A closed-loop control system and method for a constant pressure valve of an aircraft engine fuel servo

Abstract

The present application provides a closed-loop control system and method for a constant pressure valve of an aircraft engine fuel servo, in which a stabilizing controller controls the constant pressure valve based on the reference return oil pressure increment and the constant pressure oil pressure increment output by the controlled object control device at the previous moment, and outputs control data for controlling the controlled object; the controlled object control device controls the controlled object based on the inlet pressure increment and the variable load area increment of the disturbance input, as well as the control data, and outputs the constant pressure oil pressure increment at the current moment. The system reveals the design mechanism of the constant pressure valve, and processes the dynamic performance of the system based on the stabilizing controller and the controlled object control device.

Description

Technical Field

[0001] The present application relates to the design field of aircraft engine control systems, and in particular, to a constant pressure valve closed-loop control system and method for an aircraft engine fuel servo. Background Art

[0002] The aircraft engine fuel servo constant pressure device is one of the most basic and important components in the aircraft engine hydraulic mechanical control system. It adjusts the oil pressure after the pump with a wide working range to the pressure that meets the system requirements to ensure the stable operation of the hydraulic servo system and the fuel metering system. The constant pressure device provides the servo reference pressure, and its performance directly affects the stability and dynamic performance of the control system. If the constant pressure device works unstably, it will cause the output fuel pressure to fluctuate, causing problems such as engine combustion fluctuations and speed fluctuations; if the constant pressure device responds slowly, it will cause the servo pressure to be adjusted untimely and inaccurately, which will cause the hydraulic mechanical control system to lose its function and cause engine abnormalities.

[0003] The constant pressure device widely used in aircraft engine control systems is similar to the direct-acting constant pressure valve in industrial process control systems. At present, domestic and foreign scholars' research on direct-acting constant pressure valves mainly focuses on modeling, simulation, stability analysis, etc., while research on design is extremely rare. The dynamic model built in the early stage was limited to the transfer function method of classical control theory, and it was difficult to reveal the design mechanism of the constant pressure valve. Summary of the invention

[0004] The purpose of the embodiments of the present application is to provide a closed-loop control system and method for a constant pressure valve of an aircraft engine fuel servo, so as to solve the problem that the prior art cannot reveal the design mechanism of the constant pressure valve.

[0005] In a first aspect, a closed-loop control system for a constant pressure valve of an aircraft engine fuel servo is provided, the system may include: a stabilization controller and a controlled object control device;

[0006] The stabilization controller is used to calculate the constant pressure oil pressure increment ΔP0 based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output control data for controlling the controlled object;

[0007] The controlled object control device is used to adjust the inlet pressure increment ΔP based on the disturbance input. in and variable load area increment ΔA out2 , and the control data, control the controlled object, and output the constant pressure oil pressure increment ΔP at the current moment C .

[0008] In an optional implementation, the control data includes an inlet throttle flow area increment ΔA in And the constant pressure valve movement speed increment

[0009] In an optional implementation, the stabilization controller includes a constant pressure valve dynamic characteristic unit and a gain unit;

[0010] The constant pressure valve dynamic characteristic unit is based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output the displacement increment Δx of the constant pressure valve y And the constant pressure valve movement speed increment

[0011] The gain unit increases the displacement increment Δx of the constant pressure valve movement y Perform gain control and output the inlet throttle flow area increment ΔA in .

[0012] In an optional implementation, the gain control law of the stabilization controller is determined by the flow area A of the inlet throttle hole of the constant pressure valve. in and the inlet throttle opening x u The design function is A in =f in (x u ), and its deviation is expressed as ΔA in =-K C Δx y , where the inlet throttle opening increment Δx u The negative displacement increment of the constant pressure valve Δx y equal to the control gain of the stabilizing controller

[0013] In an optional implementation, the constant pressure valve closed-loop control system further includes a frequency domain analysis unit;

[0014] The frequency domain analysis unit is used to obtain the open-loop transfer function of the constant pressure valve closed-loop control system based on the acquired state space model of the stabilization controller and the controlled object control device; the open-loop transfer function includes 3 poles, 1 zero point and an open-loop gain;

[0015] Based on the control gain K of the stabilization controller C , the open-loop gain of the constant pressure valve closed-loop control system and the turning frequency ω3 of the frequency domain curve corresponding to the zero point in the open-loop transfer function are controlled.

