Matching verification method, device and equipment of fuel system and storage medium

Abstract

The invention relates to a matching verification method and device of a fuel system, computer equipment, a computer readable storage medium and a computer program product. The method comprises the steps that the fuel supply pressure and the fuel supply flow which can be provided by a fuel system and the minimum working pressure of an actuating device included in the fuel system are obtained, and the consumption flow of the fuel system in the working process is obtained; comparing the oil supply pressure with the minimum working pressure to obtain a first comparison result, and comparing the oil supply flow with the consumption flow to obtain a second comparison result; and verifying the matching of the fuel system according to the first comparison result and the second comparison result to obtain a verification result. By adopting the method, the engine operation stability can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of engine fuel systems, and in particular to a fuel system matching verification method, device, computer equipment, computer-readable storage medium and computer program product. Background Art

[0002] As the demand for adaptive variable cycle engines in the modern aviation industry continues to increase, the number of geometrically adjustable devices deployed on the engine has also increased. As the number of geometrically adjustable devices increases, the fuel flow consumed by the actuator also increases significantly, resulting in a more significant mutual influence between the actuator and the fuel metering unit. Therefore, if the matching between the actuator and the fuel metering unit is not fully considered during the design of the engine's fuel system, it may lead to problems such as reduced fuel metering accuracy and slow actuation response, thereby reducing the quality of engine control and even posing a serious threat to flight safety.

[0003] However, when using traditional technology, if a large number of geometrically adjustable devices are deployed, it is easy to cause unstable engine operation. Summary of the invention

[0004] Based on this, it is necessary to provide a fuel system matching verification method, device, computer equipment, computer-readable storage medium and computer program product that can improve the stability of engine operation in order to address the above technical problems.

[0005] In a first aspect, the present application provides a fuel system matching verification method. The method comprises:

[0006] Obtaining the fuel supply pressure and fuel supply flow rate that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and obtaining the consumption flow rate of the fuel system during operation;

[0007] Comparing the oil supply pressure with the minimum working pressure to obtain a first comparison result, and comparing the oil supply flow rate with the consumption flow rate to obtain a second comparison result;

[0008] The matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result.

[0009] In one embodiment, the number of the actuating devices is multiple, and the matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result, including:

[0010] When the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate, the verification result is determined to be verification passed.

[0011] In one embodiment, the process of obtaining the minimum working pressure includes:

[0012] Substituting the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula, the rod chamber pressure is obtained;

[0013] Substituting the rod chamber pressure, the rod chamber area, the rodless chamber area of ​​the actuator cylinder and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure;

[0014] The rodless chamber pressure, the flow coefficient of the electro-hydraulic servo valve, the throttling area, the maximum actuation distance and the longest actuation time are substituted into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0015] In one embodiment, obtaining the consumption flow of the fuel system during operation includes:

[0016] Obtaining a metered flow, a steady-state consumption flow, and a dynamic consumption flow of the fuel system;

[0017] The consumption flow rate is determined as the sum of the metering flow rate, the steady-state consumption flow rate and the dynamic consumption flow rate.

[0018] In one embodiment, the process of obtaining the metered flow rate includes:

[0019] The metering flow is determined according to an engine performance model corresponding to the fuel system.

[0020] In one embodiment, the process of obtaining the steady-state consumption flow includes:

[0021] The sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system is determined as the steady-state consumption flow.

[0022] In one embodiment, the process of obtaining the dynamic consumption flow includes:

[0023] Calculating the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device;

[0024] The dynamic consumption flow is determined by multiplying the ratio by the rodless chamber area of ​​the actuator.

[0025] In one embodiment, obtaining the fuel supply pressure that can be provided by the fuel system includes:

[0026] Substituting the metering flow rate, working fluid density, actuator valve pressure difference of the fuel system, reverse pressure of the combustion chamber included in the engine, nozzle equivalent area, and nozzle flow coefficient into the formula of nozzle flow rate and nozzle front and rear pressure difference to obtain the metering pressure of the fuel system;

[0027] Determining the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve;

[0028] The sum of the maximum value and the differential pressure of the metering valve of the fuel system is determined as the fuel supply pressure.

[0029] In one embodiment, the process of obtaining the fuel supply flow rate that can be provided by the fuel system includes:

[0030] The fuel flow of the fuel system in the ignition state, the high-pressure rotor physical speed corresponding to the fuel flow of the fuel system in the ignition state, and the high-pressure rotor physical speed component of the fuel system under the target operating conditions are substituted into the fuel supply flow formula to obtain the fuel supply flow.

[0031] In a second aspect, the present application also provides a fuel system matching verification device. The device comprises:

[0032] A first acquisition module is used to acquire the fuel supply pressure and fuel supply flow rate that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and to acquire the consumption flow rate of the fuel system during operation;

[0033] A comparison module, configured to compare the oil supply pressure with the minimum working pressure to obtain a first comparison result, and to compare the oil supply flow rate with the consumption flow rate to obtain a second comparison result;

[0034] The second acquisition module is used to verify the matching of the fuel system according to the first comparison result and the second comparison result to obtain a verification result.

[0035] In a third aspect, the present application further provides a computer device, wherein the computer device comprises a memory and a processor, wherein the memory stores a computer program, and when the processor executes the computer program, the steps of the method described in the first aspect are implemented.

[0036] In a fourth aspect, the present application further provides a computer-readable storage medium, wherein a computer program is stored on the computer-readable storage medium, and when the computer program is executed by a processor, the steps of the method described in the first aspect are implemented.

[0037] In a fifth aspect, the present application further provides a computer program product, wherein the computer program product comprises a computer program, and when the computer program is executed by a processor, the steps of the method described in the first aspect are implemented.

[0038] In the above-mentioned fuel system matching verification method, device, computer equipment, computer-readable storage medium and computer program product, the computer equipment first obtains the fuel supply pressure and fuel supply flow that can be provided by the fuel system and the minimum working pressure of the actuator included in the fuel system, and obtains the consumption flow of the fuel system during operation, then compares the fuel supply pressure with the minimum working pressure to obtain a first comparison result, and compares the fuel supply flow with the consumption flow to obtain a second comparison result, and then verifies the matching of the fuel system according to the first comparison result and the second comparison result to obtain a verification result. In the above-mentioned matching verification method, by comparing the fuel supply pressure of the fuel system with the minimum working pressure of the actuator, and comparing the fuel supply flow with the consumption flow of the fuel system, the pressure and fuel flow of the actuator of the fuel system during operation can be quantitatively analyzed according to the comparison results, so that the matching between the actuator and the metering unit can be accurately verified according to the results of the quantitative analysis, avoiding the problems of slow adjustment of the actuator in the fuel system and insufficient fuel supply due to the mismatch between the actuator and the metering unit of the fuel system, thereby improving the stability of engine operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] In order to more clearly illustrate the technical solutions in the embodiments of the present application or related technologies, the drawings required for use in the embodiments of the present application or related technical descriptions will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0040] Figure 1 A schematic diagram of a flow chart of a method for verifying the compatibility of a fuel system in one embodiment;

[0041] Figure 2 A schematic diagram of a process for obtaining a minimum working pressure in an embodiment;

[0042] Figure 3 A schematic diagram of a flow chart for obtaining consumed flow in one embodiment;

[0043] Figure 4 A schematic diagram of a process for obtaining dynamic consumption flow in one embodiment;

[0044] Figure 5A schematic diagram of a flow chart for obtaining oil supply pressure in one embodiment;

[0045] Figure 6 is a structural block diagram of a fuel system matching verification device in one embodiment;

[0046] Figure 7 FIG. 4 is a diagram showing the internal structure of a computer device in one embodiment. DETAILED DESCRIPTION

[0047] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0048] In one embodiment, Figure 1 As shown, a fuel system matching verification method is provided. This embodiment uses the method applied to a computer device as an example. In this embodiment, the method includes the following steps:

[0049] Step 101, obtaining the fuel supply pressure and fuel supply flow rate that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and obtaining the consumption flow rate of the fuel system during operation.

