Electro-hydraulic servo control type anti-icing and anti-surge valve and control method

Abstract

This invention belongs to the field of fluid control technology, and specifically relates to an electro-hydraulic servo-controlled anti-icing and anti-surge valve and its control method. The anti-icing and anti-surge valve includes an air passage housing and a piston component. The air passage housing contains a piston chamber, and an electro-hydraulic servo-controlled actuator for driving the piston component is mounted on the air passage housing. An exhaust pipe is located on the outer side of the air passage housing corresponding to the piston chamber. Anti-surge vents and anti-icing vents are located on the air passage housing corresponding to the piston chamber wall. Along the direction of piston component movement, the anti-icing and anti-surge valve has a first stroke position, a second stroke position, and a third stroke position. The electro-hydraulic servo-controlled anti-icing and anti-surge valve and its control method of this invention have the advantage of high system integration. By integrating anti-icing and anti-surge functions into a single valve, the number of independent components in the system is reduced, achieving a simplified valve structure and integrated design.

Description

Technical Field

[0001] This invention belongs to the field of aero-engine fluid control technology, and in particular relates to an electro-hydraulic servo-controlled anti-icing and anti-surge valve and its control method. Background Technology

[0002] When aero-engines operate in low-temperature, high-humidity environments, the air intake is prone to icing, leading to airflow distortion and subsequently compressor surge, seriously threatening flight safety. Traditional anti-icing valves mostly employ mechanical or pneumatic control, which suffers from the following problems: low control precision: mechanical valves rely on springs and diaphragms for actuation, resulting in sluggish response and difficulty in precisely adjusting the opening; limited functionality: existing valves are only designed for anti-icing or anti-surge, lacking sufficient coordinated control capabilities; poor reliability: they are prone to jamming due to mechanical wear under complex operating conditions. In recent years, electro-hydraulic servo technology has been introduced into the field of fluid control due to its high dynamic characteristics, but existing solutions mostly focus on single functions (such as anti-icing) and lack closed-loop feedback mechanisms, making it difficult to meet the dual requirements of aero-engines for rapid response and high precision. Summary of the Invention

[0003] In view of this, the present invention aims to provide an electro-hydraulic servo-controlled anti-icing and anti-surge valve and its control method to solve the above-mentioned technical problems.

[0004] To achieve the above objectives, the technical solution of the present invention is implemented as follows:

[0005] In a first aspect, the present invention provides an electro-hydraulic servo-controlled anti-icing and anti-surge valve, the anti-icing and anti-surge valve comprising an air passage housing and a piston component, wherein the air passage housing has a piston chamber, the piston component is located in the piston chamber, the air passage housing is provided with an electro-hydraulic servo-controlled actuator for driving the piston component to move, an exhaust pipe is provided on the outer side of the air passage housing corresponding to the position of the piston chamber, and anti-surge air holes and anti-icing air holes are provided on the air passage housing corresponding to the position of the piston chamber wall; the outer peripheral wall of the piston component cooperates with the cavity wall of the piston chamber, and along the moving direction of the piston component, the anti-icing and anti-surge valve has a first stroke position, a second stroke position, and a third stroke position. Position; when the piston is in the first stroke position, the piston chamber and the exhaust pipe are not connected; during the process of the piston moving from the first stroke position to the second stroke position, the piston chamber and the exhaust pipe are connected through the anti-icing vent, and the gas flow rate in the anti-icing vent gradually increases; during the process of the piston moving from the second stroke position to the third stroke position, the piston chamber and the exhaust pipe are also connected through the anti-surge vent, and the gas flow rate in both the anti-surge vent and the anti-icing vent gradually increases; when the piston is in the third stroke position, the gas flow rate in both the anti-surge vent and the anti-icing vent reaches its maximum.

[0006] Furthermore, the anti-icing and anti-surge valve also includes a guide cylinder, one end of which extends into the piston cavity and communicates with the piston cavity, and the other end is disposed on the air passage housing. The length direction of the guide cylinder is the same as the movement direction of the piston component, and the piston component is provided with a guide rod that slides with the guide cylinder.

