A method and system for dynamic pressure control and instantaneous flow compensation of large flow oil supply

Abstract

A method and system for dynamic pressure control and instantaneous flow compensation for high-flow oil supply relates to the field of automatic control technology. This method solves the problem of effectively achieving flow regulation and pressure stability control in high-flow servo systems. The method includes: constructing a mathematical model of a high-flow accumulator group; constructing a high-flow cartridge valve pressure control model based on the mathematical model; constructing a lead controller; and adjusting the cartridge valve according to the lead controller to control the accumulator output through the cartridge valve to achieve flow compensation. The present invention has application in the field of ultra-large test piece simulation.

Description

Technical Field

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

[0002] When testing very large specimens, such as bridge load bearings, heavy-duty loading test rigs are often used to study the response and failure modes under static and dynamic loads. One of the key objectives of these tests is to evaluate the load-bearing capacity, deformation behavior, and failure mechanisms of large components under extreme conditions. To simulate real-world operating conditions, the test rig needs to be able to provide loads of varying types and sizes, especially at high speeds, which place a significant demand on the system's hydraulic oil. According to relevant research and practical experience, the oil flow requirement for a hydraulic system at high speeds can reach 45,000 L / min, placing extremely high demands on the design and control of the hydraulic system.

[0003] However, current technology is not yet capable of effectively achieving flow regulation and pressure stability control in servo systems operating at such high flow rates. In oil supply systems operating at lower flow rates, multiple accumulators are often used in conjunction with the oil supply system to regulate flow and ensure the system can cope with transient load changes during testing. This approach can address fluctuations in oil demand to a certain extent, but the problem becomes more complex under high flow conditions. Especially at high flow rates, load changes can lead to significant flow fluctuations, which in turn can significantly affect the oil supply pressure. Research has shown that in such conditions, pressure fluctuations in the oil supply system can reach as high as 10%, posing a significant challenge to the stability and accuracy of the hydraulic system. Summary of the Invention

[0004] The present invention aims to effectively realize 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 a mathematical model of a large flow accumulator group;

[0006] Construct a high-flow cartridge valve pressure control model based on the high-flow accumulator group mathematical model;

[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 by 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 oil filling pressure, Q is the oil discharge flow, DV is the oil discharge volume, P1 is the current oil pressure value inside the large flow accumulator group, b is the relative height of the liquid level, a is the oil filling to P m The internal liquid level of the accumulator.

[0015] Furthermore, a preferred embodiment is proposed, wherein 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 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 servo valve flow rate 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 advance controller is:

[0025]

[0026] Where T is the time transition coefficient and a is the gain coefficient.

[0027] Furthermore, a preferred method is proposed for adjusting the cartridge valve 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 the opening of each cartridge valve, 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 to build a large flow cartridge valve pressure control model based on 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 a computer program is stored in the memory. 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, which stores a computer program. When the computer program is run by a processor, it executes the steps of a large-flow oil supply dynamic pressure control and instantaneous flow compensation method as described in any one of the above.

[0037] The present invention is beneficial in that:

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

[0039] This invention proposes a method for dynamic pressure control and instantaneous flow compensation for high-flow oil supply. By constructing a mathematical model of a high-flow accumulator group, the accumulator's behavior is accurately modeled. This mathematical model allows for more accurate prediction and control of the accumulator's performance under varying load and flow conditions, providing a theoretical basis for subsequent pressure control and flow compensation. This model-based design improves the system's accuracy and reliability. The cartridge valve, a high-precision flow and pressure control element, works in conjunction with the accumulator group to effectively regulate system pressure, ensuring that the oil supply system's pressure remains within a stable range even when the flow rate fluctuates dramatically. The cartridge valve's high responsiveness enables it to quickly adjust to flow changes, thereby achieving dynamic pressure control. By constructing a look-ahead controller, the invention anticipates and proactively adjusts flow and pressure fluctuations. While traditional feedback control only adjusts after fluctuations occur, look-ahead control can proactively respond based on load trends, reducing pressure fluctuations and flow regulation lag. This proactive compensation mechanism significantly improves system stability under high-load and high-flow conditions.

[0040] Furthermore, the method proposed in this invention achieves dynamic flow compensation by adjusting the accumulator output through the cartridge valve. When flow demand fluctuates dramatically, the hydraulic system can quickly respond and compensate through the accumulator output, ensuring stable operation. This technology significantly reduces pressure fluctuations within the system, avoiding the supply shortages or pressure overloads caused by rapid flow changes in traditional methods.

