Hydraulic system for frequent start-stop test of wind power reducer

Abstract

A hydraulic system for a frequent start-stop test of a wind power speed reducer relates to the technical field of wind power speed reducer tests and is used for loading the wind power speed reducer, so that the test efficiency can be effectively improved. In the hydraulic system for the frequent start-stop test of the wind power speed reducer, the hydraulic pump is used as a power source, the system pressure is accurately controlled through the electromagnetic proportional overflow valve, and the hydraulic flow direction switching is realized through the electro-hydraulic directional control valve; the output hydraulic oil can selectively and independently load a single speed reducer or load two speed reducers at the same time after being shunted.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of wind power reducer test, in particular to a hydraulic system for wind power reducer frequent start-stop test. BACKGROUND

[0002] At present, as one of the core components of wind turbine generator, the wind power reducer realizes the effective conversion and utilization of wind energy through a complex gear transmission structure, and its reliability is crucial to the stable operation of the wind turbine generator.

[0003] Among them, the wind power reducer frequent start-stop test is a key link to verify its reliability, and the current wind power reducer frequent start-stop test generally adopts motor loading method, and the single reversing time is as high as about 40 seconds, while the wind power reducer frequent start-stop test needs to complete tens of thousands of reversing cycles, so that the test cycle of a type of wind power reducer is as long as one month, which seriously restricts the product delivery efficiency.

[0004] Therefore, how to provide a hydraulic system for wind power reducer frequent start-stop test, which can make the reversing speed significantly better than the motor by virtue of the fluid transmission characteristics and the quick response mechanism of the electromagnetic valve, and effectively improve the test efficiency, has become a technical problem to be solved by the person skilled in the art. SUMMARY

[0005] The purpose of the present application is to provide a hydraulic system for wind power reducer frequent start-stop test, which uses a hydraulic system to load the wind power reducer, thereby effectively improving the test efficiency.

[0006] In order to achieve the above purpose, the technical scheme adopted by the present application is as follows: A hydraulic system for wind power reducer frequent start-stop test, which uses a hydraulic pump as a power source, accurately controls the system pressure through an electromagnetic proportional overflow valve, and realizes hydraulic flow switching by using an electro-hydraulic reversing valve, and the output hydraulic oil can selectively implement independent loading on a single reducer or simultaneously load on two reducers after being divided; The hydraulic oil is divided into main and branch oil paths by the electro-hydraulic reversing valve; a first stop valve and a second stop valve, a first pressure gauge and a second pressure gauge, a first pressure sensor and a second pressure sensor, and a first hydraulic motor are arranged on the main oil path, the first stop valve and the second stop valve are used to control the on-off of the oil path, the first pressure gauge and the second pressure gauge are used to display the main path pressure, the first pressure sensor and the second pressure sensor are used for main path pressure signal conversion output, and the first hydraulic motor is used for loading on the first reducer; The branch oil circuit is provided with a third stop valve and a fourth stop valve, a first electromagnetic proportional pressure reducing valve and a second electromagnetic proportional pressure reducing valve, a first check valve and a second check valve, a third pressure gauge and a fourth pressure gauge, a third pressure sensor and a fourth pressure sensor, and a second hydraulic motor, wherein the third stop valve and the fourth stop valve are used for controlling the on-off of the oil circuit, the first electromagnetic proportional pressure reducing valve and the second electromagnetic proportional pressure reducing valve are used for regulating the branch pressure, the first check valve and the second check valve are used for controlling the flow direction of the hydraulic oil, the third pressure gauge and the fourth pressure gauge are used for displaying the main circuit pressure, the third pressure sensor and the fourth pressure sensor are used for branch pressure signal conversion output, and the second hydraulic motor is used for loading the second speed reducer. When the third stop valve and the fourth stop valve are closed and the first stop valve and the second stop valve are opened, only the main circuit works, the first hydraulic motor loads the first speed reducer to realize the test of a single speed reducer; when the third stop valve, the fourth stop valve, the first stop valve and the second stop valve are all opened, the first hydraulic motor loads the first speed reducer and the second hydraulic motor loads the second speed reducer to realize the test of two wind power speed reducers at the same time.