[0050] Among them, the fuel system is the fuel that provides clean, pressurized fuel to the aircraft engine. The fuel flow rate can be adjusted according to the different needs of the flight phase to ensure the performance and stability of the engine under different working conditions. The fuel provided by the fuel system can be combined with the air entering the combustion chamber, releasing energy during the combustion process, thereby generating propulsion. Among them, the fuel supply pressure refers to the pressure of the fuel that can be provided at the outlet of the main gear pump of the fuel system during the operation of the actuating device of the fuel system, and the fuel supply flow rate refers to the amount of fuel that can be provided by the main gear pump during the operation of the fuel system.

[0051] The actuator refers to the component in the fuel system that controls the injection and supply of fuel to ensure the normal operation of the engine. For example, the actuator may include a fuel pump, an injector, and other components. Common actuators may include guide vane actuators, bleed valves, ejector actuators, and the like. The minimum operating pressure of the actuator refers to the minimum pressure required for the actuator to work properly.

[0052] The consumption flow refers to the flow of fuel consumed by the fuel system during its operation. The consumption flow may include the fuel flow consumed by the actuator during the actuation process, the fuel flow required for cooling and / or leakage in the fuel system, and the fuel flow required for the fuel metering unit in the fuel system to supply fuel.

[0053] It should be noted that in a non-variable cycle engine, the fuel metering unit included in the engine's fuel system usually only shares the oil source behind the gear pump with the guide vane actuator, and the amount of fuel consumed by the guide vane actuator is relatively small. Therefore, the coupling effect between the metering function corresponding to the fuel metering unit and the actuating function corresponding to the actuating device is not prominent; however, in a variable cycle engine, the number of geometrically adjustable devices increases, resulting in a significant increase in the fuel flow consumed by the actuating device, which leads to a prominent coupling effect between the metering function and the actuating function, and the mutual influence between the two is more significant. Therefore, when designing the fuel metering unit and the actuating device of the fuel system, it is necessary to consider the matching between the metering function corresponding to the fuel metering unit and the actuating function corresponding to the actuating device, so as to avoid the problem of reduced fuel metering accuracy and slow response of the actuating device, which leads to reduced engine performance.

[0054] In the process of considering the matching between the metering function and the actuation function, mathematical means can be used to quantify the constraints of the two parameters of pressure and flow into specific matching judgment basis, so as to verify the matching of the fuel system according to the comparison results of pressure and flow, and improve the reliability of the matching judgment process.

[0055] The following is a detailed description of the process of determining the basis for matching verification:

[0056] When the metering function and the actuation function share the same oil source, the following constraints on the oil supply pressure and consumption flow should be met:

[0057] ① The fuel supply pressure of the fuel system shall not be lower than the pressure threshold required for the normal operation of each actuator included in the fuel system;

[0058] ② During the normal operation of the actuating device of the fuel system, the additional consumption flow shall not lead to insufficient fuel supply, that is, the fuel supply flow of the fuel system shall be greater than the dynamic consumption flow, steady-state consumption flow and metering flow consumed during the normal operation of the actuating device.

[0059] Assume that the fuel system includes If the engine operating condition is , the complete working range of the engine is The engine working area during the operation is ,but Under this definition, the pressure constraint of the fuel system can be expressed as:

[0060]

[0061] in, is the engine operating condition, is the minimum working pressure of the actuator, is the pressure at the outlet of the main pump of the fuel system, that is, the fuel supply pressure that the fuel system can provide. Based on this pressure constraint, the pressure judgment basis of the actuator can be described as: , the pressure constraints all hold.

[0062] The flow constraint of the fuel system can be expressed as:

[0063]

[0064] in, To measure flow, is the total steady-state consumption flow, To dynamically consume the total traffic, is the oil supply flow of the gear pump, that is, the oil supply flow that the fuel system can provide. Based on this flow constraint, the flow judgment basis of the actuator can be described as: , the flow constraints all hold.

[0065] In this embodiment, the computer equipment can obtain the fuel supply pressure, fuel supply flow and minimum working pressure of the actuator according to the design requirements of the fuel system, and perform simulation tests on the fuel system, and obtain the consumption flow of the system during operation during the simulation test.

[0066] Obtain the fuel supply pressure and fuel supply flow of the fuel system under the target working condition within the target time period, and obtain the required working conditions of the actuator under the target working condition within the target time period.

[0067] Step 102, comparing the oil supply pressure with the minimum working pressure to obtain a first comparison result, and comparing the oil supply flow rate with the consumption flow rate to obtain a second comparison result.

[0068] The first comparison result refers to the comparison result between the oil supply pressure and the minimum working pressure, and the second comparison result refers to the comparison result between the oil supply flow rate and the consumption flow rate.

[0069] In this embodiment, the computer device can calculate the pressure difference between the oil supply pressure and the minimum working pressure, determine the first comparison result based on the pressure difference, and calculate the flow difference between the oil supply flow and the consumption flow, and determine the second comparison result based on the flow difference.

[0070] For example, if the pressure difference is a positive value, the first comparison result can be determined as the oil supply pressure is greater than the minimum working pressure, and if the pressure difference is a negative value, the first comparison result can be determined as the oil supply pressure is less than the minimum working pressure. If the flow difference is a positive value, the first comparison result can be determined as the oil supply flow is greater than the consumption flow, and if the flow difference is a negative value, the first comparison result can be determined as the oil supply flow is less than the consumption flow.

[0071] Step 103: Verify the matching of the fuel system according to the first comparison result and the second comparison result to obtain a verification result.

[0072] The verification result refers to the verification result of whether the actuator and the metering unit in the fuel system match each other. Optionally, the verification result may be that the fuel system has passed the matching verification, or the verification result may be that the fuel system has failed the matching verification. If the matching verification passes, there is no need to correct the actuator and the metering unit. If the matching verification fails, the actuator and the metering unit need to be corrected. It can be understood that if both the first comparison result and the second comparison result meet the above-mentioned pressure and flow constraints, it can be determined that the matching verification has passed.

