CN109139350B - Overspeed protection and flow control device for pumped storage power station - Google Patents
Overspeed protection and flow control device for pumped storage power station Download PDFInfo
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- CN109139350B CN109139350B CN201811151810.1A CN201811151810A CN109139350B CN 109139350 B CN109139350 B CN 109139350B CN 201811151810 A CN201811151810 A CN 201811151810A CN 109139350 B CN109139350 B CN 109139350B
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- 238000003860 storage Methods 0.000 title claims abstract description 35
- 238000012544 monitoring process Methods 0.000 claims description 21
- 230000001105 regulatory effect Effects 0.000 claims description 21
- 230000011218 segmentation Effects 0.000 claims description 10
- 238000005520 cutting process Methods 0.000 claims description 8
- 230000007547 defect Effects 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 98
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 46
- 230000009471 action Effects 0.000 description 7
- 238000009434 installation Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000010998 test method Methods 0.000 description 2
- 238000013024 troubleshooting Methods 0.000 description 2
- 230000004888 barrier function Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000011946 reduction process Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B15/00—Controlling
- F03B15/02—Controlling by varying liquid flow
- F03B15/04—Controlling by varying liquid flow of turbines
- F03B15/06—Regulating, i.e. acting automatically
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
- F03B13/06—Stations or aggregates of water-storage type, e.g. comprising a turbine and a pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B15/00—Controlling
- F03B15/02—Controlling by varying liquid flow
- F03B15/04—Controlling by varying liquid flow of turbines
- F03B15/06—Regulating, i.e. acting automatically
- F03B15/18—Regulating, i.e. acting automatically for safety purposes, e.g. preventing overspeed
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Water Turbines (AREA)
Abstract
The invention discloses an overspeed protection and flow control device for a pumped storage power station, which belongs to the technical field of pumped storage and comprises a first cartridge valve, a second cartridge valve, a first sectional closing cartridge valve and a second sectional closing cartridge valve, and is characterized in that: the hydraulic control system further comprises an oil return tank, a pilot type electro-hydraulic reversing valve, a first sectionally closed pilot electromagnetic valve, a second sectionally closed pilot electromagnetic valve, a first accident cartridge valve and a second accident cartridge valve, wherein the first accident cartridge valve and the first accident cartridge valve are respectively connected to a servomotor closing cavity, the second accident cartridge valve is connected with the oil return tank, and the pilot type electro-hydraulic reversing valve is respectively connected with control cavities of the first accident cartridge valve, the second accident cartridge valve, the first cartridge valve and the second cartridge valve. According to the invention, the accident cartridge valve, the sectional closing cartridge valve and the sectional closing pilot electromagnetic valve are highly integrated, so that the connection of an oil pipeline is reduced, the defect of more leakage points is avoided, and the running reliability and safety of the unit are improved.
Description
Technical Field
The invention relates to the technical field of pumped storage, in particular to an overspeed protection and flow control device for a pumped storage power station.
Background
The overspeed protection and flow control device is key protection equipment of a hydropower station speed regulation system, and has the main functions that: unit accident shutdown, overspeed shutdown and servomotor multistage rate shutdown. Under the condition that the speed regulator cannot be normally shut down and the guide vane servomotor cannot be timely shut down, the rotating speed of the unit can be quickly increased to the flying rotating speed, so that the flying accident is avoided for limiting the overspeed of the unit, and the accident protection or mechanical overspeed protection device timely shuts down the guide vane servomotor according to the shutdown rate requirement calculated by the unit regulation under the condition, thereby protecting the safety of the unit.
Segmented shut down is also an important device required for hydropower stations. According to the requirements of unit regulation and protection calculation, the speed of the water turbine cannot be too high in the emergency shutdown process, so that the damage to the flow channel due to the water hammer effect is prevented. The pumped storage unit has two different working conditions of a water turbine and a water pump, so that the requirements on the opening and closing rules of the unit are different from those of a common hydropower station unit; under different working conditions, the closing speed and the closing mode required by the unit are different; in addition, the required opening speed of the unit is different from the fastest closing speed of the unit under various working conditions.
The existing accident closing and two-section closing devices in the markets at home and abroad at present cannot meet the requirements of multi-speed starting and stopping, emergency stopping and overspeed protection comprehensive control of the pumped storage unit, various functional valve groups are arranged in an excessively dispersed mode in different degrees, mechanical adjustment accuracy is not high, adjustment is very inconvenient, and the phenomenon of set point drift can be caused after long-time operation. Some valve groups have complicated electric and mechanical combined logic control modes, and the function definition is unclear, so that risks are caused for long-term safe operation of the monitoring system. Meanwhile, the installation positions of the functional valve groups are scattered, so that the system pipeline arrangement is complex, and the problems of multiple oil leakage points, overlong response time of the valve groups, untimely system state switching and the like are easily caused by overlong connecting pipelines; if the installation positions of the excessive connecting pipe orifices and the control oil pipe joints are unreasonable, the pressure fluctuation among the pipe orifices is easy to cause the misoperation of certain hydraulic control function, and the operation safety of the power station is seriously affected.
