Background Art

[0002] When testing super-large specimens such as bridge force bearings, heavy-duty loading test benches are usually used to study the response and failure mode under static and dynamic loads. One of the key goals of these tests is to evaluate the load-bearing capacity, deformation behavior, and failure mechanism of large components under extreme conditions. In order to simulate the real working environment, the test bench needs to be able to provide different types and sizes of loads, especially under high-speed conditions, where the system hydraulic oil demand is extremely large. According to relevant research and practical experience, the oil flow demand of the hydraulic system at high speed can reach 45,000L / min, which places extremely high demands on the design and control of the hydraulic system.

[0003] However, current technology has not yet been able to effectively achieve flow regulation and pressure stability control in servo systems with such large flows. In oil supply systems with smaller flows, multiple accumulators are usually used in conjunction with the oil supply system to regulate the flow to ensure that the system can cope with instantaneous load changes during the test. This method can cope with fluctuations in oil demand to a certain extent, but the problem is more complicated under large flow conditions. Especially in the case of large flows, load changes may cause more drastic flow fluctuations, which in turn have a significant impact on the oil supply pressure. Studies have shown that in this case, the pressure fluctuation of the oil supply system can reach up to about 10%, which poses a great challenge to the stability and accuracy of the hydraulic system. Summary of the invention

[0004] The present invention aims at effectively realizing the flow regulation and pressure stability control in a large flow servo system, and proposes a large flow oil supply dynamic pressure control and instantaneous flow compensation method, the method comprising:

[0005] Construct mathematical model of large flow accumulator group;

[0006] The pressure control model of the large flow cartridge valve is constructed based on the mathematical model of the large flow accumulator group;

[0007] Build a look-ahead controller;

[0008] The cartridge valve is adjusted according to the advance controller, and the control amount output by the accumulator is controlled through the cartridge valve to achieve flow compensation.

[0009] Furthermore, a preferred method is proposed, wherein the mathematical model of the large flow accumulator group is constructed, including:

[0010] P m×(a×V01+V02) n1 =P0×(V01+V02) n1

[0011] P m ×(a×V01+V02) n2 =P1×(b×V01+V02) n2

[0012] (b×V01+V02)-(a×V01+V02)=V1-V2=DV

[0013] DV=∫Qdt

[0014] Among them, V01 is the volume of the accumulator, V02 is the volume of the nitrogen bottle, P0 is the initial charging pressure, P m is the maximum filling pressure, Q is the discharge flow, DV is the discharge volume, P1 is the current internal oil pressure value of the large flow accumulator group, b is the relative height of the liquid level, a is the filling pressure to P m The internal liquid level of the accumulator.

[0015] Furthermore, a preferred method is proposed, in which the pressure control model of the large flow cartridge valve is:

[0016]

[0017] Among them, Q is the flow rate of the cartridge valve, Q2 is the output flow rate, Q p Provide flow for oil source pump station, Q L is the servo valve flow rate, V t is the pipeline volume, B e is the bulk elastic modulus, P2 is the cartridge valve output pressure, and t is the time.

[0018] Furthermore, a preferred embodiment is proposed, wherein the output pressure of the cartridge valve is:

[0019]

[0020] Among them, V 0l is the initial inflation volume, P 0l is the initial inflation pressure.

[0021] Furthermore, a preferred embodiment is proposed, wherein the flow rate of the servo valve is:

[0022]

[0023] Among them, k ql is the flow gain of the actuator servo valve, P l is the load voltage drop.

[0024] Furthermore, a preferred embodiment is proposed, wherein the lead controller is:

[0025]

[0026] Among them, T is the time turning coefficient and a is the gain coefficient.

[0027] Furthermore, a preferred method is also proposed, in which the cartridge valve is adjusted according to the advance controller, including:

[0028] J = ∫α i β i Δi=1,…,n

[0029] Among them, α i is energy, β i is the weighted amount for each cartridge valve opening, Δ is the adjustment amount output by the advance controller, and n is the number of cartridge valves.