[0073] In this embodiment, the computer device can determine the verification result of the matching of the fuel system based on the first comparison result and the second comparison result. For example, if the first comparison result indicates that the fuel supply pressure is greater than the minimum working pressure, and the second result indicates that the fuel supply flow rate is greater than the consumption flow rate, it can be determined that the pressure and flow rate meet the constraint conditions for matching, that is, the matching verification is passed. If the first comparison result indicates that the fuel supply pressure is less than the minimum working pressure, and the second result indicates that the fuel supply flow rate is greater than the consumption flow rate, or if the first comparison result indicates that the fuel supply pressure is greater than the minimum working pressure, and the second result indicates that the fuel supply flow rate is less than the consumption flow rate, or if the first comparison result indicates that the fuel supply pressure is less than the minimum working pressure, and the second result indicates that the fuel supply flow rate is less than the consumption flow rate, it can be determined that the pressure and / or flow rate do not meet the constraint conditions for matching, that is, the matching verification is not passed.

[0074] It can be understood that through the matching verification process of the above-mentioned quantitative analysis, accurate matching analysis can be performed, reducing multiple revisions caused by unreasonable fuel system design, thereby reducing the research and development cost and time cycle of the fuel system, and can also reduce the problem of unstable engine operation and performance degradation caused by mismatch between the fuel metering unit and the actuator design.

[0075] In the above-mentioned fuel system matching verification method, the computer device first obtains the fuel supply pressure and fuel supply flow that can be provided by the fuel system and the minimum working pressure of the actuator included in the fuel system, and obtains the consumption flow of the fuel system during operation. Then, the fuel supply pressure and the minimum working pressure are compared to obtain a first comparison result, and the fuel supply flow and the consumption flow are compared to obtain a second comparison result. Then, according to the first comparison result and the second comparison result, the matching of the fuel system is verified to obtain a verification result. In the above-mentioned matching verification method, by comparing the fuel supply pressure of the fuel system and the minimum working pressure of the actuator, and comparing the fuel supply flow of the fuel system and the consumption flow, the pressure and fuel flow of the actuator of the fuel system during operation can be quantitatively analyzed according to the comparison results, so that the matching between the actuator and the metering unit can be accurately verified according to the results of the quantitative analysis, avoiding the problems of slow adjustment of the actuator and insufficient fuel supply in the fuel system due to the mismatch between the actuator and the metering unit of the fuel system, thereby improving the stability of engine operation.

[0076] In an exemplary embodiment, if the fuel system includes a plurality of actuating devices, the above step 103 includes: when the first comparison result is that the fuel supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the fuel supply flow rate is greater than the consumption flow rate, determining that the verification result is verification passed.

[0077] It should be noted that each different actuator included in the fuel system has a different corresponding minimum working pressure. Therefore, in order to meet the matching requirements of the fuel system, the fuel supply pressure needs to be greater than the minimum working pressure corresponding to each actuator, that is, the fuel supply pressure needs to be greater than the maximum value of the minimum working pressures.

[0078] In this embodiment, the computer device can calculate the difference between the oil supply pressure and each minimum working pressure respectively. If each difference is a positive value, it can be determined that the oil supply pressure is greater than the maximum value of each minimum working pressure; or, the computer device can select the maximum value from each minimum working pressure, and then calculate the difference between the oil supply pressure and the maximum value. If the difference is a positive value, it can be determined that the oil supply pressure is greater than the maximum value of each minimum working pressure. Therefore, the computer device can determine that the verification result is verification passed when the first comparison result is that the oil supply pressure is greater than the maximum value of each minimum working pressure, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate.

[0079] In this embodiment, the computer device determines that the verification result is a passed verification when the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate. This can avoid the problem that the minimum working pressure of a certain actuator is greater than the oil supply pressure, causing the actuator to fail to work normally, thereby ensuring that each actuator can work normally, thereby improving the accuracy of the matching verification result.

[0080] It is understandable that the minimum working pressure required for the actuator to work properly is related to multiple factors. The specific process of obtaining the minimum working pressure is described in detail below. In an exemplary embodiment, Figure 2 As shown, the process of obtaining the minimum working pressure includes:

[0081] Step 201, substitute the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula to obtain the rod chamber pressure.

[0082] Among them, the electro-hydraulic servo valve is a flow control valve in the actuator. The electro-hydraulic servo valve can receive analog electrical signals and output modulated flow and pressure accordingly. The flow coefficient of the electro-hydraulic servo valve refers to the inverse of the ratio of the fuel flow rate of the electro-hydraulic servo valve to the pressure difference per unit time. The larger the flow coefficient, the greater the flow rate of the electro-hydraulic servo valve. The throttling area of ​​the electro-hydraulic servo valve refers to the throttling port flow area changed by the relative movement between the valve core and the valve body, which is used to control the fuel flow or pressure, thereby achieving precise hydraulic control. The pressure of the electro-hydraulic servo valve refers to the pressure at the T end of the electro-hydraulic servo valve.

[0083] The actuator device includes an actuator cylinder, which can be used to adjust the angle of the compressor guide vane so that the compressor maintains a high efficiency at different flow rates. In the hydraulic system, hydraulic oil is injected into the cylinder of the actuator cylinder, and the piston in the actuator cylinder is pushed to move under the action of the oil pressure. In the pneumatic system, the air pressure is delivered to the inside of the piston to push the piston in the actuator cylinder, thereby realizing the control of the actuator cylinder. The actuator cylinder includes a rod chamber and a rodless chamber, wherein the rod chamber is the space on one side of the piston rod. When the oil enters the rod chamber, the piston will be pushed forward to realize the extension of the cylinder; the rodless chamber is the space on the other side of the piston rod. When the oil is discharged from the rodless chamber, the piston is pulled backward to realize the retraction of the cylinder. Among them, the rod chamber area is the hydraulic pressure area of ​​the rod chamber of the actuator cylinder, and the rod chamber pressure is the pressure on the rod chamber of the actuator cylinder per unit area.

[0084] The maximum actuation distance refers to the distance that the actuator moves between the two end stop positions, and the maximum actuation time refers to the longest time that the actuator can be actuated. For example, if the maximum actuation time is 2 seconds, the actuation time requirement of the actuator should not exceed 2 seconds.

[0085] It should be noted that in the process of determining the minimum working pressure of the actuator, the following assumptions can be considered:

[0086] ① Assume that the actuator included in the actuating device is directly driven by the electro-hydraulic servo valve;

[0087] ②Assume that under the maximum current, the actuator moves approximately in a uniform linear motion between the two end stop positions;

[0088] ③ Assume that the leakage between the rod chamber and the rodless chamber of the actuator cylinder included in the actuator device can be ignored.

[0089] Based on the above assumptions and the working principle of a single actuator, it can be assumed that the force balance relationship of the actuator is: rod cavity pressure × rod cavity area = rodless cavity pressure × rodless cavity area + maximum load force of the actuator. Among them, the rod cavity area, rodless cavity area, and maximum load force of the actuator can be given according to the target working conditions and design requirements of the fuel system. Therefore, the minimum working pressure of the actuator can be determined by solving the rod cavity pressure and rodless cavity pressure.

[0090] Among them, the rod cavity pressure can be solved according to the rod cavity flow balance formula corresponding to the rod cavity flow balance relationship. The rod cavity flow balance formula can be expressed as:

[0091]

[0092] in, is the rod chamber pressure, is the flow coefficient of the electro-hydraulic servo valve, is the throttling area, is the electro-hydraulic servo valve pressure, is the rod cavity area, is the maximum actuation distance, is the longest actuation time. , , , are all known quantities that are input. , The known quantity given according to the design requirements of the fuel system can be obtained by solving the above formula: .