The Chinese patent document with publication number CN 102042159A and publication date 2011, 05 and 04 discloses a sectional closing device for realizing closing rate adjustment of a pumped storage unit, which is characterized by comprising a sectional closing valve FD I, a sectional closing valve FD II and a sectional closing hydraulic valve integrated block JCK; the sectional closing valve FD I comprises a hydraulic control reversing valve V1 and an electromagnetic reversing valve V2, wherein V1 is a two-position two-way hydraulic control reversing valve, V2 is a two-position four-way electromagnetic reversing valve, and V2 is arranged on a valve body of the hydraulic control reversing valve V1 and used for controlling reversing of the hydraulic control reversing valve V1; the sectional closing valve FD II comprises a three-position four-way pilot operated directional valve V3, a shuttle valve S1 and cartridge valves C1, C2 and C3, wherein the cartridge valves C1, C2 and C3 are integrated on the same valve body, and the pilot operated directional valve V3 and the shuttle valve S1 are arranged on the valve body and used for controlling the switch of the cartridge valves; the sectional closing hydraulic valve integrated block JCK comprises two-position four-way travel reversing valves V4 and V6 and two-position four-way electromagnetic reversing valves V5 and V7, wherein the travel reversing valve V4 and the electromagnetic reversing valve V5 are in one group, and the travel reversing valve V6 and the electromagnetic reversing valve V7 are in the other group and are used for judging a water turbine/water pump direction inflection point signal; the sectional closing valve FD I and the sectional closing valve FD II are connected in series in an open cavity pipeline of the speed regulation system, and the sectional closing hydraulic valve integrated block JCK is arranged beside the guide vane servomotor in the foundation pit; the operation oil pipeline JG of the guide vane servomotor closing cavity is connected with the guide vane servomotor closing cavity and the P port of the hydraulic control reversing valve V3, the operation oil pipeline JK of the guide vane servomotor opening cavity is connected with the A port of the hydraulic control reversing valve V1, the control pressure oil pipeline P1 is connected with the P port of the electromagnetic reversing valve V2, the B port of the hydraulic control reversing valve V1 is connected with the A1 port, the A2 port and the A3 port of the cartridge valve C1, the C2 port and the A3 port of the C3 port, the B1 port, the B2 port and the B3 port of the cartridge valve C1, the C2 port and the B3 port of the C3 port are connected with the guide vane servomotor opening cavity pipeline, the control pressure oil pipeline P2 is connected with the P port of the travel reversing valve V4 and the V6, the A port of the travel reversing valve V4 is connected with the P port of the electromagnetic reversing valve V5, the A port of the travel reversing valve V6 is connected with the P port of the electromagnetic reversing valve V7, the B port of the electromagnetic reversing valve V5 is connected with the a-end hydraulic control cavity of the hydraulic control reversing valve V3, and the A-end of the electromagnetic reversing valve V7 is connected with the hydraulic control cavity of the hydraulic control reversing valve V3.
The sectional closing device disclosed in the patent document realizes the adjustment of different closing rates of the water turbine direction and the water pump direction of the pumped storage unit, and ensures the safe and reliable operation of the pumped storage unit.
The Chinese patent literature with publication number of CN 101430358 and publication date of 2009 month 05 and 13 discloses a whole set of starting test method for the first water pump working condition of a pumped storage power station, which sequentially comprises a unit water pump working condition test, a unit power generation working condition test, a working condition conversion test and an accident shutdown test, and is characterized in that: firstly, performing a working condition test of the unit water pump, wherein the working condition test of the unit water pump comprises the following steps:
a. water pump working condition no-load test: starting a unit by using a static frequency converter, wherein the unit is integrated into a power grid for operation under the state that a guide vane is closed and a rotating wheel is in air; measuring the input power of the unit, the stator and rotor currents, the temperatures of all parts of the unit and the vibration and swing values of the unit, and checking the dynamic balance of the unit after the electric working conditions of the unit are connected in a grid; measuring the temperature, thrust and guide bearing bush temperature of each part until the temperature is stable during idle running, if the phenomenon of rising of the bush Wen Jiju is found during running, stopping immediately, and after the running is stable, performing an automatic stopping test to check the correctness of a stopping program;
b. pumping test of water pump working condition: operating a unit inflation water-pressing system to exhaust, monitoring the water level rising condition of a draft tube and the pressure between a guide vane and a rotating wheel, recording a pressure change oscillogram, and determining the optimal time and opening speed of the guide vane; opening the water inlet ball valve and the guide vane according to the opening relation curve of the water inlet ball valve and the guide vane; recording parameters such as input power of a motor, pressure between a guide vane and a rotating wheel, volute pressure, draft tube pressure, servomotor stroke and the like when the zero flow working condition is transited to the pumping working condition; the vibration of the upper and lower frames, the top cover, the bearing support and the main shaft swing degree are recorded; correcting and optimizing parameters such as a guide vane opening rule according to the recorded data and the actual lift; after the pumping working condition stably operates, measuring the input power of a motor, the opening degree of a guide vane, pumping flow, lift, unit vibration and swing degree, noise, volute, draft tube pressure and pressure pulsation, the temperature of each part of the unit, the flow and pressure of a cooling system, shaft voltage and the like; drawing a comprehensive curve of the water turbine/water pump according to parameters such as actually measured input power, lift, flow, guide vane opening and the like, and comparing the comprehensive curve with a curve provided by a manufacturing plant;
c. and (3) stopping test of the working condition of the water pump: the unit operates under rated load, and gives a shutdown instruction at the local control unit to check the correctness of an automatic load reduction program and an automatic shutdown program of the unit; recording a time sequence chart, rotating speed characteristics and overall time of main program actions in a normal shutdown process, and determining tripping time of the circuit breaker in a load reduction process; under rated load, simulating mechanical accidents and electric protection actions to trip the accident shutdown of the breaker, checking the correctness of a shutdown program of a load dump test of the working condition of the water pump, and checking the input of a normal and mechanical accident shutdown point braking device, the input of a protection device and the locking condition; parameters such as current, voltage, guide vane opening, volute and draft tube pressure, guide vane and runner pressure, servomotor travel, rotating speed, total shutdown time, vibration of each part of the unit and main shaft swing degree and the like of a stator and a rotor in the shutdown process are recorded, guide vane closing rules are corrected according to oscillograms of the parameters, and process parameters are optimized.