[0016] In an optional implementation, the frequency domain analysis unit is further used for:

[0017] If detected Based on the spring elastic modulus K, the open-loop gain of the constant pressure valve closed-loop control system, the turning frequency ω1 and the turning frequency ω2 of the frequency domain curve corresponding to the first pole and the second pole in the open-loop transfer function are controlled; wherein, K f is the viscous friction coefficient, M y is the moving mass of the constant pressure valve;

[0018] In an optional implementation, the frequency domain analysis unit is further used for:

[0019] If detected Based on the volume V0 of the constant pressure chamber, the magnitude of the turning frequency ω4 of the frequency domain curve corresponding to the fourth pole in the open-loop transfer function of the constant pressure valve closed-loop control system is controlled.

[0020] In a second aspect, a method for closed-loop control system of a constant pressure valve of an aircraft engine fuel servo is provided, which is applied to the system described in the first aspect, and the method comprises:

[0021] The stabilization controller is based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output control data for controlling the controlled object;

[0022] The inlet pressure increment ΔP of the controlled object control device based on the disturbance input in and variable load area increment ΔA out2 , and the control data, control the controlled object, and output the constant pressure oil pressure increment ΔP at the current moment C .

[0023] According to a third aspect, a computer-readable storage medium is provided, wherein a computer program is stored in the computer-readable storage medium, and when the computer program is executed by a processor, the method steps in the second aspect are implemented.

[0024] The stabilization controller in the closed-loop control system of the constant pressure valve of the fuel servo of the aircraft engine provided in the embodiment of the present application is based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the control device of the controlled object at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , controls the constant pressure valve and outputs control data for controlling the controlled object; the controlled object control device controls the inlet pressure increment ΔP based on the disturbance input in and variable load area increment ΔA out2, and control data, control the controlled object, and output the current constant pressure oil pressure increment ΔP C The system reveals the design mechanism of the constant pressure valve and processes the dynamic performance of the system based on the stabilization controller and the controlled object control device. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments of the present application will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0026] Figure 1 A schematic diagram of the structure of a constant pressure valve provided in an embodiment of the present application;

[0027] Figure 2 A schematic diagram of the structure of a closed-loop control system for a constant pressure valve of an aircraft engine fuel servo provided in an embodiment of the present application;

[0028] Figure 3 A schematic diagram of a constant pressure valve control circuit design provided in an embodiment of the present application;

[0029] Figure 4 A schematic diagram of a Bode diagram provided in an embodiment of the present application;

[0030] Figure 5 A flow chart of a closed-loop control method for a constant pressure valve of an aircraft engine fuel servo provided in an embodiment of the present application. DETAILED DESCRIPTION

[0031] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments of the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0032] The closed-loop control method of the constant pressure valve of the aircraft engine fuel servo provided in the embodiment of the present application is divided into three parts to address the design problem of the constant pressure valve:

[0033] (1) A linear incremental description analysis method is proposed. The controlled object control system is described by the cavity pressure and the stabilization controller is described by the closed-loop feedback motion valve. The closed-loop control system of the constant pressure valve is constructed. By deriving the cavity pressure dynamic equation and the closed-loop feedback motion valve dynamic equation, the state space model and frequency domain response model of the constant pressure valve are established.

[0034] (2) Based on the frequency domain loop shaping analysis method, the influence of the key structural parameter - control gain on the system dynamic performance and stability is analyzed;

[0035] (3) On this basis, a frequency domain design method for control gain is proposed. At the same time, a design method for the inlet throttling orifice area and opening degree is given. The characteristic function relationship between the inlet throttling orifice area and opening degree of the constant pressure valve is clarified, which has great engineering significance.

[0036] Figure 1 A schematic diagram of the structure of a constant pressure valve provided in an embodiment of the present application is shown in FIG. Figure 1 As shown, P in is the inlet pressure, P C is the constant pressure oil pressure, P0 is the return oil pressure; A in is the inlet throttling flow area, A out1 is the fixed outlet flow area, A out2 is the variable load flow area; V0 is the control chamber volume; x y is the valve displacement. y0 is the initial position of the valve.