[0007] Furthermore, the guide rod is provided with an air-receiving hole, which is connected to the guide cylinder.

[0008] Furthermore, the anti-icing and anti-surge valve also includes a fairing, which has a receiving cavity for accommodating the guide rod. One end of the fairing is disposed on the piston member, and the other end has a receiving port that cooperates with the guide cylinder. The receiving port communicates with the receiving cavity.

[0009] Furthermore, the fairing has a horn-shaped structure, with the large-diameter end of the fairing disposed on the piston component and the small-diameter end facing the guide cylinder.

[0010] Furthermore, both the end of the piston and the fairing are provided with weight-reducing vents.

[0011] Furthermore, the electro-hydraulic servo-controlled actuator includes an oil circuit housing, on which a hydraulic cylinder and an electro-hydraulic servo valve are provided. The piston rod of the hydraulic cylinder is connected to the piston component, and the electro-hydraulic servo valve is used to receive a drive current signal and drive the piston rod of the hydraulic cylinder to move according to the drive current signal.

[0012] Furthermore, the electro-hydraulic servo-controlled actuator also includes a controller and a displacement sensor. The displacement sensor is used to detect the movement position of the piston rod in real time and generate a feedback signal to feed back to the controller. The controller corrects the drive current signal according to the feedback signal and sends the corrected drive current signal to the electro-hydraulic servo valve.

[0013] Furthermore, the gas circuit housing and the oil circuit housing are connected by a connecting housing, the connecting housing is provided with a guide hole that slides with the piston rod, and a sealing element is provided between the connecting housing and the gas circuit housing.

[0014] Secondly, the present invention provides an electro-hydraulic servo-controlled anti-icing and anti-surge valve control method, comprising:

[0015] The controller receives sensor signals from the engine, compares them with the valve target opening mapping table, and then outputs a drive current signal.

[0016] The electro-hydraulic servo valve receives the drive current signal and drives the piston rod of the hydraulic cylinder to move according to the drive current signal, so that the piston rod drives the piston component to move, thereby changing the valve opening.

[0017] The displacement sensor is used to detect the movement position of the piston rod in real time and generate a feedback signal to feed back to the controller;

[0018] The PID module in the controller is used to correct the drive current signal to obtain the corrected drive current signal;

[0019] The electro-hydraulic servo valve receives the corrected drive current signal and drives the piston rod of the hydraulic cylinder to move according to the corrected drive current signal, so that the piston rod drives the piston component to move, thereby correcting the valve opening.

[0020] Compared with existing technologies, the electro-hydraulic servo-controlled anti-icing and anti-surge valve and control method described in this invention have the following advantages:

[0021] (1) The electro-hydraulic servo-controlled anti-icing and anti-surge valve and control method described in this invention have the advantage of high system integration. By integrating the anti-icing and anti-surge functions into a single valve, the number of independent components in the system is reduced, achieving a simplified valve structure and integrated design. This helps to reduce the overall weight and space occupied by the valve, and improves the application prospects of this valve in weight-sensitive fields such as aero-engines. In addition, the electro-hydraulic servo-controlled actuator in this embodiment only consumes energy during adjustment and has zero power consumption during the static holding phase, resulting in reduced overall energy consumption. The piston components adopt a modular design, supporting quick replacement, long maintenance cycle, and low maintenance cost.

[0022] (2) The electro-hydraulic servo-controlled anti-icing and anti-surge valve and control method described in this invention achieves high-precision valve adjustment and dual-function dynamic optimization through closed-loop feedback mechanism and outlet collaborative design, meets the performance requirements of aero-engine under harsh operating conditions, and solves the problems of large size, low control accuracy, single function and insufficient reliability of traditional anti-icing or anti-surge valves. Attached Figure Description

[0023] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0024] Figure 1 This is a schematic diagram of the structure of an electro-hydraulic servo-controlled anti-icing and anti-surge valve according to Embodiment 1 of the present invention;

[0025] Figure 2 This is a schematic diagram illustrating the working principle of an electro-hydraulic servo-controlled anti-icing and anti-surge valve according to Embodiment 1 of the present invention.

