A hydraulic control system for a brake of a wind turbine

Abstract

The utility model relates to a kind of hydraulic control system for brake of wind-driven generator, including power liquid pipeline I, main shaft loop II, yaw loop III, power liquid pipeline I can produce the pressure liquid with power, main shaft loop II is connected with main shaft brake, yaw loop III is connected with yaw brake;The power liquid pipeline I is connected on hydraulic oil tank;The corresponding valve in the main shaft loop II, pipeline integrated setting is on main shaft brake module;The corresponding valve in the yaw brake pipeline III, pipeline integrated setting is on yaw brake module;After the corresponding valve integrated on main shaft brake module is separately fixed and installed, after the corresponding valve integrated on yaw brake module is separately fixed and installed, form the structure that each function module is separated and is beneficial to overhaul.The utility model reaches the beneficial effect is: pipeline indirect-beneficial to subsequent carding maintenance, redundancy design-improve reliability.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic control circuit technology for wind turbine generators, and in particular to a hydraulic control system for a brake of a wind turbine generator. Background Technology

[0002] In the braking system of a wind turbine, there are two braking points: one is braking the main shaft corresponding to the blades (e.g., for maintenance) – referred to as main shaft braking; the other is braking when the blades need to be adjusted to different directions – referred to as yaw braking. Wind turbines have a yaw system (which automatically guides the blades to find the wind direction via a wind direction sensor, controller, yaw drive motor, and yaw bearing). This system regulates oil pressure through a control valve, ensuring that the brake pads (yaw brake) are evenly applied to the yaw gear to achieve braking: a. If a suitable wind direction is found, the yaw brake must be fully engaged and locked; b. To restart wind finding, the braking state must be maintained but not completely engaged, allowing the blade head to find the wind at a low turning speed in the horizontal plane; c. If a rapid adjustment of the blade head's position in the horizontal plane is needed, braking is not required (during wind finding, if the blade head yaws excessively – rotating counterclockwise / clockwise (which may cause internal cable entanglement) – the corresponding motor needs to drive the blade head back to the correct position).

[0003] In wind turbines, both main shaft braking (high-speed shaft braking or main brake drum) and yaw braking are achieved through hydraulic systems. In most large wind turbines today, the hydraulic circuits for main shaft braking and yaw braking are quite complex, and the various hydraulic components are arranged in a disorganized manner (making subsequent maintenance and other work difficult to manage). In addition, there is a lack of redundancy design, requiring frequent maintenance to reduce the failure rate. However, many wind turbines are located on mountaintops or similar locations, which increases the workload due to frequent maintenance.

[0004] Therefore, our company redesigned the corresponding brake hydraulic circuit and separated the corresponding functional units, which not only simplified the hydraulic pipeline, but also facilitated subsequent pipeline management and maintenance. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a hydraulic control system for the brake of a wind turbine, which solves the problems of low redundancy and messy pipelines in the existing hydraulic system.

[0006] The purpose of this utility model is achieved through the following technical solution: a hydraulic control system for a brake of a wind turbine generator, including a power fluid line I, a main shaft circuit II, and a yaw circuit III. The power fluid line I can generate pressurized fluid with power. The main shaft circuit II is connected to the main shaft brake, and the yaw circuit III is connected to the yaw brake. The power hydraulic line I is connected to the hydraulic oil tank; The spindle circuit II includes a spindle braking module; the spindle braking module is a separate hydraulic valve block, and a valve for controlling the braking oil pressure is integrated on it. The spindle braking module is connected to the power end of the power hydraulic line I via port A, connected to the spindle brake via port P, and flows back to the hydraulic oil tank via port T. The yaw brake line Ⅲ includes a yaw brake module; the yaw brake module is also a separate hydraulic valve block, and a valve for controlling yaw oil pressure is integrated on it. The yaw brake module is connected to the power end of the power hydraulic line Ⅰ via port A, connected to the inlet end of the yaw brake via port A, connected to the outlet end of the yaw brake via port B, and flows back to the hydraulic oil tank via port T. Each pipeline in the power hydraulic pipeline I is integrated and fixed on the hydraulic oil tank. The corresponding valves are integrated on the main shaft braking module and then fixedly installed separately. The corresponding valves are integrated on the yaw braking module and then fixedly installed separately, forming a structure in which each functional module is separated, which is conducive to maintenance.