[0037] It should be noted that the increment of each physical quantity described below refers to the difference (or deviation) between the value of a physical quantity at a later moment and the value of the corresponding physical quantity at a previous moment.

[0038] For the description of the linear increment of the constant pressure valve, such as Figure 2 The figure shows a closed-loop control system of a constant pressure valve of an aircraft engine fuel servo provided by an embodiment of the present application. The system may include: a stabilization controller and a controlled object control device.

[0039] The stabilization controller is used to calculate the constant pressure oil pressure increment ΔP0 based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output control data for controlling the controlled object; the control data may include an increase in the flow area of ​​the inlet throttle hole ΔA in And the constant pressure valve movement speed increment

[0040] The plant control device is used to adjust the inlet pressure increment ΔP based on the disturbance inputin and variable load area increment ΔA out2 , and the control data, control the controlled object, and output the constant pressure oil pressure increment ΔP at the current moment C .

[0041] Furthermore, Figure 2 The middle stabilization controller may include a constant pressure valve dynamic characteristic unit and a gain control unit;

[0042] The constant pressure valve dynamic characteristic unit is used to determine the constant pressure oil pressure increment ΔP0 based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output the displacement increment Δx of the constant pressure valve y And the constant pressure valve movement speed increment

[0043] A gain control unit is used to increase the displacement increment Δx of the constant pressure valve movement. y Perform gain control and output the inlet throttle flow area increment ΔA in .

[0044] The gain control law of the stabilization controller is determined by the flow area A of the inlet throttle hole of the constant pressure valve. in and throttle opening x u The design function is A in =f in (x u ), and its deviation is expressed as ΔA in =-K C Δx y , where f in (x u ) represents the flow area of ​​the inlet throttle hole of the constant pressure valve A in and throttle opening x u The functional relationship of the inlet throttle opening increment Δx u The negative displacement increment of the constant pressure valve Δx y Equal, the control gain of the stabilizing controller

[0045] Specifically: According to its linearized gain characteristics: and Δx u =-Δx y (2), the gain control law of the stabilizing controller can be obtained as: ΔA in =-K C Δx y (3); where the flow area gradient is

[0046] Furthermore, the constant pressure valve closed-loop control system also includes a frequency domain analysis unit;

[0047] The frequency domain analysis unit obtains the open-loop transfer function of the closed-loop control system of the constant pressure valve based on the state space model of the stabilization controller and the controlled object control device; the open-loop transfer function consists of 3 poles, 1 zero point and open-loop gain; and based on the control gain K of the stabilization controller C , the open-loop gain of the constant pressure valve closed-loop control system and the turning frequency ω3 of the frequency domain curve corresponding to the zero point in the open-loop transfer function are controlled.

[0048] If detected The frequency domain analysis unit can control the open-loop gain of the constant pressure valve closed-loop control system, the turning frequency ω1 and the turning frequency ω2 of the frequency domain curve corresponding to the first pole and the second pole in the open-loop transfer function based on the spring elastic modulus K; wherein, K f is the viscous friction coefficient, M y is the moving mass of the constant pressure valve;

[0049] At the same time, the frequency domain analysis unit can also control the magnitude of the turning frequency ω4 of the frequency domain curve corresponding to the fourth pole in the open-loop transfer function of the constant pressure valve closed-loop control system based on the constant pressure chamber volume V0.

[0050] 1. Establish the dynamic equation of the constant pressure valve:

[0051] (1) The accused

[0052] The pressure differential-flow nonlinear dynamic equation of the main flow chamber of the constant pressure valve is described as:

[0053]

[0054] Among them, V0 is the volume of the constant pressure valve cavity, B is the elastic modulus of the liquid, ρ is the density of the liquid, C q is the orifice flow coefficient. in ,A out2 ,P in , P C As a variable, equation (5) is linearized with a small deviation at the steady-state point to obtain the pressure differential-flow linear dynamic equation:

[0055]

[0056] Among them, the inlet throttle area gain is:

[0057] The inlet throttle pressure gain is:

[0058] The outlet throttle area gain is:

[0059] The outlet throttle pressure gain is:

[0060] Then, the state space model of the controlled object is:

[0061]

[0062]

[0063] in,

[0064] C=[1],D=[0 0],H=[0 0](12)

[0065] (2) Stabilization controller

[0066] Establish the local coordinate system of valve motion, that is, take the steady-state working point x y0 =0 is the local coordinate origin of the valve core, x y is the relative displacement of the valve core, and the arrow direction is the positive direction of the local coordinate system.