The whole set of starting test method for the working condition of the first water pump of the pumped storage power station disclosed in the patent document adopts the starting scheme for the working condition of the first water pump of the first machine, thereby being beneficial to saving engineering cost, and being capable of generating power by putting the first machine into production in advance and having good social and economic benefits.
However, the prior art typified by the above patent documents all have the following drawbacks:
1. the requirements of multi-speed start-stop, emergency stop and overspeed protection comprehensive control of the pumped storage unit cannot be met, functional valve groups are distributed too dispersedly in different degrees, mechanical adjustment accuracy is not high, adjustment is very inconvenient, set point drift can be caused after long-time operation, and the operation reliability of a power station is affected.
2. The system pipeline arrangement is complex, and the overlong connecting pipeline easily causes the problems of more oil leakage points, overlong response time of a valve group and untimely system state switching; excessive connecting pipe orifices and control oil pipe joints have high requirements on installation positions, and if the installation positions are unreasonable, pressure fluctuation among the pipe orifices is easy to cause misoperation of a hydraulic control function, so that the operation safety of a power station is seriously influenced.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide an overspeed protection and flow control device for a pumped storage power station, which can meet the requirements of comprehensive control of multi-speed start-stop, emergency stop and overspeed protection of the pumped storage power station.
The invention is realized by the following technical scheme:
the utility model provides an overspeed protection and flow control device for pumped storage power station, includes control pressure oil circuit, connects the first cartridge valve on main distributing valve closed chamber through the main oil circuit, connects the second cartridge valve on main distributing valve open chamber, connects the first segmentation closed cartridge valve and the second segmentation closed cartridge valve on servomotor open chamber, its characterized in that: the hydraulic control system further comprises an oil return tank, a pilot type electrohydraulic reversing valve, a first section closing pilot electromagnetic valve for switching the first section closing cartridge valve, a second section closing pilot electromagnetic valve for switching the second section closing cartridge valve, a first accident cartridge valve connected to a main pressure oil source and a second accident cartridge valve connected to a servomotor opening cavity, wherein the first cartridge valve and the first accident cartridge valve are respectively connected to the servomotor closing cavity, the second accident cartridge valve is connected with the oil return tank, and the pilot type electrohydraulic reversing valve is respectively connected with the first accident cartridge valve, the second accident cartridge valve, the control cavity of the first cartridge valve and the control cavity of the second cartridge valve.
And the first sectional closing cartridge valve and the second sectional closing cartridge valve are connected with one-way valves in parallel, and the one-way valves are used for increasing the oil quantity of the opening cavity of the servomotor.
The first sectional closing cartridge valve and the second sectional closing cartridge valve are also connected with a flow regulating valve in parallel; and the flow regulating valve is used for regulating the slow closing rate of the first section of the servomotor.
The first sectional closing cartridge valve is an adjustable sectional closing cartridge valve and is used for adjusting the quick closing rate of the second section of the servomotor.
The first cartridge valve is used for cutting off or communicating the main distributing valve and the servomotor; and the second cartridge valve is used for cutting off or communicating the main distributing valve and the servomotor.
The control cavity oil way of the first cartridge valve and the control cavity oil way of the second cartridge valve are provided with a first pressure switch and a first pressure gauge, and the first pressure switch is used for monitoring a pressure control signal during normal open and shut down.
And the control cavity oil ways of the first accident cartridge valve and the second accident cartridge valve are provided with a second pressure switch and a second pressure gauge, and the second pressure switch is used for monitoring accident shutdown pressure signals.
The control cavity oil way of the first sectional closing cartridge valve is provided with a third pressure switch and a third pressure gauge, and the third pressure switch is used for monitoring the opening and closing states of the first sectional closing cartridge valve.
And a fourth pressure switch and a fourth pressure gauge are arranged on an oil way of the control cavity of the second section closing cartridge valve, and the fourth pressure switch is used for monitoring the opening and closing states of the second section closing cartridge valve.
The control pressure oil way is provided with a fifth pressure gauge which is used for monitoring control pressure oil.
The beneficial effects of the invention are mainly shown in the following aspects:
1. the hydraulic control system comprises a control pressure oil path, a first cartridge valve connected to a closing cavity of a main distributing valve through the main oil path, a second cartridge valve connected to an opening cavity of the main distributing valve, a first sectional closing cartridge valve and a second sectional closing cartridge valve connected to an opening cavity of a servomotor, an oil return tank, a pilot type electrohydraulic reversing valve, a first sectional closing pilot solenoid valve for switching the first sectional closing cartridge valve, a second sectional closing pilot solenoid valve for switching the second sectional closing cartridge valve, a first accident cartridge valve connected to a main pressure oil source and a second accident cartridge valve connected to an opening cavity of the servomotor, wherein the first accident cartridge valve and the first accident cartridge valve are connected to the closing cavity of the servomotor respectively, the second accident cartridge valve is connected with an oil return tank, and the pilot type electrohydraulic reversing valve is connected with the first accident cartridge valve, the second accident cartridge valve, the first sectional closing pilot solenoid valve and the second accident reversing valve respectively.