[0093] Step 202, substitute the rod chamber pressure, the rod chamber area, the rodless chamber area of ​​the actuator and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure.

[0094] Among them, the rodless cavity area is the hydraulic pressure area of ​​the rodless cavity of the actuator, and the rodless cavity pressure is the pressure on the rodless cavity per unit area of ​​the actuator. The maximum load force refers to the maximum load that the actuator can stably carry in both dynamic motion and static holding states.

[0095] In this embodiment, the force balance formula can be expressed as:

[0096]

[0097] in, is the rodless chamber pressure, is the rodless cavity area, is the maximum load force. , is a known quantity given according to the design requirements of the fuel system, is a known quantity determined according to the working conditions, is the known quantity solved in the above process. Therefore, by solving the above formula, the rodless chamber pressure can be obtained. .

[0098] Step 203, substituting the rodless chamber pressure, the flow coefficient, the throttling area, the maximum actuation distance and the longest actuation time of the electro-hydraulic servo valve into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0099] The minimum working pressure refers to the minimum pressure required for the actuator to work normally, that is, the pressure of the actuator needs to meet the minimum working pressure in order to work normally.

[0100] In this embodiment, the following formula can be obtained based on the flow balance relationship of the rodless cavity:

[0101]

[0102] in, is the minimum working pressure. , , are all known quantities that are input. is the known quantity given according to the design requirements, is the known quantity to be solved in the above process. By solving the above formula, the minimum working pressure can be obtained. .

[0103] It can be understood that, in this embodiment, if the fuel system includes multiple actuators, the above solution process can correspond to any actuator in any working condition. Therefore, when the minimum working pressure is obtained, As .

[0104] In this embodiment, the computer device first substitutes the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula to obtain the rod chamber pressure. Next, the rod chamber pressure, rod chamber area, rodless chamber area of ​​the actuating cylinder, and the maximum load force of the actuating device are substituted into the force balance formula to obtain the rodless chamber pressure. Then, the rodless chamber pressure, the flow coefficient, throttling area, maximum actuating distance, and longest actuating time of the electro-hydraulic servo valve are substituted into the rodless chamber flow balance formula to obtain the minimum working pressure. In this process, the quantified minimum working pressure can be obtained according to the relevant parameters of the fuel system and the actuating device, so that the minimum working pressure can be accurately obtained, thereby improving the accuracy of the obtained minimum working pressure.

[0105] The process of obtaining the consumption flow of the fuel system during operation is described in detail below. In an exemplary embodiment, Figure 3 As shown, the above-mentioned method of obtaining the consumption flow of the fuel system during operation includes:

[0106] Step 301, obtaining the metering flow, steady-state consumption flow and dynamic consumption flow of the fuel system.

[0107] Among them, the metering flow is the amount of fuel passing through the fuel metering unit of the fuel system per unit time, the steady-state consumption flow refers to the fuel flow required to be consumed by each component in the fuel system due to cooling and leakage, and the dynamic consumption flow refers to the flow consumed by each actuator in the fuel system due to the actuation process.

[0108] The specific process of obtaining the above-mentioned multiple consumption flows is described in detail below:

[0109] In a first possible implementation, the process of obtaining the metering flow includes: determining the metering flow according to an engine performance model corresponding to the fuel system.

[0110] The engine performance model refers to a model that describes and predicts the performance of the engine under different working conditions through mathematical and physical principles. In different engine performance models, metering flows of different functions can be set. Therefore, the computer device can determine the corresponding metering flow according to the engine performance model.

[0111] In a second possible implementation manner, the process of obtaining the steady-state consumption flow includes: determining the sum of the cooling consumption flow and the leakage consumption flow of the fuel system as the steady-state consumption flow.

[0112] The cooling consumption flow refers to the flow consumed by the components in the fuel system that require cooling during cooling. The components that require cooling may include servo valves, solenoid valves, guide vanes, etc. For example, in the working process of the actuator, the consumption flow of the cooling components may be the flow consumed by the cooling of the actuator cylinder. The leakage consumption flow refers to the leakage flow of the electro-hydraulic conversion device in the fuel system. For example, the leakage consumption flow may include the leakage flow of the electro-hydraulic servo valve, the leakage flow of the solenoid valve, etc.

[0113] Among them, the cooling consumption flow and leakage consumption flow exist in the entire working range of the engine, and the value changes with the working conditions. The cooling flow of a single actuator can be expressed as:

[0114]

[0115] in, Indicates the cooling flow of a single actuator. represents the equivalent diameter of the cooling hole, Indicates the pressure difference between the rod cavity and the rodless cavity. For example, when the equivalent diameter of the cooling hole is 0.38mm and the pressure difference between the rod cavity and the rodless cavity is 5MPa, the total cooling flow rate of 10 identical actuators is 5.39L / min.

[0116] In this embodiment, if the fuel system includes multiple electro-hydraulic conversion devices, the computer device can obtain multiple leakage consumption flows from the specification manuals corresponding to each electro-hydraulic conversion device, and use the sum of the multiple leakage consumption flows as the upper limit value of the leakage consumption flow.

[0117] The steady-state consumption flow can be expressed as:

[0118]

[0119] in, represents the steady-state consumption flow, Indicates the cooling consumption flow, Indicates leakage consumption flow, Indicates the number of cooling items, Indicates the number of leaked items.

[0120] In a third possible implementation, Figure 4 As shown, the process of obtaining dynamic traffic consumption includes:

[0121] Step 401, calculating the ratio between the maximum actuation distance and the longest actuation time of an actuating cylinder included in the actuating device.

[0122] Step 402, the ratio is multiplied by the rodless chamber area of ​​the actuator to determine the dynamic consumption flow.

[0123] The dynamic consumption flow refers to the flow consumed by each actuator during the actuation process. Unlike the steady-state consumption flow, the dynamic flow consumption does not occur continuously, but only exists during the displacement change process of the actuator.

[0124] The sum of the upper limits of dynamic consumption flow of each actuator in the fuel system can be expressed as:

[0125]

[0126] in, Indicates the number of actuators, represents the dynamic consumption flow of the i-th actuator, That is, the dynamic consumption flow of the i-th actuator device can be obtained by first calculating the ratio between the maximum actuating distance and the longest actuating time of the actuator cylinder corresponding to the i-th actuator device, and then calculating the product of the ratio and the rodless cavity area of ​​the actuator cylinder, and determining the product as the dynamic consumption flow.

[0127] Step 302, determining the sum of the metering flow, the steady-state consumption flow and the dynamic consumption flow as the consumption flow.

[0128] In this embodiment, the computer device may calculate the sum of the metering flow, the steady-state consumption flow, and the dynamic consumption flow, and then determine the sum value corresponding to the sum result as the consumption flow.

[0129] In this embodiment, the computer device obtains the metered flow, steady-state consumption flow and dynamic consumption flow of the fuel system, and can determine the sum of the metered flow, steady-state consumption flow and dynamic consumption flow as the consumption flow. Since the method for determining the consumption flow is considered from multiple angles, the accuracy of the determined consumption flow can be improved.