[0067] Set the motion mass of the pressure valve to M y , the viscous friction coefficient is K f , the spring elastic modulus is K, and the pressure bearing area at both ends of the valve is A y , the initial compression force of the spring is F L , then the nonlinear dynamic equation of the constant pressure valve motion is:

[0068]

[0069] P C ,x y , As a variable, the nonlinear dynamic equation of the constant pressure valve motion is linearized with small deviation at the steady-state point, and the linear dynamic equation of the constant pressure valve motion is obtained:

[0070]

[0071] Taking into account the control gain characteristics, the state space model of the stabilizing controller is:

[0072]

[0073]

[0074] in, C S =[-K C 0],D S =[0](16)

[0075] 2. Design the frequency domain model of the constant pressure valve closed-loop system

[0076] Assume L is the system open-loop transfer function, the block diagram of the constant pressure valve control loop design is as follows: Figure 3 shown.

[0077] (1) Open-loop transfer function

[0078] The open-loop state space model of the known constant pressure valve is:

[0079]

[0080]

[0081]

[0082]

[0083] Where: C open =[1 0 0],D open =[0],H open =[0 0](18)

[0084] The system open-loop transfer function is:

[0085]

[0086] (2) Disturbance input transfer function: Definition

[0087] Then, ΔP in ΔP C The open-loop disturbance transfer function is:

[0088]

[0089] Similarly, ΔA out2 ΔP C The open-loop disturbance transfer function is:

[0090]

[0091] (3) Control output transfer function

[0092] The closed-loop sensitivity function is defined as:

[0093]

[0094] Assuming ΔP0 = 0, the closed-loop transfer function of the system is:

[0095] ΔP C =S·G Pin-Pc ΔPin +S.G Aout2-Pc ΔA out2 (twenty four)

[0096] Among them, ΔP in ΔP C The closed-loop disturbance transfer function is:

[0097]

[0098] Its stable gain is:

[0099] Similarly, ΔA out2 ΔP C The closed-loop disturbance transfer function is

[0100]

[0101] Its steady-state gain is:

[0102] Furthermore, the influence of control gain on the open-loop frequency domain characteristics of the system and the closed-loop stability analysis are

[0103] 1. Calculation of the turning frequency of the system open-loop frequency domain characteristics

[0104] It can be seen from formula (19) that the open-loop transfer function consists of three poles, one zero and an open-loop gain. The corner frequency of its frequency domain curve is calculated as follows.

[0105] (1) When When , the second-order link is an underdamped oscillation link, and its poles are:

[0106]

[0107] The turning frequencies are defined as:

[0108] (2) When When , the second-order link is an overdamped non-oscillating link, and its poles are:

[0109]

[0110] The turning frequencies are defined as:

[0111] The third pole is:

[0112] The turning frequency is defined as:

[0113] Zero point is:

[0114] The turning frequency is defined as:

[0115] Among them, ω4>>ω1,ω2,ω3, and ω1, ω2 and ω3 are close.

[0116] The open-loop gain is:

[0117] The frequency domain response characteristics of the system are determined by the open-loop gain and four corner frequencies, among which the control gain K C It affects ω3 and open-loop gain, the design of spring elastic modulus K affects ω1, ω2 and open-loop gain, and the constant pressure chamber volume V0 affects ω4.

[0118] The design problem of the constant pressure valve is how to design the values ​​of the four turning frequencies so that the system meets the required steady-state and dynamic performance and has good robust performance, such as:

[0119] (1) To enhance the stability margin of the system, the turning frequency ω should be increased 1,2 , so that the phase angle curve moves upward, including: 1) reducing the valve mass M y ; 2) Increase the valve damping coefficient K f .

