CN118167548A - Integrated pump valve combined control hydraulic pitch system of wind driven generator - Google Patents

Abstract

The invention relates to the technical field of hydraulic control pitch control, in particular to an integrated pump valve combined control hydraulic pitch control system of a wind driven generator, which comprises the following components: the piston rod in the hydraulic lever reciprocates to realize the opening or feathering; the pump control oil way is used for conveying hydraulic oil to the hydraulic cylinder so as to push the piston rod to act; and the valve control oil way is used for conveying hydraulic oil to the hydraulic cylinder so as to push the piston rod to act. Hydraulic oil is conveyed to the hydraulic cylinder through a pump control oil way or valve control oil to perform feathering operation or opening operation. In the process of controlling the valve-controlled oil way, normal operation or differential operation can be realized, and emergency operation feathering can be switched; in the feathering or the pitching process of the valve control oil way, the oil supplementing operation can be carried out through the pump control oil way, and the pump control oil way and the valve control oil way can be jointly opened for common control. The pump control oil circuit and the valve control oil circuit can be more flexible and quicker to perform pitch operation on the angle of the engine blade, the operation process is safe and reliable, and the pitch operation requirements under various conditions can be met.

Description

Integrated pump valve combined control hydraulic pitch system of wind driven generator

Technical Field

The invention relates to the technical field of hydraulic control variable pitch, in particular to an integrated pump valve combined control hydraulic variable pitch system of a wind driven generator.

Background

The wind power pitch system is a system for controlling the rotation of blades, changing the pitch angle, ensuring the power balance of a wind generating set above the rated wind speed and ensuring the safety of the whole machine by utilizing pneumatic braking under extreme conditions. The wind power pitch system has two technical routes: the utilization rate of the hydraulic pitch system reaches more than 50% abroad, but the hydraulic pitch system is not applied in large batches in China. The hydraulic pitch scheme needs to use three main components of a hydraulic pump station, a proportional directional valve and a hydraulic cylinder; the electric pitch-changing scheme is completed by matching parts such as a servo motor driver, a storage battery pack, a speed reducer and the like, and is simpler than the electric pitch-changing scheme in theory. The reasons are as follows:

1. The hydraulic pitch system is simple in structure, high in torque and free of a speed change mechanism, and continuous adjustment of pitch angles can be achieved. The mechanisms such as a variable pitch control cabinet, a servo motor, a speed reducer and the like of the electric variable pitch system are relatively large.

2. The common problem of hydraulic pitch is hydraulic oil leakage; the components of the electric pitch system that often fail are battery pack damage, encoder damage, etc.

The hydraulic pitch scheme is theoretically better than the electric pitch scheme in the aspects of mechanism performance, system failure rate and the like, which are compared and found from the aspects of mechanism composition, structural characteristics, main failure hidden danger and the like.

At present, the wind power industry has two major development directions: firstly, the wind turbine generator is large-sized, and secondly, the proportion of offshore wind power is continuously improved. Whether the wind turbine generator is large-sized or the specific gravity of the offshore wind power is increased, the wind power pitch system is required to be higher, and the hydraulic pitch system has a development space.

Therefore, the existing hydraulic pitch system should be adjusted and optimized, the flexibility and the reliability of the hydraulic pitch system are improved, the pitch of the wind driven generator is promoted, the utilization of wind energy is improved, a more reasonable technical scheme is required to be provided, and the technical problems in the prior art are solved.

Disclosure of Invention

At least to overcome the defects mentioned in the above, the invention provides an integrated pump valve combined control hydraulic pitch system of a wind driven generator, which is more integrated compared with the distributed layout at the present stage by adjusting a hydraulic system, greatly reduces external pipelines, reduces leakage risk, adopts a mode of pump control and valve control combined control, can select various pitch control modes according to working conditions, saves more energy, reduces the pitch energy consumption of a fan and improves the wind energy utilization rate of the fan.

In order to achieve the above object, the grouting system disclosed by the invention can adopt the following technical scheme:

An integrated pump valve combined control hydraulic pitch system of a wind driven generator, comprising:

The hydraulic cylinders are in a plurality of numbers, and piston rods in the hydraulic bars reciprocate to realize the opening or feathering;

The pump control oil way is used for conveying hydraulic oil to the hydraulic cylinder to push the piston rod to act, and comprises a first pump control oil way and a second pump control oil way, the first pump control oil way is communicated to a rodless cavity of the hydraulic cylinder and used for pushing the piston rod out of the hydraulic cylinder, and the second pump control oil way is communicated to a rod cavity of the hydraulic cylinder and used for pushing the piston rod into the hydraulic cylinder; an oil return supply bypass is arranged between the first pump control oil way and the second pump control oil way, the oil return supply bypass is communicated with the first pump control oil way or the second pump control oil way in the pump control process, and the first pump control oil way and the second pump control oil way form an oil return supply circulation structure;

The valve control oil way is used for conveying hydraulic oil to the hydraulic cylinder to push the piston rod to act and comprises a valve control main way provided with an energy accumulator, and the valve control main way supplies oil to a rod cavity or a rodless cavity of the hydraulic cylinder through a proportional valve; the valve control main circuit is provided with a first valve control branch circuit and a second valve control branch circuit, the first valve control branch circuit is communicated with the first pump control oil circuit in a single direction from the valve control main circuit, and the second valve control branch circuit is communicated with the valve control main circuit in a single direction from the second pump control oil circuit; the automatic oil return device also comprises an independent oil return pipeline which is communicated with the oil supply and return bypass in one direction from the proportional valve so as to realize oil return;

and the electromagnetic valves are respectively used for controlling the on-off of the first pump control oil way, the second pump control oil way, the oil supply and return bypass, the first valve control branch and the second valve control branch.

