Hydraulic control system and method, application

Abstract

The application discloses a hydraulic control system and method and application, the system comprises, the variable control module and the controller, wherein, the variable control module is used for dynamic closed loop control of the oil pressure, the controller is used for controlling the variable control module. The hydraulic control system can realize pressure dynamic closed loop control, the regulation precision is high, and the valve response time is all within 50ms, the whole system responds quickly, can realize the control of different oil filling processes, and the oil in the clutch actuating cavity can be quickly discharged through the reversing valve, so that the engagement and disengagement control of the friction clutch is well realized.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of helicopter transmission system, and in particular to a hydraulic control system and method and application. BACKGROUND

[0002] At present, the research on helicopter rotor variable speed is still in the initial stage in China, and the control research on the multi-plate wet friction clutch for aviation has not been carried out. The control methods of the multi-plate wet friction clutch mainly include electromagnetic control, hydraulic control and pneumatic control. For the friction clutch of the variable speed transmission system, the hydraulic control is the most appropriate. When the friction clutch is engaged, the hydraulic control system needs to quickly fill the target pressure of the oil to the friction clutch actuating cavity and drive the piston; when the friction clutch is disengaged, the hydraulic control system needs to quickly discharge the oil in the friction clutch actuating cavity. However, the complete hydraulic control system scheme and product have not been formed in the research on the variable speed transmission system in China. At present, the simple oil pump is mainly used for pressure boosting, and a single pressure regulating valve is used for open-loop control of the oil pressure entering the friction clutch actuating cavity, so as to realize the engagement and disengagement of the friction clutch.

[0003] The engagement and disengagement of the friction clutch are realized only by the oil pump and the pressure regulating valve, and the control precision and pressure regulating response speed are very limited. The closed-loop control and dynamic regulation of the oil pressure cannot be realized, and the oil in the friction clutch actuating cavity cannot be quickly discharged when the pressure is released. The prior art cannot meet the control requirements of the variable speed transmission system and has no practicality. SUMMARY

[0004] The present application aims to provide a hydraulic control system and method and application. The technical problem to be solved by the present application is to realize the variable speed output of the helicopter rotor by using the multi-plate wet friction clutch in the variable speed transmission system. In order to ensure the rapidity, stability and reliability of the helicopter rotor variable speed process, a control system needs to be developed to realize the engagement and disengagement control of the friction clutch, and to support the ground test verification and improve the technical maturity of the variable speed transmission unit.

[0005] To achieve the above-mentioned purpose, the present application provides the following technical scheme:

[0006] A hydraulic control system, the system comprises a variable speed control module and a controller, wherein,

[0007] The variable speed control module is used for dynamically closed-loop controlling the oil pressure.

[0008] The controller is used for controlling the variable speed control module.

[0009] Further, the system further comprises a first pressure sensor, a temperature sensor and a flowmeter, wherein,

[0010] The first pressure sensor is used to measure the oil pressure into the clutch actuating chamber, providing feedback for the closed-loop control of the oil pressure.

[0011] The temperature sensor is used to measure the oil temperature into the clutch actuating chamber, providing the basis for the temperature correction of the system.

[0012] The flow meter is used to measure the oil flow into the clutch actuating chamber, providing feedback for the closed-loop control of the flow.

[0013] Further, the transmission control module includes an electric oil pump, a second pressure sensor, a pipeline, and a control valve integrated assembly, wherein,

[0014] The electric oil pump is connected to the control valve integrated assembly through the pipeline.

[0015] The second pressure sensor is used to measure the system pressure in the reversing valve opening chamber, providing feedback for the pressure stabilization control before the system acts.

[0016] The electric oil pump is used to pressurize the low-pressure oil from the oil tank.

[0017] Further, the electric oil pump includes a safety valve, which is integrated inside the electric oil pump; the safety valve is used to ensure that the system oil pressure does not exceed the predetermined limit.

[0018] Further, the control valve integrated assembly includes a speed regulating valve, a pressure stabilizing valve, a pressure regulating valve, a proportional valve, and a reversing valve, wherein,

[0019] The speed regulating valve and the pressure stabilizing valve cooperate to regulate the oil flow into the clutch actuating chamber.

[0020] The pressure regulating valve and the proportional valve cooperate to regulate the oil pressure into the clutch actuating chamber.

