Hydraulic generator rotor braking system

Abstract

The invention discloses a hydraulic generator rotor braking system, and relates to the field of rotor braking, the hydraulic generator rotor braking system comprises an oil return tank, a brake and a brake ring, oil pressure is controlled between the oil return tank and the brake to carry out oil delivery and discharge, and then contact with and separation from the brake ring are controlled. The rotor can be jacked up to achieve the state of jacking the rotor by increasing oil pressure input, an oil supply ring pipe, an oil discharge ring pipe and an oil overflow ring pipe are communicated between the brake and the oil return tank, and the brake is annularly arranged. The brakes are arranged around the rotor, meanwhile, the brake ring is fixedly connected to the lower portion of the rotor, the brake state is that the flashboard makes contact with the brake ring, friction force is generated, and the top rotor rotating state is that the whole rotor is lifted along with continuous lifting of the flashboard after the flashboard and the brake ring are removed.

Description

Technical Field

[0001] The invention relates to the technical field of rotor braking, in particular to a rotor braking system for a hydro-generator. Background Art

[0002] When the turbine generator stops, a brake is used to stop the turbine generator rotor from rotating. Figures 2 to 4 As shown, 0.5-0.8Mpa compressed air is used as the brake power source to achieve the braking state, and oil is used to achieve the top rotor state, which makes the energy switching frequent and the operation inconvenient. Since the power station unit is frequently started and shut down, the brake is frequently actuated, and the rubber sealing strips of the brake chamber and the return chamber are easily damaged, and the two chambers are prone to gas blowby, which brings hidden dangers to the safe and stable operation of the unit. Since the power station unit was put into operation, a large number of brakes have gas blowby defects every year. In order to ensure the safe and stable operation of the unit, the brakes with gas blowby need to be dismantled and repaired every year. Since the brakes are heavy, large, and numerous, the maintenance process is difficult and personal safety accidents are prone to occur. Therefore, a braking system that can be easily operated and can reduce the intensity of maintenance is needed. Summary of the invention

[0003] In view of the problems existing in the above-mentioned hydro-generator rotor braking system, the present invention is proposed.

[0004] Therefore, the problem to be solved by the present invention is how to improve the maintenance efficiency on the basis of simplifying the structure.

[0005] In order to solve the above technical problems, the present invention provides the following technical solutions: a hydro-generator rotor braking system, comprising: an oil return tank;

[0006] A brake, wherein an oil supply ring pipe, an oil discharge ring pipe and an oil overflow ring pipe are connected between the brake and the oil return tank, and the brake is arranged in a ring shape;

[0007] A brake ring, arranged above the brake;

[0008] supplying oil from the oil return tank to the interior of the brake through the oil supply ring pipe;

[0009] Discharging oil from the inside of the brake to the inside of the oil return tank through the oil discharge ring pipe;

[0010] The oil overflowing from the brake is received into the oil return tank through the oil overflow ring pipe.

[0011] As a preferred solution of the hydro-generator rotor braking system of the present invention, wherein: the oil supply ring pipe is provided with a high-pressure oil pump for controlling the oil supply pressure value;

[0012] The oil discharge ring pipe is provided with an electric valve for discharging the oil inside the brake.

[0013] As a preferred solution of the hydro-generator rotor braking system of the present invention, the brake includes a shell and a bottom plate arranged at the bottom of the shell, a base is sleeved on the top of the shell, a gate is arranged on the base, a slot is arranged on the outer wall of the shell, and the gate is arranged below the brake ring.

[0014] As a preferred solution of the hydro-generator rotor braking system of the present invention, a movable groove is provided on the base, a locking pile fixedly connected to the base is provided on one side of the movable groove, the locking pile is extended and retracted by a hydraulic column, the movement of the hydraulic column is remotely controlled, and the locking pile is embedded and matched with the slot and the movable groove, thereby locking the working state of the brake.

[0015] As a preferred solution of the hydro-generator rotor braking system of the present invention, the base and the bottom plate are connected via a return spring.

[0016] As a preferred solution of the hydro-generator rotor braking system of the present invention, the brake comprises an oil storage chamber and a braking chamber, the oil storage chamber is connected to the oil supply ring pipe and the oil discharge ring pipe, and the braking chamber is connected to the oil overflow ring pipe.

[0017] As a preferred solution of the hydro-generator rotor braking system of the present invention, a limit ring is arranged inside the oil storage cavity, a brake piston is fitted on the limit ring, and a sealing ring fitted with the inner wall of the brake is arranged on the brake piston.

[0018] As a preferred solution of the hydro-generator rotor braking system of the present invention, the high-pressure oil pump controls the oil delivery pressure to reach 0.7 MPA, so that the brake piston rises and presses against the gate plate to fit the brake ring to form a braking state.