In the pump valve combined control hydraulic pitch system disclosed by the invention, hydraulic oil is conveyed to a hydraulic cylinder through a pump control oil way or valve control oil to perform feathering operation or pitch operation; in the process of controlling feathering or opening the propeller by the valve-controlled oil way, a normal operation mode or a differential operation mode can be set, and an emergency operation mode can be switched to feathering; in the feathering or the pitching process of the valve control oil way, the oil supplementing operation can be carried out through the pump control oil way, and the pump control oil way and the valve control oil way can be jointly opened to jointly control the hydraulic cylinder.

Further, in the present invention, the circulation structure formed by the pump-controlled oil path may be used for oil delivery through a plurality of oil pumps, or may be used for circulation oil delivery through a single oil pump, and the structure is not limited only, but is optimized and one of the possible choices is provided herein: the first pump control oil way and the second pump control oil way are respectively communicated with the oil ports of the bidirectional oil pump, oil is supplied to the first pump control oil way and oil is returned to the second pump control oil way when the bidirectional oil pump rotates positively, and oil is supplied to the second pump control oil way and oil is returned to the first pump control oil way when the bidirectional oil pump rotates reversely; meanwhile, the bidirectional oil pump also discharges oil unidirectionally to the oil supply and return pipeline through the regulating branch. When the scheme is adopted, two oil ports of the bidirectional oil pump can both supply oil and return oil, the working states of the first pump control oil way and the second pump control oil way are combined to switch oil supply or oil return, the adjusting branch is a pipeline extending from the bidirectional oil pump to the oil supply and return pipeline and used for conveying hydraulic oil to the oil supply and return pipeline for buffering and releasing pressure when the oil pressure in the bidirectional oil pump is too high, the adjusting branch is provided with the one-way valve, and when the hydraulic oil pressure of the adjusting branch exceeds the threshold value of the one-way valve, part of hydraulic oil is conveyed from the adjusting branch to the oil supply and return pipeline.

Further, in the present invention, the composition of the oil supply and return line can take a variety of forms, which are not limited to the only one, and one of the possible choices is here and optimized and proposed: the oil supply and return bypass is provided with an oil tank, a temperature transmitter and a first pressure transmitter, the front end of the oil supply and return bypass is connected to the first pump control oil way and is controlled to be on-off by a normally closed first electromagnetic valve, and the rear end of the oil supply and return bypass is connected to the second pump control oil way and is controlled to be on-off by a normally closed second electromagnetic valve. When the scheme is adopted, the oil tank stores hydraulic oil and supplies oil outwards; the temperature transmitter and the first pressure transmitter are configured to detect the temperature and pressure of hydraulic oil in the oil supply return bypass. Because the first electromagnetic valve and the second electromagnetic valve are arranged, the communication between the oil supply and return bypass and the first pump control oil way or the second pump control oil way can be controlled, and the oil supply and return bypass is communicated with both the pump control oil ways under the normal state, and is only communicated with one of the two pump control oil ways when feathering or opening operation is carried out.

Further, the temperature of the hydraulic oil will gradually rise during the circulation process, and in order to ensure that the temperature of the hydraulic oil is within a normal range and realize stable circulation, a corresponding cooling structure should be provided, and specifically, the cooling structure may be realized by adopting various schemes, which are not limited only, and optimization is performed and one of the possible choices is proposed herein: the circulating filter cooling structure comprises a circulating bypass which is arranged and extends from the first pump control oil way or the second pump control oil way, a normally open third electromagnetic valve is arranged on the circulating bypass to control the on-off of the bypass, and the circulating bypass is further connected with the filter and the cooler and is communicated to the oil supply and return bypass. When the scheme is adopted, the circulated hydraulic oil is subjected to purification treatment and cooling treatment after the action of the filter and the cooler in the oil return process, so that the subsequent recycling is facilitated.

Still further, when valve control is performed, the hydraulic oil stored in the accumulator is limited, when the hydraulic oil function is insufficient, the hydraulic oil needs to be supplemented to promote the oil supply of the accumulator to control, the supplementing of the hydraulic oil can be realized through a pump control oil way, and the optimization is performed and one of the feasible choices is provided: the hydraulic oil pump further comprises an oil supplementing structure, wherein the oil supplementing structure comprises an oil supplementing bypass which is arranged and extends from the first pump control oil way and/or the second pump control oil way, and the oil supplementing bypass is communicated to the valve control main way in a one-way manner. When the scheme is adopted, the one-way valve is arranged on the oil supplementing bypass, and when the pressure of hydraulic oil of the oil supplementing bypass reaches the set pressure value of the one-way valve, the oil is supplemented to the valve control main path.