[0021] The reversing valve is used to switch between the oil filling process and the oil draining process.

[0022] Further, the speed regulating valve, the reversing valve, and the proportional valve are all selected to be solenoid valves.

[0023] A control method of a hydraulic control system as described above, the method comprising,

[0024] When the low-pressure oil enters the transmission control module controller, the controller adjusts the oil pressure by dynamically adjusting the opening degree of the proportional valve.

[0025] The first pressure sensor collects the oil pressure value and transmits it to the controller.

[0026] Further, the method further comprises,

[0027] The controller controls the opening of the speed regulating valve to regulate the flow of lubricating oil into the clutch actuating chamber, thereby realizing speed regulation of the lubricating oil pressure.

[0028] Further, the method further comprises that the controller controls the reversing valve to realize switching of the oil charging process or the oil discharging process.

[0029] Further, the method further comprises that the reversing valve is electrified for the oil charging process, and the first lubricating oil pressure sensor is taken as a control target, and the pressure and flow into the clutch are ensured to meet the requirements through the joint action of the pressure stabilizing valve and the speed regulating valve.

[0030] The reversing valve is de-energized for the oil discharging process, and the second lubricating oil pressure sensor is taken as a control target, and the system is kept in a pressure maintaining state through the regulating of the pressure regulating valve and the proportional valve.

[0031] The hydraulic control system as described above is applied to a helicopter variable speed transmission system.

[0032] Technical effects and advantages of the present application:

[0033] The present application is a hydraulic control system applied to a variable speed transmission system, which is completely self-developed, has dynamic adjustable pressure, high regulation precision and fast response.

[0034] The hydraulic control system can realize dynamic closed-loop control of pressure, has high regulation precision, and the response time of the adopted valves is within 50 ms, the whole system responds rapidly, can realize control of different oil charging processes, and the lubricating oil in the clutch actuating chamber can be quickly discharged through the reversing valve, thereby realizing good engagement and disengagement control of the friction clutch.

[0035] The present application has developed a product, which has passed a separate system joint test, and has been actually used in a certain variable speed transmission system project, and has completed multiple bench tests with a variable speed transmission unit, and the test results show that the hydraulic control system is rationally designed, has satisfactory function and performance, is convenient to use, and can meet the basic control requirements of the variable speed transmission system. The product has completed acceptance with the certain variable speed transmission system project.

[0036] Other features and advantages of the present application will be set forth in the following description of the application, and in part will become apparent to those skilled in the art from the description, or can be learned by practice of the application. The objects and other advantages of the present application can be realized and attained by the structure particularly pointed out in the description and the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0037] Figure 1 It is a hydraulic control system principle diagram of the variable speed transmission system of the present application;

[0038] Figure 2 It is a control valve integrated assembly structure composition diagram in one specific embodiment of the present application;

[0039] Figure 3 Figure 1 is a schematic diagram of the structure of the control valve integrated assembly in one embodiment of the present application.

[0040] In the figure: 1, inlet; 2, filter; 3, check valve; 4, speed regulating valve; 5, pressure stabilizing valve; 6, reversing valve; 7, pressure regulating valve; 8, proportional valve. DETAILED DESCRIPTION

[0041] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0042] To solve the problems in the prior art, the present application discloses a hydraulic control system, as shown in Figure 1 The system comprises a variable speed control module, a controller, a first pressure sensor, a temperature sensor and a flow meter, wherein the variable speed control module is used for dynamic closed-loop control of pressure; the controller is used for controlling the variable speed control module. The first pressure sensor is used for measuring the lubricating oil pressure entering the clutch actuating cavity, and provides feedback for lubricating oil pressure closed-loop control; the temperature sensor is used for measuring the lubricating oil temperature entering the clutch actuating cavity, and provides a basis for temperature correction of the system; and the flow meter is used for measuring the lubricating oil flow entering the clutch actuating cavity, and provides feedback for flow closed-loop control.