[0030] Based on the same inventive concept, the present invention also proposes a large flow oil supply dynamic pressure control and instantaneous flow compensation system, the system comprising:

[0031] An accumulator group model building unit is used to build a mathematical model of a large flow accumulator group;

[0032] A cartridge valve pressure control model building unit, used for building a large flow cartridge valve pressure control model according to a large flow accumulator group mathematical model;

[0033] A look-ahead controller building unit, used for building a look-ahead controller;

[0034] The flow compensation unit is used to adjust the cartridge valve according to the advance controller, and control the control amount output by the accumulator through the cartridge valve to achieve flow compensation.

[0035] Based on the same inventive concept, the present invention also proposes a computer device, including a memory and a processor, wherein the memory stores a computer program. When the processor runs the computer program stored in the memory, the processor executes a large-flow oil supply dynamic pressure control and instantaneous flow compensation method described in any one of the above items.

[0036] Based on the same inventive concept, the present invention also proposes a computer-readable storage medium, on which a computer program is stored. When the computer program is run by a processor, the steps of a large-flow oil supply dynamic pressure control and instantaneous flow compensation method as described in any one of the above are executed.

[0037] The present invention is beneficial in that:

[0038] The invention solves the problem that flow regulation and pressure stability control cannot be effectively realized in a large flow servo system.

[0039] The present invention proposes a method for dynamic pressure control and instantaneous flow compensation of large flow oil supply. By constructing a mathematical model of a large flow accumulator group, the behavior of the accumulator is accurately modeled. Through this mathematical model, the performance of the accumulator under different load and flow change conditions can be more accurately predicted and controlled, thereby providing a theoretical basis for subsequent pressure control and flow compensation. This modeling design improves the accuracy and reliability of the system. As a high-precision flow and pressure control element, the cartridge valve can effectively adjust the pressure of the system through linkage with the accumulator group to ensure that the pressure of the oil supply system always remains within a stable range when the flow changes drastically. The high responsiveness of the cartridge valve enables it to quickly adjust to flow changes, thereby realizing dynamic pressure control. By constructing an advance controller, the present invention realizes the prediction and advance adjustment of flow and pressure fluctuations. In traditional feedback control, the system will only be adjusted after the fluctuation occurs, while the advance control can respond in advance according to the trend of load changes, thereby reducing the hysteresis of pressure fluctuations and flow regulation. This advance compensation mechanism greatly improves the stability of the system under high load and high flow conditions.

[0040] Furthermore, the method proposed in the present invention realizes dynamic compensation of flow rate by adjusting the control amount of the cartridge valve to control the output of the accumulator. When the flow demand changes drastically, the hydraulic system can respond quickly and perform flow compensation through the output of the accumulator to ensure the stable operation of the hydraulic system. This technology can significantly reduce the pressure fluctuation in the system and avoid the phenomenon of insufficient supply or pressure overload caused by too fast flow changes in traditional methods.

[0041] Furthermore, by precisely controlling the pressure and flow fluctuations of the large flow oil supply system, the method proposed in the present invention can ensure that the response and failure mode research under load during the test can be carried out under more stable conditions, thereby improving the accuracy and reliability of the test data. This is particularly important for the test of super-large bridge components or other similar super-large specimens.

[0042] The present invention is applied to the field of super-large test piece simulation. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Figure 1 It is a schematic diagram of a large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method according to the first embodiment;

[0044] Figure 2 This is a layout diagram of a large flow accumulator group according to the eleventh embodiment;

[0045] Figure 3The oil source layout diagram described in Implementation Mode 11;

[0046] Figure 4 It is a schematic diagram of the dynamic pressure control and terminal instantaneous flow compensation control strategy described in the eleventh embodiment;

[0047] Figure 5 This is a diagram showing the pressure fluctuation results in the pipeline when a large flow rate of oil is supplied according to the eleventh embodiment. DETAILED DESCRIPTION

[0048] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, 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, not all of the embodiments.

[0049] Implementation method 1, see Figure 1 The present embodiment describes a method for dynamic pressure control and instantaneous flow compensation of large flow oil supply, the method comprising:

[0050] Construct mathematical model of large flow accumulator group;

[0051] The pressure control model of the large flow cartridge valve is constructed based on the mathematical model of the large flow accumulator group;

[0052] Build a look-ahead controller;

[0053] The cartridge valve is adjusted according to the advance controller, and the control amount output by the accumulator is controlled through the cartridge valve to achieve flow compensation.