Further, when the hydraulic oil pressure in the system is too high, the overflow should be performed to reduce the pressure, which can be achieved specifically by various schemes, which are not limited only, and optimization is performed and one of possible choices is proposed herein: the hydraulic oil system further comprises a first overflow structure, a second overflow structure and a valve control main circuit, wherein the first overflow structure is used for safely overflowing the hydraulic oil of the first pump control oil circuit and/or the second pump control oil circuit and/or the valve control main circuit; the first overflow structure comprises a first overflow pipeline extending from the valve control main pipeline to the independent oil return pipeline, and a first overflow valve is arranged on the first overflow pipeline. When the scheme is adopted, the first pump control oil way, the second pump control oil way and the valve control main way can safely release pressure through the first overflow valve.

Still further, for different control modes, the pressure values of the safety overflow are different, so the overflow structure should be adjusted to meet different safety overflow requirements, and various schemes can be adopted, which are not limited only, and optimization is performed and one of the possible choices is proposed: the second overflow structure is used for safely overflowing the hydraulic oil discharged by the first pump control oil way or the rodless cavity; the second overflow structure comprises a second overflow pipeline extending from the first pump control pipeline to the independent oil return pipeline, and a second overflow valve is arranged on the second overflow pipeline. By adopting the scheme, the safety overflow can be carried out when the pressure value of the first pump control oil way reaches the set value.

Furthermore, when the control is performed through the valve control oil way, the proportional valve can be adopted to convey hydraulic oil to the hydraulic cylinder for bidirectional control, and the second valve control branch can be used for differential feathering in the feathering operation process so as to improve the feathering pressure; the emergency feathering operation can also be directly carried out through the first valve control branch; when controlled by a proportional valve, an optimization can be made to propose one possible choice as follows: the proportional valve is communicated with the rodless cavity through a first proportional valve branch, and is communicated with the rod cavity through a second proportional valve branch, and the first proportional valve branch and the second proportional valve branch are respectively and correspondingly provided with an eighth normally open electromagnetic valve and a ninth normally open electromagnetic valve. When the scheme is adopted, the first proportional valve branch and the second proportional valve branch are provided with the one-way valves.

Further, on-off control and pressure monitoring are performed on the first pump control oil way and the second pump control oil way, so that communication cooperation control of the whole system can be realized by adopting various schemes, and optimization is performed and one of feasible choices is provided: a normally open fourth electromagnetic valve and a second pressure transmitter are arranged on the first pump control oil way; and a normally closed fifth electromagnetic valve and a third pressure transmitter are arranged on the second pump control oil way. When the scheme is adopted, the pressure on the pump control oil path is correspondingly detected through the pressure transmitter, the on-off state of the pump control oil path where the pressure transmitter is correspondingly controlled through the electromagnetic valve is correspondingly controlled, and the electromagnetic valve is switched to the on-off state after power is obtained.

Further, in the valve control process, the on-off of the valve control branch affects the valve control process, and the on-off setting of the valve control branch is not limited only, and is optimized and one of the possible choices is provided herein: the first valve control branch is provided with a normally closed seventh electromagnetic valve, and the second valve control branch is provided with a normally open sixth electromagnetic valve. When the scheme is adopted, the electromagnetic valve correspondingly controls the on-off state of the valve control branch circuit, and the on-off state is switched after power is obtained.

Compared with the prior art, the technical scheme disclosed by the invention has the following partial beneficial effects:

according to the invention, through setting the pump control oil way and the valve control oil way and carrying out linkage control, the pitch control operation on the blade angle of the wind generating set can be more flexible and quicker, the operation process is safe and reliable, and the pitch control operation requirements under various conditions can be met.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are needed in the embodiments will be briefly described below, it being understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered limiting the scope, and other related drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a schematic view of a hydraulic pitch system in an initial state.

Fig. 2 is a schematic diagram of feathering operation by bi-directional oil pump control.

Fig. 3 is a schematic diagram of a pitch operation by bi-directional oil pump control.

FIG. 4 is a schematic illustration of feathering operations with accumulator control.

FIG. 5 is a schematic illustration of a pitch operation controlled by an accumulator.

FIG. 6 is a schematic illustration of differential feathering operation with accumulator control.

Fig. 7 is a schematic illustration of an emergency feathering operation by accumulator control.

Fig. 8 is a schematic diagram of a feathering by a bi-directional oil pump.

Fig. 9 is a schematic diagram of oil replenishment and opening by a bi-directional oil pump.

FIG. 10 is a schematic illustration of feathering by bi-directional oil pump and accumulator coordinated control.

FIG. 11 is a schematic illustration of a bi-directional oil pump and accumulator coordinated control for pitch.

Fig. 12 is a schematic diagram of hydraulic oil circulation filtration cooling by a bi-directional oil pump.

In the above figures, the meaning of each label is:

1. A servo motor; 2. a bidirectional oil pump; 3. a first pump control oil path; 4. a return oil supply bypass; 5. a first electromagnetic valve; 6. a first pressure transmitter; 7. a temperature transmitter; 8. adjusting the branch; 9. a cooler; 10. a filter; 11. an oil tank; 12. a second electromagnetic valve; 13. a second pump control oil path; 14. a fourth electromagnetic valve; 15. an oil supplementing bypass; 16. a first overflow valve; 17. a circulation bypass; 18. a third electromagnetic valve; 19. a valve control main path; 20. an accumulator; 21. a second overflow valve; 22. a fifth electromagnetic valve; 23. a seventh electromagnetic valve; 24. a first valve control branch; 25. a proportional valve; 26. a sixth electromagnetic valve; 27. a second pressure transmitter; 28. an eighth electromagnetic valve; 29. a hydraulic cylinder; 30. a piston rod; 31. a ninth electromagnetic valve; 32. a first proportional valve branch; 33. a second proportional valve branch; 34. a third transmitter; 35. a second valve controlled branch.