[0043] Further, the variable speed control module comprises an electric lubricating oil pump, a second pressure sensor, a pipeline and a control valve integrated assembly, wherein the electric lubricating oil pump is connected with the control valve integrated assembly through the pipeline. The second pressure sensor is used for taking the second pressure sensor as a control target when the reversing valve 6 is powered off, i.e. during the oil discharge process, and adjusting the pressure regulating valve 7 to make the entire system in a suitable pressure maintaining state, so as to prepare for the next oil filling. The electric lubricating oil pump is used for pressurizing the low-pressure lubricating oil from the lubricating oil tank, and controlling the oil pressure of the entire hydraulic system through cooperation of the pressure regulating valve 7 and the proportional valve 8.

[0044] Further, a safety valve is integrated in the electric lubricating oil pump, which plays a protection role and is used for ensuring that the system oil pressure does not exceed a given limit value.

[0045] Further, as shown in Figure 2 The control valve integrated assembly comprises an inlet 1, a filter 2, a check valve 3, a speed regulating valve 4, a pressure stabilizing valve 5, a reversing valve 6, a pressure regulating valve 7 and a proportional valve 8.

[0046] The filter 2 is arranged to ensure the cleanliness of the lubricating oil entering the control valve assembly, and to avoid the sticking of the electromagnetic valve; the one-way valve is arranged to prevent backflow; the pressure stabilizing valve 5 is arranged to stabilize the counter pressure of the clutch during oil filling, and to ensure the stability of the system flow; the proportional valve 8 is arranged to mainly receive the instructions of the controller, and to output the hydraulic power to drive the pressure regulating valve, and to amplify the oil pressure.

[0047] In one specific embodiment of the present application, the speed regulating valve 4 and the pressure stabilizing valve 5 are matched to regulate the flow of the lubricating oil entering the clutch actuating cavity; and the reversing valve 6 is arranged to switch the oil filling process and the oil discharging process.

[0048] Since the friction clutch of the variable speed transmission system mainly realizes the two-stage speed change of the rotor, the hydraulic control system needs to realize the continuous switching of the oil filling and discharging processes, and the switching impact load is large at the switching moment, and the switching process is rapid, which has high requirements for the reliability of the switching mechanism. The two-position three-way valve is used for regulating the pressure of the domestic aircraft and engine, and the reliability of the installation and use of the two-position three-way valve is evaluated, and finally

[0049] the type of the reversing valve 6 is determined, and the most reliable constant flow control mode is adopted. (The service life of the domestic same type of electromagnetic valve is generally 1500-2000 times, and the service life of the reversing valve is less than 3000 times)

[0050] Further, the reversing valve 6 switches the oil circuit by receiving the electric signal, and realizes the control of the oil filling and discharging processes; the speed regulating valve 4 and the pressure stabilizing valve 5 regulate the flow of the lubricating oil entering the clutch actuating cavity, so as to realize the adjustable speed of the pressure establishment. All the electromagnetic valve assemblies are uniformly controlled by the controller, and the rapid and stable regulation of the pressure of the entire hydraulic control system is realized.

[0051] 0In order to avoid the pressure fluctuation during the switching process, a second pressure sensor is arranged in front of the speed regulating valve 4 after the electric lubricating oil pump, the pressure at the position is collected by the system, and is pre-controlled to be stable at a suitable pressure value, so as to prepare for the next oil filling. When the system executes the engagement instruction, the target pressure of the system is changed to the lubricating oil pressure 1, so as to avoid the too large change of the pressure of the system, and to cause the instability of the system pressure or the unreliable clutch engagement.

[0052] 5In one specific embodiment of the present application, in order to find the optimal engagement pressure of the friction clutch,

[0053] the most suitable control strategy is formulated. The hydraulic control system reserves the target pressure configuration parameter table in the controller, the pressure regulating valve 7 and the proportional valve 8 are matched to regulate the lubricating oil pressure entering the clutch actuating cavity, and the variable target pressure control function of the system is realized, that is, the target pressure of the system can be expressed as a function of time for automatic closed-loop control, instead of a constant value in the traditional way.