[0007] As a preferred technical solution of this application, the hydraulic valve block corresponding to the spindle braking module has a PA channel connecting port P and port A. A first spindle solenoid valve and a spindle pressure reducing valve are connected in series on the PA channel. An additional branch channel is also provided on the channel section between port A and the spindle pressure reducing valve. This branch channel is connected to port T and has a second spindle solenoid valve. The first and second spindle solenoid valves are connected to a PLC for synchronous control—that is, both are energized or de-energized simultaneously. When both are energized, the former is connected while the latter is disconnected, forming an oil circuit for spindle braking. When both are de-energized simultaneously, the former is disconnected while the latter is connected, forming an oil circuit for spindle release braking.

[0008] Furthermore, on the hydraulic valve block corresponding to the spindle braking module, there are corresponding interfaces on the channel section between port A and the spindle pressure reducing valve, which are respectively connected to the spindle low pressure detection switch, the spindle high pressure detection switch, the spindle pressure measuring point, and the spindle accumulator.

[0009] As a preferred technical solution of this application, the hydraulic valve block corresponding to the yaw brake module has: a PA channel connecting port P and port A, and a pipe BP connecting port B and port T; a first yaw solenoid valve is provided on the PA channel; a second yaw solenoid valve and a back pressure valve are sequentially connected in series in the BT channel section; a branch is also connected in parallel on the channel section between the inlet and outlet ends of the second yaw solenoid valve, and a third yaw solenoid valve is provided on this branch. The first and second yaw solenoid valves are connected to the PLC for synchronous control—that is, they are simultaneously energized or de-energized. When they are simultaneously de-energized, the former is connected and the latter is disconnected. If the third yaw solenoid valve is disconnected at this time, a yaw brake oil circuit is formed. When they are simultaneously energized, the former is disconnected and the latter is connected. If the third yaw solenoid valve is disconnected at this time, a pressurized yaw brake oil circuit is formed. When they are simultaneously energized, the former is disconnected and the latter is connected. If the third yaw solenoid valve is disconnected at this time, a yaw release oil circuit is formed.

[0010] Furthermore, on the hydraulic valve block corresponding to the yaw braking module, a yaw pressure measuring point is also connected via a corresponding interface in the passage section from port A to the first yaw solenoid valve.

[0011] As a preferred technical solution of this application, the power hydraulic pipeline I includes an electric pipeline and a manual pipeline; the electric pipeline and the manual pipeline are connected in parallel from the hydraulic cylinder to the output end of the power hydraulic pipeline I. The electric pipeline is sequentially equipped with an electric pump, a power filter element, and a power check valve; a branch line with a safety valve is also provided between the inlet end of the power check valve and the hydraulic cylinder; a branch line with an unloading valve is also provided between the outlet end of the power check valve and the hydraulic cylinder. The manual pipeline is equipped with a manual pump.

[0012] Furthermore, the main spindle circuit II also includes a brake input line and a brake return line, both of which are integrated and fixed on the hydraulic oil tank; the brake input line connects port P to the output end of the power hydraulic line I, and the line is equipped with a main spindle inflow check valve; the brake return line connects port T to the hydraulic oil tank, and the line is equipped with a main spindle return check valve.

[0013] Furthermore, the yaw circuit III also includes a yaw input line and a yaw return line, both of which are integrated and fixed on the hydraulic oil tank; the yaw input line connects port P to the output end of the power hydraulic line I, and a yaw inflow check valve is provided on the line; the yaw return line connects port T to the hydraulic oil tank, and a yaw circuit check valve is provided on the line.

[0014] Furthermore, in the aforementioned power hydraulic line I: the output end of power hydraulic line I has a branch connected to a power accumulator. The electric pump is driven by a motor, which operates intermittently. When the entire system maintains oil pressure but does not need to output oil, the motor stops working, and the oil pressure in the system is maintained through the first accumulator. A power pressure gauge and a pressure sensor are also connected via corresponding interfaces on the branch between power hydraulic line I and the power accumulator; the pressure sensor is electrically connected to a PLC.