Detailed Description

The invention is further illustrated by the following description of specific embodiments in conjunction with the accompanying drawings.

Aiming at the defects in the prior art, the technical scheme provided by the invention can solve the defects in the prior art and ensure that the pitch process is safer and more reliable.

Examples

As shown in fig. 1, this embodiment provides a wind-driven generator integrated pump valve allies oneself with accuse hydraulic pressure becomes oar system, aims at adjusting the angle of paddle through this becomes oar system, can carry out the nimble collocation of valve accuse and pump accuse, not only improves the efficiency of control, also improves the fail safe nature of control process.

As the pitch system provided in the present embodiment, one of its structures includes:

the hydraulic cylinders 29 are several in number, and piston rods 30 in the hydraulic bars reciprocate to realize the opening or feathering.

Preferably, the piston rod 30 of the hydraulic cylinder 29 acts in conjunction with the paddles to angularly deflect the paddles. And the number of hydraulic cylinders 29 provided in this embodiment is two, the number of hydraulic cylinders 29 provided in other embodiments may be one or more hydraulic cylinders 29.

As the pitch system provided in this embodiment, the second structure includes:

The pump control oil way is used for conveying hydraulic oil to the hydraulic cylinder 29 to push the piston rod 30 to act, and comprises a first pump control oil way 3 and a second pump control oil way 13, wherein the first pump control oil way 3 is communicated to a rodless cavity of the hydraulic cylinder 29 and is used for pushing the piston rod 30 out of the hydraulic cylinder 29, and the second pump control oil way 13 is communicated to a rod cavity of the hydraulic cylinder 29 and is used for pushing the piston rod 30 into the hydraulic cylinder 29; an oil supply and return bypass 4 is arranged between the first pump control oil way 3 and the second pump control oil way 13, the oil supply and return bypass 4 is communicated with the first pump control oil way 3 or the second pump control oil way 13 in the pump control process, and the first pump control oil way 3 and the second pump control oil way 13 form an oil supply and return circulation structure.

In this embodiment, the circulation structure formed by the pump-controlled oil paths may be used for oil delivery through a plurality of oil pumps, or may be used for circulation oil delivery through a single oil pump, and the structure is not limited only, but the present embodiment is optimized and adopts one of the possible choices: the first pump control oil way 3 and the second pump control oil way 13 are respectively communicated with the oil ports of the bidirectional oil pump 2, oil is supplied to the first pump control oil way 3 and oil is returned to the second pump control oil way 13 when the bidirectional oil pump 2 rotates forwards, and oil is supplied to the second pump control oil way 13 and the oil is returned to the first pump control oil way 3 when the bidirectional oil pump 2 rotates backwards; meanwhile, the bidirectional oil pump 2 also discharges oil unidirectionally to the oil supply and return pipeline through the adjusting branch 8. When the scheme is adopted, two oil ports of the bidirectional oil pump 2 can both supply oil and return oil, the working states of the first pump control oil way 3 and the second pump control oil way 13 are combined to switch oil supply or oil return, the adjusting branch 8 is a pipeline extending from the bidirectional oil pump 2 to the oil supply and return pipeline and is used for conveying hydraulic oil to the oil supply and return pipeline for buffering and releasing pressure when the oil pressure in the bidirectional oil pump 2 is too high, the adjusting branch 8 is provided with a one-way valve, and when the hydraulic oil pressure of the adjusting branch 8 exceeds the threshold value of the one-way valve, part of hydraulic oil is conveyed from the adjusting branch 8 to the oil supply and return pipeline.

Preferably, the bidirectional oil pump 2 is driven by a servo motor 1 in the present embodiment.

In this embodiment, the composition of the oil supply and return line may adopt various schemes, which are not limited to the above, and one of the possible options is optimized and adopted in this embodiment: the oil supply and return bypass 4 is provided with an oil tank 11, a temperature transmitter 7 and a first pressure transmitter 6, the front end of the oil supply and return bypass 4 is connected to the first pump control oil way 3 and is controlled to be on-off by a normally closed first electromagnetic valve 5, and the rear end of the oil supply and return bypass 4 is connected to the second pump control oil way 13 and is controlled to be on-off by a normally closed second electromagnetic valve 12. With such a scheme, the oil tank 11 stores hydraulic oil and supplies the oil to the outside; the temperature transmitter 7 and the first pressure transmitter 6 are used to detect the hydraulic oil temperature and pressure in the oil supply return bypass 4. Due to the arrangement of the first electromagnetic valve 5 and the second electromagnetic valve 12, the communication between the oil supply and return bypass 4 and the first pump control oil way 3 or the second pump control oil way 13 can be controlled, and the oil supply and return bypass 4 is communicated with both the two pump control oil ways in a normal state, and is only communicated with one of the two pump control oil ways when feathering or pitching operation is carried out.