2. According to the invention, the accident cartridge valve, the sectional closing cartridge valve and the sectional closing pilot electromagnetic valve are standard components, so that the universality and the interchangeability are high, and the requirements of various emergency shutdown rates on the pumped storage unit, which are different from the shutdown rate, can be met.
3. According to the invention, the first sectional closing cartridge valve and the second sectional closing cartridge valve are connected with the one-way valve in parallel for increasing the oil quantity of the opening cavity of the servomotor, so that the flow of the opening cavity side of the servomotor during startup is increased, and the requirement of a unit on startup time is met.
4. According to the invention, a first pressure switch and a first pressure gauge are arranged on an oil way of a control cavity of a first cartridge valve and a control cavity of a second cartridge valve; the control cavity oil ways of the first accident cartridge valve and the second accident cartridge valve are provided with a second pressure switch and a second pressure gauge; a third pressure switch and a third pressure gauge are arranged on an oil way of the control cavity of the first sectional closing cartridge valve; a fourth pressure switch and a fourth pressure gauge are arranged on an oil way of the control cavity of the second sectional closing cartridge valve; a fifth pressure gauge is arranged on the control pressure oil circuit; through setting up a plurality of pressure switches and manometer, can realize the various action states of remote monitoring valves, also make things convenient for on-the-spot observation and troubleshooting, guarantee the safe operation of unit.
5. The invention adopts the cartridge valve structure, is convenient for installation, is convenient for system control, has high through-flow capacity and oil pollution resistance, and ensures that the overspeed protection and flow control device has high integral degree and compact structure.
6. The hydraulic and electric control logic is simple and clear, the action mode of the hydraulic system under each working condition of the pumped storage unit is definitely defined, the control flow of the monitoring system is simplified, and the reliability of the unit during working condition switching is improved.
7. According to the invention, under the extreme conditions of abnormal power failure, coil damage or electromagnetic valve blocking and the like, for example, when the unit is in a working condition of a water turbine, the guide vane can be safely closed according to the slow closing speed of the first section of the unit; the guide vane can still be closed according to the requirements of adjustment and protection calculation under the working condition of the water pump, so that the running safety of the unit is improved.
Drawings
The invention will be further described in detail with reference to the drawings and detailed description, wherein:
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a graph of the closing and opening schedules of the present invention applied to a pumped-storage unit;
the marks in the figure: 1. the main distributing valve is closed, the first cartridge valve is 2, the main distributing valve is opened, the first cartridge valve is 4, the second cartridge valve is 5, the servomotor is opened, the first section is closed, the cartridge valve is 7, the second section is closed, the cartridge valve is 8, the oil return box is 9, the pilot electrohydraulic reversing valve is 10, the pilot electromagnetic valve is closed in the first section, the pilot electromagnetic valve is 11, the pilot electromagnetic valve is closed in the second section, the main pressure oil source is 12, 13, a first accident cartridge valve, 14, a second accident cartridge valve, 15, a servomotor closing cavity, 16, a one-way valve, 17, a flow regulating valve, 18, a first pressure switch, 19, a second pressure switch, 20, a third pressure switch, 21, a fourth pressure switch, 22, a first pressure gauge, 23, a second pressure gauge, 24, a third pressure gauge, 25, a fourth pressure gauge, 26 and a fifth pressure gauge;
x is the closing curve of the working condition of the water pump, y is the opening curve of the working condition of the water pump and the water turbine, and z is the closing curve of the working condition of the water turbine.
Detailed Description
Example 1
An overspeed protection and flow control device for a pumped storage power station comprises a control pressure oil path, a first cartridge valve 2 connected to a main distributing valve closing cavity 1 through a main oil path, a second cartridge valve 4 connected to a main distributing valve opening cavity 3, a first sectional closing cartridge valve 6 and a second sectional closing cartridge valve 7 connected to a servomotor opening cavity 5, an oil return tank 8, a pilot electrohydraulic reversing valve 9, a first sectional closing pilot solenoid valve 10 for switching the first sectional closing cartridge valve 6, a second sectional closing pilot solenoid valve 11 for switching the second sectional closing cartridge valve 7, a first accident cartridge valve 13 connected to a main pressure oil source 12 and a second accident cartridge valve 14 connected to the servomotor opening cavity 5, wherein the first cartridge valve 2 and the first accident cartridge valve 13 are respectively connected to the servomotor closing cavity 15, the second accident cartridge valve 14 is connected with the oil return tank 8, and the pilot electrohydraulic reversing valve 9 is respectively connected with the first accident cartridge valve 13, the second accident cartridge valve 14 and the first accident cartridge valve 4.