[0015] This utility model has the following advantages: It also achieves the following effects, and the different connection methods are... (1) Corresponding valve integration simplifies pipelines and facilitates subsequent pipeline management and maintenance; Specifically, the entire hydraulic system is divided into power hydraulic pipeline I, main spindle circuit II, and yaw circuit III. The main pipelines of power hydraulic pipeline I are fixed on the hydraulic cylinders. Some valves and pipelines of main spindle circuit II are fixed on the main spindle braking module (as hydraulic valve blocks). Some valves and pipelines of yaw circuit III are fixed on the yaw braking module (also a hydraulic module). This keeps the entire hydraulic pipeline simple, which is conducive to subsequent pipeline management, inspection, maintenance, and replacement. (2) Redundancy design improves the fault tolerance of the entire hydraulic system and enhances the reliability and availability of the entire system. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the present invention; Figure 2 This is a schematic diagram showing the disassembled power hydraulic pipeline I, main shaft circuit II, and yaw circuit III in this utility model; Figure 3 This is a schematic diagram of the power hydraulic line I and the corresponding valves and pipes integrated on the hydraulic oil tank; Figure 4 This is a schematic diagram of the pipelines on the spindle braking module in spindle circuit II, as well as the integration of various valves. Figure 5 This is a schematic diagram of the piping of the yaw braking module in yaw circuit III, as well as the integration of various valves. In the diagram: 1-Motor, 2-Electric pump, 3-Manual pump, 4.1-Power filter element, 5-Spindle pressure reducing valve, 6-Power accumulator, 7-Power check valve, 8-Power pressure gauge, 9-Safety valve, 10-Unloading valve, 12-Level gauge, 14-Back pressure valve, 15.1-Spindle first solenoid valve, 15.2-Yaw second solenoid valve, 15.3-Yaw third solenoid valve, 16.1-Spindle second solenoid valve, 16.2-Yaw first solenoid valve, 18.1-Spindle low pressure detection switch, 18.2-Spindle high pressure detection switch, 19.1-Spindle pressure measuring point, 19.2-Yaw test point, 21-Spindle accumulator. Detailed Implementation

[0017] The present invention will be further described below with reference to the accompanying drawings, but the scope of protection of the present invention is not limited to the following description.

[0018] It should be noted that in existing wind turbines, a vertical tower is installed on the ground, and a generator head is installed at the top of the tower (the generator head can swing in the horizontal plane at the top of the tower - to achieve the purpose of wind finding, which is achieved through yaw drive). The generator head has a main shaft, and blades are installed on the main shaft (the wind blows the blades to rotate, which drives the main shaft to rotate, thereby realizing power generation). In addition, a main shaft brake is installed at the main shaft (for example, when maintenance is required or other situations require stopping the blades from rotating), and a yaw brake is installed at the yaw drive (for example, when searching for wind, the yaw brake needs to work under pressure (i.e., a certain degree of braking, but not complete braking) - allowing the generator head to rotate slowly in the horizontal plane (rather than rotating quickly, which is conducive to finding a suitable wind direction). After finding the wind direction, the yaw brake needs to be fully braked and locked - preventing the generator head from rotating in the horizontal plane (therefore generating electricity). If the generator head keeps rotating clockwise / counterclockwise during the wind search, the generator head needs to be quickly returned (because if it keeps rotating clockwise / counterclockwise too many times, it will cause the internal cables of the generator to become tangled. In order to avoid excessive cable tangling, it needs to return to the untangled state and then search for wind again in the 360° range).