[0007] In actual application, the oil outlet of the hydraulic pump is connected with the P port of the electro-hydraulic reversing valve, the T port of the electro-hydraulic reversing valve is connected with an oil tank, the electromagnetic proportional overflow valve adjusts the system pressure, when the 2Y electromagnet of the electro-hydraulic reversing valve is electrified, the valve core switching makes the P-A and T-B oil circuits conductive, and the high-pressure oil at the A port drives the first hydraulic motor to operate, and the oil at the B port returns to the oil tank. When the pressure difference detected by the first pressure sensor and the second pressure sensor reaches a set value, the 1Y electromagnet of the electro-hydraulic reversing valve is electrified, the valve core switching makes the P-B and T-A oil circuits conductive, the high-pressure oil at the B port drives the first hydraulic motor to operate, and the oil at the A port returns to the oil tank to realize reverse loading. The first pressure sensor and the second pressure sensor feed back the control electromagnets 2Y and 1Y to realize the automatic reversing function of the electro-hydraulic reversing valve, complete the forward and reverse switching of the first hydraulic motor, and realize the frequent start-stop control of the first speed reducer.

[0008] The oil outlet of the hydraulic pump is connected with the P port of the electro-hydraulic reversing valve, the T port of the electro-hydraulic reversing valve is connected with an oil tank, the electromagnetic proportional overflow valve adjusts the system pressure, when the 2Y electromagnet of the electro-hydraulic reversing valve is electrified, the valve core switches to make the P-A and T-B oil paths conductive, the A port is connected with the P port of the second electromagnetic proportional pressure reducing valve, because the second electromagnetic proportional pressure reducing valve and the first electromagnetic proportional pressure reducing valve are both one-way pressure adjusting, the second one-way valve and the first one-way valve are connected in parallel on both sides of the second electromagnetic proportional pressure reducing valve and the first electromagnetic proportional pressure reducing valve for oil return, the high-pressure oil in the A port drives the second hydraulic motor to operate after being reduced in pressure by the first electromagnetic proportional pressure reducing valve and the second electromagnetic proportional pressure reducing valve, and the B port returns oil to the oil tank; When the pressure difference detected by the third pressure sensor and the fourth pressure sensor reaches a set value, the 1Y electromagnet of the electro-hydraulic reversing valve is electrified, the valve core switches to make the P-B and T-A oil paths conductive, the high-pressure oil in the B port drives the second hydraulic motor to operate, and the A port returns oil to the oil tank, so that reverse loading is realized. The electromagnets 2Y and 1Y are alternately electrified through feedback control of the third pressure sensor and the fourth pressure sensor, so that the automatic reversing function of the electro-hydraulic reversing valve is realized, the forward and reverse rotation switching of the second hydraulic motor is completed, and the frequent start-stop control of the second speed reducer is realized.

[0009] Compared with the prior art, the wind power speed reducer frequent start-stop test hydraulic system has the following advantages: In the wind power speed reducer frequent start-stop test hydraulic system, the split type multi-loop control can simultaneously simulate the frequent start-stop of two speed reducers under different working conditions, and the test efficiency is improved by 100% compared with the traditional single-loop test, and is especially suitable for consistency verification in batch production. The main loop adopts the standardized configuration of a stop valve, a pressure gauge, a pressure sensor and a hydraulic motor, the branch circuit is provided with an electromagnetic proportional pressure reducing valve and a one-way valve, and the differential loading capacity is formed, so that the individual test requirements of different speed reducers can be met. Specifically, the electromagnetic proportional pressure reducing valve in the branch circuit can adjust the loading pressure in real time according to the test requirements (adjustment accuracy ±0.5%FS), and the one-way valve and the stop valve cooperate to realize directional flow control of the hydraulic oil, so as to effectively avoid the pressure interference between different loops, and the pressure fluctuation can be controlled within ±2% in the frequent start-stop test, which is significantly better than the ±5% level of the prior art. In addition, the double hydraulic motors can simulate the torque load of the input shaft and the axial load of the output shaft of the speed reducer respectively, so as to reproduce the composite working condition in actual operation. Through real-time feedback of the pressure sensor (response time < 50ms), the system can dynamically adjust the flow ratio of the two hydraulic oils, so as to ensure that the loading error of the two speed reducers is less than 3%, and the problem that the traditional test system cannot simulate multi-dimensional load is solved. BRIEF DESCRIPTION OF DRAWINGS

[0010] Figure 1 A schematic diagram of the hydraulic system for frequent start-stop testing of wind turbine reducers provided in an embodiment of the present invention.