The temperature of the hydraulic oil will gradually rise in the circulation process, and in order to ensure that the temperature of the hydraulic oil is within a normal range and realize stable circulation, a corresponding cooling structure should be provided, and the hydraulic oil can be specifically realized by adopting various schemes, which are not limited only, and the hydraulic oil is optimized and one of the feasible choices is adopted in the embodiment: the circulating filter cooling structure comprises a circulating bypass 17 which is arranged and extends from the first pump control oil way 3 or the second pump control oil way 13, a normally open third electromagnetic valve 18 is arranged on the circulating bypass 17 to control the on-off of the bypass, and the circulating bypass 17 is also connected with the filter 10 and the cooler 9 and is communicated to the oil supply and return bypass 4. By adopting the scheme, the circulated hydraulic oil is subjected to purification treatment and cooling treatment after passing through the filter 10 and the cooler 9 in the oil return process, so that the subsequent circulation and use are facilitated.

The on-off control and pressure monitoring are performed on the first pump control oil way 3 and the second pump control oil way 13 so as to facilitate the communication cooperation control of the whole system, and various schemes can be adopted to realize the on-off control, so that the on-off control is optimized and one of the feasible choices is provided: the first pump control oil way 3 is provided with a normally open fourth electromagnetic valve 14 and a second pressure transmitter 27; the second pump control oil way 13 is provided with a normally closed fifth electromagnetic valve 22 and a third pressure transmitter. When the scheme is adopted, the pressure on the pump control oil path is correspondingly detected through the pressure transmitter, the on-off state of the pump control oil path where the pressure transmitter is correspondingly controlled through the electromagnetic valve is correspondingly controlled, and the electromagnetic valve is switched to the on-off state after power is obtained.

As the pitch system provided in this embodiment, a third structure thereof includes:

The valve control oil way is used for conveying hydraulic oil to the hydraulic cylinder 29 to push the piston rod 30 to act, and comprises a valve control main way 19 provided with an energy accumulator 20, wherein the valve control main way 19 supplies oil to a rod cavity or a rodless cavity of the hydraulic cylinder 29 through a proportional valve 25; the valve control main path 19 is provided with a first valve control branch path 24 and a second valve control branch path 35, the first valve control branch path 24 is communicated with the first pump control oil path 3 in a one-way from the valve control main path 19, and the second valve control branch path 35 is communicated with the valve control main path 19 in a one-way from the second pump control oil path 13; and an independent oil return pipeline is further included, and the independent oil return pipeline is communicated with the oil supply and return bypass 4 in a unidirectional way from the proportional valve 25 so as to realize oil return.

When the control is performed through the valve control oil way, the proportional valve 25 can be used for conveying hydraulic oil to the hydraulic cylinder 29 for bidirectional control, and the second valve control branch 35 can be used for differential feathering in the feathering operation process so as to improve the feathering pressure; emergency feathering operations may also be performed directly through the first valve control branch 24; when controlled by the proportional valve 25, an optimization can be performed and one possible option is as follows: the proportional valve 25 is communicated with a rodless cavity through a first proportional valve branch 32, and is communicated with a rod cavity through a second proportional valve branch 33, and the first proportional valve branch 32 and the second proportional valve branch 33 are respectively and correspondingly provided with a normally open eighth electromagnetic valve 28 and a normally open ninth electromagnetic valve 31. With such a solution, the first proportional valve branch 32 and the second proportional valve branch 33 are provided with check valves.

In the valve control process, the on-off of the valve control branch affects the valve control process, the on-off setting of the valve control branch is not limited only, and the embodiment is optimized and adopts one of the possible choices: the first valve control branch 24 is provided with a normally closed seventh electromagnetic valve 23, and the second valve control branch 35 is provided with a normally open sixth electromagnetic valve 26. When the scheme is adopted, the electromagnetic valve correspondingly controls the on-off state of the valve control branch circuit, and the on-off state is switched after power is obtained.

When the valve control is performed, the hydraulic oil stored in the accumulator 20 is limited, and when the hydraulic oil is insufficient in function, the hydraulic oil needs to be supplemented to promote the oil supply of the accumulator 20 to control, and the supplementing of the hydraulic oil can be realized through a pump control oil way, so that the hydraulic oil is optimized and one of feasible choices is adopted in the embodiment: and the oil supplementing structure comprises an oil supplementing bypass 15 which is arranged and extends from the first pumping oil circuit 3 and/or the second pumping oil circuit 13, and the oil supplementing bypass 15 is communicated with the valve control main circuit 19 in one way. When the scheme is adopted, the one-way valve is arranged on the oil supplementing bypass 15, and when the pressure of the hydraulic oil of the oil supplementing bypass 15 reaches the set pressure value of the one-way valve, the oil is supplemented to the valve control main path 19.

When the hydraulic oil pressure in the system is too high, the overflow should be performed to reduce the pressure, and the overflow can be specifically realized through various schemes, which are not limited solely, and the embodiment is optimized and adopts one of the possible choices: the hydraulic oil pump further comprises a first overflow structure, which is used for safely overflowing the hydraulic oil of the first pump control oil way 3, the second pump control oil way 13 and/or the valve control main way 19; the first overflow arrangement comprises a first overflow line extending from the valve control main line 19 to an independent return line, the first overflow line being provided with a first overflow valve 16. With the adoption of the scheme, the first pumping oil circuit 3, the second pumping oil circuit 13 and the valve control main circuit 19 can safely release pressure through the first overflow valve 16.