[0054] 0 In order to meet the high-precision and fast-response control requirements of the variable speed transmission system, the proportional valve 8, the speed regulating valve 4 and the reversing valve 6 used in the system are all selected to be electromagnetic valves with fast response speed and high regulation precision, and the controller controls the same by adjusting the PWM duty cycle, so that the electromagnetic valves can be reliably actuated, and thus the pressure of the entire hydraulic control system can be quickly and stably regulated. During the control process, the system demand

[0055] The pressure and flow rate can be manually input in real time by the upper computer, and the system demand pressure can also be expressed as a function of time and written into the controller in advance by software, and the controller automatically dynamically regulates the system pressure according to the pressure target value curve, so as to realize the control of different oil charging processes. The hydraulic control system can realize dynamic closed-loop control of pressure, has high regulation precision, and the response time of the electromagnetic valves used is all within 50 ms, among which the response time of the reversing valve 6 reaches 10 ms, and the action time of the pressure regulating valve 7 and the speed regulating valve 4 is all within 200 ms, and the pressure regulating valve and the speed regulating valve are reliably controlled by adjusting the PWM duty cycle. The entire system has fast response, and can realize the control of different oil charging processes, and the oil in the clutch actuating cavity can be quickly discharged through the reversing valve 6, so that the engagement and disengagement control of the friction clutch can be well realized.

[0056] The application further discloses a hydraulic control method, which comprises the following steps: when low-pressure oil enters a variable speed control module controller, the controller regulates the oil pressure by dynamically adjusting the opening degree of a pressure regulating valve 8; a first pressure sensor collects the oil pressure value and transmits the same to the controller, so as to form a closed-loop control.

[0057] As shown in Figure 3 The controller regulates the oil flow rate entering the clutch actuating cavity by controlling the opening degree of a speed regulating valve 4, so as to realize the speed-adjustable oil pressure. The controller controls the reversing valve to realize the switching of the oil charging process or the oil discharging process. When the reversing valve 6 is electrified, it is the oil charging process, and the first oil pressure sensor is taken as the control target, and the pressure regulating valve 5 and the speed regulating valve 4 jointly act to ensure that the pressure and flow rate entering the clutch meet the requirements. When the reversing valve 6 is de-energized, it is the oil discharging process, and the second oil pressure sensor is taken as the control target, and the pressure regulating valve 7 and the proportional valve 8 are regulated to make the system in a pressure maintaining state.

[0058] The application further discloses the application of the hydraulic control system in a helicopter variable speed transmission system. The application is a completely self-developed hydraulic control system applied to a variable speed transmission system, which has dynamic adjustable pressure, high regulation precision and fast response.

[0059] The technical scheme of the application will be further described below in combination with specific embodiments.

[0060] In combination with Figure 1When the low-pressure lubricating oil from the lubricating oil tank enters the electric lubricating oil pump for pressurization, the controller dynamically adjusts the opening of the pressure regulating valve according to the system required pressure through the electric current, and forms a closed-loop control with the lubricating oil pressure collected by the first pressure sensor.

[0061] Further, a safety valve is integrated in the electric lubricating oil pump, which plays a protective role and ensures that the system oil pressure does not exceed a given limit value; when it is desired to change the clutch engagement speed, the controller controls the opening of the speed regulating valve according to the instructions of the upper computer through the electric current (the system flow target value can also be set according to the actual requirements, and the controller automatically dynamically adjusts the opening of the speed regulating valve according to the collected lubricating oil flow to realize flow closed-loop control), so as to adjust the flow entering the clutch actuating cavity, so as to realize the adjustable speed of establishing pressure.

[0062] Further, when the engagement / disengagement instruction is received, the controller controls the change-over valve through the electric signal to realize the switching of the oil charging / drainage process. When the change-over valve is powered on, it is the oil charging process, and the system takes the first lubricating oil pressure sensor as the control target, and through the dynamic adjustment of the pressure regulating valve and the speed regulating valve, the pressure and flow entering the clutch are ensured to meet the requirements; when the change-over valve is powered off, it is the oil drainage process, and the system takes the first lubricating oil pressure as the control target, and through the adjustment of the pressure regulating valve, the entire system is in a suitable pressure maintaining state, ready for the next oil charging. The oil charging and oil drainage switching is realized through a two-position three-way valve, and this pressure relief scheme not only realizes the rapid oil drainage of the clutch disengagement process (the target pressure needs only about 0.5s to drop from the given value to 0), but also avoids the need to add new pipelines due to pressure relief.