[0011] Figure label: 1-Hydraulic pump; 2-Solenoid proportional relief valve; 3-Electro-hydraulic directional valve; 4-First shut-off valve; 5-First pressure gauge; 6-First pressure sensor; 7-Second pressure gauge; 8-Second pressure sensor; 9-Second shut-off valve; 20-First hydraulic motor; 21-First reducer; 10-Third shut-off valve; 11-First electromagnetic proportional pressure reducing valve; 12-First check valve; 13-Third pressure gauge; 14-Third pressure sensor; 15-Fourth pressure sensor; 16-Fourth pressure gauge; 17-Second electromagnetic proportional pressure reducing valve; 18-Second check valve; 19-Fourth shut-off valve; 22-Second hydraulic motor; 23-Second reducer. Detailed Implementation

[0012] For ease of understanding, the hydraulic system for frequent start-stop testing of wind turbine reducers provided in the embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0013] This invention provides a hydraulic system for frequent start-stop testing of wind turbine reducers, such as... Figure 1 As shown, hydraulic pump 1 is used as the power source, electromagnetic proportional relief valve 2 is used to precisely control the system pressure, and electro-hydraulic directional valve 3 is used to switch the hydraulic flow direction. The hydraulic oil output can be selectively loaded on a single reducer or loaded on two reducers at the same time after being diverted. The hydraulic oil is split into two main and branch oil circuits by the electro-hydraulic directional valve 3. The main oil circuit is equipped with a first shut-off valve 4 and a second shut-off valve 9, a first pressure gauge 5 and a second pressure gauge 7, a first pressure sensor 6 and a second pressure sensor 8, and a first hydraulic motor 20. The first shut-off valve 4 and the second shut-off valve 9 are used to control the opening and closing of the oil circuit. The first pressure gauge 5 and the second pressure gauge 7 are used to display the pressure of the main circuit. The first pressure sensor 6 and the second pressure sensor 8 are used to convert and output the pressure signal of the main circuit. The first hydraulic motor 20 is used to load the first reducer 21. The branch oil circuit is provided with a third stop valve 10 and a fourth stop valve 19, a first electromagnetic proportional pressure reducing valve 11 and a second electromagnetic proportional pressure reducing valve 17, a first check valve 12 and a second check valve 18, a third pressure gauge 13 and a fourth pressure gauge 16, a third pressure sensor 14 and a fourth pressure sensor 15, and a second hydraulic motor 22, the third stop valve 10 and the fourth stop valve 19 are used for controlling the on-off of the oil circuit, the first electromagnetic proportional pressure reducing valve 11 and the second electromagnetic proportional pressure reducing valve 17 are used for regulating the branch pressure, the first check valve 12 and the second check valve 18 are used for controlling the flow direction of the hydraulic oil, the third pressure gauge 13 and the fourth pressure gauge 16 are used for displaying the main circuit pressure, the third pressure sensor 14 and the fourth pressure sensor 15 are used for branch pressure signal conversion output, and the second hydraulic motor 22 is used for loading the second speed reducer 23. When the third stop valve 10 and the fourth stop valve 19 are closed and the first stop valve 4 and the second stop valve 9 are opened, only the main circuit works, and the first hydraulic motor 20 loads the first speed reducer 21 to realize the test of a single speed reducer; when the third stop valve 10 and the fourth stop valve 19 and the first stop valve 4 and the second stop valve 9 are all opened, the first hydraulic motor 20 loads the first speed reducer 21, and the second hydraulic motor 22 loads the second speed reducer 23 to realize the test of two wind power speed reducers at the same time.