The embodiment is the most basic implementation mode, including control pressure oil circuit, connect the first cartridge valve on the main distributing valve closed chamber through the main oil circuit, connect the second cartridge valve on the main distributing valve open chamber, connect the first segmentation closed cartridge valve and the second segmentation closed cartridge valve on the servomotor open chamber, the return tank, the pilot operated electrohydraulic switching valve, be used for switching first segmentation closed pilot operated solenoid valve of first segmentation closed cartridge valve, be used for switching second segmentation closed pilot operated solenoid valve of second segmentation closed cartridge valve, connect the first accident cartridge valve on the main pressure oil source and connect the second accident cartridge valve on the servomotor open chamber, first accident cartridge valve and first accident cartridge valve are connected respectively on the servomotor open chamber, second accident cartridge valve is connected with the oil return tank, pilot operated electrohydraulic switching valve is connected with first accident cartridge valve, second accident cartridge valve, first cartridge valve and second cartridge valve's control chamber, pilot operated solenoid valve for controlling emergency stop machine set control first accident rate and second accident rate are improved, the high-speed integrated cartridge valve is avoided through first accident rate and the second accident rate, the high-speed integrated cartridge valve is closed through the pilot operated valve, the high-speed integrated cartridge valve, the emergency stop pump is avoided.
Example 2
An overspeed protection and flow control device for a pumped storage power station comprises a control pressure oil path, a first cartridge valve 2 connected to a main distributing valve closing cavity 1 through a main oil path, a second cartridge valve 4 connected to a main distributing valve opening cavity 3, a first sectional closing cartridge valve 6 and a second sectional closing cartridge valve 7 connected to a servomotor opening cavity 5, an oil return tank 8, a pilot electrohydraulic reversing valve 9, a first sectional closing pilot solenoid valve 10 for switching the first sectional closing cartridge valve 6, a second sectional closing pilot solenoid valve 11 for switching the second sectional closing cartridge valve 7, a first accident cartridge valve 13 connected to a main pressure oil source 12 and a second accident cartridge valve 14 connected to the servomotor opening cavity 5, wherein the first cartridge valve 2 and the first accident cartridge valve 13 are respectively connected to the servomotor closing cavity 15, the second accident cartridge valve 14 is connected with the oil return tank 8, and the pilot electrohydraulic reversing valve 9 is respectively connected with the first accident cartridge valve 13, the second accident cartridge valve 14 and the first accident cartridge valve 4.
The first sectional closing cartridge valve 6 and the second sectional closing cartridge valve 7 are connected with a one-way valve 16 in parallel, and the one-way valve is used for increasing the oil quantity of the servomotor opening cavity 5.
The embodiment is a preferred implementation mode, the accident cartridge valve, the sectional closing cartridge valve and the sectional closing pilot electromagnetic valve are standard components, the universality and the interchangeability are high, and the requirements of various emergency shutdown rates on the pumped storage unit, wherein the startup rate is different from the shutdown rate, can be met.
The first sectional closing cartridge valve and the second sectional closing cartridge valve are connected with the one-way valve in parallel, which is used for increasing the oil quantity of the opening cavity of the servomotor, so that the flow quantity of the opening cavity side of the servomotor during starting is increased, and the requirement of a unit on starting time is met.
Example 3
An overspeed protection and flow control device for a pumped storage power station comprises a control pressure oil path, a first cartridge valve 2 connected to a main distributing valve closing cavity 1 through a main oil path, a second cartridge valve 4 connected to a main distributing valve opening cavity 3, a first sectional closing cartridge valve 6 and a second sectional closing cartridge valve 7 connected to a servomotor opening cavity 5, an oil return tank 8, a pilot electrohydraulic reversing valve 9, a first sectional closing pilot solenoid valve 10 for switching the first sectional closing cartridge valve 6, a second sectional closing pilot solenoid valve 11 for switching the second sectional closing cartridge valve 7, a first accident cartridge valve 13 connected to a main pressure oil source 12 and a second accident cartridge valve 14 connected to the servomotor opening cavity 5, wherein the first cartridge valve 2 and the first accident cartridge valve 13 are respectively connected to the servomotor closing cavity 15, the second accident cartridge valve 14 is connected with the oil return tank 8, and the pilot electrohydraulic reversing valve 9 is respectively connected with the first accident cartridge valve 13, the second accident cartridge valve 14 and the first accident cartridge valve 4.
The first sectional closing cartridge valve 6 and the second sectional closing cartridge valve 7 are connected with a one-way valve 16 in parallel, and the one-way valve is used for increasing the oil quantity of the servomotor opening cavity 5.
The first sectional closing cartridge valve 6 and the second sectional closing cartridge valve 7 are also connected with a flow regulating valve 17 in parallel; and the flow regulating valve 17 is used for regulating the slow closing rate of the first section of the servomotor under the working condition of the water turbine.
The first sectional closing cartridge valve 6 is an adjustable sectional closing cartridge valve and is used for adjusting the quick closing speed of the second section of the servomotor under the working condition of the water turbine.
The first cartridge valve 2 is used for cutting off or communicating the main distributing valve and the servomotor; and the second cartridge valve 4 is used for cutting off or communicating the main distributing valve and the servomotor.
The embodiment is a further preferred embodiment, and a cartridge valve structure is adopted, so that the installation is convenient, the system control is convenient, the cartridge valve has high through-flow capacity and high oil pollution resistance, and the whole integration level of the overspeed protection and flow control device is high, and the structure is compact.