[0063] The proportional valve 8, the speed regulating valve 4 and the change-over valve 6 used in the system are all selected to be electromagnetic valves with fast response speed and high adjustment accuracy, and the controller controls them through adjusting the PWM duty cycle, which ensures the reliable action of the electromagnetic valves, so as to realize the fast and stable adjustment of the pressure of the entire hydraulic control system. In the control process, the system required pressure and flow can be manually input in real time through the upper computer, and the system required pressure can also be expressed as a function of time and written into the controller in advance, and the controller automatically dynamically adjusts the system pressure according to the pressure target value curve to realize the control of different oil charging processes. This function has been verified by experiments, and the system pressure P is adjusted in sections with time t, for example, within 0-0.5s, the target pressure P=1*t; within 0.5s-1s, the target pressure P=0.5*t+0.5; within 1s-2s, the target pressure P=1.8MPa.

[0064] Finally, it should be noted that the above only describes the preferred embodiments of the present application and is not intended to limit the present application. Although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art will appreciate that the technical solutions described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalent features, and any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A hydraulic control system, characterized in that: The system includes a speed control module and a controller, wherein: The speed control module is used for dynamic closed-loop control of lubricating oil pressure; the speed control module includes an electric lubricating oil pump, a second pressure sensor, a pipeline and a control valve integrated component, wherein, The electric lubricating oil pump is connected to the control valve integrated component through a pipeline; The second pressure sensor is used to measure the system pressure of the opening chamber of the reversing valve and provide feedback for the pressure stabilization control before the system takes action; The electric lubricating oil pump is used to pressurize the low-pressure lubricating oil from the lubricating oil tank; The control valve integrated assembly comprises a speed regulating valve (4), a pressure stabilizing valve (5), a pressure regulating valve (7), a proportional valve (8) and a reversing valve (6), wherein: The speed regulating valve (4) and the pressure stabilizing valve (5) cooperate to regulate the flow of lubricating oil entering the clutch actuating chamber; The pressure regulating valve (7) and the proportional valve (8) cooperate to regulate the lubricating oil pressure entering the clutch actuating chamber; The reversing valve (6) is used to switch between the oil filling process and the oil draining process; The controller is used to control the speed control module; The system further comprises a first pressure sensor, a temperature sensor and a flow meter, wherein, The first pressure sensor is used to measure the lubricating oil pressure entering the clutch actuating chamber and provide feedback for the lubricating oil pressure closed-loop control; The temperature sensor is used to measure the temperature of the lubricating oil entering the clutch actuating chamber, providing a basis for the system to make temperature corrections; The flowmeter is used to measure the oil flow entering the clutch actuating chamber and provide feedback for flow closed-loop control.

2. A hydraulic control system according to claim 1, characterized in that: The electric lubricating oil pump includes a safety valve, which is integrated inside the electric lubricating oil pump; the safety valve is used to ensure that the system oil pressure does not exceed a predetermined limit value.

3. A hydraulic control system according to claim 1, characterized in that: The speed regulating valve (4), the reversing valve (6) and the proportional valve (8) are all electromagnetic valves.

4. A control method for a hydraulic control system according to any one of claims 1 to 3, characterized in that: The method comprises, When low-pressure lubricating oil enters the speed control module controller, the controller adjusts the lubricating oil pressure by dynamically adjusting the opening of the proportional valve (8); The first pressure sensor collects the lubricating oil pressure value and transmits it to the controller.

5. A hydraulic control method according to claim 4, characterized in that: The method further comprises, The controller adjusts the flow of lubricating oil entering the clutch actuating chamber by controlling the opening of the speed regulating valve (4), thereby realizing speed regulation of the lubricating oil pressure.

6. A hydraulic control method according to claim 4, characterized in that: The method further comprises, The controller realizes the switching of the oil filling or oil draining process by controlling the reversing valve (6).

7. A hydraulic control method according to claim 6, characterized in that: The method further comprises, When the reversing valve (6) is energized, it is an oil filling process. The first lubricating oil pressure sensor is used as the control target. The pressure stabilizing valve (5) and the speed regulating valve (4) work together to ensure that the pressure and flow entering the clutch meet the requirements. When the reversing valve (6) is powered off, it is an oil drain process. The second lubricating oil pressure sensor is used as a control target, and the system is kept in a pressure-maintaining state through regulation of the pressure regulating valve (7) and the proportional valve (8).

8. Application of the hydraulic control system according to any one of claims 1 to 3 in a helicopter variable speed transmission system.

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