[0019] As a preferred solution of the hydro-generator rotor braking system of the present invention, the electric valve controls the oil in the oil storage chamber to be discharged, at which time the brake piston and the gate plate fall back to form a gap with the brake ring, forming a return state.

[0020] As a preferred solution of the hydro-generator rotor braking system of the present invention, the high-pressure oil pump controls the oil pressure to reach 10-20MPA, at which time the gate is lifted to a position higher than the braking state, thereby pushing the brake ring to lift the rotor, forming a rotor-lifting state.

[0021] The beneficial effects of the present invention are as follows: compared with the traditional rotor brake driven by pressurized gas, our brake has no reset chamber, only a brake chamber, fewer sealing strips, a simple structure, and no defect of reduced air tightness caused by mutual influence of gas leakage between the two chambers. At the same time, the brake is driven by a spring when reset, and the action is intuitive and controllable. By setting an oil overflow pipe, if the sealing strip is damaged, the leaked pressure oil can be transported back to the return oil tank through the oil overflow pipe. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for describing the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work. Among them:

[0023] Figure 1 This is a scene diagram of the turbine generator rotor braking system.

[0024] Figure 2 Schematic diagram of the return state of the turbine generator rotor braking system.

[0025] Figure 3 This is a schematic diagram of the braking state of the hydro-generator rotor braking system.

[0026] Figure 4 This is a schematic diagram of the top rotor state of the hydro-generator rotor braking system.

[0027] Figure 5 This is the working flow chart of the turbine generator rotor braking system. DETAILED DESCRIPTION

[0028] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the specific embodiments of the present invention are described in detail below in conjunction with the accompanying drawings.

[0029] In the following description, many specific details are set forth to facilitate a full understanding of the present invention, but the present invention may also be implemented in other ways different from those described herein, and those skilled in the art may make similar generalizations without violating the connotation of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0030] Secondly, the term "one embodiment" or "embodiment" as used herein refers to a specific feature, structure or characteristic that may be included in at least one implementation of the present invention. The term "in one embodiment" that appears in different places in this specification does not necessarily refer to the same embodiment, nor is it an embodiment that is mutually exclusive with other embodiments, either individually or selectively.

[0031] Example 1

[0032] Reference Figure 1 to Figure 5 , which is the first embodiment of the present invention, provides a hydro-turbine generator rotor braking system, which includes an oil return tank 100, a brake 200 and a brake ring 300. The oil volume is transferred and discharged by controlling the oil pressure between the oil return tank 100 and the brake 200, and then the contact and separation with the brake ring 300 are controlled, thereby forming a braking state and a return state. By increasing the oil pressure input, the rotor can be lifted up to achieve a rotor-lifting state.

[0033] Specifically, the brake 200 is connected to the oil return tank 100 via an oil supply ring pipe 201, an oil discharge ring pipe 202 and an oil overflow ring pipe 203. The brake 200 is arranged in a ring. Under normal working conditions, the generator rotor is roughly cylindrical, so the brake 200 is arranged around the bottom of the rotor. At the same time, a brake ring 300 is fixedly connected to the bottom of the rotor. Therefore, the braking state is that the gate plate 205a is in contact with the brake ring 300, generating friction, and the top rotor rotation state is after the gate plate 205a is in contact with the brake ring 300, and as the gate plate 205a continues to rise, the entire rotor will be lifted.

[0034] Preferably, the brake ring 300 is disposed above each brake 200 . The brake ring 300 is a part of the generator rotor and is located below the rotor.

[0035] Preferably, oil is supplied from the oil return tank 100 to the inside of the brake 200 through the oil supply ring pipe 201;

[0036] The oil is discharged from the inside of the brake 200 to the inside of the oil tank 100 through the oil discharge ring pipe 202;

[0037] The oil overflowing from the brake 200 is received into the oil return tank 100 through the oil overflow ring pipe 203 .

[0038] Preferably, the oil supply ring pipe 201 is provided with a high-pressure oil pump 201a for controlling the oil supply pressure value;

[0039] The oil drain ring pipe 202 is provided with an electric valve 202a for extracting the oil inside the brake 200. The high-pressure oil pump 201a can adopt the HPOL-WDD type, and the electric valve 202a can adopt the 9034CP.120-24 / I model.

[0040] Preferably, the brake 200 includes a shell 204 and a bottom plate 204a arranged at the bottom of the shell 204, a base 205 is sleeved on the top of the shell 204, a gate 205a is arranged on the base 205, a slot W is arranged on the outer wall of the shell 204, and the gate 205a is arranged below the brake ring 300.

[0041] Preferably, a movable groove Q is provided on the base 205, and a locking pile 205b fixedly connected to the base 205 is provided on one side of the movable groove Q. The locking pile 205b is extended and retracted by a hydraulic column 205c, and the movement of the hydraulic column 205c is remotely controlled. The locking pile 205b is embedded and matched with the slot W and the movable groove Q, thereby locking the working state of the brake.