[0054] The present embodiment proposes a method for dynamic pressure control and instantaneous flow compensation of large flow oil supply, which accurately models the behavior of the accumulator by constructing a mathematical model of a large flow accumulator group. Through this mathematical model, the performance of the accumulator under different load and flow change conditions can be more accurately predicted and controlled, thereby providing a theoretical basis for subsequent pressure control and flow compensation. As a high-precision flow and pressure control element, the cartridge valve can effectively adjust the pressure of the system through linkage with the accumulator group to ensure that the pressure of the oil supply system always remains within a stable range when the flow changes drastically. The high responsiveness of the cartridge valve enables it to quickly adjust to flow changes, thereby realizing dynamic pressure control. By constructing an advance controller, the prediction and advance adjustment of flow and pressure fluctuations are realized. In traditional feedback control, the system will only be adjusted after the fluctuation occurs, while the advance control can respond in advance according to the trend of load changes, thereby reducing the lag of pressure fluctuations and flow regulation. This advance compensation mechanism greatly improves the stability of the system under high load and high flow conditions.

[0055] Furthermore, the method proposed in this embodiment realizes dynamic compensation of flow rate by adjusting the control amount of the cartridge valve to control the output of the accumulator. When the flow demand changes drastically, the hydraulic system can respond quickly and perform flow compensation through the output of the accumulator to ensure the stable operation of the hydraulic system. This technology can significantly reduce the pressure fluctuations in the system and avoid the phenomenon of insufficient supply or pressure overload caused by too fast flow changes in traditional methods.

[0056] Furthermore, by precisely controlling the pressure and flow fluctuations of the large flow oil supply system, the method proposed in this embodiment can ensure that the response and failure mode research under load during the test can be carried out under more stable conditions, thereby improving the accuracy and reliability of the test data. This is particularly important for the test of super-large bridge components or other similar super-large specimens.

[0057] Embodiment 2: This embodiment further limits the large flow oil supply dynamic pressure control and instantaneous flow compensation method described in embodiment 1. The construction of a large flow accumulator group mathematical model includes:

[0058] P m ×(a×V01+V02) n1 =P0×(V01+V02) n1

[0059] P m ×(a×V01+V02) n2 =P1×(b×V01+V02) n2

[0060] (b×V01+V02)-(a×V01+V02)=V1-V2=DV

[0061] DV=∫Qdt

[0062] Among them, V01 is the volume of the accumulator, V02 is the volume of the nitrogen bottle, P0 is the initial charging pressure, P m is the maximum filling pressure, Q is the discharge flow, DV is the discharge volume, P1 is the current internal oil pressure value of the large flow accumulator group, b is the relative height of the liquid level, a is the filling pressure to P m The internal liquid level of the accumulator.

[0063] Implementation method 3: This implementation method is a further limitation of the large flow oil supply dynamic pressure control and instantaneous flow compensation method described in implementation method 1. The large flow cartridge valve pressure control model is:

[0064]

[0065] Among them, Q is the flow rate of the cartridge valve, Q2 is the output flow rate, Qp Provide flow for oil source pump station, Q L is the servo valve flow rate, V t is the pipeline volume, B e is the bulk elastic modulus, P2 is the cartridge valve output pressure, and t is the time.

[0066] Embodiment 4: This embodiment further limits the large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method described in embodiment 3. The output pressure of the cartridge valve is:

[0067]

[0068] Among them, V 0l is the initial inflation volume, P 0l is the initial inflation pressure.

[0069] Embodiment 5: This embodiment further limits the large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method described in embodiment 3. The servo valve flow rate is:

[0070]

[0071] Among them, k ql is the flow gain of the actuator servo valve, P l is the load voltage drop.

[0072] Embodiment 6: This embodiment further limits the large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method described in embodiment 1, and the advance controller is:

[0073]

[0074] Among them, T is the time turning coefficient and a is the gain coefficient.

[0075] Embodiment 7: This embodiment further limits the large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method described in embodiment 1, and adjusts the cartridge valve according to the advance controller, including:

[0076] J = ∫α i β i Δi=1,…,n

[0077] Among them, α i is energy, β i is the weighted amount for each cartridge valve opening, Δ is the adjustment amount output by the advance controller, and n is the number of cartridge valves.