[0041] Furthermore, by precisely controlling the pressure and flow fluctuations of the high-flow oil supply system, the proposed method ensures that the response and failure mode studies under load can be conducted under more stable conditions during the test, thereby improving the accuracy and reliability of the test data. This is particularly important for testing ultra-large bridge components and other similar ultra-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 Schematic diagram of a method for dynamic pressure control and instantaneous flow compensation of large flow oil supply according to embodiment 1;

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

[0045] Figure 3This is the oil source layout diagram described in Implementation Method 11;

[0046] Figure 4 Schematic diagram of the dynamic pressure control and terminal instantaneous flow compensation control strategy according to the eleventh embodiment;

[0047] Figure 5 This is a diagram showing the pressure fluctuation results in the pipeline during high-flow oil supply 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 combination 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 This embodiment describes a method for dynamic pressure control and instantaneous flow compensation of a large flow oil supply, the method comprising:

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

[0051] Construct a high-flow cartridge valve pressure control model based on the high-flow accumulator group mathematical model;

[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 by the cartridge valve to achieve flow compensation.

[0054] This embodiment proposes a method for dynamic pressure control and instantaneous flow compensation for high-flow oil supply. By constructing a mathematical model of a high-flow accumulator group, the accumulator's behavior is accurately modeled. This mathematical model allows for more accurate prediction and control of the accumulator's performance under varying load and flow conditions, providing a theoretical basis for subsequent pressure control and flow compensation. As a high-precision flow and pressure control element, the cartridge valve, in conjunction with the accumulator group, effectively regulates system pressure, ensuring that the oil supply system pressure remains within a stable range even when the flow rate fluctuates dramatically. The cartridge valve's high responsiveness enables it to quickly adjust to flow changes, thereby achieving dynamic pressure control. By constructing a look-ahead controller, flow and pressure fluctuations can be anticipated and adjusted in advance. While traditional feedback control only adjusts after fluctuations occur, look-ahead control can proactively respond based on load trends, reducing pressure fluctuations and flow regulation lag. This look-ahead compensation mechanism significantly improves system stability under high-load and high-flow conditions.

[0055] Furthermore, the method proposed in this embodiment achieves dynamic flow compensation by adjusting the cartridge valve to control the accumulator's output. When flow demand fluctuates dramatically, the hydraulic system can quickly respond and compensate through the accumulator's output, ensuring stable operation. This technology significantly reduces pressure fluctuations within the system, avoiding the supply shortages or pressure overloads caused by rapid flow changes in traditional methods.

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

[0057] Embodiment 2: This embodiment further defines the method for dynamic pressure control and instantaneous flow compensation for large-flow oil supply described in embodiment 1. The method for constructing a mathematical model of a large-flow accumulator group 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 oil filling pressure, Q is the oil discharge flow, DV is the oil discharge volume, P1 is the current oil pressure value inside the large flow accumulator group, b is the relative height of the liquid level, a is the oil filling to P m The internal liquid level of the accumulator.

[0063] Implementation 3: This implementation further limits the large flow oil supply dynamic pressure control and instantaneous flow compensation method described in Implementation 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 time.

[0066] Embodiment 4: This embodiment further limits the method for dynamic pressure control and instantaneous flow compensation of large flow oil supply 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] Implementation 5: This implementation further limits the method for dynamic pressure control and instantaneous flow compensation of large flow oil supply described in Implementation 3. The servo valve flow is:

[0070]

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

[0072] Implementation 6: This implementation further limits the method for dynamic pressure control and instantaneous flow compensation of large flow oil supply described in Implementation 1. The advance controller is:

[0073]

[0074] Where T is the time transition coefficient and a is the gain coefficient.

[0075] Embodiment 7: This embodiment further defines the method for dynamic pressure control and instantaneous flow compensation for large flow oil supply described in embodiment 1. The method 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 the opening of each cartridge valve, 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 according to this embodiment includes:

[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 to build a large flow cartridge valve pressure control model based on 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 a computer program is stored in the memory. 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 the large flow rate oil supply dynamic pressure control and instantaneous flow rate compensation method described in embodiment 1, and is also used to explain embodiments 2 to 7. Specifically:

[0086] like Figure 2 The layout of the high-flow accumulator group in the heavy-duty loading test bench is shown. There are three types of accumulators: the high-flow accumulator, which provides the main flow supply and is controlled by several cartridge valves. The flow rate can be adjusted by controlling the valve core stroke adjuster on the cover plate. Another type of accumulator is the high-pressure accumulator, and the other type is the pipeline accumulator. These two types of accumulators supplement the flow at different locations in the pipeline.

[0087] Figure 3 The layout of the system's oil supply components is shown. During test bench testing, average oil supply is primarily provided by the oil source. During peak flow rates, the accumulator bank supplements the supply and absorbs some of the pressure pulsation caused by load pressure drop. The accumulator bank is numerous, so multiple cartridge valves are used for control. Specifically, the control mechanism is implemented by multiple cartridge valves, while the output is provided by a single pressure sensor.