[0026] Figure 3 This is a flowchart of an electro-hydraulic servo-controlled anti-icing and anti-surge valve control method according to Embodiment 2 of the present invention.

[0027] Explanation of reference numerals in the attached figures:

[0028] 1. Air circuit housing; 2. Piston component; 3. Oil circuit housing; 4. Hydraulic cylinder; 5. Electro-hydraulic servo valve; 6. Controller; 7. Displacement sensor; 8. Anti-icing vent; 9. Anti-surge vent; 10. Piston chamber; 11. Exhaust pipe; 12. Guide cylinder; 13. Guide rod; 14. Air intake port; 15. Fairing; 16. Weight reduction vent; 17. Connecting housing; 18. Seal; 19. Graphite ring; 20. Locking nut; 21. Piston rod. Detailed Implementation

[0029] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, and not all of the structures.

[0030] Example 1

[0031] Figure 1 This is a schematic diagram of the structure of an electro-hydraulic servo-controlled anti-icing and anti-surge valve according to Embodiment 1 of the present invention. See also... Figure 1 The anti-icing and anti-surge valve includes an air passage housing 1 and a piston component 2. The air passage housing 1 has a piston chamber 10 inside, and the piston component 2 is located in the piston chamber 10. The air passage housing 1 is provided with an electro-hydraulic servo-controlled actuator for driving the piston component 2 to move. An exhaust pipe 11 is provided on the outside of the air passage housing 1 at a position corresponding to the piston chamber 10. Anti-surge air hole 9 and anti-icing air hole 8 are provided on the air passage housing 1 at positions corresponding to the cavity wall of the piston chamber 10.

[0032] Specifically, the outer peripheral wall of piston 2 cooperates with the cavity wall of piston chamber 10. Along the moving direction of piston 2, the anti-icing and anti-surge valve has a first stroke position, a second stroke position, and a third stroke position. During the movement of piston 2, piston 2 can block anti-surge vent 9 and anti-icing vent 8, and the length direction of anti-surge vent 9 and anti-icing vent 8 is the same as the movement of piston 2. This allows piston 2 to change the opening area of ​​anti-surge vent 9 and anti-icing vent 8 during the movement of piston 2, thereby regulating the gas flow rate through anti-surge vent 9 and anti-icing vent 8.

[0033] When piston 2 is in the first stroke position, piston chamber 10 and exhaust pipe 11 are not connected. During the process of piston 2 moving from the first stroke position to the second stroke position, piston chamber 10 and exhaust pipe 11 are connected through anti-icing vent 8, and the gas flow rate in anti-icing vent 8 gradually increases. During the process of piston 2 moving from the second stroke position to the third stroke position, piston chamber 10 and exhaust pipe 11 are also connected through anti-surge vent 9, and the gas flow rate in both anti-surge vent 9 and anti-icing vent 8 gradually increases. When piston 2 is in the third stroke position, the gas flow rate in both anti-surge vent 9 and anti-icing vent 8 reaches its maximum.

[0034] Figure 2 This is a schematic diagram illustrating the working principle of an electro-hydraulic servo-controlled anti-icing and anti-surge valve according to Embodiment 1 of the present invention. See also... Figure 1 and Figure 2 Along the moving direction of piston 2, the first stroke position is point a in the figure, the second stroke position is point b in the figure, and the third stroke position is point c in the figure. Gas enters piston chamber 10 from the direction of the arrow in the figure. When the electro-hydraulic servo-controlled actuator drives piston 2 to move, by changing the stroke position of piston 2, when the end wall of piston 2 is in the first stroke position, the outer peripheral wall of piston 2 can completely block the openings of anti-icing vent 8 and anti-surge vent 9. At this time, piston chamber 10 is not connected to exhaust pipe 11, so that the valve is in the fully closed state.

[0035] Correspondingly, when the electro-hydraulic servo-controlled actuator drives the piston 2 to move, causing the end wall of the piston 2 to move from the first stroke position to the second stroke position, as the area of ​​the outer peripheral wall of the piston 2 that can block the opening of the anti-icing vent 8 gradually decreases, the gas flow rate entering the anti-icing vent 8 through the opening of the anti-icing vent 8 gradually increases. At this time, the valve enters the anti-icing working mode, and the high-temperature and high-pressure gas enters the piston chamber 10, flows through the anti-icing vent 8, and is discharged from the exhaust pipe 11.