[0042] Preferably, the base 205 and the bottom plate 204 a are connected via a return spring 206 .

[0043] Preferably, the brake 200 includes an oil storage chamber 207 and a brake chamber 208 . The oil storage chamber 207 is communicated with the oil supply annular pipe 201 and the oil discharge annular pipe 202 , and the brake chamber 208 is communicated with the oil overflow annular pipe 203 .

[0044] Preferably, a limit ring 207a is provided inside the oil storage chamber 207, a brake piston 207b is fitted on the limit ring 207a, and a sealing ring 207b-1 is provided on the brake piston 207b to fit the inner wall of the brake 200. The height of the limit ring determines the initial position of the brake piston, thereby affecting the movement stroke and contact angle of the gate during the braking process, and thus also affecting the braking force, component wear, response time and system stability, so a large amount of data experiments are needed to obtain a better limit ring 207a height.

[0045] Regarding brake response time:

[0046] Calculation method: record the time from the issuance of the brake signal to the gate fully contacting the brake ring in each experiment; calculate the average response time and standard deviation of multiple experiments.

[0047]

[0048] Where n is the number of experiments, t i is the response time of the ith experiment;

[0049] Regarding the impact of braking force:

[0050] Calculation method:

[0051] A pressure sensor was used to record the force applied by the gate to the brake ring in each experiment.

[0052] Calculate the average braking force and standard deviation of multiple experiments.

[0053]

[0054] Where n is the number of experiments, F i is the braking force of the ith experiment;

[0055] Impact on system stability:

[0056] System stability can be measured by the standard deviation of braking response time and braking force. The smaller the standard deviation, the higher the system stability.

[0057] Impact of component wear:

[0058] Calculation method:

[0059] Measure the wear of the brake components after a certain number of braking operations; calculate the average wear and standard deviation of multiple experiments

[0060] formula:

[0061]

[0062] Table 1: Braking response time (unit: milliseconds)

[0063]

[0064] Table 2: Braking force (unit: Newton)

[0065]

[0066] Table 3: Component wear (unit: percentage, expressed in standard deviation)

[0067]

[0068] Table 4: System stability

[0069]

[0070]

[0071] Using the hypothetical data in the table, we can see the following trends:

[0072] Braking response time: The average response time at 16mm is 90ms, which is not the lowest but relatively low.

[0073] Braking force: The average braking force at 16 mm is 1780N, second only to 18 mm at 1800N.

[0074] Component wear: Average wear at 16 mm was 3.0%, close to the minimum.

[0075] System stability: At 16 mm, the standard deviation of response time and braking force are both low, indicating that the system stability is high.

[0076] Therefore, considering the braking response time, braking force, component wear and system stability, 16 mm is still the optimal limit ring height.

[0077] Preferably, the high-pressure oil pump 201a controls the oil delivery pressure to reach 0.7 MPA, so that the brake piston 207b rises and presses against the gate plate 205a to fit the brake ring 300, forming a braking state.

[0078] Preferably, the electric valve 202a controls the oil in the oil storage chamber 207 to be discharged, and at this time, the brake piston 207b and the gate plate 205a fall back to form a gap with the brake ring 300, thereby forming a return state.

[0079] Preferably, the high-pressure oil pump 201a controls the oil delivery pressure to reach 10-20 MPA, at which time the gate plate 205a is lifted to a position higher than the braking state, forming a top rotor state.

[0080] from Figure 3 It can be seen that at this time, the operating system controls the high-pressure oil pump 201a to reach 0.7MPA. At this time, the oil volume and pressure inside the oil storage chamber 207 gradually increase, and gradually push the brake piston 207b up, and make the brake piston 207b finally contact with the base 205, and continue to push the base 205 upward until the gate 205a contacts the brake ring 300, and then the braking is achieved through the friction between the two. During this process, the base 205 will stretch the return spring 206, and this is the braking state;

[0081] We from Figure 2 It can be seen that when the hydro-generator is started, the electric valve 202a is opened, the oil storage chamber 207 is discharged, and then the brake piston 207b and the gate plate 205a gradually fall back to the limit ring 207a under the rebound action of the return spring 206, and at this time a gap is also generated between the gate plate 205a and the brake ring 300, and then the rotor can rotate normally, and it is in the return state at this time;

[0082] from Figure 4 It can be seen that under normal circumstances, when the staff wants to inspect the unit, they need to lift up the rotor. At this time, the staff controls the high-pressure oil pump 201a to reach 10-20MPA. At this time, the gate 205a repeats the action in the braking state, but at this time, the gate 205a will be lifted to a position higher than the braking state due to the oil supply pressure of the high-pressure oil pump 201a becoming 10-20MPA, that is, on the basis of the contact between the gate 205a and the brake ring 300, it continues to be lifted to lift up the rotor. At this time, a signal is sent to the hydraulic column 205c to control the hydraulic column 205c to extend, so that the locking pile 205b is embedded in the slot W and the movable slot Q to form a lock, and this is the rotor lifting state; similarly, when returning, a contraction signal is sent to cause the hydraulic column 205c to contract, so that the locking pile 205b is pulled out of the slot W and the movable slot Q to release the lock.

