Generator rotor braking system

Abstract

The utility model discloses a generator rotor braking system, which relates to the field of rotor braking, and 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 and separation with 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 utility model relates to the technical field of rotor braking, in particular to a generator rotor braking system. Background Art

[0002] When a hydrogenerator shuts down, a brake is used to stop the rotation of the hydrogenerator rotor. As shown in the prior art Figures 2 to 4 compressed air at 0.5 - 0.8 Mpa is used as the power source of the brake to achieve the braking state, and the jacking rotor state is achieved by oil transmission, which results in frequent energy switching and inconvenient operation. Since the units of this power station start and stop frequently, the brake acts frequently, and the rubber sealing strips of the braking cavity and the return cavity are easily damaged, and air leakage is likely to occur between the two cavities, posing a hidden danger to the safe and stable operation of the unit. Since the power station units were put into production, a large number of brakes have had air leakage defects every year. To ensure the safe and stable operation of the units, it is necessary to disassemble and overhaul the air-leaking brakes every year. Due to the heavy weight, large volume and large quantity of the brakes, the overhaul process is difficult and personal safety accidents are likely to occur. Therefore, a braking system that can be operated conveniently and reduce the overhaul intensity is needed. Summary of the Utility Model

[0003] In view of the problems existing in the above generator rotor braking system, the present utility model is proposed.

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

[0005] To solve the above technical problems, the present utility model provides the following technical solution: a generator rotor braking system, which includes an oil return tank;

[0006] a brake, 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 brakes are arranged in a circular pattern;

[0007] a braking ring, which is arranged above the brake.

[0008] As a preferred solution of the generator rotor braking system of the present utility model, wherein: a high-pressure oil pump is arranged on the oil supply ring pipe;

[0009] an electric valve is arranged on the oil discharge ring pipe.

[0010] As a preferred solution of the generator rotor braking system of the present utility model, wherein: the brake includes a housing, and a bottom plate arranged at the bottom of the housing, a base is sleeved above the housing, a brake plate is arranged on the base, a clamping groove is arranged on the outer wall of the housing, and the brake plate is arranged below the braking ring.

[0011] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: An activity groove is provided on the base, and a locking pile fixedly connected to the base is provided on one side of the activity groove. The locking pile is telescoped by a hydraulic column, and the locking pile is embedded and fitted with the clamping groove and the activity groove, so as to lock the working state of the brake.

[0012] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: The base and the bottom plate are connected by a return spring.

[0013] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: The inside of the brake includes an oil storage cavity and a braking cavity. The oil storage cavity is communicated with the oil supply ring pipe and the oil discharge ring pipe, and the braking cavity is communicated with the oil overflow ring pipe.

[0014] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: A limiting ring is provided inside the oil storage cavity, a braking piston is fitted on the limiting ring, and a sealing ring that fits with the inner wall of the brake is provided on the braking piston.

[0015] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: The high-pressure oil pump controls the oil supply pressure to reach 0.7 MPA, so that the braking piston rises to press against the brake plate and fit with the braking ring, forming a braking state.

[0016] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: The electric valve controls the discharge of the oil in the oil storage cavity. At this time, a gap is formed between the braking piston and the brake plate when they fall back and the braking ring, forming a return state.

[0017] As a preferred embodiment of the generator rotor braking system of the present utility model, the following is provided: The high-pressure oil pump controls the oil supply pressure to reach 10 - 20 MPA. At this time, the brake plate is lifted to a position higher than the braking state, so as to push the braking ring to jack up the rotor, and a rotor jacking state is formed at this time.

[0018] The beneficial effects of the present utility model are as follows: Compared with the traditional rotor brake driven by compressed gas, the brake of the present invention has no return cavity, only a braking cavity is provided, the number of sealing strips is reduced, the structure is simple, and there will be no defect that the air leakage between the two cavities affects each other and reduces the airtightness. At the same time, when the brake is reset, it is driven by a spring, the action is intuitive and controllable, and by providing an oil overflow pipe, if the sealing strip is damaged, the leaked pressure oil can be transported back to the oil return tank through the oil overflow pipe. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] To more clearly illustrate the technical solutions of the embodiments of the present utility model, the following will briefly introduce the accompanying drawings required for the description of the embodiments. Obviously, the accompanying drawings in the following description are only some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other accompanying drawings can be obtained based on these drawings. Among them:

[0020] Figure 1 It is a scene diagram of the generator rotor braking system.

[0021] Figure 2 It is a schematic diagram of the reset state of the generator rotor braking system.

[0022] Figure 3 It is a schematic diagram of the braking state of the generator rotor braking system.

[0023] Figure 4 It is a schematic diagram of the jacking rotor state of the generator rotor braking system.