[0019] The corresponding actions of the main shaft brake and yaw brake are controlled by the hydraulic system. The problems with the existing hydraulic system are: (1) lack of redundancy design, for example: a. In the existing hydraulic system, the main shaft brake and yaw brake are pressurized by electric pumps. If there is a line fault or power outage that prevents the electric pump from working, the purpose of braking the main shaft to perform maintenance on the entire wind turbine cannot be achieved; b. In the existing hydraulic system, the pressure at each pipeline is usually directly installed with pressure gauges or pressure detection points (the pressure gauge is screwed on during testing). During inspection or maintenance, it is observed by the naked eye. If the corresponding pressure gauge has a problem, it cannot be guaranteed that the observed data is correct. Moreover, this kind of visual observation The inspection method makes the labor intensity of the inspection high; c. Each valve is electrically connected to the PLC separately. If the spindle braking / yaw braking (or the action required by the situation) is realized, if some valves required to realize the braking action can be energized normally while other valves cannot be energized normally, the pressure oil of the hydraulic system will flow to other pipeline parts (the oil pressure of the entire hydraulic system will need to be readjusted and adjusted afterward, which is very troublesome); (2) Each hydraulic component in the hydraulic system is set up separately and then connected through the corresponding pipelines. The entire hydraulic system appears very messy (not clean enough). The workload is extremely large when repairing or replacing parts later.

[0020] To address the aforementioned issues, this solution offers the following approach: Increasing redundancy in the design ensures timely detection and easy resolution of any problems. Furthermore, it centralizes some hydraulic components (primarily through the centralization of corresponding power lines on the hydraulic tank, corresponding components in the spindle circuit, and corresponding components in the yaw circuit), thereby keeping the entire hydraulic system's piping concise.

[0021] The following detailed implementation will further illustrate the concept of this solution (it should be noted that, without conflict, the embodiments and features and technical solutions in this utility model can be combined with each other).

[0022] like Figure 1 and Figure 3 As shown in the figure, this specific embodiment provides a hydraulic control system for a brake of a wind turbine, including a power fluid line I, a main shaft circuit II, and a yaw circuit III; moreover, the power fluid line I can generate pressurized fluid with power, the main shaft circuit II is connected to the main shaft brake, and the yaw circuit III is connected to the yaw brake. Among them, the power hydraulic line I is connected to the hydraulic oil tank; The spindle circuit II includes a spindle braking module, which is a separate hydraulic valve block. The hydraulic valve block has corresponding channels and corresponding valves on the channels (to realize the braking and releasing of the spindle brake). The spindle braking module is connected to the power end of the power hydraulic line I through port A1, connected to the spindle brake through port P1, and returns to the hydraulic oil tank through port T1. Among them, the yaw brake line III includes a yaw brake module, which is also a separate hydraulic valve block. The hydraulic valve block has corresponding channels and corresponding valves (to realize the braking, releasing, and pressurization of the yaw brake). The yaw brake module is connected to the power end of the power hydraulic line I through port A2, connected to the inlet end of the yaw brake through port A2, connected to the outlet end of the yaw brake through port B2, and flows back to the hydraulic oil tank through port T2. In addition, each pipeline in the power hydraulic line I is integrated and fixed on the hydraulic oil tank, and the corresponding valves are integrated on the main shaft brake module and then fixed separately. The corresponding valves are integrated on the yaw brake module and then fixed separately, forming a structure in which each functional module is separated, which is conducive to maintenance.

[0023] The hydraulic circuit structure of power hydraulic line I will be further explained below.