[0120] (2) To enhance the system's response performance, the corner frequency ω3 should be increased, or the open-loop gain K should be increased. open , so that the amplitude curve moves right and upward, including: 1) increasing the control gain K C ; 2) Reduce the spring elastic modulus K; 3) Reduce the constant pressure valve area A y .

[0121] 2. Influence of control gain on the open-loop frequency domain characteristics of the system

[0122] K C The impact on the frequency domain characteristics of the system is analyzed as follows.

[0123] Assumptions Other parameters remain unchanged, only K is changed C The Bode plot curve is as follows Figure 4 As shown. Increase K C , then ω3 increases accordingly, the open-loop gain also increases, the crossover frequency increases, and the phase margin decreases; conversely, reducing K C , then ω3 becomes smaller accordingly, the open-loop gain also decreases, the crossover frequency decreases, and the phase margin increases.

[0124] Analysis of closed-loop stability:

[0125] The characteristic polynomial of the closed-loop system is:

[0126] That is, d(s) = a0·s 3 +a1·s 2 +a2·s+a3(39)

[0127] Where: a0=1(40)

[0128]

[0129]

[0130]

[0131] According to the necessary and sufficient conditions for the stability of the third-order system: all coefficients of the characteristic equation are positive, and a1a2>a0a3, we get:

[0132] Finally, the frequency domain forming design method of constant pressure valve

[0133] In the inlet pressure disturbance variation range P in ∈[P inl ,P inh ] and variable flow area interference variation range A out2 ∈[A out2l ,A out2h ], the system needs to meet the following steady-state performance requirements and dynamic performance requirements:

[0134] Steady-state performance requirements: The steady-state error of the control chamber pressure is no greater than ΔP C , that is, the control chamber pressure design value P C0 ∈[P Cl ,P Ch ], the amplitude margin is greater than MdB, and the phase margin is greater than N degrees;

[0135] Dynamic performance requirements: adjustment time is no more than t s , the overshoot is not greater than σ.

[0136] 1. Constraints

[0137] (1) Constraint 1

[0138] According to the steady-state working principle of the main flow cavity, the steady-state flow balance equation of the controlled object can be obtained:

[0139]

[0140] Then, the inlet area opening must satisfy:

[0141] Then we get the parameter K Ain , K Pin , K Aout and KPout .

[0142] 1) According to the system stability requirements, the control gain must meet: K C <K Cmax (47)

[0143] 2) According to the requirements of the system loop open-loop transfer function L and the dynamic performance requirements of the control gain, the control gain must meet the following requirements: K C ∈[K Cl ,K Ch ](48)

[0144] (2) Constraint 2

[0145] According to the steady-state equilibrium condition of the valve motion, the valve spring compression amount in steady state is obtained:

[0146] Considering the steady-state performance requirements, that is, P C ∈[P Cl ,P Ch ], then, the range of spring compression when stable should satisfy:

[0147] When the displacement change of the designed constant pressure valve is Δx y Less than the change in spring compression Δx s0 When Δx u =-Δx y =-Δx s (51)

[0148] Then, the change in the inlet throttle opening Δx u Should be less than the designed change in spring compression Δx s0 , that is: |Δx u |≤|Δx s0 |(52)

[0149] That is, the corresponding change in the inlet throttle opening satisfies:

[0150]

[0151] Formula (47) shows that the smaller K is, the larger the range of variation of the spring compression amount, the larger the design range of the control gain, and the larger the design freedom. However, the system overshoot will increase and the adjustment time will increase.