Example 4
An overspeed protection and flow control device for a pumped storage power station comprises a control pressure oil path, a first cartridge valve 2 connected to a main distributing valve closing cavity 1 through a main oil path, a second cartridge valve 4 connected to a main distributing valve opening cavity 3, a first sectional closing cartridge valve 6 and a second sectional closing cartridge valve 7 connected to a servomotor opening cavity 5, an oil return tank 8, a pilot electrohydraulic reversing valve 9, a first sectional closing pilot solenoid valve 10 for switching the first sectional closing cartridge valve 6, a second sectional closing pilot solenoid valve 11 for switching the second sectional closing cartridge valve 7, a first accident cartridge valve 13 connected to a main pressure oil source 12 and a second accident cartridge valve 14 connected to the servomotor opening cavity 5, wherein the first cartridge valve 2 and the first accident cartridge valve 13 are respectively connected to the servomotor closing cavity 15, the second accident cartridge valve 14 is connected with the oil return tank 8, and the pilot electrohydraulic reversing valve 9 is respectively connected with the first accident cartridge valve 13, the second accident cartridge valve 14 and the first accident cartridge valve 4.
The first sectional closing cartridge valve 6 and the second sectional closing cartridge valve 7 are connected with a one-way valve 16 in parallel, and the one-way valve is used for increasing the oil quantity of the servomotor opening cavity 5.
The first sectional closing cartridge valve 6 and the second sectional closing cartridge valve 7 are also connected with a flow regulating valve 17 in parallel; and the flow regulating valve 17 is used for regulating the slow closing rate of the first section of the servomotor under the working condition of the water turbine.
The first sectional closing cartridge valve 6 is an adjustable sectional closing cartridge valve and is used for adjusting the quick closing speed of the second section of the servomotor under the working condition of the water turbine.
The first cartridge valve 2 is used for cutting off or communicating the main distributing valve and the servomotor; and the second cartridge valve 4 is used for cutting off or communicating the main distributing valve and the servomotor.
The oil ways of the control cavities of the first cartridge valve 2 and the second cartridge valve 4 are provided with a first pressure switch 18 and a first pressure gauge 22, and the first pressure switch 18 is used for monitoring a pressure control signal during normal open and shut down.
The control cavity oil paths of the first accident cartridge valve 13 and the second accident cartridge valve 14 are provided with a second pressure switch 19 and a second pressure gauge 23, and the second pressure switch 19 is used for monitoring accident shutdown pressure signals.
The control cavity oil way of the first sectional closing cartridge valve 6 is provided with a third pressure switch 20 and a third pressure gauge 24, and the third pressure switch 20 is used for monitoring the opening and closing states of the first sectional closing cartridge valve 6.
The oil way of the control cavity of the second section closing cartridge valve 7 is provided with a fourth pressure switch 21 and a fourth pressure gauge 25, and the fourth pressure switch 21 is used for monitoring the opening and closing states of the second section closing cartridge valve 7.
The control pressure oil path is provided with a fifth pressure gauge 26, and the fifth pressure gauge 26 is used for monitoring control pressure oil.
In the embodiment, as an optimal implementation manner, a first pressure switch and a first pressure gauge are arranged on oil paths of control cavities of a first cartridge valve and a second cartridge valve; the control cavity oil ways of the first accident cartridge valve and the second accident cartridge valve are provided with a second pressure switch and a second pressure gauge; a third pressure switch and a third pressure gauge are arranged on an oil way of the control cavity of the first sectional closing cartridge valve; a fourth pressure switch and a fourth pressure gauge are arranged on an oil way of the control cavity of the second sectional closing cartridge valve; a fifth pressure gauge is arranged on the control pressure oil circuit; through setting up a plurality of pressure switches and manometer, can realize the various action states of remote monitoring valves, also make things convenient for on-the-spot observation and troubleshooting, guarantee the safe operation of unit.
The hydraulic and electric control logic is simple and clear, the action modes of the hydraulic system under each working condition of the pumped storage unit are definitely defined, the control flow of the monitoring system is simplified, and the reliability of the unit during working condition switching is improved.
Under the extreme conditions of abnormal power failure, coil damage or electromagnetic valve blocking and the like, if the unit is in the working condition of the water turbine, the unit can safely close the guide vane according to the slow closing speed of the first section; the guide vane can still be closed according to the requirements of adjustment and protection calculation under the working condition of the water pump, so that the running safety of the unit is improved.
The control pressure oil path is connected to a control pressure oil source P1.
The principle of starting up the water turbine under the working condition is as follows:
the electromagnetic valve EV03 in the pilot-operated electro-hydraulic reversing valve is positioned at the b-end resetting side, the a-end normal running side of the first sectionally closed pilot electromagnetic valve EV01 and the b-end hydraulic turbine working condition side of the second sectionally closed pilot electromagnetic valve EV02 are powered on, and pressure oil respectively enters the one-way valve S1 and the flow regulating valve M1 after passing through the second cartridge valve CV2 and then is connected in parallel to enter the servomotor opening cavity J together K . Servomotor closes chamber J G The oil in (2) passes through the first cartridge valve CV1 and the main distributing valve of the speed regulator and returns to the oil return tank. The arrangement of the one-way valve S1 increases the opening cavity J of the servomotor K The flow of the side meets the starting time requirement under the working condition. The fastest starting time of the unit is regulated by mechanical limit of a main distributing valve of the speed regulator or by adding a throttling plate on a pipeline.