[0130] In an exemplary embodiment, Figure 5 As shown, the fuel supply pressure that can be provided by the above-mentioned fuel system includes:

[0131] Step 501, substitute the metering flow rate of the fuel system, the working fluid density, the actuator valve pressure difference, the reverse pressure of the combustion chamber of the engine, the nozzle equivalent area, and the nozzle flow coefficient into the formula of the nozzle flow rate and the pressure difference before and after the nozzle to obtain the metering pressure of the fuel system.

[0132] Among them, the working fluid density is the density of the fuel inside the fuel system, that is, the fuel density. The actuator valve refers to the components included in the fuel system, and the actuator valve pressure difference refers to the pressure difference between the inlet and outlet of the actuator valve. The combustion chamber reverse pressure is the pressure corresponding to the combustion of the engine's combustion chamber when the pressure in the combustion chamber is lower than the atmospheric pressure. The nozzle equivalent area refers to the equivalent area in the engine's combustion chamber composed of the nozzle ring outlet area and the impeller outlet area. The nozzle flow coefficient refers to the flow coefficient corresponding to the fuel flowing through the nozzle throttle hole. Usually, the value of the nozzle flow coefficient can be between 0.6-0.7.

[0133] It should be noted that the metering flow and the reverse pressure of the combustion chamber are different under different working conditions of the engine. The metering flow and the reverse pressure of the combustion chamber can be obtained by simulating the engine performance model under different working conditions. The execution gate pressure difference and the nozzle equivalent area can be determined according to the design requirements of the fuel system.

[0134] In this embodiment, the formula of nozzle flow rate and pressure difference before and after the nozzle can be expressed as:

[0135]

[0136] in, is the pressure after metering, is the nozzle flow coefficient, is the nozzle equivalent area, To implement the valve pressure differential, is the reverse pressure of the combustion chamber, is the working fluid density, For any working condition, the corresponding combustion chamber reverse pressure can be obtained based on the engine performance model. and metering flow , then combined with the nozzle equivalent area , solve for the pressure after metering .

[0137] Step 502, determining the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve.

[0138] The minimum opening pressure of the actuator valve is the minimum opening pressure of the actuator valve of the fuel system, that is, the actuator valve can only be opened when the inlet pressure of the actuator valve reaches the minimum pressure threshold.

[0139] In this embodiment, the computer device can calculate the difference between the post-metering pressure and the minimum opening pressure of the actuator valve, and determine the maximum value according to the difference. Optionally, if the difference is a positive value, the maximum value can be determined as the post-metering pressure, and if the difference is a negative value, the maximum value can be determined as the minimum opening pressure of the actuator valve.

[0140] Step 503: Determine the fuel supply pressure by adding the maximum value to the differential pressure of the metering valve in the fuel system.

[0141] Among them, the metering valve is a component included in the fuel system, and the differential pressure of the metering valve refers to the pressure difference between the inlet and outlet of the metering valve.

[0142] In this embodiment, the computer device can calculate the sum value between the maximum value and the differential pressure of the metering valve, and determine the sum value as the fuel supply pressure.

[0143] Among them, the formula for determining the fuel supply pressure can be expressed as:

[0144]

[0145] Among them, is the minimum opening pressure of the actuator valve, is the differential pressure of the metering valve.

[0146] In this embodiment, the computer device substitutes the metering flow rate of the fuel system, the working fluid density, the differential pressure of the actuator valve, the reverse pressure of the combustion chamber included in the engine, the nozzle equivalent area, and the nozzle flow coefficient into the nozzle flow rate and the differential pressure formula before and after the nozzle to obtain the metered pressure of the fuel system. Then, it determines the maximum value between the metered pressure and the minimum opening pressure of the actuator valve, and determines the sum value of the maximum value and the differential pressure of the metering valve in the fuel system as the fuel supply pressure. In the process of determining the fuel supply pressure, it is possible to quantitatively analyze the fuel supply pressure using multiple parameters related to the fuel supply pressure, thereby improving the accuracy of the determined fuel supply pressure.

[0147] In an exemplary embodiment, the process of obtaining the fuel supply flow rate that the fuel system can provide includes: substituting the fuel flow rate of the fuel system in the ignition state, the physical speed of the high-pressure rotor corresponding to the fuel flow rate of the fuel system in the ignition state, and the physical speed component of the high-pressure rotor of the fuel system under the target operating condition into the fuel supply flow rate formula to obtain the fuel supply flow rate.

[0148] Among them, the fuel supply flow rate of the fuel system can be the fuel flow rate that the gear pump included in the fuel system can provide. The physical speed of the high-pressure rotor refers to the speed of the rotor in the ignition state, and the physical speed component of the high-pressure rotor refers to the component of the physical speed of the high-pressure rotor under the specified operating condition x. Among them, information such as the speed of the high-pressure rotor can be set in the target operating condition, and the speed is different in different operating conditions.

[0149] Assuming that the gear pump efficiency remains unchanged in the ignition to 100% speed range, the calculation formula for the fuel supply flow rate can be expressed as:

[0150]

[0151] Among them, is the oil supply flow rate under working condition x, is the fuel flow rate under ignition state, Indicates the physical speed of the high-pressure rotor, Represents the physical speed component of the high-pressure rotor under operating condition x.

[0152] In this embodiment, the computer device obtains the fuel supply flow rate by substituting the fuel flow rate of the fuel system in the ignition state, the high-pressure rotor physical speed corresponding to the fuel flow rate of the fuel system in the ignition state, and the high-pressure rotor physical speed component of the fuel system under the target working condition into the fuel supply flow rate formula, and can perform quantitative analysis on the fuel supply flow rate, thereby improving the accuracy of the determined fuel supply flow rate.

[0153] In an exemplary embodiment, a small and medium thrust twin-rotor turbofan engine is taken as an example, wherein the control system of the engine is composed of an electronic controller, a fuel centrifugal boost pump, a main fuel pump, a main fuel control device, a guide vane control device, a nozzle oil source pump, a nozzle control device, a booster fuel pump, a booster fuel control device, a jet ignition device, a sensor, etc. Among them, the fuel control system is the key design part. In the design of the adaptive variable cycle engine, the requirements of fan guide vane angle adjustment, duct flow control valve position adjustment, and rear adjustable duct ejector position adjustment are added.

[0154] In this embodiment, taking the actuating device as an implicit regulating device as an example, the matching analysis of the fuel system is performed using the matching verification method of the fuel system.

[0155] First, the matching analysis of the pressure constraints of the fuel system is carried out.

[0156] If the relevant parameters of the ejection regulating device are as shown in Table 1, then according to Table 1, the pressure of the rod chamber is 1 MPa, and the pressure of the rodless chamber is 3.85 MPa, so the minimum working pressure is 4.96 MPa.

[0157] Table 1

[0158]

[0159] by Taking the working condition as an example, the metering flow is about 2105L / h, and the reverse pressure of the combustion chamber is about 1.8MPa. If the relevant parameters of the main pump outlet pressure of the fuel system are shown in Table 2, the pressure after metering can be obtained to be about 7.5MPa. Combined with the above calculation formula for the fuel supply pressure, it can be concluded that the fuel supply pressure is 7.8MPa.

[0160] Table 2

[0161]

[0162] Therefore, it can be determined that the oil supply pressure is greater than the minimum working pressure, indicating that the actuator meets the pressure constraint conditions under this working condition.