[0078] Embodiment 8: A large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation system described in this embodiment, the system comprises:

[0079] An accumulator group model building unit is used to build a mathematical model of a large flow accumulator group;

[0080] A cartridge valve pressure control model building unit, used for building a large flow cartridge valve pressure control model according to a large flow accumulator group mathematical model;

[0081] A look-ahead controller building unit, used for building a look-ahead controller;

[0082] The flow compensation unit is used to adjust the cartridge valve according to the advance controller, and control the control amount output by the accumulator through the cartridge valve to achieve flow compensation.

[0083] Embodiment 9. A computer device described in this embodiment includes a memory and a processor, wherein the memory stores a computer program. When the processor runs the computer program stored in the memory, the processor executes a large-flow oil supply dynamic pressure control and instantaneous flow compensation method described in any one of embodiments 1 to 7.

[0084] Embodiment 10. A computer-readable storage medium described in this embodiment stores a computer program, and when the computer program is executed by a processor, the steps of a large-flow oil supply dynamic pressure control and instantaneous flow compensation method as described in any one of embodiments 1 to 7 are executed.

[0085] Implementation method 11: See Figures 2 to 5 This embodiment provides a specific example of a large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method described in the first embodiment, and is also used to explain the second to seventh embodiments, specifically:

[0086] like Figure 2 The layout diagram of the large flow accumulator group in the heavy-duty tonnage loading test bench shown in the figure shows that there are three types of accumulators. One is the large flow accumulator, which is the main flow supply. It is regulated and controlled by several cartridge valves. The flow can be adjusted by controlling the valve core stroke regulator on the cover plate. One is the high-pressure accumulator, and the other is the accumulator on the pipeline. These two types of accumulators are used to supplement the flow at different positions of the pipeline.

[0087] Figure 3 The layout diagram of the oil source components of the system is shown. During the test bench test, the average oil supply is mainly provided by the oil source, and the oil supply is supplemented by the accumulator group during the peak flow, and absorbs part of the pressure pulsation caused by the load pressure drop. There are many accumulator groups, and multiple cartridge valves are used for control, that is, the execution control mechanism is multiple cartridge valves, and the output uses a pressure sensor.

[0088] In this implementation, a mathematical model of a large flow accumulator group is first constructed:

[0089] P m ×(a×V01+V02) n1 =P0×(V01+V02) n1 (1)

[0090] P m ×(a×V01+V02) n2 =P1×(b×V01+V02) n2 (2)

[0091] (b×V01+V02)-(a×V01+V02)=V1-V2=DV (3)

[0092] DV=∫Qdt (4)

[0093] In the formula, V01, V02, P0, P m are the accumulator volume, nitrogen bottle volume, initial gas filling pressure, and maximum oil filling pressure, respectively. Q is the oil discharge flow rate, DV is the oil discharge volume, P1 is the current oil pressure value inside the large flow accumulator group, and b is the relative height of the liquid level. A is the oil filling to P m The internal liquid level height of the accumulator is 1. The process of filling the piston accumulator is relatively slow, which is approximately an isothermal process. Therefore, the filling polytropic index n1 is approximately 1 at this time, and the oil discharge time is only about 14s. The oil discharge speed is very fast, which is approximately an adiabatic process. At this time, the oil discharge polytropic index n2 is approximately 1.4.

[0094] According to the mathematical model of large flow accumulator group, the pressure control model of large flow cartridge valve is constructed:

[0095] Move the high flow cartridge valve core to x v The transfer function between the control voltage u is expressed by a second-order link:

[0096]

[0097] In the formula, ω v , v , k a , k v They are natural frequency, damping ratio, amplifier gain and proportional coefficient between valve core displacement and current signal. At the same time, the flow rate Q of the cartridge valve can be expressed as follows:

[0098]

[0099] In the formula, k q is the flow gain of the cartridge valve, and P2 is the output pressure of the cartridge valve.