The principle of starting up the water pump under the working condition is as follows:
the electromagnetic valve EV03 in the pilot-operated electro-hydraulic reversing valve is positioned at the b-end resetting side, the a-end normal running side of the first sectionally closed pilot electromagnetic valve EV01 is electrified, the a-end water pump working condition side of the second sectionally closed pilot electromagnetic valve EV02 is electrified, and pressure oil respectively enters the second sectionally closed cartridge valve CV6, the one-way valve S1 and the flow regulating valve M1 after passing through the second cartridge valve CV2 and then is connected in parallel to enter a servomotor opening cavity J K . Servomotor closes chamber J G The oil in (2) passes through the first cartridge valve CV1 and the main distributing valve of the speed regulator and returns to the oil return tank. The regulation of the fastest starting time of the machine set is still realized by mechanical limit of a main distributing valve of the speed regulator or by adding a throttling plate on a pipeline.
The principle of emergency shutdown under the working condition of the water turbine is as follows:
in case of emergency accident, the speed regulator can not work normally and can not close the servomotor in time, the rotating speed of the machine set can rise to the flying rotating speed quickly, and in order to limit the overspeed of the machine set and avoid the flying accident, the arrangement of the accident cartridge valve and the pilot type electrohydraulic reversing valve for closing the servomotor is an important measure for protecting the safety of the machine set. When the emergency shutdown of the unit occurs under the working condition of the water turbine, after the input side of the end a of the electromagnetic valve EV03 in the pilot-operated electro-hydraulic reversing valve is input, the first cartridge valve CV1 and the second cartridge valve CV2 are closed, and the first accident cartridge valve CV3 and the second accident cartridge valve CV4 are opened. Pressurized oil enters the servomotor closure chamber J through the first accident cartridge valve CV3 G . The normal operation side of the end a of the first sectionally closed pilot electromagnetic valve EV01 and the working condition side of the water turbine of the end b of the second sectionally closed pilot electromagnetic valve EV02 are electrified, and a servomotor opens a cavity J K The oil of the (c) is returned to the oil return tank after passing through the flow regulating valve M1 and the second accident cartridge valve CV4 in sequence. The first segment servomotor closing rate is controlled by adjusting the flow regulating valve M1. When the servomotor reaches an inflection point, the b-end subsection input side of the first subsection closing pilot electromagnetic valve EV01 is electrified when the servomotor enters the second subsection to be closed, the first subsection closing cartridge valve CV5 is opened, the pipeline flow is increased at the moment, the servomotor closing speed is increased, and the servomotor closing speed of the section is controlled by adjusting the stroke of the first subsection closing cartridge valve CV 5.
When the speed regulator does not fail, namely the input side of the end a of the electromagnetic valve EV03 in the pilot-operated electro-hydraulic reversing valve is not input, the first cartridge valve CV1 and the second cartridge valve CV2 are opened, the first accident cartridge valve CV3 and the second accident cartridge valve CV4 are closed, and pressurized oil enters the servomotor closing cavity J through the first cartridge valve CV1 G . The normal operation side of the end a of the first sectionally closed pilot electromagnetic valve EV01 and the working condition side of the water turbine of the end b of the second sectionally closed pilot electromagnetic valve EV02 are electrified, and a servomotor opens a cavity J K The oil of the oil tank returns to the oil return tank after sequentially passing through the flow regulating valve M1, the second cartridge valve CV2 and the main valve of the speed regulator. The first segment servomotor closing rate is controlled by adjusting the flow regulating valve M1. When the servomotor reaches the inflection point and enters the second section to be closedThe b-end segment input side of the first segment closing pilot electromagnetic valve EV01 is electrified, the first segment closing cartridge valve CV5 is opened, the pipeline flow is increased, the servomotor closing speed is accelerated, and the servomotor closing speed of the segment is controlled by adjusting the stroke of the first segment closing cartridge valve CV 5.
The principle of emergency closing under the working condition of the water pump is as follows:
when an emergency accident occurs to the unit and the speed regulator cannot work normally, after the input side of the end a of the electromagnetic valve EV03 in the pilot-operated electro-hydraulic reversing valve is put into operation, the first cartridge valve CV1 and the second cartridge valve CV2 are closed, and the first accident cartridge valve CV3 and the second accident cartridge valve CV4 are opened. Pressurized oil enters the servomotor closure chamber J through the first accident cartridge valve CV3 G . The working condition side of the water pump at the end a of the second section closing pilot electromagnetic valve EV02 is powered on, at the moment, the second section closing cartridge valve CV6 is opened, and the servomotor is opened to a cavity J K The oil of the (c) is returned to the oil return tank after passing through the flow regulating valve M1, the second section closing cartridge valve CV6 and the second accident cartridge valve CV4 together. The emergency shutdown rate of the servomotor under the working condition of the water pump is controlled by adjusting the stroke of the second section closing cartridge valve CV 6.
When the speed regulator does not fail, namely the input side of the end a of the electromagnetic valve EV03 in the pilot-operated electro-hydraulic reversing valve is not input, the first cartridge valve CV1 and the second cartridge valve CV2 are opened, the first accident cartridge valve CV3 and the second accident cartridge valve CV4 are closed, and at the moment, the adjustment of the fastest shutdown rate under the working condition of the water pump is still realized by adjusting the second sectional closing cartridge valve CV 6.