[0152] 2. Iterative design algorithm

[0153] Iterative design algorithm: Through the above analysis, in the given constant pressure valve structure design scheme, the iterative algorithm of the frequency domain molding design of the constant pressure valve with constraints is given as follows:

[0154] Step 1. Select a constant pressure valve structure design scheme and determine the spring compression range Δx s0 ;

[0155] Step 2. According to the disturbance input P in and A out2 Select n×m steady-state points in the range of variation and calculate A at each steady-state point in , K Ain , K Pin , K Aout , K Pout The model characteristic parameters are obtained to obtain the functional relationship between the open-loop transfer function and the control gain, that is: L i =f(K C,i ),i=1,…,n×m(51)

[0156] Step 3. According to each L i Forming requirements and system stability constraints (41) and performance constraints (42) determine K C,i , i=1,…,n×m;

[0157] Step 4. According to the geometric characteristics of the inlet throttle hole ΔA in =K C ·Δx u , get the opening x u,i and inlet throttling area A i , control gain K Ci The recursive iterative equation is:

[0158]

[0159] Step 5. If the change in the inlet throttle opening is Δx u If equation (47) is satisfied, go to Step 6; otherwise, return to Step 1 and repeat the above process.

[0160] Step 6. Determine the initial parameters. Select the inlet throttle opening change close to The design point of the initial parameters is taken as the design point of the initial parameters. The hole opening at this design point is x u . Let the initial compression of the spring be x s0 , the valve displacement is Δx when stable y , then the steady-state spring compression is: x s =x s0 +Δx y (48)

[0161] Then Δx y =x s -x s0 (49)

[0162] Then, the initial opening of the valve inlet throttle hole is: x u0 =x u +Δx y (50)

[0163] The design process is complete.

[0164] At present, the constant pressure valve analysis, design and implementation method of this application has been applied to the modeling, simulation and verification of a certain aircraft engine fuel system, laying an important foundation for the design of aircraft engine fuel system and supporting the transformation and upgrading of a certain aircraft engine control system. Therefore, this application has important engineering application value and significant economic benefits in the modeling and simulation of constant pressure valves and other hydraulic systems that use this system.

[0165] Corresponding to the above method, the embodiment of the present application also provides a closed-loop control method for a constant pressure valve of an aircraft engine fuel servo, such as Figure 5 As shown, the method includes:

[0166] Step S510: The stabilization controller controls the constant pressure valve based on the pressure difference increment deviation of the reference return oil pressure increment and the constant pressure oil pressure increment output by the control device of the controlled object at the previous moment, and outputs control data for controlling the controlled object;

[0167] Step S520: The controlled object control device controls the controlled object based on the inlet pressure increment and the variable load area increment of the disturbance input and the control data, and outputs the constant pressure oil pressure increment at the current moment.

[0168] Each method step of the method provided in the above embodiment of the present application can be implemented by the functions of the above functional units. Therefore, the specific working process and beneficial effects of each method step in the method provided in the embodiment of the present application will not be repeated here.

[0169] In another embodiment provided in the present application, a computer-readable storage medium is also provided, in which instructions are stored. When the computer-readable storage medium is run on a computer, the computer executes the constant pressure valve closed-loop control method of the aircraft engine fuel servo as described in any of the above embodiments.

[0170] In another embodiment provided in the present application, a computer program product including instructions is also provided, which, when executed on a computer, enables the computer to execute the closed-loop control method of the constant pressure valve of the aircraft engine fuel servo as described in any of the above embodiments.

[0171] Those skilled in the art will appreciate that the embodiments in the present application may be provided as methods, systems, or computer program products. Therefore, the present application may adopt a complete hardware embodiment, a complete software embodiment, or a form of an embodiment combining software and hardware. Moreover, the present application may adopt a form of a computer program product implemented on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0172] The embodiments of the present application are described with reference to the flowcharts and / or block diagrams of the methods, devices (systems), and computer program products according to the embodiments of the present application. It should be understood that each process and / or box in the flowchart and / or block diagram, as well as the combination of the processes and / or boxes 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 generate 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. Figure 1 A process or multiple processes and / or boxes Figure 1 A device that provides the functions specified in a block or multiple blocks.

[0173] These computer program instructions may also be stored in a computer-readable memory capable of directing a computer or other programmable data processing device to operate in a specific manner, so that the instructions stored in the computer-readable memory produce an article of manufacture comprising an instruction device, which implements the process Figure 1 A process or multiple processes and / or boxes Figure 1 A function specified in one or more boxes.

[0174] These computer program instructions can also be loaded onto a computer or other programmable data processing device so that a series of operating steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing instructions for implementing the process. Figure 1 A process or multiple processes and / or boxes Figure 1 The steps for the functions specified in one or more boxes.