[0100] The flow equation for the pressure reducing valve accumulator and pipeline accumulator is:

[0101]

[0102] Where V 0l , P 0l is the initial inflation volume and pressure, Q2 is the output flow rate,

[0103] The servo valve flow equation can be simplified as shown below:

[0104]

[0105] In the formula, k ql is the flow gain of the actuator servo valve, P2 is the output control pressure of the cartridge valve, P l is the load voltage drop.

[0106] According to equations (1) to (8), considering the compression flow of the pipeline, we have:

[0107]

[0108] Where V t , B e Represent the pipeline volume and bulk elastic modulus, Q p Provide flow to the oil source pump station.

[0109] In order to compensate for the lag of the cartridge valve phase when the pressure fluctuates, a lead controller is constructed. The characteristics of the lead controller are designed as follows

[0110]

[0111] In the formula, T is the time turning coefficient, a is the gain coefficient, and the specific value is determined by the specific parameters in formula (9).

[0112] Since the accumulator is controlled by multiple cartridge valves, in order to better control pressure fluctuations and extend the service life of the accumulator, switching control is used to reasonably control the usage frequency and opening size of each accumulator according to the usage frequency of each accumulator.

[0113] According to the control quantity of the advanced controller to adjust the output, the opening size and frequency of each actuator are reasonably allocated. The frequency of use and the opening size are the adjustment quantities in the performance indicators.

[0114] J = ∫α i β i ·Δ 1,…,n (11)

[0115] In the formula, α i To make energy, β iis the weighted amount for each cartridge valve opening, Δ is the adjustment amount output by the advance controller, and n is the number of cartridge valves.

[0116] The specific control strategy is shown in the figure Figure 4 As shown, the hydraulic pump (P) provides pressurized oil, converts mechanical energy into hydraulic energy, and pressurizes the oil into the system; the advance controller adjusts the flow of oil according to system needs, and accurately controls the flow direction and flow of hydraulic oil by controlling the opening of the cartridge valve to meet the flow requirements under different working conditions; the switching controller switches the flow direction according to the system status or instructions; the high-frequency filter filters out noise and improves control accuracy; the flow meter monitors and measures the actual flow of oil flow, obtains real-time data, and feeds it back to the control system; the accumulator provides additional hydraulic oil or pressure when needed; the pressure sensor monitors the system pressure to ensure stable operation of the system; the oil pipeline is responsible for delivering the regulated hydraulic oil to the loading test bench to ensure that the test bench obtains the necessary hydraulic resources for testing or operation. Finally, the loading test bench receives and uses hydraulic oil to perform predetermined tasks, such as testing, loading or other operations, to complete the final function of the entire system.

[0117] In this embodiment, experimental tests were also carried out. Specifically, the loading frequency was 2 Hz, the flow rate was 0-45000 L / min and the pressure fluctuation during the whole loading process was 2.5%, which met the control index of less than 5%, such as Figure 5 As shown, accurate control of force and displacement of super-large components and ultra-high speeds is achieved.

[0118] Those skilled in the art will appreciate that the embodiments of the present disclosure may be provided as methods, systems or computer program products. Therefore, the present disclosure may take the form of a complete hardware embodiment, a complete software embodiment or an embodiment combining software and hardware. Moreover, the present disclosure may take the form of a computer program product implemented on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0119] The present disclosure is described with reference to flowcharts and / or block diagrams of methods, devices (systems) and computer program products according to embodiments of the present disclosure. It should be understood that each process and / or block in the flowchart and / or block diagram and the combination of processes and / or blocks in the flowchart and / or block diagram can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor or other programmable data processing device to produce a machine, so that the instructions executed by the processor of the computer or other programmable data processing device generate instructions for implementing the processes in the flowchart and / or block diagram. Figure 1 A process or multiple processes and / or boxes Figure 1These computer program instructions can also be stored in a computer-readable memory that can guide a computer or other programmable data processing device to work in a specific way, so that the instructions stored in the computer-readable memory produce a product including an instruction device, which implements the functions specified in the process. Figure 1 A process or multiple processes and / or boxes Figure 1 A function specified in one or more boxes.

[0120] These computer program instructions can also be loaded onto a computer or other programmable data processing device so that a series of operating steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing instructions for implementing the process. Figure 1 A process or multiple processes and / or boxes Figure 1 The steps for the functions specified in one or more boxes.