[0036] When the electro-hydraulic servo-controlled actuator drives the piston 2 to move, causing the end wall of the piston 2 to move from the second stroke position to the third stroke position, the piston chamber 10 and the exhaust pipe 11 are also connected through the anti-surge hole 9. As the area of ​​the outer peripheral wall of the piston 2 that can block the opening of the anti-surge hole 9 gradually decreases, the gas flow rate entering the anti-surge hole 9 through the opening of the anti-surge hole 9 gradually increases, and the gas flow rate in the anti-icing hole 8 also gradually increases. At this time, the valve enters the anti-icing and anti-surge working mode. High-temperature and high-pressure gas enters the piston chamber 10, flows through the anti-icing hole 8 and the anti-surge hole 9, and is discharged from the exhaust pipe 11.

[0037] When the piston 2 is in the third stroke position, the outer peripheral wall of the piston 2 no longer blocks the opening of the anti-surge vent 9 and the anti-icing vent 8. The anti-icing vent 8 and the anti-surge vent 9 are in a fully open state, and the gas flow rate in the anti-surge vent 9 and the anti-icing vent 8 reaches its maximum.

[0038] Using the above-described configuration, the anti-icing vent 8 and anti-surge vent 9 are mounted on the gas path housing 1. The gas flow rate within these vents is controlled by the movement of the piston 2. This achieves structural integration and simplification of the valve system, integrating anti-icing and anti-surge functions into a single valve. This reduces the number of independent components in the valve system, and the integrated design lowers the overall weight and space occupied by the valve, which is particularly important for weight-sensitive applications such as aero-engines. Furthermore, this electro-hydraulic servo-controlled anti-icing and anti-surge valve exhibits high control efficiency, with more efficient linkage control between anti-icing and anti-surge. In anti-icing mode, it can automatically adjust the anti-surge logic to avoid surge risks caused by icing. The integrated control system shortens the signal transmission path, improving the valve's response speed to changes in engine operating conditions.

[0039] In a preferred embodiment of this invention, the anti-icing and anti-surge valve further includes a guide cylinder 12. One end of the guide cylinder 12 extends into the piston chamber 10 and communicates with the piston chamber 10, while the other end is disposed on the air passage housing 1. The length direction of the guide cylinder 12 is the same as the movement direction of the piston component 2. The piston component 2 is provided with a guide rod 13 that slides with the guide cylinder 12. The guide cylinder 12 can be fixed to the air passage housing 1 by welding or other methods, and the guide rod 13 can be installed and fixed to the end wall of the piston component 2 by screws or other methods. It should be understood that the guide cylinder 12 and the air passage housing 1, and the guide rod 13 and the piston component 2 can also be connected by integral molding, bonding, threaded connection, or other methods, which will not be elaborated here.

[0040] Optionally, a self-lubricating component such as a graphite ring 19 is installed at one end of the guide rod 13 that extends into the guide cylinder 12, thereby reducing wear between the guide rod 13 and the guide cylinder 12. By utilizing the cooperation between the guide rod 13 and the guide cylinder 12, the piston 2 can not only maintain stable movement under the guidance of the piston chamber 10, but also move stably under the guidance of the guide rod 13, providing a redundant guiding structure for the movement of the piston 2, which can significantly reduce the probability of the piston 2 jamming or seizing during movement.

[0041] Optionally, the guide rod 13 is provided with a gas-receiving hole 14, which communicates with the guide cylinder 12. The gas-receiving hole 14 on the guide rod 13 can be used to contain gas. The length direction of the gas-receiving hole 14 is the same as the length direction of the guide rod 13. During the process of the guide rod 13 extending into the guide cylinder 12, the guide rod 13 will compress the gas in the guide cylinder 12. The gas in the guide cylinder 12 can not only be discharged through the fitting gap between the inner side wall of the guide cylinder 12 and the outer side wall of the guide rod 13, but can also be stored in the gas-receiving hole 14. This helps to reduce the resistance to the movement of the guide rod 13, thereby reducing the influence of the guide rod 13 on the movement accuracy of the piston 2, and helping to improve the opening control accuracy of this valve.