For different control modes, the pressure values of the safety overflow are different, so that the overflow structure should be adjusted to meet different safety overflow requirements, and various different schemes can be adopted, which are not limited solely, and the embodiment optimizes and adopts one of the feasible choices: the hydraulic oil pump further comprises a second overflow structure which is used for safely overflowing the hydraulic oil discharged by the first pump control oil way 3 or the rodless cavity; the second overflow structure comprises a second overflow line extending from the first pumping line to the separate return line, the second overflow line being provided with a second overflow valve 21. By adopting the scheme, the safety overflow can be carried out when the pressure value of the first pump control oil way 3 reaches the set value.

The pump valve combined control hydraulic pitch system disclosed above is used for conveying hydraulic oil to the hydraulic cylinder 29 through a pump control oil way or valve control oil so as to perform feathering operation or pitch operation; in the process of controlling feathering or opening the propeller by the valve control oil way, a normal operation mode or a differential operation mode can be set, and the emergency operation mode can be switched to feathering by the pump control oil way; in the feathering or pitching process of the valve control oil way, the oil supplementing operation can be performed through the pump control oil way, and the hydraulic cylinder 29 can be controlled by jointly opening the pump control oil way and the valve control oil way.

The above description illustrates the pitch control system provided by the present invention, and when the pitch control system operates according to the above description, the following various pitch operations can be implemented:

1. pump control feathering

As shown in fig. 2, when switching from the initial state to the pump feathering state, the first solenoid valve 5 is electrically disconnected, the fourth solenoid valve 14 is electrically closed, and the seventh solenoid valve 23 is electrically disconnected.

Under the working condition, the bidirectional oil pump 2 operates and supplies oil to the first pumping oil way 3, a piston rod 30 is pushed out of a hydraulic cylinder 29 after hydraulic oil enters a rodless cavity, and when the oil pressure of the first pumping oil way 3 is too high, the pressure is relieved from the first overflow valve 16 and the second overflow valve 21; the hydraulic oil having the rod chamber flows back from the second pump control oil passage 13 to the bidirectional oil pump 2 to realize circulation, and is depressurized from the first relief valve 16 when the oil pressure of the second pump control oil passage 13 is excessively high.

2. Pump control opening paddle

As shown in fig. 3, when the pump control feathering state is switched from the initial state, the second electromagnetic valve 12 is electrically disconnected, the fourth electromagnetic valve 14 is electrically closed, and the seventh electromagnetic valve 23 is electrically disconnected.

Under the working condition, the bidirectional oil pump 2 operates and supplies oil to the second pump control oil path 13, a piston rod 30 is pushed into a hydraulic cylinder 29 after hydraulic oil enters a rod cavity, and when the oil pressure of the second pump control oil path 13 is too high, the pressure is relieved from the first overflow valve 16; the hydraulic oil without the rod cavity flows back to the bidirectional oil pump 2 from the first pump control oil way 3 to realize circulation, and the pressure of the first pump control oil way 3 is relieved from the second overflow valve 21 when the oil pressure is too high.

3. Valve-controlled feathering

As shown in fig. 4, when the valve control feathering state is switched from the initial state, the proportional valve 25 is electrically switched to the right feathering operation position, the fifth solenoid valve 22 and the seventh solenoid valve 23 are electrically disconnected, and the eighth solenoid valve 28 and the ninth solenoid valve 31 are electrically closed.

Under the working condition, the accumulator 20 operates and supplies oil to the valve control main circuit 19, hydraulic oil enters the rodless cavity through the first proportional valve branch circuit 32 and pushes the piston rod 30 out of the hydraulic cylinder 29, when the oil pressure of the valve control main circuit 19 is too high, the pressure is released from the first overflow valve 16, and when the oil pressure of the first proportional valve branch circuit 32 is too high, the pressure is released from the second overflow valve 21; the hydraulic oil with the rod cavity flows back to the independent oil return pipeline from the second proportional valve branch circuit 33 to realize circulation.

4. Valve-controlled opening paddle

As shown in fig. 5, when the valve control is switched from the initial state to the valve control opening state, the proportional valve 25 is electrically switched to the left side opening operation position, the fifth solenoid valve 22 and the seventh solenoid valve 23 are electrically disconnected, and the eighth solenoid valve 28 and the ninth solenoid valve 31 are electrically closed.

Under the working condition, the accumulator 20 operates and supplies oil to the valve control main path 19, hydraulic oil enters a rod cavity through the second proportional valve branch path 33 and pushes the piston rod 30 into the hydraulic cylinder 29, and when the oil pressure of the valve control main path 19 is too high, the pressure is relieved from the first overflow valve 16; the hydraulic oil of the rodless cavity flows back to the independent oil return pipeline from the first proportional valve branch 32 to realize circulation, and the pressure of the hydraulic oil of the first proportional valve branch 32 is relieved from the second overflow valve 21 when the oil pressure is too high.

5. Valve-controlled differential feathering

As shown in fig. 6, when the valve-controlled differential feathering state is switched from the initial state, the proportional valve 25 is electrically switched to the right feathering operation position, the fifth solenoid valve 22 and the seventh solenoid valve 23 are electrically disconnected, and the sixth solenoid valve 26, the eighth solenoid valve 28 and the ninth solenoid valve 31 are electrically closed.