[0014] Compared with the prior art, the wind power speed reducer frequent start-stop test hydraulic system has the following advantages: In the wind power speed reducer frequent start-stop test hydraulic system, the split type multi-circuit control can simultaneously simulate the frequent start-stop of two speed reducers under different working conditions, and the test efficiency is improved by 100% compared with the traditional single-circuit test, and is especially suitable for consistency verification in batch production; wherein the main circuit adopts the standardized configuration of stop valves, pressure gauges, pressure sensors and hydraulic motors, the branch circuit adds electromagnetic proportional pressure reducing valves and check valves to form differentiated loading capacity, so as to meet the individualized test requirements of different speed reducers; specifically, the electromagnetic proportional pressure reducing valve in the branch circuit can adjust the loading pressure in real time according to the test requirements (adjustment accuracy ±0.5%FS), and the check valve cooperates with the stop valve to realize the directional flow control of the hydraulic oil, thereby effectively avoiding the pressure interference between different circuits, and the pressure fluctuation can be controlled within ±2% in the frequent start-stop test, which is significantly better than the ±5% level of the prior art; in addition, the double hydraulic motors can simulate the torque load of the input shaft and the axial load of the output shaft of the speed reducer respectively, so as to reproduce the composite working condition in actual operation; through the real-time feedback of the pressure sensor (response time <50ms), the system can dynamically adjust the flow ratio of the two hydraulic oils, thereby ensuring that the loading error of the two speed reducers is less than 3%, and solving the problem that the traditional test system cannot simulate multi-dimensional load.

[0015] In actual application, for example,Figure 1 As shown, the oil outlet of the hydraulic pump 1 is connected to the P port of the electro-hydraulic directional valve 3, the T port of the electro-hydraulic directional valve 3 is connected to the oil tank, and the electromagnetic proportional relief valve 2 regulates the system pressure. When the 2Y electromagnet of the electro-hydraulic directional valve 3 is energized, the valve core switches to make the PA and TB oil circuits open. The high pressure oil at port A drives the first hydraulic motor 20 to run, and the oil at port B returns to the oil tank. When the pressure difference detected by the first pressure sensor 6 and the second pressure sensor 8 reaches the set value, the 1Y solenoid of the electro-hydraulic reversing valve 3 is energized, the valve core switches to make the PB and TA oil circuits open, the high pressure oil at port B drives the first hydraulic motor 20 to run, and the oil at port A returns to the oil tank to achieve reverse loading. The electro-hydraulic directional valve 3 automatically switches between forward and reverse directions by feedback control of the first pressure sensor 6 and the second pressure sensor 8, thereby realizing the automatic switching function of the electro-hydraulic directional valve 3 and completing the forward and reverse switching of the first hydraulic motor 20, while realizing the frequent start and stop control of the first reducer 21.

[0016] Among them, such as Figure 1 As shown, the outlet of the hydraulic pump 1 is connected to the P port of the electro-hydraulic directional valve 3, the T port of the electro-hydraulic directional valve 3 is connected to the oil tank, and the electromagnetic proportional relief valve 2 regulates the system pressure. When the 2Y electromagnet of the electro-hydraulic directional valve 3 is energized, the valve core switches to make the PA and TB oil circuits open. The A port is connected to the P port of the second electromagnetic proportional pressure reducing valve 17. Since the second electromagnetic proportional pressure reducing valve 17 and the first electromagnetic proportional pressure reducing valve 11 are both one-way pressure regulating valves, the second check valve 18 and the first check valve 12 are connected in parallel on both sides of the second electromagnetic proportional pressure reducing valve 17 and the first electromagnetic proportional pressure reducing valve 11 for oil return. The high pressure oil at the A port is reduced by the first electromagnetic proportional pressure reducing valve 11 and the second electromagnetic proportional pressure reducing valve 17 and then drives the second hydraulic motor 22 to run. The oil at the B port returns to the oil tank. When the pressure difference detected by the third pressure sensor 14 and the fourth pressure sensor 15 reaches the set value, the 1Y electromagnet of the electro-hydraulic reversing valve 3 is energized, the valve core switches to make the PB and TA oil circuits open, the high pressure oil at port B drives the second hydraulic motor 22 to run, and the oil at port A returns to the oil tank to achieve reverse loading. The electro-hydraulic directional valve 3 is automatically switched on and off by feedback control of the third pressure sensor 14 and the fourth pressure sensor 15, so as to realize the forward and reverse switching of the second hydraulic motor 22 and realize the frequent start and stop control of the second reducer 23.