[0042] In a preferred embodiment of this invention, the anti-icing and anti-surge valve further includes a fairing 15. The fairing 15 has a receiving cavity for accommodating the guide rod 13. One end of the fairing 15 is mounted on the piston member 2, and the other end has a receiving port that mates with the guide cylinder 12, communicating with the receiving cavity. The fairing 15 can be installed on the end wall of the piston member 2 by means of screws or other methods. It should be understood that the fairing 15 can also be fixed to the end wall of the piston member 2 by welding, bonding, integral molding, or other methods, which will not be elaborated here.

[0043] Using the above configuration, the shroud 15 can effectively rectify the gas entering the piston chamber 10, preventing the gas from accumulating at the end wall of the piston 2, and guiding the gas to move towards the wall of the piston chamber 10, so that the gas can smoothly enter the anti-icing vent 8 and the anti-surge vent 9.

[0044] Optionally, the fairing 15 has a horn-shaped structure, with the large-diameter end of the fairing 15 positioned on the piston 2 and the small-diameter end facing the guide cylinder 12. Compared to other structures, the horn-shaped fairing 15 has lower outer peripheral wall resistance, which can better guide the gas to the anti-icing vent 8 and the anti-surge vent 9, avoiding gas flow blockage and improving gas flow efficiency.

[0045] In a preferred embodiment of this invention, both the end of the piston 2 and the fairing 15 are provided with weight-reducing vent holes 16. By providing weight-reducing vent holes 16 at the end of the piston 2, gas can pass through the end of the piston 2, thereby maintaining a balance of gas pressure on both sides of the piston 2 during its movement. This prevents the piston 2 from jamming due to pressure differences on both sides during movement, and further improves the movement accuracy of the piston 2. In addition, the weight-reducing vent holes 16 also help reduce the mass of the piston 2 and the fairing 15, contributing to a reduction in the overall mass of the valve and achieving a lightweight design.

[0046] In a preferred embodiment of this invention, the electro-hydraulic servo-controlled actuator includes an oil circuit housing 3, on which a hydraulic cylinder 4 and an electro-hydraulic servo valve 5 are mounted. The piston rod 21 of the hydraulic cylinder 4 is connected to the piston component 2. The electro-hydraulic servo valve 5 receives a drive current signal and drives the piston rod 21 of the hydraulic cylinder 4 to move according to the drive current signal. The electro-hydraulic servo valve 5 has a dual-channel structure, thereby achieving mechanical and electrical redundancy, significantly improving the safety of this valve operation under complex conditions in aero-engines.

[0047] For example, both the hydraulic cylinder 4 and the electro-hydraulic servo valve 5 can be mounted on the oil circuit housing 3 by means of screws or other methods. The piston rod 21 has external threads, and the piston component 2 has a mounting hole that mates with the piston rod 21. A locking nut 20 is provided at one end of the piston rod 21 that passes through the mounting hole. A removable adjusting washer can also be installed between the locking nut 20 and the end wall of the piston component 2, with one end of the adjusting washer pressing against the locking nut 20 and the other end pressing against the end wall of the piston component 2.

[0048] It should be understood that the hydraulic cylinder 4 and the electro-hydraulic servo valve 5 can also be installed on the oil circuit housing 3 in other ways. The piston rod 21 and the piston part 2 can also be connected by thread, screw or other means to achieve a stable connection between the piston rod 21 and the piston part 2, so as to ensure that the piston rod 21 can drive the piston part 2 to move with high precision.

[0049] Optionally, the electro-hydraulic servo-controlled actuator also includes a controller 6 and a displacement sensor 7. The displacement sensor 7 is used to detect the movement position of the piston rod 21 in real time and generate a feedback signal to the controller 6. The controller 6 corrects the drive current signal based on the feedback signal and sends the corrected drive current signal to the electro-hydraulic servo valve 5. The displacement sensor 7 can also be a dual-channel structure. It should be noted that both the controller 6 and the displacement sensor 7 can be selected and configured as needed. The controller 6 can be installed on the oil circuit housing 3, or it can be installed elsewhere, and signal transmission between the controller 6 and the displacement sensor 7, and between the controller 6 and the electro-hydraulic servo valve 5, can be achieved through wired or wireless transmission.