[0024] See Figure 1 , Figure 2 and Figure 3 Power hydraulic pipeline I, including electric pipeline and manual pipeline (both in...) Figure 3 (The lines were thickened in the middle). One end of the electric pipeline extends into the hydraulic oil tank (a level gauge 12 is installed on the hydraulic oil tank). An electric pump 2 (driven by motor 1), a power filter element 4.1, and a power check valve 7 (to prevent backflow of pressurized fluid) are connected in series on the electric pipeline. The other end of the electric pipeline is connected to the output end of the power fluid line I. Furthermore, a bypass valve is connected in parallel between the input and output ends of the power filter element 4.1. A first differential pressure transmitter is installed at this bypass valve. When the power filter element 4.1 becomes dirty or clogged, the bypass valve allows the entire system to operate. When the bypass valve opens, the differential pressure transmitter transmits a signal to the PLC, informing it that the bypass valve is open. (Currently, visual inspection is generally used to check for blockages in the power filter element 4.1. If it is not checked, the bypass valve may remain open, or impurities may enter the entire hydraulic system, causing further pipe blockages.) One end of the manual pipeline extends into the hydraulic cylinder, and a manual pump 3 is installed on the manual pipeline (with corresponding check valves at the front and rear ends of the manual pump 3 to prevent the pressure fluid from reversing). The other end of the manual pipeline is also connected to the output end of the power hydraulic line I. The above-mentioned manual piping is a redundant design for the electric piping. When there is a power outage or the motor cannot work, the entire system can be put into normal operation by manually pressurizing it. In addition, a branch is provided between the inlet end of the power check valve 7 and the hydraulic cylinder, and a safety valve 9 is provided on this branch. It does not open under normal circumstances, but opens when the oil pressure at the output end of the power hydraulic line I exceeds the set value - which plays the role of overload protection (for example, it opens when it exceeds the set value of 178 bar to ensure that the system pressure does not exceed 190 bar and to prevent oil pressure from flowing back to the electric pump 2 - thus causing pump overload). In addition, a branch is also provided between the outlet end of the power check valve 7 and the hydraulic cylinder, and an unloading valve 10 is provided on this branch; the unloading valve 10 is used to relieve the pressure at the output end of the power hydraulic line I (that is, to relieve the pressure of the entire pressure system, and the oil pressure generated by both electric and manual lines can be relieved).

[0025] Furthermore, in the power hydraulic line I, an auxiliary electric pump 2 or manual pump 3 is also provided for operation; specifically, a branch is provided at the output end of the power hydraulic line I, which is connected to the power accumulator 6; in this scheme, the motor 1 operates intermittently. When the entire system maintains oil pressure but does not need to output oil, the motor 1 stops working and the oil pressure in the system is maintained through the first accumulator (which can improve the service life of the electric pump 2). In addition, on the branch between the power hydraulic line I and the power accumulator 6, a power pressure gauge 8 and a pressure sensor 22 are connected via corresponding interfaces. The pressure sensor 22 is electrically connected to the PLC (this pressure sensor 22 can detect the oil pressure at the output end of the power hydraulic line I - for example, it can generate an electrical signal of 0 to 20 mA based on the detected oil pressure of 0 to 258 bar, and this electrical signal is transmitted to the PLC to know the magnitude of the input oil pressure). The power pressure gauge 8 and the pressure sensor 22 form a redundant design.

[0026] The structure of the spindle braking module in spindle circuit II will be further explained below.

[0027] See Figure 1 , Figure 2 and Figure 4 On the hydraulic valve block corresponding to the spindle braking module: a P1-A1 channel is provided to connect port P1 and port A1. A first spindle solenoid valve 15.1 (normally closed, energized to open) and a spindle pressure reducing valve 5 (which reduces oil pressure, for example, to 120 bar) are connected in series on the P1-A1 channel. In addition, a branch channel is additionally provided on the channel section between port A1 and the spindle pressure reducing valve 5. This branch channel is connected to port T1 and has a second spindle solenoid valve 16.1 (normally open, energized to close). Furthermore, the first solenoid valve 15.1 and the second solenoid valve 16.1 of the spindle are connected to the PLC to achieve synchronous control—that is, both are energized or de-energized at the same time (for example, the control circuit of the first solenoid valve 15.1 and the control circuit of the second solenoid valve 16.1 of the spindle are connected in parallel; the two control circuits are connected to a single switch, and the opening and closing of this switch realizes the energization / de-energization of both valves). (1) When the first solenoid valve 15.1 and the second solenoid valve 16.1 of the spindle are energized at the same time, the former is connected and the latter is disconnected, thus forming an oil circuit for braking the spindle; (2) When the first solenoid valve 15.1 and the second solenoid valve 16.1 of the spindle are de-energized at the same time, the former is disconnected and the latter is connected, thus forming an oil circuit for releasing the spindle brake.