Under the working condition, the accumulator 20 operates and supplies oil to the valve control main circuit 19, hydraulic oil enters the rodless cavity through the first proportional valve branch circuit 32 and pushes the piston rod 30 out of the hydraulic cylinder 29, when the oil pressure of the valve control main circuit 19 is too high, the pressure is released from the first overflow valve 16, and when the oil pressure of the first proportional valve branch circuit 32 is too high, the pressure is released from the second overflow valve 21; the hydraulic oil with the rod cavity flows back to the independent oil return pipeline from the second proportional valve branch circuit 33 to realize circulation, and meanwhile, the hydraulic oil part with the rod cavity flows back to the valve control main circuit 19 from the second valve control branch circuit 35 and reenters the proportional valve 25 to be hydraulically driven.

6. Valve control emergency feathering

As shown in fig. 7, the valve control emergency feathering can be performed in the initial state.

Under the working condition, the accumulator 20 operates and supplies oil to the valve control main path 19, hydraulic oil enters the rodless cavity through the first valve control branch path 24 and pushes the piston rod 30 out of the hydraulic cylinder 29, when the oil pressure of the valve control main path 19 is too high, the pressure is released from the first overflow valve 16, and when the oil pressure of the first valve control branch path 24 is too high, the pressure is released from the second overflow valve 21; the hydraulic oil having the rod chamber flows back from the second pump control oil passage 13 to the oil supply and return bypass 4, and is depressurized from the first relief valve 16 when the oil pressure of the second pump control oil passage 13 is excessively high.

7. Valve-controlled oil-supplementing variable pitch

As shown in fig. 8 and 9, oil can be replenished under the working conditions of valve control feathering, valve control opening, valve control difference feathering and valve control emergency feathering.

Specifically, the servo motor 1 is started, the first electromagnetic valve 5 and the fifth electromagnetic valve 22 are electrically closed, and hydraulic oil is supplemented to the valve control main circuit 19 through the first pump control oil circuit 3. Or the servo motor 1 is started, the second electromagnetic valve 12 and the fifth electromagnetic valve 22 are electrically closed, and hydraulic oil is supplemented to the valve control main circuit 19 through the second pump control oil circuit 13.

8. Pump valve combined control feathering

As shown in fig. 10, when the pump valve combined control feathering state is switched from the initial state, the proportional valve 25 is electrically switched to the right feathering operation position, the first electromagnetic valve 5 and the seventh electromagnetic valve 23 are electrically disconnected, and the fourth electromagnetic valve 14 and the eighth electromagnetic valve 28 are electrically closed.

Under the working condition, the accumulator 20 operates and supplies oil to the valve control main circuit 19, the hydraulic oil enters the rodless cavity through the first proportional valve branch circuit 32 and pushes the piston rod 30 out of the hydraulic cylinder 29, and when the oil pressure of the valve control main circuit 19 is too high, the pressure is relieved from the first overflow valve 16; the bidirectional oil pump 2 operates and supplies oil to the first pumping oil path 3, and when the oil pressure of the first pumping oil path 3 is too high, the pressure is relieved from the first relief valve 16 and the second relief valve 21; the hydraulic oil with the rod cavity flows back to the independent oil return pipeline from the second proportional valve branch circuit 33 and flows back to the bidirectional oil pump 2 from the second pump control oil circuit 13 to realize circulation.

9. Pump valve combined control opening paddle

As shown in fig. 11, when the pump valve combined control paddle-opening state is switched from the initial state, the proportional valve 25 is electrically switched to the right feathering operation position, the second electromagnetic valve 12 and the seventh electromagnetic valve 23 are electrically disconnected, and the fourth electromagnetic valve 14 and the ninth electromagnetic valve 31 are electrically closed.

Under the working condition, the accumulator 20 operates and supplies oil to the valve control main path 19, hydraulic oil enters a rod cavity through the second proportional valve branch path 33 and pushes the piston rod 30 into the hydraulic cylinder 29, and when the oil pressure of the valve control main path 19 is too high, the pressure is relieved from the first overflow valve 16; the bidirectional oil pump 2 operates and supplies oil to the second pump control oil path 13, hydraulic oil of the rodless cavity is decompressed from the first relief valve 16 when the oil pressure of the second pump control oil path 13 is too high, flows back to the independent oil return pipeline from the first proportional valve branch 32, and flows back to the bidirectional oil pump 2 from the first pump control oil path 3 to realize circulation, and is decompressed from the second relief valve 21 when the oil pressure of the first pump control oil path 3 is too high.

10. Hydraulic oil circulating, filtering and cooling

As shown in fig. 12, when the hydraulic oil circulation filtration cooling state is switched from the initial state, the proportional valve 25 is electrically switched to the right feathering operation position, the second solenoid valve 12 and the fifth solenoid valve 22 are electrically disconnected, and the third solenoid valve 18 is electrically closed.

Under this condition, the bidirectional oil pump 2 is operated and supplies oil to the second pump control oil passage 13 and enters the circulation bypass 17, the independent oil return pipe, and the circulation bypass is provided to form a circulation, during which the filter 10 and the cooler 9 filter and cool the hydraulic oil.

The above is an embodiment exemplified in this example, but this example is not limited to the above-described alternative embodiments, and a person skilled in the art may obtain various other embodiments by any combination of the above-described embodiments, and any person may obtain various other embodiments in the light of this example. The above detailed description should not be construed as limiting the scope of the present embodiments, which is defined in the appended claims.