[0050] For example, the displacement sensor 7 can be an LVDT linear displacement sensor 7, which can be installed inside the piston rod 21 assembly of the hydraulic cylinder 4, and can continuously feed back the position signal of the piston 2 in the valve to the controller 6. The LVDT linear displacement sensor 7 is based on the principle of a differential solenoid transformer, and its main structure consists of an iron core, a primary coil, and two secondary coils arranged symmetrically and connected in series with opposite electromotive forces. For example, the primary and secondary coils of the LVDT linear displacement sensor 7 are respectively fixed to the oil circuit housing 3 and the end of the piston rod 21 assembly inside the hydraulic cylinder 4, thereby detecting the movement position of the piston rod 21 in the hydraulic cylinder 4 in real time.

[0051] According to the transformer principle, when an AC signal E1 is provided to the primary coil, an alternating magnetic field is generated inside it. This alternating magnetic field induces electromotive forces E21 and E22 in the secondary coils. When the iron core is in the middle position of the two secondary coils, the two coils generate induced electromotive forces of equal magnitude but opposite direction, resulting in an output voltage E0. When the iron core deviates from the middle position, the mutual inductance between the two coils changes, and their induced electromotive forces increase and decrease, no longer being equal, resulting in a voltage signal output. This voltage signal has a linear relationship with the position of the iron core within a certain range, thus achieving the purpose of converting the position of the iron core into an electrical signal output.

[0052] It should be understood that other types of displacement sensors can also be used for displacement sensor 7. Those skilled in the art can select appropriate displacement sensors and their installation methods according to actual needs, as long as they can achieve real-time monitoring of the movement position of piston rod 21 of hydraulic cylinder 4. This will not be elaborated here.

[0053] Using the above setup, controller 6 can receive engine status parameters, generate a valve target opening command based on engine requirements, and output a signal that is then converted into a drive current by a power amplification module. The drive current is then input to electro-hydraulic servo valve 5, causing the piston rod 21 of the hydraulic cylinder 4 of electro-hydraulic servo valve 5 to move to the corresponding position. The PID control algorithm dynamically calculates the drive current of electro-hydraulic servo valve 5 based on the deviation between the actual opening and the target opening fed back by displacement sensor 7, thereby correcting the movement position of piston 2. Electro-hydraulic servo valve 5 is a high-frequency response servo valve. After receiving the signal from controller 6, it converts the controller 6's current signal into hydraulic force to drive the piston assembly to move linearly. Displacement sensor 7 is a linear differential transformer displacement sensor that monitors piston displacement accurately in real time and feeds back an analog voltage signal to controller 6.

[0054] Optionally, the gas passage housing 1 and the oil passage housing 3 are connected by a connecting housing 17. The connecting housing 17 has a guide hole that slides with the piston rod 21, and a sealing element 18 is provided between the connecting housing 17 and the gas passage housing 1. For example, the gas passage housing 1 and the oil passage housing 3 can be connected by bolts or other means, and the sealing element 18 can be a sealing ring. By using the connecting housing 17 to connect the oil passage housing 3 and the gas passage housing 1, and providing a sealing element 18 between the gas passage housing 1 and the oil passage housing 3, gas waste caused by gas leakage can be reduced.

[0055] In practical applications, a self-lubricating component such as a graphite ring 19 that mates with the piston rod 21 can also be installed on the connecting housing 17 at the position corresponding to the guide hole. This reduces friction between the piston rod 21 and the inner wall of the guide hole, ensuring that the guide hole can continuously and stably guide the piston rod 21 effectively and preventing jamming between the outer peripheral wall of the piston rod 21 and the inner wall of the guide hole due to friction. Thus, during the movement of the piston component 2 driven by the piston rod 21, both sides of the piston component 2 can remain stable under the guidance of the piston rod 21 and the guide rod 13, further improving the reliability of the piston component 2's movement.