[0028] Furthermore, on the hydraulic valve block corresponding to the spindle braking module, there are corresponding interfaces on the channel section between port A1 and spindle pressure reducing valve 5, which are respectively connected to spindle low pressure detection switch 18.1, spindle high pressure detection switch 18.2, spindle pressure measuring point 19.1, and spindle accumulator 21 (which is an energy-absorbing accumulator to buffer the energy of impact in the channel and reduce instantaneous pressure fluctuations). Among them, the spindle low pressure detection switch 18.1 is a low pressure transmitter (it is electrically connected to the PLC, for example, when the oil pressure is detected to be 18 bar, it sends a signal to the PLC to inform that the spindle brake is under low oil pressure at this time). Among them, the spindle high pressure detection switch 18.2 is a high pressure transmitter (it is connected to the PLC, for example, when the oil pressure is detected to be 18 bar, it sends a signal to the PLC to inform that the spindle brake is under high pressure). The spindle pressure test point 19.1 can be manually screwed with a corresponding pressure gauge / test head (for manual observation). Therefore, the spindle low pressure detection switch 18.1 and the spindle pressure test point 19.1 constitute a redundant design, as do the spindle high pressure detection switch 18.2 and the spindle pressure test point 19.1.

[0029] Furthermore, the piping on spindle circuit II is integrated as follows: In addition to the spindle braking module, spindle circuit II includes a brake input line and a brake return line. The brake input line has a spindle inflow check valve (to prevent oil backflow), with one end connected to the output end of power hydraulic line I and the other end connected to port P1. This line is fixed to the hydraulic tank. The brake return line is equipped with a spindle return check valve (to prevent oil backflow), with one end connected to port T1 and the other end connected to the hydraulic tank. This line is integrated and fixed to the hydraulic tank. This forms a centralized piping design.

[0030] The structure of the yaw brake module in yaw circuit III will be further explained below.

[0031] See Figure 1 , Figure 2 and Figure 5 The hydraulic valve block corresponding to the yaw brake module has a P2-A2 channel connecting port P2 and port A2, and a B2-P2 pipe connecting port B2 and port T2; another implementation method is... Among them, a yaw first solenoid valve 16.2 (normally open, closed when energized) is installed on the P2-A2 channel; In the B2-T2 channel section, a second yaw solenoid valve 15.2 (normally closed, energized to open) and a back pressure valve 14 (used to adjust pressure, for example, the back pressure is designed to be 20 bar) are connected in series. In the channel section between the inlet end of the second yaw solenoid valve 15.2 and the outlet end of 14, a branch is also connected in parallel, and a third yaw solenoid valve 15.3 (normally open, energized to close) is installed on this branch. Furthermore, the first yaw solenoid valve 16.2 and the second yaw solenoid valve 15.2 are connected to the PLC to achieve synchronous control - that is, both are energized or de-energized at the same time (for example, the control circuits of the first yaw solenoid valve 16.2 and the second yaw solenoid valve 15.2 are connected in parallel, and the two control circuits are on a single switch. The opening and closing of this switch realizes the energization / de-energization of both valves). (1) When the first yaw solenoid valve 16.2 and the second yaw solenoid valve 15.2 are de-energized simultaneously, the former is connected and the latter is disconnected. If the third yaw solenoid valve 15.3 is disconnected at this time, a yaw braking oil circuit is formed. (2) When the first yaw solenoid valve 16.2 and the second yaw solenoid valve 15.2 are energized simultaneously, the former is disconnected and the latter is connected. If the third yaw solenoid valve 15.3 is disconnected at this time, a yaw brake pressurized oil circuit is formed. (3) When the first yaw solenoid valve 16.2 and the second yaw solenoid valve 15.2 are energized simultaneously, the former is disconnected and the latter is connected. If the third yaw solenoid valve 15.3 is disconnected at this time, a yaw release oil circuit is formed.

[0032] It should be noted that when the first yaw solenoid valve 16.2 and the second yaw solenoid valve 15.2 are energized simultaneously (the former is disconnected while the latter is connected), if the third yaw solenoid valve 15.3 is disconnected at this time, the back pressure valve 14 will generate back pressure. This will cause the pipeline from the front end of the back pressure valve to the sequentially connected yaw solenoid valve 15.2, yaw brake, and the first yaw solenoid valve 16.2 to be under back pressure (for example, if the back pressure of the back pressure valve is set to 20 bar, then the generated back pressure will be 20 bar). It will also cause the pressure in the pipeline from the rear end of the back pressure valve to the hydraulic oil tank to be 0.