[0163] Secondly, the matching analysis of the flow constraints of the fuel system is carried out:

[0164] ① Assume the fuel flow rate under ignition state 5L / min, high pressure rotor physical speed 1680rpm, high pressure speed component rpm, where represents the dimensionless speed of the high-pressure rotor. Then the oil supply flow rate can be expressed as .in, [0,1].

[0165] ② Assuming the equivalent aperture is 0.38mm, the pressure difference between the rod cavity and the rodless cavity is 5MPa, and the total cooling flow of 10 identical actuators is 5.39L / min. The leakage flow corresponding to the electro-hydraulic conversion device can be obtained from the specification manual. For example, the leakage flow of the electro-hydraulic servo valve is 0.5*2=1L / min, and the leakage flow of the solenoid valve is 0.1L / min, so the steady-state consumption flow is 6.49L / min.

[0166] ③ According to the parameter values ​​in Table 1 above, it can be obtained that the upper limit of the steady-state consumption flow rate of the ejector is approximately 22.44L / min.

[0167] ④ The metering flow can be determined by the engine performance model, for example, assuming a dimensionless high pressure speed , the metering flow rate is about 7L / min.

[0168] Therefore, it can be determined that the oil supply flow rate is greater than the sum of the steady-state consumption flow rate, the steady-state consumption flow rate and the metering flow rate, indicating that the actuator meets the flow constraint conditions under this working condition.

[0169] To facilitate understanding by those skilled in the art, the following is a detailed introduction to the fuel system matching verification method provided by the present application. The method may include:

[0170] S1. Substitute the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula to obtain the rod chamber pressure.

[0171] S2, substitute the rod chamber pressure, rod chamber area, rodless chamber area of ​​the actuator and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure.

[0172] S3, substitute the rodless chamber pressure, flow coefficient, throttling area, maximum actuation distance and longest actuation time of the electro-hydraulic servo valve into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0173] S4, substitute the metering flow rate of the fuel system, the working fluid density, the pressure difference of the actuator valve, the reverse pressure of the combustion chamber of the engine, the nozzle equivalent area and the nozzle flow coefficient into the formula of the nozzle flow rate and the pressure difference before and after the nozzle to obtain the metering pressure of the fuel system.

[0174] S5, determining the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve.

[0175] S6, determining the sum of the maximum value and the pressure difference of the metering valve of the fuel system as the fuel supply pressure.

[0176] S7, determining the metering flow rate according to the engine performance model corresponding to the fuel system.

[0177] S8, determining the sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system as the steady-state consumption flow.

[0178] S9, calculating the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device.

[0179] S10, the ratio is multiplied by the rodless chamber area of ​​the actuator to determine the dynamic consumption flow rate.

[0180] S10, substitute the fuel flow of the fuel system in the ignition state, the physical speed of the high-pressure rotor corresponding to the fuel flow of the fuel system in the ignition state, and the physical speed component of the high-pressure rotor of the fuel system under the target working condition into the fuel supply flow formula to obtain the fuel supply flow.

[0181] S11, comparing the oil supply pressure with the minimum working pressure to obtain a first comparison result, and comparing the oil supply flow rate with the consumption flow rate to obtain a second comparison result.

[0182] S12, when the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate, determine that the verification result is verification passed.

[0183] It should be noted that for the descriptions in the above S1-S12, reference may be made to the relevant descriptions in the above embodiments, and the effects are similar, so this embodiment will not be repeated here.

[0184] It should be understood that although the steps in the flowcharts involved in the above embodiments are sequentially shown according to the arrows, these steps are not necessarily executed in the order indicated by the arrows. Unless there is a clear indication in this article, the execution of these steps has no strict order limit, and these steps can be executed in other orders. Moreover, at least a part of the steps in the flowcharts involved in the above embodiments may include multiple steps or multiple stages. These steps or stages are not necessarily executed at the same time, but can be executed at different times. The execution order of these steps or stages is not necessarily sequential, but can be executed alternately or in turn with at least a part of other steps or steps or stages in other steps.

[0185] Based on the same inventive concept, an embodiment of the present application further provides a fuel system matching verification device for implementing the fuel system matching verification method described above. The solution provided by this device to solve the problem is similar to the solution described in the above method. Therefore, the specific limitations in one or more embodiments of the fuel system matching verification device provided below can refer to the limitations on the fuel system matching verification method in the above text, and will not be repeated here.

[0186] In one embodiment, as Figure 6 shown, a fuel system matching verification device is provided, including: a first acquisition module 601, a comparison module 602, and a second acquisition module 603, where:

[0187] The first acquisition module 601 is configured to acquire the fuel supply pressure and fuel supply flow that the fuel system can provide, the minimum working pressure of the actuating device included in the fuel system, and acquire the consumption flow during the operation of the fuel system;

[0188] The comparison module 602 is configured to compare the fuel supply pressure with the minimum working pressure to obtain a first comparison result, and compare the fuel supply flow with the consumption flow to obtain a second comparison result;

[0189] The second acquisition module 603 is configured to verify the matching of the fuel system according to the first comparison result and the second comparison result, and obtain a verification result.

[0190] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, and will not be repeated here.

[0191] In one embodiment, the number of actuating devices is multiple, and the above second acquisition module includes:

[0192] The determination unit is used to determine that the verification result is a verification pass when the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate.

[0193] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0194] In one embodiment, the first acquisition module 601 includes:

[0195] A first acquisition unit is used to substitute the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the area of ​​the rod chamber of the actuating device, the maximum actuating distance, and the longest actuating time of the actuating cylinder included in the actuating device into a rod chamber flow balance formula to obtain the rod chamber pressure;

[0196] The second acquisition unit is used to substitute the rod cavity pressure, the rod cavity area, the rodless cavity area of ​​the actuator cylinder and the maximum load force of the actuator into the force balance formula to obtain the rodless cavity pressure;

[0197] The third acquisition unit is used to substitute the rodless chamber pressure, the flow coefficient, the throttling area, the maximum actuation distance and the longest actuation time of the electro-hydraulic servo valve into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0198] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0199] In one embodiment, the first acquisition module 601 further includes:

[0200] A fourth acquisition unit, used to acquire a metering flow, a steady-state consumption flow, and a dynamic consumption flow of a fuel system;

[0201] The fifth acquisition unit is used to determine the sum of the metering flow, the steady-state consumption flow and the dynamic consumption flow as the consumption flow.

[0202] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0203] In one embodiment, the fourth acquisition unit is specifically configured to:

[0204] The metering flow is determined based on the engine performance model corresponding to the fuel system.

[0205] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0206] In one embodiment, the fourth acquisition unit is specifically configured to:

[0207] The sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system is determined as the steady-state consumption flow.

[0208] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0209] In one embodiment, the fourth acquisition unit is specifically configured to:

[0210] Calculate the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device;

[0211] The dynamic consumption flow is determined by multiplying the ratio by the rodless chamber area of ​​the actuator.

[0212] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0213] In one embodiment, the first acquisition module 601 further includes:

[0214] a sixth acquisition unit, for substituting the metering flow rate of the fuel system, the working fluid density, the pressure difference of the actuator valve, the reverse pressure of the combustion chamber of the engine, the nozzle equivalent area, and the nozzle flow coefficient into the formula of the nozzle flow rate and the pressure difference before and after the nozzle to obtain the metering pressure of the fuel system;

[0215] A first determining unit, for determining a maximum value of a post-metering pressure and a minimum opening pressure of the actuator valve;

[0216] The second determining unit is used to determine the sum of the maximum value and the pressure difference of the metering valve of the fuel system as the fuel supply pressure.