[0056] The electro-hydraulic servo-controlled anti-icing and anti-surge valve described in this embodiment has the advantage of high system integration. By integrating anti-icing and anti-surge functions into a single valve, the number of independent components in the system is reduced, achieving a simplified valve structure and integrated design. This helps reduce the overall weight and space occupied by the valve, improving its application prospects in weight-sensitive fields such as aero-engines. Furthermore, the electro-hydraulic servo-controlled actuator in this embodiment only consumes energy during adjustment, with zero power consumption during the static holding phase, resulting in reduced overall energy consumption. The piston components adopt a modular design, supporting rapid replacement, long maintenance cycles, and low maintenance costs.

[0057] Example 2

[0058] Figure 3 This is a flowchart of an electro-hydraulic servo-controlled anti-icing and anti-surge valve control method according to Embodiment 2 of the present invention. See also... Figure 3 This embodiment is based on the above embodiment. Specifically, this electro-hydraulic servo-controlled anti-icing and anti-surge valve control method includes the following steps:

[0059] Step 101: Receive sensor signals from the engine using the controller, compare them with the valve target opening mapping table, and output the drive current signal.

[0060] In practical applications, the controller can receive the filtered and digitized sensor signals, compare them with the target opening mapping table, and output a PWM signal, which is then converted into the drive current signal of the electro-hydraulic servo valve by the power amplifier module.

[0061] Optionally, an anti-icing outlet and an anti-surge outlet can be integrated into the gas path housing, and the internal flow channel layout of the gas path housing can be strictly designed so that when the piston moves to different positions, the specific flow channel layout can proportionally distribute the gas entering the piston chamber to the anti-icing air hole and the anti-surge air hole. The piston position and gas flow matching data are stored in the controller to obtain the valve target opening mapping table.

[0062] Step 102: Receive the drive current signal using the electro-hydraulic servo valve, and drive the piston rod of the hydraulic cylinder to move according to the drive current signal, so that the piston rod drives the piston parts to move, thereby changing the valve opening.

[0063] Step 103: Use a displacement sensor to detect the movement position of the piston rod in real time and generate a feedback signal to feed back to the controller.

[0064] Step 104: Use the PID module in the controller to correct the drive current signal to obtain the corrected drive current signal.

[0065] Optionally, the controller also includes a fault diagnosis module, which can be used to continuously monitor the health status of the valve system in order to monitor the operation of the entire valve system.

[0066] Step 105: Receive the corrected drive current signal using the electro-hydraulic servo valve, and drive the piston rod of the hydraulic cylinder to move according to the corrected drive current signal, so that the piston rod drives the piston parts to move, thereby correcting the valve opening.

[0067] The electro-hydraulic servo-controlled anti-icing and anti-surge valve control method described in this embodiment achieves high-precision valve adjustment and dual-function dynamic optimization through a closed-loop feedback mechanism and output collaborative design, meeting the performance requirements of aero-engines under harsh operating conditions and solving the problems of large size, low control accuracy, single function and insufficient reliability of traditional anti-icing or anti-surge valves.

[0068] Note that the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention, the scope of which is determined by the scope of the appended claims.