[0017] To sum up, in the hydraulic system for frequent start-stop test of the wind power reducer provided by the embodiment of the application, the shunt control of "one pump and multiple loads" is realized by the electro-hydraulic reversing valve to form two independent oil paths of the main path and the branch path, while in the prior art, the multiple-pump parallel scheme is mostly used for multiple-device testing, which significantly increases the system complexity and energy consumption; for example, the hydraulic test table in the prior art needs to separately configure a hydraulic pump for each device, while the technical solution reduces the number of pump groups by 50% through shunt design; The system collects the main path pressure signal and the branch path pressure signal through a pressure sensor, and automatically matches the loading requirements of different reducers in combination with the cooperative regulation of the electromagnetic proportional overflow valve and the electromagnetic proportional pressure reducing valve; for example, when the branch reducer needs higher pressure, the system automatically dynamically allocates 20% of the main path pressure to the branch path; The traditional hydraulic system is prone to pressure oscillation (fluctuation amplitude > 10%) during frequent start-stop, while the technical solution controls the pressure fluctuation within ±3% through the rapid response (response time < 20ms) of the electromagnetic proportional overflow valve and the reverse flow blocking of the check valve, thereby meeting the stringent requirements of the wind power reducer on loading accuracy; The existing test system is mostly designed for specific models of reducers, while the technical solution can meet the testing requirements of different specifications of reducers through modular oil path design (standardization of the main path and customization of the branch path), and the device utilization rate is improved by 40% without the need to redesign the hydraulic circuit when the test object is replaced; The traditional single-loop test takes 48 hours to complete the full-condition test of two reducers, while the technical solution can shorten the time to 24 hours through simultaneous loading, and the test cycle is compressed by 50%; the main path adopts closed-loop control of the pressure sensor (accuracy ±0.1%FS) and the hydraulic motor (rotation speed control accuracy ±0.5%), and the branch path realizes fine loading through the electromagnetic proportional pressure reducing valve (pressure regulation resolution 0.1MPa), and the overall test accuracy is improved by 30% compared with the prior art; The main path and the branch path are both provided with independent stop valves and pressure sensors, and when a loop fails, the system can automatically switch to the standby loop, and the mean time between failures (MTBF) of the system is improved from 800 hours of the traditional scheme to 1500 hours; the electromagnetic proportional pressure reducing valve and the check valve of the branch path are designed in an integrated valve block, and when they are replaced, the entire hydraulic system does not need to be disassembled, and the maintenance time is reduced by 70%.

[0018] The above is only a specific embodiment of the application, but the protection scope of the application is not limited thereto, and any person skilled in the art can easily think of changes or replacements within the technical scope disclosed by the application, which should be covered within the protection scope of the application. Therefore, the protection scope of the application should be subject to the protection scope of the claims.