[0217] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0218] In one embodiment, the first acquisition module 601 further includes:

[0219] The seventh acquisition unit is used to substitute the fuel flow of the fuel system in the ignition state, the high-pressure rotor physical speed corresponding to the fuel flow of the fuel system in the ignition state, and the high-pressure rotor physical speed component of the fuel system under the target working condition into the fuel supply flow formula to obtain the fuel supply flow.

[0220] The fuel system matching verification device provided in this embodiment can execute the above method embodiment, and its implementation principle and technical effect are similar, which will not be repeated here.

[0221] Each module in the above fuel system matching verification device can be implemented in whole or in part by software, hardware and their combination. Each module can be embedded in or independent of the processor in the computer device in the form of hardware, or can be stored in the memory of the computer device in the form of software, so that the processor can call and execute the corresponding operations of each module.

[0222] In an exemplary embodiment, a computer device is provided. The computer device may be a server, and its internal structure diagram may be as shown in FIG. Figure 7 As shown. The computer device includes a processor, a memory, an input / output interface (Input / Output, referred to as I / O) and a communication interface. The processor, the memory and the input / output interface are connected through a system bus, and the communication interface is connected to the system bus through the input / output interface. The processor of the computer device is used to provide computing and control capabilities. The memory of the computer device includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system, a computer program and a database. The internal memory provides an environment for the operation of the operating system and the computer program in the non-volatile storage medium. The database of the computer device is used to store the metering and actuation data of the fuel system. The input / output interface of the computer device is used to exchange information between the processor and an external device. The communication interface of the computer device is used to communicate with an external terminal through a network connection. When the computer program is executed by the processor, a matching verification method for a fuel system is implemented.

[0223] Those skilled in the art will understand that Figure 7 The structure shown in the figure is only a block diagram of a part of the structure related to the solution of the present application, and does not constitute a limitation on the computer device to which the solution of the present application is applied. The specific computer device may include more or fewer components than those shown in the figure, or combine certain components, or have a different arrangement of components.

[0224] In one embodiment, a computer device is provided, including a memory and a processor, wherein a computer program is stored in the memory, and when the processor executes the computer program, the following steps are implemented:

[0225] Obtain the fuel supply pressure and fuel supply flow that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and obtain the consumption flow of the fuel system during operation;

[0226] The oil supply pressure is compared with the minimum working pressure to obtain a first comparison result, and the oil supply flow rate is compared with the consumption flow rate to obtain a second comparison result;

[0227] The matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result.

[0228] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0229] When the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate, the verification result is determined to be verification passed.

[0230] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0231] Substitute the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula to obtain the rod chamber pressure;

[0232] Substitute the rod chamber pressure, rod chamber area, rodless chamber area of ​​the actuator and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure;

[0233] Substitute the rodless chamber pressure, the flow coefficient of the electro-hydraulic servo valve, the throttling area, the maximum actuation distance and the longest actuation time into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0234] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0235] Obtain the metering flow, steady-state consumption flow and dynamic consumption flow of the fuel system;

[0236] The sum of the metering flow, the steady-state consumption flow and the dynamic consumption flow is determined as the consumption flow.

[0237] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0238] The metering flow is determined based on the engine performance model corresponding to the fuel system.

[0239] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0240] The sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system is determined as the steady-state consumption flow.

[0241] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0242] Calculate the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device;

[0243] The dynamic consumption flow is determined by multiplying the ratio by the rodless chamber area of ​​the actuator.

[0244] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0245] Substitute the metering flow rate of the fuel system, the working fluid density, the pressure difference of the actuator valve, the reverse pressure of the combustion chamber of the engine, the nozzle equivalent area, and the nozzle flow coefficient into the formula of the nozzle flow rate and the pressure difference before and after the nozzle to obtain the metering pressure of the fuel system;

[0246] Determine the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve;

[0247] The sum of the maximum value and the pressure difference of the metering valve of the fuel system is determined as the fuel supply pressure. In one embodiment, the processor further implements the following steps when executing the computer program:

[0248] The fuel flow rate of the fuel system under the ignition state, the physical speed of the high-pressure rotor corresponding to the fuel flow rate of the fuel system under the ignition state, and the physical speed component of the high-pressure rotor of the fuel system under the target working condition are substituted into the fuel supply flow rate formula to obtain the fuel supply flow rate.

[0249] In one embodiment, a computer readable storage medium is provided, on which a computer program is stored, and when the computer program is executed by a processor, the following steps are implemented:

[0250] Obtain the fuel supply pressure and fuel supply flow that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and obtain the consumption flow of the fuel system during operation;

[0251] The oil supply pressure is compared with the minimum working pressure to obtain a first comparison result, and the oil supply flow rate is compared with the consumption flow rate to obtain a second comparison result;

[0252] The matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result.

[0253] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0254] When the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate, the verification result is determined to be verification passed.

[0255] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0256] Substitute the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula to obtain the rod chamber pressure;

[0257] Substitute the rod chamber pressure, rod chamber area, rodless chamber area of ​​the actuator and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure;

[0258] Substitute the rodless chamber pressure, the flow coefficient of the electro-hydraulic servo valve, the throttling area, the maximum actuation distance and the longest actuation time into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0259] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0260] Obtain the metering flow, steady-state consumption flow and dynamic consumption flow of the fuel system;

[0261] The sum of the metering flow, the steady-state consumption flow and the dynamic consumption flow is determined as the consumption flow.

[0262] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0263] The metering flow is determined based on the engine performance model corresponding to the fuel system.

[0264] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0265] The sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system is determined as the steady-state consumption flow.

[0266] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0267] Calculate the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device;

[0268] The dynamic consumption flow is determined by multiplying the ratio by the rodless chamber area of ​​the actuator.

[0269] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0270] Substitute the metering flow rate of the fuel system, the working fluid density, the pressure difference of the actuator valve, the reverse pressure of the combustion chamber of the engine, the nozzle equivalent area, and the nozzle flow coefficient into the formula of the nozzle flow rate and the pressure difference before and after the nozzle to obtain the metering pressure of the fuel system;

[0271] Determine the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve;

[0272] The sum of the maximum value and the pressure difference of the metering valve of the fuel system is determined as the fuel supply pressure. In one embodiment, when the computer program is executed by the processor, the following steps are also implemented:

[0273] The fuel flow rate of the fuel system under the ignition state, the physical speed of the high-pressure rotor corresponding to the fuel flow rate of the fuel system under the ignition state, and the physical speed component of the high-pressure rotor of the fuel system under the target working condition are substituted into the fuel supply flow rate formula to obtain the fuel supply flow rate.

[0274] In one embodiment, a computer program product is provided, comprising a computer program, which, when executed by a processor, implements the following steps:

[0275] Obtain the fuel supply pressure and fuel supply flow that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and obtain the consumption flow of the fuel system during operation;

[0276] The oil supply pressure is compared with the minimum working pressure to obtain a first comparison result, and the oil supply flow rate is compared with the consumption flow rate to obtain a second comparison result;

[0277] The matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result.