Claims

1. An electro-hydraulically servo-controlled ice and surge prevention valve, characterized by: The anti-icing and anti-surge valve includes an air passage housing (1) and a piston (2). The air passage housing (1) contains a piston chamber (10), and the piston (2) is located within the piston chamber (10). The air passage housing (1) is equipped with an electro-hydraulic servo-controlled actuator for driving the piston (2) to move. An exhaust pipe (11) is located on the outer side of the air passage housing (1) corresponding to the position of the piston chamber (10). Anti-surge air holes (9) and anti-icing air holes (8) are located on the air passage housing (1) corresponding to the position of the piston chamber (10). The outer peripheral wall of the piston (2) cooperates with the cavity wall of the piston chamber (10). Along the moving direction of the piston (2), the anti-icing and anti-surge valve... There are three stroke positions: a first stroke position, a second stroke position, and a third stroke position. When the piston (2) is in the first stroke position, the piston chamber (10) and the exhaust pipe (11) are not connected. During the process of the piston (2) moving from the first stroke position to the second stroke position, the piston chamber (10) and the exhaust pipe (11) are connected through the anti-icing vent (8), and the gas flow rate in the anti-icing vent (8) gradually increases. During the process of the piston (2) moving from the second stroke position to the third stroke position, the piston chamber (10) and the exhaust pipe (11) are also connected through the anti-surge vent (9), and the anti-surge vent (9) and the anti-icing vent... The gas flow rate in the hole (8) gradually increases; when the piston (2) is in the third stroke position, the gas flow rate in the anti-surge hole (9) and the anti-icing hole (8) reaches the maximum; the anti-icing and anti-surge valve also includes a guide cylinder (12), one end of the guide cylinder (12) extends into the piston cavity (10) and communicates with the piston cavity (10), and the other end is set on the air passage housing (1), the length direction of the guide cylinder (12) is the same as the moving direction of the piston (2), and the piston (2) is provided with a guide rod (13) that slides with the guide cylinder (12); the electro-hydraulic servo control drive includes an oil passage housing (3), the oil passage housing ( 3) The device is equipped with a hydraulic cylinder (4) and an electro-hydraulic servo valve (5). The piston rod of the hydraulic cylinder (4) is connected to the piston (2). The electro-hydraulic servo valve (5) is used to receive the drive current signal and drive the piston rod (21) of the hydraulic cylinder (4) to move according to the drive current signal. The electro-hydraulic servo control drive also includes a controller (6) and a displacement sensor (7). The displacement sensor (7) is used to detect the moving position of the piston rod (21) in real time and generate a feedback signal to feed back to the controller (6). The controller (6) corrects the drive current signal according to the feedback signal and sends the corrected drive current signal to the electro-hydraulic servo valve (5).

2. An electro-hydraulically servo-controlled anti-icing and anti-surge valve according to claim 1, characterized in that: The guide rod (13) is provided with an air-receiving hole (14), which is connected to the guide cylinder (12).

3. The electro-hydraulic servo-controlled anti-icing and anti-surge valve according to claim 1, characterized in that: The anti-icing and anti-surge valve also includes a fairing (15), which has a cavity for accommodating the guide rod (13). One end of the fairing (15) is mounted on the piston (2), and the other end has a receiving port that cooperates with the guide cylinder (12). The receiving port communicates with the cavity.

4. The electro-hydraulic servo-controlled anti-icing and anti-surge valve according to claim 3, characterized in that: The fairing (15) has a horn-shaped structure. The large-diameter end of the fairing (15) is disposed on the piston (2), and the small-diameter end is disposed towards the guide cylinder (12).

5. The electro-hydraulic servo-controlled anti-icing and anti-surge valve according to claim 3, characterized in that: The piston (2) and the fairing (15) are both provided with weight-reducing vents (16).

6. The electro-hydraulic servo-controlled anti-icing and anti-surge valve according to claim 1, characterized in that: The gas passage housing (1) and the oil passage housing (3) are connected by a connecting housing (17). The connecting housing (17) is provided with a guide hole that slides with the piston rod (21). A sealing element (18) is provided between the connecting housing (17) and the gas passage housing (1).

7. A control method for an electro-hydraulic servo-controlled anti-icing and anti-surge valve according to any one of claims 1-6, characterized in that, include: The controller receives sensor signals from the engine, compares them with the valve target opening mapping table, and then outputs a drive current signal. The electro-hydraulic servo valve receives the drive current signal and drives the piston rod of the hydraulic cylinder to move according to the drive current signal, so that the piston rod drives the piston component to move, thereby changing the valve opening. The displacement sensor is used to detect the movement position of the piston rod in real time and generate a feedback signal to feed back to the controller; The drive current signal is corrected using the PID module in the controller to obtain the corrected drive current signal; The electro-hydraulic servo valve receives the corrected drive current signal and drives the piston rod of the hydraulic cylinder to move according to the corrected drive current signal, so that the piston rod drives the piston component to move, thereby correcting the valve opening.

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