Claims

1. A hydraulic system for frequent start-stop testing of wind turbine reducers, characterized in that, A hydraulic pump is used as the power source. The system pressure is precisely controlled by an electromagnetic proportional relief valve, and the hydraulic flow direction is switched by an electro-hydraulic directional valve. The output hydraulic oil can be selectively loaded on a single reducer or loaded on two reducers at the same time after being diverted. Hydraulic oil is split into main and branch oil circuits via the electro-hydraulic directional valve. The main oil circuit is equipped with a first shut-off valve and a second shut-off valve, a first pressure gauge and a second pressure gauge, a first pressure sensor and a second pressure sensor, and a first hydraulic motor. The first shut-off valve and the second shut-off valve are used to control the on / off of the oil circuit. The first pressure gauge and the second pressure gauge are used to display the main circuit pressure. The first pressure sensor and the second pressure sensor are used to convert and output the main circuit pressure signal. The first hydraulic motor is used to load the first reducer. The branch oil circuit is equipped with a third and a fourth shut-off valve, a first and a second electromagnetic proportional pressure reducing valve, a first and a second check valve, a third and a fourth pressure gauge, a third and a fourth pressure sensor, and a second hydraulic motor. The third and fourth shut-off valves are used to control the on / off of the oil circuit. The first and second electromagnetic proportional pressure reducing valves are used to regulate the branch pressure. The first and second check valves are used to control the flow direction of the hydraulic oil. The third and fourth pressure gauges are used to display the main circuit pressure. The third and fourth pressure sensors are used to convert and output the branch pressure signal. The second hydraulic motor is used to load the second reducer. When the third and fourth shut-off valves are closed and the first and second shut-off valves are open, only the main circuit works, and the first hydraulic motor loads the first reducer to achieve a test of a single reducer. When the third and fourth shut-off valves, as well as the first and second shut-off valves, are all open, the first hydraulic motor loads the first reducer, and the second hydraulic motor loads the second reducer, so as to enable the two wind turbine reducers to be tested simultaneously.

2. The hydraulic system for frequent start-stop testing of wind turbine reducers according to claim 1, characterized in that, The outlet of the hydraulic pump is connected to the P port of the electro-hydraulic directional valve, the T port of the electro-hydraulic directional valve is connected to the oil tank, the electromagnetic proportional relief valve regulates the system pressure, when the 2Y electromagnet of the electro-hydraulic directional valve is energized, the valve core switches to make the PA and TB oil circuits open, the high pressure oil at port A drives the first hydraulic motor to run, and the oil at port B returns to the oil tank. When the pressure difference detected by the first pressure sensor and the second pressure sensor reaches the set value, the 1Y solenoid of the electro-hydraulic reversing valve is energized, the valve core switches to make the PB and TA oil circuits open, the high pressure oil at port B drives the first hydraulic motor to run, and the oil at port A returns to the oil tank to achieve reverse loading. The electro-hydraulic directional valve automatically switches between forward and reverse directions by alternating energization of electromagnets 2Y and 1Y through feedback control of the first pressure sensor and the second pressure sensor, and at the same time realizes the frequent start and stop control of the first reducer.

3. The hydraulic system for frequent start-stop testing of wind turbine reducers according to claim 1, characterized in that, The outlet of the hydraulic pump is connected to the P port of the electro-hydraulic directional valve, and the T port of the electro-hydraulic directional valve is connected to the oil tank. The electromagnetic proportional relief valve regulates the system pressure. When the 2Y electromagnet of the electro-hydraulic directional valve is energized, the valve core switches to make the PA and TB oil circuits open. The A port is connected to the P port of the second electromagnetic proportional pressure reducing valve. Since both the second electromagnetic proportional pressure reducing valve and the first electromagnetic proportional pressure reducing valve are unidirectional pressure regulating valves, the second check valve and the first check valve are connected in parallel on both sides of the second electromagnetic proportional pressure reducing valve and the first electromagnetic proportional pressure reducing valve for oil return. The high-pressure oil at the A port is reduced by the first electromagnetic proportional pressure reducing valve and the second electromagnetic proportional pressure reducing valve and then drives the second hydraulic motor to run. The oil at the B port returns to the oil tank. When the pressure difference detected by the third pressure sensor and the fourth pressure sensor reaches the set value, the 1Y solenoid of the electro-hydraulic reversing valve is energized, the valve core switches to make the PB and TA oil circuits open, the high pressure oil at port B drives the second hydraulic motor to run, and the oil at port A returns to the oil tank to achieve reverse loading. The electromagnets 2Y and 1Y are alternately energized by feedback control from the third and fourth pressure sensors to realize the automatic switching function of the electro-hydraulic directional valve, complete the forward and reverse switching of the second hydraulic motor, and realize the frequent start and stop control of the second reducer.

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