[0083] The existing brake uses gas for braking and returning, and oil for top rotor, while ours uses oil for all states, which enables us to complete various actions on the basis of using only one power source, greatly reducing the complexity of operation and more effectively controlling energy consumption;

[0084] At the same time, when the internal sealing strip of the existing brake is damaged, gas will leak between the brake chamber and the return chamber, which will reduce the air tightness of the device. However, after our solution cancels the return chamber, first of all, since only oil is used, there will be no gas leakage. Even if the sealing ring 207b-1 is damaged, although the oil in the oil storage chamber 207 will gradually transfer to the brake chamber 208, since the brake chamber 208 is provided with an oil overflow ring pipe 203 connected to the oil return tank 100, the overflow oil in the brake chamber 208 can return to the oil return tank 100 again.

[0085] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the spirit and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. A hydro-generator rotor braking system, characterized in that: include, Return oil tank (100); A brake (200), wherein an oil supply annular pipe (201), an oil discharge annular pipe (202) and an oil overflow annular pipe (203) are connected between the brake (200) and the oil return tank (100), and the brake (200) is arranged in a ring; A brake ring (300) is arranged above each of the brakes (200); supplying oil from the oil return tank (100) to the interior of the brake (200) through the oil supply ring pipe (201); Discharging oil from the inside of the brake (200) to the inside of the oil return tank (100) through the oil discharge ring pipe (202); The oil overflowing from the brake (200) is received into the oil return tank (100) through the oil overflow ring pipe (203).

2. The hydro-generator rotor braking system according to claim 1, characterized in that: The oil supply ring pipe (201) is provided with a high-pressure oil pump (201a) for controlling the oil supply pressure value; The oil discharge ring pipe (202) is provided with an electric valve (202a) for discharging the oil inside the brake (200).

3. The hydro-generator rotor braking system according to claim 2, characterized in that: The brake (200) comprises a shell (204) and a bottom plate (204a) arranged at the bottom of the shell (204); a base (205) is sleeved on the top of the shell (204); a gate plate (205a) is arranged on the base (205); a slot (W) is arranged on the outer wall of the shell (204); and the gate plate (205a) is arranged below the brake ring (300).

4. The hydro-generator rotor braking system according to claim 3, characterized in that: The base (205) is provided with a movable groove (Q), and a locking pile (205b) fixedly connected to the base (205) is provided on one side of the movable groove (Q). The locking pile (205b) is extended and retracted by a hydraulic column (205c), and the movement of the hydraulic column (205c) is remotely controlled. The locking pile (205b) is embedded and matched with the card slot (W) and the movable groove (Q), thereby locking the working state of the brake.

5. The hydro-generator rotor braking system according to claim 4, characterized in that: The base (205) and the bottom plate (204a) are connected via a return spring (206).

6. The hydro-generator rotor braking system according to claim 5, characterized in that: The brake (200) comprises an oil storage chamber (207) and a brake chamber (208) therein; the oil storage chamber (207) is in communication with the oil supply ring pipe (201) and the oil discharge ring pipe (202); and the brake chamber (208) is in communication with the oil overflow ring pipe (203).

7. The hydro-generator rotor braking system according to claim 6, characterized in that: A limit ring (207a) is arranged inside the oil storage cavity (207), a brake piston (207b) is arranged on the limit ring (207a), and a sealing ring (207b-1) is arranged on the brake piston (207b) and is in contact with the inner wall of the brake (200).

8. The hydro-generator rotor braking system according to claim 7, characterized in that: The high-pressure oil pump (201a) controls the oil delivery pressure to reach 0.7 MPA, so that the brake piston (207b) rises and presses against the gate plate (205a) to fit with the brake ring (300), thereby forming a braking state.

9. The hydro-generator rotor braking system according to claim 8, characterized in that: The electric valve (202a) controls the oil in the oil storage chamber (207) to be discharged. At this time, the brake piston (207b) and the gate plate (205a) fall back to form a gap with the brake ring (300), thus forming a return state.

10. The hydro-generator rotor braking system according to claim 9, characterized in that: The high-pressure oil pump (201a) controls the oil delivery pressure to reach 10-20 MPA, at which time the gate plate (205a) is lifted to a position higher than the braking state, thereby pushing the brake ring to lift the rotor, forming a rotor-lifting state.

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