Claims (10)

1. An integrated pump valve combined control hydraulic pitch system of a wind driven generator, which is characterized by comprising:

the hydraulic cylinders (29) are in a plurality of numbers, and piston rods (30) in the hydraulic bars reciprocate to realize the opening or feathering;

The hydraulic control system comprises a hydraulic cylinder (29), a pump control oil circuit and a piston rod (30), wherein the hydraulic cylinder is used for conveying hydraulic oil to the hydraulic cylinder (29) to push the piston rod (30) to act, the pump control oil circuit comprises a first pump control oil circuit (3) and a second pump control oil circuit (13), the first pump control oil circuit (3) is communicated to a rodless cavity of the hydraulic cylinder (29) and is used for pushing the piston rod (30) out of the hydraulic cylinder (29), and the second pump control oil circuit (13) is communicated to a rod cavity of the hydraulic cylinder (29) and is used for pushing the piston rod (30) into the hydraulic cylinder (29); an oil supply and return bypass (4) is arranged between the first pump control oil way (3) and the second pump control oil way (13), the oil supply and return bypass (4) is communicated with the first pump control oil way (3) or the second pump control oil way (13) in the pump control process, and the first pump control oil way (3) and the second pump control oil way (13) form an oil supply and return circulation structure;

The valve control oil way is used for conveying hydraulic oil to the hydraulic cylinder (29) to push the piston rod (30) to act and comprises a valve control main way (19) provided with an energy accumulator (20), and the valve control main way (19) supplies oil to a rod cavity or a rodless cavity of the hydraulic cylinder (29) through a proportional valve (25); a first valve control branch (24) and a second valve control branch (35) are arranged on the valve control main path (19), the first valve control branch (24) is unidirectionally communicated with the first pump control oil path (3) from the valve control main path (19), and the second valve control branch (35) is unidirectionally communicated with the valve control main path (19) from the second pump control oil path (13); the automatic oil return device also comprises an independent oil return pipeline which is communicated with the oil supply and return bypass (4) in one way from the proportional valve (25) so as to realize oil return;

the electromagnetic valves are used for controlling the on-off of the first pump control oil way (3), the second pump control oil way (13), the oil supply and return bypass (4), the first valve control branch (24) and the second valve control branch (35) respectively.

2. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the first pump control oil way (3) and the second pump control oil way (13) are respectively communicated with the oil ports of the bidirectional oil pump (2), oil is supplied to the first pump control oil way (3) and oil is returned to the second pump control oil way (13) when the bidirectional oil pump (2) rotates positively, and oil is supplied to the second pump control oil way (13) and the oil is returned to the first pump control oil way (3) when the bidirectional oil pump (2) rotates reversely; meanwhile, the bidirectional oil pump (2) also discharges oil unidirectionally to the oil supply and return pipeline through the adjusting branch (8).

3. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the oil supply and return bypass (4) on be provided with oil tank (11), temperature transmitter (7) and first pressure transmitter (6), and the front end of oil supply and return bypass (4) is connected to first pump accuse oil circuit (3) and is controlled the break-make by normally closed first solenoid valve (5), the rear end of oil supply and return bypass (4) is connected to second pump accuse oil circuit (13) and is controlled the break-make by normally closed second solenoid valve (12).

4. The wind turbine integrated pump valve controlled hydraulic pitch system of claim 3, wherein: the circulating filter cooling structure comprises a circulating bypass (17) which is arranged and extends from the first pump control oil way (3) or the second pump control oil way (13), a normally open third electromagnetic valve (18) is arranged on the circulating bypass (17) to control the on-off of the bypass, and the circulating bypass (17) is further connected with the filter (10) and the cooler (9) and is communicated to the oil supply and return bypass (4).

5. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the hydraulic oil filling system further comprises an oil filling structure, wherein the oil filling structure comprises an oil filling bypass (15) which is arranged and extends from the first pump control oil way (3) and/or the second pump control oil way (13), and the oil filling bypass (15) is communicated to the valve control main way (19) in one way.

6. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the hydraulic oil control system further comprises a first overflow structure, a second overflow structure and a third overflow structure, wherein the first overflow structure is used for safely overflowing the hydraulic oil of the first pump control oil way (3), the second pump control oil way (13) and/or the valve control main way (19); the first overflow structure comprises a first overflow pipeline extending from the valve control main pipeline (19) to the independent oil return pipeline, and a first overflow valve (16) is arranged on the first overflow pipeline.

7. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the hydraulic oil pump further comprises a second overflow structure which is used for safely overflowing the hydraulic oil discharged by the first pump control oil way (3) or the rodless cavity; the second overflow structure comprises a second overflow pipeline extending from the first pump control pipeline to the independent oil return pipeline, and a second overflow valve (21) is arranged on the second overflow pipeline.

8. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the proportional valve (25) is communicated with the rodless cavity through a first proportional valve branch (32), and is communicated with the rod cavity through a second proportional valve branch (33), and the first proportional valve branch (32) and the second proportional valve branch (33) are respectively and correspondingly provided with an eighth normally open electromagnetic valve (28) and a ninth normally open electromagnetic valve (31).

9. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: a fourth electromagnetic valve (14) which is normally open and a second pressure transmitter (27) are arranged on the first pump control oil way (3); and a normally closed fifth electromagnetic valve (22) and a third pressure transmitter are arranged on the second pump control oil way (13).

10. The wind turbine integrated pump valve combined control hydraulic pitch system of claim 1, wherein: the first valve control branch (24) is provided with a normally closed seventh electromagnetic valve (23), and the second valve control branch (35) is provided with a normally open sixth electromagnetic valve (26).