[0024] Figure 5 It is a working flow chart of the generator rotor braking system. Detailed implementation manners

[0025] To make the above objects, features, and advantages of the present utility model more obvious and understandable, the following will describe the detailed implementation manners of the present utility model in conjunction with the accompanying drawings of the specification.

[0026] In the following description, many specific details are set forth to fully understand the present utility model. However, the present utility model can also be implemented in other ways different from those described herein. Those skilled in the art can make similar extensions without departing from the connotation of the present utility model. Therefore, the present utility model is not limited by the specific embodiments disclosed below.

[0027] Secondly, the so-called "one embodiment" or "embodiment" herein refers to a specific feature, structure, or characteristic that can be included in at least one implementation manner of the present utility model. The "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 alone or selectively.

[0028] Embodiment 1

[0029] Refer to Figures 1 to 5, which is the first embodiment of the present utility model. This embodiment provides a generator rotor braking system. The generator rotor braking system includes an oil return tank 100, a brake 200, and a brake ring 300. The oil quantity is input 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 reset state. By increasing the oil pressure input, the rotor can be lifted to achieve the rotor lifting state.

[0030] Specifically, for the brake 200, an oil supply ring pipe 201, an oil drain ring pipe 202, and an oil overflow ring pipe 203 are connected between the brake 200 and the oil return tank 100. The brake 200 is arranged in a ring shape. Since the generator rotor is generally cylindrical in a normal working environment, the brake 200 is arranged around the lower part of the rotor. At the same time, a brake ring 300 is fixedly connected to the lower part of the rotor. Therefore, in the braking state, the brake plate 205a contacts the brake ring 300 to generate friction. For the rotor lifting state, after the brake plate 205a contacts the brake ring 300, as the brake plate 205a continues to rise, the entire rotor will be lifted.

[0031] Preferably, the brake ring 300 is arranged above each brake 200. The brake ring 300 is part of the generator rotor and is located below the rotor.

[0032] Preferably, oil is supplied from the oil return tank 100 to the inside of the brake 200 through the oil supply ring pipe 201;

[0033] Oil is drained from the inside of the brake 200 to the inside of the oil return tank 100 through the oil drain ring pipe 202;

[0034] The oil overflowing from the brake 200 is received into the oil return tank 100 through the oil overflow ring pipe 203.

[0035] Preferably, a high-pressure oil pump 201a for controlling the oil supply pressure value is arranged on the oil supply ring pipe 201, and the high-pressure oil pump 201a can adopt the HPOL-WDD type;

[0036] An electric valve 202a for pumping the oil inside the brake 200 is arranged on the oil drain ring pipe 202, and the electric valve 202a can adopt the 9034CP.120-24 / I model.

[0037] Preferably, the brake 200 includes a housing 204 and a bottom plate 204a arranged at the bottom of the housing 204. A base 205 is sleeved above the housing 204, a brake plate 205a is arranged on the base 205, a card slot W is arranged on the outer wall of the housing 204, and the brake plate 205a is arranged below the brake ring 300.

[0038] Preferably, an activity slot Q is provided on the base 205. A locking pile 205b fixedly connected to the base 205 is provided on one side of the activity slot Q. The locking pile 205b expands and contracts through a hydraulic column 205c, and the action of the hydraulic column 205c is remotely controlled. The locking pile 205b is in embedded fit with the card slot W and the activity slot Q, thereby locking the working state of the brake.

[0039] Preferably, the base 205 and the bottom plate 204a are connected by a return spring 206.

[0040] Preferably, the inside of the brake 200 includes an oil storage cavity 207 and a brake cavity 208. The oil storage cavity 207 communicates with the oil supply ring pipe 201 and the oil discharge ring pipe 202, and the brake cavity 208 communicates with the oil overflow ring pipe 203.

[0041] Preferably, a limiting ring 207a is provided inside the oil storage cavity 207. A brake piston 207b is attached to the limiting ring 207a. A sealing ring 207b-1 that fits with the inner wall of the brake 200 is provided on the brake piston 207b. The height of the limiting ring determines the initial position of the brake piston, thereby affecting the movement stroke and contact angle of the brake plate during braking. Therefore, it will also affect the braking force, component wear, response time, and system stability. Therefore, a large number of data experiments are required to obtain a better height of the limiting ring 207a.

[0042] Regarding the braking response time:

[0043] Calculation method: Record the time from the braking signal being issued to the brake plate completely contacting the brake ring in each experiment; calculate the average response time and standard deviation of multiple experiments.

[0044]

[0045] Among them, n is the number of experiments, and t i is the response time of the i-th experiment;

[0046] Regarding the influence on the braking force:

[0047] Calculation method: Use a pressure sensor to record the force exerted by the brake plate on the brake ring in each experiment.

[0048] Calculate the average braking force and standard deviation of multiple experiments.