[0121] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present disclosure rather than to limit its protection scope. Although the present disclosure has been described in detail with reference to the above embodiments, ordinary technicians in the relevant field should understand that after reading the present disclosure, those skilled in the art can still make various changes, modifications or equivalent substitutions to the specific implementation methods of the invention, but these changes, modifications or equivalent substitutions are all within the protection scope of the disclosed claims to be approved.

Claims

1. A method for dynamic pressure control and instantaneous flow compensation of large flow oil supply, characterized in that: The method comprises: Construct mathematical model of large flow accumulator group; Construct a pressure control model of a large flow cartridge valve based on the mathematical model of a large flow accumulator group; Build a look-ahead controller; The cartridge valve is adjusted according to the advance controller, and the control amount output by the accumulator is controlled through the cartridge valve to achieve flow compensation.

2. A large flow oil supply dynamic pressure control and instantaneous flow compensation method according to claim 1, characterized in that: The method of constructing a mathematical model of a large flow accumulator group includes: P m ×(a×V01+V02) n1 =P0×(V01+V02) n1 P m ×(a×V01+V02) n2 =P1×(b×V01+V02) n2 (b×V01+V02)-(a×V01+V02)=V1-V2=DV DV=∫Qdt Among them, V01 is the volume of the accumulator, V02 is the volume of the nitrogen bottle, P0 is the initial charging pressure, P m is the maximum filling pressure, Q is the discharge flow, DV is the discharge volume, P1 is the current internal oil pressure value of the large flow accumulator group, b is the relative height of the liquid level, a is the filling pressure to P m The internal liquid level of the accumulator.

3. The method for dynamic pressure control and instantaneous flow compensation of large flow oil supply according to claim 1 is characterized in that: The large flow cartridge valve pressure control model is: Among them, Q is the flow rate of the cartridge valve, Q2 is the output flow rate, Q p Provide flow for oil source pump station, Q L is the servo valve flow rate, V t is the pipeline volume, B e is the bulk elastic modulus, P2 is the cartridge valve output pressure, and t is the time.

4. A large flow oil supply dynamic pressure control and instantaneous flow compensation method according to claim 3, characterized in that: The cartridge valve output pressure is: Among them, V 0l is the initial inflation volume, P 0l is the initial inflation pressure.

5. The method for dynamic pressure control and instantaneous flow compensation of large flow oil supply according to claim 3 is characterized in that: The servo valve flow rate is: Among them, k ql is the flow gain of the actuator servo valve, P l is the load voltage drop.

6. The method for dynamic pressure control and instantaneous flow compensation of large flow oil supply according to claim 1 is characterized in that: The advance controller is: Among them, T is the time turning coefficient and a is the gain coefficient.

7. A large flow oil supply dynamic pressure control and instantaneous flow compensation method according to claim 1, characterized in that: Regulate cartridge valves based on look-ahead controllers, including: J=∫α i ·β i ·Δi=1,…,n Among them, α i is energy, β i is the weighted amount for each cartridge valve opening, Δ is the adjustment amount output by the advance controller, and n is the number of cartridge valves.

8. A large flow oil supply dynamic pressure control and instantaneous flow compensation system, characterized in that: The system comprises: An accumulator group model building unit is used to build a mathematical model of a large flow accumulator group; A cartridge valve pressure control model building unit, used for building a large flow cartridge valve pressure control model according to a large flow accumulator group mathematical model; A look-ahead controller building unit, used for building a look-ahead controller; The flow compensation unit is used to adjust the cartridge valve according to the advance controller, and control the control amount output by the accumulator through the cartridge valve to achieve flow compensation.

9. A computer device, characterized in that: It comprises a memory and a processor, wherein the memory stores a computer program, and when the processor runs the computer program stored in the memory, the processor executes a large flow oil supply dynamic pressure control and instantaneous flow compensation method according to any one of claims 1-7.

10. A computer-readable storage medium, characterized in that: The computer-readable storage medium stores a computer program, which, when executed by a processor, executes the steps of a large-flow oil supply dynamic pressure control and instantaneous flow compensation method as described in any one of claims 1-7.

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