[0033] In this scheme, a return oil filter 4.2 (with a corresponding bypass valve) is also installed on the pipeline from the yaw brake to port B2 to remove impurities.

[0034] Furthermore, on the hydraulic valve block corresponding to the yaw brake module, there is a yaw pressure test point 19.2 (which can be manually installed with a pressure gauge / tester) connected to the passage section from port A2 to the first yaw solenoid valve 16.2.

[0035] Furthermore, the pipelines in yaw circuit III are designed in an integrated manner: in addition to the yaw braking module, yaw circuit III also includes a yaw input pipeline and a yaw return pipeline; the yaw input pipeline has a yaw inflow check valve (to prevent backflow), one end of which is connected to port P2 and the other end is connected to the output end of power hydraulic pipeline I, and the pipeline is fixed to the hydraulic oil tank; the yaw output pipeline has a yaw circuit check valve (to prevent backflow), one end of which is connected to port T2 and the other end is connected to the hydraulic oil tank.

[0036] It should be noted that all the valves, corresponding motors, and transmitters mentioned above are electrically connected to the PLC (this is the control logic commonly used in the hydraulic field; the specific circuit control logic can be implemented using conventional circuits in this field, and will not be elaborated here).

[0037] The above embodiments only illustrate preferred implementation methods, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can make several modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model.

Claims

1. A hydraulic control system for a brake of a wind turbine generator, comprising a power fluid line I, a main shaft circuit II, and a yaw circuit III, wherein the power fluid line I generates pressurized fluid with power, the main shaft circuit II is connected to a main shaft brake, and the yaw circuit III is connected to a yaw brake, characterized in that: The power hydraulic line I is connected to the hydraulic oil tank; The spindle circuit II includes a spindle braking module; the spindle braking module is a separate hydraulic valve block, and a valve for controlling the braking oil pressure is integrated on it. The spindle braking module is connected to the power end of the power hydraulic line I via port A1, connected to the spindle brake via port P1, and flows back to the hydraulic oil tank via port T1. The yaw brake line Ⅲ includes a yaw brake module; the yaw brake module is also a separate hydraulic valve block, and it integrates a valve for controlling yaw oil pressure. The yaw brake module is connected to the power end of the power hydraulic line Ⅰ via port A2, connected to the inlet end of the yaw brake via port A2, connected to the outlet end of the yaw brake via port B2, and flows back to the hydraulic oil tank via port T2. Each pipeline in the power hydraulic pipeline I is integrated and fixed on the hydraulic oil tank. The corresponding valves are integrated on the main shaft braking module and then fixedly installed separately. The corresponding valves are integrated on the yaw braking module and then fixedly installed separately, forming a structure in which each functional module is separated, which is conducive to maintenance.

2. The hydraulic control system for a brake in a wind turbine generator according to claim 1, characterized in that: On the hydraulic valve block corresponding to the main spindle braking module: A P1-A1 channel is provided to connect port P1 and port A1. A first spindle solenoid valve (15.1) and a spindle pressure reducing valve (5) are connected in series on the P1-A1 channel. An additional branch channel is provided on the channel section between port A1 and the spindle pressure reducing valve (5). The branch channel is connected to port T1 and has a second spindle solenoid valve (16.1). The first solenoid valve (15.1) and the second solenoid valve (16.1) of the main spindle are connected to the PLC to achieve synchronous control - that is, both are energized or de-energized at the same time. When both are energized, the former is connected and the latter is disconnected - thus forming an oil circuit for braking the main spindle. When both are de-energized at the same time, the former is disconnected and the latter is connected - thus forming an oil circuit for releasing the main spindle brake.