[0049]

[0050] Among them, n is the number of experiments, and F i is the braking force of the i-th experiment;

[0051] Regarding the influence on system stability:

[0052] System stability can be measured by the braking response time and the standard deviation of the braking force. The smaller the standard deviation, the higher the system stability.

[0053] Regarding the impact of component wear:

[0054] Calculation method:

[0055] After a certain number of braking operations, measure the wear degree of the brake components; calculate the average wear degree and standard deviation of multiple experiments

[0056] Formula:

[0057]

[0058] Table 1: Braking response time (unit: milliseconds)

[0059]

[0060] Table 2: Braking force (unit: Newtons)

[0061]

[0062] Table 3: Component wear (unit: percentage, represented by standard deviation)

[0063]

[0064] Table 4: System stability

[0065]

[0066]

[0067] From the assumed data in the table, the following trends can be seen:

[0068] Braking response time: At 16 mm, the average response time is 90 ms, which is not the lowest but relatively low.

[0069] Braking force: At 16 mm, the average braking force is 1780 N, second only to 1800 N at 18 mm.

[0070] Component wear: At 16 mm, the average wear is 3.0%, close to the minimum value.

[0071] System stability: At 16 mm, both the standard deviation of the response time and the standard deviation of the braking force are low, indicating high system stability.

[0072] Therefore, considering the braking response time, braking force, component wear, and system stability comprehensively, 16 mm is still the optimal height of the limit ring

[0073] Preferably, the high-pressure oil pump 201a controls the oil delivery pressure to reach 0.7 MPA, causing the brake piston 207b to rise and press against the brake plate 205a to fit with the brake ring 300, forming a braking state.

[0074] Preferably, the electric valve 202a controls the discharge of the oil in the oil storage chamber 207. At this time, a gap is formed between the brake piston 207b and the brake plate 205a as they fall back, forming a return state.

[0075] Preferably, the high-pressure oil pump 201a controls the oil delivery pressure to reach 10 - 20 MPA. At this time, the brake plate 205a is lifted to a position higher than the braking state, forming a rotor jacking state.

[0076] From Figure 3 It can be seen that at this time, the operating system controls the high-pressure oil pump 201a to reach 0.7 MPA. At this time, the oil volume and pressure inside the oil storage chamber 207 gradually increase, and gradually push the brake piston 207b to rise, and finally the brake piston 207b contacts the base 205 and continues to push the base 205 upward until the brake plate 205a contacts the brake ring 300, and then 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 at this time;

[0077] And from Figure 2 It can be seen that when the hydrogenerator starts up at this time, the electric valve 202a is opened, and the oil in the oil storage chamber 207 is drained. Then, the brake piston 207b and the brake plate 205a gradually fall back onto the limit ring 207a under the elastic return of the return spring 206. At this time, a gap is also generated between the brake plate 205a and the brake ring 300, and then the rotor can rotate normally. This is the return state at this time;

[0078] From Figure 4 It can be seen that under normal circumstances, when the staff needs to repair the unit, they need to jack up the rotor. At this time, the staff controls the high-pressure oil pump 201a to reach 10 - 20 MPA. At this time, the brake plate 205a repeats the action in the braking state, but at this time, due to the oil supply pressure of the high-pressure oil pump 201a becoming 10 - 20 MPA, the brake plate 205a will be lifted to a position higher than the braking state. That is, on the basis of the contact between the brake plate 205a and the brake ring 300, it continues to be lifted to jack 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 card slot W and the movable slot Q to form a lock. This is the rotor jacking state at this time; Similarly, when returning, a contraction signal is sent to make the hydraulic column 205c contract, so that the locking pile 205b is withdrawn from the card slot W and the movable slot Q to release the lock.

[0079] The existing brake uses gas during braking and return operations, and uses oil when jacking the rotor. However, our solution uses oil in all states. This enables us to complete various operations while only requiring one power source, greatly reducing the complexity of operation and more effectively controlling energy consumption.

[0080] At the same time, when the internal sealing strip of the existing brake is damaged, it will cause air leakage between the braking chamber and the return chamber, which will reduce the airtightness of the device. However, in our solution, after canceling the return chamber, first, since oil is used in all cases, there will be no air leakage. Even if the sealing ring 207b-1 is damaged, although the oil in the oil storage chamber 207 will gradually transfer to the braking chamber 208, because there is an oil overflow ring pipe 203 connected to the oil return tank 100 in the braking chamber 208, the oil overflow in the braking chamber 208 can return to the oil return tank 100 again.

[0081] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be modified or equivalently replaced without departing from the spirit and scope of the technical solutions of the present invention, and they should all be covered within the scope of the claims of the present invention.

Claims

1. A 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).

2. The 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); The oil discharge ring pipe (202) is provided with an electric valve (202a).

3. The 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 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 locking pile (205b) is embedded and matched with the clamping groove (W) and the movable groove (Q), thereby locking the working state of the brake.

5. The 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 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 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 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 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 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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