[0278] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0279] When the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate, the verification result is determined to be verification passed.

[0280] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0281] Substitute the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula to obtain the rod chamber pressure;

[0282] Substitute the rod chamber pressure, rod chamber area, rodless chamber area of ​​the actuator and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure;

[0283] Substitute the rodless chamber pressure, the flow coefficient of the electro-hydraulic servo valve, the throttling area, the maximum actuation distance and the longest actuation time into the rodless chamber flow balance formula to obtain the minimum working pressure.

[0284] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0285] Obtain the metering flow, steady-state consumption flow and dynamic consumption flow of the fuel system;

[0286] The sum of the metering flow, the steady-state consumption flow and the dynamic consumption flow is determined as the consumption flow.

[0287] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0288] The metering flow is determined based on the engine performance model corresponding to the fuel system.

[0289] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0290] The sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system is determined as the steady-state consumption flow.

[0291] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0292] Calculate the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device;

[0293] The dynamic consumption flow is determined by multiplying the ratio by the rodless chamber area of ​​the actuator.

[0294] In one embodiment, when the computer program is executed by a processor, the following steps are also implemented:

[0295] Substitute the metering flow rate of the fuel system, the working fluid density, the pressure difference of the actuator valve, the reverse pressure of the combustion chamber of the engine, the nozzle equivalent area, and the nozzle flow coefficient into the formula of the nozzle flow rate and the pressure difference before and after the nozzle to obtain the metering pressure of the fuel system;

[0296] Determine the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve;

[0297] The sum of the maximum value and the pressure difference of the metering valve of the fuel system is determined as the fuel supply pressure. In one embodiment, when the computer program is executed by the processor, the following steps are also implemented:

[0298] The fuel flow rate of the fuel system under the ignition state, the physical speed of the high-pressure rotor corresponding to the fuel flow rate of the fuel system under the ignition state, and the physical speed component of the high-pressure rotor of the fuel system under the target working condition are substituted into the fuel supply flow rate formula to obtain the fuel supply flow rate.

[0299] Those skilled in the art can understand that all or part of the processes in the above-mentioned embodiments can be completed by instructing the relevant hardware through a computer program, and the computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, any reference to the memory, database or other medium used in the embodiments provided in this application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetoresistive random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. As an illustration and not limitation, RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM). The database involved in each embodiment provided in this application may include at least one of a relational database and a non-relational database. Non-relational databases may include distributed databases based on blockchains, etc., but are not limited to this. The processor involved in each embodiment provided in this application may be a general-purpose processor, a central processing unit, a graphics processor, a digital signal processor, a programmable logic device, a data processing logic device based on quantum computing, etc., but are not limited to this.

[0300] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0301] The above embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the present application shall be subject to the attached claims.

Claims

1. A fuel system matching verification method, characterized in that: The method comprises: Obtaining the fuel supply pressure and fuel supply flow rate that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and obtaining the consumption flow rate of the fuel system during operation; Comparing the oil supply pressure with the minimum working pressure to obtain a first comparison result, and comparing the oil supply flow rate with the consumption flow rate to obtain a second comparison result; The matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result.

2. The method according to claim 1, characterized in that The number of the actuating devices is multiple, and the matching of the fuel system is verified according to the first comparison result and the second comparison result to obtain a verification result, including: When the first comparison result is that the oil supply pressure is greater than the maximum value of the minimum working pressures, and the second comparison result is that the oil supply flow rate is greater than the consumption flow rate, the verification result is determined to be verification passed.

3. The method according to claim 1, characterized in that The process of obtaining the minimum working pressure includes: Substituting the flow coefficient, throttling area, and pressure of the electro-hydraulic servo valve included in the actuating device, as well as the rod chamber area, maximum actuating distance, and longest actuating time of the actuating cylinder included in the actuating device into the rod chamber flow balance formula, the rod chamber pressure is obtained; Substituting the rod chamber pressure, the rod chamber area, the rodless chamber area of ​​the actuator cylinder and the maximum load force of the actuator into the force balance formula to obtain the rodless chamber pressure; The rodless chamber pressure, the flow coefficient of the electro-hydraulic servo valve, the throttling area, the maximum actuation distance and the longest actuation time are substituted into the rodless chamber flow balance formula to obtain the minimum working pressure.

4. The method according to claim 1, characterized in that The obtaining of the consumption flow of the fuel system during operation includes: Obtaining a metered flow, a steady-state consumption flow, and a dynamic consumption flow of the fuel system; The consumption flow rate is determined as the sum of the metering flow rate, the steady-state consumption flow rate and the dynamic consumption flow rate.

5. The method according to claim 4, characterized in that The process of obtaining the metered flow includes: The metering flow is determined according to an engine performance model corresponding to the fuel system.

6. The method according to claim 4, characterized in that The process of obtaining the steady-state consumption flow includes: The sum of the cooling consumption flow of the fuel system and the leakage consumption flow of the fuel system is determined as the steady-state consumption flow.

7. The method according to claim 4, characterized in that The process of obtaining the dynamic consumption flow includes: Calculating the ratio between the maximum actuation distance and the longest actuation time of the actuating cylinder included in the actuating device; The dynamic consumption flow is determined by multiplying the ratio by the rodless chamber area of ​​the actuator.

8. The method according to claim 1, characterized in that The obtaining of the fuel supply pressure that can be provided by the fuel system includes: Substituting the metering flow rate, working fluid density, actuator valve pressure difference of the fuel system, reverse pressure of the combustion chamber included in the engine, nozzle equivalent area, and nozzle flow coefficient into the formula of nozzle flow rate and nozzle front and rear pressure difference to obtain the metering pressure of the fuel system; Determining the maximum value of the post-metering pressure and the minimum opening pressure of the actuator valve; The sum of the maximum value and the differential pressure of the metering valve of the fuel system is determined as the fuel supply pressure.

9. The method according to claim 1, characterized in that: The process of obtaining the fuel supply flow rate that can be provided by the fuel system includes: The fuel flow of the fuel system in the ignition state, the high-pressure rotor physical speed corresponding to the fuel flow of the fuel system in the ignition state, and the high-pressure rotor physical speed component of the fuel system under the target operating conditions are substituted into the fuel supply flow formula to obtain the fuel supply flow.

10. A fuel system matching verification device, characterized in that: The device comprises: A first acquisition module is used to acquire the fuel supply pressure and fuel supply flow rate that can be provided by the fuel system and the minimum working pressure of the actuating device included in the fuel system, and to acquire the consumption flow rate of the fuel system during operation; A comparison module, configured to compare the oil supply pressure with the minimum working pressure to obtain a first comparison result, and to compare the oil supply flow rate with the consumption flow rate to obtain a second comparison result; The second acquisition module is used to verify the matching of the fuel system according to the first comparison result and the second comparison result to obtain a verification result.

11. A computer device comprising a memory and a processor, wherein the memory stores a computer program, wherein: When the processor executes the computer program, the steps of the method according to any one of claims 1 to 9 are implemented.

12. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of the method according to any one of claims 1 to 9 are implemented.

13. A computer program product, comprising a computer program, characterized in that When the computer program is executed by a processor, the steps of the method according to any one of claims 1 to 9 are implemented.

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