[0175] Although the preferred embodiments of the present application have been described, those skilled in the art may make additional changes and modifications to these embodiments once they have learned the basic creative concept. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments and all changes and modifications falling within the scope of the embodiments of the present application.

[0176] Obviously, those skilled in the art can make various changes and modifications to the embodiments in the present application without departing from the spirit and scope of the embodiments in the present application. Thus, if these modifications and variations of the embodiments in the present application fall within the scope of the claims and their equivalents in the embodiments of the present application, the embodiments of the present application are also intended to include these modifications and variations.

Claims

1. A closed-loop control system for a constant pressure valve of an aircraft engine fuel servo, characterized in that: The system comprises: a stabilization controller and a controlled object control device; The stabilization controller is used to calculate the constant pressure oil pressure increment ΔP0 based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output control data for controlling the controlled object; The controlled object control device is used to adjust the inlet pressure increment ΔP based on the disturbance input. in and variable load area increment ΔA out2 , and the control data, control the controlled object, and output the constant pressure oil pressure increment ΔP at the current moment C ; The control data includes the flow area increment ΔA of the inlet throttle hole in And the constant pressure valve movement speed increment Wherein, the stabilization controller includes a constant pressure valve dynamic characteristic unit and a gain unit; The constant pressure valve dynamic characteristic unit is based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output the displacement increment Δx of the constant pressure valve y And the constant pressure valve movement speed increment The gain unit increases the displacement increment Δx of the constant pressure valve movement y Perform gain control and output the inlet throttle flow area increment ΔA in .

2. The system according to claim 1, characterized in that The gain control law of the stabilization controller is determined by the flow area A of the inlet throttle hole of the constant pressure valve. in and the inlet throttle opening x u The design function is A in =f in (x u ), and its deviation is expressed as ΔA in =-K C ·Δx y , where the inlet throttle opening increment Δx u The negative displacement increment of the constant pressure valve Δx y equal to the control gain of the stabilizing controller 3. The system according to claim 1, characterized in that The constant pressure valve closed-loop control system also includes a frequency domain analysis unit; The frequency domain analysis unit is used to obtain the open-loop transfer function of the constant pressure valve closed-loop control system based on the acquired state space model of the stabilization controller and the controlled object control device; the open-loop transfer function includes 3 poles, 1 zero point and an open-loop gain; Based on the control gain K of the stabilization controller C , the open-loop gain of the constant pressure valve closed-loop control system and the turning frequency ω3 of the frequency domain curve corresponding to the zero point in the open-loop transfer function are controlled.

4. The system according to claim 3, characterized in that The frequency domain analysis unit is further used for: If detected Based on the spring elastic modulus K, the open-loop gain of the constant pressure valve closed-loop control system, the turning frequency ω1 and the turning frequency ω2 of the frequency domain curve corresponding to the first pole and the second pole in the open-loop transfer function are controlled; wherein, K f is the viscous friction coefficient, M y is the moving mass of the constant pressure valve.

5. The system according to claim 4, characterized in that The frequency domain analysis unit is further used for: If detected Based on the volume V0 of the constant pressure chamber, the magnitude of the turning frequency ω4 of the frequency domain curve corresponding to the third pole in the open-loop transfer function of the constant pressure valve closed-loop control system is controlled.

6. A closed-loop control system method for a constant pressure valve of an aircraft engine fuel servo, characterized in that: Applied to the system of claims 1-5, the method comprises: The stabilization controller is based on the reference return oil pressure increment ΔP0 and the constant pressure oil pressure increment ΔP output by the controlled object control device at the previous moment. C The pressure difference increment deviation of the constant pressure valve e u , control the constant pressure valve and output control data for controlling the controlled object; The inlet pressure increment ΔP of the controlled object control device based on the disturbance input in and variable load area increment ΔA out2 , and the control data, control the controlled object, and output the constant pressure oil pressure increment ΔP at the current moment C .

7. A computer-readable storage medium, characterized in that: The computer-readable storage medium stores a computer program, and when the computer program is executed by a processor, the method steps described in claim 6 are implemented.

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