[0088] In this implementation, the mathematical model of the 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] Where V01, V02, P0, P m They are the accumulator volume, nitrogen bottle volume, initial charging pressure, and maximum oil filling pressure, Q is the oil discharge flow, 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 When the liquid level inside the accumulator is high, the piston accumulator is filled with oil slowly, which is approximately an isothermal process. Therefore, the oil 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] The pressure control model of the large-flow cartridge valve is constructed based on the mathematical model of the large-flow accumulator group:

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

[0096]

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

[0098]

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

[0100] The flow equations for the pressure reducing valve accumulator and pipeline accumulator are:

[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] Where 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 for oil source pumping station.

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

[0110]

[0111] Where 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 output of the advance controller, the opening size and frequency of each actuator are reasonably allocated. The performance index uses the frequency and opening size as the adjustment quantity.

[0114] J = ∫α i β i ·Δ 1,…,n (11)

[0115] Where, α i To make the energy, β iis the weighted amount for the opening of each cartridge valve, 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, converting mechanical energy into hydraulic energy and forcing the oil into the system. The look-ahead controller adjusts the oil flow rate according to system requirements, precisely controlling the flow direction and volume of the hydraulic oil by controlling the opening of the cartridge valve to meet flow requirements under different operating conditions. The switching controller switches the flow direction according to system status or instructions. The high-frequency filter filters out noise and improves control accuracy. The flow meter monitors and measures the actual oil flow rate, 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 system pressure to ensure stable system operation. The oil pipeline is responsible for delivering the regulated hydraulic oil to the loading test bench, ensuring that the test bench has the necessary hydraulic resources for testing or operation. Finally, the loading test bench receives and uses the hydraulic oil to perform the predetermined tasks, such as testing, loading, or other operations, completing the final function of the entire system.

[0117] In this embodiment, a test was also conducted. Specifically, the loading frequency was 2 Hz, the flow rate was changed rapidly from 0 to 45,000 L / min, and the pressure fluctuation during the entire loading process was 2.5%, meeting the control index of less than 5%. Figure 5 As shown, accurate control of force and displacement of ultra-large components and ultra-high speeds is achieved.

[0118] Those skilled in the art will appreciate that embodiments of the present disclosure may be provided as methods, systems, or computer program products. Thus, the present disclosure may take the form of an entirely hardware embodiment, an entirely software embodiment, or an embodiment combining software and hardware. Furthermore, 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 magnetic 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 the instruction device, which implements the function specified in the process. Figure 1 a process or multiple processes and / or boxes Figure 1 The 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 operational steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing the instructions executed on the computer or other programmable device for implementing the process. Figure 1 a process or multiple processes and / or boxes Figure 1 A step that specifies a function 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 and are not intended to limit its scope of protection. 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 scope of protection of the disclosed claims.

Claims

1. A method for dynamic pressure control and instantaneous flow compensation of large flow oil supply, characterized in that: The method comprises: Construct a mathematical model of a large flow accumulator group; Construct a high-flow cartridge valve pressure control model based on the high-flow accumulator group mathematical model; 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; The construction of a mathematical model of a large flow accumulator group includes: in, V 01 is the accumulator volume, V 02 is the volume of the nitrogen cylinder, P 0 is the initial inflation pressure, P m is the maximum oil filling pressure, Q is the oil discharge flow, DV is the oil discharge volume, P 1 is the current oil pressure value inside the large flow accumulator group, b is the relative height of the liquid level, and a is the oil filling to P m The internal liquid level height of the accumulator at 1000 Hz, n1 is the variable index of oil filling, and n2 is the variable index of oil discharge; The high flow cartridge valve pressure control model is: in, Q is the cartridge valve flow rate, Q 2 is the output flow, Q p Provide flow for oil source pumping station, is the servo valve flow rate, V t is the pipeline volume, is the bulk elastic modulus, P2 is the cartridge valve output pressure, and t is the time; The cartridge valve output pressure is: in, V 0l is the initial inflation volume, P 0l is the initial inflation pressure; The servo valve flow rate is: in, k ql is the flow gain of the actuator servo valve, P l is the load voltage drop; The advance controller is: Where T is the time transition coefficient, a is the gain coefficient; Cartridge valve regulation based on lead controller, including: in, For energy, Weight each cartridge valve opening, is the regulation quantity output by the advance controller, n is the number of cartridge valves.

2. A large flow oil supply dynamic pressure control and instantaneous flow compensation system, characterized in that: The system is implemented based on the large flow oil supply dynamic pressure control and instantaneous flow compensation method described in claim 1, and the system includes: 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 to build a large flow cartridge valve pressure control model based on 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.

3. A computer device, characterized in that: The invention comprises a memory and a processor, wherein a computer program is stored in the memory. 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 claim 1.

4. 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 claimed in claim 1.

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