The working principle of the mechanical overspeed hydraulic signal oil port K1 is as follows:
the hydraulic oil port K1 of the mechanical overspeed is connected with the electromagnetic valve EV03 in the pilot-operated electrohydraulic reversing valve, the hydraulic oil port K1 of the mechanical overspeed receives a pressure oil signal from the mechanical overspeed protection device and is used as the final protection barrier for unit protection, when the unit overspeed protection device acts, the pressure oil signal of the mechanical overspeed protection device disappears, the hydraulic reversing valve YD01 in the pilot-operated electrohydraulic reversing valve realizes reversing under the action of a spring, and the first cartridge valve CV1 and the second cartridge valve CV2 are closed; the first accident cartridge valve CV3 and the second accident cartridge valve CV4 are open; pressure oil from the main pressure oil source P0 enters the servomotor closing chamber through the first accident cartridge valve CV3, and the servomotor is quickly closed, so that the unit safety is protected.
Claims (9)
1. The utility model provides an overspeed protection and flow control device for pumped storage power station, includes control pressure oil circuit, connects first cartridge valve (2) on main distributing valve closes chamber (1) through the main oil circuit, connects second cartridge valve (4) on main distributing valve opens chamber (3), connects first segmentation on servomotor opens chamber (5) and closes cartridge valve (6) and second segmentation and close cartridge valve (7), its characterized in that: the hydraulic servo control system further comprises an oil return tank (8), a pilot type electrohydraulic reversing valve (9), a first section closing pilot electromagnetic valve (10) for switching a first section closing cartridge valve (6), a second section closing pilot electromagnetic valve (11) for switching a second section closing cartridge valve (7), a first accident cartridge valve (13) connected to a main pressure oil source (12) and a second accident cartridge valve (14) connected to a servomotor opening cavity (5), wherein the first cartridge valve (2) and the first accident cartridge valve (13) are respectively connected to a servomotor closing cavity (15), the second accident cartridge valve (14) is connected with the oil return tank (8), and the pilot type electrohydraulic reversing valve (9) is respectively connected with the first accident cartridge valve (13), the second accident cartridge valve (14), and control cavities of the first cartridge valve (2) and the second cartridge valve (4);
a fifth pressure gauge (26) is arranged on the control pressure oil path, and the fifth pressure gauge (26) is used for monitoring control pressure oil.
2. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the first sectional closing cartridge valve (6) and the second sectional closing cartridge valve (7) are connected with a one-way valve (16) which is used for increasing the oil quantity of the servomotor opening cavity (5) in parallel.
3. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the first sectional closing cartridge valve (6) and the second sectional closing cartridge valve (7) are also connected with a flow regulating valve (17) in parallel; and a flow regulating valve (17) for regulating the slow closing rate of the first section of the servomotor.
4. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the first sectional closing cartridge valve (6) is an adjustable sectional closing cartridge valve and is used for adjusting the quick closing speed of the second section of the servomotor.
5. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the first cartridge valve (2) is used for cutting off or communicating the main distributing valve and the servomotor; and the second cartridge valve (4) is used for cutting off or communicating the main distributing valve and the servomotor.
6. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the control cavity oil way of the first cartridge valve (2) and the control cavity oil way of the second cartridge valve (4) are provided with a first pressure switch (18) and a first pressure gauge (22), and the first pressure switch (18) is used for monitoring a pressure control signal during normal open and shut down.
7. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the control cavity oil ways of the first accident cartridge valve (13) and the second accident cartridge valve (14) are provided with a second pressure switch (19) and a second pressure gauge (23), and the second pressure switch (19) is used for monitoring accident shutdown pressure signals.
8. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the control cavity oil way of the first sectional closing cartridge valve (6) is provided with a third pressure switch (20) and a third pressure gauge (24), and the third pressure switch (20) is used for monitoring the opening and closing states of the first sectional closing cartridge valve (6).
9. An overspeed protection and flow control device for pumped-storage power stations as set forth in claim 1, wherein: the control cavity oil way of the second sectional closing cartridge valve (7) is provided with a fourth pressure switch (21) and a fourth pressure gauge (25), and the fourth pressure switch (21) is used for monitoring the opening and closing states of the second sectional closing cartridge valve (7).
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| CN110966137B (en) * | 2019-12-23 | 2021-02-05 | 国网新源控股有限公司回龙分公司 | Secondary shutdown control method for pumped storage unit |
| CN112628054B (en) * | 2020-12-17 | 2023-03-14 | 内蒙古呼和浩特抽水蓄能发电有限责任公司 | Method and system for measuring flow of water pump turbine of pumped storage unit |
| CN115875185A (en) * | 2022-11-03 | 2023-03-31 | 中国长江电力股份有限公司 | Overspeed protection device and method for hydroelectric generating set |
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Effective date of registration: 20190513 Address after: 618000 No. 18, Third Section of Lushan South Road, Deyang City, Sichuan Province Applicant after: DONGFANG ELECTRIC AUTOMATIC CONTROL ENGINEERING Co.,Ltd. Applicant after: DONGFANG ELECTRIC MACHINERY Co.,Ltd. Address before: 618000 No. 138 Jialing Jiangxi Road, Jingyang District, Deyang City, Sichuan Province Applicant before: DFEM ELECTRIC CONTROL EQUIPMENT Co.,Ltd. Applicant before: DONGFANG ELECTRIC MACHINERY Co.,Ltd. |
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