3. The hydraulic control system for a brake in a wind turbine generator according to claim 2, characterized in that: On the hydraulic valve block corresponding to the main spindle braking module, there are also corresponding interfaces on the channel section between port A1 and the main spindle pressure reducing valve (5), which are respectively connected to the main spindle low pressure detection switch (18.1), main spindle high pressure detection switch (18.2), main spindle pressure measuring point (19.1) and main spindle accumulator (21).

4. A hydraulic control system for a brake of a wind turbine according to claim 1 or 2, characterized in that: On the hydraulic valve block corresponding to the yaw brake module: There is a P2-A2 channel connecting port P2 and port A2, and a B2-P2 pipe connecting port B2 and port T2. A first yaw solenoid valve (16.2) is installed on the P2-A2 channel. In the B2-T2 channel section, a second yaw solenoid valve (15.2) and a back pressure valve (14) are connected in series. In the channel section between the inlet end of the second yaw solenoid valve (15.2) and the outlet end of (14), a branch is also connected in parallel, and a third yaw solenoid valve (15.3) is installed on the branch. The first yaw solenoid valve (16.2) and the second yaw solenoid valve (15.2) are connected to the PLC to achieve synchronous control - that is, they are energized or de-energized synchronously. When they are de-energized synchronously, the former is connected and the latter is disconnected. If the third yaw solenoid valve (15.3) is disconnected at this time, a yaw braking oil circuit is formed. When they are energized synchronously, the former is disconnected and the latter is connected. If the third yaw solenoid valve (15.3) is disconnected at this time, a yaw brake pressurized oil circuit is formed. When they are energized synchronously, the former is disconnected and the latter is connected. If the third yaw solenoid valve (15.3) is disconnected at this time, a yaw release oil circuit is formed.

5. A hydraulic control system for a brake in a wind turbine generator according to claim 4, characterized in that: On the hydraulic valve block corresponding to the yaw brake module: The yaw pressure measurement point (19.2) is also connected to the channel section from port A2 to the first yaw solenoid valve (16.2) via a corresponding interface.

6. A hydraulic control system for a brake of a wind turbine generator according to claim 1 or 4, characterized in that: The aforementioned power hydraulic pipeline I includes an electric pipeline and a manual pipeline; An electric pipeline and a manual pipeline are connected in parallel between the hydraulic cylinder and the output end of the power hydraulic line I; The electric pipeline is sequentially equipped with an electric pump (2), a power filter element (4.1), and a power check valve (7); a branch is also provided between the inlet end of the power check valve (7) and the hydraulic cylinder, and a safety valve (9) is provided on the branch; a branch is also provided between the outlet end of the power check valve (7) and the hydraulic cylinder, and an unloading valve (10) is provided on the branch. A manual pump (3) is installed on the manual pipeline.

7. A hydraulic control system for a brake in a wind turbine generator according to claim 6, characterized in that: The main spindle circuit II also includes a brake input line and a brake return line, both of which are integrated and fixed on the hydraulic oil tank; The brake input line connects port P1 to the output end of power hydraulic line I, and this line is equipped with a main shaft inflow check valve; the brake return line connects port T1 to the hydraulic oil tank, and this line is equipped with a main shaft return check valve.

8. A hydraulic control system for a brake in a wind turbine generator according to claim 6, characterized in that: The yaw circuit III also includes a yaw input line and a yaw return line, both of which are integrated and fixed on the hydraulic oil tank. The yaw input line connects port P2 to the output end of power hydraulic line I, and a yaw inflow check valve is installed on this line; the yaw return line connects port T2 to the hydraulic oil tank, and a yaw return check valve is installed on this line.

9. A hydraulic control system for a brake in a wind turbine generator according to claim 6, characterized in that: In the aforementioned power hydraulic pipeline I: The output end of the power hydraulic pipeline I is provided with a branch, which is connected to the power accumulator (6). The electric pump (2) is driven by the motor (1). The motor (1) works intermittently. When the entire system maintains oil pressure but does not need to output oil, the motor (1) stops working and the oil pressure in the system is maintained by the first accumulator. On the branch line between the power hydraulic line I and the power accumulator (6), a power pressure gauge (8) and a pressure sensor (22) are connected via corresponding interfaces; the pressure sensor (22) is electrically connected via a PLC.

Images